CN218000207U - Hydraulic pump type clutch - Google Patents

Abstract

The utility model relates to a hydraulic pump formula clutch, including casing assembly, intermeshing's drive gear and driven gear. Hydraulic fluid is sealed within the housing assembly, and the driven gear is disposed on the housing assembly and is capable of rotating relative to the housing assembly. The shell assembly and the driving gear form a power input unit connected with the engine and a power output unit connected with the gearbox. The shell assembly comprises a separating body, the inner side of the separating body is in contact with the driving gear and the driven gear to form an inner side sealing cavity, and the outer side of the separating body forms an outer side sealing cavity. The flow regulating component is arranged on the separating body. The utility model has the advantages of simple structure, the separation and reunion is fast, and it is less to generate heat, easy operation, and the separation and reunion degree is controlled easily. The combined or separated state of the clutch can be controlled by controlling the flow regulating component, and when the flow regulating component is not completely closed, the engine is separated from or partially connected with the gearbox. When the flow regulating assembly is fully closed, the engine is fully connected to the transmission.

Description

Hydraulic pump type clutch

Technical Field

The utility model belongs to the technical field of automobile clutch, concretely relates to hydraulic pump formula clutch.

Background

The clutch is installed between the engine and the transmission of the automobile, and is usually installed together with the flywheel set of the crankshaft of the engine and is a part for cutting off and transmitting power between the engine and the transmission of the automobile. During the whole process of starting the automobile to run normally or shifting gears, the driver can operate the clutch according to the requirement to ensure that the engine and the transmission are temporarily separated or gradually connected so as to cut off or transmit the power output from the engine to the transmission.

Therefore, the clutch has the following functions: firstly, the gradual connection between the engine and the transmission can be realized, thereby ensuring the smooth starting of the automobile. Secondly, the connection between the engine and the transmission is temporarily cut off to facilitate the gear change. In addition, the separating action of the clutch can prevent the transmission device such as a speed changer from overloading when the automobile is braked suddenly.

Clutches commonly used in the prior art include friction plate clutches and torque converters, however, both of these clutches have their own disadvantages. In particular, the friction plate clutch is liable to generate heat, and the engagement point is difficult to grasp, and the moment of engagement is liable to be jerked. Torque converters transmit torque by means of fluid, and have the disadvantage of low efficiency due to a difference in rotational speed.

Accordingly, there is a need to provide a clutch that is more stable in performance and easier to operate.

SUMMERY OF THE UTILITY MODEL

Technical problem to be solved

In order to solve the clutch that exists among the prior art and generate heat easily, skid, the joint is difficult to hold, is difficult to the problem of operation, the utility model provides a fluid pressure type clutch.

(II) technical scheme

In order to achieve the above object, the utility model discloses a main technical scheme include:

a hydraulic pump clutch includes a housing assembly, and a drive gear and a driven gear that mesh with each other; the housing assembly is internally sealed with hydraulic fluid, and the driven gear is arranged on the housing assembly and can rotate relative to the housing assembly;

one of the shell assembly and the driving gear is a power input unit, and the other one of the shell assembly and the driving gear is a power output unit;

the power input unit is connected with an engine, and the power output unit is connected with a gearbox;

the shell component comprises a separating body, the inner side arc surface of the separating body is an arc surface and is in circular contact with the outlines of the driving gear and the driven gear to form an inner side sealing cavity; the outer side of the separator forms an outer sealed cavity; the inner side sealing cavity and the outer side sealing cavity are respectively positioned on two sides of the meshing position of the driving gear and the driven gear;

a flow regulating component is arranged on the separating body;

when the flow regulating assembly is not completely closed, the power input unit drives the driving gear and the driven gear to rotate and pump out the hydraulic fluid, so that the hydraulic fluid between the inner sealing cavity and the outer sealing cavity flows through the flow regulating assembly for circulation, and the driving gear and the shell assembly are in a non-synchronous rotating state;

when the flow regulating assembly is completely closed, the flow circulation of hydraulic fluid between the inner side sealing cavity and the outer side sealing cavity is blocked, the driving gear and the driven gear are forced to be seized due to the fact that hydraulic pressure cannot relatively rotate, and the shell assembly, the driving gear and the driven gear are in a synchronous rotating state.

In the hydraulic pump clutch as described above, it is preferable that 2 or more driven gears are provided, distributed around the drive gear, and engaged with the drive gear.

The hydraulic pump clutch as described above, preferably, the number of the division bodies is the same as the number of the driven gears;

the inner side circular arc surface of the separating body, the driven gear and the driving gear form an inner side sealing cavity, and the outer side surface of the separating body forms an outer side sealing cavity.

The hydraulic pump clutch as described above, preferably, the flow regulating assembly includes flow regulating valves respectively disposed on the plurality of separators, and a first oil port and a second oil port are respectively disposed on two sides of the flow regulating valve;

the first oil port faces the inner side sealing cavity, and the second oil port faces the outer side sealing cavity.

