Hydraulic starting and decelerating integrated transmission assembly

Abstract

The present application belongs to the field of vehicle power transmission and auxiliary braking technology, and is especially a hydraulic starting and retarding integrated transmission assembly. The hydraulic starting and retarding integrated transmission assembly comprises a shell, an input shaft, an output shaft, a coupling, a first wet clutch, a first wet clutch driving end fixedly connected shell, an input side impeller slidingly connected sleeve, an input side impeller, an output side impeller, an idling loss suppression return spring, a one-way clutch and a second wet brake. The present application is beneficial to reducing the number of parts, improving the compactness of the transmission assembly structure and the system integration; in the hydraulic starting state, torque is transmitted through the working medium, so that a speed difference is allowed to exist between the input shaft and the output shaft, thereby buffering the transmission impact during the starting process of the vehicle and improving the smoothness of the vehicle starting; the slip loss and the working medium temperature rise generated by continuously using hydraulic transmission can be reduced, and the transmission efficiency under normal driving conditions can be improved.

Description

Technical Field

[0001] This invention relates to the field of vehicle power transmission and auxiliary braking technology, specifically to a hydraulic start-up and deceleration integrated transmission assembly. Background Technology

[0002] With increasing demands for smooth starting, transmission efficiency, and continuous braking capability in commercial vehicles, engineering vehicles, and heavy-duty vehicles, vehicle transmission systems typically require hydraulic start, mechanical direct drive, and auxiliary retarding functions. Hydraulic start reduces starting shock, mechanical direct drive reduces hydraulic slip loss, and hydraulic retarding reduces the thermal load and frictional wear of the service brakes. In existing technologies, when hydraulic start and hydraulic retarding devices are installed separately, there are problems such as a large number of components, complex structure, and large space occupation. Although some integrated devices can share hydraulic working components, they still require coordination of the mechanical direct drive mechanism, impeller fixing mechanism, and unidirectional transmission mechanism to avoid interference between different power transmission paths.

[0003] Furthermore, in non-hydraulic operating states such as mechanical direct drive, even when the hydraulic working chamber is in a low-fill or drained state, airflow disturbance, residual working medium agitation, and idling drag losses may still occur between the two oppositely positioned impellers. Therefore, how to utilize the same set of hydraulic impellers to achieve functional switching between hydraulic start-up and hydraulic deceleration, and coordinate the mechanical direct drive path, the fixed path of the output impeller, and the unidirectional transmission path, while avoiding rigid interference between different power paths and reducing idling drag losses in non-hydraulic operating states, is a technical problem that needs to be solved in this field. Summary of the Invention

[0004] The purpose of this section is to outline some aspects of the embodiments of the present invention and to briefly describe some preferred embodiments. Simplifications or omissions may be made in this section, as well as in the abstract and title of this application, to avoid obscuring the purpose of these documents; however, such simplifications or omissions should not be construed as limiting the scope of the invention.

[0005] To address the aforementioned technical problems, according to one aspect of the present invention, the present invention provides the following technical solution:

[0006] A hydraulic start-up and deceleration integrated transmission assembly includes a housing, an input shaft, an output shaft, a coupling, a first wet clutch, a first wet clutch drive end fixed connecting housing, an input side impeller sliding connecting sleeve, an input side impeller, an output side impeller, a idling loss suppression return spring, a one-way clutch, and a second wet brake.

[0007] The first wet clutch includes a first wet clutch driving end connected to the input shaft and a first wet clutch driven end connected to the output shaft via a coupling. The first wet clutch is used to selectively connect or disconnect the mechanical direct drive force transmission path between the input shaft and the output shaft.

[0008] The first wet clutch driving end fixed connecting shell is fixedly connected to the first wet clutch driving end, and is drivenly connected to the input side impeller through the input side impeller sliding connecting sleeve. The input side impeller sliding connecting sleeve is used to transmit circumferential torque between the first wet clutch driving end fixed connecting shell and the input side impeller, and allows the input side impeller to move axially in the direction close to or away from the output side impeller. The axial movement connection restricts the input side impeller from circumferentially rotating relative to the first wet clutch driving end fixed connecting shell. The input side impeller and the output side impeller are arranged axially opposite each other, and a hydraulic working chamber for accommodating the working medium is formed between the input side impeller and the output side impeller. The idling loss suppression return spring acts on the input side impeller or the input side impeller sliding connecting sleeve, and applies an elastic force to the input side impeller in the direction away from the output side impeller.

[0009] The second wet brake includes a rotating end connected to the output-side impeller and a fixed end fixed to the housing. The second wet brake is used to selectively fix the output-side impeller to the housing. The rotating end of the second wet brake is also connected to the output shaft via a one-way clutch. The one-way clutch is used to transmit the torque of the output-side impeller in the power output direction to the output shaft and to block the transmission of reverse torque from the output shaft to the output-side impeller.

[0010] The input-side impeller and the output-side impeller are a shared set of impellers for both hydraulic start-up and hydraulic deceleration states. In the hydraulic start-up state, the output-side impeller acts as a driven impeller receiving the hydraulic torque transmitted by the input-side impeller, and transmits torque to the output shaft via the rotating end of the second wet brake and the one-way clutch in a locked state. In the mechanical direct drive state, the first wet clutch establishes a mechanical direct drive force transmission path between the input shaft and the output shaft. The hydraulic working chamber is in a low-fill or drained state. The idling loss suppression return spring causes the input-side impeller to move away from the output-side impeller, and the one-way clutch is in an overrunning state. In the hydraulic deceleration state, the output shaft drives the input-side impeller to rotate in the opposite direction via the coupling and the first wet clutch. The second wet brake fixes the output-side impeller to the housing, making the output-side impeller a fixed reaction impeller, and the one-way clutch is in an overrunning state to disconnect the rigid torque transmission between the output shaft and the fixed output-side impeller.

