JP2001330146A - Assistor for operating transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an assistor for operating a transmission capable of miniaturization in a diametric direction and an axial direction of a piston. SOLUTION: A power piston 5 is slidably arranged in a power cylinder part 2 fixed on an upper case 6 of a transmission T, pressure chambers 11a, 11b are partitioned by the power piston 5. A control valve 3 is arranged in the power piston 5. The control valve 3 arranges valve spools 71a, 71b opposedly and radially interposes an input transmitting pin 76 and a rod member 4a of a shift lever 4 of the transmission T therebetween. When the input transmitting pin 76 is moved in one direction, high pressure air is supplied from this side operating pressure chamber 26 to the reverse side pressure chamber 11, internal air is discharged to the atmosphere through an exhaust port 22 of a shift level chamber 23 from an exhaust chamber 21 in the other side, in this way the rod member 4a is followed the displacement of the input transmitting pin 76.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a speed change operation booster mounted on a vehicle such as an automobile, and more particularly to an improvement thereof.

[0002]

2. Description of the Related Art In conventional vehicles, particularly buses and trucks having a large transmission, an actuator that uses fluid pressure (particularly air pressure) is incorporated in a gear shift operation booster, and a smooth gear shift is performed with a light operating force of a change lever. You can operate it.

[0003] This type of speed change operation booster usually includes a power cylinder portion, a control valve mechanism portion, and an operation rod whose end is connected to a change lever side. The power cylinder section includes a cylinder body, a piston slidably disposed within the cylinder body, and a piston for dividing the cylinder body into two pressure chambers; A hollow piston rod connected to the shift lever side of the transmission.
The control valve mechanism is disposed in the hollow piston rod, and is opened and closed by the operation rod slidably disposed in the piston rod.

[0004] High-pressure air is supplied to one of the pressure chambers and low-pressure air is supplied to the other of the pressure chambers via the valve mechanism by a relative displacement between the operation rod and the piston rod by operating the change lever. And, together with the piston, the piston rod is made to follow the displacement caused by the operation of the operating rod, so that the light operating force of the change lever is boosted to rotate the shift lever of the transmission. Is operated.

[0005] However, the conventional speed change operation booster has the following problems. That is,
(A) Since the housing of the booster and the shift lever of the transmission are separate structures, the structure is complicated and large.

(B) Since the operating points of the operating force (output) to the shift lever of the transmission of the booster and the shift command operating force (input) from the change lever are the same, (I) The operation stroke of the change lever cannot be changed. Therefore, the operability is poor. (Ii) There is no degree of freedom in mounting the booster to the transmission, and the vehicle mountability is poor.

(C) Further, since the power cylinder and the control valve of the booster have an integral structure,
(I) The operation stroke of the speed change operation lever cannot be changed. Therefore, the operability is poor. (Ii) There is no degree of freedom in mounting the booster to the transmission, and the vehicle mountability is poor.

Therefore, in order to solve the above problems,
The transmission operation booster shown in FIG. 13 or FIG. 14 is configured as follows.

A cylinder main body 110 of the power cylinder 102 of the speed change operation booster 101 is integrally formed with or disposed on the shift lever 104, and is slidably disposed within the cylinder main body 110. Piston 1
The output shaft end 05 is fixed to the main body of the transmission or a vehicle body to which the transmission main body is fixed via a piston rod 106 so that the output shaft end does not move in the rotation direction of the shift lever 104. I have.

The shift operation booster 101 supplies and discharges high-pressure air to and from two pressure chambers 111a and 111b divided by a piston 105 in the cylinder body 110 based on the shift command operation force. The control valve 103 includes a shift command operating force transmitting unit, or the shift command operating force transmitting unit and the shift lever 1.
04 or one of the shift levers 104.

Further, the positions of the cylinder main body 110 and the control valve 103 are different from each other in the radial direction, the circumferential direction, or the axial direction of the rotation of the shift lever 104.

With such a configuration, for example, high-pressure air is supplied to the pressure chamber 111a and another pressure chamber 111a is supplied to the pressure chamber 111a.
b, low-pressure air is introduced into the power cylinder 10
The second cylinder body 110 moves with respect to the transmission body, and the shift lever 104 rotates to perform a shift operation.

Further, the position where the command operation force from the change lever acts on the shift lever 104 can be changed to the position where the power cylinder 102 acts. Further, the control valve 103 for controlling the operating pressure of the high-pressure air of the power cylinder 102 according to a command operation stroke of the change lever is provided between the change lever and the shift lever 104 of the transmission. ing.

[0014]

However, even such a conventional speed change operation booster has the following problems. That is, in the conventional transmission operating booster, (a) the control valve 103 is disposed inside the output shaft, and the piston 105 is disposed outside the output shaft. (b) Since the connecting portion of the shift lever 104 of the output shaft is arranged in series with the piston 105, the size increases in the axial direction. Further, Japanese Patent Application Laid-Open No. H11-32
In the transmission operation booster 5241, since the power cylinder and the control valve are separately arranged, the size is increased.

The present invention has been made in view of such circumstances, and has as its object to provide a transmission operation booster that can be downsized in both the radial and axial directions of the piston.

[0016]

SUMMARY OF THE INVENTION The present invention has been made to solve the above problem, and doubles the shift command operating force transmitted from the shift operation command operating means via the shift command operating force transmitting means. In a transmission operation booster for operating a shift lever of a transmission by force, a cylinder body of a power cylinder fixed to a transmission body and a cylinder body slidably disposed in the cylinder body. A piston that defines a pressure chamber on each end side thereof, and a control valve that is disposed inside the piston and that supplies and discharges fluid pressure to and from the pressure chamber.
An input transmission unit inserted radially into the piston to operate the control valve; and an output transmission unit inserted radially into the piston and transmitting the output of the piston to the shift lever. And

The input transmitting means has an input transmitting piston disposed in parallel with the cylinder body and connected to the shift command operating force transmitting means.

The input transmitting means has an input transmitting lever having one end connected to the speed change command operating force transmitting means and the other end having an input transmitting member for operating the control valve.

The piston is provided with a guide member for the output transmission means.

The control valve is a spool valve type control valve. A supply valve is provided on both outer sides of the spool valve for communicating and shutting off the pressure chamber and the compressed air source, and a pressure chamber is provided inside the spool valve. And an exhaust valve that communicates with and shuts off the air.

[0021]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Next, an embodiment of a transmission operation booster according to the present invention will be described with reference to the drawings.
FIGS. 1 to 6 show a transmission operation booster according to a first embodiment of the present invention, and FIGS. 7 to 11 show a transmission operation booster according to a second embodiment. 12 is shown in FIG. First, a transmission operation booster 1 according to a first embodiment of the present invention will be described with reference to FIG.
This will be described with reference to FIGS.

A schematic configuration of the transmission operation booster 1 will be described with reference to FIG. As shown in the figure, the speed change operation booster 1 rotates a shift lever 4 connected to an end of a shift shaft (shift shaft) Ta rotatably disposed within a main body Tb of the transmission T. Power cylinder part 2
And an operation unit 7 connected to the change lever 9 via a link mechanism, and a control valve 3 operated by the operation of the operation unit 7 to supply and discharge compressed air pressure to the power cylinder unit 2. I have.

The power cylinder 2 has a power piston 5 (piston) and a cylinder body 10. The cylinder body 10 is arranged such that the axis of the power cylinder 2 is tangential to the rotation of the shift lever 4 of the transmission T.
The transmission T is fixed to the main body Tb side (upper case 6). The other end of the shift lever 4, one end of which is connected to the end of the shift shaft Ta, is engaged with the power piston 5, and the shift of the shift lever 4 is caused by the movement of the power piston 5. The operation unit 7 connected to the change lever 9 is engaged with the control valve 3, and the control valve is controlled by the operation force from the change lever applied to the operation unit 7. The control valve 3 is a spool valve having valve spools 71a and 71b and valve sleeves 72a and 72b in the first and second embodiments, as described later. It is a one-valve, two-seat type having valve lifters 81a, 81b, valve seat members 82a, 82b, and valve members 83a, 83b.

When the operation unit 7 is displaced by operating the change lever 9, the compressed air is supplied to and discharged from the power cylinder unit 2 by the operation of the control valve 3 to which the compressed air is supplied. The shift lever 4 is operated while following the displacement of the operation unit 7 via the power piston 5 to rotate the shift shaft Ta of the transmission T.

Next, each configuration of the speed change operation booster will be described with reference to FIGS. As shown in FIG. 3 or FIG. 4, in the cylinder body 10 of the power cylinder unit 2,
A cylinder 10a is formed. This cylinder 10a
Is divided into a pressure chamber (A) 11a and a pressure chamber (B) 11b by a power piston 5 slidably disposed inside. The cylinder 10a is sealed with a plug 12 using a ring-shaped sheet member. This plug 12
Is fixed by a retaining ring 13, thereby preventing the plug 12 from coming out of the cylinder body 10.

In the power piston 5, a control valve 3 for supplying and discharging air pressure to and from the pressure chamber (A) 11a and the pressure chamber (B) 11b is slidably disposed. The axis of the control valve 3 coincides with the axis of the power piston 5.

As shown in FIG. 3 or FIG. 4, a valve hole is formed in the power piston 5 along the axial direction, and a valve constituting a part of the control valve 3 is formed in the valve hole. Sleeves 72a and 72b are provided, and both ends forming a part of the control valve 3 are formed with small diameters in their inner diameter holes.
Valve spools 71a and 71b each having a step diameter are slidably supported while being guided at one end and a large diameter portion, respectively. The valve spools 71a and 71b have the same shape, and are arranged to face each other such that the respective spool axes overlap with each other. This concentricity need not be high precision. Holes are formed in the valve spools 71a and 71b along the axial direction for weight reduction. Further, the valve spools 71a and 71b may be formed of resin for weight reduction and cost reduction.

