Wet clutch and working machine

Abstract

The invention belongs to the technical field of vehicle engineering, and discloses a wet clutch and an operation machine.The wet clutch comprises a transmission hub frame, a main shaft and a control device, the transmission hub frame comprises an inner hub and an outer hub which are arranged at intervals in the radial direction, and a piston and a friction plate set which are arranged in the axial direction are arranged between the inner hub and the outer hub; the main shaft serves as a center shaft of the transmission hub frame and forms a hollow oil channel extending in the axial direction, the hollow oil channel is further provided with a bypass working oil channel and a bypass lubricating oil channel which are spaced in the axial direction, the bypass working oil channel is used for being communicated with a driving cavity of the piston, and the bypass lubricating oil channel is used for being communicated with an installation cavity of the friction plate set. The control device is used for controlling the hollow oil duct between the bypass working oil duct and the bypass lubricating oil duct to be connected or disconnected. According to the clutch, an oil supply path for working oil and an oil supply path for lubricating oil are integrated together, so that the hydraulic control difficulty of the clutch is reduced, and the structural design is simpler.

Description

Technical Field

[0001] The present invention belongs to the technical field of vehicle engineering, and in particular relates to a wet clutch and an operating machine. Background Art

[0002] The clutch is generally composed of a main shaft, an inner hub, an outer hub, an active friction plate, a driven friction plate, a piston, etc. When the clutch is engaged, the piston drives the driven friction plate to fit with the active friction plate, thereby realizing the transmission between the outer hub and the inner hub.

[0003] A wet clutch typically requires constant oil cooling for the engaged driven and active friction plates. Therefore, in addition to the working oil channels that supply oil to the piston's drive chamber, existing wet clutch spindles also feature cooling lubricating oil channels for cooling the friction plates. In other words, the working and cooling lubricating oil channels are separate and independent. Furthermore, piston driving and friction plate cooling require different oil pressures and timing, requiring separate hydraulic mechanisms to control these functions. This results in a complex wet clutch structure and high control difficulty. Summary of the Invention

[0004] In view of the above-mentioned defects or shortcomings, the present invention provides a wet clutch and an operating machine to solve the technical problems of the existing wet clutch having a complex structure and being difficult to control.

[0005] To achieve the above-mentioned objectives, the present invention provides a wet clutch, comprising a transmission hub frame, a main shaft and a control device, the transmission hub frame comprising an inner hub and an outer hub arranged radially at intervals, a piston and a friction plate group arranged axially between the inner hub and the outer hub, the main shaft serving as the central axis of the transmission hub frame and forming an axially extending hollow oil channel, the hollow oil channel further comprising an axially spaced bypass working oil channel and a bypass lubricating oil channel, the bypass working oil channel being used to connect to a driving chamber of the piston, the bypass lubricating oil channel being used to connect to an installation chamber of the friction plate group, and the control device being used to control the conduction or cutoff of the hollow oil channel between the bypass working oil channel and the bypass lubricating oil channel.

[0006] In this embodiment, an oil inlet is provided at one end of the hollow oil passage, and the other end is a plugging end. The bypass working oil passage is arranged closer to the oil inlet than the bypass lubricating oil passage.

[0007] In this embodiment, the control device is arranged in the hollow oil channel between the bypass working oil channel and the bypass lubricating oil channel. The control device is a normally closed device and the hollow oil channel is opened only when the working oil pressure of the bypass working oil channel reaches the set conduction oil pressure value.

[0008] In this embodiment, the control device is a relief valve or a back pressure check valve provided in the hollow oil passage between the bypass working oil passage and the bypass lubricating oil passage.

[0009] In this embodiment, the control device is an oil plug assembly, which includes a plunger and a plunger elastic member. The plunger is arranged axially and set in the hollow oil channel between the bypass working oil channel and the bypass lubricating oil channel. One end of the plunger elastic member is fixed, and the other end elastically presses the plunger. The oil input from the oil inlet can drive the plunger to move axially to connect the bypass working oil channel and the bypass lubricating oil channel.

[0010] In this embodiment, the oil plug assembly further includes a plunger adjustment member for adjusting the axial position of the plunger.

[0011] In this embodiment, the wet clutch further includes an oil drain passage, which is provided on the outer hub and communicates with the radially outer side of the driving chamber.

[0012] In this embodiment, the wet clutch further includes a plug assembly, which is a normally open device and closes the oil drain passage only when the working oil pressure of the drive chamber reaches a set closing oil pressure value.

[0013] In this embodiment, the oil drain channel includes an axial oil drain channel and a radial oil drain channel. The plug assembly is arranged in the axial oil drain channel and includes an oil drain plug and an oil drain elastic member. The oil drain plug is provided with an axially arranged plug inner oil channel and a radial oil guide groove extending from the peripheral wall of the plug inner oil channel. The working oil in the driving chamber can drive the oil drain plug to move axially to control the radial misalignment between the radial oil guide groove and the radial oil drain channel.

[0014] In this embodiment, the outer hub includes a radial hub wall extending radially inward to the main shaft, and the oil drain channel is arranged at the radial outer end of the radial hub wall; wherein, the first drive chamber and the second drive chamber are respectively provided on both sides of the radial hub wall, the axial oil drain channel connects the first drive chamber and the second drive chamber, and the oil channel inside the plug axially passes through the oil drain plug.