[0011] In a preferred embodiment of the hydraulic start-up and deceleration integrated transmission assembly described in this invention, the housing comprises a front housing, a middle housing, and a rear housing connected sequentially along the axial direction, the front housing, the middle housing, and the rear housing together forming an accommodating space; at least a portion of the input shaft and the first wet clutch are disposed within the front housing, the input-side impeller and the output-side impeller are disposed within the middle housing, and at least a portion of the second wet brake, the one-way clutch, and the output shaft are disposed within the rear housing;

[0012] The input shaft is rotatably supported on the front housing via an input end support bearing, the output shaft is rotatably supported on the rear housing via an output end support bearing, the input-side impeller is supported via an input-side impeller support bearing, and the output-side impeller is supported via an output-side impeller support bearing.

[0013] In a preferred embodiment of the hydraulic start-up and deceleration integrated transmission assembly described in this invention, the first wet clutch further includes a first wet clutch hydraulic piston and a first wet clutch return spring; the first wet clutch hydraulic piston is axially movable to push the driving end and the driven end of the first wet clutch to press against each other and engage; the first wet clutch return spring acts on the first wet clutch hydraulic piston to push the first wet clutch hydraulic piston back to its original position after the hydraulic pressure acting on the first wet clutch hydraulic piston is released, thereby separating the driving end and the driven end of the first wet clutch.

[0014] As a preferred embodiment of the hydraulic start-up and deceleration integrated transmission assembly described in this invention, the second wet brake further includes a second wet brake hydraulic piston and a second wet brake return spring; the second wet brake hydraulic piston is axially movable to push the rotating end and the fixed end of the second wet brake to press against each other and engage; the second wet brake return spring acts on the second wet brake hydraulic piston to push the second wet brake hydraulic piston back to its original position after the hydraulic pressure acting on the second wet brake hydraulic piston is released, thereby separating the rotating end and the fixed end of the second wet brake.

[0015] In a preferred embodiment of the hydraulic start-up and deceleration integrated transmission assembly described in this invention, the input-side impeller sliding connecting sleeve is connected to the input-side impeller and forms an axial sliding connection with the first wet clutch driving end fixed connecting shell; the axial sliding connection restricts the input-side impeller from circumferentially rotating relative to the first wet clutch driving end fixed connecting shell, and allows the input-side impeller to move in a direction closer to or farther from the output-side impeller;

[0016] The input-side impeller has a working position close to the output-side impeller and a separated position away from the output-side impeller; when the input-side impeller is in the working position, a hydraulic circulation channel is formed between the input-side impeller and the output-side impeller; when the input-side impeller is in the separated position, the axial distance between the input-side impeller and the output-side impeller is greater than the axial distance between them when the input-side impeller is in the working position.

[0017] When the hydraulic working chamber is in a low-fill or drain state, the idling loss suppression return spring causes the input-side impeller to move toward the separation position, thereby increasing the axial distance between the input-side impeller and the output-side impeller.

[0018] As a preferred embodiment of the hydraulic start-up and retarding integrated transmission assembly described in this invention, the transmission assembly can selectively operate in a hydraulic start-up state, a mechanical direct drive state, or a hydraulic retarding state; in the hydraulic start-up state, both the first wet clutch and the second wet brake are in a disengaged state, the hydraulic working chamber is in a fluid-filled state, the input-side impeller drives the output-side impeller to rotate through the working medium, and the output-side impeller drives the output shaft to rotate through the rotating end of the second wet brake and the one-way clutch in a locked state;

[0019] In the mechanical direct drive state, the first wet clutch is engaged, the second wet brake is disengaged, and the input shaft drives the output shaft to rotate sequentially through the first wet clutch and the coupling; the hydraulic working chamber is in a low-fill or drained state, the input-side impeller moves away from the output-side impeller under the action of the idling loss suppression return spring, and the one-way clutch is in an overrunning state.

[0020] In a preferred embodiment of the hydraulic start-up and deceleration integrated transmission assembly described in this invention, in the hydraulic deceleration state, both the first wet clutch and the second wet brake are engaged. The output shaft drives the input-side impeller to rotate sequentially through the coupling, the driven end of the first wet clutch, the driving end of the first wet clutch, the fixed connecting housing of the driving end of the first wet clutch, and the sliding connecting sleeve of the input-side impeller. The second wet brake fixes the output-side impeller to the housing. The input-side impeller drives the working medium in the hydraulic working chamber to circulate, thereby generating a hydraulic deceleration torque acting on the input-side impeller and transmitted to the output shaft via the first wet clutch and the coupling. The one-way clutch is in an overrunning state to disconnect the rigid torque transmission between the output shaft and the fixed output-side impeller.

[0021] In a preferred embodiment of the hydraulic start-up and deceleration integrated transmission assembly described in this invention, when the output-side impeller drives the output shaft in the power output direction, the one-way clutch is in a locked state to transmit the torque of the output-side impeller to the output shaft; when the rotational speed of the output shaft is higher than the rotational speed of the output-side impeller, or when the output shaft has a tendency to drag the output-side impeller in the opposite direction, the one-way clutch is in an overrunning state to block the reverse torque transmitted from the output shaft to the output-side impeller.

