A variable control system of anti-logic proportional valve and vane pump

Abstract

An anti-logic proportional valve and a vane pump variable control system relate to the technical field of automobile oil pump displacement control. The anti-logic proportional valve comprises a valve body, a plunger and a spring. The valve body is provided with a valve hole for accommodating the plunger and the spring. The valve body is provided with an A port, a P port and a T port connected to the valve hole. The outer peripheral surface of the plunger is provided with a first annular oil groove and a second annular oil groove. The plunger is also provided with a radial hole communicating with the second annular oil groove. An axial hole connecting the radial hole and the T port is also provided in the middle of the plunger. The precision of the valve body hole of the proportional valve is easy to ensure. The invention also relates to a vane pump variable control system using an anti-logic proportional valve. The control system has a simple structure and installation, and a regular mechanical valve control structure, which is conducive to the stability of the vane pump output pressure.

Description

Technical Field

[0001] The present invention relates to the technical field of automobile oil pump displacement control, in particular to an anti-logic proportional valve and a vane pump variable control system. Background Art

[0002] Since the operation of the automobile engine oil pump also consumes a part of the engine power, the traditional fixed-displacement oil pump is designed according to the oil pump demand at the engine hot idle speed. The oil pump supply flow rate increases almost linearly with the speed change. At high speed, the output oil volume is too much. When the engine speed rises to a certain level, the oil pump output flow rate will be greater than the engine demand. An oil pump pressure limiting valve is required to bypass the excess oil, resulting in energy waste. To reduce the power consumption of the oil pump, the oil pump supply volume needs to be matched with the actual oil demand of the engine, and the use of a variable displacement controlled oil pump can meet this requirement.

[0003] The Chinese utility model application patent No. 2015106253728 discloses a control system for a main oil channel feedback single-chamber two-stage variable displacement vane pump. The system enables the single-chamber feedback variable displacement vane pump to achieve two-stage variable displacement, but the control system has the following defects: since the oil passage chamber of the pilot valve is always connected to the main oil channel, and the oil passage chamber is adjacent to the spring chamber, in the high-pressure mode, the high-pressure oil in the oil passage chamber can easily leak into the spring chamber through the gap between the valve core surface and the valve sleeve, and then flow into the feedback pressure oil chamber, which is equivalent to opening the pilot valve in advance, thereby affecting the control accuracy and causing the oil pump to change the variable in advance. Summary of the Invention

[0004] In view of the defect in the above-mentioned prior art that the control accuracy is difficult to ensure, the technical problem to be solved by the present invention is to provide an inverse logic proportional valve, in which the accuracy of the inner hole of the valve body is easy to ensure.

[0005] In order to solve the above technical problems, the technical solution of the present invention is: an anti-logic proportional valve, the anti-logic proportional valve includes a valve body, a plunger and a spring, the valve body is provided with a valve hole for accommodating the plunger and the spring, the valve body is provided with an A port, a P port and a T port connected to the valve hole; the outer peripheral surface of the plunger is provided with a first annular oil groove, and the first annular oil groove can make the A port and the P port communicate with each other in the initial state of the anti-logic proportional valve; the cross-sectional area of ​​the groove wall of the first annular oil groove close to the spring is larger than the cross-sectional area on the other side, thereby forming an area difference; a second annular oil groove is also provided on the plunger away from the spring in the first annular oil groove, and the second annular oil groove can communicate with the A port in the open state of the anti-logic proportional valve, and a radial hole communicating with the second annular oil groove is also provided on the plunger, and an axial hole connecting the radial hole and the T port is also provided in the middle of the plunger.

[0006] Aiming at the defect of complex control system structure in the existing technology, a variable control system for a vane pump is proposed. The control system has simple structure and installation, regular valve control structure, which is conducive to ensuring the stability of the vane pump output pressure.

[0007] To solve the above technical problems, the technical solution adopted is: a vane pump variable control system, including a vane pump, an oil outlet, a main oil channel, an oil pan and a mechanical valve. The vane pump includes a pump body, a feedback pressure oil chamber, a rotor and a variable slider; the control system also includes an inverse logic proportional valve, which includes a valve body, a plunger and a spring. The valve body is provided with a valve hole for accommodating the plunger and spring. The valve body is provided with an A port, a P port and a T port connected to the valve hole; a first annular oil groove is provided on the outer peripheral surface of the plunger, which can make the A port and the P port communicate with each other in the initial state of the anti-logic proportional valve; the cross-sectional area of ​​the groove wall of the first annular oil groove close to the spring is larger than the cross-sectional area on the other side, thereby forming an area difference; a second annular oil groove is also provided on the plunger away from the spring of the first annular oil groove, which can communicate with the A port under the action of the electromagnetic force and oil pressure of the anti-logic proportional valve, and the electromagnetic force of the anti-logic proportional valve is controlled by the ECU; a radial hole communicating with the second annular oil groove is also provided on the plunger, and an axial hole connecting the radial hole and the T port is also provided in the middle of the plunger; the P port is connected to the main oil channel, and the A port is connected to the mechanical valve.

[0008] The mechanical valve includes a valve sleeve, a valve core and a spring. The valve core includes an intermediate shaft and discs respectively arranged at both ends of the intermediate shaft. The valve chamber of the mechanical valve is divided into a control chamber, an oil passage chamber and a spring chamber by the discs at both ends of the intermediate shaft; the control chamber is always connected to the main oil channel, and the spring chamber is always connected to the A port of the anti-logic proportional valve. The valve sleeve is provided with a first oil channel for connecting to the oil pan and a second oil channel for connecting to the feedback pressure oil chamber.

[0009] When the A port and P port of the anti-logic proportional valve are connected, and the A port and T port are not connected, the pressure oil flows through the oil outlet of the vane pump through the main oil channel into the P port of the anti-logic proportional valve and the control chamber of the mechanical valve. At this time, the P port, A port and the control chamber of the mechanical valve of the anti-logic proportional valve are all filled with pressure oil.

[0010] Before the oil pressure in the main oil channel reaches the minimum opening pressure point, the pressure oil flows to the spring chamber of the mechanical valve through the P port and the A port. The valve core of the mechanical valve does not move. The pressure oil in the feedback pressure oil chamber flows into the oil pan through the second oil channel and the first oil channel of the mechanical valve in turn.

[0011] When the oil pressure in the main oil channel reaches the lowest opening pressure point, the inverse logic proportional valve adjusts the size of the electromagnetic force under the control of the ECU. The plunger of the inverse logic proportional valve compresses the spring under the action of the electromagnetic force and oil pressure. At this time, the A port and the P port of the inverse logic proportional valve are blocked, and the A port and the T port are connected; the channel between the main oil channel and the P port is closed, and the pressure oil in the spring chamber of the mechanical valve is discharged into the oil pan through the A port and the T port of the inverse logic proportional valve. The oil pressure generated by the pressure oil in the control chamber of the mechanical valve pushes the valve core of the mechanical valve toward the spring chamber. Part of the pressure oil in the control chamber flows from the second oil channel into the feedback pressure oil chamber to directly act on the variable slider, reducing the eccentricity between the variable slider and the rotor, thereby reducing the output displacement.

[0012] Before the oil pressure in the main oil channel reaches the maximum opening pressure point, the pressure oil flows to the spring chamber of the mechanical valve through the P port and the A port. The valve core of the mechanical valve does not move. The pressure oil in the feedback pressure oil chamber flows into the oil pan through the second oil channel and the first oil channel of the mechanical valve in turn.

[0013] When the oil pressure in the main oil channel reaches the maximum pressure opening point, the ECU controls the inverse logic proportional valve and adjusts the electromagnetic force of the inverse logic proportion to 0. Under the action of the oil pressure in the main oil channel, the inverse logic proportional valve pushes the plunger to compress the spring, so that port A and port T are connected, and the channel between the main oil channel and port P is closed. The pressure oil in the spring chamber is discharged into the oil pan through port A and port T of the inverse logic proportional valve. The pressure oil in the control chamber of the mechanical valve generates oil pressure to push the valve core of the mechanical valve toward the spring chamber. Part of the pressure oil in the control chamber flows from the second oil channel into the feedback pressure oil chamber to directly act on the variable slider, reducing the eccentricity between the variable slider and the rotor, thereby reducing the output displacement.

[0014] The beneficial effects achieved by the present invention are as follows: the hole accuracy of the valve body of the anti-logic proportional valve is easy to ensure, and the electromagnetic force of the anti-logic proportional valve can be adjusted by the ECU; the structure of the vane pump variable control system is simple to install; the mechanical valve control structure is regular, which is beneficial to the stability of the vane pump output pressure, the vane pump does not play a decisive role in the minimum opening pressure point, is easy to design, and can be universally designed. BRIEF DESCRIPTION OF THE DRAWINGS

[0015] Figure 1 This is an enlarged schematic diagram of the initial state of the inverse logic proportional valve in an embodiment of the present invention;

[0016] Figure 2 This is an enlarged schematic diagram of the inverse logic proportional valve in the embodiment of the present invention when it is in the open state;

[0017] Figure 3 is a schematic diagram of a control system in an initial state according to an embodiment of the present invention;

[0018] Figure 4 is a schematic diagram of a control system in an embodiment of the present invention when in an on state;

[0019] In the picture:

[0020] 1——Vane pump 11——Feedback pressure oil chamber

[0021] 2 - oil outlet 3 - main oil channel 4 - safety valve

[0022] 5 - filter 6 - motor 7 - oil pan

[0023] 8——Negative logic proportional valve 81——Valve body 82——Port A

[0024] 83——P port 84——T port 85——plunger

[0025] 86 - first annular oil groove 87 - second annular oil groove 88 - radial hole

[0026] 89——Axial hole 9——Mechanical valve 91——Valve sleeve

[0027] 91a - first oil passage 91b - second oil passage 92 - control chamber

[0028] 93——Oil chamber 94——Spring chamber 95——Valve core. DETAILED DESCRIPTION

[0029] In order to facilitate understanding by those skilled in the art, the present invention will be further described below with reference to embodiments and drawings. The contents mentioned in the embodiments are not intended to limit the present invention.

[0030] In the description of the present invention, it should be noted that, unless otherwise specified and limited, the terms "connected", "connected" and "connected" should be understood in a broad sense. For example, internal connectivity can be direct connection or indirect connection through an intermediate medium. For ordinary technicians in this field, the specific meaning of the terms can be understood according to the specific circumstances.

[0031] Example 1

[0032] like Figure 1 、 2As shown, an inverse logic proportional valve, the inverse logic proportional valve 8 includes a valve body 81, a plunger 85 and a spring. The valve body 81 is provided with a valve hole for accommodating the plunger 85 and the spring. The valve body 85 is provided with an A port 82, a P port 83 and a T port 84 communicating with the valve hole; the outer peripheral surface of the plunger 85 is provided with a first annular oil groove 86, which enables the A port 82 and the P port 83 to communicate with each other in the initial state of the inverse logic proportional valve 8; the cross-sectional area of ​​the groove wall of the first annular oil groove 86 close to the spring is larger than the cross-sectional area on the other side, thereby forming an area difference; a second annular oil groove 87 is further provided on the plunger 85 away from the spring in the first annular oil groove 86, which can communicate with the A port 82 when the inverse logic proportional valve 8 is in the open state; the plunger 85 is further provided with a radial hole 88 communicating with the second annular oil groove 87, and an axial hole 89 connecting the radial hole 88 and the T port 84 is further provided in the middle of the plunger 85.

[0033] Example 2

[0034] like Figures 1 to 4 As shown, a vane pump variable control system includes a vane pump 1, an oil outlet 2, a main oil channel 3, an oil pan 7, and a mechanical valve 9. The vane pump 1 includes a pump body, a feedback pressure oil chamber 11, a rotor, and a variable slider. The control system also includes an inverse logic proportional valve 8, which includes a valve body 81, a plunger 85, and a spring. The valve body 81 is provided with a valve hole for accommodating the plunger 85 and the spring. The valve body 85 is provided with an A port 82, a P port 83 and a T port 84 which are connected to the valve hole; a first annular oil groove 86 is provided on the outer peripheral surface of the plunger 85, which can make the A port 82 and the P port 83 communicate with each other in the initial state of the anti-logic proportional valve 8; the cross-sectional area of ​​the groove wall of the first annular oil groove 86 close to the spring is larger than the cross-sectional area on the other side, thereby forming an area difference; a second annular oil groove 87 is also provided on the plunger 85 away from the spring of the first annular oil groove 86, and the second annular oil groove 87 can communicate with the A port 82 under the action of the electromagnetic force and oil pressure of the anti-logic proportional valve 8, and the magnitude of the electromagnetic force of the anti-logic proportional valve 8 is controlled by the ECU; a radial hole 88 communicating with the second annular oil groove 87 is also provided on the plunger 85, and an axial hole 89 connecting the radial hole 88 and the T port 84 is also provided in the middle of the plunger 85; the P port 83 is connected to the main oil channel 3, and the A port 82 is connected to the mechanical valve 9.

[0035] Specifically, the mechanical valve 9 includes a valve sleeve 91, a valve core 95 and a spring. The valve core 95 includes an intermediate shaft and discs respectively arranged at both ends of the intermediate shaft. The valve chamber of the mechanical valve 9 is divided into a control chamber 92, an oil passage chamber 93 and a spring chamber 94 by the discs at both ends of the intermediate shaft; the control chamber 92 is always connected to the main oil channel 3, and the spring chamber 94 is always connected to the A port 82 of the anti-logic proportional valve 8. The valve sleeve 91 is provided with a first oil channel 91a for connecting to the oil pan 7 and a second oil channel 91b for connecting to the feedback pressure oil chamber 11.

[0036] Specifically, if Figure 3 As shown, in the control system, when the A port 82 and the P port 83 of the anti-logic proportional valve 8 are connected, and the A port 82 and the T port 84 are not connected; the pressure oil flows through the oil outlet 2 of the vane pump 1 through the main oil channel 3 into the P port 83 of the anti-logic proportional valve 8 and the control chamber 92 of the mechanical valve 9. At this time, the P port 83, the A port 82 of the anti-logic proportional valve 8 and the control chamber 92 of the mechanical valve 9 are all filled with pressure oil.

[0037] Before the oil pressure in the main oil channel 3 reaches the minimum opening pressure point, the pressure oil flows through the P port 83 and the A port 82 to the spring chamber 94 of the mechanical valve 9. The valve core 95 of the mechanical valve 9 does not move. The pressure oil in the feedback pressure oil chamber 11 flows into the oil pan 7 through the second oil channel 91b and the first oil channel 91a of the mechanical valve 9 in turn.

[0038] like Figure 4 As shown, when the oil pressure in the main oil channel 3 reaches the minimum opening pressure point, the inverse logic proportional valve 8 adjusts the magnitude of the electromagnetic force under the control of the ECU, and the plunger 85 of the inverse logic proportional valve 8 compresses the spring under the action of the electromagnetic force and the oil pressure. At this time, the A port 82 and the P port 83 of the inverse logic proportional valve 8 are blocked, and the A port 82 and the T port 84 are connected; the passage between the main oil channel 2 and the P port 83 is closed, and the pressure oil in the spring chamber 94 of the mechanical valve 9 is discharged into the oil pan 7 through the A port 82 and the T port 84 of the inverse logic proportional valve 8. The oil pressure generated by the pressure oil in the control chamber 92 of the mechanical valve 9 pushes the valve core 95 of the mechanical valve 9 toward the spring chamber 94. Part of the pressure oil in the control chamber 92 flows from the second oil channel 91b into the feedback pressure oil chamber 11 and directly acts on the variable slider, reducing the eccentricity between the variable slider and the rotor, thereby reducing the output displacement.

[0039] Specifically, if Figure 3 As shown, before the oil pressure in the main oil channel 3 reaches the maximum opening pressure point, the pressure oil flows through the P port 83 and the A port 82 to the spring chamber 94 of the mechanical valve 9, the valve core 95 of the mechanical valve 9 does not move, and the pressure oil in the feedback pressure oil chamber 11 flows into the oil pan 7 through the second oil channel 91b and the first oil channel 91a of the mechanical valve 9 in sequence.

[0040] like Figure 4As shown, when the oil pressure in the main oil gallery 3 reaches the maximum pressure opening point, the ECU controls the inverse logic proportional valve 8 and adjusts the electromagnetic force of the inverse logic proportional valve 8 to 0. Under the action of the oil pressure in the main oil gallery 3, the inverse logic proportional valve 8 pushes the plunger 85 to compress the spring, so that the A port 82 and the T port 84 are connected. The passage between the main oil gallery 3 and the P port 83 is closed, and the pressurized oil in the spring chamber 94 is discharged into the oil pan 7 through the A port 82 and the T port 84 of the inverse logic proportional valve 8. The pressurized oil in the control chamber 92 of the mechanical valve 9 generates oil pressure to push the valve core 95 of the mechanical valve 9 toward the spring chamber 94. Part of the pressurized oil in the control chamber 92 flows from the second oil gallery 91b into the feedback pressure oil chamber 11 to directly act on the variable slider, reducing the eccentricity between the variable slider and the rotor, thereby reducing the output displacement.

[0041] Specifically, assuming that the opening pressure of the inverse logic proportional valve 8 is P, the area difference between the groove walls on both sides of the first annular oil groove of the inverse logic proportional valve 8 is S, the spring force of the inverse logic proportional valve 8 is F1, and the force of the electromagnetic force on the inverse logic proportional valve is F2, that is, P×S+F2=F1. The control system can change the opening pressure P by adjusting the electromagnetic force F2 of the inverse logic proportional valve 8, that is, at the minimum opening pressure point P, the required electromagnetic force is large; at the maximum opening pressure point, the required electromagnetic force is 0.

[0042] The hole accuracy of the valve body of the anti-logic proportional valve of the present invention is easy to ensure, and the electromagnetic force of the anti-logic proportional valve can also be adjusted by the ECU; the vane pump variable control system structure is simple to install, and the mechanical valve control structure is regular, which is conducive to the stability of the vane pump output pressure; the vane pump does not play a decisive role in the minimum opening pressure point, is easy to design, and can be universally designed.

[0043] The above embodiments are preferred implementation schemes of the present invention. In addition, the present invention can also be implemented in other ways. Any obvious replacement without departing from the concept of the present technical solution is within the scope of protection of the present invention.

[0044] In order to make it easier for ordinary technicians in this field to understand the improvements of the present invention over the prior art, some drawings and descriptions of the present invention have been simplified, and for the sake of clarity, some other elements are omitted in this application document. Ordinary technicians in this field should realize that these omitted elements may also constitute the content of the present invention.

Claims

1. A vane pump variable control system, comprising: A vane pump (1), an oil outlet (2), a main oil channel (3), an oil pan (7) and a mechanical valve (9), wherein the vane pump (1) comprises a pump body, a feedback pressure oil chamber (11), a rotor and a variable slider; characterized in that: the control system further comprises an inverse logic proportional valve (8), the inverse logic proportional valve (8) comprises a valve body (81), a plunger (85) and a spring, the valve body (81) is provided with a valve hole for accommodating the plunger (85) and the spring, the valve body (81) is provided with an A port (82), a P port (83) and a T port (84) communicating with the valve hole; the outer peripheral surface of the plunger (85) is provided with A first annular oil groove (86) is provided. The first annular oil groove (86) enables the A port (82) and the P port (83) to communicate with each other in the initial state of the anti-logic proportional valve (8). The cross-sectional area of ​​the groove wall of the first annular oil groove (86) close to the spring is larger than the cross-sectional area of ​​the other side, thereby forming an area difference. A second annular oil groove (87) is also provided on the plunger (85) away from the spring of the first annular oil groove (86). The second annular oil groove (87) can communicate with the A port (82) under the action of the electromagnetic force of the anti-logic proportional valve (8) and the oil pressure. The magnitude of the electromagnetic force of the anti-logic proportional valve (8) is determined by ECU control; the plunger (85) is further provided with a radial hole (88) communicating with the second annular oil groove (87); an axial hole (89) connecting the radial hole (88) and the T port (84) is further provided in the middle of the plunger (85); the P port (83) is connected to the main oil passage (3); the A port (82) is connected to the mechanical valve (9); the mechanical valve (9) comprises a valve sleeve (91), a valve core (95) and a spring; the valve core (95) comprises an intermediate shaft and disks respectively arranged at both ends of the intermediate shaft; the valve chamber of the mechanical valve (9) is divided into a control chamber ( The control chamber (92) is always connected to the main oil passage (3), the spring chamber (94) is always connected to the A port (82) of the inverse logic proportional valve (8), and the valve sleeve (91) is provided with a first oil passage (91a) for connecting to the oil pan (7) and a second oil passage (91b) for connecting to the feedback pressure oil chamber (11); the first oil passage (91a) is connected to the oil passage chamber (93), and the second oil passage (91b) is selectively connected to the control chamber (92) or the oil passage chamber (93) depending on the position of the valve core (95) in the valve chamber.

2. The variable control system of the vane pump according to claim 1, characterized in that: The A port (82) of the anti-logic proportional valve (8) is in communication with the P port (83), while the A port (82) is not in communication with the T port (84); the pressure oil flows into the P port (83) of the anti-logic proportional valve (8) and the control chamber (92) of the mechanical valve (9) through the oil outlet (2) of the vane pump (1) and the main oil passage (3); at this time, the P port (83), the A port (82) of the anti-logic proportional valve (8) and the control chamber (92) of the mechanical valve (9) are all filled with pressure oil; before the oil pressure of the main oil passage (3) reaches the minimum opening pressure point, the pressure oil flows into the P port (83), the A port (82) and the control chamber (92) of the mechanical valve (9) through the main oil passage (3). (82) flows to the spring chamber (94) of the mechanical valve (9), the valve core (95) of the mechanical valve (9) does not move, and the pressure oil in the feedback pressure oil chamber (11) flows into the oil pan (7) through the second oil passage (91b), the oil passage chamber (93) and the first oil passage (91a) of the mechanical valve (9) in sequence; when the oil pressure in the main oil passage (3) reaches the minimum opening pressure point, the inverse logic proportional valve (8) adjusts the magnitude of the electromagnetic force under the control of the ECU, and the plunger (85) of the inverse logic proportional valve (8) compresses the spring under the action of the electromagnetic force and the oil pressure, and at this time The A port (82) and the P port (83) of the anti-logic proportional valve (8) are not connected, and the A port (82) and the T port (84) are connected; the passage between the main oil passage (3) and the P port (83) is closed, and the pressure oil in the spring chamber (94) of the mechanical valve (9) is discharged into the oil pan (7) through the A port (82) and the T port (84) of the anti-logic proportional valve (8); the oil pressure generated by the pressure oil in the control chamber (92) of the mechanical valve (9) pushes the valve core (95) of the mechanical valve (9) to move toward the spring chamber (94), and part of the pressure oil in the control chamber (92) is discharged from the second oil passage ( The pressure oil flows into the feedback pressure oil chamber (11) and directly acts on the variable slider, so that the eccentricity between the variable slider and the rotor is reduced, thereby reducing the output displacement; before the oil pressure in the main oil channel (3) reaches the maximum opening pressure point, the pressure oil flows to the spring chamber (94) of the mechanical valve (9) through the P port (83) and the A port (82), the valve core (95) of the mechanical valve (9) does not move, and the pressure oil in the feedback pressure oil chamber (11) flows into the oil pan (7) through the second oil channel (91b), the oil chamber (93), and the first oil channel (91a) of the mechanical valve (9) in sequence;When the oil pressure of the main oil channel (3) reaches the maximum pressure opening point, the ECU controls the anti-logic proportional valve (8) to adjust the electromagnetic force of the anti-logic proportional valve to 0. Under the action of the oil pressure of the main oil channel (3), the anti-logic proportional valve (8) pushes the plunger (85) to compress the spring, so that the A port (82) and the T port (84) are connected, and the passage between the main oil channel (3) and the P port (83) is closed. The pressure oil in the spring chamber (94) is discharged into the oil pan (7) through the A port (82) and the T port (84) of the anti-logic proportional valve (8). The pressure oil in the control chamber (92) of the mechanical valve (9) generates oil pressure to push the valve core (95) of the mechanical valve (9) to move toward the spring chamber (94). Part of the pressure oil in the control chamber (92) flows from the second oil channel (91b) into the feedback pressure oil chamber (11) to directly act on the variable slider, so that the eccentricity between the variable slider and the rotor is reduced, thereby reducing the output displacement. ;

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