[0015] In this embodiment, the oil passage in the plug is a throttling passage.

[0016] In this embodiment, the friction plate group includes a first plate group arranged on the outer hub and a second plate group arranged on the inner hub. An outer elastic member for elastically stretching the friction plates in the first plate group is provided between the friction plates in the first plate group, and an inner elastic member for elastically stretching the friction plates in the second plate group is provided between the friction plates in the axial direction. The friction plates in the inner plate group and the friction plates in the outer plate group are interdigitated and alternately distributed. The piston is used to move axially to push the first plate group in the friction plate group to engage with the second plate group.

[0017] In this embodiment, the first plate group includes a plurality of first friction plates extending radially and spaced axially in sequence, a first spacing slot is formed between any adjacent first friction plates, and the first spacing slot is provided with an external elastic member for axially spreading the adjacent first friction plates; the second plate group includes a plurality of second friction plates extending radially and spaced axially in sequence, a second spacing slot is formed between any adjacent second friction plates, and the second spacing slot is provided with an internal elastic member for axially spreading the adjacent second friction plates; wherein, the plurality of first friction plates and the plurality of second friction plates are interdigitated and alternately distributed.

[0018] In this embodiment, the axial distances between any adjacent first friction plates and second friction plates are equal.

[0019] To achieve the above objectives, the present invention further provides a working machine, wherein the working machine includes the wet clutch described above.

[0020] In the wet clutch of the present invention, when high-pressure oil is introduced into the hollow oil channel, part of the oil will enter the drive chamber from the bypass working oil channel to push the piston to squeeze the friction plate group, thereby realizing the transmission of the outer hub and the inner hub. At the same time, if the control device is turned on, part of the high-pressure oil in the hollow oil channel will also flow from the bypass lubricating oil channel into the installation chamber to lubricate and cool the friction plate group in the installation chamber. The wet clutch provided by the present invention integrates the oil supply lines of the working oil and the lubricating oil in the hollow oil channel, so that the hollow oil channel can supply oil to the drive chamber and the installation chamber respectively. Compared with the existing two-way independent oil supply method, the difficulty of hydraulic control of the clutch is greatly reduced, and the structural design is also simpler.

[0021] Other features and advantages of the present invention will be described in detail in the following detailed description. BRIEF DESCRIPTION OF THE DRAWINGS

[0022] The accompanying drawings are used to provide an understanding of the present invention and constitute a part of the specification. Together with the following detailed description, they are used to explain the present invention but do not constitute a limitation of the present invention. In the accompanying drawings:

[0023] Figure 1 is a schematic diagram of the overall structure of the left friction plate group of the wet clutch in an embodiment of the present invention when it is in an engaged state;

[0024] Figure 2 is a schematic diagram of the overall structure of the friction plate group on the right side of the wet clutch according to an embodiment of the present invention when it is in an engaged state;

[0025] Figure 3 2 is a schematic structural diagram of the oil plug assembly and the bypass lubricating oil passage according to an embodiment of the present invention;

[0026] Figure 4 2 is a schematic structural diagram of the plug assembly and the radial oil drain passage aligned and matched according to an embodiment of the present invention;

[0027] Figure 5 2 is a schematic structural diagram of a plug assembly and a radial oil drain passage according to an embodiment of the present invention when the plug assembly and the radial oil drain passage are staggered;

[0028] Figure 6 is a schematic diagram of the coordination structure of the friction plate group according to an embodiment of the present invention;

[0029] Figure 7 Schematic diagram of the exploded structure of the friction plate group according to an embodiment of the present invention.

[0030] Description of Reference Numerals

[0031] 11. Inner hub; 111. Hub body; 112. Inner hub mounting bracket; 113. Inner hub bearing; 114. Inner baffle; 12. Outer hub; 121. Radial hub wall; 122. Axial hub wall; 123. Outer baffle; 124. Sealing ring; 12a. Drain passage; 12a-2. Axial drain passage; 12a-1. Radial drain passage; 13. Piston; 14. Friction plate group; 141. First plate group; 141-1. First friction plate; 141-2. Outer elastic member; 142. Second plate group; 142-1. Second friction plate; 142-2. Inner elastic member ;15. Return spring;1a. Drive chamber;1b. Installation chamber;2. Spindle;2a. Hollow oil channel;2a-1. Oil inlet;2a-2. Hollow oil channel section;2a-3. Avoidance section;2b. Bypass working oil channel;2c. Bypass lubricating oil channel;21. Shaft retaining ring;22. Mounting baffle;3. Control device;31. Plunger;32. Plunger elastic member;33. Plunger adjustment member;4. Plug assembly;41. Oil drain plug;411. Oil channel inside the plug;412. Radial oil guide groove;42. Oil drain elastic member;43. Oil drain plug;431. Plug channel. DETAILED DESCRIPTION

[0032] The specific embodiments of the present invention are described in detail below with reference to the accompanying drawings. It should be understood that the specific embodiments described herein are only used to illustrate and explain the present invention and are not intended to limit the present invention.

[0033] The wet clutch of the present invention will be described below with reference to the accompanying drawings.

