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CN104930142A - Multi-speed transmission - Google Patents

Multi-speed transmission Download PDF

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Publication number
CN104930142A
CN104930142A CN201510123428.XA CN201510123428A CN104930142A CN 104930142 A CN104930142 A CN 104930142A CN 201510123428 A CN201510123428 A CN 201510123428A CN 104930142 A CN104930142 A CN 104930142A
Authority
CN
China
Prior art keywords
component
gear
planet gear
gear train
torque
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
CN201510123428.XA
Other languages
Chinese (zh)
Other versions
CN104930142B (en
Inventor
J.M.哈特
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
GM Global Technology Operations LLC
Original Assignee
GM Global Technology Operations LLC
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from US14/640,798 external-priority patent/US9651118B2/en
Application filed by GM Global Technology Operations LLC filed Critical GM Global Technology Operations LLC
Publication of CN104930142A publication Critical patent/CN104930142A/en
Application granted granted Critical
Publication of CN104930142B publication Critical patent/CN104930142B/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/62—Gearings having three or more central gears
    • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/62—Gearings having three or more central gears
    • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
    • F16H3/663—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with conveying rotary motion between axially spaced orbital gears, e.g. RAVIGNEAUX
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H2003/442—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion comprising two or more sets of orbital gears arranged in a single plane
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0069—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising ten forward speeds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/201—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with three sets of orbital gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/2012—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with four sets of orbital gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/202—Transmissions using gears with orbital motion characterised by the type of Ravigneaux set
    • F16H2200/2023—Transmissions using gears with orbital motion characterised by the type of Ravigneaux set using a Ravigneaux set with 4 connections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2046—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with six engaging means

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)
  • Retarders (AREA)

Abstract

A transmission is provided having an input member, an output member, at least three planetary gear sets, a plurality of coupling members and a plurality of torque transmitting devices. The torque transmitting devices include clutches and brakes actuatable in combinations of three to establish a plurality of forward gear ratios and at least one reverse gear ratio.

Description

Multi-speed transmission
The cross reference of related application
This application claims the rights and interests of the U.S. Provisional Application No. 61/968,156 submitted on March 20th, 2014.The disclosure of above-mentioned application is by reference to being contained in herein.
Technical field
The present invention relates in general to a kind of multi-speed transmission, and relates more specifically to a kind of speed changer with multiple speed, three or four planetary gear set and multiple torque-transmitting mechanisms.
Background technique
The content of this part only provides the background information relevant with the disclosure, and may form or may not form prior art.
Typical multi-speed transmission uses friction clutch, planetary pinion to arrange and the combination of fixed interconnection realizes multiple velocity ratio.The quantity of planetary gear set and physical layout are usually by packaging, cost and desired speed ratio regulation.
Although current variator realizes its expection object, but to transmission configuration that is new-type and that improve to need be in fact continual, described transmission configuration represents the performance (especially from the angle of efficiency, responsiveness and flatness) of improvement and the packaging (size mainly reduced and weight) of improvement.Therefore, that improve, that cost is effective, compact multi-speed transmission is needed.
Summary of the invention
Be provided for the speed changer of motor vehicle.This speed changer comprises: input link; Output link; There is the first planet gear train of first, second, third and fourth component; There is the second planetary gear set of first, second, and third component; There is the third planet gear train of first, second, and third component; First interconnecting component, described first interconnecting component is directly connected to the second component of described first planet gear train and the second component of described second planetary gear set; Second interconnecting component, described second interconnecting component is directly connected to the first component of described second planetary gear set and the second component of described third planet gear train; And six torque-transmitting mechanisms, described torque-transmitting mechanisms optionally can engage to be connected with other components in described first, second, third and fourth component and fixed component by each component in the first, second, third and fourth component of described first, second, and third planetary gear set.Described six torque-transmitting mechanisms with the combined engagement of at least three to set up at least ten forward gear ratio and a reverse gear ratio between described input link and described output link.
In one aspect of the invention, first in described six torque-transmitting mechanisms optionally can engage to be connected with the first component of described third planet gear train by the 3rd component of described first planet gear train.
In another aspect of this invention, second in described six torque-transmitting mechanisms optionally can engage to be connected with the 3rd component of described third planet gear train by the 3rd component of described first planet gear train.
In another aspect of this invention, the 3rd in described six torque-transmitting mechanisms optionally can engage to be connected with the 3rd component of described third planet gear train by the 4th component of described first planet gear train.
In another aspect of this invention, the 4th in described six torque-transmitting mechanisms optionally can engage to be connected with the 3rd component of described third planet gear train by the 3rd component of described second planetary gear set.
In another aspect of this invention, the 5th in described six torque-transmitting mechanisms optionally can engage to be connected with described fixed component by the first component of described first planet gear train.