[0022] As a preferred embodiment of the hydraulic start-up and deceleration integrated transmission assembly described in this invention, the first wet clutch driving end and the first wet clutch driven end respectively include friction transmission components arranged alternately along the axial direction; the second wet brake rotating end and the second wet brake fixed end respectively include friction braking components arranged alternately along the axial direction.

[0023] In a preferred embodiment of the hydraulic start-up and deceleration integrated transmission assembly described in this invention, when the transmission assembly switches from the hydraulic start-up state to the mechanical direct drive state, the first wet clutch switches from the disengaged state to the engaged state, the second wet brake remains disengaged, the one-way clutch switches from the locked state to the overrunning state, the hydraulic working chamber switches from the filled state to the low-filled state, and the idling loss suppression return spring moves the input-side impeller to the disengaged position in a direction away from the output-side impeller; when the transmission assembly exits the hydraulic deceleration state, the second wet brake switches from the engaged state to the disengaged state to release the fixation on the output-side impeller, and after the hydraulic working chamber enters the low-filled state, the idling loss suppression return spring moves the input-side impeller to the disengaged position in a direction away from the output-side impeller.

[0024] Compared with the prior art, the beneficial effects of the present invention are:

[0025] This invention utilizes the cooperation of a first wet clutch, a second wet brake, and a one-way clutch under different operating conditions. In the hydraulic start-up state, the same set of input-side and output-side impellers performs hydraulic transmission; in the hydraulic deceleration state, the output-side impeller switches to a fixed reaction impeller to form hydraulic deceleration; and simultaneously, in the mechanical direct drive state, the first wet clutch establishes a mechanical direct drive path between the input and output shafts. This achieves hydraulic start-up, mechanical direct drive, and hydraulic deceleration functions within the same transmission assembly, reducing the number of parts and improving structural compactness and system integration.

[0026] This invention transmits torque through a working medium in a hydraulic start-up state, allowing a speed difference between the input and output shafts, thereby buffering the transmission shock during vehicle start-up and improving the smoothness of vehicle start-up.

[0027] This invention establishes a mechanical direct drive force transmission path between the input shaft and the output shaft through a first wet clutch in mechanical direct drive mode, which can reduce slip loss and working medium temperature rise caused by continuous use of hydraulic transmission and improve transmission efficiency under normal driving conditions.

[0028] In a hydraulically decelerated state, the present invention uses a first wet clutch to reverse the rotation of the input-side impeller on the output shaft, and uses a second wet brake to fix the output-side impeller to the housing. This allows the mechanical energy of the vehicle transmission system to be converted into the heat energy of the working medium through the hydraulic working chamber, thereby generating a continuous hydraulic deceleration torque and reducing the thermal load and frictional wear of the vehicle's service brake.

[0029] This invention enables the input-side impeller to move axially while maintaining circumferential torque transmission through a sliding connecting sleeve. It also reduces airflow disturbance, residual working medium agitation, and idling drag loss by suppressing the return spring from increasing the axial distance between the two impellers when the hydraulic working chamber is in a low-fill or drained state.

[0030] This invention uses a one-way clutch to lock and transmit torque in hydraulic start-up mode, and enters overrunning mode in mechanical direct drive mode and hydraulic slow-down mode. This can prevent the output shaft from dragging the output side impeller in the reverse direction, and prevent the output shaft from forming a rigid lock with the fixed output side impeller in hydraulic slow-down mode. Attached Figure Description

[0031] To more clearly illustrate the technical solutions of the embodiments of the present invention, the present invention will be described in detail below with reference to the accompanying drawings and detailed embodiments. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort. Wherein:

[0032] Figure 1 This is a schematic diagram of the axial cross-sectional structure of an integrated hydraulic start-up and deceleration transmission assembly according to the present invention.

[0033] Figure 2 This is a power transmission route diagram of an integrated hydraulic start-up and deceleration transmission assembly in the hydraulic start-up state according to the present invention.

[0034] Figure 3 This is a power transmission route diagram of the hydraulic start-up and deceleration integrated transmission assembly of the present invention when it is in mechanical direct drive mode;

[0035] Figure 4 This is a diagram showing the power and reaction force transmission route of a hydraulic start-up and deceleration integrated transmission assembly in a hydraulic deceleration state according to the present invention.

[0036] The red lines in the diagram represent the power transmission routes in different modes of the transmission assembly.

[0037] In the diagram: 1-Front housing; 2-Fixed connecting housing for the driving end of the first wet clutch; 3-Hydraulic piston for the first wet clutch; 4-Return spring for the first wet clutch; 5-Driven end of the first wet clutch; 6-Sliding connecting sleeve for the input side impeller; 7-Driving end of the first wet clutch; 8-Input side impeller; 9-Middle housing; 10-Output side impeller; 11-Hydraulic piston for the second wet brake; 12-Return spring for the second wet brake; 13-Rotating end of the second wet brake; 14-Fixed end of the second wet brake; 15-Rear housing; 16-Output end support bearing; 17-One-way clutch; 18-Output side impeller support bearing; 19-Output shaft; 20-Return spring to suppress idling loss; 21-Input side impeller support bearing; 22-Coupling; 23-Input shaft; 24-Input end support bearing. Detailed Implementation

[0038] To make the above-mentioned objects, features and advantages of the present invention more apparent and understandable, the specific embodiments of the present invention will be described in detail below with reference to the accompanying drawings.