[0034] A wet clutch generally comprises a transmission hub carrier and a main shaft 2. The main shaft 2 serves as the central axis of the transmission hub carrier, which includes an inner hub 11 and an outer hub 12 spaced radially apart. Both inner hub 11 and outer hub 12 are sleeved onto the main shaft 2, with one hub in a driving or fixed connection to the main shaft 2 and the other in a sliding engagement with the main shaft 2. A piston 13 and a friction plate pack 14 are axially arranged between the inner and outer hubs 11, 12. One axial side of the piston 13 defines its drive chamber 1a, while the other side houses the friction plate pack 14. The piston 13 drives the friction plate pack 14 into engagement, thereby achieving transmission between the inner and outer hubs 11, 12.

[0035] Existing wet clutches typically feature two independent oil passages on the main shaft, one to supply oil to the drive chamber for piston 13 and the other to the mounting chamber for friction plate pack 14. However, during operation, the piston 13 and the friction plate pack require different oil pressures and flows, resulting in a complex internal structure and high control difficulty.

[0036] In view of this, the present invention discloses a novel wet clutch. Figure 1 and Figure 2 In the embodiment shown, the wet clutch includes a transmission hub carrier and a main shaft 2 , as well as a control device 3 .

[0037] Compared to conventional clutch main shafts, the main shaft 2 in this embodiment is formed with an axially extending hollow oil passage 2a. It is also provided with an axially spaced bypass working oil passage 2b and a bypass lubricating oil passage 2c. The bypass working oil passage 2b connects to the drive chamber 1a of the piston 13, while the bypass lubricating oil passage 2c connects to the mounting chamber 1b of the friction plate pack 14. A control device 3 controls the flow of the hollow oil passage 2a between the bypass working oil passage 2b and the bypass lubricating oil passage 2c.

[0038] When high-pressure oil is introduced into the hollow oil passage 2a, part of the oil will enter the drive chamber 1a from the bypass working oil passage 2b to push the piston 13 to squeeze the friction plate group 14, thereby realizing the transmission of the outer hub 12 and the inner hub 11. At the same time, if the control device 3 is turned on, part of the high-pressure oil in the hollow oil passage 2a will also flow from the bypass lubricating oil passage 2c into the installation chamber 1b to lubricate and cool the friction plate group 14 in the installation chamber 1b. In summary, the wet clutch provided by the present invention integrates the oil supply lines of the working oil and the lubricating oil on the hollow oil passage 2a, so that the hollow oil passage 2a can supply oil to the drive chamber 1a and the installation chamber 1b respectively. Compared with the existing two-way independent oil supply method, the difficulty of the hydraulic control of the clutch is greatly reduced, and the structural design is also simpler.

[0039] It should be noted that the axial extension mentioned in the embodiment of the present invention may be a straight line axial extension or a generally zigzag extension in the axial direction, and the same applies to the radial extension.

[0040] like Figure 1 and Figure 2 As shown, in this embodiment, hollow oil passage 2a has an oil inlet 2a-1 at one end and a blocked end at the other. Bypass working oil passage 2b is located closer to oil inlet 2a-1 than bypass lubricating oil passage 2c. That is, after oil enters hollow oil passage 2a, it preferentially flows into drive chamber 1a, regardless of whether control device 3 is energized, ensuring a quick and timely response from piston 13.

[0041] like Figure 1 and Figure 2 As shown, in this embodiment, control device 3 is disposed in hollow oil passage 2a between bypass working oil passage 2b and bypass lubricating oil passage 2c. Control device 3 is a normally closed device and opens hollow oil passage 2a only when the working oil pressure in bypass working oil passage 2b reaches a set oil pressure. Control device 3 can be opened actively through electronic or hydraulic control, such as when the oil pressure reaches the set oil pressure, the controller actively issues a corresponding command to open control device 3. Alternatively, control device 3 can be opened passively, such as when the oil pressure reaches the set oil pressure, the oil pressure automatically pushes control device 3 open.

[0042] Furthermore, in this embodiment, based on principle, the control device 3 can be a solenoid valve such as an electrically controlled reversing valve or an electrically controlled relief valve, which can be opened and closed by a control signal. The control device 3 can also be a passive hydraulic control valve such as a relief valve or a back-pressure check valve. When the oil pressure in the hollow oil passage 2a reaches the conduction oil pressure value, the control device 3 is pushed open by the oil, achieving conduction.

[0043] In another embodiment, the control device 3 may also use the movement stroke of the piston 13 and the engagement state of the friction plate group 14 as the control conditions for opening.

[0044] For a wet clutch, when the friction plate pack 14 is disengaged, the frictional heat generated between the plates 14 is minimal, and therefore the need for lubricating cooling oil is also minimal. If oil is introduced into the mounting chamber 1b too early, it will be wasted. However, when the friction plate pack 14 is engaged, a significant amount of frictional heat is generated. If oil is introduced too late, the friction plate pack 14 may overheat, shortening the life of the clutch.

[0045] The clutch in the present invention can set the opening timing of the control device 3 so that the control device 3 is opened just when the friction plate group 14 reaches the critical state of contact, thereby matching the contact state of the friction plate group 14 with the timing of oil entering from the bypass lubricating oil channel 2c, thereby achieving the purpose of saving oil flow.

