CN113685527A - Longitudinally-arranged continuously variable transmission - Google Patents
Longitudinally-arranged continuously variable transmission Download PDFInfo
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- CN113685527A CN113685527A CN202111043465.1A CN202111043465A CN113685527A CN 113685527 A CN113685527 A CN 113685527A CN 202111043465 A CN202111043465 A CN 202111043465A CN 113685527 A CN113685527 A CN 113685527A
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- 230000005540 biological transmission Effects 0.000 title claims abstract description 131
- 230000007246 mechanism Effects 0.000 claims abstract description 132
- 230000009467 reduction Effects 0.000 claims abstract description 73
- 230000008859 change Effects 0.000 claims abstract description 48
- 238000013016 damping Methods 0.000 claims description 18
- 230000008901 benefit Effects 0.000 description 5
- 230000006872 improvement Effects 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
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- 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
- F16H47/00—Combinations of mechanical gearing with fluid clutches or fluid gearing
- F16H47/06—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the hydrokinetic type
- F16H47/08—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the hydrokinetic type the mechanical gearing being of the type with members having orbital motion
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- 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
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
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- 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
- F16H57/00—General details of gearing
- F16H57/08—General details of gearing of gearings with members having orbital motion
- F16H57/10—Braking arrangements
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- 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
- F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
- F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
- F16H63/30—Constructional features of the final output mechanisms
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Abstract
The invention discloses a longitudinally-arranged continuously variable transmission which comprises an output shaft, a continuously variable transmission mechanism, a forward reverse gear switching mechanism, a gear speed change mechanism and a reduction gear mechanism, wherein the forward reverse gear switching mechanism is used for switching forward gears and reverse gears, the reduction gear mechanism is connected with the forward reverse gear switching mechanism, the gear speed change mechanism is connected with the continuously variable transmission mechanism and the gear speed change mechanism, and the reduction gear mechanism is connected with the output shaft. The longitudinally-arranged continuously variable transmission adopts a mode of combining the continuously variable transmission mechanism and the gear speed change mechanism, realizes a larger speed change range, and realizes higher torque bearing capacity and higher transmission efficiency under a low-speed working condition; but also can improve the compactness of the arrangement structure and reduce the weight and the cost.
Description
Technical Field
The invention belongs to the technical field of transmissions, and particularly relates to a longitudinally-arranged continuously variable transmission.
Background
The value of the maximum total transmission ratio divided by the minimum total transmission ratio of the transmission is called the speed change range of the transmission, the speed change range represents the speed change capacity of the transmission, the larger the speed change range is, the higher the power performance and the economic performance of the whole vehicle and the reduction of the noise of the high-speed cruising working condition of the whole vehicle are facilitated, the speed change range of the stepless speed change mechanism depends on the maximum running radius and the minimum running radius of the input bevel wheel and the output bevel wheel, and is limited by the aspects of bearing torque, structure, size and the like, and the speed change range of the longitudinally-arranged stepless speed change mechanism with the existing structure is greatly limited.
Another need for improvement of the longitudinally-arranged continuously variable transmission with the existing structure is that when the transmission is in a low vehicle speed working condition, the transmission ratio of the continuously variable transmission mechanism is in a large transmission ratio position, the torque of the power input by the power source can be greatly amplified, a transmission part bears a great load under a maximum large torque working condition, the bearing capacity of the continuously variable transmission mechanism under the large transmission ratio working condition is insufficient, a method of limiting the maximum input torque or reducing the maximum transmission ratio is usually adopted in design, but the negative effects of insufficient power or reduction of the speed ratio range and the like can be brought.
The transmission efficiency of the stepless speed change mechanism is low under the working condition of large transmission ratio under the influence of the efficiency characteristic of the stepless speed change mechanism, and in addition, a hydraulic system for pushing the conical disc to clamp needs hydraulic support with enough large pressure under the working condition of large transmission ratio and large torque, so that the increase of the load consumption of an oil pump for providing hydraulic pressure is brought; therefore, the conditions that the efficiency of the existing continuously variable transmission is low under the working condition of large transmission ratio and large torque are caused together.