The hydraulic pump clutch as described above, preferably, the flow regulating assembly includes a flow regulating valve; the flow regulating valve is disposed on only one of the plurality of separators; the flow control valve is characterized in that a first oil port and a second oil port are respectively arranged on two sides of the flow control valve, the first oil port faces to the inner side sealing cavity, and the second oil port faces to the outer side sealing cavity.

In the hydraulic pump clutch described above, preferably, the plurality of inner seal cavities are communicated with each other through inner pipes;

the plurality of outer side sealing cavities are communicated through outer side pipelines respectively.

In the hydraulic pump clutch described above, preferably, the inner pipe and the outer pipe are both provided outside the housing assembly.

The hydraulic pump type clutch as described above, preferably, the housing assembly further includes a cylindrical sealing housing, and a driven gear shaft perpendicular to and fixedly connected to the housing;

the shell comprises 2 circular end covers and a circumferential main body, and the separating body is connected with the main body and is in sealing connection with the 2 circular end covers; the 2 circular end covers respectively clamp the driving gear and the driven gear to provide axial sealing;

two ends of the driven gear shaft are respectively and fixedly connected with the 2 circular end covers in a vertical manner;

the driven gear is arranged on the driven gear shaft and can rotate along the driven gear shaft;

the inner side pipeline and the outer side pipeline are arranged outside the round surface end cover.

The hydraulic pump type clutch as described above, preferably, the flow regulating assembly further includes an operating lever, a pressure plate, a pressure spring, a release bearing, and a shift fork;

the flow regulating valve is connected with the operating rod, and the pressure plate is connected with the other end of the operating rod; the pressure spring is arranged between the shell assembly and the pressure plate;

the release bearing is arranged on one side, away from the shell assembly, of the pressure plate, and the shifting fork is arranged on the release bearing.

(III) advantageous effects

The utility model has the advantages that:

the utility model discloses be applied to the clutch with the theory of operation of hydraulic pump, set up the drive gear and the casing subassembly of hydraulic pump, especially gear pump into power input unit and power take off unit, set up the flow control subassembly on the endless liquid route in casing subassembly, through the resistance of the on-off degree control hydraulic fluid of control flow control subassembly to make relative motion resistance change between drive gear and the casing subassembly, play the effect of separation and reunion. When the flow regulating assembly is not completely closed, the oil pumped out by the gear pump flows through the flow regulating assembly from the sealing cavity on one side to the sealing cavity on the other side, the clutch plays a role in separation, the engine is separated from or partially connected with the gearbox, when the flow regulating assembly is completely closed, the oil pumped out by the gear pump is blocked and cannot reach the sealing cavity on the other side from the sealing cavity on one side, so that the driving gear and the driven gear cannot rotate relative to each other due to the fact that the pressure is locked, and the engine is completely connected with the gearbox through the clutch.

Utility model's using-way is nimble, and drive gear and housing assembly can both be connected with the engine as power input unit to simple structure, each part is very in the same direction as smooth in the course of the work. The clutch degree of the clutch can be controlled by controlling the on-off degree of the flow regulating assembly, a user can operate and master the clutch degree conveniently, controllability is high, clutch speed is high, heat is less, and transmission efficiency is high.

Drawings

Fig. 1 is an overall schematic diagram of a hydraulic pump clutch according to the present invention;

fig. 2 is a schematic structural view of a hydraulic pump clutch in embodiment 1;

FIG. 3 is a schematic structural view of the hydraulic pump clutch according to embodiment 1 at another angle;

fig. 4 is a schematic structural view of the hydraulic pump clutch according to embodiment 1 at a further angle;

fig. 5 is a schematic internal structure diagram of the hydraulic pump clutch in embodiment 2;

fig. 6 is a schematic view of the overall structure of the hydraulic pump clutch according to embodiment 2.

[ description of reference ]

1: a drive gear; 2: a driven gear; 3: a hydraulic fluid; 4: a separator;

21: a first driven gear; 22: a second driven gear; 23: a third driven gear;

41: a first separator; 42: a second separator; 43: a third separator; 44: a housing; 441: an end cap; 442: a main body; 45: a driven gear shaft;

5: a first inboard sealed chamber; 6: a first outboard sealed cavity; 7: a second inboard sealed chamber; 8: a second outboard sealed cavity; 9: a third inboard sealed chamber; 10: a third outboard sealed cavity; 11: a flow regulating valve; 12: a first oil port; 13: a second oil port; 14: a first inner pipe; 15: a second inner pipe; 16: a first outboard duct; 17: a second outboard duct; 18: a locking groove;

19: an operating lever; 20: a platen; 24: a pressure spring; 25: a shifting fork; 26: a flow regulating valve mounting position; 27: and separating the bearing.

Detailed Description

For a better understanding of the present invention, reference will now be made in detail to the present invention, examples of which are illustrated in the accompanying drawings.

As shown in fig. 1 to 6, the present invention provides a hydraulic pump type clutch, which includes a housing assembly, and a driving gear 1 and a driven gear 2 that are engaged with each other. Hydraulic fluid 3 is sealed within the housing assembly and a driven gear 2 is disposed on and rotatable relative to the housing assembly. The hydraulic pump of various structures can be adopted to hydraulic pump formula clutch, can be gear pump, plunger pump or screw pump etc. the utility model discloses use the gear pump to carry out concrete structural design and explanation as the example.

One of the housing assembly and the drive gear 1 is a power input unit, and the other is a power output unit. Specifically, the power input unit is connected with the engine, and the power output unit is connected with the gearbox.

The shell component comprises a separating body 4, the inner circular arc surface of the separating body 4 is closely contacted with the driving gear 1 and the driven gear 2 to form an inner sealing cavity, and the outer side of the separating body forms an outer sealing cavity. A flow regulating assembly is arranged on the separating body 4.

When the flow regulating assembly is fully opened or partially opened, namely in a non-fully closed state, the power input unit drives the driving gear 1 and the driven gear 2 which are meshed with each other to rotate under the power of the engine.

If the power input unit is the driving gear 1, the driving gear 1 drives the driven gear 2 to rotate, and due to the meshing relationship, the driven gear 2 and the driving gear 1 rotate in opposite directions, and the hydraulic fluid 3 having the characteristic of not being compressed continuously circulates between the inner seal cavity and the outer seal cavity under the squeezing action of the driving gear 1 and the driven gear 2. Assuming that the flow control valve is fully opened at this time, in an ideal state, the circulation of the hydraulic fluid between the inner seal cavity and the outer seal cavity has substantially no resistance, and can be regarded as that the gear pump smoothly pumps out the oil, and at this time, the driving gear 1 and the driven gear 2 are smoothly meshed and rotated, so that the mutual rotation between the driving shaft and the housing is smooth, and no large torque is transmitted.

When the flow regulating assembly is in a partially opened state, the circulating flow of the hydraulic fluid between the inner side sealing cavity and the outer side sealing cavity is limited by the flow regulating assembly, and the hydraulic fluid at the moment is not as smooth as the flow regulating assembly when passing through the flow regulating assembly when being fully opened, but can still pass through the flow regulating assembly. However, because of the resistance of the hydraulic fluid passing through the flow regulating assembly, the pressure of the hydraulic fluid inside one of the inner seal chamber and the outer seal chamber is high (the specific high pressure chamber needs to be determined according to the rotation direction of the driving gear), and the meshing reverse rotation between the driven gear 2 and the driving gear 1 is hindered. It can be seen that the pumping movement of the oil pump becomes difficult, in particular: relative rotation between the drive shaft and the housing becomes difficult, and torque transmission occurs between the drive shaft and the housing, and one of them rotates at a relatively slow rotation speed following the other, which corresponds to a state in which the clutch is in a semi-interlocked state. Along with the opening degree of flow control subassembly is littleer and smaller, and one side sealed intracavity oil hydraulic pressure is bigger and bigger, and the reverse meshing rotation of driven gear 2 relative drive gear 1 is more and more difficult, shows that it is more and more difficult relative rotation each other between casing and the drive shaft, and one side drives the other side and rotates in the syntropy and both rotational speed are more and more close.

In the above case, the transmission of power proceeds as follows: the torque of the driving gear is transmitted to the housing through the shaft of the driven gear when the relative meshing rotation between the driving gear and the driven gear becomes difficult.

If the power input unit is a shell assembly, a driven gear shaft on the shell assembly drives the driven gear to revolve along the driving gear, and meanwhile, the driven gear can rotate around the shaft of the driven gear because the driven gear is meshed with the driving gear.

When the flow regulating assembly is completely opened, under an ideal state, the gear pump formed by the gear pair pumps oil out from the sealed cavity on one side, the oil smoothly flows through the flow regulating assembly to the sealed cavity on the other side and returns to the suction side of the gear pump to form circulation, the driven gear 2 smoothly rotates to rotate without transmitting torque, the shell assembly rotates around the driving gear 1 as a whole, and the driving gear 1 does not rotate along with the shell.

When the flow regulating assembly is in a partially opened state, the circulating flow of the hydraulic fluid between the inner side sealing cavity and the outer side sealing cavity is limited by the flow regulating assembly, and the hydraulic fluid at the moment is not as smooth as the flow regulating assembly when passing through the flow regulating assembly when being fully opened, but can still pass through the flow regulating assembly. However, because the hydraulic fluid has resistance when passing through the flow rate adjusting assembly, the pressure of the hydraulic fluid inside one of the inner side sealed cavity or the outer side sealed cavity is high (the specific high pressure cavity needs to be determined according to the rotation direction of the driving gear), the gear pump cannot smoothly pump the oil, and the rotation of the driven gear 2 is blocked, so that the gear and the gear shaft gradually tend to be rigidly coupled, the gear shaft drives the driven gear to generate torque in the revolution direction, the driving gear 1 is driven to rotate in the same direction, and the rotation of the driven gear is more difficult as the opening degree of the flow rate adjusting assembly is smaller and smaller, the ratio of the torque of the rotation to be converted into the revolution is larger, and the rotation speed of the driving gear 1 is closer to the rotation speed of the driven gear 2. The gear pump is characterized in that the gear pump is more difficult to pump oil and the relative rotation between the shell and the driving gear is more difficult as the flow regulating assembly is increasingly limited to flow, so that the torque coupling degree is higher and higher, and the power transmission is in a semi-linkage state.