[0046] Specifically, if Figure 1 、 Figure 2 and Figure 3 As shown, for a passive hydraulically controlled valve-type control device 3, the control device 3 can be configured to open when the oil pressure in the hollow oil channel 2a is ≥ P2. During clutch operation, oil at a pressure of P1 (P1 < P2) is first injected into the hollow oil channel 2a. After the oil at P1 flows out of the bypass working oil channel 2b, it drives the piston 13 to move, causing the friction plate pack 14 to move toward engagement. At this point, the control device 3 has not yet reached the opening condition. As the piston 13 moves, the resistance to its movement gradually increases under the action of the return spring 15 and the elastic members within the friction plate pack 14. When the oil pressure in the hollow oil channel 2a automatically rises to P2 due to the increased resistance to piston 13 movement, or when the external oil pressure is manually changed to P2, the control device 3 opens, and oil enters the mounting chamber 1b through the bypass lubrication oil channel 2c, providing lubrication and cooling for the engaged friction plate pack 14.

[0047] When the friction plate group 14 reaches the critical contact state, the piston cannot move further. At this time, the flow rate of the installation chamber can be adjusted by adjusting the injection flow rate of the hollow oil channel 2a.

[0048] like Figure 1 、 Figure 2 and Figure 3 As shown, in this embodiment, the control device 3 can be structurally an oil plug assembly, comprising a plunger 31 and a plunger elastic member 32. The plunger 31 is axially arranged and disposed in the hollow oil passage 2a between the bypass working oil passage 2b and the bypass lubricating oil passage 2c. The oil passage 2a essentially refers to the portion of the hollow oil passage 2a between the bypass working oil passage 2b and the bypass lubricating oil passage 2c. The plunger elastic member 32 has one end fixed, while the other end elastically presses against the plunger 31. Oil input from the oil inlet 2a-1 drives the plunger 31 to move axially, thereby connecting the bypass working oil passage 2b and the bypass lubricating oil passage 2c.

[0049] The hollow oil passage 2a includes a hollow oil passage section 2a-2 located between the bypass working oil passage 2b and the bypass lubricating oil passage 2c, and a relief section 2a-3 connected to the hollow oil passage section 2a-2. A plunger 31 can move in and out between the hollow oil passage section 2a-2 and the relief section 2a-3. A plunger elastic member 32 is used to push the plunger 31 from the relief section 2a-3 into the hollow oil passage section 2a-2, maintaining the plunger 31 in a position blocking the hollow oil passage section 2a-2 under normal conditions. The force exerted on the plunger 31 by the oil in the hollow oil passage section 2a-2 is directed from the hollow oil passage section 2a-2 to the relief section 2a-3, while the force exerted on the plunger 31 by the plunger elastic member 32 is directed from the relief section 2a-3 to the hollow oil passage section 2a-2. That is, when the oil pressure in the hollow oil channel section 2a-2 reaches the set value, the oil will overcome the thrust of the plunger elastic member 32 and push the oil plug from the hollow oil channel section 2a-2 into the avoidance section 2a-3, thereby bypassing the conduction between the working oil channel 2b and the bypass lubricating oil channel 2c.

[0050] like Figure 2 and Figure 3 As shown, in this embodiment, the hollow oil channel section 2a-2 and the avoidance section 2a-3 can be axially aligned, or there can be a certain angle between them. The end of the avoidance section 2a-3 away from the hollow oil channel section 2a-2 is the plugging end of the hollow oil channel 2a. The oil plug assembly also includes a plunger adjustment member 33, which is installed on the plugging end of the hollow oil channel 2a. The plunger elastic member 32 elastically supports between the plunger 31 and the plunger adjustment member 33. The plunger adjustment member 33 is used to provide support for the pre-tightening of the plunger elastic member 32. By axially aligning the hollow oil channel section 2a-2 and the avoidance section 2a-3, the processing of the hollow oil channel 2a is facilitated.

[0051] like Figure 3 As shown, in this embodiment, a throttling channel can be provided in the hollow oil channel section 2a-2. The throttling channel can not only enable the bypass working oil channel 2b to build pressure first, but also limit the oil plug so that the oil plug is maintained in the hollow oil channel section 2a-2 under the action of the plunger elastic member 32.

[0052] like Figure 1 、 Figure 2 and Figure 4 As shown, in this embodiment, the drive chamber 1a is formed between the outer hub 12 and the piston 13. An oil drain passage 12a can be provided on the outer hub 12. One end of the oil drain passage 12a communicates with the drive chamber 1a, and the other end serves as an oil drain outlet. The provision of the oil drain passage 12a allows residual oil in the drive chamber 1a to be drained when the clutch is disengaged.

[0053] like Figure 1 and Figure 4As shown, in this embodiment, when the outer hub 12 rotates, the oil remaining in the driving chamber 1a will be thrown to the radial outermost end of the driving chamber 1a. To ensure that the oil can be discharged smoothly, the oil drain channel 12a is preferably connected to the radial outer side of the driving chamber 1a.

[0054] In this embodiment, the plug assembly 4 is a normally open device and closes the oil drain passage 12a only when the working oil pressure of the drive chamber 1a reaches a set closing oil pressure value.