Disclosure of Invention
The present invention is directed to solving at least one of the problems of the prior art. Therefore, the invention provides a longitudinally-arranged continuously variable transmission, aiming at improving the speed change range and the compactness of the arrangement structure.
In order to achieve the purpose, the invention adopts the technical scheme that: a longitudinally-arranged continuously variable transmission comprises an output shaft, a continuously variable transmission mechanism, a forward reverse gear switching mechanism used for switching forward gears and reverse gears, a gear transmission mechanism connected with the forward reverse gear switching mechanism, and a reduction gear mechanism connected with the continuously variable transmission mechanism and the gear transmission mechanism, wherein the reduction gear mechanism is connected with the output shaft, and the forward gear transmission ratio of the gear transmission mechanism is larger than 1.
The speed reduction gear mechanism comprises an intermediate shaft, a first-stage speed reduction driving gear, a first-stage speed reduction driven gear, a second-stage speed reduction driving gear and a second-stage speed reduction driven gear, the first-stage speed reduction driven gear is arranged on the intermediate shaft and meshed with the first-stage speed reduction driving gear, the second-stage speed reduction driving gear is arranged on the intermediate shaft, the second-stage speed reduction driven gear is meshed with the second-stage speed reduction driving gear, and the second-stage speed reduction driven gear is connected with the output shaft.
The first-stage speed reduction driving gear is connected with the stepless speed change mechanism through a first clutch.
The gear speed change mechanism comprises a gear shift input shaft connected with the forward and reverse gear switching mechanism, a gear shift driving gear arranged on the gear shift input shaft and a gear shift driven gear which is rotatably arranged on the intermediate shaft and meshed with the gear shift driving gear, and the intermediate shaft is provided with a synchronizer used for controlling the gear shift driven gear to be jointed and separated with the intermediate shaft.
The gear-shift driven gear and the synchronizer are positioned between the primary reduction driven gear and the secondary reduction driving gear.
The forward and reverse gear switching mechanism comprises a forward gear clutch, a reverse gear brake and a planetary gear mechanism, the planetary gear mechanism is connected with the forward gear clutch, the reverse gear brake and the stepless speed change mechanism, and the gear speed change mechanism is connected with the planetary gear mechanism.
The longitudinally-arranged continuously variable transmission also comprises a torsion damping component, and the continuously variable transmission mechanism is positioned between the torsion damping component and the forward and reverse gear switching mechanism.
The stepless speed change mechanism comprises an input cone pulley and an output cone pulley, the input cone pulley is connected with the torsion vibration damping component and the forward reverse gear switching mechanism, the input cone pulley is located between the torsion vibration damping component and the forward reverse gear switching mechanism, the output cone pulley is connected with the first clutch, and the first clutch is located between the output cone pulley and the speed reduction gear mechanism.
The torsional vibration damping component is a hydraulic torque converter, a dual-mass flywheel or a torsional vibration damper.
The longitudinally-arranged continuously variable transmission adopts a mode of combining the continuously variable transmission mechanism and the gear speed change mechanism, realizes a larger speed change range, and realizes higher torque bearing capacity and higher transmission efficiency under a low-speed working condition; but also can improve the compactness of the arrangement structure and reduce the weight and the cost.
Drawings
The description includes the following figures, the contents shown are respectively:
FIG. 1 is a schematic structural view of a longitudinal continuously variable transmission of the present invention;
labeled as: 1. a hydraulic torque converter; 1a, a pump impeller; 1b, a turbine; 1c, a guide wheel; 2. a transmission housing; 3. an input shaft; 4. a transmission belt; 5. an output cone pulley; 5a, a first output conical disc; 5b, a second output conical disc; 6. inputting a cone pulley; 6a, a first input conical disc; 6b, a second input conical disc; 7. a first clutch; 9. a primary reduction drive gear; 10. a primary reduction driven gear; 11. a gear guard input shaft; 15. a synchronizer; 16. the gear keeps off from the moving gear; 17. a gear stage drive gear; 18. a secondary reduction driven gear; 19. an output shaft; 20. a secondary reduction drive gear; 21. an intermediate shaft; 27. a forward gear clutch; 28. a reverse gear brake; 29. a planetary wheel mechanism; 29a, a planet wheel input member; 29b, a planetary output member; 30. forward reverse gear switching mechanism.
