CN102808867B - Plunger clutch and vehicle provided with plunger clutch - Google Patents
Plunger clutch and vehicle provided with plunger clutch Download PDFInfo
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- CN102808867B CN102808867B CN201210290821.4A CN201210290821A CN102808867B CN 102808867 B CN102808867 B CN 102808867B CN 201210290821 A CN201210290821 A CN 201210290821A CN 102808867 B CN102808867 B CN 102808867B
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- plunger
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- 238000009826 distribution Methods 0.000 claims description 45
- 239000010720 hydraulic oil Substances 0.000 abstract description 36
- 238000005299 abrasion Methods 0.000 abstract description 5
- 239000003921 oil Substances 0.000 description 118
- 230000005540 biological transmission Effects 0.000 description 8
- 230000033001 locomotion Effects 0.000 description 5
- 230000000694 effects Effects 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 230000008859 change Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 238000002347 injection Methods 0.000 description 2
- 239000007924 injection Substances 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 230000002035 prolonged effect Effects 0.000 description 2
- 238000010521 absorption reaction Methods 0.000 description 1
- 230000009471 action Effects 0.000 description 1
- 230000003139 buffering effect Effects 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 238000005520 cutting process Methods 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000000149 penetrating effect Effects 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
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Abstract
The invention discloses a plunger clutch and a vehicle provided with the plunger clutch, wherein the plunger clutch includes an input shaft, an output shaft and an axial plunger pump connecting assembly; the axial plunger pump connecting assembly includes a housing, a first end cap, a second end cap, a cylinder body, a plunger and a swash plate; the first end cap and the second end cap are arranged at the two ends of the housing, so as to form the space containing the cylinder body, the plunger and the swash plate; one end of the plunger is arranged in the plunger hole of the cylinder body in a sliding way, and the other end thereof is contacted with the swash plate; the input shaft is connected with the cylinder body, and the output shaft is connected with the swash plate; or the input shaft is connected with the swash plate, and the output shaft is connected with the cylinder body. The plunger clutch can realize the on/off working states of the clutch by controlling the flow variation of the hydraulic oil in the plunger pump. The plunger clutch can avoid the high possibility of abrasion of the existing clutch.
Description
Technical Field
The invention relates to the field of engineering machinery, in particular to a plunger type clutch and a vehicle with the plunger type clutch.
Background
The clutch is a device provided between the engine and the transmission for transmitting or cutting off the power of the engine. At present, the clutch devices used in the power transmission process in the mechanical field mostly adopt the following two forms: the plate clutch and the hydraulic torque converter are provided with a plate clutch unit actually, and the hydraulic torque converter plays a role in buffering the clutch action of equipment.
The plate clutch has a wide variety, but the basic working principle is as follows: when the clutch needs to be opened, an acting force (mechanical force, electromagnetic force, hydraulic force, etc.) pushes the release fork, thereby pressing the release bearing toward the middle portion of the diaphragm spring. As the middle of the diaphragm spring is pushed in, a set of pins near the outside of the spring will cause the spring to pull the pressure plate away from the clutch disc. Thereby disengaging the clutch from the rotating engine. When the clutch needs to be opened, the spring pushes the pressure plate towards the clutch disc direction, so that the flywheel is pressed. This locks the engine to the transmission input shaft so that they rotate at the same speed. The clutch plate is easy to wear, the starting smoothness is not good, and the overload protection function is not provided. Although the hydraulic torque converter overcomes the defects, the hydraulic torque converter has large power loss, complex structure and high use cost.
In view of the foregoing, there is a need for a clutch that overcomes the shortcomings of current clutching devices.
Disclosure of Invention
In view of the above, the present invention provides a plunger type clutch and a vehicle equipped with the plunger type clutch to solve the above problems of the existing clutch.
