JP2016102423A - Oil pump - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an oil pump capable of properly restarting an engine.SOLUTION: An oil pump 100 includes an adjustment ring 14 relatively rotatably supporting an outer rotor 13 from a radial outer side in a state that an external tooth 12A of an inner rotor 12 and an internal tooth 13A of the outer rotor 13 are engaged with each other, an operating portion 50 which is disposed on an outer peripheral face of the adjustment ring 14, and to which driving force is input to increase and decrease a pressure of an oil discharged from a discharge port 3, a guide portion G communicated with a suction port 2 or the discharge port 3, disposed on a casing 1 including the inner rotor 12 and the outer rotor 13, and the adjustment ring 14, and guiding the adjustment ring 14 according to driving force input to the operating portion 50, and driving force control portion 16 controlling driving force input to the operating portion 50, and maximizing a pressure of the oil discharged from the discharge port 3 before stop of an engine E when the stop of the engine E is instructed.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a variable displacement oil pump.

  2. Description of the Related Art Conventionally, variable displacement oil pumps that can change the suction amount and discharge amount of a pump have been used. As such a variable displacement type oil pump, for example, an inner rotor having external teeth and driven around a driving rotation axis, and an inner tooth engaging with the inner rotor in an eccentric state, and rotating around a driven axis. Some have an outer rotor provided inside the casing. This type of oil pump is provided with an adjustment ring that revolves the driven center of the outer rotor around the driving rotation axis in a state where the inner rotor and the outer rotor mesh with each other, and the adjustment ring is displaced to displace the outer rotor. The pump capacity can be changed by revolving.

  In changing the pump capacity in this way, in the variable capacity type oil pump, the outer rotor is configured to revolve with respect to the inner rotor, so the size of the gap formed between the casing and the outer rotor Changes. When foreign matter is caught between the casing and the adjustment ring, the range in which the outer rotor can revolve is limited with respect to the preset maximum range. May deviate from pressure. Then, the technique which detects whether such a foreign material was bitten has been examined (for example, patent document 1).

  The hydraulic control device for an internal combustion engine described in Patent Literature 1 includes a pressure stage switching mechanism, a detection unit, and a determination unit. The pressure stage switching mechanism controls the oil pressure by switching the pressure of the oil supplied to each part of the engine between a high pressure state and a low pressure state. The detecting means detects the pressure of the oil after being controlled by the pressure stage switching mechanism. The determination means is assumed when the oil pressure detected by the detection means is in a high pressure state in a state in which a command to set the oil pressure to a high pressure state is output to the pressure stage switching mechanism. It is determined that an abnormality has occurred in the pressure stage switching mechanism when the value falls below a predetermined abnormality determination value that is set between a value and a value that is assumed when the pressure is low. Alternatively, when the oil pressure detected by the detecting means is in a high pressure state in a state where a command is output to the pressure stage switching mechanism to set the oil pressure to a low pressure state, the determination means is It is determined that an abnormality has occurred in the pressure stage switching mechanism when it exceeds a predetermined abnormality determination value that is set between a value that is assumed and a value that is assumed when the pressure is low.

JP 2010-116890 A

  The technique described in Patent Document 1 detects an abnormality (such as a foreign object biting) during control of the oil pressure by the pressure stage switching mechanism, and does not prevent an abnormality due to the foreign object biting in advance. . For this reason, for example, when the oil pressure is low and the oil pump is stopped by engaging foreign matter, the required oil pressure cannot be supplied to the engine even if the engine is restarted. It may be impossible to start.

  In view of the above problems, an object of the present invention is to provide an oil pump that can prevent foreign matter from getting caught and can restart the engine satisfactorily.

  In order to achieve the above object, the oil pump according to the present invention includes a plurality of external teeth, an inner rotor that rotates about a first rotational axis by a rotational force transmitted from an engine, and the outer An outer rotor that is formed in an annular shape having a plurality of inner teeth that mesh with the teeth, and that rotates in accordance with the rotation of the inner rotor with a second rotation axis that is eccentric with respect to the first rotation axis; and the outer teeth A suction port that supplies oil between the inner teeth and a discharge port that discharges oil supplied from the suction ports as the inner rotor rotates from between the outer teeth and the inner teeth are formed. An adjustment ring that supports the outer rotor from the outside in the radial direction in a state in which the casing enclosing the inner rotor and the outer rotor meshes with the outer teeth and the inner teeth. An operating portion that is provided on the outer peripheral surface of the adjustment ring and that increases or decreases the pressure of oil discharged from the discharge port when a driving force is input; and the suction port or the discharge port; and the casing and the adjustment A guide portion that is provided on the ring and guides the adjustment ring so that the second rotation axis revolves around the first rotation axis according to a driving force input to the operation unit; A driving force control unit that controls the driving force input to the operation unit and, when instructed to stop the engine, maximizes the pressure of oil discharged from the discharge port before stopping the engine; It is in the point to have.

  With such a characteristic configuration, the guide unit guides the adjustment ring so that the second rotation axis revolves around the first rotation axis in accordance with the driving force input to the operation unit. At this time, even if a foreign object is caught in the guide portion, the foreign object can be discharged to the suction port or the discharge port before the engine is stopped. For this reason, when the engine is restarted, it is possible to prevent the movable range of the adjustment ring from being restricted due to the biting of foreign matter. Therefore, even when the oil discharge amount required for the oil pump when restarting the engine is large, it is possible to prevent foreign matter from getting caught and to restart the engine satisfactorily.

  Further, it is preferable that the stop instruction is a state in which a gear stage not for forward travel is selected in the transmission mechanism to which the rotational force of the engine is transmitted.

  With such a configuration, the driving force control unit can easily identify that there has been an instruction to stop the engine. Therefore, the driving force control unit can reliably set the pressure of the oil discharged from the discharge port to the maximum side before the engine is stopped.

It is sectional drawing of the oil pump in a pump capacity | capacitance maximum state. It is sectional drawing of the oil pump in a pump capacity minimum state. It is a flowchart which shows control of an oil pump.

  The oil pump according to the present invention is configured such that the engine can be restarted even when the movable part in the oil pump bites in a foreign object immediately before the engine is stopped. Hereinafter, the oil pump 100 of the present embodiment will be described in detail. FIG. 1 shows a variable displacement oil pump 100 whose discharge pressure can be changed as an example of the oil pump 100. In the present embodiment, the oil pump 100 is mounted on a vehicle and driven by the engine E of the vehicle. The use is for supplying oil for lubricating the engine E and supplying oil to hydraulic equipment such as a valve opening / closing timing control device of the engine E.

  The oil pump 100 according to this embodiment includes an inner rotor 12, an outer rotor 13, a casing 1, an adjustment ring 14, a suction port 2, a discharge port 3, an operation unit 50, a guide unit G, a driving force control unit 16, and discharge pressure detection. A unit 17 and a shift position detection unit 18 are provided. In particular, in order to perform various processes for changing the capacity of the oil pump 100, the driving force control unit 16 is constructed by hardware and / or software using a CPU as a core member.

  The inner rotor 12 has a plurality of external teeth 12A, and rotates about the first rotation axis X by the rotational power transmitted from the engine E. The inner rotor 12 is formed in an annular shape, and a plurality of external teeth 12A are formed on the outer peripheral surface thereof. These external teeth 12A are configured in a tooth surface shape according to a trochoid curve, a cycloid curve, or the like. In this embodiment, rotational power is transmitted from the engine E (the crankshaft of the engine E) to the inner rotor 12. The engine E is a power source of a vehicle on which the oil pump 100 is mounted. The inner rotor 12 is arranged coaxially with the first rotation axis X, is rotatably supported with respect to the casing 1 via the drive shaft 11 to which the rotational power of the engine E is transmitted, and is integrated with the drive shaft 11. Rotate.

  The outer rotor 13 is formed in an annular shape having a plurality of internal teeth 13A meshing with the external teeth 12A, and rotates according to the rotation of the inner rotor 12 with a second rotation axis Y that is eccentric with respect to the first rotation axis X. To do. The outer rotor 13 is also formed in an annular shape like the inner rotor 12, and a plurality of internal teeth 13A are formed on the inner peripheral surface thereof. The inner teeth 13A of the outer rotor 13 are configured to have one more tooth than the outer teeth 12A of the inner rotor 12, and when the outer rotor 13 rotates, the tooth surface that contacts the outer teeth 12A of the inner rotor 12 It is molded into a shape. Therefore, a predetermined gap Q is provided between the outer teeth 12A and the inner teeth 13A.

  The casing 1 includes an inner rotor 12 and an outer rotor 13. Encapsulating means including and configuring inside.

  Further, a suction port 2 and a discharge port 3 are formed in the casing 1. The suction port 2 is an opening formed in the wall 1 </ b> A of the casing 1. Specifically, the suction port 2 is provided on the wall 1 </ b> A facing the axial end surface of the outer rotor 13 in the inner wall of the casing 1, and is provided along the radial direction of the outer rotor 13. From such a suction port 2, oil is supplied between the external teeth 12A and the internal teeth 13A. Between the external teeth 12A and the internal teeth 13A is the predetermined gap Q described above. As a result, oil is supplied to the gap Q between the outer teeth 12 </ b> A and the inner teeth 13 </ b> A from the suction port 2 provided on the axial end portions of the inner rotor 12 and the outer rotor 13.

  Similarly to the suction port 2, the discharge port 3 also includes an opening formed in the wall portion 1 </ b> A of the casing 1. Specifically, the discharge port 3 is provided on the wall portion 1 </ b> A facing the axial end surface of the outer rotor 13 in the inner wall of the casing 1, and is provided along the radial direction of the outer rotor 13. In the present embodiment, the discharge port 3 is provided on the wall portion 1A on the side where the suction port 2 is provided. That is, the suction port 2 and the discharge port 3 are provided in the wall portion 1A facing the same direction. Moreover, the opening part which comprises the discharge port 3 is spaced apart from the opening part which comprises the suction port 2, and is provided along the radial direction of the outer rotor 13. As shown in FIG. From such a discharge port 3, the oil supplied from the suction port 2 with the rotation of the inner rotor 12 is discharged from between the outer teeth 12A and the inner teeth 13A. Between the external teeth 12A and the internal teeth 13A is the predetermined gap Q described above. Accordingly, oil flows out from the gap Q between the outer teeth 12A and the inner teeth 13A to the discharge port 3 provided on the side of the inner rotor 12 and the outer rotor 13 in the axial direction.

  In the oil pump 100, the inner rotor 12 is driven to rotate in the direction of arrow A. Therefore, when the adjustment ring 14 is in the posture (initial position) shown in FIG. 1, the negative pressure acting region that reduces the pressure between the outer teeth 12 </ b> A of the inner rotor 12 and the inner teeth 13 </ b> A of the outer rotor 13 is used. The suction port 2 faces, and the discharge port 3 faces a positive pressure acting region that compresses oil between the outer teeth 12A of the inner rotor 12 and the inner teeth 13A of the outer rotor 13. This functions to suck oil from the suction port 2 and send oil from the discharge port 3.

  The adjustment ring 14 supports the outer rotor 13 so as to be relatively rotatable from the outside in the radial direction in a state where the outer teeth 12A and the inner teeth 13A are engaged with each other. The adjustment ring 14 is formed in a ring shape having an inner peripheral surface coaxial with the second rotation axis Y so as to insert the outer rotor 13 therein. In addition, the outer periphery of the outer rotor 13 is formed in a circular shape centered on the second rotation axis Y. As a result, the center position of the inner periphery of the adjustment ring 14 coincides with the position of the second rotation axis Y of the outer rotor 13, and the adjustment ring 14 supports the outer peripheral surface of the outer rotor 13 on its inner peripheral surface.

  The operation unit 50 is provided on the outer peripheral surface of the adjustment ring 14 and increases or decreases the pressure of oil discharged from the discharge port 3 when a driving force is input. In the present embodiment, the operation unit 50 is provided so as to protrude from the outer peripheral surface of the adjustment ring 14 in a direction away from the second rotation axis Y. The driving force is a driving force that revolves the second rotational axis Y of the outer rotor 13 around the first rotational axis X of the inner rotor 12 as described later. Here, the outer rotor 13 is accommodated in the adjustment ring 14 so as to be relatively rotatable. For this reason, the adjustment ring 14 revolves around the first rotation axis X as the second rotation axis Y revolves. Therefore, the driving force input to the operation unit 50 corresponds to a driving force for revolving the adjustment ring 14 itself.

  The guide portion G is provided on the casing 1 and the adjustment ring 14 and is adjusted so that the second rotation axis Y revolves around the first rotation axis X according to the driving force input to the operation unit 50. Guide the ring 14. In the present embodiment, a guide pin 31 that protrudes parallel to the first rotation axis X is formed on the wall 1 </ b> A of the casing 1 so as to protrude. Guide grooves 32 into which the protruding ends of these two guide pins 31 are respectively fitted are formed at two locations on the outer peripheral portion of the adjustment ring 14. The two guide pins 31 and the two guide grooves 32 constitute a guide portion G. The first guide portion G1 configured by one of the two guide pins 31 and one of the two guide grooves 32 communicates with the suction port 2, and the other of the two guide pins 31 and the other of the two guide grooves 32. The configured second guide part G2 is provided in communication with the discharge port 3. Below, when it is not necessary to distinguish the 1st guide part G1 and the 2nd guide part G2, it demonstrates as the guide part G. FIG.

  In addition, an engagement recess 36 is formed between the first guide part G1 and the second guide part G2 on the outer periphery of the adjustment ring 14. A seal vane 37 is disposed between the casing 1 and the engagement recess 36.

  Here, a pressurized space 1Q in which the discharge pressure from the discharge port 3 acts is formed inside the casing 1, and the first pressure chamber 51 on the high pressure side in which the oil pressure in the pressurized space 1Q directly acts. And a second pressure chamber 52 on the low pressure side in which the pressure of the oil in the pressurizing space 1Q acts via the electromagnetic valve V is formed. The oil in the first pressure chamber 51 is sealed by the seal vane 37, and the oil pressure in the second pressure chamber 52 acts on the operation unit 50. The operation unit 50 has a large pressure receiving area in order to receive the oil pressure efficiently, and the compression coil spring 6 is disposed on the side opposite to the direction in which the oil pressure acts.

  In the oil pump 100, the oil in the pressurizing space 1Q is supplied to the electromagnetic valve V through the oil filter 55, and the oil from the electromagnetic valve V is supplied to the second pressure chamber 52 through the oil passage 56. It is configured as follows. The oil passage 56 is formed in the casing 1 in a groove shape.

  In this oil pump 100, the protruding end of the operation portion 50 is brought into sliding contact with the inner peripheral surface of the casing 1 when the adjustment ring 14 is operated. At this time, an engagement recess 58 is formed at the protruding end of the operation portion 50 so that oil in the second pressure chamber 52 does not leak from the sliding portion, and a seal vane is provided between the casing 1 and the engagement recess 58. 59 is arranged. Thereby, the adjustment ring 14 can be operated without the oil supplied to the second pressure chamber 52 leaking.

  The discharge pressure detection unit 17 detects the pressure of oil discharged from the discharge port 3. The discharge pressure detection unit 17 includes a pressure sensor that detects oil pressure. The oil discharged from the discharge port 3 corresponds to oil immediately after discharge from the discharge port 3 or oil supplied to the main gallery M as hydraulic equipment such as the valve opening / closing timing control device described above. In the present embodiment, the discharge pressure detection unit 17 detects the pressure of oil supplied to the main gallery M. Hereinafter, “pressure of oil discharged from the discharge port 3” will be described as “discharge pressure”. The detection result by the discharge pressure detection unit 17 is transmitted to a driving force control unit 16 described later.

  The driving force control unit 16 controls the driving force input to the operation unit 50 so that the pressure of oil discharged from the discharge port 3 becomes a desired required oil pressure. The oil pressure of the oil discharged from the discharge port 3, that is, the discharge pressure is transmitted as a detection result of the discharge pressure detection unit 17 described above. The desired required oil pressure is set in advance according to the rotational speed of the engine E in this embodiment. This is because the hydraulic pressure required for the main gallery M differs depending on the rotational speed of the engine E. Such a required oil pressure is preferably stored in advance in the driving force control unit 16 as a map that defines the relationship between the engine speed and the required oil pressure. Rotational speed information indicating the current rotational speed of the engine E is also transmitted from the engine E to the driving force control unit 16.

  Such a driving force control part 16 is comprised by ECU etc., and controls the solenoid valve V based on required hydraulic pressure. As specific examples of the control, a low pressure control mode, a high pressure control mode, and a DUTY control mode for repeatedly changing the low pressure control and the high pressure control are set. Specifically, it may be changed between the low pressure control and the high pressure control, or may be changed by appropriately setting each DUTY. Furthermore, the DUTY set value may be exchanged at a constant cycle or may be changed at random. Moreover, you may set suitably the period which replaces DUTY setting value.

  In the high pressure control mode, the solenoid valve V is set to a position that prevents oil from coming out of the pressurizing space 1Q and opens the second pressure chamber 52 to the atmosphere. In the low pressure control mode, the solenoid valve V is set to a position where oil from the pressurizing space 1Q is applied to the operation unit 50 via the oil passage 56.

  As described above, by setting the driving force control unit 16 to the high pressure control mode, the operation of increasing the oil discharge amount from the oil pump 100 is realized, and by setting the driving force control unit 16 to the low pressure control mode. Realizes the operation to reduce the oil discharge amount from the oil pump 100 even when the rotation speed of the engine E is low, or to reduce the oil discharge amount from the oil pump 100 only when the rotation speed of the engine E is high. To do. Accordingly, it is possible to suppress an inconvenience that the excessive amount of oil is discharged based on the conditions or the discharge pressure is excessively increased to deteriorate the fuel efficiency of the engine E.

  The driving force control unit 16 controls the electromagnetic valve V so that the detection result of the discharge pressure detection unit 17 coincides with the required hydraulic pressure set according to the current rotation speed of the engine E, so that the adjustment ring 14 The input driving force is controlled by feedback control.

  Thereby, the inner rotor 12 and the outer rotor 13 can be brought into the state shown in FIG. 1 or the state shown in FIG. That is, in the state of FIG. 1, the drive shaft 11 is driven and rotated as described above, whereby oil is sucked from the suction port 2 and oil is discharged from the discharge port 3.

  On the other hand, in the state of FIG. 2, the movement of the second rotation axis Y revolving around the first rotation axis X is performed, and at the same time, the adjustment ring 14 rotates around the second rotation axis Y. To do. Accordingly, at this time, the outer rotor 13 also moves together, and the second rotation axis Y revolves around the first rotation axis X in a state where the outer teeth 12A of the inner rotor 12 are engaged with the inner teeth 13A of the outer rotor 13.

  In this way, the positive pressure acting region and the negative pressure acting region move around the first rotation axis X, the negative pressure acting on the suction port 2 from the negative pressure acting region decreases, and the discharge port from the positive pressure acting region. The positive pressure acting on 3 also decreases. As a result, the amount of oil supplied by the oil pump 100 is reduced.

  When the adjustment ring 14 is moved to the moving end position shown in FIG. 2, the negative pressure acting region and the positive pressure acting region are in a positional relationship across the suction port 2 and the discharge port 3. For this reason, almost no negative pressure acts on the suction port 2, and almost no positive pressure acts on the discharge port 3. For this reason, oil is not supplied or discharged, and as a result, the amount of oil discharged is reduced.

  Thus, in the present oil pump 100, the adjustment ring 14 revolves around the second rotation axis Y by 90 degrees. At this time, in the normal state, in the guide portion G, the guide pin 31 and the guide groove 32 slide with each other over an intended range. When the guide pin 31 and the guide groove 32 slide, for example, if the guide pin 31 or the guide groove 32 is scraped and the residue is caught as a foreign matter, the oil in the second pressure chamber 52 is released to the atmosphere. Even in this case, the oil discharge amount from the discharge port 3 may not be maximized.

  That is, when a foreign object is caught between the guide pin 31 and the guide groove 32, the adjustment ring 14 cannot move to the position shown in FIG. 1 or FIG. Therefore, a desired required hydraulic pressure that is uniquely determined cannot be realized, and a phenomenon occurs in which the hydraulic pressure increases or decreases. For this reason, if the engine E is restarted in such a state, the required hydraulic pressure cannot be supplied and the engine E may not be started.

  Therefore, the oil pump 100 is configured to maximize the discharge amount of the oil pump 100 before stopping the engine E when a stop command is issued to the engine E. Such control is performed by the driving force control unit 16.

  That is, when the engine E is instructed to stop, the driving force control unit 16 controls the electromagnetic valve V so as to maximize the pressure of the oil discharged from the discharge port 3 before the engine E is stopped. In the present embodiment, when the engine E is instructed to stop, the transmission mechanism TM to which the rotational force of the engine E is transmitted corresponds to a state where a gear stage not for forward travel is selected. The gears not for forward travel are “neutral gear” and “reverse gear” when the transmission mechanism TM is a manual transmission type, and “neutral gear” when the transmission mechanism TM is an automatic transmission type. Or “reverse gear” or “parking gear”. Whether or not such a gear is selected is detected by the shift position detector 18, and the detection result is transmitted to the driving force controller 16.

  Maximizing the pressure of oil discharged from the discharge port 3 means maximizing the amount of oil discharged from the discharge port 3, and means that the state shown in FIG. Therefore, the driving force control unit 16 controls the state shown in FIG. 1 so that the oil discharged from the discharge port 3 is maximized when the gear stage not for forward travel is selected, and then The engine E is stopped. As a result, even if foreign matter is generated in the guide portion G before the engine E is stopped, it can be discharged to either the suction port 2 or the discharge port 3. Therefore, since the engine E is stopped after the adjustment ring 14 is shifted to the state shown in FIG. 1, when the engine E is to be restarted, the engine E can be started smoothly.

  Even if foreign matter is not discharged from the guide portion G before the engine E is started, the adjustment ring 14 can be moved to a position where the amount of oil discharged from the discharge port 3 is maximized. Therefore, when the engine E is restarted, it can be avoided that the amount of oil increases and the engine E cannot be started.

Next, control of the oil pump 100 will be described with reference to the flowchart of FIG.
When the vehicle stops traveling (step # 1: Yes), the gear position selected in the transmission mechanism TM is detected by the shift position detector 18 (step # 2).

36).
At this time, when the forward gear is selected (step # 3: Yes), the driving force control unit 16 controls the oil pressure discharged from the oil pump 100 while changing it to an appropriate hydraulic pressure. (Step # 4). The vehicle continues to travel (step # 5) and returns to step # 1 to continue the process.

  In step # 3, when the forward gear is not selected (step # 3: No), the driving force control unit 16 enters the high pressure control mode in which the oil discharged from the oil pump 100 becomes the maximum side. Control (step # 6). After this control, the engine E is stopped (step # 7), and the process ends.

  In this way, the oil pump 100 controls the discharge amount to the maximum before stopping the engine E, which is the power source of the oil pump 100, so that foreign matter is temporarily present in the guide portion G during the operation of the oil pump 100. Even if it exists, the foreign matter can be discharged from the guide portion G before the engine E is stopped. Therefore, it is possible to prevent the foreign matter from being caught in the guide portion G, and hence it is possible to prevent the starting failure of the engine E thereafter.

[Other Embodiments]
In the above embodiment, the driving force control unit 16 has been described as controlling the electromagnetic valve V based on the oil discharge pressure from the discharge port 3, but instead of the oil discharge pressure from the discharge port 3, the rotation of the engine E is performed. It may be controlled by the number and the number of rotations of the oil pump 100, or may be controlled by other methods.

  In the above-described embodiment, it has been described that the instruction to stop the engine E is a state in which the gear stage that is not for forward travel is selected in the transmission mechanism TM. However, the engine stop button may be pressed. The engine key may be turned off. In this case, the adjustment ring 14 operates so that the oil discharge amount of the oil pump 100 reaches the maximum side from the time when the engine stop button is pressed or the engine key is turned off. It is preferable to delay the stop of the engine E for a predetermined time so that

  The present invention can be used for a variable displacement oil pump.

1: Casing 2: Suction port 3: Discharge port 12: Inner rotor 12A: External teeth 13: Outer rotor 13A: Internal teeth 14: Adjustment ring 16: Driving force control unit 100: Oil pump 50: Operation unit E: Engine G: Guide part TM: Transmission mechanism X: First rotation axis Y: Second rotation axis

Claims (2)

An inner rotor having a plurality of external teeth and rotating about a first rotation axis by a rotational force transmitted from the engine;
An outer rotor that is formed in an annular shape having a plurality of internal teeth that mesh with the external teeth, and that rotates according to the rotation of the inner rotor at a second rotational axis that is eccentric with respect to the first rotational axis;
A suction port that supplies oil between the external teeth and the internal teeth, and a discharge port that discharges oil supplied from the suction ports as the inner rotor rotates from between the external teeth and the internal teeth And a casing enclosing the inner rotor and the outer rotor;
An adjustment ring that supports the outer rotor so as to be relatively rotatable from the radially outer side in a state where the outer teeth and the inner teeth mesh with each other;
An operating portion that is provided on the outer peripheral surface of the adjustment ring and that increases or decreases the pressure of oil discharged from the discharge port when a driving force is input;
The second rotation axis is centered on the first rotation axis according to the driving force input to the operation portion, provided in the casing and the adjustment ring, and communicating with the suction port or the discharge port. A guide portion that guides the adjustment ring so as to revolve.
A driving force control unit that controls the driving force input to the operation unit, and when the engine is instructed to stop, the driving force control unit that maximizes the pressure of oil discharged from the discharge port before the engine stops;
Oil pump equipped with.   2. The oil pump according to claim 1, wherein the stop instruction is a state in which a gear stage not for forward travel is selected in a transmission mechanism to which the rotational force of the engine is transmitted.

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