[0055] like Figure 1 、 Figure 2 and Figure 4 As shown, in this embodiment, the wet clutch further includes a plug assembly 4, which is a normally open device and closes the oil drain passage 12a only when the working oil pressure of the drive chamber 1a reaches a set closing oil pressure value.

[0056] The working principle of the plug assembly 4 is similar to that of the oil plug assembly, except that the plug assembly 4 is a normally open device. The plug assembly 4 can be actively or passively controlled from open to closed by means of electrical control, hydraulic control, etc.

[0057] For example, for the hydraulically controlled passively closed plug assembly 4, when the pressure in the driving chamber 1a is lower than the closing oil pressure value, the plug assembly 4 will be in a conducting state, and when the pressure in the driving chamber 1a is higher than the closing oil pressure value, the plug assembly 4 will switch states under the push of hydraulic pressure to cut off the oil drain channel 12a and the driving chamber.

[0058] Return to the working state of the clutch, such as Figure 1 、 Figure 4 and Figure 5 As shown, when the friction plate pack 14 is engaged, the drive chamber 1a reaches a high pressure, which is generally greater than the closing oil pressure. At this time, the plug assembly 4 is in a closed state, thereby preventing pressure relief in the drive chamber 1a and ensuring the engagement and clamping force of the friction plate pack 14. When the friction plate pack 14 is disengaged, the oil inlet 2a-1 of the hollow oil passage 2a discharges most of the hydraulic oil in the drive chamber 1a, and the drive chamber 1a reaches a low pressure. At this time, the plug assembly 4 is in a conductive state, and the oil drain passage 12a can completely drain the remaining oil in the drive chamber 1a, thereby ensuring the complete disengagement of the friction plate pack 14 and preventing the clutch from slipping.

[0059] like Figure 4 and Figure 5As shown, structurally, the oil drain passage 12a may include an axial oil drain passage 12a-2 and a radial oil drain passage 12a-1. The plug assembly 4 is disposed in the axial oil drain passage 12a-2 and may include an oil drain plug 41 and an oil drain elastic member 42. The oil drain plug 41 is provided with an axially arranged plug inner oil passage 411 and a radial oil guide groove 412 extending from the peripheral wall of the plug inner oil passage 411. The working oil in the drive chamber 1a can drive the oil drain plug 41 to move axially to control the radial misalignment of the radial oil guide groove 412 with the radial oil drain passage 12a-1. The oil drain elastic member 42 is used to drive the radial oil guide groove 412 to radially align with the radial oil drain passage 12a-1 when the oil pressure in the drive chamber 1a is lower than the shut-off oil pressure.

[0060] When the clutch is engaged, the drive chamber 1a reaches high pressure, causing the oil to overcome the elastic force of the drain spring 42 and push the drain plug 41 to a position where the radial oil guide groove 412 is offset from the radial drain passage 12a-1, effectively blocking the drain passage 12a. When the drive chamber 1a reaches low pressure, the drain spring 42 returns the drain plug 41 to align the radial oil guide groove 412 with the radial drain passage 12a-1.

[0061] like Figure 1 As shown, in this embodiment, a return spring 15 can be installed between the main shaft 2 and the piston 13, or between the inner hub 11 and the piston 13, or between the outer hub 12 and the piston 13. The return spring 15 is used to reset the main shaft when the hollow oil passage 2a is depressurized. For example, the main shaft 2 can be provided with a shaft retaining ring 21 and a mounting plate 22. The return spring 15 can be installed between the mounting plate 22 of the main shaft 2 and the piston 13.

[0062] like Figure 1 As shown, in this embodiment, the inner hub 11 and the main shaft 2 are radially spaced to form an oil supply chamber, which is radially adjacent to the mounting chamber 1b of the friction plate group 14 and separated by the inner hub 11. The inner hub 11 is also provided with an oil inlet hole that extends radially and mounts the chamber 1b and the oil supply chamber. When the oil enters from the bypass lubricating oil channel 2c, it will first enter the oil supply chamber, and then enter the mounting chamber 1b through the oil inlet hole on the inner hub 11 to lubricate and cool the friction plate group 14.

[0063] like Figure 1 As shown, in this embodiment, the return spring 15 can be installed in the lubricating oil supply chamber.

[0064] like Figure 1As shown, in the embodiment of the present invention, the inner hub 11 includes a hub body 111 and an inner hub mounting frame 112. The hub body 111 is used to separate the lubricating oil supply chamber from the mounting chamber 1b. The inner hub mounting frame 112 is used to be mounted on an inner hub bearing 113. The inner hub bearing 113 is used to roll with the main shaft 2. The lubricating oil inlet hole is provided in the hub body 111. The inner hub bearing 113 is limited in position, thereby achieving the fixed position between the inner hub 11 and the main shaft 2.

[0065] like Figure 1 As shown, in this embodiment, the outer hub 12 includes a radial hub wall 121 extending radially inward toward the spindle 2, and an axial hub wall 122 extending axially along the spindle 2. An oil drain passage 12a is provided at the radially outer end of the radial hub wall 121 to minimize residual oil in the drive chamber 1a. The radial hub wall 121 is fixedly connected to the spindle 2 to secure the outer hub 12 with the spindle 2.

[0066] like Figure 1 and Figure 2 As shown, in this embodiment, the drive chamber 1a is surrounded by the radial hub wall 121, the axial hub wall 122 and the axial side wall of the piston 13, and the installation chamber 1b is surrounded by the hub body 111, the axial hub wall 122 and the other axial side wall of the piston 13.

