CN112303283A - Variable control system for inverse logic proportional valve and vane pump - Google Patents
Variable control system for inverse logic proportional valve and vane pump Download PDFInfo
- Publication number
- CN112303283A CN112303283A CN202011179105.XA CN202011179105A CN112303283A CN 112303283 A CN112303283 A CN 112303283A CN 202011179105 A CN202011179105 A CN 202011179105A CN 112303283 A CN112303283 A CN 112303283A
- Authority
- CN
- China
- Prior art keywords
- oil
- port
- valve
- pressure
- cavity
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
- F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
- F16K11/06—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements
- F16K11/065—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members
- F16K11/07—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members with cylindrical slides
- F16K11/0716—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members with cylindrical slides with fluid passages through the valve member
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
- F01M1/00—Pressure lubrication
- F01M1/02—Pressure lubrication using lubricating pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
- F04C14/10—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
- F04C14/12—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using sliding valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
- F04C14/24—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
- F16K17/20—Excess-flow valves
- F16K17/22—Excess-flow valves actuated by the difference of pressure between two places in the flow line
- F16K17/24—Excess-flow valves actuated by the difference of pressure between two places in the flow line acting directly on the cutting-off member
- F16K17/28—Excess-flow valves actuated by the difference of pressure between two places in the flow line acting directly on the cutting-off member operating in one direction only
- F16K17/30—Excess-flow valves actuated by the difference of pressure between two places in the flow line acting directly on the cutting-off member operating in one direction only spring-loaded
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K27/00—Construction of housing; Use of materials therefor
- F16K27/04—Construction of housing; Use of materials therefor of sliding valves
- F16K27/041—Construction of housing; Use of materials therefor of sliding valves cylindrical slide valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K3/00—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing
- F16K3/30—Details
- F16K3/314—Forms or constructions of slides; Attachment of the slide to the spindle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
- F16K31/122—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a piston
- F16K31/1221—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a piston one side of the piston being spring-loaded
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16N—LUBRICATING
- F16N23/00—Special adaptations of check valves
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
Abstract
A variable control system of a reverse logic proportional valve and a vane pump relates to the technical field of displacement control of an automobile oil pump. The inverse logic proportional valve comprises a valve body, a plunger and a spring, wherein a valve hole for accommodating the plunger and the spring is formed in the valve body, and the valve body is provided with an A port, a P port and a T port which are communicated with 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 communicated with the second annular oil groove, and the middle of the plunger is also provided with an axial hole for connecting the radial hole and the T port; the valve body hole precision of the proportional valve is easy to guarantee; the invention also relates to a variable control system of the vane pump, which uses the inverse logic proportional valve. The control system is simple in structure installation, and the mechanical valve control structure is regular, so that the stability of the output pressure of the vane pump is facilitated.
Description
Technical Field
The invention relates to the technical field of automobile oil pump displacement control, in particular to a variable control system of an inverse logic proportional valve and a vane pump.
Background
Because the running of the engine oil pump of the automobile also consumes a part of engine power, the traditional fixed displacement oil pump is designed according to the oil pump demand when the engine is in hot idling, the oil supply flow of the oil pump is almost linearly increased along with the change of the rotating speed, the output oil quantity is excessive at high speed, when the rotating speed of the engine is increased to a certain degree, the output flow of the oil pump is larger than the demand of the engine, and an oil pump pressure limiting valve is needed to bypass redundant engine oil, thereby causing the waste of energy; to reduce the power consumption of the oil pump, the oil supply amount of the oil pump needs to be matched with the actual oil demand of the engine, and the oil pump using variable displacement control can meet the requirement.
The patent with the application number of 2015106253728 of the utility model discloses a control system of a main oil gallery feedback single-cavity two-stage variable displacement vane pump, this system makes the single-cavity feedback variable displacement vane pump realize the two-stage variable displacement, but this control system has following defect: because the oil passing cavity of the pilot valve is always communicated with the main oil duct and is adjacent to the spring cavity, high-pressure oil in the oil passing cavity easily leaks to the spring cavity through a gap between the peripheral surface of the valve core and the valve sleeve in a high-pressure mode and then flows into the feedback pressure oil cavity, which is equivalent to opening the pilot valve in advance, thereby influencing the control precision and enabling the oil pump to carry out variable in advance.