In one aspect, the present invention provides a plunger clutch comprising an input shaft, an output shaft, and an axial plunger pump coupling assembly comprising a housing, a first end cap, a second end cap, a cylinder block, a plunger, and a swash plate, wherein,
the first end cover and the second end cover are arranged at two ends of the shell to form a space for accommodating the cylinder block, the plunger and the swash plate;
one end of the plunger is slidably arranged in a plunger hole of the cylinder body, and the other end of the plunger is contacted with the swash plate;
the input shaft is connected with the cylinder body, and the output shaft is connected with the swash plate; or,
the input shaft is connected with the swash plate, and the output shaft is connected with the cylinder block.
Furthermore, the axial plunger pump type connecting assembly also comprises an oil distribution disc, the oil distribution disc is arranged between the first end cover or the second end cover and the cylinder body, and the oil distribution disc is provided with an oil inlet hole and an oil outlet hole;
the oil inlet hole is communicated with the oil outlet hole through an oil way, and a switch device for controlling the on-off of the oil way is arranged on the oil way between the oil inlet hole and the oil outlet hole.
Furthermore, a plurality of first oil ducts are arranged on the oil distribution disc, and the first oil ducts are respectively communicated with the oil inlet and the oil outlet;
a second oil duct is arranged on the shell and communicated with the first oil duct;
the switching device is provided on the second oil passage.
Furthermore, a bulge is arranged on the oil distribution disc, and the first oil passage is communicated with the outside of the oil distribution disc at the bulge;
the shell is provided with a groove, the groove is matched with the protrusion, and the second oil duct is communicated with the first oil duct at the groove.
Further, the switching device is a flow control valve.
Further, the plunger type clutch further comprises an overflow valve, and the overflow valve and the flow control valve are arranged on the second oil passage in parallel.
Furthermore, an axial through hole is formed in the plunger.
Furthermore, an oil filling hole and a hole plug matched with the oil filling hole are formed in the shell.
Further, the input shaft is connected with the cylinder key, and the output shaft is connected with the swash plate key; or,
the input shaft is connected with the swash plate key, and the output shaft is connected with the cylinder body key.
In another aspect of the invention, there is also provided a vehicle having an engine and a gearbox with a plunger clutch as described above disposed therebetween.
The axial plunger pump type connecting assembly for the plunger clutch is connected between the input shaft and the output shaft, and takes the connection of the input shaft and the cylinder body as an example, when the input shaft drives the cylinder body to rotate, when hydraulic oil in the cylinder body can normally flow out and external hydraulic oil can be normally supplemented into the cylinder body, the plunger can freely axially move in the cylinder body along with the rotation of the cylinder body, and the power of the input shaft cannot be transmitted to the swash plate and the output shaft; when hydraulic oil in the cylinder body can not circulate and be replaced with external hydraulic oil, the position of the plunger in the cylinder body can be kept unchanged, and along with the rotation of the cylinder body, the plunger can also drive the swash plate to rotate, so that the power of the input shaft is transmitted to the output shaft. The plunger type clutch can realize the on-off working state of the clutch by controlling the flowing change of the hydraulic oil in the cylinder body, and can avoid the problem of easy abrasion in the existing clutch.
Drawings
The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate an embodiment of the invention and, together with the description, serve to explain the invention and not to limit the invention. In the drawings:
FIG. 1 is a schematic structural diagram of an embodiment of a plunger-type clutch according to the present invention;
FIG. 2 is an exploded schematic view of the plunger clutch shown in FIG. 1;
FIG. 3 is a schematic view of the oil distribution pan of the plunger clutch shown in FIG. 1;
FIG. 4 is a schematic illustration of a flow control valve of the plunger-type clutch of FIG. 1;
fig. 5 is a schematic sectional view showing the structure of a plunger of the plunger type clutch shown in fig. 1.
Detailed Description
It should be noted that the embodiments and features of the embodiments may be combined with each other without conflict. The present invention will be described in detail below with reference to the embodiments with reference to the attached drawings.
The basic idea of the invention is that: in order to solve the problems that the existing clutch plate is easy to wear, poor in starting smoothness, free of overload protection function and the like, the invention provides the plunger type clutch, power is transmitted by virtue of the plunger pump, and the clutch effect of the plunger type clutch is realized by virtue of whether hydraulic oil in the cylinder body flows and changes, namely the hydraulic oil in the cylinder body can normally circulate with the outside of the cylinder body through the oil distribution disc, the plunger pump does not transmit power, and the plunger type clutch is in an 'off' state; the hydraulic oil in the cylinder body is cut off from flowing, the plunger of the plunger pump is kept still and can transmit power, and the plunger type clutch is in an 'on' state.