Detailed Description
Reference will now be made in detail to the present preferred embodiments of the present invention, examples of which are illustrated in the accompanying drawings, so as to provide those skilled in the art with a more complete, accurate and thorough understanding of the principles and aspects of the present invention, and to facilitate its implementation.
As shown in fig. 1, the present invention provides a vertical continuously variable transmission, which includes an output shaft 19, a torsional vibration damping member, a continuously variable transmission mechanism, a forward reverse switching mechanism 30 for switching between a forward gear and a reverse gear, a gear change mechanism connected to the forward reverse switching mechanism 30, and a reduction gear mechanism connected to the continuously variable transmission mechanism and the gear change mechanism, wherein the reduction gear mechanism is connected to the output shaft 19, and a forward gear transmission ratio of the gear change mechanism is greater than 1.
Specifically, as shown in fig. 1, the continuously variable transmission mechanism is located between the forward/reverse switching mechanism 30 and the torsion damping member, and the torsion damping member is connected to the power source. The stepless speed change mechanism mainly comprises an input cone pulley 6, an output cone pulley 5 and a transmission belt 4 matched with the input cone pulley 6 and the output cone pulley 5, wherein the central shaft of the input cone pulley 6 is connected with an input shaft 3, the input shaft 3 is connected with a torsional vibration damping component, the input cone pulley 6 is composed of a first input cone disk 6a and a second input cone disk 6b, the first input cone disk 6a and the second input cone disk 6b are connected without relative rotation and can move relatively and axially within a certain range, the output cone pulley 5 is composed of a first output cone disk 5a and a second output cone disk 5b, the first output cone disk 5a and the second output cone disk 5b are connected without relative rotation and can move relatively and axially within a certain range, the transmission belt 4 is wound between the input cone pulley 6 and the output cone pulley 5, the transmission belt 4 is controllably clamped axially by the first input cone disk 6a and the second input cone disk 6b, the drive belt 4 is simultaneously controllably axially clamped by a first output cone disc 5a and a second output cone disc 5 b.
As shown in fig. 1, the reduction gear mechanism includes an intermediate shaft 21, a primary reduction driving gear 9, a primary reduction driven gear 10 provided on the intermediate shaft 21 and meshed with the primary reduction driving gear 9, a secondary reduction driving gear 20 provided on the intermediate shaft 21, and a secondary reduction driven gear 18 meshed with the secondary reduction driving gear 20, and the secondary reduction driven gear 18 is connected to an output shaft 19. The first-stage reduction driving gear 9 is connected with the stepless speed change mechanism through a first clutch 7, the first clutch 7 is used for controlling the transmission and the interruption of power between the reduction gear mechanism and the stepless speed change mechanism, the first clutch 7 and the output conical pulley 5 are coaxially arranged, and the input end of the first clutch 7 is connected with the output conical pulley 5 in a non-relative-rotation mode. The first-stage reduction driven gear 10 is coaxially and fixedly connected with an intermediate shaft 21, the second-stage reduction driving gear 20 is coaxially and fixedly connected with the intermediate shaft 21, the second-stage reduction driven gear 18 is coaxially and fixedly connected with an output shaft 19, the output shaft 19 and the rotary central shaft of the output conical wheel 5 are arranged in parallel, and the output shaft 19 is a power output component of the longitudinally-arranged continuously variable transmission.