Disclosure of Invention
Aiming at the defect that the control precision is not easy to guarantee in the prior art, the invention aims to solve the technical problem of providing the inverse logic proportional valve, and the precision of the inner hole of the valve body is easy to guarantee.
In order to solve the technical problems, the technical scheme of the invention is as follows: a reverse logic proportional valve comprises a valve body, a plunger and a spring, wherein a valve hole for accommodating the plunger and the spring is formed in the valve body; the outer peripheral surface of the plunger is provided with a first annular oil groove which can enable the port A and the port P to be communicated with each other in the initial state of the inverse logic proportional valve; the sectional area of the groove wall of the first annular oil groove close to the spring is larger than that of the other side of the groove wall, so that an area difference is formed; the plunger of the first annular oil groove far away from the spring is also provided with a second annular oil groove, the second annular oil groove can be communicated with the port A in the opening state of the inverse logic proportional valve, the plunger is also provided with a radial hole communicated with the second annular oil groove, and the middle of the plunger is also provided with an axial hole for connecting the radial hole and the port T.
Aiming at the defect of complex structure of the control system in the prior art, the variable control system of the vane pump is provided, the control system is simple in structure installation, and the valve control structure is regular, so that the stability of the output pressure of the vane pump can be ensured.
In order to solve the technical problems, the adopted technical scheme is as follows: a variable control system of a vane pump comprises the vane pump, an oil outlet, a main oil duct, an oil pan and a mechanical valve, wherein the vane pump comprises a pump body, a feedback pressure oil cavity, a rotor and a variable sliding block; the control system also comprises a reverse logic proportional valve, the reverse logic proportional valve comprises a valve body, a plunger and a spring, a valve hole for accommodating the plunger and the spring is arranged in the valve body, and the valve body is provided with an A port, a P port and a T port which are communicated with the valve hole; the outer peripheral surface of the plunger is provided with a first annular oil groove which can enable the port A and the port P to be communicated with each other in the initial state of the inverse logic proportional valve; the sectional area of the groove wall of the first annular oil groove close to the spring is larger than that of the other side of the groove wall, so that an area difference is formed; a plunger of the first annular oil groove, which is far away from the spring, is also provided with a second annular oil groove, the second annular oil groove can be communicated with the port A under the action of the electromagnetic force and the oil pressure of the inverse logic proportional valve, and the electromagnetic force of the inverse logic proportional valve is controlled by the ECU; the plunger is also provided with a radial hole communicated with the second annular oil groove, and the middle of the plunger is also provided with an axial hole for connecting the radial hole and the T port; the port P is connected with the main oil duct, and the port A is connected with the mechanical valve.
The mechanical valve comprises a valve sleeve, a valve core and a spring, wherein the valve core comprises a middle shaft and discs arranged at two ends of the middle shaft respectively, and a valve cavity of the mechanical valve is divided into a control cavity, an oil passing cavity and a spring cavity by the discs at two ends of the middle shaft; the control cavity is always connected with the main oil duct, the spring cavity is always connected with the port A of the inverse logic proportional valve, and the valve sleeve is provided with a first oil duct used for connecting the oil pan and a second oil duct used for connecting the feedback pressure oil cavity.
The control system is arranged when the port A of the inverse logic proportional valve is communicated with the port P and the port A is not communicated with the port T; the pressure oil flows into the P port of the inverse logic proportional valve and the control cavity of the mechanical valve through the oil outlet of the vane pump through the main oil passage, and the P port and the A port of the inverse logic proportional valve and the control cavity of the mechanical valve are filled with the pressure oil at the moment.
Before the oil pressure of the main oil duct does not reach the lowest opening pressure point, pressure oil flows to a spring cavity of the mechanical valve through the port P and the port A, a valve core of the mechanical valve does not move, and the pressure oil of the feedback pressure oil cavity sequentially flows into the oil pan through the second oil duct and the first oil duct of the mechanical valve.
