CN101006293A

CN101006293A - Torque transmission structure, traction drive transmission device, and steering device for vehicle

Info

Publication number: CN101006293A
Application number: CN 200680000600
Authority: CN
Inventors: 东崎康嘉; 吉见壮司; 梅田彰彦; 园部浩之; 盐津勇; 平山贵良
Original assignee: Mitsubishi Heavy Industries Ltd
Current assignee: Mitsubishi Heavy Industries Ltd
Priority date: 2005-02-24
Filing date: 2006-02-23
Publication date: 2007-07-25
Also published as: CN101586645A; CN101586645B

Abstract

The invention provides a variable-speed traction drive transmission device compact and having high durability. The traction drive transmission device (10) varies, by the use of traction of rolling bodies (K) arranged between an input shaft (Si) and an output shaft (So), the speed of rotation of the input shaft (Si) into a desired transmission ratio to output the result by the output shaft (So). The traction drive transmission device (10) is placed inclined so that the rotation axes of the rolling bodies (K) are not orthogonal to the axes of the input shaft (Si) and the output shaft (So), and has a load regulation cam (50) and a transmission ratio variation mechanism of a differential type using a worm gear (55). The load regulation cam (50) automatically varies a preload applied to the rolling bodies (K) according to torque of the input shaft (Si). The transmission ratio variation mechanism is connected to a retainer (40) as the traction input-output member of the rolling bodies (K) and varies a transmission ratio by controlling the speed of rotation of the retainer (40).

Description

Torque transmission structure, traction drive transmission device and Vehicular steering apparatus

Technical field

The present invention relates to for example to be applicable to the torque transmission structure of the steering control system etc. of vehicle, and, relate to the traction drive transmission device and the Vehicular steering apparatus that use this torque transmission structure.

Background technique

At present, known have a following traction drive transmission device, and its utilization acts on the tangential force on the contacting part of solid of rotation of rolling sliding mode, carries out the transmission of torque between the rotating speed of input shaft rotational speed and output shaft with gear ratio.In this traction drive transmission device, the gear ratio of output input is linear.(for example, with reference to patent documentation 1)

In addition, as can carrying out linear infinite variable speed speed change gear, known have a planet gear type speed change gear.(for example, with reference to patent documentation 2)

In addition, known have a following Vehicular steering apparatus, it slows down the gear ratio of temporary transient speedup by making retarder on the torque drive path that has as the steering transmission system of the differential transmission mechanism of speed increaser function, finally makes the velocity ratio of steering control system integral body turn back to for example 1: 1.(for example, with reference to patent documentation 3)

Patent documentation 1: the spy opens the 2003-278866 communique

Patent documentation 2: open flat 1-139161 communique in fact

Patent documentation 3: the spy opens the 2004-58896 communique

But, above-mentioned existing traction drive transmission device or planet gear type speed change gear because the gear ratio of input output is fixed linearity, so, in a speed change gear, can not realize with predefined linear speed regulating than different gear ratio arbitrarily.

In addition, make speed increaser and retarder in torque transmission system etc. and the velocity ratio of steering control system integral body is set for the Vehicular steering apparatus of desirable value, be arranged in the limited space of vehicle if consider, then same axle is gone up and elongation vertically because speed increaser and retarder are arranged in, and therefore has problems aspect miniaturization.

Under such background, wish a kind of small-sized and torque transmission structure that serviceability is high of exploitation, can use in the torque drive path of for example Vehicular steering apparatus etc., produce the axial push power that changes corresponding to the torque of transmission.

In addition, wish a kind of small-sized and traction drive transmission device that serviceability is high of exploitation and use the Vehicular steering apparatus of this traction drive transmission device that this traction drive transmission device can make the gear ratio of input output between centers freely change.

In addition, wish a kind of small-sized and traction drive transmission device that serviceability is high of exploitation and use the Vehicular steering apparatus of this traction drive transmission device, this traction drive transmission device can make the gear ratio of input output between centers freely change, and can increase the driving torque of output shaft.

Summary of the invention

The present invention is in view of the above problems and proposes, and its purpose is to provide the traction drive transmission device of a kind of small-sized and torque transmission structure that serviceability is high, the small-sized and variable speed that serviceability is high and uses the Vehicular steering apparatus of said structure and device.

In addition, the object of the present invention is to provide a kind of traction drive transmission device of the small-sized and variable speed that serviceability is high and use the Vehicular steering apparatus of this traction drive transmission device, this traction drive transmission device can make the gear ratio of input output between centers freely change, and can increase the driving torque of output shaft.

The present invention adopts following method in order to solve the above problems.

The torque transmission structure of first aspect present invention, carrying out the torque transmission between the opposing side of two parts of configuration rotatably on the same axis, it is characterized in that, between described opposing side, be provided with the recess that many group section configurations form plane of inclination or curved surface, set compression relief cam in this recess space.

According to such torque transmission structure, owing between described opposing side, be provided with the recess that many group section configurations form plane of inclination or curved surface, set compression relief cam in this recess space, therefore, be assembled into the effect of the small-sized compression relief cam between the opposing side by axial length with prolonging hardly, can produce the axial push power that changes corresponding to the torque of transmission.

The traction drive transmission device of second aspect present invention, the traction of the rolling element of utilization between input shaft and output shaft, make described input shaft rotational speed be varied to desirable gear ratio and from the output of described output shaft, it is characterized in that, make the nonopiate earth tilt configuration of axis of rotation axis and the described input shaft and the described output shaft of described rolling element, and have: pre-pressure regulator, it makes the precompressed that imposes on described rolling element change automatically corresponding to the torque of described input shaft; The gear ratio changeable mechanism of differential type, the traction inputoutput unit of itself and described rolling element links, and carries out the rotating speed control of this traction inputoutput unit and makes described gear ratio variation.

According to such traction drive transmission device, owing to make the nonopiate earth tilt configuration of axis of rotation axis and the input shaft and the output shaft of rolling element, and have pre-pressure regulator that the precompressed that imposes on rolling element is automatically changed corresponding to the torque of described input shaft, and control and make the gear ratio changeable mechanism of the differential type of gear ratio variation with the rotating speed that the traction inputoutput unit of rolling element links, carries out this traction inputoutput unit, therefore, pre-pressure regulator is regulated the precompressed of the rolling element that imposes on tilted configuration corresponding to the torque of input shaft.That is, the precompressed controlling mechanism produces the thrust load corresponding to driving torque, and this thrust load becomes the precompressed of rolling element to axial push.In addition, owing to have differential type gear ratio changeable mechanism, can regulate the gear ratio of input and output shaft and setting at random.

Third aspect present invention on the second aspect basis, has described output shaft is applied rotating force and increases the driving torque assisting agency of driving torque.

At this moment, by the effect of driving torque assisting agency, increase to desirable value and be output to the output shaft torque transmitted.

Fourth aspect present invention, on second aspect or third aspect basis, make the described rolling element that is equipped on the retainer between the inner ring that is provided with described input shaft and be provided with between the outer ring of described output shaft, pre-pressure regulator is set on described inner ring, and, described gear ratio changeable mechanism and described retainer are linked, thus, transmit to outer ring via the rolling element that is equipped on the rolling element holding part as output shaft as the torque of the inner ring of input shaft.At this moment, on input shaft, pre-pressure regulator corresponding to the torque of input shaft regulating action in the precompressed of rolling element, so, can when having input torque, precompressed be suppressed at inferior limit.In addition, the gear ratio changeable mechanism is with the retainer binding of drawing the transmission inputoutput unit and carry out differential Spin Control, so, the gear ratio of input and output shaft is changed.In addition, under the situation that driving torque assisting agency and the output shaft that is arranged on the outer ring link, the big torque output that will increase the driving torque of output shaft.

Fifth aspect present invention, on second aspect or third aspect basis, make and have the described rolling element that disposes on the retainer of described output shaft between the inner ring and outer ring that are provided with on the described input shaft, pre-pressure regulator is set on described retainer, and, described gear ratio changeable mechanism and described outer ring are linked, thus, as the torque of the inner ring of input shaft via the output shaft transmission of the rolling element that is equipped on the rolling element holding part to retainer.At this moment, on the retainer as output shaft, pre-pressure regulator acts on the precompressed of rolling element corresponding to the torque adjustment of input shaft, therefore, can when having input torque precompressed be suppressed at inferior limit.In addition, because the outer ring of gear ratio changeable mechanism and traction transmission inputoutput unit links and carries out differential Spin Control, so can change the gear ratio of input and output shaft.In addition, under the situation that driving torque assisting agency and the output shaft that is arranged on the retainer link, the big torque output that will increase the driving torque of output shaft.

Sixth aspect present invention, on the second aspect basis, make and have the described rolling element that disposes on the retainer of described input shaft between inner ring and be provided with between the outer ring of described output shaft, described pre-pressure regulator is set on described inner ring and links described gear ratio changeable mechanism, thus, transmit to outer ring via the rolling element that is equipped on the rolling element holding part as the torque of the retainer of input shaft as output shaft.At this moment, on inner ring, pressure regulator in the precompressed of rolling element, therefore, can not be suppressed at inferior limit with precompressed corresponding to the torque corrective action of input shaft when having input torque in advance.In addition, because the gear ratio changeable mechanism links with the inner ring that draws the transmission inputoutput unit and carries out differential Spin Control, therefore can change the gear ratio of input and output shaft.

At this moment, by formative gear portion on the outer circumferential face of described outer ring or side and with the rack pinion engagement, make the rotating torques of input shaft convert the straight line motion of rack pinion to via the outer ring of output shaft.

A eighth aspect of the present invention, on second aspect or third aspect basis, make and have the described rolling element that disposes on the retainer of described input shaft between the inner ring and outer ring that are provided with on the described output shaft, described pre-pressure regulator is set on described inner ring, and, described gear ratio changeable mechanism and described outer ring are linked, thus, as the torque of the retainer of input shaft via the rolling element that is equipped on the rolling element holding part to inner ring transmission as output shaft.At this moment, on inner ring, pre-pressure regulator acts on the precompressed of rolling element corresponding to the torque adjustment of input shaft, so, can when having input torque, precompressed be suppressed at inferior limit.In addition, the gear ratio changeable mechanism links with the outer ring of drawing the transmission inputoutput unit and carries out differential Spin Control, so can change the gear ratio of input and output shaft.In addition, owing under the situation that the output shaft that is provided with on driving torque assisting agency and the inner ring links, will increase the big torque output of the driving torque of output shaft.

A ninth aspect of the present invention, on the second aspect basis, make at the described rolling element that sets on the retainer as described output shaft between inner ring and be provided with between the outer ring of described input shaft, described pre-pressure regulator is set and links described gear ratio changeable mechanism at described inner ring.Thus, as the torque of the retainer of input shaft via the rolling element that is equipped on the rolling element holding part to retainer transmission as output shaft.At this moment, on inner ring, pre-pressure regulator comes the precompressed of regulating action in rolling element corresponding to the torque of input shaft, therefore, can when having input torque precompressed be suppressed at inferior limit.In addition, because the inner ring of gear ratio changeable mechanism and traction transmission inputoutput unit links and carries out differential Spin Control, so can change the gear ratio of input and output shaft.

At this moment, by formative gear portion on the outer circumferential face of described retainer or on the side and with the rack pinion engagement, make the rotating torques of input shaft convert the straight line motion of rack pinion to via the retainer of output shaft.

A eleventh aspect of the present invention, on the basis of the second aspect or the third aspect, make the described rolling element that is equipped on the retainer between being provided with the inner ring on the described output shaft and being provided with between the outer ring on the described input shaft, pre-pressure regulator is set on described inner ring, and, described gear ratio changeable mechanism and described retainer are linked.Thus, as the torque of the outer ring of input shaft via the rolling element that is equipped on the rolling element holding part to inner ring transmission as output shaft.At this moment, on output shaft, pre-pressure regulator comes the precompressed of regulating action in rolling element corresponding to the torque of input shaft, therefore, can when having input torque precompressed be suppressed at inferior limit.In addition, because the retainer of gear ratio changeable mechanism and traction transmission inputoutput unit links and carries out differential Spin Control, so can change the gear ratio of input and output shaft.In addition, under the situation that the output shaft that is provided with on driving torque assisting agency and the inner ring links, the big torque output of the driving torque of output shaft will be increased.

Traction drive transmission device of the present invention, the traction of the rolling element of utilization between input shaft and output shaft, make described input shaft rotational speed be varied to desirable gear ratio and from the output of described output shaft, simultaneously, described input shaft and output shaft left and right symmetrically linked and carry out two stage speed change, it is characterized in that, make the nonopiate earth tilt configuration of axis of rotation axis and the described input shaft and the described output shaft of described rolling element, and have: pre-pressure regulator, it makes the precompressed that imposes on described rolling element change automatically corresponding to the torque of the between centers that links first order speed changing portion and second level speed changing portion; The gear ratio changeable mechanism, the traction inputoutput unit of itself and described rolling element links, and carries out the rotating speed control of this traction inputoutput unit and makes described gear ratio variation.

According to such traction drive transmission device, owing to make the nonopiate earth tilt configuration of axis of rotation axis and the input shaft and the output shaft of rolling element, and has the pre-pressure regulator that makes the precompressed automatic variation that imposes on rolling element corresponding to the torque of the between centers that links first order speed changing portion and second level speed changing portion, and link with the traction inputoutput unit of rolling element and carry out the rotating speed control of this traction inputoutput unit and make the gear ratio changeable mechanism of gear ratio variation, so pre-pressure regulator is automatically regulated the precompressed that changes the rolling element that imposes on tilted configuration corresponding to the torque of the between centers that links first order speed changing portion and second level speed changing portion.In addition, owing to have differential type gear ratio changeable mechanism, can transfer the gear ratio of input and output shaft and setting arbitrarily.At this moment, owing to carry out the two-stage speed change by first order speed changing portion and second level speed changing portion, so, on identical sense of rotation, become 1: 1 based on the input/output relation that draws transmission.

A thirteenth aspect of the present invention on the basis aspect the 12, has described output shaft is applied rotating force and increases the driving torque assisting agency of driving torque.

At this moment, the effect by driving torque assisting agency makes to the output shaft torque transmitted and increases to desirable value and be output.

A fourteenth aspect of the present invention, aspect the 12 or on the basis of the 13 aspect, have: first order speed changing portion, it makes the described rolling element that is equipped on first retainer between first inner ring that is provided with described input shaft and be provided with between first outer ring that links output shaft; Second level speed changing portion, it makes the described rolling element that is equipped on second retainer between second inner ring that is provided with described output shaft and be provided with between second outer ring that links input shaft, on the axle linking department of described binding output shaft and described binding input shaft, described pre-pressure regulator is set, and, described gear ratio changeable mechanism is attached on described first retainer, described second retainer is fixed on the housing.Thus, on first order speed changing portion, as the torque of first inner ring of input shaft via the rolling element on the rolling element holding part that is provided in first retainer to transmitting as first outer ring that links output shaft.

Then, on the speed changing portion of the second level, via pre-pressure regulator to as the second outer ring torque transmitted that links input shaft, via the rolling element on the rolling element holding part that is provided in second retainer to the second inner ring transmission as output shaft.At this moment, on the axle linking department, pre-pressure regulator comes the precompressed of regulating action in the rolling element of first order speed changing portion and second level speed changing portion corresponding to the torque that links output shaft, therefore, can when having input torque precompressed be suppressed at inferior limit.In addition, because the retainer of gear ratio changeable mechanism and traction transmission inputoutput unit links and carries out differential Spin Control, so can change the gear ratio of input and output shaft.In addition, under the situation that the output shaft that is provided with on the driving torque assisting agency and second inner ring links, the big torque output of the driving torque of output shaft will be increased.

A fifteenth aspect of the present invention, aspect the 12 or on the basis of the 13 aspect, have: make the first order speed changing portion of described rolling element between first inner ring that is provided with described input shaft and first outer ring that sets on first retainer that links output shaft having; Second level speed changing portion, it makes the described rolling element that sets on second retainer with binding input shaft between second inner ring that is provided with described output shaft and second outer ring, on the axle linking department of described binding output shaft and described binding input shaft, described pre-pressure regulator is set, and, described gear ratio changeable mechanism and described first outer ring are linked, described second outer ring is fixed on the housing.Thus, on first order speed changing portion, as the torque of first inner ring of input shaft via the rolling element on the rolling element holding part that is provided in first retainer to as the first retainer transmission that links output shaft.

Then, on the speed changing portion of the second level, via pre-pressure regulator to as the second retainer torque transmitted that links input shaft, via the rolling element on the rolling element holding part that is provided in second retainer to the second inner ring transmission as output shaft.At this moment, on the axle linking department, pre-pressure regulator comes the precompressed of regulating action in the rolling element of first order speed changing portion and second level speed changing portion corresponding to the torque that links output shaft, therefore, can when having input torque precompressed be suppressed at inferior limit.In addition, the gear ratio changeable mechanism links with the outer ring of drawing the transmission inputoutput unit and carries out differential Spin Control, therefore, can change the gear ratio of input and output shaft.In addition, owing under the situation that the output shaft that is provided with on the driving torque assisting agency and second inner ring links, will increase the big torque output of the driving torque of output shaft.

A sixteenth aspect of the present invention, aspect the 12 or on the basis of the 13 aspect, have: first order speed changing portion, it makes has the described rolling element that sets on first retainer of described input shaft between being provided with between first inner ring and first outer ring that links output shaft; Second level speed changing portion, it makes has the described rolling element that sets on second retainer of described output shaft between being provided with between second inner ring and second outer ring that links input shaft, on the axle linking department of described binding output shaft and described binding input shaft, described pre-pressure regulator is set, and, described gear ratio changeable mechanism and described first outer ring are linked, described second outer ring is fixed on the housing.Thus, on first order speed changing portion, as the torque of first retainer of input shaft via the rolling element on the rolling element holding part that is provided in first retainer to as the first inner ring transmission that links output shaft.

Then, on the speed changing portion of the second level, via pre-pressure regulator to as the second retainer torque transmitted that links input shaft, via the rolling element on the rolling element holding part that is provided in second retainer to the second retainer transmission as output shaft.At this moment, on the axle linking department, pre-pressure regulator comes the precompressed of regulating action in the rolling element of first order speed changing portion and second level speed changing portion corresponding to the torque that links output shaft, therefore, can when having input torque precompressed be suppressed at inferior limit.In addition, the outer ring of gear ratio changeable mechanism and traction transmission inputoutput unit links also carries out differential Spin Control, so, can change the gear ratio of input and output shaft.In addition, under the situation that driving torque assisting agency and the output shaft that is arranged on second holding part link, the big torque output that will increase the driving torque of output shaft.

A seventeenth aspect of the present invention, aspect the 12 or on the basis of the 13 aspect, have: first order speed changing portion, it makes the described rolling element that is equipped on first retainer between being provided with first inner ring that links output shaft and being provided with between first outer ring of described input shaft; Second level speed changing portion, it makes the described rolling element that is equipped on second retainer between being provided with second inner ring that links input shaft and being provided with between second outer ring on the described output shaft, on the axle linking department of described binding output shaft and described binding input shaft, described pre-pressure regulator is set, and, described gear ratio changeable mechanism and described first retainer are linked, described second retainer is fixed on the housing.Thus, on first order speed changing portion, as the torque of first outer ring of input shaft via the rolling element on the rolling element holding part that is provided in first retainer to as the first inner ring transmission that links output shaft.

Then, on the speed changing portion of the second level, to as the second inner ring torque transmitted that links input shaft, transmit to second outer ring as output shaft via the rolling element on the rolling element holding part that is provided in second retainer via pre-pressure regulator.At this moment, on the axle linking department, pre-pressure regulator comes the precompressed of regulating action in the rolling element of first order speed changing portion and second level speed changing portion corresponding to the torque that links output shaft, so, can when having input torque, precompressed be suppressed at inferior limit.In addition, because the retainer of gear ratio changeable mechanism and traction transmission inputoutput unit links and carries out differential Spin Control, so can change the gear ratio of input and output shaft.In addition, under the situation that driving torque assisting agency and the output shaft that is arranged on second outer ring link, the big torque output that will increase the driving torque of output shaft.

Traction drive transmission device of the present invention, the traction of the rolling element of utilization between input shaft and output shaft, make described input shaft rotational speed be varied to desirable gear ratio and from the output of described output shaft, simultaneously, link described input shaft and output shaft and carry out two stage speed change, it is characterized in that, make the nonopiate earth tilt configuration of axis of rotation axis and the described input shaft and the described output shaft of described rolling element, and have: pre-pressure regulator, it makes the precompressed that imposes on described rolling element change automatically corresponding to the torque of the between centers that links first order speed changing portion and second level speed changing portion; The gear ratio changeable mechanism, the traction inputoutput unit of itself and described rolling element links, carry out the rotating speed control of this traction inputoutput unit and described gear ratio is changed, link the traction inputoutput unit of described first order speed changing portion and described second level speed changing portion also integrated, and, the gear ratio of two speed changing portions is provided with difference.

According to such traction drive transmission device, owing to make the nonopiate earth tilt configuration of axis of rotation axis and the described input shaft and the described output shaft of described rolling element, and has the pre-pressure regulator that makes the precompressed automatic variation that imposes on described rolling element corresponding to the torque of the between centers that links first order speed changing portion and second level speed changing portion, and the gear ratio changeable mechanism of described gear ratio variation is controlled and made to the rotating speed that carries out this traction inputoutput unit with the traction inputoutput unit binding of described rolling element, link the traction inputoutput unit of described first order speed changing portion and described second level speed changing portion also integrated, gear ratio to two speed changing portions is provided with difference, thereby pre-pressure regulator is automatically adjusted the precompressed that changes the rolling element that imposes on tilted configuration according to the torque of the between centers that links first order speed changing portion and second level speed changing portion.In addition, owing to carry out the two-stage speed change by first order speed changing portion and second level speed changing portion, the traction inputoutput unit of two speed changing portions is integrated and gear ratio is provided with difference, therefore, can adjust the gear ratio of input and output shaft and setting arbitrarily by differential type gear ratio changeable mechanism, and, the input/output relation based on the traction transmission can be become 1: 1 in identical sense of rotation.

A nineteenth aspect of the present invention on the basis of the tenth eight aspect, has: first order speed changing portion, and it makes has the described rolling element that sets on first retainer of described input shaft between being provided with between first inner ring that links output shaft and the outer ring binding parts; Second level speed changing portion, it makes has the described rolling element that sets on second retainer of described output shaft between being provided with between second inner ring that links input shaft and the described outer ring binding parts, on the axle linking department of described binding output shaft and described binding input shaft, described pre-pressure regulator is set, and described gear ratio changeable mechanism and described outer ring link parts and link.Thus, on first order speed changing portion, as the torque of first retainer of input shaft via the rolling element that on the rolling element holding part of first retainer, sets to as the first inner ring transmission that links output shaft.Then, on the speed changing portion of the second level, via pre-pressure regulator to as the second inner ring torque transmitted that links input shaft, via the rolling element that on the rolling element holding part of second retainer, sets to the second retainer transmission as output shaft.At this moment, on the axle linking department, pre-pressure regulator comes the precompressed of regulating action in the rolling element of first order speed changing portion and second level speed changing portion corresponding to the torque that links output shaft, therefore, can when having input torque precompressed be suppressed at inferior limit.In addition, gear ratio on two speed changing portions is provided with difference, therefore, links and carry out differential Spin Control, can change the gear ratio of input and output shaft by changeable mechanism and outer ring being linked parts.

A twentieth aspect of the present invention, in aspect second aspect～19 on each the basis, described pre-pressure regulator is the torque transmission structure that carries out the torque transmission between the opposing side of two parts that dispose around same axis rotation, preferably between described opposing side, be provided with the recess that many group section configurations form plane of inclination or curved surface, set compression relief cam in this recess space.

In addition, the of the present invention the 20 on the one hand, aspect second aspect～20 on each the basis, preferred described gear ratio changeable mechanism is the worm gear with driving source that can Spin Control.This worm gear has the failure protection function when output shaft is imported.

In addition, the 22 aspect of the present invention, second aspect～20 on the one hand on each the basis, preferred described gear ratio changeable mechanism be with described input shaft and the coaxial hollow motor that sets of described output shaft epicyclic type mechanism as driving source, thus, the outside dimension of device is diminished.

In addition, the 23 aspect of the present invention, aspect second aspect～5th, in the eight aspect, the tenth one side, the 13 aspect～the 17 aspect, the 20 aspect～the 22 aspect on each the basis, preferred described driving torque assisting agency is the worm gear with Vidacare corp of easy control.

Vehicular steering apparatus of the present invention is characterized in that, driver's steering operation via each described traction drive transmission device in a second aspect of the present invention～the 23 aspect to the Steering Wheel transmission of vehicle.

According to such Vehicular steering apparatus, the torque of the steering shaft that is produced by steering comes the precompressed of regulating action in rolling element by pre-pressure regulator, big precompressed when therefore, the minimal precompressed that does not produce steering torque from when keeping straight on varies to anxious steering.Therefore, rolling element can prevent big precompressed continuous action relatively.In addition, owing to differential Spin Control is carried out in the gear ratio changeable mechanism and the retainer binding of traction transmission inputoutput unit, so can change the gear ratio of input and output shaft, and, if adopt the towing gear of one-level speed change that axial length is shortened, if adopt the towing gear of two stage speed change then to make input/output relation become 1: 1 in identical sense of rotation.

In addition, under the situation with the driving torque assisting agency that output shaft is applied driving torque, the increase along with the driving torque of exporting from output shaft can alleviate driver's steering force.

According to above-mentioned the present invention, the torque transmission structure of a kind of axial weak point and miniaturization can be provided, it is arranged between the opposing side of two parts of same axis rotation, by setting compression relief cam between a plurality of recesses that form plane of inclination or curved surface in section configuration, via compression relief cam with torque from one-level side (input side) parts to secondary side (output shaft side) parts transmission, and, corresponding to this driving torque, change from the axial push power (thrust load) of one-level side component to the effect of secondary side component.

Adopt the traction drive transmission device of above-mentioned torque transmission structure, can make precompressed (axial push power) change of the rolling element that acts on the traction transmission corresponding to the driving torque between the input and output shaft.Therefore, in the traction drive transmission device of the driving torque change between input and output shaft, always do not act on big precompressed, therefore, can prolong the life-span of rolling element rolling.Its result is carrying out the traction drive transmission device of torque transmission to output shaft from input shaft via rolling element, can prolong the remarkable result that obtains reliability and serviceability raising by the life-span of rolling element.

In addition, because the gear ratio changeable mechanism with differential type by control gear ratio changeable mechanism, can obtain gear ratio arbitrarily between input shaft and output shaft.Particularly, as long as adopt, just can provide boundary dimension little traction drive transmission device with the hollow motor that sets coaxially with input shaft and output shaft epicyclic type mechanism as driving source.

In addition, under situation, can make from the driving torque of output shaft output and increase to desirable value and output with the driving torque assisting agency that output shaft is applied driving torque.

In addition, Vehicular steering apparatus with above-mentioned traction drive transmission device, when not carrying out steering and stop or when craspedodrome etc., make the precompressed that acts on rolling element for minimum, the precompressed that changes corresponding to the cogging of the input shaft that produces based on steering (steering shaft) side affacts on the rolling element, therefore, equipment miniaturization, the life-span by rolling element prolongs and obtains the significant more effect that reliability and serviceability also improve simultaneously.Particularly, employing with input shaft and the coaxial hollow motor that sets of output shaft as the little towing gear of boundary dimension of the epicyclic type mechanism of driving source, can provide to be applicable to the Vehicular steering apparatus that environment is set that the narrow and small strictness in space is set.

And, owing to have the gear ratio changeable mechanism of differential mode,, therefore, can suitably set best gear ratio corresponding to the steering situation so the gear ratio of input output between centers is at random changed.Particularly, when steerings such as parking in lateral, it is big that gear ratio becomes, can obtain big steering angle with few steering amount, when steering such as running at high speed, gear ratio diminishes, craspedodrome increase etc., be set to best gear ratio as long as control the gear ratio variable control mechanisms, promptly can improve the operability of steering gear.

In addition, under situation, can make from the driving torque of output shaft output and increase to desirable value and output with the driving torque assisting agency that output shaft is applied driving torque.Therefore, can provide the steering force that alleviates the driver, the Vehicular steering apparatus that improves operability.

Description of drawings

Fig. 1 is the sectional drawing of first mode of execution of expression traction drive transmission device of the present invention;

Fig. 2 is the stereogram of summary configuration example of the Vehicular steering apparatus of the expression traction drive transmission device that is assembled with Fig. 1;

Fig. 3 is the sectional drawing of first variation of the traction drive transmission device of presentation graphs 1;

Fig. 4 is the sectional drawing of second variation of the traction drive transmission device of presentation graphs 1;

Fig. 5 is the sectional drawing of the 3rd variation of the traction drive transmission device of presentation graphs 1;

Fig. 6 is the sectional drawing of the 4th variation of the traction drive transmission device of presentation graphs 1;

Fig. 7 is the sectional drawing of the 5th variation of the traction drive transmission device of presentation graphs 1;

Fig. 8 is the sectional drawing of second mode of execution of expression traction drive transmission device of the present invention;

Fig. 9 is the sectional drawing of first variation of the traction drive transmission device of presentation graphs 8;

Figure 10 is the sectional drawing of second variation of the traction drive transmission device of presentation graphs 8;

Figure 11 is the sectional drawing of the 3rd variation of the traction drive transmission device of presentation graphs 8;

Figure 12 is the sectional drawing of the 4th variation of the traction drive transmission device of presentation graphs 8;

Figure 13 is the sectional drawing of the 3rd mode of execution of expression traction drive transmission device of the present invention;

Figure 14 is the sectional drawing of the 4th mode of execution of expression traction drive transmission device of the present invention;

Figure 15 is the sectional drawing of first variation of the traction drive transmission device of expression Figure 14;

Figure 16 is the sectional drawing of second variation of the traction drive transmission device of expression Figure 14;

Figure 17 is the sectional drawing of the 3rd variation of the traction drive transmission device of expression Figure 14;

Figure 18 is the sectional drawing of the 5th mode of execution of expression traction drive transmission device of the present invention;

Figure 19 is the sectional drawing of first variation of the traction drive transmission device of expression Figure 18;

Figure 20 is the sectional drawing of second variation of the traction drive transmission device of expression Figure 18;

Figure 21 is the sectional drawing of the 3rd variation of the traction drive transmission device of expression Figure 18.

Embodiment

Below, describe based on the mode of execution of accompanying drawing torque driving mechanism of the present invention, traction drive transmission device and Vehicular steering apparatus.

First mode of execution

Fig. 1 is the sectional drawing of first mode of execution of expression traction drive transmission device of the present invention.This traction drive transmission device (hereinafter referred to as " speed change gear ") 10 has that utilization makes input shaft Si between the traction of the rolling element K between input shaft Si and the output shaft So rotation speed change becomes desirable gear ratio and from the function of output shaft So output.

Traction is to affact as the solid of rotation of rolling sliding mode and be equipped with the tangential force of the contacting part of a plurality of rolling element K, in illustrated example, make a plurality of rolling element K of keeping by retainer 40 between between the inner ring 20 that is provided with input shaft Si and the outer ring 30 that is provided with output shaft So, formation traction drive mechanism TR.The rheological properties of the oil film that the surface of contact of this traction drive mechanism TR by inner ring 20 and outer ring 30 and rolling element K forms, can be from inner ring 20 via rolling element K with transmission of torque to the outer ring 30.When this torque transmission, rolling element K revolves round the sun in the outside at inner ring 20 in rotation.

Traction drive mechanism TR is accommodated in the housing 11 of speed change gear 10, and the input shaft Si and the output shaft So that are configured on the same axis are outstanding outside from the two end part of housing 11.

Inner ring 20 is two sections structures of cutting apart, owing to carry out the torque transmission between the opposing side of two parts that dispose around same axis rotation, so be equipped with compression relief cam 50.That is, inner ring 20 is divided into input axial region 21 and inner ring portion 22, is provided with many group recesses 23 between opposing side 21a, the 22a of input axial region 21 and inner ring portion 22, and its placement forms the compression relief cam 50 of cylindrical shape.This recess 23 is that a pair of slot part that the symmetrical position at opposing side 21a, 22a is provided with is respectively formed one group and the space that forms, and compression relief cam 50 is being accommodated in this space by the moving state of skid.Such recess 23 is radial equally spacedly at circumferencial direction many groups is set from the axle center, but this quantity can suitably be selected according to many conditions.In addition, in illustrated example, be provided with four groups of recesses 23 of spacings with 90 degree at circumferencial direction, each recess 23 makes compression relief cam 50 phase mutual noninterferences and is arranged on the position of the suitable distance in distance axis center.

In addition, the section configuration of recess 23 forms plane of inclination or curved surface.In illustrated example, being provided with isosceles triangle on opposing side 21a, 22a is the slot part of section configuration separately, overlaps the recess 23 that forms the rectangular cross section shape by making relative a pair of slot part.In addition, the slot part that forms recess 23 need not to be provided on the symmetrical position of opposing side 21a, 22a, as long as can form recess between opposing side.

In addition, the input axial region 21 of inner ring 20 is rotatably supported on the housing 11 via bearing 12, and not shown torque the source takes place links with the input axial region 21 that is projected into housing 11 outsides.In addition, the symbol 13 among the figure is oil sealings, the 14th, and at the leaf spring of pushing input axial region 21 vertically, the 24th, be fixed on the inboard connected element on the outer circumferential face of inner ring portion 22.

Its result, the compression relief cam 50 of the cylindrical shape that is provided with at recess 23 when when input axial region 21 is imported, utilizes wedge effect to produce power to axial push inner ring portion 22, be thrust load.This thrust load changes corresponding to the size of the shaft torque of importing to input axial region 21.Therefore, form a plurality of recesses 23 between the face that the input axial region 21 of configuration and output axial region 22 these two parts are relative rotating around same axis, set compression relief cam 50 and carry out the torque transmission at each recess 23, thus, become the torque transmission structure that changes the thrust load that acts on inner ring portion 22 corresponding to cogging to the input of input axial region.Such torque transmission structure is because the compression relief cam 50 of cylindrical shape between opposing side 21a, 22a, can inferior limit suppress axial prolongation.Such torque driving mechanism in traction drive mechanism TR, makes the pre-pressure regulator that the precompressed that imposes on rolling element K automatically changes and works as the torque corresponding to input shaft Si.

Retainer 40 is provided with the rolling element holding part 42 of pectination in the form of a ring interior week of main body 41 roughly, main body 41 is to be rotatably supported in parts on the housing 11 via pair of bearings 12.The rolling element K of configuration is by comb section clamping and tapered roller that can rotation on rolling element holding part 42, and the axis of its rotation axis and input shaft Si and output shaft So is non-orthogonal and tilt.Routine connected element 24 and outside connected element 32 constituted the tapered roller bearing that rolling element K can one side rotation be revolved round the sun between two

connected elements

24,32 on one side in this rolling element K utilized, described inboard connected element 24 rollably supports interior all sides of rolling element K, described outside connected element 32 is fixed in the outer ring portion 31 of outer ring 30 described later, rollably supports the face of outer circumferential side.

In this tapered roller bearing, on the surface of contact of rolling element K and inboard connected element 24 and rolling element K and rolling element K and outside connected element 32, form thin oil film, carry out the torque transmission by the traction transmission.In addition, on the rolling element holding part 42 that keeps rolling element K, being not limited to above-mentioned pectination, also can be the various variation of ladder shape etc. for example.

Outer ring 30 is that outer ring portion 31 is the parts of one with output axial region 33, and output axial region 33 is rotatably supported on the housing 11 via bearing 12.In addition, the output axial region 33 of the outstanding housing 11 outsides tooth bar of Vehicular steering apparatus for example; Gearing is such, links with the device of not shown slave end.

In addition, outer ring portion 33 is parts of the roughly ring-type of an end opening, and the side face side is fixed with the outside connected element 32 that constitutes above-mentioned tapered roller bearing within it.

Above-mentioned retainer 40 has the gear part 41a in the outer circumferential face formation of main body 41, this gear part 41a and worm gear 55 engagements and the binding of working as the gear ratio changeable mechanism.This worm gear 55 has not shown driving sources such as motor, can variablely control to desirable rotating speed.Promptly, owing to make the rotation speed change of the retainer 40 that rotates integratedly with the revolution that constitutes the rolling element K of tapered roller bearing by the rotating speed of control worm gear 55, so, become the gear ratio changeable mechanism of the differential type that the gear ratio that makes between input shaft Si and the output shaft So changes.In other words, retainer 40 is to utilize traction to carry out the constituting component of the traction drive mechanism TR of torque transmission, so, as if worm gear 55 and retainer 40 being linked and carrying out rotating speed and control, then become the gear ratio changeable mechanism that makes the transformable differential type of gear ratio, this retainer 40 is influence traction inputoutput units with regard to moving that rolling element K is drawn.

The speed change gear 10 of Gou Chenging is not having on the input shaft Si under the situation of input torque like this, just from the active force of leaf spring 14, makes precompressed that rolling element K applied (in figure as shown by arrows) be minimum value by this application of force as axial pushing force.Tilt owing to the axis of the rotation axis of rolling element K and input shaft Si and output shaft So is non-orthogonal, so this precompressed is to be the power that component acts on surface of contact with axial pushing force.In addition, in order to stop moving or compression relief cam 50 is remained in the recess 23 vertically such as input shaft Si, the active force of this leaf spring 14 necessitates.

When being subjected to torque on the input shaft Si, the precompressed regulatory function that corresponding to input torque precompressed is changed owing to the compression relief cam 50 between performance opposing side 21a, the 22a is so add to the precompressed of rolling element K and torque proportional and rise from inner ring portion 22.Its result utilizes to be fixed on the inboard connected element 24 of inner ring portion 22 and the traction between the rolling element K, and rolling element K rotation is on one side revolved round the sun around the outside of inner ring portion 22 with retainer 40 one on one side.And the outside that utilizes rolling element K and be fixed on outer ring portion 31 links the traction between the parts 32, and output shaft So rotation is transmitted and made to torque to outer ring portion 31.At this moment, the sense of rotation of output shaft So is the direction opposite with input shaft Si.

At this moment, by worm gear 55 is rotated with desirable rotating speed, with the rotating speed of the retainer 40 of its engagement, be that the revolution rotating speed of rolling element K is affected and changes, therefore, utilize rotating speed with the output shaft So of the traction rotation of this rolling element K also to be subjected to same influence and change.

Therefore, the rotating speed of input shaft Si under the situation of output shaft So output, can access the desirable gear ratio that changes corresponding to the rotating speed of worm gear 55 at the traction drive mechanism TR that links via the worm gear 55 with the variable control that can carry out rotating speed.That is, the gear ratio between the input and output shaft is not linear, can fixed scope select arbitrarily gear ratio and set.

In addition, act on the precompressed of rolling element K, under the situation that does not have the torque input on the input shaft Si, become the minimum value that causes by the application of force of leaf spring 14, so, the big precompressed that produces when rolling element K does not always act on the torque transmission relatively, therefore, can prolong the life-span of rolling element K.

In addition, above-mentioned precompressed is regulated owing to realizing by the structure that sets the compression relief cam 50 of cylindrical shape parts between input axial region 21 and inner ring portion 22, so become the midget plant that speed change gear 10 can not maximize at axially-extending.

And the speed change gear 10 of above-mentioned formation is because the quantity of the bearing that needs is fewer, so can make the assembling when making become simple.In addition, when under identical condition, comparing, owing to can turn round in lower zone at the rotating speed of worm gear 55, can reduce running noise, and, can the face pressure-controlled of rolling element K is lower, also can make the driving torque of the input shaft Si that sets compression relief cam 50 also set lowlyer, favourable to working life and serviceability aspect.

Fig. 2 is the summary of Vehicular steering apparatus ST is represented in expression as the suitable example of above-mentioned speed change gear 10 a stereogram.

Vehicular steering apparatus ST is used to operate the direction of travel of vehicle and the device of turning, and the steering operation by rotation steering tiller 60 can make the direction of

Steering Wheel

61,61 change.The operation of steering tiller 60 is input to speed change gear 10 as the rotating torques of top steering shaft 62, is made the Chi Tiao ﹠amp that links with bottom steering shaft 63 by the output torque of speed change at this speed change gear 10; Gearing 64 actions.Its result is with Chi Tiao ﹠amp; The not shown bindiny mechanism that gearing 64 links can link with tooth bar, and the direction of

Steering Wheel

61,61 is changed to desirable direction.

In such Vehicular steering apparatus ST, top steering shaft 62 links with the input shaft Si of speed change gear 10, and bottom steering shaft 63 links with the output shaft So of speed change gear 10.

Therefore, when carrying out steering operation, transmit to input shaft Si from top steering shaft 62 by the torque that the operation of steering tiller 60 produces, become the torque of desirable gear ratio to transmit and to make tooth bar to bottom steering shaft 63 from output shaft So in speed change gear 10 inner conversions; Gearing 64 actions.

Therefore, under the not operated situation of steering tiller 60, for example when stopping or when keeping straight on etc., owing on top steering shaft 62 and input shaft Si, there is not torque, so, affact the precompressed minimum of rolling element K.Like this, can prolong the life-span of rolling element K effectively, improve serviceability and the reliability of Vehicular steering apparatus ST.

In addition, under the situation that the operation quantitative change of steering tiller 60 is big during low speed driving like that such as for example parking in lateral,, then can obtain big steering angle with little lever operated amount if the rotating speed of control worm gear 55 increases gear ratio.That is, if make the rotating speed increase of input shaft Si and export the rotating speed of regulating worm gear 55 in this wise, then owing to little lever operated amount (rotating speed of top steering shaft 62) speedup and to 63 outputs of bottom steering shaft, so can increase tooth bar from output shaft So; The tooth bar amount of movement of gearing 64 also changes turning to of

Steering Wheel

61,61 significantly, therefore, improves the operability of Vehicular steering apparatus ST.

Then, based on Fig. 3 first variation of the speed change gear of above-mentioned first mode of execution is described, in addition, the part mark identical symbol identical with above-mentioned mode of execution omits its detailed description.

For the speed change gear 10A that in this variation, illustrates, following aspect is different with above-mentioned mode of execution, promptly, the inner ring 20A that is provided with input shaft Si is structure as a whole, the retainer 40A that is provided with output shaft So is two-part segmenting structure, between the mating face, set compression relief cam 50, and the worm gear 55 of gear ratio changeable mechanism links with outer ring 30A.

That is, the retainer 40A that will have output shaft So forms and is divided into holding part main body 43 and output axial region 44 two-part segmenting structures, sets the rolling element K of tapered roller on the rolling element holding part 42 of the pectination that is provided with on the holding part main body 43.And, between opposing side 43a, the 44a of holding part main body 43 and output axial region 44, be equipped with the compression relief cam 50 that works as above-mentioned pre-pressure regulator.

In addition, make precompressed (among the figure shown in the arrow) generation effect and make rolling element K between inner ring 20A that is provided with input shaft Si and outer ring 30A, and carry out between inner ring 20A and retainer 40A, setting thrust-bearing 15 with the relative rotation based on the torque transmission of drawing.And, the gear part 30a engagement that the worm gear of gear ratio changeable mechanism 55 and outer circumferential surface at outer ring 30A form and linking.In addition, the symbol 12 among the figure is bearings, the 13rd, and oil sealing, the 14th, leaf spring, the 16th, tapered roller bearing.

In the speed change gear 10A that constitutes like this, transmit to output axial region 44 via being provided in the rolling element K on the rolling element holding part 42 as the output shaft So of retainer 40A as the torque of the inner ring 20A of input shaft Si.At this moment, in retainer 40A,, can when having input torque, precompressed be suppressed at inferior limit because compression relief cam 50 acts on the precompressed of rolling element K corresponding to the torque adjustment of input shaft Si as output shaft So.In addition, the precompressed of this moment is regulated by compression relief cam 50, produces by the thrust load f that acts on the thrust-bearing 15 from holding part main body 43.In addition, because the gear part 30a of the worm gear 55 of gear ratio changeable mechanism and the outer ring 30A of traction inputoutput unit links and carries out differential Spin Control, so can change the gear ratio of input and output shaft.

And the speed change gear 10A of above-mentioned formation has the identical advantage of sense of rotation of input and output shaft.In addition, when identical condition compares, particularly since the face of rolling element K can be constrained make quite low, so be favourable aspect working life and the serviceability.

Then, describe for second variation of the speed change gear of first mode of execution based on Fig. 4.In addition, the part mark identical symbol identical with above-mentioned mode of execution omits its detailed description.

For the speed change gear 10B that in this variation, illustrates, has the rolling element holding part 42 that pectination is set on the retainer 40B of input shaft Si, make the rolling element K that on this rolling element holding part 42, sets between inner ring 20B that becomes two-part segmenting structure and outer ring 30B as output shaft So, the compression relief cam 50 of pre-pressure regulator is set between the opposing side of inner ring 20B, and links the worm gear 55 of gear ratio changeable mechanism.

At this moment, inner ring 20B is divided into the 22B of inner ring portion and gear forms axial region 25 two-part, form the helical spring 17 that is equipped with compression relief cam 50 between opposing side 22b, the 25b of axial region 25 and is defined as minimum precompressed at the 22B of inner ring portion and gear, gear part 25a that on the outer circumferential face of gear formation portion 25, forms and also binding of the worm gear of gear ratio changeable mechanism 55 engagements.

In addition, also can be on as the outer circumferential face of the outer ring 30B of output shaft So formative gear portion 34, for example, make this gear part 34 obtain converting to straight-line output with rack pinion 70 engagements with rotatablely moving.At this moment, also can be in the side of outer ring 30B formative gear portion 34.

In addition, the symbol 12 among the figure is bearings, the 13rd, and oil sealing, the 15th, thrust-bearing, the 16th, tapered roller bearing.

In the speed change gear 10B that constitutes like this, transmit to outer ring 30B via the rolling element K that is provided on the rolling element holding part 42 as output shaft So as the torque of the retainer 40B of input shaft Si.At this moment, in inner ring 20B, because compression relief cam 50 comes the precompressed of regulating action in rolling element K corresponding to the torque of input shaft Si, so can when having input torque, precompressed be suppressed at inferior limit.In addition, because the gear part 25a binding of the gear formation portion 25 that the worm gear 55 of gear ratio changeable mechanism and the inner ring 20B that will draw inputoutput unit are cut apart and carry out differential Spin Control, so, can change the gear ratio of input and output shaft.

In addition, the speed change gear 10B of above-mentioned formation not only has the identical advantage of sense of rotation of input and output shaft, because the quantity of the bearing that needs get final product less, so the assembling can make manufacturing the time becomes simple.In addition, when under identical condition, comparing, owing to can lower scope turn round at the rotating speed of worm gear 55, so can reduce running noise, and then can the face pressure-controlled of rolling element K is lower, also can make the driving torque of the input shaft Si that sets compression relief cam 50 also set lowlyer, so also be favourable aspect working life and the durability.Especially, if form rack pinion 70 and built-in Chi Tiao ﹠amp are set; The structure of gear mechanism then can make the further miniaturization of Vehicular steering apparatus.

Then, based on Fig. 4 the 3rd variation of the speed change gear of above-mentioned first mode of execution is described, in addition, the part mark identical symbol identical with above-mentioned mode of execution omits its detailed description.

In the speed change gear 10C of this variation explanation, has the rolling element holding part 42 that pectination is set on the retainer 40C of input shaft Si, make the rolling element K that on this rolling element holding part 42, sets between inner ring 20C that is provided with output shaft So and outer ring 30C, on inner ring 20C, compression relief cam 50 is set, and worm gear 55 is attached on the 30C of outer ring as the gear ratio changeable mechanism as pre-pressure regulator.

At this moment inner ring 20C is divided into the 22C of inner ring portion and output axial region 26 two-part, is equipped with the helical spring 17 of compression relief cam 50 and the minimum precompressed of regulation between opposing side 22c, the 26c of 22C of inner ring portion and output axial region 26.

In the speed change gear 10C that constitutes like this, transmit to the 22C of inner ring portion via being provided in the rolling element K on the rolling element holding part 42 as the inner ring 20C of output shaft So as the torque of the retainer 40C of input shaft Si.At this moment, in inner ring 20C, because compression relief cam 50 comes the precompressed of corrective action in rolling element K corresponding to the torque of input shaft Si, so can when having input torque, precompressed be suppressed at inferior limit.In addition, because the worm gear 55 of gear ratio changeable mechanism links with the gear part 30a that forms on the outer ring 30C of traction inputoutput unit and carries out differential Spin Control, so, can change the gear ratio of input and output shaft.

In addition, the speed change gear 10C of above-mentioned formation not only has the identical advantage of sense of rotation of input and output shaft, because the quantity of the bearing that needs get final product less, so the assembling can make manufacturing the time becomes simple.Especially, when under identical condition, comparing, owing to can lower scope turn round at the rotating speed of worm gear 55, so can reduce running noise.

Then, based on Fig. 6 the 4th variation of the speed change gear of above-mentioned first mode of execution is described, in addition, the part mark identical symbol identical with above-mentioned mode of execution omits its detailed description.

In the speed change gear 10D of this variation explanation, the rolling element holding part 42 of pectination is set on the retainer 40D as output shaft So, make the rolling element K that on this rolling element holding part 42, sets between the inner ring 20D that is divided into two-part structure and be provided with between the outer ring 30D of input shaft Si, the compression relief cam 50 of pre-pressure regulator is set between the opposing side of inner ring 20D, and links the worm gear 55 of gear ratio changeable mechanism.

At this moment, inner ring 20D is divided into the 22D of inner ring portion and gear formation portion 25 two-part, be equipped with compression relief cam 50 between opposing side 22d, the 25d of 22D of inner ring portion and gear formation portion 25, gear part 25a that forms on the outer circumferential face of

gear formation portion

25 and 55 engagements of the worm gear of gear ratio changeable mechanism also link.

In addition, also formative gear portion 45 on as the outer circumferential face of the retainer 40D of output shaft So for example, also can make this gear part 45 obtain converting to rotatablely moving straight-line output with rack pinion 70 engagements.At this moment, also can be in the side of retainer 40D formative gear portion 45.

In addition, the symbol 12 among the figure is bearings, the 13rd, and oil sealing, the 14th, the leaf spring of the minimum precompressed of regulation, the 16th, tapered roller bearing.

The speed change gear 10D of Gou Chenging like this transmits to the retainer 40D as output shaft So via the rolling element K that is provided on the rolling element holding part 42 as the torque of the outer ring 30D of input shaft Si.At this moment, in inner ring 20D,, can when having input torque, precompressed be suppressed at inferior limit because compression relief cam 50 comes the precompressed of corrective action in rolling element K corresponding to the torque of input shaft Si.In addition, because the gear part 25a binding of the gear formation portion 25 that the worm gear 55 of gear ratio changeable mechanism and the inner ring 20D that will draw inputoutput unit are cut apart and carry out differential Spin Control, so can change the gear ratio of input and output shaft.

In addition, the speed change gear 10D of above-mentioned formation has the identical advantage of sense of rotation of input and output shaft.And, when under identical condition, comparing, the face of rolling element K can be constrained and make lowlyer, also can make the driving torque of the input shaft Si that sets compression relief cam 50 also set lowlyer, therefore, favourable aspect working life and serviceability.In addition, if form rack pinion 70 and built-in Chi Tiao ﹠amp are set; The structure of gear mechanism then can make the further miniaturization of Vehicular steering apparatus.

Then, based on Fig. 7 the 5th variation of the speed change gear of above-mentioned first mode of execution is described, in addition, the part mark identical symbol identical with above-mentioned mode of execution omits its detailed description.

In the speed change gear 10E of this variation explanation, the rolling element holding part 42 of pectination is set on retainer 40E, make the rolling element K that on this rolling element holding part 42, sets between the inner ring 20E of two-part segmenting structure that is provided with output shaft So and be provided with between the outer ring 30E of input shaft Si, between the opposing side of inner ring 20E, pre-pressure regulator is set, and worm gear 55 is attached on the retainer 40E as the gear ratio changeable mechanism as compression relief cam 50.

At this moment, inner ring 20E is divided into the 22E of inner ring portion and output axial region 26 two-part, is equipped with compression relief cam 50 on opposing side 22e, the 26e of 22E of inner ring portion and output axial region 26,

In the speed change gear 10E that constitutes like this, transmit to the 22E of inner ring portion via the rolling element K that is provided on the rolling element holding part 42 as the inner ring 20E of output shaft So as the torque of the outer ring 30E of input shaft Si.At this moment, in inner ring 20E,, can when having input torque, precompressed be suppressed at inferior limit because compression relief cam 50 comes the precompressed of corrective action in rolling element K corresponding to the torque of input shaft Si as output shaft So.In addition, because the worm gear 55 of gear ratio changeable mechanism links with the gear part that forms on the retainer 40E of traction inputoutput unit and carries out differential Spin Control, so, can change the gear ratio of input and output shaft.

In addition, the speed change gear 10E of above-mentioned formation when comparing, owing to can lower scope turn round at the rotating speed of worm gear 55, can reduce running noise under identical condition.

Second mode of execution

Then, describe based on second mode of execution of accompanying drawing speed change gear of the present invention.The mode of execution that the following describes is by connecting the input output of two groups of above-mentioned traction transmission gear shifts, constitutes the speed change of the first order and carries out the two stage speed change of the speed change opposite with it in the second level.In addition, the part mark identical symbol identical with above-mentioned mode of execution omits its detailed description.

The speed change gear 10F of mode of execution shown in Figure 8, the traction of the rolling element K of utilization between input shaft Si and output shaft So, make the rotation speed change of input shaft Si become desirable gear ratio and export from output shaft So, and left and right symmetrically links input shaft Si and output shaft So and carries out two stage speed change.

Be arranged on axially bilateral symmetry substantially and axial region on the inner ring of the first order speed changing portion TR1 that links and second level speed changing portion TR2 at two of housing 11 side-prominent input shaft Si and output shaft So.

First order speed changing portion TR1 is provided with the rolling element holding part 142 of pectination on the main body 141 of first retainer 140, make the rolling element K that sets on this rolling element holding part 142 between first inner ring 120 that is provided with input shaft Si and be provided with between first outer ring 130 that links output shaft 131 and constitute.Even under this situation, rolling element holding part 142 is not limited to pectination, can suitably select ladder shape etc.

Second level speed changing portion TR2 is provided with the rolling element holding part 242 of pectination on the main body 241 of second retainer 240, make the rolling element K that sets on this rolling element holding part 242 between second inner ring 220 that is provided with output shaft So and be provided with between second outer ring 230 that links input shaft 23 1 and constitute.Even under this situation, rolling element holding part 242 is not limited to pectination, can suitably select ladder shape etc.

In addition, above-mentioned rolling element K is in any one of first order speed changing portion TR1 and second level speed changing portion TR2, and its rotation axis is the non-orthogonal and tilted configuration with the axis of input shaft Si and output shaft So all.

Relative at the end end face of the binding output shaft 131 that makes first order speed changing portion TR1 and the binding input shaft 231 of second level speed changing portion TR2 and on the axle linking department that links, be provided with the compression relief cam 50 that works as pre-pressure regulator.This compression relief cam 50 is identical with the first above-mentioned mode of execution, and the recess space that forms between the opposing side of axle linking department is contained setting with the state that slides that can roll.Such recess is from the axle center to be provided with radially at circumferencial direction equally spacedly to be organized more, but this quantity can suitably be selected according to many conditions.

In addition, first retainer 140 has the gear part 141a that forms on the outer circumferential face of main body 141, this gear part 141a and worm gear 55 engagements and the binding of working as the gear ratio changeable mechanism.That is, this formation is the structure that makes up with the traction drive mechanism that the input and output shaft mode of left and right symmetry will illustrate in the first embodiment.In addition, second retainer 240 is to be fixed on the housing 11 and to form the motionless parts of its part, and the symbol 12 among the figure is bearings, the 13rd, and oil sealing, the 14th, leaf spring.

According to such speed change gear 10F, in first order speed changing portion TR1,, transmit to having first outer ring 130 that links output shaft 131 via the rolling element K on the rolling element holding part 142 that is provided in first retainer 140 as the torque of first inner ring 120 of input shaft Si by the traction transmission.Then, in the speed changing portion TR2 of the second level, torque is transmitted to having second outer ring 230 that links input shaft 231 via the compression relief cam 50 that works as pre-pressure regulator, and transmits to second inner ring 220 as output shaft So via the rolling element K that sets on the rolling element holding part 242 of second retainer 240.

At this moment, to link carry-out part 131 via compression relief cam 50 and link in the axle linking department that links between the input part 231, because compression relief cam 50 comes the precompressed of corrective action in the rolling element K of first order speed changing portion and second level speed changing portion corresponding to the torque that links carry-out part 131, so when not having input torque, can suppress the minimal precompressed of leaf spring 14 regulations.In addition, because the worm gear 55 of gear ratio changeable mechanism links with the gear part 141a that forms on first holding part 140 of traction inputoutput unit and carries out differential Spin Control, so, the gear ratio of input and output shaft can be changed to desirable value.

In addition, the speed change gear 10F of Gou Chenging is after first order speed changing portion TR1 speed change like this, and speed changing portion TR2 carries out reverse speed change in the second level, so, for example after first order speed changing portion TR1 speedup, slow down, make input/output relation become 1: 1 based on the trace traction at second level speed changing portion TR2.Therefore, when this device is assembled into Vehicular steering apparatus ST, can directly apply flexibly existing Chi Tiao ﹠amp; Gearing 64.

In addition, the speed change gear 10F of above-mentioned formation, when under identical condition, comparing, owing to particularly can lower scope turn round at the rotating speed of worm gear 55, so can reduce running noise.In addition, because the number of bearings of using is few, so have the advantage of easy assembling.

