Variable displacement oil pump

Abstract

The utility model discloses a variable displacement oil pump, which comprises a pump body, an oil pump, a first oil pump, a second oil pump and a second oil pump, wherein an accommodating space and a feedback oil duct are arranged in the pump body; the aligning ring is arranged in the accommodating space, a control oil cavity is formed between the outer wall surface of the aligning ring and the inner wall surface of the accommodating space, the control oil cavity is communicated with the feedback oil duct, and the aligning ring can move along a preset path; the rotor is located in the aligning ring, the rotor and the aligning ring are eccentrically arranged, and the rotor can rotate with the preset axis as the center; the partition pieces are arranged in the aligning ring and used for dividing the space between the outer wall face of the rotor and the inner wall face of the aligning ring into a plurality of closed areas, and the areas of the different closed areas are different; and at least part of the pressure regulating valve is located in the feedback oil duct. Compared with the prior art, through the arrangement of the aligning ring and the pressure regulating valve, the requirement of the engine on the engine oil pressure under different working conditions can be automatically regulated, the engine oil pressure is always in a relatively ideal area, the power loss of the engine is reduced, and the fuel economy of the engine is improved.

Description

Technical Field

[0001] The utility model relates to the technical field of oil pumps, in particular to a variable displacement oil pump. Background Art

[0002] In the existing technology, the current variable displacement oil pump uses an electromagnetic control valve to regulate the pressure, which makes the variable displacement oil pump cost too high. Many companies tend to use fixed displacement oil pumps for cost considerations, resulting in high engine fuel consumption. The electromagnetic control valve pressure regulation has the following defects / problems:

[0003] 1. The variable displacement oil pump with solenoid control valve has a high unit cost, resulting in a limited range of use. It is usually only used in high-end engine models.

[0004] 2. The space required for layout is large and has many requirements, which is not conducive to layout;

[0005] 3. There are higher logic control requirements, which require special calibration, increasing the test cost;

[0006] Causes:

[0007] 1. The solenoid valve has very high requirements for precision, and high investment is required in materials, technology, manufacturing, quality control, etc., so the unit price is naturally not cheap;

[0008] 2. The solenoid valve itself has a certain volume, and coupled with the wiring harness and plug, there are many aspects to consider when arranging it, and the layout space and requirements are relatively high;

[0009] 3. The solenoid valve is controlled by the control unit ECU, so it needs to be calibrated, resulting in additional testing costs. Utility Model Content

[0010] The purpose of the utility model is to provide a variable displacement oil pump to solve the technical problems in the prior art. The utility model can automatically adjust the demand of the engine for oil pressure under different working conditions by mechanical means.

[0011] The utility model provides a variable displacement oil pump, comprising:

[0012] A pump body, wherein the pump body has a receiving space and a feedback oil channel;

[0013] A centering ring is disposed in the accommodating space, wherein a control oil chamber is formed between an outer wall surface of the centering ring and an inner wall surface of the accommodating space, the control oil chamber is connected to the feedback oil passage, and the centering ring can move along a preset path;

[0014] A rotor is located in the centering ring and is eccentrically arranged with respect to the centering ring, and the rotor can rotate around a preset axis;

[0015] a separator disposed in the centering ring, the separator being used to separate the space between the outer wall surface of the rotor and the inner wall surface of the centering ring into a plurality of sealed areas, wherein the areas of different sealed areas are different;

[0016] A pressure regulating valve is at least partially located in the feedback oil channel, and the pressure regulating valve is used to control the on-off and flow rate of the feedback oil channel.

[0017] The variable displacement oil pump as described above, wherein preferably, the feedback oil passage includes a first oil passage and a second oil passage that are connected to each other, the first oil passage is connected to the main oil passage of the engine, and the second oil passage has a connecting hole, the connecting hole being connected to the second oil passage and the control oil chamber respectively;

[0018] The pressure regulating valve includes a valve core, which is movably arranged in the second oil channel. The outer surface of the valve core is tightly fitted with the inner surface of the second oil channel, and the communicating hole is located on the moving path of the valve core.

[0019] In the variable displacement oil pump as described above, preferably, a first elastic member is further provided in the second oil passage, and the first elastic member is connected to the valve core so that the valve core can elastically move back and forth in the second oil passage.