When the oil pressure of the main oil duct reaches the lowest opening pressure point, the reverse logic proportional valve adjusts the magnitude of electromagnetic force under the control of the ECU, a plunger of the reverse logic proportional valve compresses a spring under the action of the electromagnetic force and the oil pressure, at the moment, an A port and a P port of the reverse logic proportional valve are not communicated, and the A port is communicated with a T port; the main oil duct and the P port are closed, pressure oil in a spring cavity of the mechanical valve is discharged into an oil pan through an A port and a T port of the inverse logic proportional valve, oil pressure generated by the pressure oil in the control cavity of the mechanical valve pushes a valve core of the mechanical valve to move towards the spring cavity, and partial pressure oil in the control cavity flows into the feedback pressure oil cavity from the second oil duct to directly act on the variable slider, so that the eccentricity between the variable slider and the rotor is reduced, and the output displacement is reduced.
Before the oil pressure of the main oil duct does not reach the maximum opening pressure point, pressure oil flows to a spring cavity of the mechanical valve through the port P and the port A, a valve core of the mechanical valve does not move, and the pressure oil of the feedback pressure oil cavity sequentially flows into the oil pan through the second oil duct and the first oil duct of the mechanical valve.
When the oil pressure of the main oil duct reaches the maximum pressure opening point, the ECU controls the inverse logic proportional valve to adjust the electromagnetic force of the inverse logic proportion to 0, the inverse logic proportional valve pushes the plunger to compress the spring under the action of the oil pressure of the main oil duct, so that the port A is communicated with the port T, the passage of the main oil duct and the port P is closed, the pressure oil in the spring cavity is discharged into the oil pan through the port A and the port T of the inverse logic proportional valve, the pressure oil in the control cavity of the mechanical valve generates oil pressure to push the valve core of the mechanical valve to move towards the spring cavity, and partial pressure oil in the control cavity flows into the feedback pressure oil cavity from the second oil duct to directly act on the variable slider, so that the eccentricity between the variable slider and the rotor.
The invention has the following beneficial effects: the hole precision of the valve body of the inverse logic proportional valve is easy to guarantee, and the electromagnetic force of the inverse logic proportional valve can be adjusted through the ECU; the vane pump variable control system is simple in structure installation; the mechanical valve control structure is regular, the stability of the output pressure of the vane pump is facilitated, the vane pump does not play a decisive role in the lowest opening pressure point, and the mechanical valve control structure is easy to design and can be designed universally.
Drawings
FIG. 1 is an enlarged schematic view of an inverted logic proportional valve in an initial state according to an embodiment of the present invention;
FIG. 2 is an enlarged schematic view of an inverted logic proportional valve in an embodiment of the present invention in an open state;
FIG. 3 is a schematic diagram of the control system in an initial state according to an embodiment of the present invention;
FIG. 4 is a schematic diagram of the control system in an ON state according to an embodiment of the present invention;
in the figure:
1-vane pump 11-feedback pressure oil chamber
2-oil outlet 3-main oil gallery 4-safety valve
5-filter 6-motor 7-oil pan
8-inverse logic proportional valve 81-valve body 82-port A
83-P port 84-T port 85-plunger piston
86-first annular oil groove 87-second annular oil groove 88-radial hole
89-axial hole 9-mechanical valve 91-valve sleeve
91 a-first oil passage 91 b-second oil passage 92-control chamber
93-oil passing cavity 94-spring cavity 95-valve core.
Detailed Description
In order to facilitate understanding of those skilled in the art, the present invention will be further described with reference to the following examples and drawings, which are not intended to limit the present invention.
In the description of the present invention, it should be noted that unless otherwise specified and limited, the terms "connected," "connected," and "communicating" are to be construed broadly, for example, the internal communication may be directly connected or indirectly connected through an intermediate, and the specific meaning of the terms may be understood by those skilled in the art according to specific situations.
Example 1
As shown in fig. 1 and 2, the inverse logic proportional valve 8 comprises a valve body 81, a plunger 85 and a spring, wherein a valve hole for accommodating the plunger 85 and the spring is arranged in the valve body 81, and the valve body 85 is provided with an a port 82, a P port 83 and a T port 84 which are communicated with the valve hole; the outer peripheral surface of the plunger 85 is provided with a first annular oil groove 86, and 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 inverse logic proportional valve 8; the cross-sectional area of the wall of the first annular oil groove 86 adjacent the spring is greater than the cross-sectional area of the other side, thereby forming a difference in area; a second annular oil groove 87 is also provided in the plunger 85, which is located away from the spring, of the first annular oil groove 86, the second annular oil groove 87 is capable of communicating with the port a 82 in the open state of the inverse logic proportional valve 8, the plunger 85 is also provided with a radial hole 88 communicating with the second annular oil groove 87, and an axial hole 89 connecting the radial hole 88 with the port T84 is also provided in the middle of the plunger 85.