[0039] Secondly, the present invention is described in detail with reference to the schematic diagrams. When detailing the embodiments of the present invention, for ease of explanation, the cross-sectional views illustrating the device structure may be partially enlarged, not according to the usual scale. Furthermore, the schematic diagrams are merely examples and should not limit the scope of protection of the present invention. In addition, actual fabrication should include three-dimensional spatial dimensions of length, width, and depth.

[0040] To make the objectives, technical solutions, and advantages of the present invention clearer, the embodiments of the present invention will be described in further detail below with reference to the accompanying drawings.

[0041] like Figure 1 As shown, a hydraulic start-up and deceleration integrated transmission assembly includes a front housing 1, a middle housing 9, a rear housing 15, a first wet clutch driving end fixed connecting housing 2, a first wet clutch hydraulic piston 3, a first wet clutch return spring 4, a first wet clutch driven end 5, an input side impeller sliding connecting sleeve 6, a first wet clutch driving end 7, an input side impeller 8, an output side impeller 10, a second wet brake hydraulic piston 11, a second wet brake return spring 12, a second wet brake rotating end 13, a second wet brake fixed end 14, an output end support bearing 16, a one-way clutch 17, an output side impeller support bearing 18, an output shaft 19, a idling loss suppression return spring 20, an input side impeller support bearing 21, a coupling 22, an input shaft 23, and an input end support bearing 24.

[0042] The front housing 1, the middle housing 9, and the rear housing 15 are connected sequentially along the axial direction of the transmission assembly, and together form a receiving space for accommodating the various components of the transmission assembly. The front housing 1 is located on the input side of the transmission assembly, the middle housing 9 is located between the front housing 1 and the rear housing 15, and the rear housing 15 is located on the output side of the transmission assembly.

[0043] The input shaft 23 is rotatably supported on the front housing 1 via an input end support bearing 24. The input end of the input shaft 23 is used for transmission connection with an engine, motor, or other external power source. The output shaft 19 is rotatably supported on the rear housing 15 via an output end support bearing 16. The output end of the output shaft 19 is used for connection with a gearbox, drive shaft, or other external transmission components. The input shaft 23 and the output shaft 19 are coaxially arranged.

[0044] The first wet clutch is located between the input shaft 23 and the output shaft 19, and includes the first wet clutch driving end 7, the first wet clutch driven end 5, the first wet clutch hydraulic piston 3, and the first wet clutch return spring 4.

[0045] The first wet clutch driving end 7 is fixedly connected to the input shaft 23, so that the first wet clutch driving end 7 can rotate synchronously with the input shaft 23. The first wet clutch driven end 5 is connected to one end of the coupling 22, and the other end of the coupling 22 is connected to the output shaft 19, so that the first wet clutch driven end 5 can transmit torque to the output shaft 19 through the coupling 22.

[0046] The driving end 7 and the driven end 5 of the first wet clutch are respectively provided with friction transmission components arranged alternately along the axial direction. The hydraulic piston 3 of the first wet clutch is movably disposed on one side of the first wet clutch and is used to push the driving end 7 and the driven end 5 of the first wet clutch to press against each other.

[0047] When the first wet clutch hydraulic piston 3 is subjected to hydraulic pressure, the first wet clutch hydraulic piston 3 moves axially, causing the first wet clutch driving end 7 to engage with the first wet clutch driven end 5 and rotate synchronously, thereby connecting the mechanical direct drive force transmission path between the input shaft 23 and the output shaft 19.

[0048] The first wet clutch return spring 4 acts on the first wet clutch hydraulic piston 3. When the hydraulic pressure acting on the first wet clutch hydraulic piston 3 is released, the first wet clutch return spring 4 pushes the first wet clutch hydraulic piston 3 to reset, causing the first wet clutch driving end 7 to separate from the first wet clutch driven end 5, thereby disconnecting the mechanical direct drive force transmission path between the input shaft 23 and the output shaft 19.

[0049] The first wet clutch driving end fixed connecting shell 2 is fixedly connected to the first wet clutch driving end 7, so that the first wet clutch driving end fixed connecting shell 2 can rotate synchronously with the input shaft 23 and the first wet clutch driving end 7.

[0050] The input-side impeller sliding connecting sleeve 6 is disposed between the first wet clutch driving end fixed connecting shell 2 and the input-side impeller 8. The input-side impeller sliding connecting sleeve 6 is connected to the input-side impeller 8 and forms an axial sliding connection with the first wet clutch driving end fixed connecting shell 2. The axial sliding connection can restrict the input-side impeller 8 from circumferential relative rotation with respect to the first wet clutch driving end fixed connecting shell 2, while allowing the input-side impeller 8 to move axially.

[0051] Through the above connection structure, the first wet clutch driving end fixed connection shell 2 can transmit circumferential torque to the input side impeller 8 through the input side impeller sliding connection sleeve 6, and enable the input side impeller 8 to move in the direction of approaching or moving away from the output side impeller 10.

[0052] The input-side impeller 8 is supported by the input-side impeller support bearing 21, and the output-side impeller 10 is supported by the output-side impeller support bearing 18. The input-side impeller 8 and the output-side impeller 10 are arranged axially opposite to each other, and a hydraulic working chamber for containing the working medium is formed between the input-side impeller 8 and the output-side impeller 10.

