阅读说明：本技术 叶片泵 (Vane pump ) 是由 倪伟 张欣林 姜维 于 2020-05-28 设计创作，主要内容包括：本公开提供了一种叶片泵,属于发动机技术领域。所述叶片泵包括先导模块和泵模块,先导模块包括先导壳体、先导阀芯和两位三通换向阀,先导阀芯的外周壁上具有第一活塞环和第二活塞环,第一活塞环和第二活塞环的外周壁均与先导壳体的内壁密封滑动配合以将先导壳体的内腔化分为第一腔体、第二腔体和第三腔体,泵模块包括泵壳体、转子叶片组件和滑块,滑块可活动地安装在泵壳体内,滑块的外壁具有挡块,挡块位于滑块的外壁和泵壳体的内壁之间的间隙中,滑块的外壁、挡块的一侧面和泵壳体内壁形成反馈腔。通过本公开提供的叶片泵可以灵活调整叶片泵的排量。(The disclosure provides a vane pump, and belongs to the technical field of engines. The vane pump includes guide's module and pump module, guide's module includes the guide's casing, guide's case and two tee bend switching-over valves, first piston ring and second piston ring have on the periphery wall of guide's case, the periphery wall of first piston ring and second piston ring all with the sealed sliding fit of the inner wall of guide's casing in order to divide into first cavity with the intracavity of guide's casing, second cavity and third cavity, pump module includes the pump casing, rotor blade subassembly and slider, slider movably installs in the pump casing, the outer wall of slider has the dog, the dog is located the clearance between the outer wall of slider and the inner wall of pump casing, the outer wall of slider, a side and the pump casing inner wall of dog form the feedback chamber. The displacement of the vane pump can be flexibly adjusted through the vane pump provided by the disclosure.)

1. A vane pump, characterized in that it comprises a pilot module (1) and a pump module (2), wherein:

the pilot module (1) comprises a pilot housing (11), a pilot valve core (12) and a two-position three-way reversing valve (13), wherein a first piston ring (121) and a second piston ring (122) are arranged on the outer peripheral wall of the pilot valve core (12), the outer diameter of the first piston ring (121) is larger than that of the second piston ring (122), the outer peripheral walls of the first piston ring (121) and the second piston ring (122) are in sealing sliding fit with the inner wall of the pilot housing (11) so as to divide the inner cavity of the pilot housing (11) into a first cavity (14), a second cavity (15) and a third cavity (16), the second cavity (15) is located between the first cavity (14) and the third cavity (16), the first cavity (14) is used for being communicated with a crankcase of an engine, and a first elastic piece (141) is arranged in the first cavity (14), the first elastic piece (141) abuts against a first side wall of the first piston ring (121), the second cavity (15) is used for being communicated with a lubricating oil channel of the engine, an oil inlet of the two-position three-way reversing valve (13) is communicated with the lubricating oil channel of the engine, a first working oil port of the two-position three-way reversing valve (13) is communicated with the third cavity (16), and a second working oil port of the two-position three-way reversing valve (13) is used for being communicated with a crankcase of the engine;

the pump module (2) comprises a pump housing (21), a rotor blade assembly (22) and a slide block (23), wherein the slide block (23) is movably installed in the pump housing (21), the outer wall of the slide block (23) is provided with a stop block (231), the stop block (231) is positioned in a gap between the outer wall of the slide block (23) and the inner wall of the pump housing (21), the outer wall of the slide block (23), one side surface of the stop block (231) and the inner wall of the pump housing (21) form a feedback cavity (24), the feedback cavity (24) is communicated with the first cavity (14) or the second cavity (15) alternatively along with the movement of the pilot valve core (12), the other side surface of the stop block (231) is provided with a second elastic piece (2311), the second elastic piece (2311) is connected with the inner wall of the pump housing (21), and the rotor blade assembly (22) is rotatably installed in the slide block (23), so as to divide the internal space of the slide block (23) into an oil inlet cavity (25) and a plurality of working cavities (26), wherein the volume of the oil inlet cavity (25) is inversely related to the volume of the feedback cavity (24).

2. A vane pump according to claim 1, characterized in that the outer wall of the slide (23) has a semi-cylindrical block (232), the inner wall of the pump housing (21) has a slot (211), the semi-cylindrical block (232) is axially rotatably inserted in the slot (211) itself, and the rotational axis of the semi-cylindrical block (232) is parallel to the rotational axis of the rotor blade assembly (22).

3. A vane pump as claimed in claim 1, characterized in that the outer wall of the slide (23) has a pin (233), the pin (233) being parallel to the rotational axis of the rotor blade assembly (22), the inner wall of the pump housing (21) having a receptacle (212), one end of the pin (233) being connected to the slide (23), the other end of the pin (233) being rotatably inserted in the receptacle (212).

4. The vane pump of claim 1, characterized in that one end of the pilot valve spool (12) protrudes beyond the first piston ring (121), the first elastic member (141) is a first spring, a first end of the first spring is sleeved on the pilot valve spool (12) and abuts against a first side wall of the first piston ring (121), and a second end of the first spring is connected with an inner wall of the first cavity (14).

5. A vane pump as claimed in claim 1, characterized in that the second elastic member (2311) is a second spring, the inner wall of the pump housing (21) has a counter bore (213), the other side of the stopper (231) has a groove (2312), a first end of the second spring is inserted in the counter bore (213), and a second end of the second spring is inserted in the groove (2312).

6. A vane pump as claimed in claim 1, characterized in that the rotor vane assembly (22) comprises a rotor (221) and a plurality of vanes (222), the rotor (221) is rotatably positioned in the pump housing (21), each vane (222) is slidably inserted on the rotor (221), the sliding direction of the vanes (222) is perpendicular to the axis of the rotor (221), and one side of each vane (222) is in sliding contact with the inner wall of the sliding block (23).

7. A vane pump according to claim 6, characterized in that the pump module (2) further comprises a positioning ring (27), the positioning ring (27) being movably arranged inside the rotor (221), the axis of the positioning ring (27) being parallel to the axis of the rotor (221), the peripheral wall of the positioning ring (27) being in sliding contact with the other side edge of each of the vanes (222).

8. A vane pump according to any one of claims 1 to 7, characterized in that a pressure tap (241) is inserted on the inner wall of the feedback chamber (24).

9. A vane pump as set forth in any of claims 1-7 characterized in that the pilot housing (11) has a first oil drain opening (111), the first cavity (14) is communicated with the crankcase of the engine through the first oil drain opening (111), a first adjusting screw (1111) is inserted in the first oil drain opening (111), and the first adjusting screw (1111) is used for adjusting the opening degree of the first oil drain opening (111).

10. The vane pump according to any one of claims 1 to 7, characterized in that a second oil drain opening (112) is formed in the pilot housing (11), the third cavity (16) is communicated with a crankcase of the engine through the second oil drain opening (112), a second adjusting screw (1121) is inserted into the second oil drain opening (112), and the second adjusting screw (1121) is used for adjusting the opening degree of the second oil drain opening (112).

Technical Field

The disclosure belongs to the technical field of engines, and particularly relates to a vane pump.

Background

A vane pump is a common hydraulic pump for an automobile, and supplies lubricating oil to the entire engine by converting mechanical energy into hydraulic energy of the lubricating oil.

Disclosure of Invention

The embodiment of the disclosure provides a vane pump, which can flexibly adjust the displacement of the vane pump. The technical scheme is as follows:

the disclosed embodiment provides a vane pump, which comprises a pilot module and a pump module, wherein:

the pilot module comprises a pilot housing, a pilot valve core and a two-position three-way reversing valve, wherein a first piston ring and a second piston ring are arranged on the peripheral wall of the pilot valve core, the outer diameter of the first piston ring is larger than that of the second piston ring, the peripheral walls of the first piston ring and the second piston ring are in sealed sliding fit with the inner wall of the pilot housing so as to divide the inner cavity of the pilot housing into a first cavity, a second cavity and a third cavity, the second cavity is located between the first cavity and the third cavity, the first cavity is communicated with a crankcase of an engine, a first elastic piece is arranged in the first cavity and abutted against a first side wall of the first piston ring, the second cavity is communicated with a lubricating oil channel of the engine, and an oil inlet of the two-position three-way reversing valve is communicated with the lubricating oil channel of the engine, a first working oil port of the two-position three-way reversing valve is communicated with the third cavity, and a second working oil port of the two-position three-way reversing valve is communicated with a crankcase of the engine;

the pump module comprises a pump housing, a rotor blade assembly and a sliding block, wherein the sliding block is movably installed in the pump housing, a check block is arranged on the outer wall of the sliding block, the check block is located in a gap between the outer wall of the sliding block and the inner wall of the pump housing, the outer wall of the sliding block, a side face of the check block and the inner wall of the pump housing form a feedback cavity, the feedback cavity is communicated with the first cavity or the second cavity along with the movement of a pilot valve core, a second elastic piece is arranged on the other side face of the check block, the second elastic piece is connected with the inner wall of the pump housing, the rotor blade assembly is rotatably installed in the sliding block so as to divide the inner space of the sliding block into an oil inlet cavity and a plurality of working cavities, and the volume of the oil inlet cavity and the volume of the feedback cavity are.

Optionally, the outer wall of the slide block has a semi-cylindrical block, and the inner wall of the pump housing has a slot, the semi-cylindrical block being axially rotatably inserted into the slot, the rotational axis of the semi-cylindrical block being parallel to the rotational axis of the rotor blade assembly.

Optionally, the outer wall of the sliding block is provided with a pin shaft, the pin shaft is parallel to the rotating shaft of the rotor blade assembly, the inner wall of the pump housing is provided with a jack, one end of the pin shaft is connected with the sliding block, and the other end of the pin shaft is rotatably inserted into the jack.

Optionally, one end of the pilot valve element protrudes out of the first piston ring, the first elastic element is a first spring, a first end of the first spring is sleeved on the pilot valve element and abuts against a first side wall of the first piston ring, and a second end of the first spring is connected with an inner wall of the first cavity.

Optionally, the second elastic member is a second spring, the inner wall of the pump housing has a counter bore, the other side of the stopper has a groove, a first end of the second spring is inserted into the counter bore, and a second end of the second spring is inserted into the groove.

Optionally, the rotor blade assembly includes a rotor and a plurality of blades, the rotor is rotatably located in the pump housing, each blade is slidably inserted into the rotor, the sliding direction of the blade is perpendicular to the axis of the rotor, and one side of each blade is in sliding contact with the inner wall of the sliding block.

Optionally, the vane pump further comprises a positioning ring movably disposed in the rotor, an axis of the positioning ring is parallel to an axis of the rotor, and an outer peripheral wall of the positioning ring is in sliding contact with another side edge of each of the vanes.

Optionally, a pressure measuring joint is inserted on the inner wall of the feedback cavity.

Optionally, a first oil drainage port is formed in the pilot housing, the first cavity is communicated with a crankcase of the engine through the first oil drainage port, a first adjusting screw is inserted into the first oil drainage port, and the first adjusting screw is used for adjusting the opening degree of the first oil drainage port.

Optionally, a second oil drainage port is formed in the pilot housing, the third cavity is communicated with a crankcase of the engine through the second oil drainage port, a second adjusting screw is inserted into the second oil drainage port, and the second adjusting screw is used for adjusting the opening degree of the second oil drainage port.

The technical scheme provided by the embodiment of the disclosure has the following beneficial effects:

for the vane pump provided by the embodiment of the disclosure, when the engine is not started, the pilot valve core is in the initial position under the action of the first elastic part, and at the moment, the feedback cavity is communicated with the first cavity.

When the engine is started, a part of lubricating oil in a lubricating oil passage of the engine flows into the second cavity and acts on the first piston ring and the second piston ring. At the moment, because the pressure in a lubricating oil passage of the engine is lower, the two-position three-way reversing valve is arranged at the right position, and an oil inlet of the two-position three-way reversing valve is communicated with the first working oil port. And the other part of lubricating oil in a lubricating oil passage of the engine enters the third cavity after passing through the oil inlet of the two-position three-way reversing valve and the first working oil port. Then, the acting area of the two lubricating oils on the pilot valve core is the sum of the sectional areas of the first piston ring and the pilot valve core. The first cavity is communicated with the feedback cavity. Therefore, lubricating oil in the feedback cavity is drained to the crankcase through the first cavity, the sliding block is located at the original position, the volume of the feedback cavity is the minimum, the volume of the oil inlet cavity is the maximum at the moment, and the displacement of the vane pump is the maximum. This provides sufficient lubrication during engine start-up.

Along with the starting of the engine, the pressure of a lubricating oil passage of the engine is gradually increased under the action of the vane pump. If the engine is in a low-pressure mode, at the moment, the two-position three-way reversing valve is arranged on the right position, and an oil inlet of the two-position three-way reversing valve is communicated with the first working oil port. In the same way, the acting area of the two lubricating oils on the pilot valve core is the sum of the sectional areas of the first piston ring and the pilot valve core. Because pressure in the lubricating oil passage of the engine is increased, the upward movement amount of the pilot valve core is increased, so that the second cavity is communicated with the feedback cavity. Therefore, lubricating oil in a lubricating oil channel of the engine enters the feedback cavity and acts on the stop block, so that the sliding block rotates, the volume of the feedback cavity is increased, the volume of the oil inlet cavity is decreased, and the displacement of the vane pump is reduced. This limits the maximum pressure of the lubricating oil so that the engine is always in the low pressure mode.

After the engine is started, if the engine is in the process of switching from the low-pressure mode to the high-pressure mode, at the moment, a part of lubricating oil in a lubricating oil passage of the engine flows into the second cavity and acts on the first piston ring and the second piston ring. Because the two-position three-way reversing valve is arranged at the left position, and the oil inlet of the two-position three-way reversing valve is communicated with the second working oil port, the other part of lubricating oil in the lubricating oil passage of the engine flows through the oil inlet of the two-position three-way reversing valve and the second working oil port and then is discharged to the crankcase of the engine. Then, the acting area of the two lubricating oils on the pilot valve core is the difference of the cross-sectional areas of the first piston ring and the second piston ring. The first cavity is communicated with the feedback cavity. Therefore, lubricating oil in the feedback cavity is drained to the crankcase through the first cavity, the sliding block moves towards the original position, the volume of the feedback cavity is reduced, the volume of the oil inlet cavity is increased, and the displacement of the vane pump is increased. This may further increase the pressure of the lubricating oil in the engine, thereby facilitating switching of the engine from the low pressure mode to the high pressure mode.

After the engine is in a high-pressure state, the pressure of a lubricating oil passage of the engine is gradually increased under the action of the vane pump. At the moment, the two-position three-way reversing valve is arranged at the left position, and an oil inlet of the two-position three-way reversing valve is communicated with the second working port. Similarly, the acting area of the two lubricating oils on the pilot valve core is the difference between the cross-sectional areas of the first piston ring and the second piston ring. Due to the fact that pressure in a lubricating oil channel of the engine is increased, even if no oil pressure exists in the third cavity, the pilot valve core can be pushed to move upwards, and the second cavity is communicated with the feedback cavity. Therefore, lubricating oil in a lubricating oil channel of the engine enters the feedback cavity and acts on the stop block, so that the sliding block rotates, the volume of the feedback cavity is increased, the volume of the oil inlet cavity is decreased, and the displacement of the vane pump is reduced. This limits the maximum pressure of the lubricating oil so that the engine is always in high pressure mode.

That is to say, the vane pump that this embodiment provided not only can adjust the discharge capacity of vane pump in a flexible way, can also divide into two kinds of modes and go to inject the maximum pressure of lubricating oil to make the vane pump can be according to the different stages that automobile engine was located, the discharge capacity of flexible adjustment vane pump has reduced the friction loss.

Drawings

In order to more clearly illustrate the technical solutions in the embodiments of the present disclosure, the drawings needed to be used in the description of the embodiments are briefly introduced below, and it is obvious that the drawings in the following description are only some embodiments of the present disclosure, and it is obvious for those skilled in the art to obtain other drawings based on the drawings without creative efforts.

FIG. 1 is a cross-sectional view of a vane pump provided in an embodiment of the present disclosure;

FIG. 2 is a schematic structural diagram of a pilot valve cartridge provided by an embodiment of the present disclosure;

FIG. 3 is a schematic structural diagram of a two-position three-way directional valve provided by an embodiment of the present disclosure.

The symbols in the drawings represent the following meanings:

1. a pilot module; 11. a pilot housing; 111. a first oil drainage port; 1111. a first adjusting screw; 112. a second oil drainage port; 1121. a second adjusting screw; 113. a first through hole; 114. a second through hole; 12. a pilot valve spool; 121. a first piston ring; 122. a second piston ring; 13. a two-position three-way reversing valve; 14. a first cavity; 141. a first elastic member; 15. a second cavity; 16. a third cavity;

2. a pump module; 21. a pump housing; 211. a slot; 212. a jack; 213. a counter bore; 22. a rotor blade assembly; 221. a rotor; 222. a blade; 23. a slider; 231. a stopper; 2311. a second elastic member; 2312. a groove; 232. a semi-cylindrical block; 233. a pin shaft; 24. a feedback chamber; 241. a pressure measuring joint; 25. an oil inlet cavity; 26. a working chamber; 27. a positioning ring;

100. a pilot channel; 200. and (5) sealing rings.

Detailed Description

To make the objects, technical solutions and advantages of the present disclosure more apparent, embodiments of the present disclosure will be described in detail with reference to the accompanying drawings.

The embodiment of the disclosure provides a vane pump, which belongs to a part of a vehicle lubricating system and can adjust the displacement of the vane pump according to the pressure of lubricating oil of a vehicle. For better description of the operation of the vane pump, the following brief description is given of the lubrication system of the vehicle:

the lubricating system of the automobile engine comprises a lubricating oil channel, a crankcase and a vane pump, wherein the lubricating oil channel is used for conveying lubricating oil to each lubricating part, the crankcase is used for storing the lubricating oil, and a certain amount of lubricating oil is pumped out of the crankcase and pressurized by the vane pump and then is continuously conveyed to the surfaces of all parts for lubrication.

Fig. 1 is a sectional view of a vane pump according to an embodiment of the present disclosure, and the following describes a structure of the vane pump with reference to fig. 1:

the vane pump comprises a pilot module 1 and a pump module 2, wherein: the pilot module 1 comprises a pilot housing 11, a pilot valve core 12 and a two-position three-way reversing valve 13, wherein a first piston ring 121 and a second piston ring 122 (see fig. 2) are arranged on the outer peripheral wall of the pilot valve core 12, the outer diameter of the first piston ring 121 is larger than that of the second piston ring 122, the outer peripheral walls of the first piston ring 121 and the second piston ring 122 are in sealing sliding fit with the inner wall of the pilot housing 11 to divide the inner cavity of the pilot housing 11 into a first cavity 14, a second cavity 15 and a third cavity 16, the second cavity 15 is located between the first cavity 14 and the third cavity 16, the first cavity 14 is used for being communicated with a crankcase of an engine, a first elastic member 141 is arranged in the first cavity 14, the first elastic member 141 is abutted against the first side wall of the first piston ring 121, the second cavity 15 is used for being communicated with a lubricating oil passage of the engine, an oil inlet p of the two-position three-way reversing valve 13 is communicated with a, and a first working oil port a of the two-position three-way reversing valve 13 is communicated with the third cavity 16, and a second working oil port b of the two-position three-way reversing valve 13 is communicated with a crankcase of the engine.

The pump module 2 comprises a pump housing 21, a rotor blade assembly 22 and a slider 23, wherein the slider 23 is movably installed in the pump housing 21, the outer wall of the slider 23 is provided with a stop 231, the stop 231 is positioned in a gap between the outer wall of the slider 23 and the inner wall of the pump housing 21, the outer wall of the slider 23, one side surface of the stop 231 and the inner wall of the pump housing 21 form a feedback cavity 24, the feedback cavity 24 is alternatively communicated with the first cavity 14 or the second cavity 15 along with the movement of the pilot valve spool 12, the other side surface of the stop 231 is provided with a second elastic piece 2311, the second elastic piece 2311 is connected with the inner wall of the pump housing 21, the rotor blade assembly 22 is rotatably installed in the slider 23 to divide the inner space of the slider 23 into an oil inlet cavity 25 and a plurality of working cavities 26, and the volume of the oil inlet cavity 25.

With the vane pump according to the embodiment of the present disclosure, when the engine is not started, the pilot valve spool 12 is in the initial position under the action of the first elastic member 141, and the feedback chamber 24 is in communication with the first chamber 14.

At the time of engine start, a part of the lubricating oil in the lubricating oil passage of the engine flows into the second chamber 15 and acts on the first piston ring 121 and the second piston ring 122. At this time, because the pressure in the lubricating oil passage of the engine is low, the two-position three-way directional control valve 13 is placed at the right position, and the oil inlet p of the two-position three-way directional control valve 13 is communicated with the first working oil port a (see fig. 3). And the other part of lubricating oil in the lubricating oil passage of the engine passes through the oil inlet p of the two-position three-way reversing valve 13 and the first working oil port a and then enters the third cavity 16. Then, the area of action of the two lubricating oils on the pilot valve core 12 at this time is the sum of the cross-sectional areas of the first piston ring 121 and the pilot valve core 12. The first chamber 14 communicates with the feedback chamber 24. Therefore, the lubricating oil in the feedback chamber 24 is drained to the crankcase through the first chamber 14, the slider 23 is in the original position, the volume of the feedback chamber 24 is the smallest, and the volume of the oil inlet chamber 25 is the largest at this time, and the displacement of the vane pump is the largest. This provides sufficient lubrication during engine start-up.

Along with the starting of the engine, the pressure of a lubricating oil passage of the engine is gradually increased under the action of the vane pump. If the engine is in a low-pressure mode, at the moment, the two-position three-way reversing valve 13 is arranged at the right position, and the oil inlet p of the two-position three-way reversing valve 13 is communicated with the first working oil port a. Similarly, the acting area of the two lubricating oils on the pilot valve core 12 is the sum of the cross-sectional areas of the first piston ring 121 and the pilot valve core 12. As the pressure in the lubricating oil passage of the engine increases, the amount of upward (direction in fig. 2) movement of the pilot spool 12 increases, so that the second chamber 15 communicates with the feedback chamber 24. Therefore, at this time, the lubricating oil in the lubricating oil passage of the engine enters the feedback chamber 24 and acts on the stopper 231, so that the slider 23 rotates, the volume of the feedback chamber 24 becomes large, the volume of the oil inlet chamber 25 becomes small, and the displacement of the vane pump decreases. This limits the maximum pressure of the lubricating oil so that the engine is always in the low pressure mode.

After the engine is started, if the engine is in the process of switching from the low-pressure mode to the high-pressure mode, a part of lubricating oil in a lubricating oil passage of the engine flows into the second cavity 15 and acts on the first piston ring 121 and the second piston ring 122. Because the two-position three-way reversing valve 13 is arranged at the left position, and the oil inlet p of the two-position three-way reversing valve 13 is communicated with the second working oil port b, the other part of lubricating oil in the lubricating oil passage of the engine flows through the oil inlet p of the two-position three-way reversing valve 13 and the second working oil port b and then is discharged to the crankcase of the engine. Then, the area of action of the two lubricating oils on the pilot valve core 12 at this time is the difference between the cross-sectional areas of the first piston ring 121 and the second piston ring 122. The first chamber 14 communicates with the feedback chamber 24. Therefore, the lubricating oil in the feedback chamber 24 is drained to the crankcase through the first chamber 14, the slider 23 moves to the original position, the volume of the feedback chamber 24 decreases, the volume of the oil inlet chamber 25 increases, and the displacement of the vane pump increases. This may further increase the pressure of the lubricating oil in the engine, thereby facilitating switching of the engine from the low pressure mode to the high pressure mode.

After the engine is in a high-pressure state, the pressure of a lubricating oil passage of the engine is gradually increased under the action of the vane pump. At this time, the two-position three-way reversing valve 13 is arranged at the left position, and the oil inlet p of the two-position three-way reversing valve 13 is communicated with the second working port. Similarly, the area of action of the two lubricating oils on the pilot valve core 12 is the difference between the cross-sectional areas of the first piston ring 121 and the second piston ring 122. Due to the increased pressure in the oil gallery of the engine, the pilot spool 12 is pushed to move upward (in the direction of fig. 2) even if there is no oil pressure in the third chamber 16, so that the second chamber 15 communicates with the feedback chamber 24. Therefore, at this time, the lubricating oil in the lubricating oil passage of the engine enters the feedback chamber 24 and acts on the stopper 231, so that the slider 23 rotates, the volume of the feedback chamber 24 becomes large, the volume of the oil inlet chamber 25 becomes small, and the displacement of the vane pump decreases. This limits the maximum pressure of the lubricating oil so that the engine is always in high pressure mode.

That is to say, the vane pump that this embodiment provided not only can adjust the discharge capacity of vane pump in a flexible way, can also divide into two kinds of modes and go to inject the maximum pressure of lubricating oil to make the vane pump can be according to the different stages that automobile engine was located, the discharge capacity of flexible adjustment vane pump has reduced the friction loss.

Exemplarily, in the low pressure mode the maximum pressure of the lubricating oil in the lubrication system is 2 bar. In the high-pressure mode, the maximum pressure of the lubricating oil in the lubricating system is 4 bar.

When the feedback chamber 24 communicates with the first chamber 14, the slider 23 is pushed by the second elastic member 2311 to return, so that the lubricating oil in the feedback chamber 24 is discharged to the crankcase of the engine through the first chamber 14.

Illustratively, the pilot module 1 further includes a pilot channel 100, and the pilot channel 100 functions as a lubricating oil channel for communicating the second cavity 15 with the engine, an oil inlet of the two-position three-way directional valve 13, and a lubricating oil channel for the engine.

Referring again to fig. 2, the pilot housing 11 has a first through hole 113 and a second through hole 114, the first through hole 113 communicates the lubricating oil passage with the second chamber 15, and the second through hole 114 communicates with the feedback chamber 24 and communicates with either the first chamber 14 or the second chamber 15 as the pilot spool 12 moves.

Referring again to fig. 1, the outer wall of the slider 23 has a semi-cylindrical block 232, the inner wall of the pump housing 21 has a slot 211, the semi-cylindrical block 232 is rotatably inserted into the slot 211 along its own axial direction, and the rotation axis of the semi-cylindrical block 232 is parallel to the rotation axis of the rotor blade assembly 22.

In the above embodiment, the semi-cylindrical block 232 is inserted into the insertion slot 211, so that the rotation of the sliding block 23 can be better realized, and the stop block 231 is acted by the lubricating oil in the feedback cavity 24, and the displacement of the vane pump is further adjusted.

Illustratively, the arc surface of the semi-cylindrical block 232 and the inner wall of the slot 211 are matched and spaced so that the slider 23 can rotate smoothly.

Alternatively, the outer wall of the slider 23 may have a pin 233, the pin 233 may be parallel to the rotational axis of the rotor blade assembly 22, the inner wall of the pump housing 21 may have a receptacle 212, one end of the pin 233 may be coupled to the slider 23, and the other end of the pin 233 may be rotatably inserted into the receptacle 212.

In the above embodiment, on the one hand, the pin 233 is inserted into the insertion hole 212, so that the slider 23 can be better rotated, and thus the baffle plate is acted by the lubricating oil in the feedback cavity 24, and the displacement of the vane pump is adjusted. On the other hand, the slider 23 can be effectively prevented from coming off the pump housing 21.

With reference to fig. 1, one end of the pilot valve core 12 protrudes out of the first piston ring 121, the first elastic element 141 is a first spring, a first end of the first spring is sleeved on the pilot valve core 12 and abuts against a first side wall of the first piston ring 121, and a second end of the first spring is connected to an inner wall of the first cavity 14.

In the above embodiment, the first spring is sleeved on the pilot valve spool 12, which not only facilitates connection between the first spring and the pilot valve spool 12, but also guides the expansion and contraction of the first spring.

Alternatively, the second elastic member 2311 is a second spring, the inner wall of the pump housing 21 has a counter bore 213, the other side surface of the stopper 231 has a groove 2312, a first end of the second spring is inserted into the counter bore 213, and a second end of the second spring is inserted into the groove 2312.

In the above embodiment, counterbore 213 facilitates the installation of the first end of the second spring, thereby facilitating the connection of the second spring to the inner wall of pump housing 21. The groove 2312 facilitates installation of the second end of the second spring, thereby facilitating connection of the second spring to the stop 231. That is, the second spring is better installed by counterbore 213 and groove 2312.

Alternatively, the rotor blade assembly 22 includes a rotor 221 and a plurality of blades 222, the rotor 221 is rotatably disposed in the pump housing 21, each blade 222 is slidably inserted into the rotor 221, the sliding direction of the blade 222 is perpendicular to the axis of the rotor 221, and one side of each blade 222 is in sliding contact with the inner wall of the sliding block 23.

In the above embodiment, the vane 222 is acted on by the lubricating oil, so that the vane 222 slides on the rotor 221, thereby adjusting the volumes of the oil inlet chamber 25 and the working chamber 26, and achieving the suction and the oil discharge.

Illustratively, when the lubrication action stopper 231 in the feedback chamber 24 rotates clockwise, the second elastic member 2311 is compressed, and the eccentricity of the rotor 221 and the slider 23 is increased, thereby decreasing the vane pump displacement. Otherwise, the displacement of the vane pump is increased.

Optionally, the vane pump further comprises a positioning ring 27, the positioning ring 27 is movably disposed in the rotor 221, an axis of the positioning ring 27 is parallel to an axis of the rotor 221, and an outer peripheral wall of the positioning ring 27 is in sliding contact with the other side edge of each vane 222.

In the above embodiment, the positioning ring 27 functions to position the blade 222 and to limit the blade 222 in the radial direction of the slider 23.

Optionally, a pressure tap 241 is inserted into the inner wall of the feedback chamber 24.

In the above embodiment, the pressure measuring connector 241 is used to communicate with a pressure gauge, and can measure not only the pressure of the feedback chamber 24 but also the sealing property of the feedback chamber 24.

Illustratively, in a non-test state, a plug (not shown) is inserted into the pressure tap 241, thereby sealing the pressure tap 241 and preventing the overflow of the lubricating oil. In the test state, the plug is removed from the pressure measuring joint 241 and connected to a pressure gauge, so that the pressure can be measured.

Optionally, the pilot housing 11 has a first oil drainage port 111, the first cavity 14 is communicated with a crankcase of the engine through the first oil drainage port 111, a first adjusting screw 1111 is inserted into the first oil drainage port 111, and the first adjusting screw 1111 is used to adjust an opening degree of the first oil drainage port 111.

In the above embodiment, the first adjusting screw 1111 may adjust the opening degree of the first oil drainage port 111, so as to adjust the speed of oil drainage of the first oil drainage port 111.

Optionally, the pilot housing 11 has a second oil drainage port 112, the third cavity 16 is communicated with the crankcase of the engine through the second oil drainage port 112, a second adjusting screw 1121 is inserted into the second oil drainage port 112, and the second adjusting screw 1121 is used to adjust the opening degree of the second oil drainage port 112.

In the above embodiment, the second adjusting screw 1121 may adjust the opening degree of the second oil drainage port 112, so as to adjust the speed of oil drainage of the second oil drainage port 112.

For example, sealing rings 200 are respectively clamped between the first adjusting screw 1111 and the first pressure relief opening and between the second adjusting screw 1121 and the second oil relief opening 112, so that leakage is prevented.

In this embodiment, the two-position three-way selector valve 13 is a solenoid valve.

In the above embodiment, the two-position three-way directional valve 13 is an electromagnetic valve, which is convenient to control, high in sensitivity and more accurate in control.

Illustratively, when the two-position three-way reversing valve 13 is powered on, the valve core of the two-position three-way reversing valve 13 is arranged at the right position, and at the moment, the oil inlet p of the two-position three-way reversing valve 13 is communicated with the first working oil port a. When the two-position three-way reversing valve 13 is powered off, the valve core of the two-position three-way reversing valve 13 is arranged at the left position, and the oil inlet p of the two-position three-way reversing valve 13 is communicated with the second working oil port b.

The working principle of the vane pump is briefly explained as follows:

at the time of engine start, a part of the lubricating oil in the lubricating oil passage of the engine flows into the second chamber 15 and acts on the first piston ring 121 and the second piston ring 122. At this time, because the pressure in the lubricating oil passage of the engine is low, the two-position three-way directional control valve 13 is placed at the right position, and the oil inlet p of the two-position three-way directional control valve 13 is communicated with the first working oil port a (see fig. 3). And the other part of lubricating oil in the lubricating oil passage of the engine passes through the oil inlet p of the two-position three-way reversing valve 13 and the first working oil port a and then enters the third cavity 16. Then, the area of action of the two lubricating oils on the pilot valve core 12 at this time is the sum of the cross-sectional areas of the first piston ring 121 and the pilot valve core 12. The first chamber 14 communicates with the feedback chamber 24. Therefore, the lubricating oil in the feedback chamber 24 is drained to the crankcase through the first chamber 14, the slider 23 is in the original position, the volume of the feedback chamber 24 is the smallest, and the volume of the oil inlet chamber 25 is the largest at this time, and the displacement of the vane pump is the largest. This provides sufficient lubrication during engine start-up.

Along with the starting of the engine, the pressure of a lubricating oil passage of the engine is gradually increased under the action of the vane pump. If the engine is in a low-pressure mode, at the moment, the two-position three-way reversing valve 13 is arranged at the right position, and the oil inlet p of the two-position three-way reversing valve 13 is communicated with the first working oil port a. Similarly, the acting area of the two lubricating oils on the pilot valve core 12 is the sum of the cross-sectional areas of the first piston ring 121 and the pilot valve core 12. As the pressure in the lubricating oil passage of the engine increases, the amount of upward (direction in fig. 2) movement of the pilot spool 12 increases, so that the second chamber 15 communicates with the feedback chamber 24. Therefore, at this time, the lubricating oil in the lubricating oil passage of the engine enters the feedback chamber 24 and acts on the stopper 231, so that the slider 23 rotates, the volume of the feedback chamber 24 becomes large, the volume of the oil inlet chamber 25 becomes small, and the displacement of the vane pump decreases. This limits the maximum pressure of the lubricating oil so that the engine is always in the low pressure mode.

After the engine is started, if the engine is in the process of switching from the low-pressure mode to the high-pressure mode, a part of lubricating oil in a lubricating oil passage of the engine flows into the second cavity 15 and acts on the first piston ring 121 and the second piston ring 122. Because the two-position three-way reversing valve 13 is arranged at the left position, and the oil inlet p of the two-position three-way reversing valve 13 is communicated with the second working oil port b, the other part of lubricating oil in the lubricating oil passage of the engine flows through the oil inlet p of the two-position three-way reversing valve 13 and the second working oil port b and then is discharged to the crankcase of the engine. Then, the area of action of the two lubricating oils on the pilot valve core 12 at this time is the difference between the cross-sectional areas of the first piston ring 121 and the second piston ring 122. The first chamber 14 communicates with the feedback chamber 24. Therefore, the lubricating oil in the feedback chamber 24 is drained to the crankcase through the first chamber 14, the slider 23 moves to the original position, the volume of the feedback chamber 24 decreases, the volume of the oil inlet chamber 25 increases, and the displacement of the vane pump increases. This may further increase the pressure of the lubricating oil in the engine, thereby facilitating switching of the engine from the low pressure mode to the high pressure mode.

After the engine is in a high-pressure state, the pressure of a lubricating oil passage of the engine is gradually increased under the action of the vane pump. At this time, the two-position three-way reversing valve 13 is arranged at the left position, and the oil inlet p of the two-position three-way reversing valve 13 is communicated with the second working port. Similarly, the area of action of the two lubricating oils on the pilot valve core 12 is the difference between the cross-sectional areas of the first piston ring 121 and the second piston ring 122. Due to the increased pressure in the oil gallery of the engine, the pilot spool 12 is pushed to move upward (in the direction of fig. 2) even if there is no oil pressure in the third chamber 16, so that the second chamber 15 communicates with the feedback chamber 24. Therefore, at this time, the lubricating oil in the lubricating oil passage of the engine enters the feedback chamber 24 and acts on the stopper 231, so that the slider 23 rotates, the volume of the feedback chamber 24 becomes large, the volume of the oil inlet chamber 25 becomes small, and the displacement of the vane pump decreases. This limits the maximum pressure of the lubricating oil so that the engine is always in high pressure mode.

The above description is intended to be exemplary only and not to limit the present disclosure, and any modification, equivalent replacement, or improvement made without departing from the spirit and scope of the present disclosure is to be considered as the same as the present disclosure.