In the above case, the transmission of power proceeds as follows: the smaller the opening degree of the flow regulating assembly is, the less the part of power for extruding the hydraulic fluid is, and the more the part for driving the driving gear is. Therefore, when the flow regulating assembly is in a non-complete closing state, the driving gear 1 and the housing assembly are always in a same-direction but non-synchronous rotation state, and the engine and the gearbox are in a separated or partially connected state.

The hydraulic pump produces relative displacement motion between the pump body and moving part and makes pressure volume produce the change and pump out liquid, the utility model discloses be applied to the clutch with the theory of operation of hydraulic pump, set up the hydraulic pump, especially the drive gear and the casing subassembly of gear pump into power input unit and power output unit, set up the flow control subassembly on the liquid route of the circulation in the casing subassembly, only need through adjusting the difficult and easy degree of flow control subassembly control hydraulic fluid, flow and pressure between the inside and outside sealed chamber of hydraulic fluid promptly, can control the clutch degree of hydraulic pump formula clutch.

Utility model's using-way is nimble, and drive gear and housing assembly can both be connected with the engine as power input unit to simple structure, each part is very in the same direction as smooth in the course of the work. The clutch degree of the clutch can be controlled by controlling the on-off degree of the flow regulating assembly, a user can operate and master the clutch degree conveniently, controllability is high, clutch speed is high, heat is less, and transmission efficiency is high.

Example 1

As shown in fig. 2 to 4, the present embodiment provides a hydraulic pump clutch including a housing assembly, and a driving gear 1 and a driven gear 2 that mesh with each other. The shell assembly is internally sealed with hydraulic fluid 3, and the driving gear 1 and the driven gear 2 are wholly immersed in the hydraulic fluid 3. The driven gear 2 is provided on the housing assembly and is rotatable relative to the housing assembly. In the present embodiment, the hydraulic fluid 3 is hydraulic oil that is not compressible.

As shown in fig. 3 to 4, the housing assembly includes a cylindrical seal housing 44, a driven gear shaft 45, and a partition body 4. The housing 44 includes 2 circular end caps 441 and a circumferential main body 442 (the other end cap is not temporarily shown in fig. 3 and 4), two ends of the driven gear shaft 45 are perpendicular to and connected to the 2 circular end caps 441, and the driven gear 2 is disposed on the driven gear shaft 45 and can rotate around the driven gear shaft 45 or rotate together with the housing assembly under the driving of the driven gear shaft 45. A partition body 4 is provided inside the housing 44 and is integrally formed with the main body 442, the partition body 4 being in sealing connection with 2 circular end caps 441, the 2 circular end caps 441 sandwiching the driving gear and the driven gear, respectively, to provide axial sealing. In this embodiment, the partition body 4 extends toward the drive gear 1, an inner end face of the partition body 4 contacts the drive gear 1 and the driven gear 2, and an outer end face thereof faces the housing 44. Specifically, the inner side of the partition body 4 forms an inner side sealed cavity with the 2 end caps 441, the driving gear 1 and the driven gear 2, and the outer side of the partition body 4 forms an outer side sealed cavity with the housing 44, the driving gear 1 and the driven gear 2, and the inner side sealed cavity and the outer side sealed cavity are sealed spaces.

This embodiment uses the gear pump structure as the clutch, but the gear pump is at the rotation in-process, and hydraulic oil can produce certain pulsation, consequently, if regard the gear pump structure as clutch direct application on the car, then can have some slight vibrations at the clutch operation in-process for the travelling comfort is not good. In order to eliminate the pulsation generated in the flowing process of the hydraulic fluid and enable the clutch to be more stable, a plurality of driven gears meshed with the driving gear can be arranged in the embodiment, and the arrangement of a plurality of gear pump structures is equal to that of the pulsation generated in the flowing process of the hydraulic oil, so that the running stability of the clutch is improved.

Specifically, the driven gear 2 includes a first driven gear 21, a second driven gear 22, and a third driven gear 23, and the first driven gear 21, the second driven gear 22, and the third driven gear 23 are identical in size and number of teeth and are uniformly distributed outside the driving gear 1.

The partition bodies 4 include identical first partition bodies 41, second partition bodies 42, and third partition bodies 43 corresponding to the driven gears, the first partition bodies 41, the second partition bodies 42, and the third partition bodies 43 are alternately arranged, inner end surfaces thereof are respectively closely attached to the driving gear 1 and the driven gears in a one-to-one correspondence, and outer end surfaces thereof face the housing 44.

The inner end surface of the first separator 41 forms a first inner sealed chamber 5 with the 2 end caps 441, the first driven gear 21, and the drive gear 1, and the outer end surface of the first separator 41 forms a first outer sealed chamber 6 with the housing 44, the drive gear, and the first driven gear 21. The inner end surface of the second partition body 42 forms a second inner hermetic chamber 7 with the 2 end caps 441, the second driven gear 22, and the driving gear 1, and the outer end surface thereof forms a second outer hermetic chamber 8 with the housing 44, the driving gear 1, and the second driven gear 22. The inner circular arc surface of the third partitioning body 43 forms a third inner seal cavity 9 with the 2 end caps 441, the third driven gear 23, and the drive gear 1, and the outer end surface thereof forms a third outer seal cavity 10 with the housing 44, the drive gear 1, and the third driven gear 23. All the inner measuring sealing cavities and the outer side sealing cavities are sealing cavities.

The flow regulating assembly comprises a flow regulating valve 11 respectively arranged on a first separating body 41, a second separating body 42 and a third separating body 43, wherein a first oil port 12 and a second oil port 13 are respectively arranged on two sides of the flow regulating valve 11, the first oil port 12 faces to the inner side sealed cavity, and the second oil port 13 faces to the outer side sealed cavity.

In this embodiment, the drive gear 1 is connected to the engine as a power input unit, the housing assembly is connected to the transmission as a power output unit, and it is assumed that the drive gear 1 rotates in the clockwise direction. The following describes the clutch principle of the hydraulic pump clutch:

the flow regulating valves 11 on the separating bodies are opened, the driving gear 1 rotates clockwise to drive the 3 driven gears meshed with the driving gear to rotate anticlockwise, and the hydraulic oil is continuously extruded by the tooth tips on the driving gear and the driven gears. Taking the first inner side sealing cavity 5 as an example, the hydraulic oil between the tooth tips of the driving gear 1 and the first driven gear 21 is squeezed into the first inner side sealing cavity 5, at this time, the first inner side sealing cavity 5 is a high pressure cavity, the third outer side sealing cavity 10 is a low pressure cavity, along with the continuous rotation of the gears, part of the hydraulic oil in the first inner side sealing cavity 5 passes through the flow regulating valve 11 through the first oil port 12, and then is squeezed into the first outer side sealing cavity 6 through the second oil port 12, and the first outer side sealing cavity 6 is a low pressure cavity. Similarly, the hydraulic oil is squeezed into the second inner side seal chamber 7, then reaches the second outer side seal chamber 8 through the next set of flow control valve, is squeezed into the third inner side seal chamber 9 by the gear, then reaches the third outer side seal chamber 10 through the next set of flow control valve, and repeatedly passes through the above-mentioned circulation flow path. In the process of the circular flow of the hydraulic oil, the hydraulic oil is pressed into the first inner side sealing cavity 5, the second inner side sealing cavity 7 and the third inner side sealing cavity 9, and the hydraulic oil belongs to a high-pressure cavity; the hydraulic oil in the first outer side sealing cavity 6, the second outer side sealing cavity 8 and the third outer side sealing cavity 10 is extruded out and belongs to a low-pressure cavity; the first oil port 12 facing the inner side sealing cavity is an oil inlet, and the second oil port 13 facing the outer side sealing cavity is an oil outlet.

When the flow regulating valve is completely closed, the driven gear 2 and the driving gear 1 rotate synchronously, and the clutch completely connects the engine and the gearbox. When the flow regulating valve is fully opened, a certain flow resistance of hydraulic oil still exists, so that a certain degree of relative movement still exists between the driven gear 2 and the driving gear 1, only the reverse meshing rotating speed of the driven gear 2 relative to the driving gear 1 is maximum in the state, but the whole body can rotate along the same direction of the driving gear 1 along with the shell assembly, and the connection degree of the clutch is minimum at the moment. When the flow rate adjustment valve 11 is in the partially open state, the circulation flow of the hydraulic oil is restricted by the flow rate adjustment valve, which results in a high pressure of the hydraulic oil in the inside seal chamber, thereby hindering the meshing reverse rotation between the driven gear 2 and the drive gear 1. Specifically, the reverse meshing rotational movement of the driven gear 2 with respect to the drive gear 1 is hindered, so that the reverse meshing rotational movement of the driven gear 2 with respect to the drive gear 1 becomes difficult, the reverse meshing rotational speed of the driven gear 2 with respect to the drive gear 1 becomes slow, and the driven gear 2 also rotates along the drive gear 1 following the entire housing assembly, in the same rotational direction as the drive gear 1, but at a lower rotational speed than the drive gear 1. As the opening degree of the flow rate regulating valve becomes smaller, the reverse meshing rotational speed of the driven gear 2 with respect to the driving gear 1 becomes smaller, and the rotational speed in the same direction as the housing assembly as a whole but at a different speed along the driving gear 1 becomes faster and faster. Conversely, as the opening degree of the flow control valve is increased, the counter-meshing rotational speed of the driven gear 2 with respect to the driving gear 1 is increased, and the rotational speed in the same direction as the housing assembly as a whole along the driving gear 1 but at a different speed is decreased. Therefore, the degree of clutch engagement can be changed by changing the degree of opening of the regulating flow rate regulating valve.

The flow regulating valves 11 on the separating bodies are completely closed, and due to the characteristic that the hydraulic fluid 3 is not compressed, the hydraulic fluid in all the inner side sealed cavities and the hydraulic fluid in all the outer side sealed cavities stop flowing and circulating, the relative motion between the driving gear 1 and the driven gear 2 stops, and the driven gear 2 completely matches with the motion of the driving gear 1 to drive the shell assembly to synchronously rotate with the driving gear 1, so that the engine and the gearbox are completely connected.

When the driving gear 1 rotates along the anticlockwise direction, the low-pressure cavity and the high-pressure cavity are exchanged, and the oil inlet and the oil outlet are exchanged.

In this embodiment, the sealing performance of the gear pump cannot be absolutely ensured, and although the contact surfaces of the driven gear 2 and the partition body 4 are in a tight sealing state, a slight gap is inevitably formed. Therefore, in the actual operation process, after the flow control valve 11 is completely closed for a period of time, some Xu Shenlou of hydraulic oil can appear, and the hydraulic oil flows from the high-pressure cavity to the low-pressure cavity, so that the pressure of the hydraulic oil in the high-pressure cavity is insufficient, and the driving gear 1 and the driven gear 2 can rotate relatively to destroy the complete connection state of the clutch. In order to solve the above problem, the present embodiment further provides a locking assembly including a locking groove 18 provided on one of the driven gears 2, and an elastic plunger provided on the housing 44, the elastic plunger being capable of expanding and contracting in the axial direction of the housing 44 to be inserted into the locking groove 18 or separated from the locking groove 18. When the elastic plunger piston is inserted into the locking groove 18, the driven gear 2 is locked with the shell assembly, and the transmission efficiency of the clutch is guaranteed to be hundred percent.

In addition, the temperature of the hydraulic oil rises during the continuous circulation flow, and therefore, the flow rate adjusting valve 11 in this embodiment needs to be a valve body insensitive to temperature.

Further, the present embodiment controls the degree of opening of the flow rate adjustment valve 11 by the expansion and contraction of the operation lever 19 on the flow rate adjustment valve 11. As shown in fig. 1, the installation direction of the operating rod 19 is parallel to the transmission shaft of the clutch, the pressure plate 20 is installed at the top end of the operating rod, the pressure spring 24 with pre-pressure is arranged between the pressure plate 20 and the housing 44, and the pressure spring 24 can push the pressure plate 20 away from the housing 44, so that the opening and closing degree of the flow regulating valve can be adjusted. Furthermore, a release bearing 27 is arranged on the outer side of the pressure plate 20, a shifting fork 25 is mounted on the release bearing 24, and the shifting fork 25 can enable the release bearing 24 to tightly press or release the pressure plate 27.

When the fork 25 presses the release bearing 27 toward the housing assembly, the release bearing 27 pushes the pressure plate 22 to move toward the housing assembly, and the pressure plate 22 pushes the operating rod 19 to contract inward. When the shifting fork 25 releases the release bearing 27 outwards, the pressure spring 24 pushes the pressure plate 20 to move outwards, and simultaneously pulls the operating rod 19 to extend outwards, so that the area of the internal channel of the flow regulating valve 11 is changed, the smooth degree of hydraulic oil circulation is changed, the coupling degree between the shell assembly and the driving gear is changed, and the effect of a clutch is achieved.

Example 2

The present embodiment is different from embodiment 1 in that the housing assembly is connected to the engine as a power input unit, and the drive gear 1 is connected to the transmission as a power output unit.

The clockwise shell assembly is taken as an example for explanation: opening flow control valve 11 on the partition body 4, the shell assembly can drive driven gear 2 to rotate synchronously under the action of the engine, hydraulic oil is continuously extruded by tooth tips on the driving gear and the driven gear, taking first outer side sealing cavity 6 as an example, hydraulic oil between tooth tips of driving gear 1 and first driven gear 21 is extruded into first outer side sealing cavity 6, at the moment, first outer side sealing cavity 6 is a high pressure cavity, and second inner side sealing cavity 7 is a low pressure cavity. In the process of the circular flow of the hydraulic oil, the hydraulic oil in the first inner side sealing cavity 5, the second inner side sealing cavity 7 and the third inner side sealing cavity 9 is extruded out and belongs to a low-pressure cavity; the hydraulic oil in the first outside seal cavity 6, the second outside seal cavity 8 and the third outside seal cavity 10 is pressed in, belongs to a high pressure cavity, and is opposite to the embodiment 1, the first oil port 12 is an oil outlet, and the second oil port 13 is an oil inlet.

When the flow regulating valve is fully opened, the driven gear 2 and the shell assembly rotate along the driving gear 1 as a whole, certain pressure still exists in hydraulic oil at the moment, only the pressure is minimum, the driving gear 1 can also be driven by the driven gear to rotate in the same direction, and only the rotating speed is in a minimum state, so that the separation degree of the engine and the gearbox is maximum.

When the flow regulating valve is completely closed, hydraulic fluid can not circularly flow through the flow regulating valve, the relative motion between the driving gear 1 and the driven gear 2 is stopped, the driving gear 1 and the driven gear 2 are connected in a rigid mode, the driving gear 1, the driven gear 2 and the shell assembly are quickly in a synchronous rotating state and have the same rotating speed, and therefore the complete connection of the engine and the gearbox is achieved.

When the flow control valve is in a partially open state, the circulating flow of the hydraulic fluid between the inner seal chamber and the outer seal chamber is restricted by the flow control valve, and the hydraulic fluid passing through the flow control valve is not as smooth as when the flow control valve is fully open, but can still pass through the flow control valve. However, since there is resistance when the hydraulic fluid passes through the flow rate control valve, the pressure of the hydraulic fluid inside the outer seal chamber is high, and the driven gear 2 rotates the drive gear 1 in the same direction, but the rotation speed of the drive gear 1 is lower than that of the driven gear 2. As the opening degree of the flow rate adjustment valve becomes smaller, the rotation speed of the drive gear 1 and the rotation speed of the driven gear 2 become closer to each other. Conversely, as the opening degree of the flow rate adjustment valve becomes larger, the difference between the rotation speed of the drive gear 1 and the rotation speed of the driven gear 2 becomes larger.

When the housing assembly and the driven gear 2 rotate in the counterclockwise direction, the low pressure chamber and the high pressure chamber are exchanged, and the oil inlet and the oil outlet are exchanged.

Example 3

As shown in fig. 5 to 6, the present embodiment provides a hydraulic pump clutch, which is different from embodiment 1 in that 1 flow rate adjustment valve is provided only on the first driven gear 21.

Similarly, a first oil port 12 and a second oil port 13 are respectively disposed on both sides of the flow control valve 11, the first oil port 12 faces the first inner sealed cavity 5, and the second oil port 13 faces the first outer sealed cavity 6.

The first inner sealed chamber 5 is communicated with the second inner sealed chamber 7 through a first inner pipeline 14, and the second inner sealed chamber 7 is communicated with the third inner sealed chamber 9 through a second inner pipeline 15. The first outside packing chamber 6 communicates with the second outside packing chamber 8 through a first outside duct 16, and the second outside packing chamber 8 communicates with the third outside packing chamber 10 through a second outside duct 17.

The first inner side sealed cavity 5, the second inner side sealed cavity 7 and the third inner side sealed cavity 9 are connected into a whole through a first inner side pipeline 14 and a second inner side pipeline 15, and hydraulic oil can circulate in the first inner side sealed cavity, the second inner side sealed cavity and the third inner side sealed cavity. The inner side sealing cavity is communicated with the first oil port of the flow regulating valve, and hydraulic oil in the inner side sealing cavity can flow through the flow regulating valve through the first oil port.

The first outer side sealing cavity 6, the second outer side sealing cavity 8 and the third outer side sealing cavity 10 are connected into a whole through a first outer side pipeline 16 and a second outer side pipeline 17, the outer side sealing cavities are communicated with a second oil port of the flow regulating valve, and hydraulic oil in the outer side sealing cavities can flow through the flow regulating valve through the second oil port.

The first inner duct 14, the second inner duct 15, the first outer duct 16, and the second outer duct 17 may be provided on the end cover 441 of the housing assembly or may be provided on the body 442. As long as all the inside seal cavities can be communicated with each other, all the outside seal cavities can be communicated with each other, and the inside seal cavities and the outside seal cavities are isolated from each other.

As in embodiments 1 and 2, the inside seal chamber and the outside seal chamber are high-pressure chambers or low-pressure chambers depending on the power input unit and the rotational directions of the power input unit that are different between clockwise and counterclockwise.

All high-pressure hydraulic oil in the high-pressure cavity in this embodiment flows back to all low-pressure cavities after passing through the flow control valve, and only one flow control valve needs to be arranged in the whole clutch, so that the cost can be effectively saved. In addition, this embodiment only sets up 1 flow control valve and controls the flow of hydraulic oil, makes the hydraulic oil circulation between each sealed chamber through setting up the pipeline simultaneously, can also weaken the pulsation that causes in every gear pump rotation process.