[0053] The input-side impeller 8 serves as the active impeller, driving the circulating flow of the working medium within the hydraulic working chamber. The output-side impeller 10 is a switchable impeller; in the hydraulic start-up state, it acts as a driven impeller receiving the hydraulic torque transmitted by the input-side impeller 8, while in the hydraulic slow-down state, it acts as a fixed reaction impeller.

[0054] The second wet brake is located between the output impeller 10 and the rear housing 15, and includes a second wet brake rotating end 13, a second wet brake fixed end 14, a second wet brake hydraulic piston 11, and a second wet brake return spring 12.

[0055] The rotating end 13 of the second wet brake is connected to the output impeller 10, enabling the rotating end 13 of the second wet brake to rotate synchronously with the output impeller 10. The fixed end 14 of the second wet brake is fixedly connected to the rear housing 15. The rotating end 13 and the fixed end 14 of the second wet brake are respectively provided with friction braking components arranged alternately along the axial direction.

[0056] The hydraulic piston 11 of the second wet brake is axially movable and disposed on one side of the second wet brake. When the hydraulic piston 11 of the second wet brake is subjected to hydraulic pressure, the hydraulic piston 11 of the second wet brake moves axially and pushes the rotating end 13 of the second wet brake and the fixed end 14 of the second wet brake to press against each other.

[0057] Since the fixed end 14 of the second wet brake is fixedly connected to the rear housing 15, when the rotating end 13 of the second wet brake is combined with the fixed end 14 of the second wet brake, the rotating end 13 of the second wet brake and the output side impeller 10 connected thereto are fixed to the housing.

[0058] The second wet brake return spring 12 acts on the second wet brake hydraulic piston 11. When the hydraulic pressure acting on the second wet brake hydraulic piston 11 is released, the second wet brake return spring 12 pushes the second wet brake hydraulic piston 11 to reset, causing the rotating end 13 of the second wet brake to separate from the fixed end 14 of the second wet brake, thereby releasing the fixed connection between the output side impeller 10 and the housing.

[0059] A one-way clutch 17 is disposed between the rotating end 13 of the second wet brake and the output shaft 19. When the output-side impeller 10 drives the output shaft 19 in the power output direction through the rotating end 13 of the second wet brake, the one-way clutch 17 is locked, so that the torque of the output-side impeller 10 can be transmitted to the output shaft 19 through the rotating end 13 of the second wet brake and the one-way clutch 17.

[0060] When the rotational speed of the output shaft 19 is higher than that of the output side impeller 10, or when the output shaft 19 has a tendency to reverse the output side impeller 10, the one-way clutch 17 is in an overrunning state to block the reverse torque transmitted from the output shaft 19 to the rotating end 13 of the second wet brake and the output side impeller 10.

[0061] The input-side impeller 8 has a working position close to the output-side impeller 10 and a separated position away from the output-side impeller 10. When the input-side impeller 8 is in the working position, a hydraulic circulation channel is formed between the input-side impeller 8 and the output-side impeller 10; when the input-side impeller 8 is in the separated position, the axial distance between the input-side impeller 8 and the output-side impeller 10 is greater than the axial distance between them when the input-side impeller 8 is in the working position.

[0062] The idling loss suppression return spring 20 acts on the input side impeller 8 or the input side impeller sliding connecting sleeve 6, and applies an elastic force to the input side impeller 8 in a direction away from the output side impeller 10.

[0063] When the hydraulic working chamber is in a low-fill or drained state, and torque is not required to be transmitted through the hydraulic working chamber, the idling loss suppression return spring 20 causes the input impeller 8 to move toward the separation position, thereby increasing the axial distance between the input impeller 8 and the output impeller 10.

[0064] When the input-side impeller 8 moves axially, the input-side impeller sliding connecting sleeve 6 maintains the circumferential torque transmission relationship between the first wet clutch driving end fixed connecting shell 2 and the input-side impeller 8. By increasing the axial distance between the input-side impeller 8 and the output-side impeller 10, the airflow disturbance, residual working medium agitation, and mutual drag between the two impellers can be reduced, thereby reducing the idling drag loss in non-hydraulic working conditions.

[0065] When the transmission assembly needs to perform hydraulic start-up or hydraulic deceleration, the input-side impeller 8 is positioned close to the output-side impeller 10, forming a corresponding hydraulic circulation channel between the input-side impeller 8 and the output-side impeller 10. This embodiment does not limit the specific driving method for the input-side impeller 8 to move from the separated position to the working position.

[0066] The transmission assembly in this embodiment can selectively operate in hydraulic start-up mode, mechanical direct drive mode, or hydraulic retarding mode according to the vehicle's operating needs.

[0067] like Figure 2 As shown, when the vehicle needs to start, the transmission assembly is in a hydraulic starting state. At this time, the first wet clutch and the second wet brake are both disengaged, the input-side impeller 8 is in the working position, and the hydraulic working chamber is in the fluid-filled state required for hydraulic starting.

[0068] The input shaft 23 drives the first wet clutch driving end 7 to rotate, and the first wet clutch driving end fixed connecting shell 2 drives the first wet clutch driving end to rotate synchronously. The first wet clutch driving end fixed connecting shell 2 drives the input side impeller 8 to rotate through the input side impeller sliding connecting sleeve 6.