In another aspect of this invention, the 6th in described six torque-transmitting mechanisms optionally can engage to be connected with described fixed component by the first component of described third planet gear train.
In another aspect of this invention, the second component of the described input link second component and described second planetary gear set that are connected to described first planet gear train is jointly to rotate.
In another aspect of this invention, the second component of described output link the first component and described third planet gear train that are connected to described second planetary gear set is jointly to rotate.
In another aspect of this invention, first component of described first planet gear train is sun gear component, the second component of described first planet gear train is gear member, 3rd component of described first planet gear train is frame, 4th component of described first planet gear train is gear ring and sun gear component, described second and the first component of third planet gear train be gear member, described second and the second component of third planet gear train be frame, described second and the 3rd component of third planet gear train be sun gear component.
In another aspect of this invention, described first planet gear train is stacking planetary gear set, this stacking planetary gear set has and supports so that first group and two groups of epicyclic gears rotating by frame, and wherein, described first group of planetary pinion and described sun gear component and described gear ring and sun gear component engage, and described two groups of epicyclic gears and described gear ring and sun gear component and described gear member engage.
In another aspect of this invention, first component of described first planet gear train is the first sun gear component, the second component of described first planet gear train is frame, 3rd component of described first planet gear train is gear member, 4th component of described first planet gear train is secondary sun wheel component, described second and the first component of third planet gear train be gear member, described second and the second component of third planet gear train be frame, described second and the 3rd component of third planet gear train be sun gear component.
In another aspect of this invention, described first planet gear train comprises the group leader's planetary pinion and one group of shor planet gear that support by described frame, and wherein, described long planet gear all engages with described first sun gear component, described gear member and described shor planet gear, and wherein, described shor planet gear all engages with described long planet gear and described secondary sun wheel component.
In another aspect of this invention, described first planet gear train comprises and all has one of major diameter part and small diameter portion and to organize a performance scalariform planetary pinion and comprise one group of non-step-like planetary pinion, wherein, each step-like planetary pinion engages with described first sun gear component in described large-diameter portion office and eachly to engage with described gear member and described non-step-like planetary pinion in described minor diameter office, and wherein, each non-step-like planetary pinion engages with described step-like planetary pinion and described secondary sun wheel component.
In another aspect of this invention, described first planet gear train comprises the group leader's planetary pinion and one group of shor planet gear that support by described frame, and wherein, described long planet gear all engages with described secondary sun wheel component and described shor planet gear, and wherein, described shor planet gear all engages with described long planet gear, described first sun gear component and described gear member.
The present invention also provides following scheme:
1., for a speed changer for motor vehicle, comprising:
Input link;
Output link;
There is the first planet gear train of the first component, second component, the 3rd component and the 4th component;
There is the second planetary gear set of the first component, second component and the 3rd component;
There is the third planet gear train of the first component, second component and the 3rd component;
First interconnecting component, described first interconnecting component is directly connected to the second component of described first planet gear train and the second component of described second planetary gear set;
Second interconnecting component, described second interconnecting component is directly connected to the first component of described second planetary gear set and the second component of described third planet gear train; And
Six torque-transmitting mechanisms, described torque-transmitting mechanisms optionally can engage the first component of described first planet gear train, the second planetary gear set and third planet gear train, second component, the 3rd component to be connected with other components in described first, second, third and fourth component and fixed component with each component in the 4th component; And
Wherein, described six torque-transmitting mechanisms with the combined engagement of at least three to set up at least ten forward gear ratio and at least one reverse gear ratio between described input link and described output link.
2. the speed changer according to scheme 1, is characterized in that, first in described six torque-transmitting mechanisms optionally can engage to be connected with the first component of described third planet gear train by the 3rd component of described first planet gear train.
3. the speed changer according to scheme 2, is characterized in that, second in described six torque-transmitting mechanisms optionally can engage to be connected with the 3rd component of described third planet gear train by the 3rd component of described first planet gear train.
4. the speed changer according to scheme 3, is characterized in that, the 3rd in described six torque-transmitting mechanisms optionally can engage to be connected with the 3rd component of described third planet gear train by the 4th component of described first planet gear train.
5. the speed changer according to scheme 4, is characterized in that, the 4th in described six torque-transmitting mechanisms optionally can engage to be connected with the 3rd component of described third planet gear train by the 3rd component of described second planetary gear set.
6. the speed changer according to scheme 5, is characterized in that, the 5th in described six torque-transmitting mechanisms optionally can engage to be connected with described fixed component by the first component of described first planet gear train.
7. the speed changer according to scheme 6, is characterized in that, the 6th in described six torque-transmitting mechanisms optionally can engage to be connected with described fixed component by the first component of described third planet gear train.
8. the speed changer according to scheme 1, is characterized in that, the second component of second component and described second planetary gear set that described input link is connected to described first planet gear train is jointly to rotate.