Preferred embodiments of the present invention will be described in further detail below with reference to the accompanying drawings:
fig. 1 is a schematic structural diagram of an embodiment of a plunger clutch provided by the present invention, which is shown by a partially cut-away effect, and the plunger clutch includes an input shaft 2, an output shaft 8, and an axial plunger pump type connecting assembly 100, where the axial plunger pump type connecting assembly 100 includes a housing 10, a first end cap 1, a second end cap 11, a cylinder 5, a plunger 6, and a swash plate 7, where the first end cap 1 and the second end cap 11 are disposed at two ends of the housing 10 to form a space for accommodating the cylinder 5, the plunger 6, and the swash plate 7; one end of the plunger 6 is slidably arranged in a plunger hole of the cylinder body 5, and the other end of the plunger is contacted with the swash plate 7; the input shaft 2 is connected to the cylinder block 5, and the output shaft 8 is connected to the swash plate 7.
After the plunger type clutch is assembled according to the connection relation, when the input shaft 2 drives the cylinder 5 to rotate, when the hydraulic oil in the cylinder 5 can normally flow out and the external hydraulic oil can be normally supplemented into the cylinder 5, the plunger 6 of the axial plunger pump type connecting assembly 100 can freely axially move in the cylinder 5 along with the rotation of the cylinder 5, and the power of the input shaft 2 cannot be transmitted to the swash plate 7 and the output shaft 8; when the hydraulic oil in the cylinder block 5 can not be circulated and replaced with the external hydraulic oil, the position of the plunger 6 in the cylinder block 5 can be kept unchanged, and along with the rotation of the cylinder block 5, the plunger 6 can also drive the swash plate 7 to rotate, so that the power of the input shaft 2 is transmitted to the output shaft 8. The plunger type clutch can realize the on-off working state of the clutch by controlling the flowing change of the hydraulic oil in the cylinder body, and can avoid the problem of easy abrasion in the existing clutch.
The above embodiment is exemplified by the input shaft 2 being connected to the cylinder block 5, and as an alternative embodiment, the input shaft 2 may also be connected to the swash plate 7, and the output shaft 8 is connected to the cylinder block 5.
As a preferred embodiment of the plunger type clutch of the present invention, as shown in fig. 1, a cylinder 5, a plunger 6, a swash plate 7 are accommodated in a space between a first end cap 1, a second end cap 11, a housing 10, an input shaft 2 is preferably keyed to the cylinder 5, and the input shaft 2 is rotatably provided on the first end cap 1 through a bearing 3; one end of the plunger 6 is disposed in the cylinder 5, the other end is in contact with the swash plate 7, and the end surface in contact with the swash plate 7 is preferably configured to be inclined; the swash plate 7 is in selective key connection with an output shaft 8, and the output shaft 8 is rotatably arranged on a second end cover 11 through a bearing 9.
The oil distribution pan 4 of the axial plunger pump connection assembly 100 is arranged between the first end cap 1 and the cylinder 5. As shown in fig. 3, the oil distribution disc 4 is provided with a plurality of oil distribution holes similar to kidney-shaped holes, the number of the oil distribution holes is preferably equal to the number of the plungers 6, and whether the oil distribution holes are oil inlet holes or oil outlet holes is determined according to the positions of the plungers 6 in the corresponding plunger holes. In the present embodiment, the number of the plungers 6 is preferably 6. Referring again to fig. 1, since the upper plunger 6 is in a position protruding from the cylinder 5, the oil distribution hole in the upper portion of the oil distribution pan 4 is an oil inlet hole, and correspondingly, the oil distribution hole in the lower portion is an oil outlet hole.