[0020] In the variable displacement oil pump as described above, preferably, one end of the second oil passage away from the first oil passage is threadedly connected to a screw plug, and the screw plug is connected to the first elastic member.

[0021] In the variable displacement oil pump as described above, preferably, the first elastic member is a spring, and opposite ends of the spring are in contact with the valve core and the screw plug respectively.

[0022] In the variable displacement oil pump as described above, preferably, an oil unloading hole is further provided in the second oil passage, the oil unloading hole is located on the moving path of the valve core, and the connecting hole is closer to the first oil passage than the oil unloading hole.

[0023] In the variable displacement oil pump as described above, preferably, one end of the oil unloading hole away from the second oil passage is connected to the oil pump chain.

[0024] A variable displacement oil pump as described above, wherein preferably, a rotating pin is provided in the accommodating space, the aligning ring is movably connected to the rotating pin, and the preset path is a rotational movement path of the aligning ring with the rotating pin as the center.

[0025] In the variable displacement oil pump as described above, preferably, a second elastic member is provided in the accommodating space, and the second elastic member is connected to the aligning ring so that the aligning ring can elastically move back and forth on the preset path.

[0026] A variable displacement oil pump as described above, wherein preferably, a plurality of guide grooves are provided on the outer circumferential surface of the rotor, and the plurality of guide grooves are arranged in a ring-shaped manner with the preset axis as the center line, and the preset axis is located on the extension line of the guide groove, and the separator includes a plurality of separator blocks, and the plurality of separator blocks correspond one-to-one to the plurality of guide grooves, and each of the separator blocks is guided and fitted in the corresponding guide groove.

[0027] Compared with the existing technology, the utility model can automatically adjust the engine's demand for oil pressure under different working conditions by providing a self-aligning ring and a pressure regulating valve, so that the oil pressure is always in a relatively ideal area, reducing the engine's power loss and improving the engine's fuel economy. BRIEF DESCRIPTION OF THE DRAWINGS

[0028] Figure 1 This is a schematic structural diagram of a variable displacement oil pump provided by an embodiment of the present utility model;

[0029] Figure 2 It is a cross-sectional view of a variable displacement oil pump provided by an embodiment of the present utility model.

[0030] Description of reference numerals:

[0031] 10- pump body, 11- accommodation space, 12- feedback oil channel, 121- first oil channel, 122- second oil channel, 13- control oil chamber, 14- rotating pin, 15- communicating hole, 16- oil unloading hole;

[0032] 20-aligning ring, 21-second elastic member;

[0033] 30-rotor, 31-guide groove;

[0034] 40-separator, 41-separator block;

[0035] 50-pressure regulating valve, 51-valve core, 52-first elastic member, 53-screw plug. DETAILED DESCRIPTION

[0036] The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the present invention, and should not be construed as limiting the present invention.

[0037] like Figure 1 as well as Figure 2As shown, an embodiment of the present invention provides a variable displacement oil pump, comprising a pump body 10, a centering ring 20, a rotor 30, a separator 40 and a pressure regulating valve 50, wherein:

[0038] The pump body 10 has an accommodating space 11 and a feedback oil passage 12 therein. The accommodating space 11 has an oil inlet (not shown) and an oil outlet (not shown). The feedback oil passage 12 is connected to the main oil passage of the engine (not shown).

[0039] The aligning ring 20 is arranged in the accommodating space 11. A control oil chamber 13 is formed between the outer wall surface of the aligning ring 20 and the inner wall surface of the accommodating space 11. The control oil chamber 13 is connected to the feedback oil channel 12. The aligning ring 20 can move along a preset path. The aligning ring 20 is arranged in a movable state in the accommodating space 11. In a feasible implementation method, the preset path is pre-set, and the oil pressure in the feedback oil channel 12 will drive the aligning ring 20 to move and keep the aligning ring 20 in a certain posture in the preset path.

[0040] The rotor 30 is located in the centering ring 20 and is eccentrically arranged with respect to the centering ring 20. The rotor 30 can rotate around a preset axis. The rotor 30 is usually driven by the crankshaft of the engine through gears or chains. When the engine is running, the rotation of the crankshaft drives the rotor 30 to rotate.