As shown in fig. 1, the gear shift mechanism includes a gear stage input shaft 11 connected to the forward/reverse switching mechanism 30, a gear stage driving gear 17 provided on the gear stage input shaft 11, and a gear stage driven gear 16 rotatably provided on an intermediate shaft 21 and meshed with the gear stage driving gear 17, and a synchronizer 15 for controlling engagement and disengagement of the gear stage driven gear 16 with and from the intermediate shaft 21 is provided on the intermediate shaft 21. The axis of the gear input shaft 11 is parallel to the axis of the intermediate shaft 21, and the gear input shaft 11 is coaxially arranged with the forward and reverse switching mechanism 30 and is connected with the output member of the planetary gear mechanism 29 on the forward and reverse switching mechanism 30 in a non-relative rotation manner; the gear shift input shaft 11 is provided with a gear shift driving gear 17 which is connected in a non-relative-rotation mode, the intermediate shaft 21 is provided with a synchronizer 15 which is connected in a non-relative-rotation mode, the intermediate shaft 21 is further provided with a gear shift driven gear 16 which can rotate freely relative to the intermediate shaft 21, the gear shift driven gear 16 and the synchronizer 15 are located between the primary speed reduction driven gear 10 and the secondary speed reduction driving gear 20, and the diameter of the gear shift driving gear 17 is smaller than that of the gear shift driven gear 16. The gear stage driven gear 16 is disposed between the synchronizer 15 and the secondary reduction driving gear 20, or the gear stage driven gear 16 is disposed between the synchronizer 15 and the primary reduction driven gear 10. The synchronizer 15 has an engagement sleeve which is connected to the intermediate shaft 21 in a rotationally fixed manner and is axially movable, and the engagement sleeve has two operating state positions, namely a position engaged with the gear shift driven gear 16 and a position disengaged from the gear shift driven gear 16. After the engagement gear sleeve is engaged with the gear shift driven gear 16, the synchronizer 15 connects the gear shift driven gear 16 and the intermediate shaft 21 into a whole, and the gear shift driven gear 16 and the intermediate shaft 21 can synchronously rotate; after the engagement sleeve is disengaged from the driven gear 16, the synchronizer 15 cannot integrally connect the driven gear 16 with the countershaft 21, and the driven gear 16 cannot rotate synchronously with the countershaft 21, and the driven gear 16 is free on the countershaft 21.
As shown in fig. 1, the forward-reverse switching mechanism 30 preferably includes a forward clutch 27, a reverse brake 28, and a planetary gear mechanism 29, and the planetary gear mechanism 29 is arranged coaxially with the input bevel gear 6. The planetary gear mechanism 29 comprises a planet carrier, a planetary gear input part 29a, a planetary gear output part 29b and a planetary gear rotatably arranged on the planet carrier, the planetary gear is meshed with the planetary gear input part 29a and the planetary gear output part 29b, and the planetary gear input part 29a and the planetary gear output part 29b are coaxially arranged. The planet carrier is connected to a reverse brake 28, the reverse brake 28 is used for braking the planet carrier, the gear change mechanism is connected to a planet wheel output member 29b of the planet wheel mechanism 29, the planet wheel input member 29a is connected to the central shaft of the input cone pulley 6 in a non-rotating manner, the planet wheel input member 29a is connected to a forward clutch 27, and the forward clutch 27 is used for engaging and disengaging the planet wheel input member 29a and the planet wheel output member 29 b.
As shown in fig. 1, the vertically-mounted continuously variable transmission of the present invention has two power transmission paths, which are a first power transmission path and a second power transmission path, respectively. The first power transmission path is a path through which the power of the power source is transmitted sequentially via the center shaft of the input bevel wheel 6, the forward/reverse switching mechanism 30, the gear shift mechanism, the intermediate shaft 21, the secondary reduction drive gear 20, the secondary reduction driven gear 18, and the output shaft 19; the second power transmission path is a path through which the power of the power source is transmitted via the continuously variable transmission mechanism, the first clutch 7, the reduction gear mechanism, and the output shaft 19. The first power transmission path and the second power transmission path are switched by cooperation of the forward-reverse switching mechanism 30 and the first clutch 7, so that the power of the power source can be selectively transmitted through the first power transmission path and the second power transmission path.
The torsional vibration damping means may be a torque converter, a dual mass flywheel or a torsional vibration damper. As shown in fig. 1, in the present embodiment, the torsion damping member is a torque converter 1.
The longitudinally-arranged continuously variable transmission has three actual working gears, namely a reverse gear, a forward gear and a continuously variable transmission.
When the vertical continuously variable transmission is in a reverse gear position, the forward clutch 27 in the forward and reverse gear switching mechanism 30 is in a separated state, the planet wheel input part 29a and the planet wheel output part 29b can relatively rotate, the reverse brake 28 is in an engaged state, the planet carrier is braked by the reverse brake 28, the planet carrier cannot rotate, the first clutch 7 is in a separated state, the engaging gear sleeve of the synchronizer 15 moves to a position engaged with the gear driven gear 16, the power of the power source is sequentially transmitted to the output shaft 19 through the torsion damping part, the input shaft 3, the central shaft of the input bevel wheel 6, the planet wheel input part 29a, the planet wheel output part 29b, the gear input shaft 11, the gear driving gear 17, the gear driven gear 16, the synchronizer 15, the intermediate shaft 21, the secondary reduction driving gear 20 and the secondary reduction driven gear 18, the power of the output shaft 19 is transmitted to the wheels of the vehicle, thereby implementing a reverse gear function.
When the longitudinally-arranged continuously variable transmission is in a forward gear position, a forward gear clutch 27 in a forward reverse gear switching mechanism 30 is in an engaged state, the forward gear clutch 27 integrally connects a planetary gear input part 29a and a planetary gear output part 29b, the planetary gear input part 29a and the planetary gear output part 29b cannot relatively rotate, a reverse gear brake 28 is in a disengaged state, a planetary carrier can rotate, a first clutch 7 is in a disengaged state, an engagement gear sleeve of a synchronizer 15 moves to a position engaged with a gear driven gear 16, and the power of a power source sequentially passes through a torsion damping part, an input shaft 3, a central shaft of an input bevel gear 6, an integral structure formed by the planetary gear mechanism 29 and the forward gear clutch 27, a gear input shaft 11, a gear driving gear 17, a gear driven gear 16, the synchronizer 15, an intermediate shaft 21, a gear, The secondary reduction driving gear 20 and the secondary reduction driven gear 18 are transmitted to the output shaft 19, and the power of the output shaft 19 is transmitted to the wheels of the vehicle, thereby implementing a forward gear shift function, which is generally used as a first gear for starting the vehicle.
When the vertically-mounted continuously variable transmission of the present invention is in a continuously variable transmission range, the forward clutch 27 is in a disengaged state, the planetary gear input member 29a and the planetary gear output member 29b can rotate relative to each other, the reverse brake 28 is in a disengaged state, the carrier can rotate, the first clutch 7 is in an engaged state, the power of the power source is transmitted to the output shaft 19 via the torsional vibration damping member, the input shaft 3, the continuously variable transmission mechanism, the first clutch 7, and the reduction gear mechanism in this order, and the power of the output shaft 19 is transmitted to the wheels of the vehicle. The input cone pulley 6 and the output cone pulley 5 of the stepless speed change mechanism are respectively provided with a hydraulic piston clamping mechanism, the clamping force of two cone disks on the input cone pulley 6 to the transmission belt 4 is adjusted by adjusting the hydraulic pressure of the hydraulic piston clamping mechanism filled on the input cone pulley 6, the clamping force of two cone disks on the output cone pulley 5 to the transmission belt 4 is adjusted by adjusting the hydraulic pressure of the hydraulic piston clamping mechanism filled on the input cone pulley 6, the transmission belt 4 is kept in a 'tight' state under the combined action of the clamping forces exerted on the input cone pulley 6 and the output cone pulley 5 by the input cone pulley 6 and the output cone pulley 5 to transmit power, the running radius of the transmission belt 4 on the input cone pulley 6 and the output cone pulley 5 is divided by the running radius of the transmission belt 4 on the input cone pulley 6 to be called as a transmission ratio, and the running radii of the transmission belt 4 on the input cone pulley 6 and the output cone pulley 5 can be adjusted by respectively adjusting the hydraulic pressure of the hydraulic piston clamping mechanisms filled on the input cone pulley 6 and the output cone pulley 5, the transmission ratio of the continuously variable transmission mechanism can be adjusted, and the transmission ratio is continuously adjustable, thereby realizing the function of 'continuously variable transmission'.