As shown in fig. 2 and 3, the oil distribution disc 4 is further provided with a plurality of first oil passages, the number of the first oil passages is preferably equal to the number of the plungers 6, and the first oil passages are respectively in one-to-one correspondence with the oil distribution holes and serve as an oil outlet passage and an oil inlet passage of the oil distribution disc 4; two bulges are arranged on the upper part of the oil distribution disc 4, and the first oil duct is communicated with the outside of the oil distribution disc 4 through the two bulges respectively.
The corresponding position of the two bulges on the shell 10 is provided with a matched groove, and during assembly, the bulges of the oil distribution disc 4 are correspondingly assembled with the grooves of the shell 10. The housing 10 is provided with a second oil passage which communicates with the first oil passage of the oil distribution pan 4 at the above-mentioned groove. The hydraulic oil passes through the oil outlet hole of the oil distribution disc 4, the first oil duct and the second oil duct in sequence from the plunger hole of the cylinder body 5, returns to the first oil duct, the oil inlet hole of the oil distribution disc 4 and the plunger hole of the cylinder body 5, and reciprocates in this way to form a complete hydraulic oil loop. Through which the hydraulic oil in the cylinder 5 is in active flow communication, so that the plunger 6 is free to move axially in the cylinder 5.
It should be noted that the first oil passage of the oil distribution disc 4 is communicated with the oil inlet and the oil outlet, and forms a communicated hydraulic circuit with the cylinder 5 and the shell 10, therefore, the oil inlet and the oil outlet of the oil distribution disc 4 in this embodiment may be a through hole arranged in the axial direction of the oil distribution disc 4, or a groove arranged on the oil distribution disc 4; similarly, the depth of the first oil passage may be a groove axially penetrating the oil distribution disc 4, or a groove having a depth smaller than the axial thickness of the oil distribution disc 4. The second oil passage on the housing 10 is preferably a through hole provided inside the housing as an oil passage, but may be another type of oil passage. The above-mentioned hydraulic oil circuit is only a preferred embodiment, and it is also possible to provide a suitable oil tank outside the axial plunger pump type connecting assembly 100 and communicate with the oil inlet and the oil outlet of the oil distribution disc 4, respectively, and to achieve the same function.
The casing 10 is further provided with a switch device, which is located on the oil path of the second oil path and controls the on/off of the oil path of the second oil path. Any device capable of making and breaking an oil path may be used in the present invention. As shown in fig. 1 and 2, the switching device is preferably implemented as a flow control valve 13, and the flow control valve 13 can not only control the on/off of the second oil passage, but also adjust the flow rate on the second oil passage, and can control the oil inlet and outlet speeds of the oil distribution plate 4 by controlling the flow rate, so that the resistance between the plunger 6 and the swash plate 7 can be adjusted, and the half-clutch state of the plunger clutch can be realized. The flow control valve 13 is preferably an electromagnetic flow control valve, and as shown in fig. 4, is a schematic structural view of an electromagnetic flow control valve applied to the present embodiment. It should be understood that the flow control valve 13 may also be a hydraulic valve, electro-hydraulic valve, etc., based on the above flow control.
In order to protect the plunger type clutch under an excessive load, the embodiment is further provided with a relief valve 14, and the relief valve 14 is arranged in the oil passage of the second oil passage in parallel with the flow control valve 13, as shown in fig. 1 and 2; preferably, an oil inlet and an oil outlet of the relief valve 14 are respectively connected to the oil passage of the second oil passage, and when the relief valve 14 is opened, the hydraulic oil circuit in the cylinder 5 can be communicated.
The housing 10 is further provided with an oil injection hole for injecting hydraulic oil into the cylinder 5, and the oil injection hole is provided with a hole plug 12, as shown in fig. 2.
As shown in fig. 5, the plunger 6 in this embodiment is provided with an axial through hole, which has a small diameter and only allows a small amount of hydraulic oil to flow from the cylinder block to the surface of the swash plate 7, so as to form an oil film between the plunger 6 and the swash plate 7 and protect the components of the plunger pump. As can also be seen from fig. 5, the end surface of the plunger 6 at the end contacting the swash plate 7 is inclined to facilitate better engagement of the swash plate 7, and this configuration is only a preferred configuration and can be implemented in other forms, such as a universal joint at the contact end.