[0069] The input-side impeller 8 drives the working medium in the hydraulic working chamber to circulate, and drives the output-side impeller 10 to rotate through the momentum exchange of the working medium. The output-side impeller 10 drives the rotating end 13 of the second wet brake to rotate synchronously.

[0070] Since the rotating end 13 and the fixed end 14 of the second wet brake are separated, the output impeller 10 can rotate freely. The one-way clutch 17 is locked in the power output direction, and the rotating end 13 of the second wet brake drives the output shaft 19 to rotate through the one-way clutch 17, thereby realizing hydraulic starting.

[0071] In hydraulic start-up mode, power is transmitted sequentially from the input shaft 23, the first wet clutch driving end 7, the first wet clutch driving end fixed connecting shell 2, and the input side impeller sliding connecting sleeve 6 to the input side impeller 8, and then from the input side impeller 8 to the output side impeller 10 through the working medium, and finally from the output side impeller 10 to the output shaft 19 through the second wet brake rotating end 13 and the one-way clutch 17.

[0072] Since the input-side impeller 8 and the output-side impeller 10 transmit torque through the working medium, and a speed difference is allowed between the input shaft 23 and the output shaft 19, the transmission shock during vehicle start-up can be buffered, thereby improving the smoothness of vehicle start-up.

[0073] like Figure 3 As shown, when the vehicle completes its start-up and enters normal driving mode, the transmission assembly is in mechanical direct drive mode. At this time, the first wet clutch is engaged, the second wet brake is disengaged, and the hydraulic working chamber is in low-fill or drained state.

[0074] The hydraulic piston 3 of the first wet clutch moves axially under hydraulic pressure and pushes the driving end 7 and the driven end 5 of the first wet clutch to press against each other, so that the driving end 7 and the driven end 5 of the first wet clutch engage and rotate synchronously.

[0075] The input shaft 23 drives the first wet clutch driving end 7 to rotate. The first wet clutch driving end 7 transmits power to the coupling 22 through the first wet clutch driven end 5. The coupling 22 then transmits power to the output shaft 19, thus forming a mechanical direct drive force transmission path between the input shaft 23 and the output shaft 19.

[0076] In mechanical direct drive mode, when the speed of the output shaft 19 is higher than the speed of the output side impeller 10, or when the output shaft 19 has a tendency to drag the output side impeller 10 in the opposite direction, the one-way clutch 17 is in overrunning state to block the transmission of reverse torque from the output shaft 19 to the output side impeller 10.

[0077] After the hydraulic working chamber enters a low-filling or draining state, the idling loss suppression return spring 20 causes the input-side impeller 8 to move to the separation position in a direction away from the output-side impeller 10, thereby increasing the axial distance between the input-side impeller 8 and the output-side impeller 10, thus reducing the idling drag loss generated by the hydraulic working components under mechanical direct drive.

[0078] like Figure 4 As shown, when the vehicle needs assisted retardation, the transmission assembly is in a hydraulic retardation state. At this time, both the first wet clutch and the second wet brake are engaged, the input-side impeller 8 is in the working position, and the hydraulic working chamber is in the fluid-filled state required for hydraulic retardation.

[0079] The vehicle transmission system reverses the rotation of the output shaft 19, which in turn drives the coupling 22 to rotate. The coupling 22 then transmits the rotational power to the driven end 5 of the first wet clutch. Since the first wet clutch is engaged, the driven end 5 of the first wet clutch drives the driving end 7 of the first wet clutch to rotate synchronously.

[0080] The first wet clutch driving end 7 drives the input side impeller 8 to rotate through the first wet clutch driving end fixed connecting shell 2 and the input side impeller sliding connecting sleeve 6.

[0081] The hydraulic piston 11 of the second wet brake moves axially under hydraulic pressure, pushing the rotating end 13 of the second wet brake and the fixed end 14 of the second wet brake to press against each other. Since the fixed end 14 of the second wet brake is fixedly connected to the rear housing 15, after the second wet brake is engaged, the rotating end 13 of the second wet brake and the output impeller 10 are fixed to the housing, so that the output impeller 10 acts as a fixed reaction impeller.

[0082] The input-side impeller 8 drives the working medium in the hydraulic working chamber to circulate under the reverse drag of the output shaft 19. The working medium applies a counter torque to the fixed output-side impeller 10, and the counter torque is transmitted sequentially through the output-side impeller 10, the rotating end 13 of the second wet brake, and the fixed end 14 of the second wet brake to the rear housing 15.

[0083] Simultaneously, the working medium applies a hydraulic resistance torque to the input-side impeller 8 in the opposite direction of its rotation. This hydraulic resistance torque is transmitted sequentially through the input-side impeller sliding connecting sleeve 6, the first wet clutch driving end fixed connecting shell 2, the first wet clutch driving end 7, the first wet clutch driven end 5, and the coupling 22 to the output shaft 19, thereby forming a hydraulic retarding torque acting on the output shaft 19.

[0084] In the hydraulic slow-speed state, the one-way clutch 17 is in the overrun state to block the rigid torque transmission between the output shaft 19 and the fixed output side impeller 10 in the reverse drag direction, so as to prevent the output shaft 19 from forming a rigid lock with the rear housing 15 through the one-way clutch 17.

[0085] During the hydraulic retardation process, the mechanical energy of the vehicle transmission system is converted into the heat energy of the working medium through the hydraulic interaction between the input impeller 8, the working medium and the output impeller 10, thereby producing a continuous auxiliary retardation effect on the vehicle transmission system.