[0067] like Figure 1 As shown, in this embodiment, the outer hub 12 is provided with an outer baffle 123 for limiting the friction plate group 14 , and the inner hub 11 is provided with an inner baffle 114 for limiting the friction plate group 14 .

[0068] like Figure 1 As shown, in this embodiment, sealing rings 124 are provided between the piston 13 and the outer hub 12 , and between the piston 13 and the main shaft 2 .

[0069] like Figure 1 and Figure 2 As shown, in this embodiment, there are two mounting chambers 1b and two drive chambers 1a. Specifically, a first drive chamber and a second drive chamber are provided on either side of the radial hub wall 121. Each drive chamber 1a also corresponds to a mounting chamber 1b for the piston 13 and the friction plate assembly 14. An axial oil drain passage 12a-2 connects the first and second drive chambers, and an internal oil passage 411 axially extends through the drain plug 41.

[0070] Specifically, if Figure 1As shown, the two drive chambers 1a are respectively the first drive chamber (left chamber) and the second drive chamber (right chamber). The clutch also includes a piston 13, a friction plate assembly 14, a mounting chamber 1b, an inner hub 11, and the like corresponding to the two drive chambers 1a. An oil drain plug 41 is movably disposed within the axial oil drain passage 12a-2 and is capable of axial left and right movement. Oil drain elastic members 42 are provided on either axial side of the oil drain plug 41. The two oil drain elastic members 42 are each in a pre-compressed state to maintain the oil drain plug 41 in a balanced position intermediate between the radial oil guide groove 412 and the radial oil drain passage 12a-1. Oil drain plugs 43 are also installed at each end of the oil drain passage 12a. The oil drain plugs 43 have a plug channel 431 disposed therein. The oil drain plugs 43 are used to provide support for the oil drain elastic member 42 during pre-tightening.

[0071] When both the left and right friction plate groups 14 are disengaged, the left and right chambers are both at low pressure. Under the action of the oil drain elastic member 42, the oil drain plug 41 is in a state of opening the oil drain passage 12a. Thus, when the friction plate groups 14 are disengaged during gear shifting, the oil drain passage 12a can quickly drain the oil from either the left or right chamber, preventing incomplete separation of the friction plate groups 14 due to residual oil in the drive chamber 1a, thereby reducing friction plate heating and power loss caused by shifting. When one of the left and right friction plate groups 14 needs to engage, the oil drain plug 41 moves rightward or leftward accordingly, causing the radial oil guide groove 412 to shift away from the radial oil drain passage 12a-1, thus closing the oil drain passage 12a. This ensures that when the friction plate groups 14 engage, no oil leaks from the corresponding drive chamber 1a. The pressure in the working oil chamber remains stable, facilitating smooth power transmission during the shifting wet clutch.

[0072] In this embodiment, when the number of the mounting chamber 1 b and the driving chamber 1 a is two, the number of the hollow oil passages 2 a on the main shaft 2 may also be two.

[0073] In this embodiment, the oil passage 411 in the plug is a throttling passage, which can help the driving chamber 1a to quickly build up pressure when the friction plate group 14 needs to be engaged.

[0074] like Figure 1 、 Figure 6 and Figure 7As shown, in this embodiment, the friction plate group 14 includes a first plate group 141 arranged on the outer hub 12 and a second plate group 142 arranged on the inner hub 11. An outer elastic member 141-2 for elastically stretching along the axial direction is provided between the friction plates in the first plate group 141, and an inner elastic member 142-2 for elastically stretching along the axial direction is provided between the friction plates in the second plate group 142. The spacing between the friction plates in the first plate group 141 is maintained by the outer elastic member 141-2, and the spacing between the friction plates in the second plate group 142 is maintained by the inner elastic member 142-2. The first plate group 141 and the second plate group 142 are both arranged in a comb shape. After the first plate group 141 and the second plate group 142 are inserted and matched, the friction plates of the first plate group 141 and the friction plates of the second plate group 142 are arranged alternately in sequence.

[0075] Specifically, the first plate group 141 includes a plurality of first friction plates 141-1 extending radially and spaced axially in sequence. A first spacing slot is formed between any adjacent first friction plates 141-1. The first spacing slot is provided with an external elastic member 141-2 for axially spreading the adjacent first friction plates 141-1 apart. The first spacing slot is used for one-to-one insertion of the second friction plates 142-1.

[0076] The second plate group 142 includes a plurality of second friction plates 142-1 extending radially and spaced axially in sequence. A second spacing slot is formed between any adjacent second friction plates 142-1. The second spacing slot is provided with an internal elastic member 142-2 for axially spreading the adjacent second friction plates 142-1 apart. The second spacing slot is used for one-to-one insertion of the first friction plates 141-1.

[0077] Finger-fitting means that the first friction plate 141-1 and the second friction plate 142-1 are inserted into each other's spaced slots one by one. After the finger-fitting is completed, the first friction plate 141-1 and the second friction plate 142-1 will be alternately arranged in the order of first-second-first-second along the axial direction.