It will be appreciated by those skilled in the art that for the above embodiment, the number of plungers 6 may be varied according to different requirements; the input shaft 2 and the output shaft 8 of the clutch can be exchanged; the bulge on the oil distribution disc 4 can be arranged as required as long as the first oil channel is communicated with the second oil channel; the flow control valve 13 may be configured with different forms of control valves according to different design requirements. Such alternatives, which do not alter the spirit of the invention, are considered to be within the scope of the invention as claimed.
After the plunger type clutch is configured and assembled according to the structural characteristics and the connection relation, the plunger type clutch can be used in a vehicle transmission system, the input shaft 2 is connected with an engine output shaft of a vehicle, and the output shaft 8 is connected with an input shaft of a gearbox.
When the plunger type clutch works, the plunger type clutch is mainly divided into three working states:
state 1: disconnected power transmission state
The engine rotates the input shaft 2 and the cylinder 5 keyed to the input shaft 2, together with the plunger 6 placed inside the cylinder 5. The flow control valve 13 is fully opened, and the hydraulic oil in the cylinder 5 smoothly flows in and out from the oil inlet and outlet holes of the oil distribution disc 4, and can form a closed hydraulic oil circuit through the second oil passage on the housing 10. When the cylinder 5 rotates, the plunger 6 rotates along with the cylinder, the right end of the plunger 6 is subjected to the resistance of the swash plate 7, the hydraulic oil in the cylinder 5 is pressed by the plunger 6 to flow according to the circuit, and the plunger 6 freely moves axially in the cylinder 5. Therefore, in this state, the power between the input shaft 2 and the output shaft 8 of the plunger clutch is cut off, and the power of the engine cannot be transmitted to the transmission.
State 2: semi-clutched state
The flow control valve is gradually closed, that is, the flow control valve 13 is in a state of being opened according to a certain proportion, at this time, the throughput of the hydraulic oil from the flow control valve 13 is reduced, the flow speed is reduced, and the oil distribution speed of the hydraulic oil in the cylinder 5 through the oil distribution disc 4 is reduced. When the cylinder 5 rotates, the axial movement of the plunger 6 in the cylinder 5 is resisted to some extent by the hydraulic oil, and therefore, the plunger 6 pushes the swash plate 7 to rotate with a small force, thereby realizing a half-clutch state of the plunger clutch.
The half-clutch state can be changed slowly along with the opening and closing proportion of the flow control valve 13, the flow rate of the passing flow is gradually reduced, the resistance of the plunger 6 to the hydraulic oil is gradually increased, the torque of the swash plate 7 is also gradually increased, and the power of the engine is gradually transmitted to the output shaft 8, so that the plunger type clutch is smoothly clutched. With the flow control valve 13 being gradually fully closed from fully open, the plunger type clutch can smoothly be shifted from the open state to the partially engaged state, and further to the engaged state.
State 3: engaged state
As the flow control valve 13 is completely closed, it cuts off the flow of the second oil passage, that is, the hydraulic oil in each plunger hole in the cylinder 5 cannot flow in and out through the oil distribution pan 4, so that the oil amount of the hydraulic oil in each plunger hole remains unchanged. When the cylinder body 5 rotates, the hydraulic oil in the cylinder body 5 can block the axial movement of the plunger 6, so that the plunger 6 keeps the original position unchanged, the other end of the plunger 6 can drive the swash plate 7 to rotate, the power input by the engine is output through the swash plate 7 and the output shaft 8, and the power combination, namely the meshing state, of the plunger type clutch is realized.
Under the meshing state, when the output shaft 8 is overloaded and the swash plate 7 is suddenly stopped, the output shaft 8 transmits overload pressure to the plunger 6 through the swash plate 7, hydraulic oil in the cylinder block 5 is subjected to the overload pressure, the oil pressure on the high-pressure side of the oil distribution disc 4 is suddenly increased, the overflow valve 14 arranged on the oil path of the second oil path is opened, the hydraulic oil in the cylinder block 5 enters the low-pressure oil absorption side from the high-pressure side through the overflow valve 14 to enable the oil path to be communicated, and power input by the engine is released in an overflow mode, so that the engine and related parts are protected.