Example 2
As shown in fig. 1 to 4, a vane pump variable control system comprises a vane pump 1, an oil outlet 2, a main oil gallery 3, an oil pan 7 and a mechanical valve 9, wherein the vane pump 1 comprises a pump body, a feedback pressure oil cavity 11, a rotor and a variable slider; the control system further comprises a reverse logic proportional valve 8, the reverse logic proportional valve 8 comprises a valve body 81, a plunger 85 and a spring, a valve hole for accommodating the plunger 85 and the spring is formed in the valve body 81, and the valve body 85 is provided with an A port 82, a P port 83 and a T port 84 which are communicated with the valve hole; the outer peripheral surface of the plunger 85 is provided with a first annular oil groove 86, and 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 inverse logic proportional valve 8; the cross-sectional area of the wall of the first annular oil groove 86 adjacent the spring is greater than the cross-sectional area of the other side, thereby forming a difference in area; a second annular oil groove 87 is also arranged on the plunger 85, which is far away from the spring, of the first annular oil groove 86, the second annular oil groove 87 can be communicated with the port A82 under the action of the electromagnetic force and the oil pressure of the inverse logic proportional valve 8, and the electromagnetic force of the inverse logic proportional valve 8 is controlled by the ECU; the plunger 85 is also provided with a radial hole 88 communicated with the second annular oil groove 87, and the middle of the plunger 85 is also provided with an axial hole 89 for connecting the radial hole 88 with the T port 84; the P port 83 is connected to the main gallery 3, and the a port 82 is connected to the mechanical valve 9.
Specifically, the mechanical valve 9 comprises a valve sleeve 91, a valve core 95 and a spring, wherein the valve core 95 comprises a middle shaft and discs respectively arranged at two ends of the middle shaft, and a valve cavity of the mechanical valve 9 is divided into a control cavity 92, an oil passing cavity 93 and a spring cavity 94 by the discs at two ends of the middle shaft; the control chamber 92 is always connected to the main oil gallery 3, the spring chamber 94 is always connected to the port a 82 of the inverse logic proportional valve 8, and the valve housing 91 is provided with a first oil gallery 91a for connecting the oil pan 7 and a second oil gallery 91b for connecting the feedback pressure oil chamber 11.
Specifically, as shown in fig. 3, the control system is in the state that the port a 82 of the inverse logic proportional valve 8 is communicated with the port P83, and the port a 82 is not communicated with the port T84; the pressure oil flows into the P port 83 of the inverse logic proportional valve 8 and the control chamber 92 of the mechanical valve 9 through the main oil gallery 3 via the oil outlet 2 of the vane pump 1, and at the moment, the P port 83 and the a port 82 of the inverse logic proportional valve 8 and the control chamber 92 of the mechanical valve 9 are all filled with the pressure oil.
Before the oil pressure of the main oil gallery 3 does not reach the lowest opening pressure point, the pressure oil flows to the spring cavity 94 of the mechanical valve 9 through the port P83 and the port a 82, the valve element 95 of the mechanical valve 9 does not move, and the pressure oil in the feedback pressure oil cavity 11 flows into the oil pan 7 through the second oil gallery 91b and the first oil gallery 91a of the mechanical valve 9 in sequence.
As shown in fig. 4, when the oil pressure in the main oil gallery 3 reaches the lowest opening pressure point, the reverse logic proportional valve 8 adjusts the magnitude of the electromagnetic force under the control of the ECU, the plunger 85 of the reverse logic proportional valve 8 compresses the spring under the action of the electromagnetic force and the oil pressure, the port a 82 and the port P83 of the reverse logic proportional valve 8 are not communicated, and the port a 82 and the port T84 are communicated; the passages of the main oil gallery 2 and the port P83 are closed, the pressure oil in the spring cavity 94 of the mechanical valve 9 is discharged into the oil pan 7 through the port a 82 and the port T84 of the inverse logic proportional valve 8, the oil pressure generated by the pressure oil in the control cavity 92 of the mechanical valve 9 pushes the valve core 95 of the mechanical valve 9 to move towards the spring cavity 94, and part of the pressure oil in the control cavity 92 flows into the feedback pressure oil cavity 11 from the second oil gallery 91b to directly act on the variable slider, so that the eccentricity between the variable slider and the rotor is reduced, and the output displacement is reduced.