[0041] The separator 40 is arranged in the centering ring 20. The separator 40 is used to divide the space between the outer wall surface of the rotor 30 and the inner wall surface of the centering ring 20 into several closed areas. Since the rotor 30 and the centering ring 20 are eccentrically arranged, the areas of different closed areas are different. As the rotor 30 rotates, the space of several closed areas near the oil inlet side gradually increases, forming vacuum oil suction, and the space of several closed areas near the oil outlet side gradually decreases, forming pressure oil discharge. The adjustment of the displacement depends on the eccentricity of the centering ring 20 and the rotor 30. By adjusting the eccentricity, the spatial change amplitude of the closed area can be changed, thereby changing the amount of oil pumped by the rotor 30 per rotation.

[0042] The pressure regulating valve 50 is at least partially located in the feedback oil channel 12. The pressure regulating valve 50 is used to control the on-off and flow rate of the feedback oil channel 12. In the embodiment provided in the present application, the pressure regulating valve 50 is a mechanical pressure regulating valve 50. The mechanical valve replaces the solenoid valve in the prior art to automatically adjust the engine's demand for oil pressure under different working conditions, so that the oil pressure is always in a relatively ideal area, which can reduce the power loss of the engine and improve the engine fuel economy. At the same time, the cost of the oil pump in manufacturing, procurement and quality control is greatly reduced, achieving the effect of reducing costs and increasing efficiency.

[0043] When the engine is idling or at a relatively low speed, the oil pressure in the engine main oil gallery is low, the pressure regulating valve 50 in the feedback oil gallery 12 is closed, the control oil chamber 13 is pressureless or has low pressure, and the aligning ring 20 is stationary. At this time, the eccentricity between the aligning ring 20 and the rotor 30 is at its initial maximum position, the displacement is also maximum, and the pressure provided to the lubrication system just meets the engine's demand. When the engine speed increases, the oil pump speed also increases, increasing the oil supply to the lubrication system and increasing the oil pressure in the engine main oil gallery, exceeding the engine's oil pressure requirement. At this time, the excess oil pressure in the engine main oil gallery enters the feedback oil gallery 12 of the oil pump, opening the pressure regulating valve 50 and allowing the oil pressure to enter the control oil chamber 13. This pressure then pushes the aligning ring 20, causing it to move along the preset path. The eccentricity between the aligning ring 20 and the rotor 30 begins to gradually decrease, and the oil pump flow rate also decreases accordingly. After the aligning ring 20 moves to the optimal position along the preset path, the pressure supplied by the oil pump to the entire engine lubrication system is also optimal.

[0044] Reference Figure 2 As shown, the feedback oil passage 12 includes a first oil passage 121 and a second oil passage 122 that are connected to each other. The first oil passage 121 is connected to the main oil passage of the engine. The second oil passage 122 has a connecting hole 15, which is connected to the second oil passage 122 and the control oil chamber 13 respectively. The oil sent from the main oil passage of the engine passes through the first oil passage 121 and the second oil passage 122 in sequence and then enters the control oil chamber 13 through the connecting hole 15. The pressure regulating valve 50 is located in the second oil passage 122. When the engine is idling or at a low speed, the pressure regulating valve 50 is turned off. When the engine speed is low, the pressure regulating valve 50 blocks the oil in the first oil channel 121 from entering the second oil channel 122, and thus cannot enter the control oil chamber 13. When the engine is at a higher speed, the excess oil pressure in the main oil channel of the engine enters the feedback oil channel 12, and the pressure regulating valve 50 is opened. The oil in the first oil channel 121 can enter the second oil channel 122 until it enters the control oil chamber 13 from the connecting hole 15. During this process, the opening of the pressure regulating valve 50 can be controlled to adjust the oil pressure entering the control oil chamber 13.