Correspondingly, the invention also provides a vehicle which is provided with an engine and a gearbox, and the plunger type clutch is arranged between the engine and the gearbox.
The plunger type clutch of the invention takes the acting force between the plunger of the axial plunger pump type connecting component and the driven plate (namely the swash plate) as a power transmission mode, and can control the on-off of a hydraulic oil path in the cylinder body through the flow control valve, thereby realizing the control of the opening and closing of the plunger type clutch. The plunger clutch of the present invention has many advantages:
1. in the process from disconnection to power combination of the plunger type clutch, the flow of the flow control valve is gradually reduced, the resistance of hydraulic oil on the movement of the plunger is gradually increased, the torque on the swash plate is gradually increased, the whole process is stable and continuous, and the clutch is smooth;
2. in the engaged state, the flow control valve is completely closed, the hydraulic oil flow in the plunger type clutch is 0, the power loss is small, and the transmission efficiency is high;
3. when the load of the output end of the clutch is overlarge, the overflow valve is opened, so that the overload protection effect on the engine is realized;
4. only when the gear is shifted, the plunger and the cylinder body do relative motion, and the plunger and the cylinder body do not have relative motion after the gear shifting is finished, so that the abrasion of the plunger and the cylinder body is effectively reduced, the reliability of the clutch is improved, and the service life of the clutch is prolonged;
5. the plunger is provided with an axial through hole for lubrication, so that the abrasion between the plunger and the swash plate is reduced, the reliability of the clutch is improved, and the service life of the clutch is prolonged;
6. the invention has small volume, compact and simple structure and convenient installation and maintenance under the same power condition;
7. is easy to be combined with various control methods, and is convenient to realize automatic work.
The above description is only for the purpose of illustrating the preferred embodiments of the present invention and is not to be construed as limiting the invention, and any modifications, equivalents, improvements and the like that fall within the spirit and principle of the present invention are intended to be included therein.
Claims (10)
1. A plunger type clutch is characterized by comprising an input shaft (2), an output shaft (8) and an axial plunger pump type connecting assembly (100), wherein the axial plunger pump type connecting assembly (100) comprises a shell (10), a first end cover (1), a second end cover (11), a cylinder body (5), a plunger (6) and a swash plate (7),
the first end cover (1) and the second end cover (11) are arranged at two ends of the shell (10) to form a space for accommodating the cylinder block (5), the plunger (6) and the swash plate (7);
one end of the plunger (6) is slidably arranged in a plunger hole of the cylinder body (5), and the other end of the plunger is contacted with the swash plate (7);
the input shaft (2) is connected with the cylinder body (5), and the output shaft (8) is connected with the swash plate (7); or,
the input shaft (2) is connected with the swash plate (7), and the output shaft (8) is connected with the cylinder body (5).
2. Plunger clutch according to claim 1, characterized in that the axial plunger pump connection assembly (100) further comprises an oil distribution disc (4), the oil distribution disc (4) being arranged between the first end cover (1) or the second end cover (11) and the cylinder block (5), the oil distribution disc (4) being provided with an oil inlet and an oil outlet;
the oil inlet hole is communicated with the oil outlet hole through an oil way, and a switch device for controlling the on-off of the oil way is arranged on the oil way between the oil inlet hole and the oil outlet hole.
3. The plunger type clutch as set forth in claim 2, characterized in that a plurality of first oil passages are provided on the oil distribution disc (4), the first oil passages being respectively communicated with the oil inlet hole and the oil outlet hole;
a second oil duct is arranged on the shell (10) and communicated with the first oil duct;
the switching device is provided on the second oil passage.
4. The plunger type clutch as set forth in claim 3, characterized in that a bulge is provided on the oil distribution disc (4), and the first oil passage communicates with the outside of the oil distribution disc (4) at the bulge;
a groove is formed in the shell (10), the groove is matched with the protrusion, and the second oil duct is communicated with the first oil duct at the groove.
5. Plunger clutch according to claim 4, characterized in that the switching means is a flow control valve (13).
6. Plunger clutch according to claim 5, characterized in that it further comprises a relief valve (14), which relief valve (14) is arranged in parallel with the flow control valve (13) on the second oil channel.
7. Plunger clutch according to any of claims 1-6, characterized in that the plunger (6) is provided with an axial through hole.
8. Plunger clutch according to any of claims 1-6, characterized in that the housing (10) is provided with an oil hole and a hole plug (12) cooperating with the oil hole.
9. Plunger clutch according to any of claims 1-6, characterized in that the input shaft (2) is keyed with the cylinder block (5) and the output shaft (8) is keyed with the swash plate (7); or,
the input shaft (2) is connected with the swash plate (7) in a key mode, and the output shaft (8) is connected with the cylinder body (5) in a key mode.
10. A vehicle having an engine and a gearbox, characterized in that a plunger clutch according to any one of claims 1-9 is arranged between the engine and the gearbox.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201210290821.4A CN102808867B (en) | 2012-08-15 | 2012-08-15 | Plunger clutch and vehicle provided with plunger clutch |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201210290821.4A CN102808867B (en) | 2012-08-15 | 2012-08-15 | Plunger clutch and vehicle provided with plunger clutch |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102808867A CN102808867A (en) | 2012-12-05 |
| CN102808867B true CN102808867B (en) | 2015-05-13 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201210290821.4A Expired - Fee Related CN102808867B (en) | 2012-08-15 | 2012-08-15 | Plunger clutch and vehicle provided with plunger clutch |
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| CN (1) | CN102808867B (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN108006113B (en) * | 2018-01-26 | 2023-10-20 | 吉林大学 | Radial friction clutch with plunger cylinder pushing conical guide rail |
| CN110345035A (en) * | 2019-08-20 | 2019-10-18 | 山东兰徳液压精工有限公司 | A kind of plunger pump for farm machinery |
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| JPH06346926A (en) * | 1993-06-10 | 1994-12-20 | Kanzaki Kokyukoki Mfg Co Ltd | Pressure regulating valve device of hydraulic clutch |
| CN2457365Y (en) * | 2000-12-26 | 2001-10-31 | 上海易初通用机器有限公司 | Plunger oblique disc type compressor |
| CN200971937Y (en) * | 2006-10-12 | 2007-11-07 | 江苏黄海汽配股份有限公司 | Hydraulic clutch general pump |
| CN101550999A (en) * | 2008-04-01 | 2009-10-07 | 张敏 | Hydraulic stepless speed-change driver |
| CN101696721A (en) * | 2009-05-27 | 2010-04-21 | 北京联合大学 | Swash plate guide-rod rotary stepless transmission |
| CN102092377A (en) * | 2011-01-11 | 2011-06-15 | 谢陵波 | Active intrusive retarding system |
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2012
- 2012-08-15 CN CN201210290821.4A patent/CN102808867B/en not_active Expired - Fee Related
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH06346926A (en) * | 1993-06-10 | 1994-12-20 | Kanzaki Kokyukoki Mfg Co Ltd | Pressure regulating valve device of hydraulic clutch |
| CN2457365Y (en) * | 2000-12-26 | 2001-10-31 | 上海易初通用机器有限公司 | Plunger oblique disc type compressor |
| CN200971937Y (en) * | 2006-10-12 | 2007-11-07 | 江苏黄海汽配股份有限公司 | Hydraulic clutch general pump |
| CN101550999A (en) * | 2008-04-01 | 2009-10-07 | 张敏 | Hydraulic stepless speed-change driver |
| CN101696721A (en) * | 2009-05-27 | 2010-04-21 | 北京联合大学 | Swash plate guide-rod rotary stepless transmission |
| CN102092377A (en) * | 2011-01-11 | 2011-06-15 | 谢陵波 | Active intrusive retarding system |
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| CN102808867A (en) | 2012-12-05 |
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