As shown in FIG. 3 or FIG. 4, the inside of the valve hole between the valve spools 71a and 71b has a step shape, and the plates 73a and 73 are brought into contact with this portion.
b is provided. The plates 73a, 73b are provided with holes larger than the small diameter portion of the valve spools 71a, 71b, respectively, and are smaller than the large diameter portion.
1b are respectively inserted. By this insertion, each end face of the large diameter portion of the valve spool 71a, 71b is
3a and 73b respectively contact the outer surfaces. Since the distance between the plates 73a and 73b is kept constant by the step shape in the valve hole, the valve gap is stabilized, and the performance of the valve is improved. The plates 73a and 73b are provided with a plurality of ventilation holes (not shown) along the circumferential direction.

As shown in FIG. 3 or FIG. 4, after the valve spools 71a and 71b are respectively inserted into the valve holes of the power piston 5, they are sealed from both sides with plugs 75 using a ring-shaped sheet member. This plug 75 is used for the retaining ring 2
9 to prevent the plug 75 from slipping out of the power piston 5.

As shown in FIG. 4, compressed air is supplied to the inside of the power piston 5 at both ends of the valve spools 71a and 71b of the control valve 3 through an air passage 24 formed inside the cylinder body 10. An air chamber (A) 25a and an air chamber (B) 25b communicating with the source are formed.
In the power piston 5, air passages 24a and 24b extending in the axial direction are formed. This air passage 24
“a” is opened at one end face (right end face in FIG. 4) of the power piston 5 and communicates with the pressure chamber (A) 11a. Air passage 2
4b is open to the other end surface (the left end surface in FIG. 4) of the power piston 5 and communicates with the pressure chamber (B) 11b. Thus, the air passages 24a and 24b extend in the opposite direction,
They do not communicate with each other.

As shown in FIG. 3 or FIG. 4, the air chamber (A) 25a and the air chamber (B) 2 in the power piston 5 are provided.
5b and the exhaust chamber 21, compressed air is supplied / discharged by the operation of the control valve 3, and the pressure chambers (A) 11a and the pressure chambers (B) of the power cylinder unit 2 are supplied.
An operating pressure chamber (A) 26a and an operating pressure chamber (B) 26b communicating with 11b are formed respectively. That is, the pressure chamber (A) 11a communicates with the working pressure chamber (A) 26a through the air passage 24a, and the pressure chamber (B) 11b communicates with the working pressure chamber (B) 26b through the air passage 24b.
The positions of the pressure chamber (A) 11a and the pressure chamber (B) 11b
The pressure chambers (A) 11a are arranged alternately, and are arranged on the side of the working pressure chamber (B) 26b, and the pressure chamber (B) is arranged on the side of the working pressure chamber (A) 26a.

The valve spools 71a, 7 of the control valve 3
1b are formed in two stages of large and small diameters, respectively, of which a supply valve (A) 27a and a supply valve (B) 27b each having a small sheet diameter ring-shaped sheet member are provided in a small diameter portion. Is provided with an exhaust valve (A) 28a and an exhaust valve (B) 28b each having a ring-shaped seat member having a large seat diameter.

That is, a supply valve (A) 27a which is closed when not in operation is formed between the air chamber (A) 25a and the working pressure chamber (A) 26a, and the working pressure chamber (A) 26a And an exhaust valve (A) that is open when not in operation.
A non-operating closed supply valve (B) 27b is formed between the air chamber (B) 25b and the working pressure chamber (B) 26b to form the working pressure chamber (B) 26b. The exhaust valve (B), which is open when not in operation,
28b are respectively formed.

Air chamber (A) 25a, air chamber (B) 25b
Are connected to a compressed air source (not shown) through the air passage 24 (see FIG. 4), so that the compressed air acts on the small diameter side ends of the valve spools 71a and 71b. For this reason, the valve spools 71a, 71b are urged in a direction in which they contact the plates 73a, 73b. Therefore, the non-operation neutral positions of the valve spools 71a and 71b are maintained.

As shown in FIG. 3 or 4, the air pressure of the air pressure chamber (A) 25a or the air chamber (B) 25b and the valve spools 71a, 71b maintained at the inoperative neutral position by the plates 73a, 73b. An input transmission pin (input transmission member) 76 and a guide member 77 that constitute a part of the operation unit 7 are inserted between them in the radial direction. The guide member 77 guides the input transmission pin 76 and the rod portion 4a of the shift lever 4, and transmits the output of the power piston 5 to the rod portion 4a of the shift lever 4, and is fixed as shown in FIG. It is fixed to the power piston 5 by a pin 78.