9. the speed changer according to scheme 1, is characterized in that, the second component of the first component and described third planet gear train that described output link is connected to described second planetary gear set is jointly to rotate.
10. the speed changer according to scheme 1, it is characterized in that, first component of described first planet gear train is sun gear component, the second component of described first planet gear train is gear member, 3rd component of described first planet gear train is frame, 4th component of described first planet gear train is gear ring and sun gear component, first component of described second planetary gear set and third planet gear train is gear member, the second component of described second planetary gear set and third planet gear train is frame, 3rd component of described second planetary gear set and third planet gear train is sun gear component.
11. speed changers according to scheme 10, it is characterized in that, described first planet gear train is stacking planetary gear set, described stacking planetary gear set has and supports so that the first group of planetary pinion rotated and two groups of epicyclic gears by frame, and wherein, described first group of planetary pinion and described sun gear component and described gear ring and sun gear component engage, and described two groups of epicyclic gears and described gear ring and sun gear component and described gear member engage.
12. speed changers according to scheme 1, it is characterized in that, first component of described first planet gear train is the first sun gear component, the second component of described first planet gear train is frame, 3rd component of described first planet gear train is gear member, 4th component of described first planet gear train is secondary sun wheel component, first component of described second planetary gear set and third planet gear train is gear member, the second component of described second planetary gear set and third planet gear train is frame, 3rd component of described second planetary gear set and third planet gear train is sun gear component.
13. speed changers according to scheme 12, it is characterized in that, described first planet gear train comprises the group leader's planetary pinion and one group of shor planet gear that support by described frame, and wherein, described long planet gear all engages with described first sun gear component, described gear member and described shor planet gear, and wherein, described shor planet gear all engages with described long planet gear and described secondary sun wheel component.
14. speed changers according to scheme 12, it is characterized in that, described first planet gear train comprises and all has one of major diameter part and small diameter portion and to organize a performance scalariform planetary pinion and comprise one group of non-step-like planetary pinion, wherein, each step-like planetary pinion engages with described first sun gear component in described large-diameter portion office and eachly to engage with described gear member and described non-step-like planetary pinion in described minor diameter office, and wherein, each non-step-like planetary pinion engages with described step-like planetary pinion and described secondary sun wheel component.
15. speed changers according to scheme 12, it is characterized in that, described first planet gear train comprises the group leader's planetary pinion and one group of shor planet gear that support by described frame, and wherein, described long planet gear all engages with described secondary sun wheel component and described shor planet gear, and wherein, described shor planet gear all engages with described long planet gear, described first sun gear component and described gear member.
16. 1 kinds, for the speed changer of motor vehicle, comprising:
Input link;
Output link;
There is the first planet gear train of the first component, second component, the 3rd component and the 4th component;
There is the second planetary gear set of the first component, second component and the 3rd component;
There is the third planet gear train of the first component, second component and the 3rd component;
First torque-transmitting mechanisms, it optionally can engage the first component the 3rd component of described first planet gear train to be connected to described third planet gear train;
Second torque-transmitting mechanisms, it optionally can engage the 3rd component the 3rd component of described first planet gear train to be connected to described third planet gear train;
3rd torque-transmitting mechanisms, it optionally can engage the 3rd component the 4th component of described first planet gear train to be connected to described third planet gear train;
4th torque-transmitting mechanisms, it optionally can engage the 3rd component the 3rd component of described second planetary gear set to be connected to described third planet gear train;
5th torque-transmitting mechanisms, it optionally can engage that the first component of described first planet gear train is connected to fixed component; And
6th torque-transmitting mechanisms, it optionally can engage that the first component of described third planet gear train is connected to described fixed component; And
Wherein, described six torque-transmitting mechanisms with the combined engagement of at least three to set up at least ten forward gear ratio and at least one reverse gear ratio between described input link and described output link.
17. speed changers according to scheme 16, is characterized in that, also comprise:
First interconnecting component, described first interconnecting component is directly connected to the second component of described first planet gear train and the second component of described second planetary gear set; And
Second interconnecting component, described second interconnecting component is directly connected to the first component of described second planetary gear set and the second component of described third planet gear train.
18. speed changers according to scheme 17, it is characterized in that, the second component of second component and described second planetary gear set that described input link is connected to described first planet gear train is jointly to rotate, and wherein, the second component of the first component and described third planet gear train that described output link is connected to described second planetary gear set is jointly to rotate.
19. speed changers according to scheme 18, it is characterized in that, first component of described first planet gear train is sun gear component, the second component of described first planet gear train is gear member, 3rd component of described first planet gear train is frame, 4th component of described first planet gear train is gear ring and sun gear component, first component of described second planetary gear set and third planet gear train is gear member, the second component of described second planetary gear set and third planet gear train is frame, sun gear component with the 3rd component of described second planetary gear set and third planet gear train.
20. speed changers according to scheme 18, it is characterized in that, first component of described first planet gear train is the first sun gear component, the second component of described first planet gear train is frame, 3rd component of described first planet gear train is gear member, 4th component of described first planet gear train is secondary sun wheel component, first component of described second planetary gear set and third planet gear train is gear member, the second component of described second planetary gear set and third planet gear train is frame, 3rd component of described second planetary gear set and third planet gear train is sun gear component.
Further feature of the present invention, aspect and benefit will be apparent by reference to aftermentioned explanation and accompanying drawing, and in the accompanying drawings, identical reference character represents identical parts, element or feature.
Illustrative in nature of the present invention is only exemplary, and the modification not departing from essence of the present invention is intended to comprise within the scope of the invention.This modification is not considered to depart from the spirit and scope of the present invention.
Accompanying drawing explanation
The object of accompanying drawing as herein described only for illustrating, and be not meant to and limit the scope of the present disclosure by any way.
Fig. 1 is the lever diagram of speed changer in accordance with the principles of the present invention;
Fig. 2 is the schematic diagram of the embodiment of the speed changer of Fig. 1 in accordance with the principles of the present invention;
Fig. 3 is the schematic diagram of another embodiment of the speed changer of Fig. 1 in accordance with the principles of the present invention;
Fig. 4 is the schematic diagram of the another embodiment of the speed changer of Fig. 1 in accordance with the principles of the present invention;
Fig. 5 is the schematic diagram of the another embodiment of the speed changer of Fig. 1 in accordance with the principles of the present invention;
Fig. 6 is the schematic diagram of the another embodiment of the speed changer of Fig. 1 in accordance with the principles of the present invention; And
Fig. 7 is truth table, and it illustrates that the example of the jointing state of each torque delivery element is to produce multiple advance of the speed changer shown in Fig. 1-6 and at least one reverse speed or velocity ratio.
Embodiment
The following description is only exemplary in essence, and is not intended to limit the disclosure, application or uses.
Refer now to Fig. 1, show the embodiment of multi-speed transmission 10 with the form of lever diagram.Lever diagram is the schematic diagram of the parts of the mechanical device of such as automatic transmission.Each independently lever represents planetary gear set, and wherein planetary three basic mechanical parts represent by node.Thus, single lever comprises three nodes: one for sun gear, one for planetary carrier, one for gear ring.In some cases, two levers can be combined into the single lever had more than three nodes (usual four nodes).Such as, if two nodes on two different levers are interconnected by fixed connecting piece, so they can be expressed as the individual node on single lever.Relative length between the node of each lever may be used for the gear ring-sun gear ratio representing each respective teeth wheels.Then, these lever ratios are for changing the velocity ratio of speed changer to realize suitable ratio and to compare progression.Mechanical links between the node of each planetary gear set or cross tie part are represented by thin horizontal line, and torque transmitting device (such as clutch and break) is expressed as the finger-type thing of intertexture.The further elaboration of the form of lever diagram, object and use is found in the SAE Paper 810102 " The Lever Analogy:A New Tool in Transmission Analysis " of Benford and Leising, and the document is in this as with reference to all introducing.
Multi-speed transmission 10 comprises input shaft or component 12, first gear unit assembly 14, second gear unit assembly 16, the 3rd gear unit assembly 18 and output shaft or component 20.In the lever diagram of Fig. 1, the first gear unit assembly 14 has four nodes: first node 14A, Section Point 14B, the 3rd node 14C and the 4th node 14D.Second gear unit assembly 16 has three nodes: first node 16A, Section Point 16B and the 3rd node 16C.3rd gear unit assembly 18 has three nodes: first node 18A, Section Point 18B and the 3rd node 18C.Input link 12 is connected to the Section Point 14B of the first gear unit assembly 14 and Section Point 16B of the second gear unit assembly 16 constantly.Output link 20 is connected to the Section Point 18B of the 3rd the gear unit assembly 18 and first node 16A of the second gear unit assembly 16 constantly.
3rd node 14C of the first gear unit assembly 14 is optionally connected to the first node 18A of the 3rd gear unit assembly 18 by first clutch 22.3rd node 14C of the first gear unit assembly 14 is optionally connected to the 3rd node 18C of the 3rd gear unit assembly 18 by second clutch 24.4th node 14D of the first gear unit assembly 14 is optionally connected to the 3rd node 18C of the 3rd gear unit assembly 18 by the 3rd clutch 26.3rd node 16C of the second gear unit assembly 16 is optionally connected to the 3rd node 18C of the 3rd gear unit assembly 18 by four clutches 28.The first node 14A of the first gear unit assembly 14 is optionally connected to fixed component or element 31, such as case of transmission by the first break 30, to limit the rotation of the first node 14A of the first gear unit assembly 14.The first node 18A of the 3rd gear unit assembly 18 is optionally connected to fixed component 31 by second brake 32, to limit the rotation of the first node 18A of the 3rd gear unit assembly 18.
Refer now to Fig. 2, stick plot represents the schematic layout of the embodiment of multi-speed transmission 10 in accordance with the principles of the present invention.In fig. 2, the reference character of the lever diagram of Fig. 1 continues to be suitable for.Clutch and coupling are correspondingly illustrated, and the node of gear unit assembly is now revealed as the parts of planetary gear set, such as sun gear, gear ring, planetary pinion and planetary carrier.
Such as, the first gear unit assembly 14 is constructed to radially stacked planetary gear set, and it has the sun gear component 14A of whole radially aligned, planetary pinion frame 14C, gear member 14B and sun gear/gear ring common gear component 14D.Common gear component 14D has wheel tooth (formation gear ring) on an internal surface and wheel tooth on the outer surface (formation sun gear).Frame 14C rotatably supports in first group of planetary pinion or small gear 14E(figure and only one of them is shown) and two groups of epicyclic gears or small gear 14F(figure in only one of them is shown).First group of planetary pinion 14E is all configured to intermesh with gear member 14B and common gear component 14D.Two groups of epicyclic gears 14F is all configured to intermesh with common gear component 14D and sun gear component 14A.Sun gear component 14A is connected jointly to rotate with the first axle or interconnecting component 34.Planetary carrier 14C is connected jointly to rotate with the second axle or interconnecting component 36.Common gear component 14D is connected jointly to rotate with the 3rd axle or interconnecting component 38.Gear ring 14B is connected jointly to rotate with input (in) axle or component 12.
Second gear unit assembly 16 comprises sun gear component 16C, planetary pinion frame 16B and gear member 16A.Planetary pinion frame 16B rotatably supports in one group of planetary pinion or small gear 16D(figure and only one of them is shown).Planetary pinion 16D is all configured to intermesh with sun gear component 16C and gear member 16A.Sun gear component 16C is connected jointly to rotate with the 4th axle or interconnecting component 40.Frame 16B is connected jointly to rotate with input shaft or component 12.Gear member 16A is connected jointly to rotate with output (out) axle or component 20.
3rd gear unit assembly 18 comprises sun gear component 18C, planetary pinion frame 18B and gear member 18A.Planetary pinion frame 18B rotatably supports in one group of planetary pinion or small gear 18D(figure and only one of them is shown).Planetary pinion 18D is all configured to intermesh with sun gear component 18C and gear member 18A.Sun gear component 18C is connected jointly to rotate with the 5th axle or interconnecting component 42.Frame 18B is connected jointly to rotate with output shaft or component 20.Gear member 18A is connected jointly to rotate with the 6th axle or interconnecting component 44.
Input shaft or component 12 are connected to input source constantly, the turbine (not shown) of such as motor (not shown) or torque converter.Output shaft or component 20 export with the such as motor vehicle of final driver element or transmission case (not shown) and are connected constantly.
The torque-transmitting mechanisms comprising first, second, third and fourth clutch 22,24,26,28 and first and second break 30,32 allow axle or interconnecting component 34,36,38,40,42,44 and other axles or interconnecting component 34,36,38,40,42,44, the component of planetary gear set 14,16,18 or the selectivity of fixed component or case of transmission 31 interconnect.Such as, first clutch 22 optionally can engage that the second interconnecting component 36 is connected to the 6th interconnecting component 44.Second clutch 24 optionally can engage that the second interconnecting component 36 is connected to the 5th interconnecting component 42.3rd clutch 26 optionally can engage that the 3rd interconnecting component 38 is connected to the 5th interconnecting component 42.Four clutches 28 optionally can engage that the 4th interconnecting component 40 is connected to the 5th interconnecting component 42.First break 30 optionally can engage that the first interconnecting component 34 is connected to fixed component or case of transmission 31, rotates relative to housing 31 to limit sun gear component 14A.Second brake 32 optionally can engage that the 6th interconnecting component 44 is connected to fixed component or case of transmission 31, to limit the rotation of gear member 18A.
Refer now to Fig. 3, stick plot represents the schematic layout of another embodiment of multi-speed transmission 100 in accordance with the principles of the present invention.In figure 3, the reference character of the figure of Fig. 1 and 2 continues to be suitable for.Clutch and coupling are correspondingly illustrated, and gear unit assembly 14,16 with 18 node can correspond to the parts different from those parts shown in Fig. 2 of planetary gear set now.
Such as, the first gear unit assembly 14 is constructed to Ravigneaux (ravigneaux) planetary gear set, and it has the first sun gear component 11A, secondary sun wheel component 14D, planetary pinion frame 14B and gear member 14C.Frame 14B rotatably supports in group leader's planetary pinion or small gear 14E(figure and only one of them is shown) and one group of shor planet gear or small gear 14F(figure in only one of them is shown).This group leader's planetary pinion 14E is all configured to intermesh with gear member 14C, sun gear component 14A and shor planet gear 14F.This group shor planet gear 14F is all configured to intermesh with sun gear component 14D and long planet gear 14E.Sun gear component 14A is connected to the first axle or interconnecting component 34 jointly to rotate.Gear member 14C is connected to the second axle or interconnecting component 36 jointly to rotate.Sun gear component 14D is connected to the 3rd axle or interconnecting component 38 jointly to rotate.Frame 14B is connected to input shaft or component 12 jointly to rotate.
Second gear unit assembly 16 comprises sun gear component 16C, planetary pinion frame 16B and gear member 16A.Planetary pinion frame 16B rotatably supports in one group of planetary pinion or small gear 16D(figure and only one of them is shown).Planetary pinion 16D is all configured to intermesh with sun gear component 16C and gear member 16A.Sun gear component 16C is connected jointly to rotate with the 4th axle or interconnecting component 40.Frame 16B is connected jointly to rotate with input shaft or component 12.Gear member 16A is connected jointly to rotate with output shaft or component 20.
3rd gear unit assembly 18 comprises sun gear component 18C, planetary pinion frame 18B and gear member 18A.Planetary pinion frame 18B rotatably supports in one group of planetary pinion or small gear 18D(figure and only one of them is shown).Planetary pinion 18D is all configured to intermesh with sun gear component 18C and gear member 18A.Sun gear component 18C is connected jointly to rotate with the 5th axle or interconnecting component 42.Frame 18B is connected jointly to rotate with output shaft or component 20.Gear member 18A is connected jointly to rotate with the 6th axle or interconnecting component 44.
Input shaft or component 12 are connected to input source constantly, the turbine (not shown) of such as motor (not shown) or torque converter.Output shaft or component 20 export with the such as motor vehicle of final driver element or transmission case (not shown) and are connected constantly.
The torque-transmitting mechanisms comprising first, second, third and fourth clutch 22,24,26,28 and first and second break 30,32 allow axle or interconnecting component 34,36,38,40,42,44 and other axles or interconnecting component 34,36,38,40,42,44, the component of planetary gear set 14,16,18 or the selectivity of fixed component or case of transmission 31 interconnect.Such as, first clutch 22 optionally can engage that the second interconnecting component 36 is connected to the 6th interconnecting component 44.Second clutch 24 optionally can engage that the second interconnecting component 36 is connected to the 5th interconnecting component 42.3rd clutch 26 optionally can engage that the 3rd interconnecting component 38 is connected to the 5th interconnecting component 42.Four clutches 28 optionally can engage that the 4th interconnecting component 40 is connected to the 5th interconnecting component 42.First break 30 optionally can engage that the first interconnecting component 34 is connected to fixed component or case of transmission 31, rotates relative to housing 31 to limit sun gear component 14A.Second brake 32 optionally can engage that the 6th interconnecting component 44 is connected to fixed component or case of transmission 31, to limit the rotation of gear member 18A.
Refer now to Fig. 4, stick plot represents the schematic layout of another embodiment of multi-speed transmission 200 in accordance with the principles of the present invention.In the diagram, the reference character of the diagram of Fig. 1 and 3 continues to be suitable for.But in speed changer 200, planetary pinion or small gear 14E are constructed to the step-like small gear 201 with major diameter part 202 and small diameter portion 204.Major diameter part 202 and the sun gear component 14A of each step-like planetary pinion 201 intermesh.Small diameter portion 204 and the gear member 14C and planetary pinion 14F of each step-like planetary pinion 201 intermesh.Planetary pinion 14F all intermeshes with step-like planetary pinion 201 and sun gear component 14D.
Refer now to Fig. 5, stick plot represents the schematic layout of another embodiment of multi-speed transmission 300 in accordance with the principles of the present invention.In Figure 5, the reference character of the diagram of Fig. 1 and 3 continues to be suitable for.But in speed changer 300, long planet gear or small gear 14E are configured to shor planet gear or small gear 302, and shor planet gear or small gear 14F are configured to long planet gear or small gear 304.Shor planet gear 302 all intermeshes with sun gear component 14A, gear member 14C and long planet gear 304.Long planet gear or small gear 304 all intermesh with shor planet gear 302 and sun gear component 14D.
Refer now to Fig. 6, stick plot represents the schematic layout of the embodiment of multi-speed transmission 400 in accordance with the principles of the present invention.In figure 6, the reference character of the lever diagram of Fig. 1 continues to be suitable for.Clutch and coupling are correspondingly illustrated, and the node of gear unit assembly is now revealed as the parts of planetary gear set, such as sun gear, gear ring, planetary pinion and planetary carrier.
Such as, the first gear unit assembly 14 is constructed to two the independent planetary gear trains comprising first planet gear train 402 and the second planetary gear set 404.Therefore, multiple parts of some both node on behalf first and second planetary gear set 402,404 in the first gear unit assembly 14.Such as, first planet gear train 402 comprises sun gear component 402A, planetary pinion frame 402B and gear member 402C.Frame 402B rotatably supports in one group of planetary pinion or small gear 402D(figure and only one of them is shown).Each planetary pinion 402D and sun gear component 402A and gear member 402C intermeshes.Second planetary gear set 404 comprises sun gear component 404A, planetary pinion frame 404B and gear member 404C.Frame 404B rotatably supports in one group of planetary pinion or small gear 404D(figure and only one of them is shown).Each planetary pinion 404D and sun gear component 404A and gear member 404C intermeshes.Therefore, the first node 14A of the first gear unit assembly 14 represents sun gear component 402A.The Section Point 14B of the first gear unit assembly 14 represents frame 402B and gear ring 404C.3rd node 14C of the first gear unit assembly represents gear member 402C and frame 404B.4th node 14D of the first gear unit assembly 14 represents sun gear component 404A.
Sun gear component 402A is connected to the first axle or interconnecting component 434 jointly to rotate.Planetary carrier 402B is connected to input shaft or component 12 jointly to rotate.Gear member 402C is connected to the second axle or interconnecting component 436 jointly to rotate.
Sun gear component 404A is connected to the 3rd axle or interconnecting component 438 jointly to rotate.Frame 404B is connected to the second axle or interconnecting component 436 jointly to rotate.Gear member 404C is connected to input shaft or component 12 jointly to rotate.
Second gear unit assembly 16 comprises sun gear component 16C, planetary pinion frame 16B and gear member 16A.Planetary pinion frame 16B rotatably supports in one group of planetary pinion or small gear 16D(figure and only one of them is shown).Planetary pinion 16D is all configured to intermesh with sun gear component 16C and gear member 16A.Sun gear component 16C is connected jointly to rotate with the 4th axle or interconnecting component 440.Frame 16B is connected jointly to rotate with input shaft or component 12.Gear member 16A is connected jointly to rotate with output shaft or component 20.
3rd gear unit assembly 18 comprises sun gear component 18C, planetary pinion frame 18B and gear member 18A.Planetary pinion frame 18B rotatably supports in one group of planetary pinion or small gear 18D(figure and only one of them is shown).Planetary pinion 18D is all configured to intermesh with sun gear component 18C and gear member 18A.Sun gear component 18C is connected jointly to rotate with the 5th axle or interconnecting component 442.Frame 18B is connected jointly to rotate with output shaft or component 20.Gear member 18A is connected jointly to rotate with the 6th axle or interconnecting component 444.
Input shaft or component 12 are connected to input source constantly, the turbine (not shown) of such as motor (not shown) or torque converter.Output shaft or component 20 export with the such as motor vehicle of final driver element or transmission case (not shown) and are connected constantly.
The torque-transmitting mechanisms comprising first, second, third and fourth clutch 22,24,26,28 and first and second break 30,32 allow axle or interconnecting component 434,436,438,440,442,444 and other axles or interconnecting component 434,436,438,440,442,444, the component of gear unit assembly 14,16,18 or the selectivity of fixed component or case of transmission 31 interconnect.Such as, first clutch 22 optionally can engage that the second interconnecting component 436 is connected to the 6th interconnecting component 444.Second clutch 24 optionally can engage that the second interconnecting component 436 is connected to the 5th interconnecting component 442.3rd clutch 26 optionally can engage that the 3rd interconnecting component 438 is connected to the 5th interconnecting component 442.Four clutches 28 optionally can engage that the 4th interconnecting component 440 is connected to the 5th interconnecting component 442.First break 30 optionally can engage that the first interconnecting component 434 is connected to fixed component or case of transmission 31, rotates relative to housing 31 to limit sun gear component 402A.Second brake 32 optionally can engage that the 6th interconnecting component 444 is connected to fixed component or case of transmission 31, to limit the rotation of gear member 18A.
Refer now to Fig. 7 and continue with reference to figure 2-6, will the operation of multi-speed transmission 10,100,200,300,400 be described.Will be appreciated that moment of torsion can be delivered to output shaft or component 20 with multiple forward velocity or torque ratio and at least one reverse speed or torque ratio from input shaft or component 12 by speed changer.Each advance and reverse speed or torque ratio by torque-transmitting mechanisms (namely, the first break 30, second brake 32, first clutch 22, second clutch 24, the 3rd clutch 26, four clutches 28) in one or more joints realize, hereafter will be described.
Fig. 7 is truth table, it illustrates the various combinations of the torque-transmitting mechanisms being reinstated or engage to realize each range state." X " in frame refers to that concrete clutch or break are engaged to realize expecting range state.Also show the actual numerical value velocity ratio of each range state, but should be understood that these numerical value are only exemplary and they can carry out regulating with the various application of applicable speed changer and operation standard in broad range.Certainly, depend on selected gear diameter, the gear number of teeth and gear configurations, also can realize other velocity ratios.