[0078] By providing outer elastic members 141-2 between the friction plates of the first plate group 141, the relative spacing between the friction plates in the first plate group 141 is maintained after the friction plate group 14 is separated. By providing inner elastic members 142-2 between the friction plates of the second plate group 142, the relative spacing between the friction plates in the second plate group 142 is maintained after the friction plate group 14 is separated. The friction plate spacing of each plate group is guaranteed, so that each time the clutch cuts power, the friction plates can be reset to the specified gap under the action of the elastic members, thereby ensuring that all friction plates are completely separated, without any contact between the friction plates, no clutch torque exists, and no power loss in the transmission system.

[0079] like Figure 1 and Figure 7As shown, in this embodiment, the inner hub 11 further includes two inner baffles 114 axially spaced apart and radially outwardly disposed on the hub body 111. A plurality of first mounting keys equidistantly arranged axially are disposed between the two inner baffles 114. The second friction plates 142-1 are mounted one-to-one on the first mounting keys, and the inner elastic members 142-2 elastically abut between adjacent second friction plates 142-1. The first mounting keys and the two inner baffles 114 limit the position of each second friction plate 142-1 relative to the inner hub 11.

[0080] like Figure 1 and Figure 7 As shown, in this embodiment, an outer baffle 123 is provided on the axial hub wall 122 of the outer hub 12. A plurality of second mounting keys, equidistantly spaced axially, are formed between the outer baffle 123 and the piston 13. The first friction plates 141-1 are mounted one-to-one on the second mounting keys, and the outer elastic member 141-2 elastically abuts axially between adjacent first friction plates 141-1. The positional constraints imposed by the piston 13 and the outer baffle 123, as well as the positional constraints imposed by the second mounting keys on each first friction plate 141-1, ensure that each first friction plate 141-1 is positioned relative to the outer hub 12.

[0081] After the clutch is assembled, the outer hub 12 and the inner hub 11 are fixed relative to the main shaft 2. The mounting keys on the inner hub 11 and the outer hub 12, as well as the retaining plate, also determine the position of the second friction plate 142-1 and the first friction plate 141-1. The relative position of the second friction plate 142-1 and the first friction plate 141-1 is fixed, and the gap between the second friction plate 142-1 and the first friction plate 141-1 is maintained by a reset member. This ensures that each time the friction plate pack 14 is disengaged, the second friction plate 142-1 is accurately reset to a fully disengaged position under the action of the internal elastic member 142-2.

[0082] like Figure 6 As shown, in this embodiment, the axial spacing between any adjacent first friction plates 141-1 and second friction plates 142-1 is equal. The thickness of the first friction plate 141-1 is λ1, and the thickness of the second friction plate 142-1 is λ2. After the first plate group 141 and the second plate group 142 are installed, the gap between two adjacent first friction plates 141-1 is Δ1, and the gap between two adjacent second friction plates 142-1 is Δ2. To ensure equal spacing, the installation relationship must ensure that (Δ1-λ2) / 2=(Δ2-λ1) / 2=δ.

[0083] The present invention also discloses a working machine, wherein the working machine includes the wet clutch described above. Since the working machine adopts all the technical solutions of the above embodiments, it has at least the beneficial effects brought by the above embodiments, which will not be repeated here.

[0084] In the description of the present invention, it should be understood that the terms "first" and "second" are used for descriptive purposes only and should not be understood to indicate or imply relative importance or implicitly specify the number of the technical features indicated. Therefore, a feature defined as "first" or "second" may explicitly or implicitly include at least one of such features. In the description of the present invention, "plurality" means at least two, for example, two, three, etc., unless otherwise specifically defined.

[0085] In the present invention, unless otherwise specified or limited, the terms "installed," "connected," "connect," "fixed," etc. should be understood in a broad sense. For example, they can refer to fixed connection, detachable connection, or integration; mechanical connection, electrical connection, or communication; direct connection or indirect connection through an intermediate medium; internal communication between two elements or interaction between two elements, unless otherwise specified. Those skilled in the art will understand the specific meanings of the above terms in the present invention based on specific circumstances.

[0086] In the description of this specification, the reference terms "one embodiment", "some embodiments", "example", "specific example", or "some examples" mean that the specific features, structures, materials or characteristics described in conjunction with the embodiment or example are included in at least one embodiment or example of the present invention. In this specification, the schematic representations of the above terms do not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described can be combined in any one or more embodiments or examples in a suitable manner. In addition, those skilled in the art can combine and combine different embodiments or examples described in this specification and features of different embodiments or examples without contradiction.

[0087] Although the embodiments of the present invention have been described above, it is understood that the above embodiments are illustrative and are not to be construed as limitations on the present invention. A person skilled in the art may change, modify, replace and modify the above embodiments within the scope of the present invention.

Claims

1. A wet clutch, characterized in that: The wet clutch comprises: The transmission hub frame comprises an inner hub (11) and an outer hub (12) arranged radially at intervals, wherein a piston (13) and a friction plate group (14) arranged in the axial direction are provided between the inner hub (11) and the outer hub (12); A main shaft (2) serves as the central axis of the transmission hub frame and is formed with an axially extending hollow oil passage (2a). The hollow oil passage (2a) is further provided with an axially spaced bypass working oil passage (2b) and a bypass lubricating oil passage (2c). The bypass working oil passage (2b) is used to communicate with the driving chamber (1a) of the piston (13), and the bypass lubricating oil passage (2c) is used to communicate with the installation chamber (1b) of the friction plate group (14). The control device (3) is used to control the conduction or cutoff of the hollow oil passage (2a) between the bypass working oil passage (2b) and the bypass lubricating oil passage (2c).