[0045] In a feasible implementation, referring to Figure 2As shown, the pressure regulating valve 50 includes a valve core 51, which is movably arranged in the second oil channel 122. The outer surface of the valve core 51 is tightly fitted with the inner surface of the second oil channel 122, and the connecting hole 15 is located on the moving path of the valve core 51. When the engine is idling or at a low speed, the oil pressure in the feedback oil channel 12 is small and cannot push the valve core 51 to move. When the engine speed increases, the oil pump speed also increases, the oil provided to the lubrication system increases, the oil pressure in the engine main oil channel increases, and exceeds the engine's oil pressure demand. At this time, the excess oil pressure in the engine main oil channel enters the feedback oil channel 12, automatically pushing the valve core 51 to move. After the valve core 51 moves across the connecting hole 15, the oil can enter the control oil chamber 13 from the connecting hole 15. The oil pressure entering the control oil chamber 13 is controlled by adjusting the covering area of ​​the valve core 51 and the connecting hole 15.

[0046] Preferably, the valve core 51 is a standard sphere, and a clearance fit is formed between the outer surface of the valve core 51 and the inner surface of the second oil passage 122 , so that the valve core 51 can maintain good movement along the axial direction of the second oil passage 122 .

[0047] In order to make the valve core 51 able to move back and forth elastically on the moving path, refer to Figure 2 As shown, a first elastic member 52 is further provided in the second oil passage 122. The first elastic member 52 is preferably a spring. The first elastic member 52 is connected to the valve core 51 so that it can elastically reciprocate in the second oil passage 122. In a feasible embodiment, the first oil passage 121 and the second oil passage 122 intersect vertically. In the initial state, the first elastic member 52 naturally extends, and the valve core 51 is located at the intersection of the first oil passage 121 and the second oil passage 122. After the oil pressure in the first oil passage 121 rises to a sufficiently high level, the valve core 51 overcomes the initial preload force of the first elastic member 52, and the valve core 51 moves in the second oil passage 122, and the first elastic member 52 accumulates elastic restoring force. When the oil pressure is balanced with the elastic restoring force of the first elastic member 52, the valve core 51 remains in one posture. Under the action of the elastic restoring force of the first elastic member 52, the valve core 51 can change with the oil pressure in the feedback oil channel 12, and its position will also change accordingly. By replacing the model and parameters of the first elastic member 52, the initial preload force and the elastic restoring force applied by the first elastic member 52 on the valve core 51 can be adjusted to adapt to various working scenarios. After the oil pressure in the feedback oil channel 12 gradually decreases to less than the initial preload force of the first elastic member 52, the valve core 51 returns to its initial state, cutting off the connection between the first oil channel 121 and the second oil channel 122.

[0048] Further, refer to Figure 2As shown, the end of the second oil passage 122 away from the first oil passage 121 is threadedly connected with a screw plug 53. When the screw plug 53 is installed, thread sealant is applied to make it airtight. The end of the first elastic member 52 away from the valve core 51 is connected to the screw plug 53. The screw plug 53 is used to support the first elastic member 52 and can also control the initial preload force and elastic restoring force applied by the first elastic member 52 to the valve core 51. When the screw plug 53 is screwed toward the end close to the valve core 51, the initial preload force and elastic restoring force applied to the valve core 51 can be increased. When the screw plug 53 is screwed toward the end away from the valve core 51, the initial preload force and elastic restoring force applied to the valve core 51 can be reduced.

[0049] In a feasible embodiment, referring to Figure 2 As shown, an oil unloading hole 16 is further provided in the second oil passage 122. The oil unloading hole 16 is located on the moving path of the valve core 51. The connecting hole 15 is closer to the first oil passage 121 than the oil unloading hole 16, so that when the oil pressure is small and the aligning ring 20 is reset, the excess oil in the control oil chamber 13 is pushed into the second oil passage 122 through the connecting hole 15 and then discharged from the oil unloading hole 16, thereby draining the excess oil in the control oil chamber 13 and allowing the aligning ring 20 to be smoothly reset.

[0050] Furthermore, one end of the oil unloading hole 16 away from the second oil passage 122 is connected to the oil pump chain. When the oil pressure in the second oil passage 122 is relatively high, the valve core 51 is pushed across the connecting hole 15 and the oil unloading hole 16. A part of the oil enters the control oil chamber 13 through the connecting hole 15, and the other part of the oil flows to the oil pump chain through the oil unloading hole 16, thereby assisting in lubricating the oil pump chain and sprocket, thereby increasing the service life of the sprocket and chain. The aperture size (or cross-sectional area) and position of the oil unloading hole 16 play a vital role in regulating the oil pressure, and its position and size are determined based on analysis, calculation and experiments.