The longitudinal continuously variable transmission is provided with a forward gear, the forward gear transmission ratio of a gear speed change mechanism of the longitudinal continuously variable transmission is larger than 1, and the total transmission ratio of the forward gear of the gear speed change mechanism can be set to be larger than the maximum total transmission ratio of a step speed change mechanism of a generally known continuously variable transmission, so that the value of the total transmission ratio of the forward gear of the longitudinal continuously variable transmission divided by the minimum total transmission ratio of the continuously variable transmission mechanism in the longitudinal continuously variable transmission is larger than the value of the maximum total transmission ratio of the continuously variable transmission mechanism divided by the minimum total transmission ratio of the continuously variable transmission mechanism of other generally known continuously variable transmissions, and the longitudinal continuously variable transmission has a larger transmission range compared with the conventional continuously variable transmission.
On the other hand, the continuously variable transmission of the present invention can be designed to have a larger shift range than the previously known continuously variable transmission while moderately reducing the shift range of the continuously variable transmission mechanism therein, and reduction of the shift range of the continuously variable transmission mechanism brings about an advantage that the size and weight of the input cone pulley 6, the output cone pulley 5, and the support housing thereof of the continuously variable transmission mechanism can be relatively reduced and reduced.
The gear shifting mechanism provided by the longitudinally-arranged continuously variable transmission has the advantages that the gear gears are generally set as starting gears, namely a first gear and a reverse gear, for starting and low vehicle speed working conditions, the first gear and the reverse gear generally have large transmission ratio, under the condition of the large transmission ratio, the torque value of power input by a power source is greatly amplified, so that a transmission part bears large load, and under the low vehicle speed working condition, the power is transmitted by the gear shifting mechanism, and the continuously variable transmission mechanism does not transmit the power.
The gear speed change mechanism is obviously superior to the stepless speed change mechanism in the aspects of bearing capacity and transmission efficiency, so that the longitudinally-arranged stepless speed change mechanism has the advantages of higher torque bearing capacity and higher transmission efficiency compared with the conventional longitudinally-arranged stepless speed change mechanism under the working condition of low vehicle speed.
One of the features of the longitudinally-arranged continuously variable transmission of the present invention is that a synchronizer 15 without relative rotation coupling is provided on the intermediate shaft 21 for realizing gear shift, and an "empty" gear driven gear 16 which can rotate freely relative to the intermediate shaft 21 is also provided, which has the advantage that the first power transmission path and the second power transmission path can share a plurality of components without additional arrangement, and the shared components include the intermediate shaft 21 and its support bearing, the secondary reduction driving gear 20, and the secondary reduction driven gear 18, thereby saving the number of parts and the arrangement space, and reducing the weight and the cost.
Based on the above description of the embodiments of the longitudinally-arranged cvt according to the present invention, it can be seen that the non-limiting innovation and advantage of the present invention is that a compact, low-weight, and low-cost longitudinally-arranged cvt structure is realized under the premise of achieving a larger transmission range, higher torque-carrying capacity at low speed, and higher transmission efficiency.
The invention is described above with reference to the accompanying drawings. It is to be understood that the specific implementations of the invention are not limited in this respect. Various insubstantial improvements are made by adopting the method conception and the technical scheme of the invention; the present invention is not limited to the above embodiments, and can be modified in various ways.
Claims (9)
1. The utility model provides a indulge and put buncher, includes output shaft, infinitely variable transmission mechanism and is used for switching over the forward gear and the switching mechanism of the forward reverse gear of reverse gear which characterized in that: the transmission device also comprises a gear speed change mechanism connected with the forward and reverse gear switching mechanism and a reduction gear mechanism connected with the stepless speed change mechanism and the gear speed change mechanism, wherein the reduction gear mechanism is connected with the output shaft, and the forward gear transmission ratio of the gear speed change mechanism is greater than 1.