Then, based on Fig. 9 first variation of the speed change gear of above-mentioned second mode of execution is described.In addition, the part mark identical symbol identical with above-mentioned mode of execution omits its detailed description.

In the speed change gear 10G of this variation explanation, have: first order speed changing portion TR11, it makes the rolling element K that sets on this rolling element holding part 142 between the first inner ring 120A that is provided with input shaft Si and the first outer ring 130A having the rolling element holding part 142 that pectination is set on the first retainer 140A that links output shaft 143; Second level speed changing portion TR21, it has the rolling element holding part 242 that pectination is set on the second retainer 240A that links input shaft 243, makes the rolling element K that sets on this rolling element holding part 242 between the second inner ring 220A that is provided with output shaft So and second outer ring (be fixed on the housing 11 and become one).And, will link output shaft 143 and link the compression relief cam 50 that is provided as pre-pressure regulator on the axle linking department that input shaft 243 links and works, and the worm gear 55 of gear ratio changeable mechanism and the first outer ring 130A go up the gear part 30a binding that forms.That is, this formation is the structure with the haulage gear of first variation that illustrates in symmetrical textural association first mode of execution of input and output shaft.

According to such speed change gear 10G, in first order speed changing portion TR11,, transmit to having the first retainer 140A that links output shaft 143 via the rolling element K on the rolling element holding part 142 that is provided in first retainer 140 as the torque of the first inner ring 120A of input shaft Si by the traction transmission.Then, in the speed changing portion TR21 of the second level, the second retainer 240A torque transmitted that links input shaft 243 via the compression relief cam 50 that works as pre-pressure regulator to conduct, via the rolling element K that on the rolling element holding part 242 of the second retainer 240A, sets, transmit to the second inner ring 220A as output shaft So by the traction transmission.

At this moment, to link output shaft 143 via compression relief cam 50 and link the axle linking department that links between the input shaft 243, because compression relief cam 50 comes the precompressed of corrective action in the rolling element K of first order speed changing portion TR11 and second level speed changing portion TR21 corresponding to the torque that links output shaft 143, so precompressed can be suppressed to inferior limit when having input torque.In addition, because the worm gear 55 of gear ratio changeable mechanism links with the gear part 30a that forms on the first outer ring 130A of traction inputoutput unit and carries out differential Spin Control, so, the gear ratio of input, output shaft can be changed to desirable value.

In addition, the speed change gear 10G of Gou Chenging is after first order speed changing portion TR11 speed change like this, and speed changing portion TR21 carries out reverse speed change in the second level, so, for example after first order speed changing portion TR11 speedup, slow down at second level speed changing portion TR21, the input/output relation that draws based on trace becomes 1: 1.Therefore, when being assembled into this device among the Vehicular steering apparatus ST, can directly apply flexibly existing Chi Tiao ﹠amp; Gearing 64.

In addition, the speed change gear 10G of above-mentioned formation, when under identical condition, comparing, owing to can lower scope turn round at the rotating speed of worm gear 55, so can reduce running noise.

Then, based on Figure 10 second variation of the speed change gear of above-mentioned second mode of execution is described.In addition, the part mark identical symbol identical with above-mentioned mode of execution omits its detailed description.

In the speed change gear 10H of this variation explanation, have: first order speed changing portion TR12, it has the rolling element holding part 142 that pectination is set on the first retainer 140B of input shaft Si, makes the rolling element K that sets on this rolling element holding part 142 between being provided with between the first inner ring 120B and the first outer ring 130B that links output shaft 126; Second level speed changing portion TR22, it has the rolling element holding part 242 that pectination is set on the second retainer 240B of output shaft So, make the rolling element K that on this rolling element holding part 242, sets between be arranged on link the second inner ring 220B on the input shaft 226 and be fixed on housing 11 and second outer ring that becomes one between.And, on the axle linking department that will link

output shaft

126 and 226 bindings of binding input shaft, be provided as the compression relief cam 50 that pre-pressure regulator works, and, link as gear ratio changeable mechanism worm gear 55 that works and the gear part 30a that forms at the first outer ring 130B.That is, this formation is to make up the structure of the haulage gear of the 3rd variation of explanation in the first embodiment with the input and output shaft mode of left and right symmetry.

According to such speed change gear 10H, in first order speed changing portion TR12,, transmit via the rolling element K on the rolling element holding part 142 that is provided in the first retainer 140B as the torque of the first inner ring 140B of input shaft Si to having the first inner ring 120B that links output shaft 126.

Then, in the speed changing portion TR22 of the second level, torque is transmitted to having the second inner ring 220B that links input shaft 226 via the compression relief cam 50 as pre-pressure regulator function, and then, transmit to the second retainer 240B via the rolling element K that on the rolling element holding part 242 of the second retainer 240B, sets as output shaft So.

At this moment, to link carry-out part 126 via compression relief cam 50 and link the axle linking department that links between the input part 226, because compression relief cam 50 comes the precompressed of corrective action in the rolling element K of first order speed changing portion TR12 and second level speed changing portion TR22 corresponding to the torque that links carry-out part 126, so can when having input torque precompressed be suppressed to inferior limit.In addition, because the worm gear 55 of gear ratio changeable mechanism links with the gear part 30a that forms on the first outer ring 130B of traction inputoutput unit and carries out differential Spin Control, so, the gear ratio of input, output shaft can be changed to desirable value.

In addition, the speed change gear 10H of Gou Chenging is after first order speed changing portion TR12 speed change like this, and speed changing portion TR22 carries out reverse speed change in the second level, so, for example slow down at second level speed changing portion TR22 after first order speed changing portion TR12 speedup, the input/output relation that draws based on trace becomes 1: 1.Therefore, when being assembled into this device among the Vehicular steering apparatus ST, can directly apply flexibly existing Chi Tiao ﹠amp; Gearing 64.

In addition, the speed change gear 10H of above-mentioned formation, because the quantity of bearing is fewer, assembling easily.When under identical condition, comparing, particularly the face of rolling element K can be constrained make lower, and, set the driving torque that sets the input shaft Si of compression relief cam 50 lower, therefore, be very favourable aspect working life and the serviceability.

Then, based on Figure 11 the 3rd variation of the speed change gear of above-mentioned second mode of execution is described.In addition, the part mark identical symbol identical with above-mentioned mode of execution omits its detailed description.

In the speed change gear 10I of this variation explanation, have: first order speed changing portion TR13, it is provided with pectination on the first retainer 140C rolling element holding part 142 makes the rolling element K that sets on this rolling element holding part 142 between being provided with the first inner ring 120C that links output shaft 126 and being provided with between the first outer ring 130C of input shaft Si; Second level speed changing portion TR23, it is provided with pectination on the second retainer 240C rolling element holding part 242 makes the rolling element K that sets on this rolling element holding part 242 between being provided with the second inner ring 220C that links input shaft 226 and being provided with between the second outer ring 230C of output shaft So.And, on the axle linking department that links output shaft 126 and binding input shaft 226, be provided as the compression relief cam 50 that pre-pressure regulator works, and, link as gear ratio changeable mechanism worm gear 55 that works and the gear part 41a that on the first retainer 140C, forms.That is, this formation is to make up the structure of the haulage gear of the 5th variation that illustrates in first mode of execution with the input and output shaft mode of left and right symmetry.

According to such speed change gear 10I, in first order speed changing portion TR13, transmit to having the first inner ring 120C that links output shaft 126 via the rolling element K on the rolling element holding part 142 that is provided in the first retainer 140C as the torque of the first inner ring 130C of input shaft Si.Then, in the speed changing portion TR23 of the second level, via the compression relief cam 50 that works as pre-pressure regulator to having the second inner ring 220C torque transmitted that links input shaft 226, via form the rolling element K that sets on the rolling element holding part 242 that is provided with on the second motionless retainer of one being fixed on housing 11, transmit to the second outer ring 230C as output shaft So.

At this moment, to link output shaft 126 via compression relief cam 50 and link the axle linking department that links between the input shaft 226, because compression relief cam 50 comes the precompressed of corrective action in the rolling element K of first order speed changing portion TR13 and second level speed changing portion TR23 corresponding to the torque that links output shaft 126, so precompressed can be suppressed to inferior limit when having input torque.In addition, because the worm gear 55 of gear ratio changeable mechanism links with the gear part 41a that forms on the first retainer 140C of traction inputoutput unit and carries out differential Spin Control, so, the gear ratio of input and output shaft can be changed to desirable value.

In addition, the speed change gear 10I of Gou Chenging is after first order speed changing portion TR13 speed change like this, and speed changing portion TR23 carries out reverse speed change in the second level, so, for example slow down at second level speed changing portion TR23 after first order speed changing portion TR13 speedup, the input/output relation that draws based on trace becomes 1: 1.Therefore, when being assembled into this device among the Vehicular steering apparatus ST, can directly apply flexibly existing Chi Tiao ﹠amp; Gearing 64.

In addition, the speed change gear 10I of above-mentioned formation is when comparing under identical condition, the face of rolling element K can be constrained make lower, and the driving torque that will set the input shaft Si of compression relief cam 50 is also set lowlyer, so, be favourable aspect working life and the serviceability.In addition, owing to can lower scope turn round, can reduce running noise at the rotating speed of worm gear 55.

Then, based on Figure 12 the 4th variation of the speed change gear of above-mentioned second mode of execution is described.In addition, the part mark identical symbol identical with above-mentioned mode of execution omits its detailed description.

The speed change gear 10J that illustrates in this variation constitutes following difference,, replaces the gear ratio changeable mechanism that utilizes worm gear 55 of above explanation that is, adopts with the epicyclic type mechanism 80 of hollow motor M as driving source.In addition, speed change gear 10J has: first order speed changing portion TR14, it has the rolling element holding part 142 that pectination is set on the first retainer 140D of input shaft Si, makes the rolling element K that sets on this rolling element holding part 142 between being provided with between the first inner ring 120D and the first outer ring 130D that links output shaft 126; Second level speed changing portion TR24, it has the rolling element holding part 242 that pectination is set on the second retainer 240D of output shaft So, make the rolling element K that on this rolling element holding part 242, sets between be provided with the second inner ring 220D that links input shaft 226 and be fixed on the housing 11 and second outer ring that becomes one between.And, on the axle linking department that links output shaft 126 and binding input shaft 226, be provided as the compression relief cam 50 that pre-pressure regulator works, and the epicyclic type mechanism 80 and the first outer ring 130D that work as the gear ratio changeable mechanism link.That is, the formation of the 4th variation is in the speed change gear 10H of above-mentioned second variation, and the worm gear 55 of speed change changeable mechanism is altered to epicyclic type mechanism 80.In addition, the symbol C among the figure is the locking framework portion that comprises clutch etc.

Epicyclic type mechanism 80 has: sun gear 82, its with input shaft Si and the coaxial hollow motor M that sets of output shaft So as driving source, be arranged on the hollow motor shaft 81; A plurality of planet wheels 83; Annulus wheel 84, it is provided on the outer circumferential side of planet wheel 83.

Be arranged on the internal configurations of the input shaft Si perforation hollow motor shaft 81 on the first retainer 140D.This hollow motor shaft 81 is provided with the sun gear 82 that is formed with gear part on the end outer circumferential face of rolling element holding part 142 sides.On the periphery of sun gear 82, equally spaced set planet wheels 83 a plurality of and the gear part engagement on circumferentially, and, be equipped with by splined joint etc. and the annulus wheel 84 that links with the first outer ring 130D at the outer circumferential side of each planet wheel 83.This annulus wheel 84 makes gear part and planet wheel 83 engagements that form on the inner peripheral surface.

The epicyclic type mechanism 80 of Gou Chenging like this, when making sun gear 82 rotations integratedly with hollow motor shaft 81 by driving hollow motor M, according to the number of teeth of the gear part that forms on the number of teeth of the number of teeth of the gear part that forms on the sun gear 82, planet wheel 83 and the annulus wheel 84, the rotating speed of sun gear 82 is by speed change (decelerations) and to annulus wheel 84 transmission.The rotation of annulus wheel 84 is owing to make the first outer ring 130D rotation of the transmission inputoutput unit of one binding, the worm gear 55 of former and above-mentioned gear ratio changeable mechanism is identical, carry out differential Spin Control, the gear ratio of input and output shaft can be changed to desirable value.

That is,,,, can easily set the gear ratio of input and output shaft so carry out differential Spin Control owing to can change by the rotating speed control of hollow motor M to the rotating speed of the annulus wheel 84 and the first outer ring 130D transmission.

In addition, use hollow motor M, constitute the structure in the input and output shaft perforation hollow motor shaft 81, for example not having, worm gear 55 perhaps can make the overhang minimum, so the outside dimension of speed change gear 10J diminishes can miniaturization like that to circumferentially outstanding parts.The speed change gear 10J that boundary dimension is little so for example is highly suitable for being difficult to guaranteeing being provided with the speed change gear of the Vehicular steering apparatus ST in space.

According to such speed change gear 10J, in first order speed changing portion TR14, transmit to having the first inner ring 120B that links output shaft 126 via the rolling element K on the rolling element holding part 142 that is provided in the first retainer 140D as the torque of the first retainer 140D of input shaft Si.

Then, in the speed changing portion TR24 of the second level, to having the second inner ring 220D torque transmitted that links input shaft 226, the rolling element K that sets on the rolling element holding part 242 via the second retainer 240D transmits to the second retainer 240B as output shaft So via the compression relief cam 50 that works as pre-pressure regulator.

At this moment, to link output shaft 126 via compression relief cam 50 and link the axle linking department that links between the input shaft 226, because compression relief cam 50 comes the precompressed of corrective action in the rolling element K of first order speed changing portion TR14 and second level speed changing portion TR24 corresponding to the torque that links output shaft 126, so precompressed can be suppressed to inferior limit when having input torque.In addition, because the first outer ring 130D of the epicyclic type mechanism 80 of gear ratio changeable mechanism and traction inputoutput unit links and carries out differential Spin Control, so, the gear ratio of input, output shaft can be changed to desirable value.

In addition, the speed change gear 10J of Gou Chenging is after first order speed changing portion TR14 speed change like this, and speed changing portion TR24 carries out reverse speed change in the second level, so, for example after first order speed changing portion TR14 speedup, slow down, become 1: 1 based on the traction input/output relation of trace at second level speed changing portion TR24.Therefore, when being assembled into this device among the Vehicular steering apparatus ST, can directly apply flexibly existing Chi Tiao ﹠amp; Gearing 64.

In addition, above-mentioned epicyclic type mechanism 80 is not limited to the speed change gear 10J of formation shown in Figure 12, can replace the worm gear 55 of above-mentioned various mode of execution and variation.

The 3rd mode of execution

Then, describe based on the 3rd mode of execution of accompanying drawing speed change gear of the present invention.The input output left and right symmetrically with above-mentioned traction transmission gear shift of passing through of the mode of execution that the following describes and second mode of execution links two groups and two utmost point speed changes of carrying out the speed change opposite with first order speed change with identical gear ratio in the second level and constitutes differently, constitutes the two stage speed change that carries out opposite speed change with different gear ratio.In addition, the part mark identical symbol identical with above-mentioned mode of execution omits its detailed description.

The speed change gear 10K of mode of execution shown in Figure 13, the traction of the rolling element K of utilization between input shaft Si and output shaft So, the rotation speed change of input shaft Si is exported to desirable gear ratio and from output shaft So, and, constitute to link input shaft Si and output shaft So and carry out the structure of two stage speed change.Promptly, this speed change gear 10K, it is characterized in that, the traction inputoutput unit and being integral that link first order speed changing portion TR15 and second level speed changing portion TR25, and, gear ratio to two speed changing portion TR15, TR25 is provided with difference, constitutes for other, and is identical in fact with the speed change gear 10J of above-mentioned Figure 11.

At two of housing 11 side-prominent input shaft Si and output shaft So are the axial regions that are provided with on the retainer of axial first speed changing portion TR15 that links and second level speed changing portion TR25.

Speed change gear 10K has: first order speed changing portion TR15, it has the rolling element holding part 142A that pectination is set on the first retainer 140E of input shaft Si, makes at the rolling element K that sets on this rolling element holding part 142A to link between the parts 90 between being provided with the first inner ring 120E and the outer ring that link on the output shaft 126A; Second level speed changing portion TR25, it has the rolling element holding part 242A that pectination is set on the second retainer 240E of output shaft So, makes at the rolling element K that sets on this rolling element holding part 242A to link between the parts 90 between being provided with the second inner ring 220E and the outer ring that link input shaft 226A.And, on the axle linking department that links output shaft 126A and binding input shaft 226A, be provided as the compression relief cam 50 that pre-pressure regulator works, and, will link parts 90 bindings with the outer ring as the epicyclic type mechanism 80 that the gear ratio changeable mechanism works.

Promptly, in this embodiment, as with become the traction transmission part the suitable parts in first outer ring and second outer ring, linking parts 90 by the outer ring links first order speed changing portion TR15 and second level speed changing portion TR25 also integrated, the epicyclic type mechanism 80 of gear ratio changeable mechanism links parts 90 with this outer ring and links, and, different two speed changing portion TR15, TR25 such as combination inner ring track diameter and difference is set on gear ratio.In addition, in this case, how many differences of the gear ratio setting of two speed changing portion TR15, TR25 can have a bit.

Being arranged on input shaft Si on the first retainer 140E connects the inside of hollow motor shaft 81 and sets.This hollow motor shaft 81 is provided with the sun gear 82 of formative gear portion on the end outer circumferential face of rolling element holding part 142 sides.On the periphery of sun gear 82, to a plurality of planet wheels 83 that circumferentially uniformly-spaced are equipped with the gear part engagement, and, be equipped with by splined joint etc. at the outer circumferential side of each planet wheel 83 and link the annulus wheel 84 that parts 90 link with the outer ring.Gear part and planet wheel 83 engagements that this annulus wheel 84 forms inner peripheral surface.

The epicyclic type mechanism 80 of Gou Chenging like this, when making sun gear 82 with the rotation of hollow motor shaft 81 one by driving hollow motor M, according to the number of teeth of the gear part that forms on the number of teeth of the number of teeth of the gear part that forms on the sun gear 82, planet wheel 83 and annulus wheel 84, the rotating speed of sun gear 82 is by speed change (decelerations) and to annulus wheel 84 transmission.The rotation of annulus wheel 84 makes the outer ring of the traction inputoutput unit of one binding link parts 90 rotations, and the gear ratio at two speed changing portion TR15, TR25 has difference, therefore, can carry out differential Spin Control and the gear ratio of input and output shaft is changed to desirable value.

That is, link the rotating speed that parts 90 transmit to annulus wheel 84 and outer ring, owing to can change by the rotating speed control of hollow motor M, so carry out the gear ratio that differential Spin Control can easily be set input and output shaft.

In addition, use hollow motor M to constitute input and output shaft and connect structure in the hollow motor shaft 81, for example not have that worm gear 55 perhaps can make the overhang minimum like that to the parts of circumferentially giving prominence to, therefore, the outside dimension of speed change gear 10K diminishes and can miniaturization.Like this, the speed change gear 10K that boundary dimension is little for example is highly suitable for guaranteeing being provided with the speed change gear of the Vehicular steering apparatus ST of space difficulty.

In addition, the speed change gear 10K of above-mentioned formation also can use the big worm gear of boundary dimension 55 as the gear ratio changeable mechanism.

As mentioned above, speed change gear shown in first mode of execution of the present invention, owing to make the nonopiate earth tilt configuration of axis of rotation axis and input shaft Si and the output shaft So of rolling element K, and has the compression relief cam 50 that makes the precompressed automatic pre-pressure regulator that changes that imposes on rolling element K corresponding to the torque of input shaft Si, and link with the traction inputoutput unit of rolling element K and carry out the rotating speed control of this traction inputoutput unit and make the worm gear 55 of gear ratio changeable mechanism of the differential type of gear ratio variation, so compression relief cam 50 imposes on the precompressed of the rolling element of this tilted configuration corresponding to the torque adjustment of input shaft Si.That is, the thrust load that compression relief cam 50 produces corresponding to driving torque, this thrust load becomes the precompressed that pushes rolling element K vertically.In addition, owing to have differential type gear ratio changeable mechanism, can adjust the gear ratio of input and output shaft and setting arbitrarily.

In addition, speed change gear shown in second mode of execution of the present invention, owing to make the nonopiate earth tilt configuration of axis of rotation axis and input shaft Si and the output shaft So of rolling element K, and has the compression relief cam 50 that makes the precompressed automatic pre-pressure regulator that changes that imposes on rolling element K corresponding to the torque that links first order speed changing portion and second level speed changing portion between centers, and link with the traction inputoutput unit of rolling element K and carry out the rotating speed control of this traction inputoutput unit and make the worm gear 55 of the gear ratio changeable mechanism of gear ratio variation, so compression relief cam 50 is automatically regulated the precompressed that changes the rolling element that imposes on this tilted configuration according to the torque that links first order speed changing portion and second level speed changing portion between centers.In addition, owing to have differential type gear ratio changeable mechanism, can adjust the gear ratio of input and output shaft and setting arbitrarily.At this moment, carrying out two stage speed change by first order speed changing portion and second level speed changing portion, is 1: 1 based on the input/output relation that draws transmission in identical sense of rotation.

Particularly, if adopt the epicyclic type mechanism that utilizes the hollow motor driving, outside dimension is radially diminished and miniaturization as the gear ratio changeable mechanism.

The 4th mode of execution

Figure 14 is the sectional drawing of the 4th mode of execution of expression traction drive transmission device of the present invention.Below in Shuo Ming each mode of execution, above-mentioned speed change gear has output shaft So is applied the driving torque assisting agency that rotating force increases driving torque.In addition, the part mark identical symbol identical with above-mentioned various mode of executions omits its detailed description.

Append the gear part 35 of setting between bearing 12 on the output axial region 33 of the speed change gear 10 that this speed change gear 10L illustrates in above-mentioned first mode of execution (Fig. 1).This gear part 35 is the parts with the engagement of driving torque described later assisting agency.In addition, be projected into the output axial region 33 of housing 11 outsides, for example the tooth bar of Vehicular steering apparatus; Gearing is such, links with the device of not shown slave end.

In order to increase the driving torque assisting agency of driving torque and to work as output shaft So is applied rotating force, worm gear 55A with as gear part 35 engagements of the outer ring 30 of output shaft So and with its binding.This worm gear 55A is driven by drive units such as motor that can variable control, makes the output shaft So sideway swivel of engagement and applies desirable rotating torques and the output torque of traction drive mechanism TR is increased.

That is, be from the torque of input shaft Si from the driving torque of output shaft So output via traction drive mechanism TR output, apply desirable rotating torques and the big output torque that increases from worm gear 55A.

The speed change gear 10L of Gou Chenging has the auxiliary function of driving torque except the function of the speed change gear 10 of above-mentioned first mode of execution explanation like this.That is, when worm gear 55A applied desirable turning power to output shaft So, the driving torque of exporting via traction drive mechanism TR increased the torque of finally exporting from output shaft So corresponding to the turning power that is applied.

Therefore, become speed change gear 10L: even the input torque of input shaft Si is little with following function, also can apply desirable turning power, increase the driving torque miscellaneous function (power-aid function) of final output torque by controlling worm gear 55A according to many conditions.

In addition, when adopting such speed change gear 10 to carry out steering operation at Vehicular steering apparatus ST, transmit to input shaft Si from top steering shaft 62 by the torque that the operation of steering tiller 60 produces, become desirable gear ratio in speed change gear 10L inner conversion, and, can with apply desirable turning power make output torque that driving torque increases from output shaft So to 63 transmissions of bottom steering shaft, make tooth bar; Gearing 64 actions.

Therefore, under the not operated situation of steering tiller 60, for example when stopping or when keeping straight on etc.,, pretend the precompressed minimum of using on the rolling element K owing to do not have torque on top steering shaft 62 and the input shaft Si.Therefore, prolong the working life of rolling element K effectively, improve serviceability and the reliability of Vehicular steering apparatus ST.

In addition, for example under the situation that the operation amount of steering tiller 60 increases when low speed driving like that such as parking in lateral, if the rotating speed of control worm gear 55 and increase gear ratio then can obtain big steering angle with less steering operation amount.That is, if adjust that the rotating speed of worm gear 55 makes the big speedup of rotating speed of input shaft Si and from output shaft So output, little steering tiller operation amount (rotating speed of top steering shaft 62) speedup and to 63 outputs of bottom steering shaft can make tooth bar; The tooth bar amount of movement of gearing 64 increases, and turning to significantly of

Steering Wheel

61,61 changed, and therefore, improves the operability of Vehicular steering apparatus ST.

In addition, if suitably control the rotating torques that applies from worm gear 55A corresponding to many conditions such as travelling states, then for example utilize and when running at high speed, do not apply rotating torques or make its minimum, the operation of steering tiller 60 becomes heavily increases roadholding, perhaps when parking in lateral etc. under the situation of low-speed handing steering tiller 60, by making rotating torques become maximum, can make and operate the raising operability that lightens.

Then, based on Figure 15 first variation of the speed change gear of above-mentioned the 4th mode of execution is described.In addition, the part mark identical symbol identical with above-mentioned mode of execution omits its detailed description.

In the speed change gear 10M of this variation explanation, following aspect is different with above-mentioned mode of execution, promptly, the inner ring 20A that is provided with input shaft Si is structure as a whole, the retainer 40A that is provided with output shaft So is formed two-part segmenting structure and set compression relief cam 50 between the mating face, simultaneously, the worm gear 55 of gear ratio changeable mechanism links with outer ring 30A, and the worm gear 55A of driving torque assisting agency and the output shaft of retainer 40A partly link.

That is, the retainer 40A that will have output shaft Si is divided into holding part main body 43 and output axial region 44 two-part segmenting structures, sets the rolling element K of tapered roller on the rolling element holding part 42 of the pectination of being located at holding part main body 43.And, between opposing side 43a, the 44a of holding part main body 43 and output axial region 44, be equipped with the compression relief cam 50 that works as above-mentioned pre-pressure regulator.

In addition, make precompressed (among the figure shown in the arrow) generation effect and make rolling element K between inner ring 20A that is provided with input shaft Si and outer ring 30A, carry out torque transmission, between inner ring 20A and retainer 40A, can set thrust-bearing 15 with the relative rotation based on traction.In addition, the gear part 30a engagement that the worm gear of gear ratio changeable mechanism 55 and outer circumferential surface at outer ring 30A form also links, and the worm gear 55A of driving torque assisting agency is with gear part 35 engagements that are installed in output axial region 44 and link.In addition, the symbol 12 among the figure is bearings, the 13rd, and oil sealing, the 14th, leaf spring, the 16th, tapered roller bearing.

In the speed change gear 10M that constitutes like this, transmit to output axial region 44 via the rolling element K that is provided on the rolling element holding part 42 as the output shaft So of retainer 40A as the torque of the inner ring 20A of input shaft Si.At this moment, in retainer 40A as output shaft So since compression relief cam 50 corresponding to the torque corrective action of input shaft Si in the precompressed of rolling element K, so can when having input torque, precompressed be suppressed at inferior limit.In addition, the precompressed of this moment is adjusted by compression relief cam 50, produces by the thrust load that acts on thrust-bearing 15 from holding part main body 43.

In addition, because the gear part 30a binding of the outer ring 30A of the worm gear 55 of gear ratio changeable mechanism and traction inputoutput unit is also carried out differential Spin Control, so, the gear ratio of input and output shaft is changed, in addition, the worm gear 55A of driving torque assisting agency is attached at and exports on the gear part 35 of axial region 44 one rotations and imposes on desirable rotating torques, so, can increase from the driving torque of output shaft So output.

And the speed change gear 10M of above-mentioned formation has the identical advantage of sense of rotation of input and output shaft.In addition, when identical condition compares, particularly the face of rolling element K can be constrained make quite low, so, to working life and serviceability aspect be favourable.

Then, based on Figure 16 second variation of the speed change gear of above-mentioned the 4th mode of execution is described.In addition, the part mark identical symbol identical with above-mentioned mode of execution omits its detailed description.

In the speed change gear 10N of this variation explanation, has the rolling element holding part 42 that pectination is set on the retainer 40B of input shaft Si, make the rolling element K that on this rolling element holding part 42, sets between inner ring 20B that is provided with output shaft So and outer ring 30B, as pre-pressure regulator, compression relief cam 50 is set on inner ring 20B, and, as the gear ratio changeable mechanism, worm gear 55 is attached on the 30B of outer ring, the worm gear 55A of driving torque assisting agency is attached on the output shaft part (output axial region 26 described later) of inner ring 20B.In addition, the symbol 12 among the figure is bearings, the 13rd, and oil sealing, the 14th, leaf spring, the 15th, thrust-bearing, the 16th, tapered roller bearing.

The inner ring 20B of this moment is divided into the 22B of inner ring portion and output axial region 26 two-part, is equipped with compression relief cam 50 between opposing side 22b, the 26b of 22B of inner ring portion and output axial region 26.

In the speed change gear 10N that constitutes like this, transmit to the 22B of inner ring portion via the rolling element K that is provided on the rolling element holding part 42 as the inner ring 20B of output shaft So as the torque of the retainer 40B of input shaft Si.At this moment, in inner ring 20B since compression relief cam 50 corresponding to the torque corrective action of input shaft Si in the precompressed of rolling element K, can when having input torque, precompressed be suppressed at inferior limit.In addition, because the gear part 30a that the worm gear 55 of gear ratio changeable mechanism and outer ring 30B at the traction inputoutput unit form links and carries out differential Spin Control, so, can change the gear ratio of input and output shaft.

And the worm gear 55A of driving torque assisting agency is attached on the gear part 35 of rotating with output axial region 26 one of inner ring 20B and imposes on desirable rotating torques, so, can increase from the driving torque of output shaft So output.

In addition, the speed change gear 10N of above-mentioned formation not only has the identical advantage of sense of rotation of input and output shaft, because the negligible amounts of the bearing that needs gets final product, can make the assembling when making become simple.When particularly under identical condition, comparing,, can reduce running noise owing to can lower scope turn round at the rotating speed of worm gear 55.

Then, based on Figure 17 the 3rd variation of the speed change gear of above-mentioned the 4th mode of execution is described.In addition, the part mark identical symbol identical with above-mentioned mode of execution omits its detailed description.

In the speed change gear 10P of this variation explanation, the rolling element holding part 42 of pectination is set on retainer 40C, make the rolling element K that on this rolling element holding part 42, sets between the inner ring 20C of two-part segmenting structure that is provided with output shaft So and be provided with between the outer ring 30C of input shaft Si, between the opposing side of inner ring 20C, be provided as the compression relief cam 50 of pre-pressure regulator, and, worm gear 55 as the gear ratio changeable mechanism is attached on the retainer 40C, and the worm gear 55A of driving torque assisting agency is attached on the output shaft part (output axial region 26 described later) of inner ring 20C.In addition, the symbol 12 among the figure is bearings, the 13rd, and oil sealing, the 14th, leaf spring, the 16th, tapered roller bearing.

The 20C of inner ring portion of this moment is divided into the 22C of inner ring portion and output axial region 26 two-part, is equipped with compression relief cam 50 between opposing side 22c, the 26c of 22C of inner ring portion and output axial region 26.

In the speed change gear 10P that constitutes like this, transmit to the 22C of inner ring portion via the rolling element K that is provided on the rolling element holding part 42 as the inner ring 20C of output shaft So as the torque of the outer ring 30C of input shaft Si.At this moment, in inner ring 20C as output shaft So since compression relief cam 50 corresponding to the torque corrective action of input shaft Si in the precompressed of rolling element K, so can when having input torque, precompressed be suppressed at inferior limit.In addition, because the worm gear 55 of gear ratio changeable mechanism links with the gear part 41a that forms on the retainer 40C of traction inputoutput unit and carries out differential Spin Control, so, can change the gear ratio of input and output shaft.

In addition, the worm gear 55A of driving torque assisting agency is attached on the gear part 35 of rotating with output axial region 26 one of inner ring 20C and imposes on desirable rotating torques, so, can increase from the driving torque of output shaft So output.

In addition, when the speed change gear 10P of above-mentioned formation compares,, can reduce running noise under identical condition owing to can lower scope turn round at the rotating speed of worm gear 55.

The 5th mode of execution

Then, describe based on the 5th mode of execution of accompanying drawing speed change gear of the present invention.Below Shuo Ming mode of execution is the two stage speed change that carries out the speed change opposite with the speed change of the first order by the input output that connect two groups of above-mentioned traction transmission gear shifts in the second level.In addition, the part mark identical symbol identical with above-mentioned mode of execution omits its detailed description.

The speed change gear 10Q of mode of execution shown in Figure 180, the traction of the rolling element K of utilization between input shaft Si and output shaft So, make the rotation speed change of input shaft Si become desirable gear ratio and export from output shaft So, and left and right symmetrically links input shaft Si and output shaft So and carries out two stage speed change.

At two of housing 11 side-prominent input shaft Si and output shaft So is the axial region that is provided with on the inner ring of bilateral symmetry and the first order speed changing portion TR1 that links and second level speed changing portion TR2 substantially in the axial direction.

First order speed changing portion TR1 is provided with the rolling element holding part 142 of pectination on the main body 141 of first retainer 140, make the rolling element K that sets on this rolling element holding part 142 between first inner ring 120 that is provided with input shaft Si and be provided with between first outer ring 130 that links output shaft 131.Even under this situation, rolling element holding part 142 also is not limited to pectination, can suitably select ladder shape etc.

Second level speed changing portion TR2, the rolling element holding part 242 of pectination is set on the main body (part of housing 11) of second retainer 240, makes the rolling element K that on this rolling element holding part 242, sets between second inner ring 220 that is provided with output shaft So and be provided with between second outer ring 230 that links input shaft 231.Even under this situation, rolling element holding part 242 also is not limited to pectination, can suitably select ladder shape etc.

In addition, above-mentioned rolling element K is in any of first order speed changing portion TR1 and second level speed changing portion TR2, and its rotation axis is the non-orthogonal and tilted configuration with the axis of input shaft Si and output shaft So all.

Relative at the end end face of the binding output shaft 131 that makes first order speed changing portion TR1 and the binding input shaft 231 of second level speed changing portion TR2 and on the axle linking department that links, be provided with the compression relief cam 50 that works as pre-pressure regulator.This compression relief cam 50 is identical with the first above-mentioned mode of execution, and the recess space that forms between the opposing side of axle linking department is contained setting with the state that slides that can roll.Such recess becomes equidistantly and many groups is set radially from the axle center at circumferencial direction, but this quantity can suitably be selected according to many conditions.

In addition, first retainer 140 has the gear part 141a that forms on the outer circumferential face of main body 141, and this gear part 141a links with worm gear 55 engagements of working as the gear ratio changeable mechanism.That is, this formation is so that the input and output shaft mode of left and right symmetry makes up the traction drive mechanism that illustrates in first mode of execution and constitutes.

And second inner ring 220 with output shaft So is provided with the gear part 35 of one rotation.The worm gear 55A engagement of this gear part 35 and driving torque assisting agency and linking has to make from worm gear 55A and output shaft So is applied desirable rotating torques and the driving torque enlarged functional exported.In addition, second retainer 240 is to be fixed on the housing 11 and to form the motionless parts of its part, and the symbol 12 among the figure is bearings, the 13rd, and oil sealing, the 14th, leaf spring.

According to such speed change gear 10Q, in first order speed changing portion TR1,, transmit to having first outer ring 130 that links output shaft 131 via the rolling element K on the rolling element holding part 142 that is provided in first retainer 140 as the torque of first inner ring 120 of input shaft Si by the traction transmission.Then, in the speed changing portion TR2 of the second level, moment of torsion transmits to having second foreign steamer 230 that links input shaft 231 via the compression relief cam 50 that works as the precompressed regulating device, and transmits to second inner ring 220 as output shaft So via the rolling element K that sets on the rolling element holding part 242 of second retainer 240.

At this moment, to link carry-out part 131 via compression relief cam 50 and link the axle linking department that links between the input part 231, since compression relief cam 50 corresponding to the torque corrective action that links carry-out part 131 in the precompressed of the rolling element K of first order speed changing portion and second level speed changing portion, so can when not having input torque, be suppressed to the minimal precompressed that leaf spring 14 is stipulated.In addition, because the worm gear 55 of gear ratio changeable mechanism links with the gear part 141a that forms on first holding part 140 of traction inputoutput unit and carries out differential Spin Control, so, the gear ratio of input and output shaft can be changed to desirable value.

In addition, in above-mentioned speed change gear 10Q, because the worm gear 55A of driving torque assisting agency is attached at and has on the gear part 35 of section two inner rings 220 for the one rotation of output shaft So, so the rotation corresponding to worm gear 55A applies desirable rotating torques to output shaft So, so, can increase from the driving torque of output shaft So output.

In addition, the speed change gear 10Q of Gou Chenging is after first order speed changing portion TR1 speed change like this, and speed changing portion TR2 carries out reverse speed change in the second level, so, for example slow down at second level speed changing portion TR2 after first order speed changing portion TR1 speedup, the input/output relation that draws based on trace becomes 1: 1.Therefore, when being assembled into this device among the Vehicular steering apparatus ST, can directly apply flexibly existing Chi Tiao ﹠amp; Gearing 64.

In addition, the speed change gear 10Q of above-mentioned formation when comparing under identical condition, particularly can lower scope turn round at the rotating speed of worm gear 55, so can reduce running noise.In addition, because the number of bearings of using is few, has the advantage of easy assembling.

Then, based on Figure 19 first variation of the speed change gear of above-mentioned the 5th mode of execution is described.In addition, the part mark identical symbol identical with above-mentioned mode of execution omits its detailed description.

In the speed change gear 10R of this variation explanation, have: first order speed changing portion TR11, it makes the rolling element K that sets on this rolling element holding part 142 between the first inner ring 120A that is provided with input shaft Si and the first outer ring 130A having the rolling element holding part 142 that pectination is set on the first retainer 140A that links output shaft 143; Second level speed changing portion TR21, it has the rolling element holding part 242 that pectination is set on the second retainer 240A that links output shaft 243, makes the rolling element K that sets on this rolling element holding part 242 between the second inner ring 220A that is provided with output shaft So and second outer ring (be fixed on housing 11 and become one).

And, on the axle linking department that links output shaft 143 and binding input shaft 243, be provided as the compression relief cam 50 that pre-pressure regulator works, and, the worm gear 55 of gear ratio changeable mechanism and the gear part 30a binding that forms at the first outer ring 130A.That is, this formation is so that the input and output shaft mode of left and right symmetry makes up the haulage gear of first variation that illustrates in the 4th mode of execution constitutes.

And, the gear part 35 that one is rotated is set on the second inner ring 220A as output shaft So, the worm gear 55A and the gear part 35 that work as above-mentioned driving torque assisting agency mesh and binding.

According to such speed change gear 10R, in first order speed changing portion TR11,, transmit to having the first retainer 140A that links output shaft 143 via the rolling element K on the rolling element holding part 142 that is provided in the first retainer 140A as the torque of the first inner ring 120A of input shaft Si by the traction transmission.Then, in the speed changing portion TR21 of the second level, the second retainer 240A torque transmitted that links input shaft 243 via the compression relief cam 50 that works as pre-pressure regulator to conduct, via the rolling element K that on the rolling element holding part 242 of the second retainer 240A, sets, transmit to the second inner ring 220A as output shaft So by the traction transmission.

At this moment, to link output shaft 143 via compression relief cam 50 and link the axle linking department that links between the input shaft 243, since compression relief cam 50 corresponding to the torque corrective action that links output shaft 143 in the precompressed of the rolling element K of first order speed changing portion TR11 and second level speed changing portion TR21, so can when having input torque, precompressed be suppressed to inferior limit.

In addition, because the worm gear 55 of gear ratio changeable mechanism links with the gear part 30a that forms on the first outer ring 130A of traction inputoutput unit and carries out differential Spin Control, so, the gear ratio of input and output shaft can be changed to desirable value.

And, because the worm gear 55A of driving torque assisting agency links with output shaft So and applies desirable rotating torques, so, the driving torque of exporting from output shaft So can be increased.

In addition, the speed change gear 10R of Gou Chenging is after first order speed changing portion TR11 speed change like this, and speed changing portion TR21 carries out reverse speed change in the second level, so, for example slow down at second level speed changing portion TR21 after first order speed changing portion TR11 speedup, the input/output relation that draws based on trace becomes 1: 1.Therefore, when being assembled into this device among the Vehicular steering apparatus ST, can directly apply flexibly existing Chi Tiao ﹠amp; Gearing 64.

In addition, the speed change gear 10R of above-mentioned formation when comparing, owing to can lower scope turn round at the rotating speed of worm gear 55, can reduce running noise under identical condition.

Then, based on Figure 20 second variation of the speed change gear of above-mentioned the 5th mode of execution is described.In addition, the part mark identical symbol identical with above-mentioned mode of execution omits its detailed description.

In the speed change gear 10S of this variation explanation, have: first order speed changing portion TR12, it has the rolling element holding part 142 that pectination is set on the first retainer 140B of input shaft Si, makes the rolling element K that sets on this rolling element holding part 142 between being provided with between first inner ring, 1 20B and the first outer ring 130B that links on the output shaft 126; Second level speed changing portion TR22, it has the rolling element holding part 242 that pectination is set on the second retainer 240B of output shaft So, make the rolling element K that on this rolling element holding part 242, sets between be provided with the second inner ring 220B that links input shaft 226 and be fixed on the housing 11 and second outer ring that becomes one between.

And, on the axle linking department that links output shaft 126 and binding input shaft 226, be provided as the compression relief cam 50 that pre-pressure regulator works, and, link as gear ratio changeable mechanism worm gear 55 that works and the gear part 30a that on the first outer ring 130B, forms.That is, this formation is so that the input and output shaft mode of left and right symmetry makes up the haulage gear of second variation that illustrates in the 4th mode of execution constitutes.

And, the gear part 35 that one is rotated is set on the second retainer 240B as output shaft So, the worm gear 55A and the gear part 35 that work as above-mentioned driving torque assisting agency mesh and binding.

According to such speed change gear 10S, in first order speed changing portion TR12, transmit to having the first inner ring 120B that links output shaft 126 via the rolling element K on the rolling element holding part 142 that is provided in the first retainer 140B as the torque of the first inner ring 140B of input shaft Si.

Then, in the speed changing portion TR22 of the second level, torque is transmitted to having the second inner ring 220B that links input shaft 226 via the compression relief cam 50 that works as pre-pressure regulator, then, transmit to the second retainer 240B via the rolling element K that on the rolling element holding part 242 of the second retainer 240B, sets as output shaft So.

At this moment, to link carry-out part 126 via compression relief cam 50 and link the axle linking department that links between the input part 226, since compression relief cam 50 corresponding to the torque corrective action that links carry-out part 126 in the precompressed of the rolling element K of first order speed changing portion TR12 and second level speed changing portion TR22, so can when having input torque, precompressed be suppressed to inferior limit.

In addition, because the worm gear 55 of gear ratio changeable mechanism links with the gear part 30a that forms on the first outer ring 130B of traction inputoutput unit and carries out differential Spin Control, so, the gear ratio of input and output shaft can be changed to desirable value.

In addition, the speed change gear 10S of Gou Chenging is after first order speed changing portion TR12 speed change like this, and speed changing portion TR22 carries out reverse speed change in the second level, so, for example slow down at second level speed changing portion TR22 after first order speed changing portion TR12 speedup, the input/output relation that draws based on trace becomes 1: 1.Therefore, when being assembled into this device among the Vehicular steering apparatus ST, can directly apply flexibly existing Chi Tiao ﹠amp; Gearing 64.

In addition, the speed change gear 10S of above-mentioned formation, because the quantity of bearing is fewer, assembling easily.When under identical condition, comparing, particularly the face of rolling element K can be constrained make lower, and, also set the driving torque of the input shaft Si that sets on the compression relief cam 50 lower, be very favourable aspect working life and the serviceability.

Then, based on Figure 21 the 3rd variation of the speed change gear of above-mentioned the 5th mode of execution is described.In addition, the part mark identical symbol identical with above-mentioned mode of execution omits its detailed description.

Speed change gear 10T in this variation explanation, have: first order speed changing portion TR13, it is provided with pectination on the first retainer 140C rolling element holding part 142 makes the rolling element K that sets on this rolling element holding part 142 between being provided with the first inner ring 120C that links output shaft 126 and being provided with between the first outer ring 130C of input shaft Si; Second level speed changing portion TR23, it is provided with pectination on the second retainer 240C rolling element holding part 242 makes the rolling element K that sets on this rolling element holding part 242 between being provided with the second inner ring 220C that links input shaft 226 and being provided with between the second outer ring 230C of output shaft So.

And, on the axle linking department that links output shaft 126 and binding input shaft 226, be provided as the compression relief cam 50 that pre-pressure regulator works, and, link as gear ratio changeable mechanism worm gear 55 that works and the gear part 141a that on the first retainer 140C, forms.That is, this formation is so that the input and output shaft mode of left and right symmetry is combined in the haulage gear of the 3rd variation of the 4th mode of execution explanation constitutes.

In addition, the gear part 35 of one rotation is set on the second outer ring 230A as output shaft So, the worm gear 55A and the gear part 35 that work as above-mentioned driving torque assisting agency mesh and binding.

According to such speed change gear 10T, in first order speed changing portion TR13, transmit to having the first inner ring 120C that links output shaft 126 via the rolling element K on the rolling element holding part 142 that is provided in the first retainer 140C as the torque of the first inner ring 130C of input shaft Si.Then, in the speed changing portion TR23 of the second level, transmit to the second outer ring 230C via rolling element K to having the second inner ring 220C torque transmitted that links input shaft 226 via the compression relief cam 50 that works as pre-pressure regulator as output shaft So, described rolling element K is configured on the rolling element holding part 242, and this rolling element holding part 242 is arranged on and is fixed on the housing 11 and on the integrally formed second motionless retainer.

At this moment, to link output shaft 126 via compression relief cam 50 and link the axle linking department that links between the input shaft 226, since compression relief cam 50 corresponding to the torque corrective action that links output shaft 126 in the precompressed of the rolling element K of first order speed changing portion TR13 and second level speed changing portion TR23, so can when having input torque, precompressed be suppressed to inferior limit.

In addition, because the worm gear 55 of gear ratio changeable mechanism links with the gear part 141a that forms on the first retainer 140C of traction inputoutput unit and carries out differential Spin Control, so, the gear ratio of input and output shaft can be changed to desirable value.

And, because the worm gear 55A of driving torque assisting agency links with output shaft So and applies desirable rotating force, so, the driving torque of exporting from output shaft So can be increased.

In addition, the speed change gear 10T of Gou Chenging is after first order speed changing portion TR13 speed change like this, and speed changing portion TR23 carries out reverse speed change in the second level, so, for example slow down at second level speed changing portion TR23 after first order speed changing portion TR13 speedup, the input/output relation that draws based on trace becomes 1: 1.Therefore, when being assembled into this device among the Vehicular steering apparatus ST, can directly apply flexibly existing Chi Tiao ﹠amp; Gearing 64.

In addition, the speed change gear 10T of above-mentioned formation is when comparing under identical condition, the face of rolling element K can be constrained make lower, and, also set the driving torque of the input shaft Si of configuration compression relief cam 50 lower, therefore, be favourable aspect working life and the durability.Owing to can lower scope turn round at the rotating speed of worm gear 55, can reduce running noise.

As mentioned above, speed change gear shown in the 4th mode of execution of the present invention, owing to make the nonopiate earth tilt configuration of axis of rotation axis and input shaft Si and the output shaft So of rolling element K, and has the compression relief cam 50 that makes the precompressed automatic pre-pressure regulator that changes that imposes on rolling element K corresponding to the torque of input shaft Si, link with the traction inputoutput unit of rolling element K and carry out the rotating speed control of this traction inputoutput unit and make the worm gear 55 of gear ratio changeable mechanism of the differential type of gear ratio variation, and output shaft So applied rotating force and increase the worm gear 55A of the driving torque assisting agency of driving torque, so compression relief cam 50 is adjusted the precompressed of the rolling element that applies this tilted configuration corresponding to the torque of input shaft Si.That is, the thrust load that compression relief cam 50 produces corresponding to driving torque, this thrust load becomes the precompressed that pushes rolling element K in the axial direction.

In addition, since have differential type gear ratio changeable mechanism, the gear ratio of input and output shaft and setting arbitrarily can be adjusted, and, owing to can apply rotating force to output shaft So, can increase from the driving torque of output shaft So output by driving torque assisting agency.

In addition, speed change gear shown in the 5th mode of execution of the present invention, owing to make the nonopiate earth tilt configuration of axis of rotation axis and input shaft Si and the output shaft So of rolling element K, and has the compression relief cam 50 that makes the precompressed automatic pre-pressure regulator that changes that imposes on rolling element K corresponding to the torque that links first order speed changing portion and second level speed changing portion between centers, link with the traction inputoutput unit of rolling element K and carry out the rotating speed control of this traction inputoutput unit and make the worm gear 55 of the gear ratio changeable mechanism of gear ratio variation, and output shaft So applied rotating force and increase the worm gear 55A of the driving torque assisting agency of driving torque, so compression relief cam 50 is adjusted the precompressed of the rolling element that applies this tilted configuration corresponding to the torque that links first order speed changing portion and second level speed changing portion between centers.

In addition, owing to have differential type gear ratio changeable mechanism, thus can adjust the gear ratio of input and output shaft and setting arbitrarily, and, can apply rotating force to output shaft So by driving torque assisting agency, so can increase from the driving torque of output shaft So output.In this case, owing to carry out two stage speed change by first order speed changing portion and second level speed changing portion, so, be 1: 1 based on the input/output relation that draws transmission in identical sense of rotation.

In addition, the present invention is not limited to above-mentioned mode of execution, can suitably change in the scope that does not break away from purport of the present invention.

Claims

1. torque transmission structure, carry out transmission of torque in rotation on the same axis between the opposing side of two parts of configuration, it is characterized in that, between described opposing side, be provided with the recess that many group section configurations form plane of inclination or curved surface, set compression relief cam in this recess space.

2. traction drive transmission device, the traction of the rolling element of utilization between input shaft and output shaft, make described input shaft rotational speed be varied to desirable gear ratio and from the output of described output shaft, it is characterized in that, make the nonopiate earth tilt configuration of axis of rotation axis and the described input shaft and the described output shaft of described rolling element, and have: pre-pressure regulator, it makes the precompressed that imposes on described rolling element change automatically corresponding to the torque of described input shaft; The gear ratio changeable mechanism of differential type, it is connected with the traction inputoutput unit of described rolling element, carries out the rotating speed control of this traction inputoutput unit and described gear ratio is changed.

3. traction drive transmission device as claimed in claim 2 is characterized in that, has described output shaft is applied the driving torque assisting agency that rotating force increases driving torque.

4. as claim 2 or 3 described traction drive transmission devices, it is characterized in that, make the described rolling element that is equipped on the retainer between the inner ring that is provided with described input shaft and be provided with between the outer ring of described output shaft, described pre-pressure regulator is set on described inner ring, and, described gear ratio changeable mechanism and described retainer are linked.

5. as claim 2 or 3 described traction drive transmission devices, it is characterized in that, make and have the described rolling element that disposes on the retainer of described output shaft between inner ring that is provided with described input shaft and outer ring, described pre-pressure regulator is set on described retainer, and, described gear ratio changeable mechanism and described outer ring are linked.

6. traction drive transmission device as claimed in claim 2, it is characterized in that, make and have the described rolling element that disposes on the retainer of described input shaft between inner ring and be provided with between the outer ring of described output shaft, described pre-pressure regulator is set on described inner ring, and links described gear ratio changeable mechanism.

7. traction drive transmission device as claimed in claim 6 is characterized in that, formative gear portion and mesh with rack pinion on the outer circumferential face of described outer ring or side.

8. as claim 2 or 3 described traction drive transmission devices, it is characterized in that, make and have the described rolling element that disposes on the retainer of described input shaft between inner ring that is provided with described output shaft and outer ring, pre-pressure regulator is set on described inner ring, and, described gear ratio changeable mechanism and described outer ring are linked.

9. traction drive transmission device as claimed in claim 2, it is characterized in that, making is becoming the described rolling element that disposes on the retainer of described output shaft between inner ring and be provided with between the outer ring of described input shaft, pre-pressure regulator is set on described inner ring, and links described gear ratio changeable mechanism.

10. traction drive transmission device as claimed in claim 9 is characterized in that, formative gear portion and mesh with rack pinion on the outer circumferential face of described retainer or side.

11. as claim 2 or 3 described traction drive transmission devices, it is characterized in that, make the described rolling element that is equipped on the retainer between the inner ring that is provided with described output shaft and be provided with between the outer ring of described input shaft, described pre-pressure regulator is set on described inner ring, and, described gear ratio changeable mechanism and described retainer are linked.

12. traction drive transmission device, the traction of the rolling element of utilization between input shaft and output shaft, make described input shaft rotational speed be varied to desirable gear ratio and from the output of described output shaft, simultaneously, described input shaft and output shaft left and right symmetrically linked and carry out two stage speed change, it is characterized in that, make the nonopiate earth tilt configuration of axis of rotation axis and the described input shaft and the described output shaft of described rolling element, have: pre-pressure regulator, it makes the precompressed that imposes on described rolling element change automatically corresponding to the torque of the between centers that links first order speed changing portion and second level speed changing portion; The gear ratio changeable mechanism, the traction inputoutput unit of itself and described rolling element links, and carries out the rotating speed control of this traction inputoutput unit and makes described gear ratio variation.

13. traction drive transmission device as claimed in claim 12 is characterized in that, has described output shaft is applied the driving torque assisting agency that rotating force increases driving torque.

14., it is characterized in that having as claim 12 or 13 described traction drive transmission devices:

First order speed changing portion, it makes the described rolling element that is equipped on first retainer between first inner ring that is provided with described input shaft and be provided with between first outer ring that links output shaft;

Second level speed changing portion, it makes the described rolling element that is equipped on second retainer between second inner ring that is provided with described output shaft and be provided with between second outer ring that links input shaft,

On the axle linking department of described binding output shaft and described binding input shaft, described pre-pressure regulator is set, and, described gear ratio changeable mechanism is attached on described first retainer, described second retainer is fixed on the housing.

15., it is characterized in that having as claim 12 or 13 described traction drive transmission devices:

First order speed changing portion, it makes the described rolling element that is equipped on first retainer with binding output shaft between first inner ring that is provided with described input shaft and first outer ring;

Second level speed changing portion, it makes the described rolling element that disposes on second retainer with binding input shaft between second inner ring that is provided with described output shaft and second outer ring,

On the axle linking department of described binding output shaft and described binding input shaft, described pre-pressure regulator is set, and, described gear ratio changeable mechanism is attached on described first outer ring, described second outer ring is fixed on the housing.

16., it is characterized in that having as claim 12 or 13 described traction drive transmission devices:

First order speed changing portion, it makes has the described rolling element that disposes on first retainer of described input shaft between being provided with between first inner ring and first outer ring that links output shaft;

Second level speed changing portion, it makes has the described rolling element that disposes on second retainer of described output shaft between being provided with between second inner ring and second outer ring that links input shaft,

17., it is characterized in that having as claim 12 or 13 described traction drive transmission devices:

First order speed changing portion, it makes the described rolling element that is equipped on first retainer between being provided with first inner ring that links output shaft and being provided with between first outer ring on the described input shaft;

Second level speed changing portion, it makes the described rolling element that is equipped on second retainer between being provided with second inner ring that links input shaft and being provided with between second outer ring of described output shaft,

18. traction drive transmission device, the traction of the rolling element of utilization between input shaft and output shaft, make described input shaft rotational speed be varied to desirable gear ratio and from the output of described output shaft, simultaneously, link described input shaft and output shaft and carry out two stage speed change, it is characterized in that, make the nonopiate earth tilt configuration of axis of rotation axis and the described input shaft and the described output shaft of described rolling element, and have: pre-pressure regulator, its precompressed that will impose on described rolling element changes automatically corresponding to the torque of the between centers that links first order speed changing portion and second level speed changing portion; The gear ratio changeable mechanism, the traction inputoutput unit of itself and described rolling element links, carry out the rotating speed control of this traction inputoutput unit and described gear ratio is changed, the traction inputoutput unit of described first order speed changing portion and described second level speed changing portion linked and integrated, the gear ratio of two speed changing portions is provided with difference.

19. traction drive transmission device as claimed in claim 18 is characterized in that, has:

First order speed changing portion, it makes has the described rolling element that disposes on first retainer of described input shaft between being provided with between first inner ring that links output shaft and the outer ring binding parts;

Second level speed changing portion, it makes has the described rolling element that disposes on second retainer of described output shaft between being provided with between second inner ring that links input shaft and the described outer ring binding parts,

On the axle linking department of described binding output shaft and described binding input shaft, described pre-pressure regulator is set, and, described gear ratio changeable mechanism is attached at described outer ring links on the parts.

20. as each described traction drive transmission device in the claim 2～19, it is characterized in that, described pre-pressure regulator is in rotation on the same axis and the torque transmission structure that carries out the torque transmission between the opposing side of two parts of configuration, between described opposing side, be provided with the recess that many group section configurations form plane of inclination or curved surface, be equipped with compression relief cam in this recess space.

21., it is characterized in that described gear ratio changeable mechanism is the worm gear with driving source that can Spin Control as each described traction drive transmission device in the claim 2～20.

22. as each described traction drive transmission device in the claim 2～21, it is characterized in that, described gear ratio changeable mechanism be with described input shaft and the coaxial hollow motor that sets of described output shaft epicyclic type mechanism as driving source.

23., it is characterized in that described driving torque assisting agency is the worm gear with drive unit as each described traction drive transmission device in the claim 3～5,8,11,13～17,20～22.

24. a Vehicular steering apparatus is characterized in that, driver's steering operation via each described traction drive transmission device in the claim 2～23 to the Steering Wheel transmission of vehicle.