Such as, reverse gear is set up by engaging or reinstate second brake 32, the 3rd clutch 26 and first clutch 22.Similarly, the various combination engaged by clutch and break realizes ten forward velocity ratios or velocity ratio, such as shown in Figure 7.Fig. 7 also show multiple clutch for realizing fourth speed position and seventh speed position and break engages option.
Should be understood that, axle or interconnecting component 12,20,34,36,38,40,42,44,434,436,438,440,442 and 444 can be all single integrated support structure or the rotating parts that all can comprise multiple interconnection, and do not depart from the scope of the present invention.

Claims (10)

1., for a speed changer for motor vehicle, comprising:
Input link;
Output link;
There is the first planet gear train of the first component, second component, the 3rd component and the 4th component;
There is the second planetary gear set of the first component, second component and the 3rd component;
There is the third planet gear train of the first component, second component and the 3rd component;
First interconnecting component, described first interconnecting component is directly connected to the second component of described first planet gear train and the second component of described second planetary gear set;
Second interconnecting component, described second interconnecting component is directly connected to the first component of described second planetary gear set and the second component of described third planet gear train; And
Six torque-transmitting mechanisms, described six torque-transmitting mechanisms optionally can engage the first component of described first planet gear train, the second planetary gear set and third planet gear train, second component, the 3rd component to be connected with other components in described first, second, third and fourth component and fixed component with each component in the 4th component; And
Wherein, described six torque-transmitting mechanisms with the combined engagement of at least three to set up at least ten forward gear ratio and at least one reverse gear ratio between described input link and described output link.
2. speed changer according to claim 1, is characterized in that, first in described six torque-transmitting mechanisms optionally can engage to be connected with the first component of described third planet gear train by the 3rd component of described first planet gear train.
3. speed changer according to claim 2, is characterized in that, second in described six torque-transmitting mechanisms optionally can engage to be connected with the 3rd component of described third planet gear train by the 3rd component of described first planet gear train.
4. speed changer according to claim 3, is characterized in that, the 3rd in described six torque-transmitting mechanisms optionally can engage to be connected with the 3rd component of described third planet gear train by the 4th component of described first planet gear train.
5. speed changer according to claim 4, is characterized in that, the 4th in described six torque-transmitting mechanisms optionally can engage to be connected with the 3rd component of described third planet gear train by the 3rd component of described second planetary gear set.
6. speed changer according to claim 5, is characterized in that, the 5th in described six torque-transmitting mechanisms optionally can engage to be connected with described fixed component by the first component of described first planet gear train.
7. speed changer according to claim 6, is characterized in that, the 6th in described six torque-transmitting mechanisms optionally can engage to be connected with described fixed component by the first component of described third planet gear train.
8. speed changer according to claim 1, is characterized in that, the second component of second component and described second planetary gear set that described input link is connected to described first planet gear train is jointly to rotate.
9. speed changer according to claim 1, is characterized in that, the second component of the first component and described third planet gear train that described output link is connected to described second planetary gear set is jointly to rotate.
10., for a speed changer for motor vehicle, comprising:
Input link;
Output link;
There is the first planet gear train of the first component, second component, the 3rd component and the 4th component;
There is the second planetary gear set of the first component, second component and the 3rd component;
There is the third planet gear train of the first component, second component and the 3rd component;
First torque-transmitting mechanisms, it optionally can engage the first component the 3rd component of described first planet gear train to be connected to described third planet gear train;
Second torque-transmitting mechanisms, it optionally can engage the 3rd component the 3rd component of described first planet gear train to be connected to described third planet gear train;
3rd torque-transmitting mechanisms, it optionally can engage the 3rd component the 4th component of described first planet gear train to be connected to described third planet gear train;
4th torque-transmitting mechanisms, it optionally can engage the 3rd component the 3rd component of described second planetary gear set to be connected to described third planet gear train;
5th torque-transmitting mechanisms, it optionally can engage that the first component of described first planet gear train is connected to fixed component; And
6th torque-transmitting mechanisms, it optionally can engage that the first component of described third planet gear train is connected to described fixed component; And
Wherein, described six torque-transmitting mechanisms with the combined engagement of at least three to set up at least ten forward gear ratio and at least one reverse gear ratio between described input link and described output link.
CN201510123428.XA 2014-03-20 2015-03-20 Multi-speed transmission Active CN104930142B (en)

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US201461968156P 2014-03-20 2014-03-20
US61/968156 2014-03-20
US14/640,798 US9651118B2 (en) 2014-03-20 2015-03-06 Multi-speed transmission
US14/640798 2015-03-06

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