The above embodiments are only used for explaining the present invention, and do not constitute a limitation to the scope of the present invention, and those skilled in the art may make various modifications or changes within the scope of the claims, all of which belong to the essence of the present invention.

Claims (9)

1. A hydraulic pump clutch, characterized by comprising a housing assembly, and a driving gear (1) and a driven gear (2) which are meshed with each other; the housing assembly is internally sealed with hydraulic fluid (3), and the driven gear (2) is arranged on the housing assembly and can rotate relative to the housing assembly;

one of the shell assembly and the driving gear (1) is a power input unit, and the other one is a power output unit;

the power input unit is connected with the engine, and the power output unit is connected with the gearbox;

the shell component comprises a separating body (4), the inner side arc surface of the separating body (4) is an arc surface and is in contact with the outer circles of the tooth profiles of the driving gear (1) and the driven gear (2) to form an inner side sealing cavity; the outside of the separator (4) forms an outside sealed cavity; the inner side sealing cavity and the outer side sealing cavity are respectively positioned on two sides of the meshing position of the driving gear and the driven gear;

a flow regulating component is arranged on the separating body (4);

when the flow regulating assembly is not completely closed, the power input unit drives the driving gear (1) and the driven gear (2) to rotate and pump out the hydraulic fluid (3), so that the hydraulic fluid between the inner sealed cavity and the outer sealed cavity flows through the flow regulating assembly for circulation, and the driving gear (1) and the shell assembly are in a non-synchronous rotating state;

when the flow regulating assembly is completely closed, the flowing circulation of hydraulic fluid between the inner side sealing cavity and the outer side sealing cavity is blocked, the driving gear (1) and the driven gear (2) are forced to rotate relatively due to hydraulic pressure, so that the driving gear and the driven gear (2) are seized, and the shell assembly, the driving gear (1) and the driven gear (2) are in a synchronous rotating state.

2. The hydraulic pump clutch as claimed in claim 1, characterized in that the driven gear (2) is provided in 2 or more, distributed around the drive gear (1) and in mesh with the drive gear.

3. The hydraulic pump clutch as claimed in claim 2, characterized in that the number of separating bodies (4) is the same as the number of driven gears (2);

the inner side circular arc surface of the separating body (4), the driven gear (2) and the driving gear (1) form an inner side sealing cavity, and the outer side surface of the separating body (4) forms an outer side sealing cavity.

4. The hydraulic pump clutch according to claim 3, wherein the flow regulating assembly includes flow regulating valves (11) respectively provided on the plurality of partition bodies (4), and a first oil port (12) and a second oil port (13) are respectively provided on both sides of the flow regulating valves (11);

the first oil port (12) faces the inner side sealed cavity, and the second oil port (13) faces the outer side sealed cavity.

5. The hydraulic pump clutch according to claim 4, characterized in that the flow regulating assembly comprises a flow regulating valve (11); the flow regulating valve (11) is provided on only one of the plurality of separators (4); the flow control valve is characterized in that a first oil port (12) and a second oil port (13) are respectively arranged on two sides of the flow control valve (11), the first oil port (12) faces towards the inner side sealing cavity, and the second oil port (13) faces towards the outer side sealing cavity.

6. The hydraulic pump clutch according to claim 5, wherein the plurality of inner seal cavities are communicated with each other through inner conduits;

the plurality of outer side sealing cavities are communicated through outer side pipelines respectively.

7. The hydraulic pump clutch of claim 6, wherein the inboard conduit and the outboard conduit are both disposed outside of the housing assembly.

8. The hydraulic pump clutch as claimed in claim 6, characterized in that the housing assembly further comprises a cylindrical seal housing (44), and a driven gear shaft (45) which is perpendicular to and fixedly connected to the housing (44);

the housing (44) comprises 2 circular end covers (441) and a circumferential main body (442), and the separation body (4) is connected with the main body (442) and forms a sealing connection with the 2 circular end covers (441); the 2 circular end caps (441) respectively clamp the driving gear and the driven gear to provide axial sealing;

two ends of the driven gear shaft (45) are respectively and fixedly connected with the 2 circular end covers (441) in a vertical mode;

the driven gear (2) is arranged on the driven gear shaft (45) and can rotate along the driven gear shaft (45);

the inner side pipeline and the outer side pipeline are arranged outside the round surface end cover.

9. The hydraulic pump clutch according to claim 4 or 5, characterized in that the flow regulating assembly further comprises a lever (19), a pressure plate (20), a pressure spring (24), a release bearing (27) and a shift fork (25);

the flow regulating valve (11) is connected with the operating rod (19), and the pressure plate (20) is connected with the other end of the operating rod (19); the pressure spring (24) is arranged between the shell assembly and the pressure plate (20);

the release bearing (27) is arranged on one side, away from the shell assembly, of the pressure plate (20), and the shifting fork (25) is arranged on the release bearing (27).

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