[0051] In the embodiment provided in the present application, a rotating pin 14 is provided in the accommodating space 11, and the aligning ring 20 is movably connected to the rotating pin 14. The preset path is the rotational movement path of the aligning ring 20 with the rotating pin 14 as the center. When the engine is idling or at a lower speed, the aligning ring 20 remains at the starting end of the preset path. After the engine speed increases, the excess oil pressure in the main oil channel of the engine enters the feedback oil channel 12, the pressure regulating valve 50 is opened, and the oil pressure enters the control oil chamber 13, pushing the aligning ring 20 to move along the preset path. During the movement of the aligning ring 20 along the preset path, the eccentricity between the aligning ring 20 and the rotor 30 changes, thereby adjusting the displacement of the oil pump.

[0052] Reference Figure 2As shown, there is a second elastic member 21 in the accommodating space 11, and the second elastic member 21 is preferably a spring. The second elastic member 21 is connected to the aligning ring 20 so that the aligning ring 20 can elastically reciprocate on a preset path. In a feasible embodiment, in the initial state, the second elastic member 21 naturally stretches, and the aligning ring 20 is in a stationary state. At this time, the eccentricity between the aligning ring 20 and the rotor 30 is at the maximum position. After the oil pressure in the control oil chamber 13 rises to a sufficiently high level, the aligning ring 20 overcomes the initial preload force of the second elastic member 21, and the aligning ring 20 moves along the preset path in the accommodating space 11. The second elastic member 21 accumulates Store elastic restoring force. When the oil pressure is balanced with the elastic restoring force of the second elastic member 21, the aligning ring 20 stops moving and is in the optimal position. Under the action of the elastic restoring force of the second elastic member 21, the aligning ring 20 can change with the change of the oil pressure in the control oil chamber 13, and the position will also change accordingly. The model and parameters of the second elastic member 21 can be replaced to adjust the initial preload force and the elastic restoring force applied by the second elastic member 21 on the aligning ring 20 to adapt to various working scenarios. After the oil pressure in the control oil chamber 13 gradually decreases to less than the initial preload force of the second elastic member 21, the aligning ring 20 returns to its initial state.

[0053] In a feasible implementation, referring to Figure 1 As shown, a plurality of guide grooves 31 are provided on the outer circumferential surface of the rotor 30. The plurality of guide grooves 31 are arranged in a ring-shaped manner with a preset axis as the center line. The preset axis is located on the extension line of the guide groove 31. The separator 40 includes a plurality of separator blocks 41. The plurality of separator blocks 41 correspond one-to-one to the plurality of guide grooves 31. Each separator block 41 is guided and fitted in the corresponding guide groove 31. A closed area is formed between two adjacent separator blocks 41. Since the centering ring 20 and the rotor 30 are eccentrically arranged, there is a difference in the size of adjacent closed areas. When the centering ring 20 moves along the preset path, the separator block 41 also moves in the guide groove 31, thereby changing the space occupied by each closed area, thereby changing the spatial change amplitude of the closed area, and thereby changing the amount of oil pumped per rotation of the rotor 30.

[0054] Based on the above embodiment, the voltage regulation process of the present invention is as follows:

[0055] When the engine is idling or at a lower speed, the oil pressure in the main oil channel of the engine is low, the pressure regulating valve 50 in the feedback oil channel 12 is not opened, the control oil chamber 13 has no pressure or has a low pressure, and the aligning ring 20 is in a stationary state under the reaction force of the second elastic member 21. At this time, the eccentricity between the aligning ring 20 and the rotor 30 is at the initial maximum position, and the displacement is also the largest. The pressure provided to the lubrication system can just meet the needs of the engine.