2. The wet clutch according to claim 1, characterized in that: One end of the hollow oil passage (2a) is provided with an oil inlet (2a-1), and the other end is a plugging end. The bypass working oil passage (2b) is arranged closer to the oil inlet (2a-1) than the bypass lubricating oil passage (2c).

3. The wet clutch according to claim 1, characterized in that: The control device (3) is arranged in the hollow oil passage (2a) between the bypass working oil passage (2b) and the bypass lubricating oil passage (2c); the control device (3) is a normally closed device and opens the hollow oil passage (2a) only when the working oil pressure of the bypass working oil passage (2b) reaches a set opening oil pressure value.

4. The wet clutch according to claim 3, characterized in that: The control device (3) is an overflow valve or a back pressure check valve arranged in the hollow oil passage (2a) between the bypass working oil passage (2b) and the bypass lubricating oil passage (2c).

5. The wet clutch according to claim 3, characterized in that: The control device (3) is an oil plug assembly, which includes a plunger (31) and a plunger elastic member (32). The plunger (31) is axially arranged and disposed in a hollow oil passage (2a) between the bypass working oil passage (2b) and the bypass lubricating oil passage (2c). One end of the plunger elastic member (32) is fixed, and the other end elastically presses against the plunger (31). The oil input into the hollow oil passage (2a) can drive the plunger (31) to move axially to connect the bypass working oil passage (2b) and the bypass lubricating oil passage (2c).

6. The wet clutch according to claim 5, characterized in that: The oil plug assembly further comprises a plunger adjustment member (33) for adjusting the axial position of the plunger (31).

7. The wet clutch according to any one of claims 1 to 6, characterized in that: The wet clutch comprises: An oil drain passage (12a) is provided on the outer hub (12) and communicates with the radially outer side of the drive chamber (1a).

8. The wet clutch according to claim 7, characterized in that: The wet clutch comprises: The plug assembly (4) is a normally open device and closes the oil drain passage (12a) only when the working oil pressure of the drive chamber (1a) reaches a set closing oil pressure value.

9. The wet clutch according to claim 8, characterized in that: The oil leakage passage (12a) comprises an axial oil leakage passage (12a-2) and a radial oil leakage passage (12a-1); the plug assembly (4) is arranged in the axial oil leakage passage (12a-2) and comprises an oil leakage plug (41) and an oil leakage elastic member (42); the oil leakage plug (41) is provided with an axially arranged plug inner oil passage (411) and a radial oil guide groove (412) extending from the peripheral wall of the plug inner oil passage (411); the working oil in the drive chamber (1a) can drive the oil leakage plug (41) to move axially to control the radial alignment of the radial oil guide groove (412) and the radial oil leakage passage (12a-1).

10. The wet clutch according to claim 9, characterized in that: The outer hub (12) comprises a radial hub wall (121) extending radially inwardly to the main shaft (2), and the oil drain passage (12a) is provided at a radial outer end of the radial hub wall (121); A first drive chamber and a second drive chamber are respectively provided on both sides of the radial hub wall (121), the axial oil drain passage (12a-2) connects the first drive chamber and the second drive chamber, and the plug inner oil passage (411) axially penetrates the oil drain plug (41).

11. The wet clutch according to claim 9, characterized in that: The oil passage (411) in the plug is a throttling passage.

12. The wet clutch according to any one of claims 1 to 6, characterized in that: The friction plate group (14) includes a first plate group (141) arranged on the outer hub (12) and a second plate group (142) arranged on the inner hub (11), an outer elastic member (141-2) for elastically stretching apart in the axial direction is provided between the friction plates of the first plate group (141), and an inner elastic member (142-2) for elastically stretching apart in the axial direction is provided between the friction plates of the second plate group (142), the friction plates of the first plate group (141) and the friction plates of the second plate group (142) are interdigitated and alternately distributed, and the piston (13) is used to move axially to push the first plate group (141) and the second plate group (142) in the friction plate group (14) to engage.

13. The wet clutch according to claim 12, characterized in that: The first plate group (141) comprises a plurality of first friction plates (141-1) extending radially and sequentially spaced axially, a first spacing slot being formed between any adjacent first friction plates (141-1), and an outer elastic member (141-2) for axially spreading adjacent first friction plates (141-1) being provided in the first spacing slot; The second plate group (142) includes a plurality of second friction plates (142-1) extending radially and sequentially spaced axially, a second spacing slot is formed between any adjacent second friction plates (142-1), and an inner elastic member (142-2) is provided in the second spacing slot for axially spreading the adjacent second friction plates (142-1); Wherein, a plurality of the first friction plates (141-1) and a plurality of the second friction plates (142-1) are interdigitated and alternately distributed.

14. The wet clutch according to claim 13, characterized in that: The axial spacing between any adjacent first friction plates (141-1) and second friction plates (142-1) is equal.

15. A working machine, characterized in that: Comprising a wet clutch according to any one of claims 1 to 14.

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