The input transmission pin 76 is connected to the valve spool 71
a and 71b with a slight gap. As described above, since the positions of the valve spools 71a and 71b with respect to the valve sleeves 72a and 72b can be secured almost directly, the supply valve (A) 27a, the supply valve (B) 27b, and the exhaust valve (A) 28a in the non-operation position. , Exhaust valve (B) 28
The valve clearance of b becomes more accurate. As shown in FIG.
The hole of the guide member 77 into which the input transmission pin 76 fixed to the input transmission piston 40 protrudes in the radial direction is inserted so that the input transmission pin 76 does not rotate in the circumferential direction with respect to the axis of the power cylinder unit 2. For this purpose, the shape of the hole is long in the axial direction. That is, the inner surface of the long hole on the long axis side is a stopper surface of the input transmission pin 76. One end of an input transmission pin 76 sandwiched between the valve spools 71a and 71b projects radially from the power piston 5 and is provided at a central portion of the input transmission piston 40 slidably supported in parallel with the power piston 5. It is inserted and fixed from the radial direction. One end of the input transmission piston 40 is connected to the link mechanism 8 of the change lever 9, and the operation unit 7 is configured by the input transmission piston 40 and the input transmission pin 76.

As shown in FIG. 2 or FIG. 3, a rod portion 4a is formed at the tip of the shift lever 4, and the rod portion 4a is formed.
a is engaged with the elongated hole of the guide member 77. As shown in FIG. 6, the hole of the guide member 77 into which the rod portion 4a of the shift lever 4 is inserted has a long hole shape elongated in a direction perpendicular to the axial direction. This shape is used so that the rotation of the shift lever 4 is not hindered when the power piston 5 makes a stroke. The diameter of the long hole in the short axis direction is equal to the outer diameter of the rod portion 4a. The diameters are almost the same, and the play between the power piston 5 and the rod portion 4a is eliminated. The guide member 77 guides the input transmission pin 76 and the rod portion 4a as described above, and also controls the control valve 3.
When the compressed air is supplied to the pressure chamber 11a or 11b and the power piston 5 is operated by the operation, the power transmission unit 5 constitutes a part of an output transmission unit that transmits the output of the power piston 5 to the rod unit 4a.

As shown in FIG. 3, the plates 73a, 73
An exhaust chamber 21 is provided at the position where b is disposed, and the exhaust chamber 21 has an exhaust port 22 formed through a clearance between the long hole of the guide member 77 and the rod member 4a (see FIG. 6). In communication with the shift lever chamber 23. Note that FIG.
As shown in FIG.
The guide member on the connection side of the link mechanism 8 is provided with a sealing member 4.
No. 1 is mounted, the exhaust gas is not exhausted from the exhaust chamber 21 through this, and muddy water, dust and the like do not enter from outside.

Next, the operation of the speed change operation booster 1 will be described with reference to FIGS. The control valve 3 is
In the inoperative position shown in FIG. 3 or FIG. 4, the air from the compressed air source is supplied to the air chamber (A) 25 a of the power piston 5,
The pressure is supplied to the air chamber (B) 25b, and the pressure chamber (A) 11a and the pressure chamber (B) 11b
Is open to the atmosphere via the exhaust valve (A) 28a, the exhaust valve (B) 28b, the exhaust chamber 21, the shift lever chamber 23, and the exhaust port 22, and is in a non-operating state.

For example, in order to operate the transmission from the neutral position to the shift position, the change lever 9 is operated, and the input transmission piston 40 is connected to the input transmission pin 7.
When the operation spool 71b is moved rightward in FIG. 3 or FIG. 4 via 6, the exhaust valve (B) 28b is closed first, and then the supply valve (B) 27b is opened. Then, the air supplied to the air chamber (B) 25b is supplied to the supply valve (B).
27b, the working pressure chamber (B) 26b and the air passage 24b are introduced into the pressure chamber (B) 11b of the power cylinder unit 2. Then, with the air pressure, the power cylinder 2
Is pressed to the left, but the cylinder body 10 of the power cylinder unit 2 moves the transmission body Tb (upper) so that the axis of the power cylinder unit 2 is tangential to the rotation of the shift lever 4 of the transmission T. Since the power piston 5 is fixed to the case 6), the power piston 5
Alternatively, it moves rightward in FIG. 4 (the same direction as the moving direction of the input transmission pin 76).

At this time, the pressure chamber (A) 11a of the power cylinder section 2 has a small volume, but the air in the pressure chamber (A) 11a is released from the air passage 24a and the working pressure chamber 2a.
6a, the exhaust valve (A) 28a, the exhaust chamber 21, the shift lever chamber 23, and the exhaust port 22 are exhausted to the atmosphere, so that no pressure is generated in the pressure chamber (A) 11a.
(At this time, the supply valve (A) 27a is closed and the exhaust valve (A) 28a remains open.)

When the power piston 5 moves rightward,
The output from the power piston 5 is transmitted to the rod portion 4a via the guide member 77, and the shift lever 4 rotates rightward. As a result, the shift shaft Ta of the transmission T rotates to perform a shift operation. At this time, since the power piston 5 moves in the same direction as the operation direction of the input transmission pin 76, when the power piston 5 moves by the same stroke as the input transmission pin 76, the control valve 3 becomes the supply valve (B) 27b and the exhaust valve. (B) Both 28b are closed and act to hold it in that position. Thus, the shift operation of the transmission is performed so as to follow the operation of the change lever 9.

When the shift operation of the transmission T is completed, if the user releases his hand from the change lever 9 in the shift position, the operation input to the valve spool 71b becomes 0 (zero). 71b is returned to a position where it abuts on the plate 73b by the action force of the air pressure of the working pressure chamber (B) 26b and the air chamber (B) 25b, returns to the non-operating position, and the supply valve (B) 27b is closed. The exhaust valve (B) 28b is in the open position. Then, the air introduced into the pressure chamber (B) 11b of the power cylinder unit 2 is changed into an air passage 24b, a working pressure chamber 26b, an exhaust valve (B) 28b, an exhaust chamber 21, a shift lever chamber 23, and an exhaust port 22. , The transmission T is kept in the shift position because no force acts to return the transmission T to the neutral position.

Next, in order to return the transmission T to the neutral position, by operating the change lever 9 to move the valve spool 71a to the left in FIG. 3 or FIG. Valve (A) 28a is closed,
The supply valve (A) 27a opens. Then, the air introduced into the air chamber (A) 25a of the power piston 5 flows through the supply valve (A) 27a, the working pressure chamber (A) 26a, and the air passage 24a to the power cylinder unit 2 The power piston 5 is introduced into the pressure chamber (A) 11a,
It moves leftward in FIG. 3 or FIG. 4 and returns to the neutral position. Even when the change lever 9 is operated from the neutral position to move the valve spool 71a to the left via the input transmission pin 76, the same operation is performed as described above.

Here, when compressed air is not supplied due to a defect of the compressed air source or the like, air is supplied to the pressure chambers 11a and 11b even if the input transmission piston 40 moves and the valve spools 71a and 71b move. When the input transmission piston 40 further strokes, the input transmission pin 76 comes into contact with the inner surface (stopper surface) of the long hole of the guide member 77 to directly actuate the power piston 5. In this direction, the shift lever 4 rotates to perform a shift operation (manual operation).

Next, a speed change operation booster according to a second embodiment will be described with reference to FIGS. In addition,
In the present embodiment, description of contents common to the first embodiment is omitted.

In the present embodiment, as shown in FIG. 7, the structure of the connecting portion between the input transmitting portion and the shift lever is different from that of the first embodiment. That is, the shift shaft Ta extends outward (to the right in the figure) beyond the power cylinder portion 2 and the shift lever 4 is on the opposite side to that of the first embodiment, that is, on the same side as the input transmission pin 76. Are located.

In this embodiment, as shown in FIGS. 7 to 11, a cylindrical member 79 is fixed to the shift lever 4 instead of the rod portion 4a in the first embodiment. That is, the cylindrical member 79 is a member corresponding to the rod portion 4a of the first embodiment. As shown in FIGS. 7 to 11, the cylindrical member 79 is attached to the power piston 5 by a fixing pin 7.
The guide member 77 is inserted through an elongated hole (a hole elongated in a direction perpendicular to the axis) fixed through the hole 8.

In this embodiment, as shown in FIG.
Instead of the input transmission piston 40 used in the embodiment,
An input transmission lever 42 is provided. A link mechanism 8 from a change lever 9 (see FIG. 1) is connected to one end of the input transmission lever 42, and an input transmission pin 76 is fixed to the other end. The input transmission pin 76 penetrates through an inner diameter hole of a cylindrical member 79 fixed to one end side of the shift lever 4 and the valve spool 71 of the control valve 3.
a, 71b. The cylindrical member 79 extends radially inside the power piston 5 and engages with an inner diameter hole of a guide member 77 fixed inside the power piston 5. As shown in FIG. 10, the inner diameter hole of the guide member 77 is a long hole having a long diameter in a direction perpendicular to the stroke direction of the power piston 5. There is no play, and the outer diameter of the cylindrical member 79 and the gap are provided in the major axis direction.
Therefore, when the power piston 5 makes a stroke, the shift lever 4 moves the power piston 5 without loss of stroke.
Can be turned in accordance with the stroke of the user. The inner diameter hole of the cylindrical member is a stepped hole having a large diameter portion and a small diameter portion, and when the input transmission pin 76 moves relative to the cylindrical member 79 by a predetermined amount, the large diameter side of the input transmission pin 76 becomes the cylindrical member. The inner diameter hole 79 is in contact with the inside of the large diameter portion, and the inner surface of the large diameter portion of the inner diameter hole is the stopper surface of the input transmission pin 76 (see FIG. 11). Other configurations are
This is almost the same as the first embodiment.

Next, a speed change operation booster according to a third embodiment will be described with reference to FIG. Note that, in the present embodiment, description of contents common to the first embodiment will be omitted.

In this embodiment, unlike the first and second embodiments in which the speed change operation booster of the present invention is a spool valve type control valve, as shown in FIG. This is the case for valves. Other configurations are the same as those of the first embodiment.

A valve hole is formed in the power piston 5 'so as to extend therethrough along the axial direction. In the valve hole, valve seat members 92a, 92a constituting a part of the control valve 3' are formed.
The valve lifters 91a and 91b each having a two-step diameter with both ends formed to have small diameters are slidably supported while their large diameter portions are guided by the valve seat members 92a and 92b. I have. The valve lifters 91a, 91
“b” has the same shape, and is arranged to face each other such that the respective axes overlap each other. This concentricity need not be high precision.

As shown in FIG. 12, the valve lifter 91
The inside of the valve hole between a and 91b has a step shape,
Plates 73a and 73b are provided so as to abut this portion. The plates 73a and 73b are provided with holes larger than the small-diameter portions of the valve lifters 91a and 91b, respectively, and smaller than the large-diameter portions.
Valve lifters 91a and 91b are inserted into the holes from outside. With this insertion, the valve lifter 91
a, 91b are plates 73a, 73
abuts on the outer surface of b. Since the distance between the plates 73a and 73b is kept constant by the step shape in the valve hole, the valve gap is stabilized, and the performance of the valve is improved.

The valve lifters 91a and 91b are provided with exhaust holes 91c extending in the axial direction. This exhaust hole 9
1c is open to the exhaust chamber 21 provided at the position where the plates 73a and 73b are provided. Although the connection structure between the power piston 5 'and the shift lever 4' is not shown, it has the same structure as that of the first embodiment, and the exhaust chamber 21 includes a guide member 77 and a rod, similarly to the first embodiment. It communicates with the shift lever chamber through a gap with the portion 4a, and communicates with the atmosphere through an exhaust port formed in the shift lever chamber.

The end faces of the large diameter portions of the valve lifters 91a and 91b and the valve seats 92c facing outward in the axial direction of the valve seat members 92a and 92b come into contact with the springs 94a and 94b.
Is interposed. For this reason, the valve lifters 91a, 9
1b is pressed against the plates 73a, 73b by the urging force of the springs 94a, 94b.

When the valve lifters 91a and 91b move against the urging force of the springs 94a and 94b, the small diameter portions of the valve lifters 91a and 91b are moved to the valve seat members 92a and 92b.
It advances through the valve seat 92c of b.

The valve members 93a and 93b are
a, 92b are disposed in the inner diameter holes on the outside of the valve seat 92c, and the end faces of the valve seat 92c are formed by springs 95a, 95b.
Sitting in contact with Valve lifters 91a, 91b
When only the urging forces of the springs 94a and 94b are acting on the valve members 9a and 9b, the valve lifters 91a and 91b
3a, 93b (inactive neutral position). When the valve lifters 91a and 91b move in a direction against the urging force of the springs 94a and 94b, the valve lifters 91a and 91b move.
a, 91b press the valve members 93a, 93b, whereby the valve members 93a, 93b
The user moves in the direction opposing the biasing force of b and moves away. When the valve lifters 91a and 91b are returned to their original positions, the valve members 93a and 93b are similarly returned to their original positions and seated (non-operation neutral position). Thus, the valve lifters 91a, 91b
Operates the valve members 93a and 93b. Valve member 93
There is a gap between the outer surfaces of the valve members 93a and 93b and the inner surfaces of the valve seat members 92a and 92b, so that the valve members 93a and 93b move smoothly.

Valve lifters 91a and 91b, valve member 93
After inserting a and 93b, sealing is performed from both sides with plugs 75 'using a ring-shaped sheet member. This plug 75 '
Is fixed by a retaining ring 29, thereby preventing the plug 75 'from being pulled out. In addition, plug 75 '
Is formed in a concave shape for weight reduction.

As shown in FIG. 12, the valve member 93a,
An air chamber (A) 25a and an air chamber (B) 25b that communicate with a compressed air source via an air passage 24 (see FIG. 4) formed in the cylinder main body 10 are provided inside the power piston 5 'outside of the cylinder 93b. Are formed. Further, the same air passages 24a and 24b (see FIG. 4) as in the first and second embodiments are formed in the power piston 5 '. The air chamber (A) 25a can freely communicate with the pressure chamber (A) 11a via the air passage 24a, and the air chamber (B) 25b
Can communicate with the pressure chamber (B) 11b via the air passage 24b. That is, in this embodiment, as in the other embodiments, the pressure chamber (A) 11a and the pressure chamber (B) 1
The positions of 1b are staggered, and the pressure chamber (A) 1
1a is arranged on the side of the working pressure chamber (B) 26b, and the pressure chamber (B) is arranged on the side of the working pressure chamber (A) 26a.

Next, the operation of the speed change operation booster 1 will be described with reference to FIG. In the non-operating position shown in the figure, the control valve 3 'supplies air from the compressed air source to the air chamber (A) 25a and the air chamber (B) 25b of the power piston 5'. The pressure chamber (A) 11a and the pressure chamber (B) 11b of the power cylinder unit 2 '
It is open to the atmosphere through the exhaust holes 91c, the exhaust chamber 21, the shift lever chamber 23 (see FIG. 2), and the exhaust port 22 (see FIG. 2) of the valve lifters 91a and 91b. I have.

When the change lever 9 is operated and the input transmission piston 40 moves the valve lifter 91b rightward in FIG. 12 via the input transmission pin 76, first, the valve lifter 91b presses the valve member 93b. Then, the valve member 93b is moved rightward so as to be separated.
When the valve members 93a and 93b are separated from each other, the exhaust hole 91c of the valve lifter 91b is closed by the valve member 93b, so that the communication between the pressure chamber (B) 11b and the exhaust chamber 21 is cut off. On the other hand, the pressure chamber (B) 11b communicates with the air chamber (B) 25b via the air passage 24b (see FIG. 4), and the air supplied to the air chamber (B) 25b is supplied to the valve seat member 92b. Is introduced into the pressure chamber (B) 11b of the power cylinder portion 2 'through the space between the valve seat 92c and the valve member 93b. That is, the valve member 93b and the valve lifter 91b
Between the pressure chambers 11 of the power cylinder unit 2 ′.
The working pressure chamber communicates with a and 11b. Then, the air pressure tries to push the power piston 5 'to the left, but the cylinder body 10 of the power cylinder portion 2'
Is the transmission body T such that the axis of the power cylinder portion 2 'is tangential to the rotation of the shift lever 4 of the transmission T.
12B, the power piston 5 ′ moves rightward in FIG. 12 (the input transmission pin 76
In the same direction as the direction of movement).

At this time, the pressure chamber (A) 11a of the power cylinder portion 2 'has a small volume, but the air in the pressure chamber (A) 11a is released by the air passage 24a and the exhaust hole 9a.
1c, the exhaust chamber 21, the shift lever chamber 23 (see FIG. 2) and the exhaust port 22 (see FIG. 2) are exhausted to the atmosphere, so that no pressure is generated in the pressure chamber (A) 11a.
At this time, since the valve member 93a remains seated on the valve seat 92c of the valve seat member 92a, the air chamber (A) 2
The air supplied to 5a is not supplied to the pressure chamber (A) 11a.

The subsequent operation is the same as in the above-described embodiment. Even when the change lever 9 (see FIG. 1) is operated from the neutral position to move the valve lift 91a to the left via the input transmission piston 40, the same operation is performed as described above. As described above, the case where the one-valve, two-seat control valve is applied to the first embodiment has been described as the third embodiment, but the control valve can be similarly applied to the second embodiment.

In the first to third embodiments, a control valve for supplying and discharging compressed air to and from the two pressure chambers 11a and 11b is provided by a pair of spool valves of a pair coaxially opposed to each other. Although it is configured as a two-valve valve, the present invention is not limited to this, and may be configured as an integral spool valve or a one-valve two-seat configuration. In the first to third embodiments, air pressure is used. However, the present invention is not limited to this, and hydraulic pressure can be used.

[0065]

The transmission operation booster according to the present invention boosts the shift command operating force transmitted from the shift operation command operating means via the shift command operating force transmitting means, and shifts the shift lever of the transmission. A transmission operation booster for operating the power cylinder, a cylinder body of a power cylinder fixed to the transmission body,
Pistons slidably disposed in the cylinder body and defining pressure chambers at both end sides in the cylinder body, and provided in the pistons for supplying and discharging fluid pressure to and from the pressure chambers A control valve, input transmission means inserted radially into the piston to operate the control valve, and output transmission means inserted radially into the piston to transmit the output of the piston to the shift lever. Therefore, the size of the piston can be reduced both radially and axially.

When the input transmission means is provided in parallel with the cylinder body and has an input transmission piston connected to the speed change command operating force transmission means, the size of the piston in the radial direction can be further reduced. Can be planned.

When the input transmitting means has an input transmitting lever having one end connected to the shift command operating force transmitting means and the other end having an input transmitting member for operating the control valve, Since the structure can be simplified, the cost of the device can be reduced and the assemblability can be improved.

If the piston is provided with a guide member for the output transmission means, the operation of the output transmission means is guided by the guide member, so that a smoother operation of the apparatus can be ensured.

The control valve is a spool valve type control valve. A supply valve is provided on both outer sides of the spool valve for communicating and shutting off the pressure chamber and the compressed air source, and a pressure chamber is provided inside the spool valve. If it is configured to have an exhaust valve for communicating and shutting off the air with the atmosphere, the structure of the control valve, in particular, the entire structure can be simplified or simplified.

[Brief description of the drawings]

FIG. 1 is a schematic configuration diagram when a speed change operation booster of the present invention is mounted on a transmission.

FIG. 2 is a longitudinal sectional view showing a structure of a speed change operation booster according to the first embodiment of the present invention.

FIG. 3 is a sectional view taken along line III-III in FIG. 2;

FIG. 4 is a sectional view taken along line IV-IV in FIG. 2;

FIG. 5 is a sectional view taken along line VV in FIG. 3;

FIG. 6 is a sectional view taken along line VI-VI in FIG. 3;

FIG. 7 is a longitudinal sectional view showing a structure of a speed change operation booster according to a second embodiment of the present invention.

FIG. 8 is a sectional view taken along line VIII-VIII in FIG. 7;

FIG. 9 is a sectional view taken along line IX-IX in FIG. 7;

FIG. 10 is a sectional view taken along line XX of FIG. 7;

FIG. 11 is a sectional view taken along line XI-XI in FIG. 7;

FIG. 12 is a longitudinal sectional view illustrating a structure of a speed change operation booster according to a third embodiment of the present invention.

FIG. 13 is a longitudinal sectional view showing the structure of a conventional speed change operation booster.

14 is a longitudinal sectional view showing a structure of the speed change operation booster of FIG. 13 in a plane orthogonal to the section of the same figure.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Speed change operation booster 2, 2 'Power cylinder part 3, 3' Control valve 4 Shift lever 4a Rod member 5, 5 'Power piston 6 Upper case 7, 7' Operation part 8 Link mechanism 9 Change lever 10 Cylinder main body 10a Cylinder 11a Pressure chamber (A) 11b Pressure chamber (B) 12 Plug 13 Retaining ring 15a, 15b Bearing member 16 Rotating lever 17 Oscillating neutral axis 21 Exhaust chamber 22 Exhaust port 23 Shift lever chamber 24, 24a, 24b Air passage 25a Air chamber (A) 25b Air chamber (B) 26a Working pressure chamber (A) 26b Working pressure chamber (B) 27a Supply valve (A) 27b Supply valve (B) 28a Exhaust valve (A) 28b Exhaust valve (B) 29 Retaining ring 40 Input transmission piston 41 Sealing member 42 Input transmission lever 71a, 71b Valve spool 72a, 72b Valve sleeve 73a, 73b Plate 75, 75 'Plug 76 Input transmission pin 77 Guide member 78 Fixing pin 79 Cylindrical member 81a, 81b Valve lifter 81c Exhaust hole 82a, 82b Valve seat member 82c Valve seat 83a, 83b Valve member 84a, 84b, 85a , 85b Spring 86 Detent mechanism 91a, 91b Valve lifter 91c Exhaust hole 92a, 92b Valve seat member 92c Valve seat 93a, 93b Valve member 94a, 94b, 95a, 95b Spring T transmission Ta Shift shaft Tb Transmission body

Claims (5)

[Claims] A transmission operation booster for operating a shift lever of a transmission by boosting a shift command operation force transmitted from a shift operation command operation means via a shift command operation force transmission means. A cylinder body of a power cylinder fixed to the machine body, a piston slidably disposed within the cylinder body, and a pressure chamber at each end of the cylinder body that defines a pressure chamber; and a piston disposed within the piston. A control valve that supplies and discharges fluid pressure to and from the pressure chamber, an input transmission unit that is inserted into the piston from the radial direction to operate the control valve, and an output of the piston that is inserted into the piston from the radial direction and outputs the piston. And a power transmitting means for transmitting the power to the shift lever. 2. The transmission according to claim 1, wherein the input transmitting means has an input transmitting piston disposed in parallel with the cylinder body and connected to the shift command operating force transmitting means. Operation booster. 3. The input transmitting means has an input transmitting lever having one end connected to the speed change command operating force transmitting means and the other end having an input transmitting member for operating the control valve. 2. The transmission operating booster according to claim 1. 4. The transmission operating booster according to claim 1, wherein a guide member for the output transmission means is provided on the piston. 5. The control valve is a spool valve type control valve, a supply valve for communicating / cutting off the pressure chamber and a compressed air source on both outsides of the spool valve, and a supply valve on the inside of the spool valve. The transmission operating booster according to any one of claims 1 to 4, further comprising an exhaust valve that communicates and shuts off the pressure chamber and the atmosphere.