Dual chamber two stage step full variable mechanical vane pump

Abstract

The utility model discloses a two cavity two -step full variable mechanical type vane pump, including control valve and pump body, be provided with rotor chamber in the casing of pump body, be installed with rotor, vane and variable slide in rotor chamber, be provided with first spring between the right side of variable slide and rotor chamber inner wall, and the left side of variable slide and rotor chamber left side wall leave the interval, form A cavity, be provided with first pressure oil port on the casing, recessed groove is seted up in the left side of rotor chamber, and the left side of variable slide is protruding and is provided with the plug, forms B cavity, and be provided with second pressure oil port on the casing, control valve includes valve sleeve, valve element and second spring, is provided with first interface and second interface on the valve sleeve, the top of valve element is provided with the oil channel vertically, and the bottom end communication of oil channel is horizontally set up and is provided with control hole, and the tail end of control hole is correspondingly seted up with first interface, is still provided with the oil outlet on the valve sleeve, and the recessed ring groove of valve element middle part, can realize the output pressure of step control vane pump under not adding the solenoid valve control.

Description

Technical Field

[0001] This utility model relates to the field of vane pump technology, specifically to a dual-chamber, two-stage, fully variable mechanical vane pump. Background Technology

[0002] As engine speed gradually increases, the oil pump's pumping volume and pressure increase accordingly. Once the pumping volume and pressure meet lubrication needs, further increases would consume more engine power. Therefore, a variable displacement oil pump is necessary. Using a variable displacement oil pump can generally reduce fuel consumption in passenger car engines by 1% to 2%.

[0003] A two-stage variable displacement vane pump control system, disclosed in publication number CN205154617U, includes a pump body, a feedback pressure control chamber, a variable slider, a variable spring, a control valve, and a pilot valve. Displacement is changed by combining the control valve and the pilot valve to control the feedback pressure control chamber. However, this technical solution has complex control components, requiring two sets of valves (pilot valve and control valve) to achieve displacement control, which is not conducive to structural simplification and weight reduction. Furthermore, it lacks pressure step control capability and cannot meet the system's instantaneous demand for high oil pressure. Utility Model Content

[0004] This invention aims to solve the technical problems existing in the prior art, and innovatively proposes a dual-chamber two-stage step-variable mechanical vane pump, which can achieve step-controlled vane pump output pressure without the addition of solenoid valve control.

[0005] To achieve the above objectives, this utility model provides a dual-chamber two-stage step fully variable mechanical vane pump, including a control valve and a pump body. The pump body includes a housing, and a rotor chamber is provided inside the housing. A rotor, vanes, and a variable slider are installed inside the rotor chamber. The control valve includes a valve sleeve and a valve core slidably connected inside the valve sleeve. A second spring for supporting the valve core is provided at the bottom of the valve sleeve. The variable slider is slidably installed in the rotor chamber. A first spring is provided between the right side of the variable slider and the inner wall of the rotor chamber. A gap is left between the left side of the variable slider and the left side wall of the rotor chamber to form a cavity A. A first pressure oil port is provided on the housing corresponding to cavity A.

[0006] The rotor cavity has a recessed groove on the left side, and the variable slider has a protruding plug on the left side that is plugged in the groove, so that cavity B is formed between the plug and the bottom of the groove, and a second pressure oil port is provided on the housing corresponding to cavity B.

[0007] The valve sleeve is provided with a first interface and a second interface that are respectively connected to the first pressure oil port and the second pressure oil port; the top of the valve core is provided with an oil passage vertically, and the bottom end of the oil passage is connected to a horizontally provided control hole. The initial position of the control hole is located between the first interface and the second interface, and during the downward movement of the valve core, the end of the control hole can dock with the first interface for intermittent connection to the first interface.

[0008] The valve sleeve is also provided with an oil discharge port. The outer wall of the middle part of the valve core is recessed with an annular groove located above the control hole. The vertical extension length of the annular groove is greater than the distance between the first interface and the oil discharge port, so that the first interface and the oil discharge port are connected through the annular groove, allowing the pressurized oil to flow out from the A cavity.

[0009] In the above scheme, the cross-sectional area of ​​cavity B is smaller than that of cavity A, so that the variable slider moves at different moving speeds and reaction speeds in different states, thereby realizing two different displacement adjustment speeds.

[0010] In the above scheme: the oil unloading port is located below the second interface, that is, the oil unloading port and the second interface are staggered to prevent the oil unloading port from being directly connected to the second interface as much as possible.

[0011] In the above scheme: the vertical extension length of the annular groove is also greater than the distance between the second interface and the oil discharge port, so that the second interface and the oil discharge port can be connected through the annular groove, so that the pressure oil flows out from the B cavity and realizes the oil discharge of the B cavity.

[0012] In the above scheme: the left end of the plug is provided with a stop block for abutting against the left side wall of cavity B, to prevent the end of the plug from abutting against the left side wall of cavity B.

[0013] In summary, the beneficial effects of this utility model are as follows: the oil passage on the valve core not only meets the needs of valve core movement but also connects to chamber A through a control hole, thereby enabling step control of the vane pump's output pressure without the addition of a solenoid valve, saving space and equipment costs, while reducing the vane pump's overflow loss, improving its efficiency, and lowering costs. The variable slider forms two independent chambers with the housing, thus meeting the engine's displacement requirements under different operating conditions. Furthermore, during use, the pressurized oil in chamber A is discharged through the annular groove and the drain port, instantly restoring the vane pump's eccentricity to its initial set value, thus restoring the vane pump's displacement to its initial set, and causing a step increase in the main oil passage oil pressure, meeting the engine's high oil pressure requirements under high-speed, durable operating conditions. By forming multiple working states during valve core movement, full-range variable displacement can be achieved. Attached Figure Description

[0014] Figure 1 This is a schematic diagram of the present invention.

[0015] Figure 2 This is a schematic diagram of the second state of this utility model.

[0016] Figure 3 This is a schematic diagram of the third state of this utility model.

[0017] Figure 4 This is a schematic diagram of the fourth state of this utility model.

[0018] Figure 5 This is a schematic diagram illustrating the relationship between rotational speed and power in this utility model. Detailed Implementation

[0019] The present invention will be further described below with reference to embodiments and accompanying drawings:

[0020] like Figures 1-4 The illustrated dual-chamber, two-stage step-variable mechanical vane pump includes a control valve and a pump body. The pump body includes a housing 1, within which a rotor chamber is provided. A rotor 3, vanes 4, and a variable slider 2 are installed within the rotor chamber. The lateral extension length within the rotor chamber is greater than the lateral extension length of the variable slider 2, which is slidably mounted within the rotor chamber. A first spring 5 is installed between the right side of the variable slider 2 and the inner wall of the rotor chamber. A gap is left between the left side of the variable slider 2 and the left side wall of the rotor chamber, forming chamber A 6. A first pressure port 18 is provided on the housing 1 corresponding to chamber A 6.

[0021] A groove is recessed on the left side of the rotor cavity, and a plug protrudes from the left side of the variable slider 2, forming cavity B. The plug allows cavity A 6 and cavity B 7 to be two independent chambers, and a second pressure oil port 17 is provided on the housing 1 corresponding to cavity B 7. A stop block is provided at the left end of the plug to prevent the end of the plug from abutting against the left wall of cavity B 7.

[0022] The control valve includes a valve sleeve 8 and a valve core 9 slidably connected within the valve sleeve. A second spring 14 is provided at the bottom of the valve sleeve 8 to support the valve core 9. The valve sleeve 8 is provided with a first interface 15 and a second interface 16 respectively communicating with a first pressure oil port 18 and a second pressure oil port 17. The valve sleeve 8 is also provided with an oil discharge port 12 located below the second interface 16.

[0023] A vertically oriented oil passage 10 is provided at the top of the valve core 9, and a horizontally oriented control hole 13 is connected to the bottom end of the oil passage 10. The initial position of the control hole 13 is located between the first interface 15 and the second interface 16, and the end of the control hole 13 is directly above the first interface 15. During the downward movement of the valve core 9, the end of the control hole 13 can engage with the first interface 15 to intermittently connect to the first interface 15, so as to input pressurized oil into chamber A 6.

[0024] An annular groove 11 is recessed on the outer wall of the middle part of the valve core 9, located above the control hole 13. The vertical extension length of the annular groove 11 is greater than the distance between the first interface 15 and the oil discharge port 12, thereby connecting the first interface 15 and the oil discharge port 12 through the annular groove 11, allowing pressurized oil to flow out from the A chamber 6. Furthermore, the vertical extension length of the annular groove 11 is also greater than the distance between the second interface 16 and the oil discharge port 12, enabling the second interface 16 and the oil discharge port 12 to be connected through the annular groove 11, allowing pressurized oil to flow out from the B chamber 7.

[0025] When in use, it has the following working states:

[0026] State 1: As the engine speed Ne increases, typically around 1500 rpm at idle, the main oil circuit pressure rises rapidly to meet the oil pressure requirements of the engine's oil-using components. See appendix for details. Figure 1 illustrate.

[0027] State 2: As the engine speed Ne increases, typically to around 2500 rpm, the valve core 9 moves downwards, the control hole 13 connects with the first interface 15, and begins to connect to chamber A 6, as shown below. Figure 2 As shown, pressurized oil enters chamber A6, which in turn pushes the variable slider 2 to the right, gradually reducing the eccentricity of the vane pump, thereby reducing the displacement of the vane pump and the pump's output flow rate. During this stage, the pressure in the main oil passage rises slowly, meeting the lubrication and cooling needs of various oil-using components under operating conditions.

[0028] State 3: As the engine speed Ne reaches a medium-high speed, typically around 3500 rpm, the valve core 9 continues to move downwards. The control hole 13 of the valve core 9 is misaligned with the first interface 15, beginning to close the connection with chamber A 6. The oil discharge port 12 is then connected to the first interface 15 via the annular groove 11. Under the elastic force of the first spring 5, the pressurized oil in chamber A 6 flows out from the oil discharge port 12, and the variable slider 2 moves to the left. The eccentricity of the vane pump instantly returns to its initial setting value. The vane pump displacement also returns to its initial setting value, and the main oil passage oil pressure increases dramatically, meeting the engine's high oil pressure requirements under high-speed, durable operating conditions.

[0029] State 4: As the engine speed Ne continues to rise, the valve core 9 continues to move downwards until the second port 16 is exposed. The pressurized oil at the top of the valve core 9 can then directly enter chamber B 7 from the second port 16, thereby pushing the variable slider 2 to the right, slowly reducing the eccentricity of the vane pump, thus reducing the vane pump's displacement and output flow, preventing excessive oil pressure in the main oil circuit and damage to the oil-using components. The relationship between speed and power in each operating state is as follows: Figure 5 As shown.

Claims

1. A double-cavity two-stage step full variable mechanical vane pump, comprising a control valve and a pump body, the pump body comprising a casing (1) in which a rotor cavity is provided, a rotor (3), a vane (4) and a variable slider (2) being installed in the rotor cavity, the control valve comprising a valve sleeve (8) and a valve core (9) slidingly connected in the valve sleeve, a second spring (14) for supporting the valve core (9) being provided at the bottom of the valve sleeve (8), characterized in that: The variable slider (2) is slidably installed in the rotor cavity, a first spring (5) is arranged between the right side of the variable slider (2) and the inner wall of the rotor cavity, and a left side of the variable slider (2) is spaced from the left side wall of the rotor cavity to form an A cavity (6), and a first pressure oil port (18) is arranged on the shell (1) corresponding to the A cavity (6); A groove is concavely arranged on the left side of the rotor cavity, and a plug is convexly arranged on the left side of the variable slider (2) and plugs into the groove, so that the B cavity is formed between the plug and the groove bottom, and a second pressure oil port (17) is arranged on the shell (1) corresponding to the B cavity (7); The valve sleeve (8) is provided with a first interface (15) and a second interface (16) which are in communication with the first pressure oil port (18) and the second pressure oil port (17), respectively; an oil channel (10) is vertically arranged on the top of the valve core (9), the bottom end of the oil channel (10) is communicated with a horizontally arranged control hole (13), the initial position of the control hole (13) is located between the first interface (15) and the second interface (16), and in the downward process of the valve core (9), the end of the control hole (13) can be connected with the first interface (15) for intermittent communication with the first interface (15); The valve sleeve (8) is further provided with a oil discharge port (12), and an annular groove (11) is concavely arranged on the outer side wall of the middle part of the valve core (9) and located above the control hole (13), the vertical extension length of the annular groove (11) is greater than the distance between the first interface (15) and the oil discharge port (12), so that the first interface (15) and the oil discharge port (12) are communicated through the annular groove (11), and the pressure oil flows out from the A cavity (6).

2. The two-cavity two-stage step full variable mechanical vane pump according to claim 1, characterized in that: The cross-sectional area of the B cavity (7) is smaller than that of the A cavity (6).

3. The dual cavity two stage step full variable mechanical vane pump according to claim 1, characterized in that: The oil discharge port (12) is located below the second interface (16).

4. The dual cavity two-stage step PVMP according to claim 3, characterized in that: The vertical extension length of the annular groove (11) is also greater than the distance between the second interface (16) and the oil discharge port (12), so as to communicate the second interface (16) and the oil discharge port (12) through the annular groove (11).

5. The dual cavity two-stage step PVMP according to claim 1, characterized in that: A stop block is arranged at the left end of the plug for abutting against the left side wall of the B cavity (7), so as to prevent the end of the plug from abutting against the left side wall of the B cavity (7). A stop block is arranged at the left end of the plug for abutting against the left side wall of the B cavity (7), so as to prevent the end of the plug from abutting against the left side wall of the B cavity (7).

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