[0086] When the transmission assembly switches from hydraulic start-up mode to mechanical direct drive mode, the first wet clutch switches from disengagement mode to engagement mode, the second wet brake remains disengaged, the one-way clutch 17 moves from lock-up mode to overrunning mode, the hydraulic working chamber enters low-filling or draining mode, and the idling loss suppression return spring 20 moves the input-side impeller 8 to the disengagement position.

[0087] When the transmission assembly exits the hydraulic slow-down state, the second wet brake is disengaged, and the return spring 12 of the second wet brake pushes the hydraulic piston 11 of the second wet brake to reset, so that the rotating end 13 of the second wet brake is separated from the fixed end 14 of the second wet brake, thereby releasing the fixation on the output side impeller 10.

[0088] After the hydraulic working chamber enters a low-filling or draining state, the idling loss suppression return spring 20 causes the input-side impeller 8 to move to the separation position in a direction away from the output-side impeller 10, thereby enabling the hydraulic working component to enter a low-loss state.

[0089] The above description is only one specific embodiment of the present invention. Without departing from the technical concept of the present invention, the number of friction transmission components of the first wet clutch and the second wet brake, the sliding connection form of the input side impeller sliding connecting sleeve 6, the specific structure of the one-way clutch 17, the form of each support bearing, and the axial movement structure of the input side impeller 8 can all be adjusted or replaced according to actual needs.

[0090] Although the present invention has been described above with reference to embodiments, various modifications can be made and components can be replaced with equivalents without departing from the scope of the invention. In particular, as long as there is no structural conflict, the features in the disclosed embodiments can be combined with each other in any manner. The lack of an exhaustive description of these combinations in this specification is merely for the sake of brevity and resource conservation. Therefore, the present invention is not limited to the specific embodiments disclosed herein, but includes all technical solutions falling within the scope of the claims.

Claims

1. A hydraulic start-up and deceleration integrated transmission assembly, characterized in that, It includes a housing, an input shaft, an output shaft, a coupling, a first wet clutch, a fixed connecting housing for the driving end of the first wet clutch, a sliding connecting sleeve for the input side impeller, an input side impeller, an output side impeller, a return spring to suppress idling loss, a one-way clutch, and a second wet brake. The first wet clutch includes a first wet clutch driving end connected to the input shaft and a first wet clutch driven end connected to the output shaft via a coupling. The first wet clutch is used to selectively connect or disconnect the mechanical direct drive force transmission path between the input shaft and the output shaft. The first wet clutch driving end fixed connecting shell is fixedly connected to the first wet clutch driving end, and is drivenly connected to the input side impeller through the input side impeller sliding connecting sleeve. The input side impeller sliding connecting sleeve is used to transmit circumferential torque between the first wet clutch driving end fixed connecting shell and the input side impeller, and allows the input side impeller to move axially in the direction close to or away from the output side impeller. The axial movement connection restricts the input side impeller from circumferentially rotating relative to the first wet clutch driving end fixed connecting shell. The input side impeller and the output side impeller are arranged axially opposite each other, and a hydraulic working chamber for accommodating the working medium is formed between the input side impeller and the output side impeller. The idling loss suppression return spring acts on the input side impeller or the input side impeller sliding connecting sleeve, and applies an elastic force to the input side impeller in the direction away from the output side impeller. The second wet brake includes a rotating end connected to the output-side impeller and a fixed end fixed to the housing. The second wet brake is used to selectively fix the output-side impeller to the housing. The rotating end of the second wet brake is also connected to the output shaft via a one-way clutch. The one-way clutch is used to transmit the torque of the output-side impeller in the power output direction to the output shaft and to block the transmission of reverse torque from the output shaft to the output-side impeller. The input-side impeller and the output-side impeller are a shared set of impellers for both hydraulic start-up and hydraulic deceleration states. In the hydraulic start-up state, the output-side impeller acts as a driven impeller receiving the hydraulic torque transmitted by the input-side impeller, and transmits torque to the output shaft via the rotating end of the second wet brake and the one-way clutch in a locked state. In the mechanical direct drive state, the first wet clutch establishes a mechanical direct drive force transmission path between the input shaft and the output shaft. The hydraulic working chamber is in a low-fill or drained state. The idling loss suppression return spring causes the input-side impeller to move away from the output-side impeller, and the one-way clutch is in an overrunning state. In the hydraulic deceleration state, the output shaft drives the input-side impeller to rotate in the opposite direction via the coupling and the first wet clutch. The second wet brake fixes the output-side impeller to the housing, making the output-side impeller a fixed reaction impeller, and the one-way clutch is in an overrunning state to disconnect the rigid torque transmission between the output shaft and the fixed output-side impeller.

2. The hydraulic start-up and deceleration integrated transmission assembly according to claim 1, characterized in that, The housing includes a front housing, a middle housing, and a rear housing connected sequentially along the axial direction, the front housing, the middle housing, and the rear housing together forming an accommodating space; at least a portion of the components of the input shaft and the first wet clutch are disposed in the front housing, the input-side impeller and the output-side impeller are disposed in the middle housing, and at least a portion of the components of the second wet brake, the one-way clutch, and the output shaft are disposed in the rear housing; The input shaft is rotatably supported on the front housing via an input end support bearing, the output shaft is rotatably supported on the rear housing via an output end support bearing, the input-side impeller is supported via an input-side impeller support bearing, and the output-side impeller is supported via an output-side impeller support bearing.