Specifically, as shown in fig. 3, before the oil pressure in the main oil gallery 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 spool 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 gallery 91b and the first oil gallery 91a of the mechanical valve 9 in this order.
As shown in fig. 4, when the oil pressure of the main oil gallery 3 reaches the maximum pressure opening point, the ECU controls the inverse logic proportional valve 8 to adjust the electromagnetic force of the inverse logic proportional valve 8 to 0, the inverse logic proportional valve 8 pushes the plunger 85 to compress the spring under the action of the oil pressure of the main oil gallery 3, so that the port a 82 is communicated with the port T84, the passage of the main oil gallery 3 and the port P83 is closed, the pressure oil in the spring chamber 94 is discharged into the oil pan 7 through the port a 82 and the port T84 of the inverse logic proportional valve 8, the pressure oil in the control chamber 92 of the mechanical valve 9 generates the oil pressure to push the valve element 95 of the mechanical valve 9 to move towards the spring chamber 94, and part of the pressure oil in the control chamber 92 flows into the feedback pressure oil chamber 11 from the second oil gallery 91b to directly act on the variable slider, so that the eccentricity between the variable slider and.
Specifically, assuming that the opening pressure of the inverse logic proportional valve 8 is P, the area difference between the groove walls on the two 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, the acting force of the electromagnetic force on the inverse logic proportional valve is F2, i.e., 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, i.e., 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.
The hole precision of the valve body of the inverse logic proportional valve is easy to guarantee, and the electromagnetic force of the inverse logic proportional valve can be adjusted through the ECU; the vane pump variable control system is simple in structure installation, and the mechanical valve control structure is regular, so that the stability of the output pressure of the vane pump is facilitated; the vane pump does not play a decisive role in the lowest opening pressure point, is easy to design and can be designed universally.
The above embodiments are preferred implementations of the present invention, and the present invention can be implemented in other ways without departing from the spirit of the present invention.
Some of the drawings and descriptions of the present invention have been simplified to facilitate the understanding of the improvements over the prior art by those skilled in the art, and some other elements have been omitted from this document for the sake of clarity, and it should be appreciated by those skilled in the art that such omitted elements may also constitute the subject matter of the present invention.
Claims (3)
1. An inverse logic proportional valve, characterized by: the inverse logic proportional valve (8) comprises a valve body (81), a plunger (85) and a spring, a valve hole for accommodating the plunger (85) and the spring is formed in the valve body (81), and the valve body (85) is provided with an A port (82), a P port (83) and a T port (84) which are communicated with the valve hole; the outer peripheral surface of the plunger (85) is provided with a first annular oil groove (86), and the first annular oil groove (86) enables the port A (82) and the port P (83) to be communicated with each other in the initial state of the inverse logic proportional valve (8); the sectional area of the wall of the first annular oil groove (86) close to the spring is larger than that of the other side, so that an area difference is formed; the first annular oil groove (86) is further provided with a second annular oil groove (87) on a plunger (85) far away from the spring, the second annular oil groove (87) can be communicated with the port A (82) in an opening state of the inverse logic proportional valve (8), the plunger (85) is further provided with a radial hole (88) communicated with the second annular oil groove (87), and the middle of the plunger (85) is further provided with an axial hole (89) for connecting the radial hole (88) with the port T (84).