[0056] When the engine speed increases, the oil pump speed also increases, the oil supplied to the lubrication system increases, and the oil pressure in the engine main oil channel increases, exceeding the engine's demand for oil pressure. At this time, the excess oil pressure in the engine main oil channel enters the feedback oil channel 12, automatically pushing the pressure regulating valve 50 core to move, the pressure regulating valve 50 opens, and the oil pressure enters the control oil chamber 13. The pressure then pushes the aligning ring 20 and the second elastic member 21, causing the aligning ring 20 to rotate along the rotating pin 14, and the eccentricity between the aligning ring 20 and the rotor 30 begins to gradually decrease. At this time, the flow rate of the oil pump also decreases accordingly; when the pressure is balanced with the reaction force of the second elastic member 21, the aligning ring 20 stops moving and is in the optimal position, and the pressure supplied by the oil pump to the entire lubrication system of the engine is also in the optimal state.

[0057] The above describes in detail the structure, features and effects of the present invention based on the embodiments shown in the drawings. The above is only a preferred embodiment of the present invention, but the scope of implementation of the present invention is not limited to what is shown in the drawings. Any changes made in accordance with the concept of the present invention, or modifications to equivalent embodiments with equivalent changes, which do not exceed the spirit covered by the description and drawings, should be within the scope of protection of the present invention.

Claims

1. A variable displacement oil pump, characterized in that: include: A pump body, wherein the pump body has a receiving space and a feedback oil channel; A centering ring is disposed in the accommodating space, wherein a control oil chamber is formed between an outer wall surface of the centering ring and an inner wall surface of the accommodating space, the control oil chamber is connected to the feedback oil passage, and the centering ring can move along a preset path; A rotor is located in the centering ring and is eccentrically arranged with respect to the centering ring, and the rotor can rotate around a preset axis; a separator disposed in the centering ring, the separator being used to separate the space between the outer wall surface of the rotor and the inner wall surface of the centering ring into a plurality of sealed areas, wherein the areas of different sealed areas are different; A pressure regulating valve is at least partially located in the feedback oil channel, and the pressure regulating valve is used to control the on-off and flow rate of the feedback oil channel.

2. The variable displacement oil pump according to claim 1, characterized in that: The feedback oil passage includes a first oil passage and a second oil passage that are connected to each other. The first oil passage is connected to the main oil passage of the engine. The second oil passage has a connecting hole, and the connecting holes are connected to the second oil passage and the control oil chamber respectively. The pressure regulating valve includes a valve core, which is movably arranged in the second oil channel. The outer surface of the valve core is tightly fitted with the inner surface of the second oil channel, and the communicating hole is located on the moving path of the valve core.

3. The variable displacement oil pump according to claim 2, characterized in that: A first elastic member is further provided in the second oil passage. The first elastic member is connected to the valve core so that the valve core can elastically move back and forth in the second oil passage.

4. The variable displacement oil pump according to claim 3, characterized in that: One end of the second oil passage away from the first oil passage is threadedly connected to a screw plug, and the screw plug is connected to the first elastic member.

5. The variable displacement oil pump according to claim 4, characterized in that: The first elastic member is a spring, and opposite ends of the spring are respectively in contact with the valve core and the screw plug.

6. The variable displacement oil pump according to claim 2, characterized in that: An oil unloading hole is further provided in the second oil passage. The oil unloading hole is located on the moving path of the valve core. The communicating hole is closer to the first oil passage than the oil unloading hole.

7. The variable displacement oil pump according to claim 6, characterized in that: One end of the oil unloading hole away from the second oil passage is connected to an oil pump chain.

8. The variable displacement oil pump according to claim 1, characterized in that: A rotating pin is provided in the accommodating space, the centering ring is movably connected to the rotating pin, and the preset path is the rotational movement path of the centering ring with the rotating pin as the center.

9. The variable displacement oil pump according to claim 1, characterized in that: A second elastic member is provided in the accommodating space, and the second elastic member is connected to the centering ring so that the centering ring can elastically move back and forth on the preset path.

10. The variable displacement oil pump according to claim 1, characterized in that: A plurality of guide grooves are provided on the outer circumferential surface of the rotor, and the plurality of guide grooves are arranged in a ring-shaped manner with the preset axis as the center line. The preset axis is located on the extension line of the guide groove. The separator includes a plurality of separator blocks, and the plurality of separator blocks correspond to the plurality of guide grooves one by one. Each of the separator blocks is guided and fitted into the corresponding guide groove.

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