2. The tandem continuously variable transmission according to claim 1, wherein: the speed reduction gear mechanism comprises an intermediate shaft, a first-stage speed reduction driving gear, a first-stage speed reduction driven gear, a second-stage speed reduction driving gear and a second-stage speed reduction driven gear, the first-stage speed reduction driven gear is arranged on the intermediate shaft and meshed with the first-stage speed reduction driving gear, the second-stage speed reduction driving gear is arranged on the intermediate shaft, the second-stage speed reduction driven gear is meshed with the second-stage speed reduction driving gear, and the second-stage speed reduction driven gear is connected with the output shaft.
3. The tandem continuously variable transmission according to claim 2, wherein: the first-stage speed reduction driving gear is connected with the stepless speed change mechanism through a first clutch.
4. The tandem continuously variable transmission according to claim 2 or 3, wherein: the gear speed change mechanism comprises a gear shift input shaft connected with the forward and reverse gear switching mechanism, a gear shift driving gear arranged on the gear shift input shaft and a gear shift driven gear which is rotatably arranged on the intermediate shaft and meshed with the gear shift driving gear, and the intermediate shaft is provided with a synchronizer used for controlling the gear shift driven gear to be jointed and separated with the intermediate shaft.
5. The tandem continuously variable transmission according to claim 4, wherein: the gear-shift driven gear and the synchronizer are positioned between the primary reduction driven gear and the secondary reduction driving gear.
6. The tandem continuously variable transmission according to any one of claims 1 to 5, wherein: the forward and reverse gear switching mechanism comprises a forward gear clutch, a reverse gear brake and a planetary gear mechanism, the planetary gear mechanism is connected with the forward gear clutch, the reverse gear brake and the stepless speed change mechanism, and the gear speed change mechanism is connected with the planetary gear mechanism.
7. The tandem continuously variable transmission according to any one of claims 1 to 6, wherein: the stepless speed change mechanism is positioned between the torsion damping component and the forward and reverse gear switching mechanism.
8. The tandem continuously variable transmission according to claim 7, wherein: the stepless speed change mechanism comprises an input cone pulley and an output cone pulley, the input cone pulley is connected with the torsion vibration damping component and the forward reverse gear switching mechanism, the input cone pulley is located between the torsion vibration damping component and the forward reverse gear switching mechanism, the output cone pulley is connected with the first clutch, and the first clutch is located between the output cone pulley and the speed reduction gear mechanism.
9. The tandem continuously variable transmission according to claim 7, wherein: the torsional vibration damping component is a hydraulic torque converter, a dual-mass flywheel or a torsional vibration damper.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111043465.1A CN113685527B (en) | 2021-09-07 | 2021-09-07 | Longitudinally-arranged stepless speed changer |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202111043465.1A CN113685527B (en) | 2021-09-07 | 2021-09-07 | Longitudinally-arranged stepless speed changer |
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| CN113685527A true CN113685527A (en) | 2021-11-23 |
| CN113685527B CN113685527B (en) | 2024-01-26 |
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| CN202111043465.1A Active CN113685527B (en) | 2021-09-07 | 2021-09-07 | Longitudinally-arranged stepless speed changer |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114165573A (en) * | 2021-12-15 | 2022-03-11 | 芜湖万里扬变速器有限公司 | Longitudinal stepless speed variator |
| CN117553108A (en) * | 2024-01-12 | 2024-02-13 | 北京中科原动力科技有限公司 | Agricultural machinery gearbox and agricultural machinery |
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| CN117553108A (en) * | 2024-01-12 | 2024-02-13 | 北京中科原动力科技有限公司 | Agricultural machinery gearbox and agricultural machinery |
| CN117553108B (en) * | 2024-01-12 | 2024-04-30 | 北京中科原动力科技有限公司 | Agricultural machinery gearbox and agricultural machinery |
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| CN113685527B (en) | 2024-01-26 |
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