3. The hydraulic start-up and deceleration integrated transmission assembly according to claim 1, characterized in that, The first wet clutch further includes a first wet clutch hydraulic piston and a first wet clutch return spring; the first wet clutch hydraulic piston is axially movable to push the first wet clutch driving end and the first wet clutch driven end to press against each other and engage; the first wet clutch return spring acts on the first wet clutch hydraulic piston to push the first wet clutch hydraulic piston to reset after the hydraulic pressure acting on the first wet clutch hydraulic piston is released, so that the first wet clutch driving end and the first wet clutch driven end are separated.

4. The hydraulic start-up and deceleration integrated transmission assembly according to claim 1, characterized in that, The second wet brake further includes a second wet brake hydraulic piston and a second wet brake return spring; the second wet brake hydraulic piston is axially movable to push the rotating end of the second wet brake and the fixed end of the second wet brake to press against each other and engage; the second wet brake return spring acts on the second wet brake hydraulic piston to push the second wet brake hydraulic piston to reset after the hydraulic pressure acting on the second wet brake hydraulic piston is released, so that the rotating end of the second wet brake separates from the fixed end of the second wet brake.

5. The hydraulic start-up and deceleration integrated transmission assembly according to claim 1, characterized in that, The input-side impeller sliding connection sleeve is connected to the input-side impeller and forms an axial sliding connection with the first wet clutch driving end fixed connection shell; the axial sliding connection restricts the input-side impeller from circumferential relative rotation with respect to the first wet clutch driving end fixed connection shell, and allows the input-side impeller to move in a direction closer to or further away from the output-side impeller; The input-side impeller has a working position close to the output-side impeller and a separated position away from the output-side impeller; when the input-side impeller is in the working position, a hydraulic circulation channel is formed between the input-side impeller and the output-side impeller; when the input-side impeller is in the separated position, the axial distance between the input-side impeller and the output-side impeller is greater than the axial distance between them when the input-side impeller is in the working position. When the hydraulic working chamber is in a low-fill or drain state, the idling loss suppression return spring causes the input-side impeller to move toward the separation position, thereby increasing the axial distance between the input-side impeller and the output-side impeller.

6. The hydraulic start-up and deceleration integrated transmission assembly according to claim 1, characterized in that, The transmission assembly can selectively operate in a hydraulic start-up state, a mechanical direct drive state, or a hydraulic slow-down state. In the hydraulic start-up state, both the first wet clutch and the second wet brake are in a disengaged state, the hydraulic working chamber is in a fluid-filled state, the input-side impeller drives the output-side impeller to rotate through the working medium, and the output-side impeller drives the output shaft to rotate through the rotating end of the second wet brake and the one-way clutch in a locked state. In the mechanical direct drive state, the first wet clutch is engaged, the second wet brake is disengaged, and the input shaft drives the output shaft to rotate sequentially through the first wet clutch and the coupling; the hydraulic working chamber is in a low-fill or drained state, the input-side impeller moves away from the output-side impeller under the action of the idling loss suppression return spring, and the one-way clutch is in an overrunning state.

7. The hydraulic start-up and deceleration integrated transmission assembly according to claim 6, characterized in that, In the hydraulic deceleration state, both the first wet clutch and the second wet brake are engaged. The output shaft drives the input-side impeller to rotate sequentially through the coupling, the driven end of the first wet clutch, the driving end of the first wet clutch, the fixed connecting housing of the driving end of the first wet clutch, and the sliding connecting sleeve of the input-side impeller. The second wet brake fixes the output-side impeller to the housing. The input-side impeller drives the working medium in the hydraulic working chamber to circulate, generating a hydraulic deceleration torque that acts on the input-side impeller and is transmitted to the output shaft through the first wet clutch and the coupling. The one-way clutch is in an overrunning state to disconnect the rigid torque transmission between the output shaft and the fixed output-side impeller.

8. The hydraulic start-up and deceleration integrated transmission assembly according to claim 1, characterized in that, When the output-side impeller drives the output shaft in the power output direction, the one-way clutch is in a locked state to transmit the torque of the output-side impeller to the output shaft; when the rotational speed of the output shaft is higher than the rotational speed of the output-side impeller, or when the output shaft has a tendency to drag the output-side impeller in the opposite direction, the one-way clutch is in an overrunning state to block the reverse torque transmitted from the output shaft to the output-side impeller.

9. The hydraulic start-up and deceleration integrated transmission assembly according to claim 1, characterized in that, The first wet clutch driving end and the first wet clutch driven end each include friction transmission components arranged alternately along the axial direction; the second wet brake rotating end and the second wet brake fixed end each include friction braking components arranged alternately along the axial direction.

10. The hydraulic start-up and deceleration integrated transmission assembly according to claim 7, characterized in that, When the transmission assembly switches from the hydraulic start-up state to the mechanical direct drive state, the first wet clutch switches from the disengaged state to the engaged state, the second wet brake remains disengaged, the one-way clutch switches from the locked state to the overrunning state, the hydraulic working chamber switches from the filled state to the low-filled state, and the idling loss suppression return spring moves the input-side impeller away from the output-side impeller to the disengaged position. When the transmission assembly exits the hydraulic deceleration state, the second wet brake switches from the engaged state to the disengaged state to release the fixation on the output-side impeller, and after the hydraulic working chamber enters the low-filled state, the idling loss suppression return spring moves the input-side impeller away from the output-side impeller to the disengaged position.

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