2. A vane pump variable control system comprising: the oil-return pump comprises a vane pump (1), an oil outlet (2), a main oil duct (3), an oil pan (7) and a mechanical valve (9), wherein the vane pump (1) comprises a pump body, a feedback pressure oil cavity (11), a rotor and a variable slider; the method is characterized in that: the control system further comprises a reverse logic proportional valve (8), the reverse logic proportional valve (8) comprises a valve body (81), a plunger (85) and a spring, a valve hole for accommodating the plunger (85) and the spring is formed in the valve body (81), and the valve body (85) is provided with an A port (82), a P port (83) and a T port (84) communicated with the valve hole; the outer peripheral surface of the plunger (85) is provided with a first annular oil groove (86), and the first annular oil groove (86) enables the port A (82) and the port P (83) to be communicated with each other in the initial state of the inverse logic proportional valve (8); the sectional area of the wall of the first annular oil groove (86) close to the spring is larger than that of the other side, so that an area difference is formed; a plunger (85) of the first annular oil groove (86) far away from the spring is also provided with a second annular oil groove (87), the second annular oil groove (87) can be communicated with the port A (82) under the action of the electromagnetic force and the oil pressure of the inverse logic proportional valve (8), and the electromagnetic force of the inverse logic proportional valve (8) is controlled by an ECU; the plunger (85) is also provided with a radial hole (88) communicated with the second annular oil groove (87), and the middle of the plunger (85) is also provided with an axial hole (89) for connecting the radial hole (88) with the T port (84); the port P (83) is connected with the main oil gallery (3), and the port A (82) is connected with the mechanical valve (9);
the mechanical valve (9) comprises a valve sleeve (91), a valve core (95) and a spring, wherein the valve core (95) comprises a middle shaft and discs arranged at two ends of the middle shaft respectively, and a valve cavity of the mechanical valve (9) is divided into a control cavity (92), an oil passing cavity (93) and a spring cavity (94) by the discs at two ends of the middle shaft; the control cavity (92) is always connected with the main oil gallery (3), the spring cavity (94) is always connected with the port A (82) of the inverse logic proportional valve (8), and the valve sleeve (91) is provided with a first oil gallery (91 a) used for being connected with the oil pan (7) and a second oil gallery (91b) used for being connected with the feedback pressure oil cavity (11).
3. The vane pump variable control system according to claim 2, characterized in that: the port A (82) of the inverse logic proportional valve (8) is communicated with the port P (83), and the port A (82) is not communicated with the port T (84); pressure oil flows into a P port (83) of the inverse logic proportional valve (8) and a control cavity (92) of the mechanical valve (9) through a main oil duct (3) through an oil outlet (2) of the vane pump (1), and the P port (83) and an A port (82) of the inverse logic proportional valve (8) and the control cavity (92) of the mechanical valve (9) are filled with the pressure oil;
before the oil pressure of the main oil gallery (3) does not reach the lowest opening pressure point, pressure oil flows to a spring cavity (94) of a mechanical valve (9) through a port P (83) and a port A (82), a valve core (95) of the mechanical valve (9) does not move, and the pressure oil of the feedback pressure oil cavity (11) sequentially flows into an oil pan (7) through a second oil gallery (91b) and a first oil gallery (91 a) of the mechanical valve (9);
when the oil pressure of the main oil gallery (3) reaches a lowest opening pressure point, the reverse logic proportional valve (8) is controlled by an ECU to regulate the magnitude of electromagnetic force, a plunger (85) of the reverse logic proportional valve (8) compresses a spring under the action of the electromagnetic force and the oil pressure, at the moment, an A port (82) and a P port (83) of the reverse logic proportional valve (8) are not communicated, and the A port (82) is communicated with a T port (84); the main oil channel (2) and the P port (83) are closed, pressure oil in a spring cavity (94) of the mechanical valve (9) is discharged into an oil sump (7) through an A port (82) and a T port (84) of the inverse logic proportional valve (8), oil pressure generated by the pressure oil in a control cavity (92) of the mechanical valve (9) pushes a valve core (95) of the mechanical valve (9) to move towards the spring cavity (94), and partial pressure oil in the control cavity (92) flows into a feedback pressure oil cavity (11) from a second oil channel (91b) to directly act on the variable slider, so that the eccentric quantity of the variable slider and a rotor is reduced, and the output displacement is reduced;
before the oil pressure of the main oil gallery (3) does not reach a maximum opening pressure point, pressure oil flows to a spring cavity (94) of a mechanical valve (9) through a port P (83) and a port A (82), a valve core (95) of the mechanical valve (9) does not move, and the pressure oil of the feedback pressure oil cavity (11) sequentially flows into an oil pan (7) through a second oil gallery (91b) and a first oil gallery (91 a) of the mechanical valve (9);
when the oil pressure of the main oil gallery (3) reaches a maximum pressure opening point, the ECU controls the inverse logic proportional valve (8) to adjust the electromagnetic force of the inverse logic proportional valve to 0, the inverse logic proportional valve (8) pushes a plunger (85) to compress a spring under the action of the oil pressure of the main oil gallery (3), so that an A port (82) is communicated with a T port (84), a passage of the main oil gallery (3) and the P port (83) is closed, pressure oil of a spring cavity (94) is discharged into an oil pan (7) through the A port (82) and the T port (84) of the inverse logic proportional valve (8), pressure oil in a control cavity (92) of the mechanical valve (9) generates the oil pressure to push a valve core (95) of the mechanical valve (9) to move towards the spring cavity (94), and partial pressure oil of the control cavity (92) flows into a feedback pressure oil cavity (11) from a second oil gallery (91b) to directly act on a variable block, the eccentricity between the variable slide block and the rotor is reduced, and the output displacement is reduced.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011179105.XA CN112303283A (en) | 2020-10-29 | 2020-10-29 | Variable control system for inverse logic proportional valve and vane pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011179105.XA CN112303283A (en) | 2020-10-29 | 2020-10-29 | Variable control system for inverse logic proportional valve and vane pump |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN112303283A true CN112303283A (en) | 2021-02-02 |
Family
ID=74330672
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202011179105.XA Pending CN112303283A (en) | 2020-10-29 | 2020-10-29 | Variable control system for inverse logic proportional valve and vane pump |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN112303283A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113738633A (en) * | 2020-05-27 | 2021-12-03 | 东风富奥泵业有限公司 | Pressure limiting valve device structure, pressure regulating plunger and hydraulic pump |
-
2020
- 2020-10-29 CN CN202011179105.XA patent/CN112303283A/en active Pending
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113738633A (en) * | 2020-05-27 | 2021-12-03 | 东风富奥泵业有限公司 | Pressure limiting valve device structure, pressure regulating plunger and hydraulic pump |
| CN113738633B (en) * | 2020-05-27 | 2023-10-10 | 富奥泵业(湖北)有限公司 | Pressure limiting valve device structure, pressure regulating plunger and hydraulic pump |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN104912619B (en) | System for controlling oil drainage type single-cavity two-stage variable displacement blade pump | |
| JP4776203B2 (en) | Variable displacement vane pump with variable target adjuster | |
| EP1790855A2 (en) | Hydraulic pump system with variable flow and pressure | |
| CN110206610B (en) | Pressure control system based on fixed displacement engine oil pump with simplified structure | |
| CN101892981A (en) | Variable capacity lubricant vane pump | |
| CN108894847B (en) | Control system of direct-push type single-cavity supercharging variable-discharge oil pump | |
| US10480349B2 (en) | System and method for distributing and controlling oil flow | |
| CA2408982C (en) | Regulated pump | |
| US10267310B2 (en) | Variable pressure pump with hydraulic passage | |
| CN112303283A (en) | Variable control system for inverse logic proportional valve and vane pump | |
| CN213598622U (en) | Variable control system for inverse logic proportional valve and vane pump | |
| CN106051441B (en) | A kind of output displacement can be changed duplex impeller pump and its control system | |
| CN108412831A (en) | Shunt variable voltage control commutation pile-up valve | |
| CN108643986A (en) | Valve of the fuel automobile engine lubricating system containing temperature control and decompression function | |
| CN112576487A (en) | In-line piston pump | |
| CN208203689U (en) | Shunt variable voltage control commutation pile-up valve | |
| CN203797312U (en) | Vane-type displacement-variable oil pump | |
| JP4061142B2 (en) | Variable displacement vane pump with variable target adjuster | |
| CN104100825B (en) | Displacement-variable oil pump | |
| CN210178435U (en) | Device of two-stage variable engine oil pump controlled by combination valve | |
| CN210179289U (en) | Two-stage variable oil pump with double regulating cavities and controlled by regulating valve | |
| CN213478418U (en) | Oil pump of vehicle and engine | |
| CN109139176B (en) | Pressure control system based on fixed displacement engine oil pump | |
| CN110017190B (en) | Method and device for controlling two-stage variable oil pump by combined valve | |
| CN103742775A (en) | Vane variable displacement oil pump |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination |