JPH0550093U - Variable displacement vane pump device - Google Patents

Abstract

(57) [Summary] [Purpose] At low speeds, prevent the pump discharge flow rate from fluctuating by the switching operation of the pressure sensing type switching valve. [Configuration] Second suction port 4 forming a specific pump chamber
An electromagnetic valve 16 is provided at an intermediate portion of a suction-side passage 22 that connects between 1'and the pressure-sensitive switching valve 1. A control means 17 for controlling the operation of the solenoid valve 16 is provided. This control means 1
7 is provided with a rotation speed sensor 18 for inputting a rotation speed signal,
When the rotation speed is low, the control means 17 controls switching by the signal from the rotation speed sensor 18 so that the spool 161 of the solenoid valve 16 closes the intake passage 22. As a result, at a low rotational speed, the discharge oil is forcibly delivered from the specific pump chamber regardless of the load pressure, so that the steering force assist does not fluctuate and a good steering feeling can be obtained.

Description

[Detailed description of the device]

[0001]

[Industrial applications]

 The present invention relates to a variable displacement vane pump, and more particularly to a hydraulic pump device suitable for supplying a working fluid to a power steering device for an automobile.

[0002]

[Prior Art]

 In the hydraulic pump device used in the power steering system for automobiles, the discharge capacity of the pump is set so that the steering force can be sufficiently assisted even at low speed running (generally when the engine speed is low). Therefore, in such a hydraulic pump, the hydraulic oil is discharged at a flow rate proportional to the engine speed as the engine speed (engine speed) rises. This means that the flow rate of hydraulic fluid becomes excessive during high-speed running (generally when the engine speed is high), where steering force assistance is rarely needed. In order to deal with such a phenomenon, a part of the hydraulic oil discharged from the pump (discharging oil) is not sent to the power assist section of the power steering system, but is bypassed to the hydraulic pump to control the flow rate. (Flow control valve) The method is widely used.

However, in this flow rate control valve system, high-pressure discharge oil discharged from the hydraulic pump is guided to the flow rate control valve, discharged from there to a bypass passage, and then returned to the pump suction port side. Therefore, when the engine rotates at high speed, it consumes energy according to the engine speed. In other words, the bypass recirculation method using the flow control valve causes energy loss due to bypass recirculation when almost no steering force assistance is required when driving at high speeds. There is a problem that it leads to deterioration of fuel efficiency. Therefore, as a means for reducing the energy loss when such steering force assistance is not required, there is a conventional one using a switching valve as disclosed in JP-A-60-256579. Has been adopted.

This is a vane pump including a rotor, a vane, a cam ring, a side plate, a housing, and the like, to which a switching valve including a spool and a spring is added. And when the steering wheel is not steered because the power assist part needs a small amount of hydraulic oil for assisting the steering force due to the action of the switching valve, the hydraulic oil is circulated in a part of the vane pump to While the pump function is stopped to reduce energy loss, when steering wheel steering that requires a large amount of hydraulic oil, the switching valve is switched using the pressure generated by steering wheel as a parameter to stop the pump. It aims to provide sufficient power assist by restoring the function of the room.

[0005]

[Problems to be solved by the device]

By the way, in the vane pump device that increases and decreases the pump discharge capacity by the switching valve system that switches by pressure as described above, when the pump rotation speed (rotation speed) is low, the same pump rotation speed N ₁ as shown in FIG. Even at this time, the pump discharge flow rate shows a value different from Q ₁ or Q ₂ depending on whether the specific pump chamber is stopped or all pump chambers are in full operation. This means that the amount of hydraulic oil supplied to the power assist section differs, which in turn results in different steering force assistance states. Therefore, when the pump speed is the same, that is, even when the engine speed is the same, the power assist amount changes, which makes the steering feeling of the power steering device uncomfortable. Therefore, it is an object (problem) of the present invention to provide an energy-saving variable displacement vane pump device that solves such a problem in steering feeling.

[0006]

[Means for Solving the Problems]

 In order to solve the above problems, in the present invention, a rotor that is housed in a housing and is rotationally driven, a vane that slides in a slit of the rotor, the rotor that is outside the vane, A cam ring that forms a pump chamber together with a vane, a side plate on the side surface of the rotor, vane, and cam ring that contributes to the formation of the pump chamber, a plurality of sets of suction ports and discharge ports provided on the side plate, etc. When the discharge flow rate of the discharge oil (working oil) delivered from the vane pump consisting of the above and the pressure chambers connected to each of the discharge ports exceeds a specified value, the excess discharge oil is bypassed to the bypass passage connected to the suction port. A hydraulic pump device comprising a flow control valve for recirculation, the suction side passage communicating with a suction chamber provided on the suction port side, the discharge Has a communication passage communicating with a specific port of the pressure port, has a discharge passage connecting the specific discharge port and the pressure chamber, and has the specific discharge at the tip of the discharge passage. It has a check valve that operates only to let discharge oil flow out from the port side to the pressure chamber side, and further shuts off the communication state between the communication passage and the suction side passage by the pressure of the pressure chamber. In a variable displacement vane pump device equipped with a pressure sensing type switching valve that switches as described above, a rotational speed (rotation speed) is increased between the pressure sensing type switching valve and the specific suction port or the specific discharge port. A switching mechanism that operates in accordance with the above is provided, and a control means is provided for controlling the operation of the switching mechanism so as to shut off the switching valve and the specific port when the rotation speed is low. speed Rotational speed of the input rotation speed) signal (it was decided to adopt a configuration in which the rotational speed) sensor.

[0007]

[Action]

 With the above configuration, in the present invention, when the vane pump starts to operate, for example, in FIG. 1, the hydraulic oil sucked from the suction passage is guided to the suction chamber 28 and is guided to the suction chamber 28. A part of the hydraulic oil thus sucked is sucked from the first suction port 41, pressurized in the pump chamber, and discharged from the first discharge port 31 to the pressure chamber 27. After that, the flow rate is controlled by the flow rate control valve 26, and the flow rate is sent to a power assist unit (not shown) of the power steering apparatus.

By the way, when the power assist section is not assisting the steering force (power assist), the hydraulic pressure (load pressure) of the power assist section is low, and therefore the pressure of the pressure chamber 27 is low. Is also kept low. As a result, since the pressure introduced from the pressure introducing passage 21 is also low, the spool 11 of the pressure sensing type switching valve 1 is pushed to the right by the action of the spring force of the spring 15 and is placed in the state shown by the solid line in FIG. .. As a result, the communication passage 23 and the suction side passage 22 are brought into communication with each other through the inside of the pressure sensing type switching valve 1. However, in the present invention, when the rotation speed (rotation speed) is low, the solenoid valve 16 is closed. As shown in FIG. 1, the spool 161 operates so as to block the suction-side passage 22, so that the second discharge port 31 ′ which is the specific discharge port and the second suction port 41 ′ which is the specific suction port. The communication with is cut off, and the hydraulic oil is not circulated. Therefore, the oil discharged from the second discharge port 31 ′ is constantly sent from the discharge port 81 to the pressure chamber 27. That is, in FIG. 6, at the low speed rotation, the pump discharge flow rate in the all pump chamber operating state can be obtained as shown by the solid line regardless of the load pressure.

When the pump rotation speed reaches a certain value and is at least N ₂ rotation speed or more, the solenoid valve 16 operates and the spool 161 moves to the state shown in FIG. Therefore, the pressure sensing type switching valve 1 is switched according to the change of the load pressure of the pressure chamber 27, and all pump chambers are in full operation or a specific pump chamber is stopped to be in an energy saving state. The operation or stop state of these specific pump rooms will be described based on Table 1.

In the case of the condition (a), that is, in this case, the engine rotation speed is in the low speed state, the steering force assistance is hardly performed, and the load pressure of the power assist unit is also in the low pressure state. This is the case. In this case, since the load pressure is low when only the pressure sensing type switching valve 1 is used, the discharge oil from the second discharge port 31 'which is a specific port circulates to the second suction port 41' which is a specific suction port. However, in the present invention, the circulation path is shut off by the action of the solenoid valve 16 or the like which operates according to the engine speed (rotation speed), and the pressure chamber 27 is also supplied from the second discharge port 31 '. The discharged oil will be sent to. That is, both the first pump chamber and the second pump chamber operate. Next, in the case of condition (b), the engine speed is low and the load pressure of the power assist unit is high, so it is necessary to make a large amount of power assistance. Therefore, the first pump chamber and the second pump chamber are both in full operation. Next, the condition (C) is a case where the engine speed is high and the load pressure of the power assist unit is a low pressure state. In this state, almost no power assist is required. Therefore, the solenoid valve 16 is operated so that the suction side passage 22 is opened, and the pressure sensing type switching valve 1 is also connected to the communication passage 23 and the suction side passage. 22 is switched to be in a communication state. As a result, the hydraulic oil circulates in the second pump chamber, which is a specific pump chamber, and the pump function is stopped, resulting in an energy-saving operation state. Finally, in the case of condition (d), the engine speed is high and the load pressure of the power assist unit is high. In this case, the spool 161 connected to the solenoid valve 16 is switched so as to open the suction side passage, but the pressure sensing type switching valve 1 makes the communication state between the suction side passage 22 and the communication passage 23. Since the switching is made so as to be cut off, the circulation of the hydraulic oil in the second pump chamber is cut off, and the discharge oil is also sent from the second pump chamber to the pressure chamber 27.

[0011]

【Example】

 A first embodiment according to the present invention will be described with reference to FIGS. As shown in FIG. 1, the structure of this embodiment is such that a vane pump including a rotor 6, a vane 7, a cam ring 5 and the like, a pressure sensing type switching valve 1 including a spool 11 and a spring 15 and the pressure sensing type switching. A solenoid valve 16 provided at an intermediate portion of a suction side passage 22 connecting the valve 1 and the suction chamber 28, a control means 17 for controlling the operation of the solenoid valve 16, and a rotation for inputting a signal to the control means 17. It is basically a variable displacement vane pump device including a speed (rotation speed) sensor 18. In such a basic configuration, the vane pump is a conventionally known one, and is housed in the housing 2 to rotate the rotor 6, and the vane 7 that slides in the slit of the rotor 6. A cam ring 5, which is located outside the vane 7 and forms a pump chamber with the rotor 6, vanes 7 and the like, side plates 3 and 4 on the side surfaces of the rotor 6, vanes 7, and cam ring 5, which contribute to the formation of the pump chamber. The basic configuration is that the hydraulic pump is composed of a plurality of sets of suction ports 41, 41 'and discharge ports 31, 31' provided on the side plates 3, 4, and in addition to these, the second suction port 41 'is provided near the circumferential ends of the side plates 3 and 4 and the cam ring 5, and further has a pressure chamber 27 connected to the discharge ports 31 and 31'. A flow rate control valve 26 is provided so as to be connected to the pressure chamber 27, and a bypass passage 29 is provided for bypassing excess discharge oil from the flow rate control valve 26 to the suction side. A suction chamber 28 connected to the suction ports 41 and 41 ′ is provided downstream of 29.

The pressure sensing type switching valve 1 has a sub-cylinder 13 in a switching valve housing 12, and a sub-cylinder chamber 133 formed in the sub-cylinder 13 has a spool 11 and a spring 15 built therein. In addition to these, a cylinder chamber 122 is provided between the switching valve housing 12 and the sub-cylinder 13, and the pressure chamber 27 is provided on one head side of the spool 11. Is provided with a switching valve pressure chamber 14 communicating with the pressure introducing passage 21 and the hydraulic oil flow port 132, and a spring 15 for giving a spring reaction force to the spool 11 is provided on the other head side. It has been configured. It should be noted that, of the land parts 111, 111 ′ provided near the head of the spool 11, the land part 111 provided on the side facing the switching valve pressure chamber 14 has a land part having the above-mentioned thickness. It is configured to have a value sufficient to block the opening of the hydraulic oil flow port 132. That is, the land portion 111 is configured to overlap the hydraulic oil flow port 132. The solenoid valve 16 provided in the middle of the suction side passage 22 includes a spool 161 for opening the suction side passage 22 and a solenoid for opening and closing the spool 161.

In addition to these configurations, the side plate 3 on the side having the discharge ports 31 and 31 'is provided with a discharge passage 33 continuously from the second discharge port 31'. Further, the discharge passage 33 is provided so as to extend toward the center line direction of the rotation shaft, and the final end thereof is provided so as to open in a circular shape around the center line. Further, a disc-shaped sub-plate 8 is provided in contact with the side plate 3, and a plurality of sub-plates 8 are continuously provided in the opening of the discharge passage 33 as shown in FIG. A structure is provided in which a discharge port 81 composed of an opening is provided. A guide 82 is provided near the center of the sub-plate 8, and the guide 82 is provided with a disc-shaped valve 9 for opening and closing the discharge port 81 provided in the sub-plate 8. ing. The valve 9 is provided with a spring 99 that constantly acts to close the discharge port 81, and the spring 99 and the valve 9 form a check valve 32.

The operating state of the first embodiment having the above configuration will be described. When the vane pump starts operating, for example, in FIG. 1, the hydraulic oil sucked from the suction passage is guided to the suction chamber 28 via the bypass passage 29. Part of the hydraulic oil introduced to the suction chamber 28 is sucked from the first suction port 41, pressurized in the pump chamber, and discharged from the first discharge port 31 to the pressure chamber 27. After that, the flow rate is controlled by the flow rate control valve 26, and the flow rate is sent to a power assist unit (not shown) of the power steering apparatus.

By the way, in the present embodiment, when the rotational speed is low, the control means 17 is activated by a signal from the rotational speed sensor 18 and sends a control signal to the solenoid valve 16. The solenoid valve 16 operates based on this control signal, and as shown in FIG. 1, the spool 161 switches so as to close the suction side passage 22. As a result, when the rotational speed is low, the communication state between the second discharge port 31 'and the second suction port 41' is always cut off. Therefore, the discharge oil from the second discharge port 31 ′ is sent out from the valve 9 to the pressure chamber 27 through the discharge passage 33 and the discharge port 81 regardless of the load pressure of the power assist unit. That is, the condition (a) or (b) in Table 1 is satisfied.

Next, when the rotation speed becomes high, the control means 17 receives the signal from the rotation speed sensor 18 and drives the solenoid valve 16 to switch the spool 161 to the state shown in FIG. Take control. As a result, the suction side passage 22 is opened, and the pressure sensing type switching valve 1 and the suction chamber 28 are in communication with each other. Under such a circumstance, when the load pressure of the power assist portion changes, the spool 11 in the pressure sensing type switching valve 1 performs the switching operation according to the change of the load pressure, that is, the change of the load pressure of the pressure chamber 27. Do. These will be described below. When the power assist unit is not performing steering force assistance (power assist), the hydraulic pressure (load pressure) of the power assist unit is low and the load pressure of the pressure chamber 27 is also low. .. As a result, since the pressure introduced from the pressure introducing passage 21 is also low, the pressure in the switching valve pressure chamber 14 in the pressure sensing type switching valve 1 is also low, and the spool 11 is pushed to the right by the action of the spring force of the spring 15, It is placed in the state shown by the solid line in FIG. Therefore, the communication passage 23 communicating with the second discharge port 31 ′ and the suction-side passage 22 are communicated with each other via the cylinder chamber 122, the hydraulic oil flow port 132, the sub-cylinder chamber 133 and the like in the pressure sensing type switching valve 1. Become. As a result, the discharge oil delivered from the second discharge port 31 'is guided to the second suction port 41' via the above-mentioned paths. That is, in the second pump chamber formed by the second discharge port 31 'and the second suction port 41', the working oil circulates, and the condition (C) in Table 1 is achieved.

On the other hand, when the power assist unit starts steering force assistance, the load pressure rises and the pressure in the pressure chamber 27 rises. As a result, the pressure in the switching valve pressure chamber 14 propagated from the pressure chamber 27 via the pressure inlet passage 21, the cylinder chamber 122, the hydraulic oil flow port 132 provided in the sub-cylinder 13, and the like also rises. As a result, the spool 11 housed in the sub-cylinder 13 moves to the left against the spring force of the spring 15 and reaches the position shown by the chain double-dashed line in FIG. As a result, between the communication passage 23 connected to the second discharge port 31 ′ and the suction side passage 22 connected to the second suction port 41 ′, the land portion 111 of the spool 11 provided in the sub cylinder 13 is provided. Will be shut off. Therefore, the discharge oil discharged from the second discharge port 31 ′ is guided to the discharge port 81 of the sub-plate 8 through the discharge passage 33 as shown by the solid arrow in FIG. 2, and the check valve 32 is opened here. It flows into the pressure chamber 27. This increases the discharge capacity of the vane pump, which contributes to assisting the steering force of the power assist unit. That is, the condition (2) in Table 1 is achieved.

Next, a second embodiment will be described with reference to FIGS. 3 and 4. The configuration of this embodiment is also basically the same as that of the first embodiment. A slight difference is that, instead of the solenoid valve 16 used in the first embodiment, the rotation speed sensitive valve 20 connects the pressure sensing type switching valve 1 and the second discharge port 31 ′ with a communication passage 23. It was installed in the middle part of the. The rotation speed sensitive valve 20 is composed of a spool 201, a spring 215 and the like. A rotation speed sensitive throttle 39 is provided between the first discharge port 31 and the pressure chamber 27, and a spring 215 in the rotation speed sensitive valve 20 is housed downstream of the rotation speed sensitive throttle 39. And a chamber on the side opposite to the side on which the spring 215 of the rotation speed sensing valve 20 is provided and the upstream side of the rotation speed sensing throttle 39. Are configured to communicate with each other. By adopting such a configuration, in the present embodiment, when the pump rotation speed (engine rotation speed) is low, the pump discharge flow rate is small, so the differential pressure across the rotation speed sensitive diaphragm 39 is also small, and therefore the rotation speed perception is small. As shown in FIG. 3, the spool 201 of the valve 20 operates so that the land portion 211 closes the communication passage 23 by the action of the spring force of the spring 215. As a result, the communication passage 23 and the suction-side passage 22 are shut off, and the discharge oil discharged from the second discharge port 31 ′ is always delivered to the pressure chamber 27 via the discharge passage 33 and the check valve 32. The Rukoto. That is, the condition (a) or (b) in Table 1 is satisfied. On the other hand, when the pump rotational speed increases, the differential pressure across the rotational speed sensitive throttle 39 increases, and the position of the spool 201 in the rotational speed sensitive valve 20 becomes the state shown in FIG. Therefore, in such a state of the rotation speed sensitive valve 20, the communication passage 23 is in an open state. Under such a circumstance, when the load pressure of the power assist portion is low, the pressure of the pressure chamber 27 is also low, so that the spool 11 of the pressure sensing type switching valve 1 is in the position shown by the solid line in FIG. Therefore, the communication passage 23 and the suction-side passage 22 are in communication with each other, and the discharge oil discharged from the second discharge port 31 'is guided to the second suction port 41'. Here, in the second pump chamber, The discharged oil (operating oil) circulates as indicated by the broken line arrow in FIG. That is, the condition (C) in Table 1 is achieved.

Next, when the power assist portion starts steering force assistance, the load pressure of the pressure chamber 27 rises, and the spool 11 of the pressure sensing type switching valve 1 accordingly moves to the position shown by the chain double-dashed line in FIG. Switch to. As a result, the communication state between the communication passage 23 and the suction-side passage 22 is blocked. Therefore, the discharge oil discharged from the second discharge port 31 'is sent to the pressure chamber 27 via the discharge passage 33, the check valve 32, etc., and then contributes to the steering force assist in the power assist portion. That is, the condition (2) in Table 1 is achieved.

The third embodiment will be described with reference to FIG. The configuration of this embodiment is basically the same as that of the first embodiment. The difference is that instead of the solenoid valve 16 provided in the first embodiment, a cam mechanism 19 for directly controlling the spool 11 in the pressure sensing type switching valve 1 and a cam mechanism 19 for driving the cam mechanism 19 are controlled. That is, the stepping motor 191 is provided. That is, in FIG. 5, a cam mechanism 19 is provided in contact with one end of the spool 11 in the pressure sensing type switching valve 1, and a stepping motor 191 that transmits a driving force to the cam mechanism 19 is mechanically connected to the stepping motor. A control means 17 for controlling the operation of 191 is provided, and a rotation speed sensor 18 for inputting a rotation speed signal to the control means 17 is provided.

With this configuration, when the rotation speed is determined to be low by the signal from the rotation speed sensor 18, the stepping motor 191 is driven by the signal from the control means 17, The cam mechanism 19 is operated to the state shown by the chain double-dashed line in FIG. As a result, the spool 11 comes to the position shown by the chain double-dashed line, and the land portion 111 of the spool 11 closes the hydraulic oil flow port 132 provided in the sub-cylinder 13. As a result, the communication state between the communication passage 23 and the suction side passage 22 is forcibly cut off. As a result, the discharge oil discharged from the second discharge port 31 ′ is sent from the valve 9 to the pressure chamber 27 via the discharge passage 33 and the discharge port 81. That is, the condition (a) or (b) in Table 1 is satisfied.

On the other hand, when it is determined that the rotation speed is high, the stepping motor 191 operates based on the signal from the control means 17 to operate the cam mechanism 19 to the position shown by the solid line in FIG. Under such a circumstance, when the load pressure of the power assist unit is low, the pressure in the pressure chamber 27 is also low, and the switching valve pressure in the pressure sensing type switching valve 1 introduced through the pressure introducing passage 21. The pressure in the chamber 14 is also kept low. As a result, the spool 11 is pushed to the right by the action of the spring force of the spring 15, and is placed at the position shown by the solid line in FIG. Therefore, the communication passage 23 and the suction-side passage 22 are in communication with each other via the cylinder chamber 122, the hydraulic oil flow port 132, the sub-cylinder chamber 133, and the discharge oil discharged from the second discharge port 31 'is As indicated by the broken line arrow 5 in FIG. 5, the fluid circulates to the second suction port 41 ′. That is, the condition (C) in Table 1 is achieved. Next, when the power assist unit starts steering force assistance and the load pressure rises, the load pressure in the pressure chamber 27 also rises, and the pressure in the switching valve pressure chamber 14 communicating with the pressure introducing passage 21 also rises. To do. As a result, the spool 11 moves to the left against the spring reaction force of the spring 15 and reaches the position shown by the chain double-dashed line in FIG. Therefore, the land portion 111 of the spool 11 closes the hydraulic oil circulation port 132, and the communication state between the communication passage 23 and the suction side passage 22 is cut off. Therefore, the discharge oil discharged from the second discharge port 31 ′ is delivered from the valve 9 to the pressure chamber 27 via the discharge passage 33 and the discharge port 81, and thereafter contributes to assisting the steering force in the power assist unit. That is, the condition (d) in Table 1 is achieved. In the above-described embodiment, the switching control is performed by using the rotation speed and the pressure as parameters, but since the engine rotation speed and the vehicle speed generally have a correspondence relationship, the vehicle speed is controlled by the parameter instead of the rotation speed. You may

[0023]

[Effect of the device]

 According to the present invention, in a vane pump having a plurality of intake ports and discharge ports, when the load pressure of the power assisting device power assist part is low, some of the intake ports and discharge ports are operated with hydraulic oil. In the variable displacement vane pump device having a pressure sensing type switching valve that operates so as to circulate the pump function to stop the pump function and restore the stopped pump function when the load pressure rises. A switching mechanism that operates according to the rotation speed is provided in the middle of various passages that connect between the vane pump and the pressure-sensing switching valve, and the switching mechanism operates when the rotation speed is low. A control means is provided for controlling so as to cut off the connection with the port of the unit, and a rotation speed (revolution speed) sensor for inputting a rotation speed (revolution speed) signal to the control means is provided. When the pump rotation speed is low, all pump chambers are forced to be in the operating state, which is not the case with the conventional one at low rotation speed (low rotation speed). Also, the phenomenon that the power assist amount fluctuates at the same pump rotation speed has been resolved. This eliminates fluctuations in the power assist amount, smoothens the steering force assistance, and improves the steering feel.

[Table 1]

[Brief description of drawings]

FIG. 1 is a vertical sectional view showing the overall configuration of a first embodiment according to the present invention.

FIG. 2 is a vertical cross-sectional view showing the overall configuration of the first embodiment according to the present invention, and is a view showing a state in which an electromagnetic valve is operated.

FIG. 3 is a skeleton structure diagram showing an overall configuration of a second embodiment according to the present invention.

FIG. 4 is a skeleton structure diagram showing an overall configuration of a second embodiment according to the present invention, and is a diagram showing a state in which a rotation speed sensitive valve is operated.

FIG. 5 is a vertical sectional view showing the overall configuration of a third embodiment according to the present invention.

FIG. 6 is a diagram showing a relationship between a pump rotation speed and a discharge flow rate of a variable displacement vane pump device of a switching valve system.

[Explanation of Codes] 1 Pressure sensing type switching valve 11 Spool 111 Land portion 12 Switching valve housing 122 Cylinder chamber 13 Sub-cylinder 132 Hydraulic oil flow port 133 Sub-cylinder chamber 14 Switching valve pressure chamber 15 Spring 16 Electromagnetic valve 161 Spool 17 Control means 18 rotation speed sensor (rotation speed sensor) 19 cam mechanism 191 stepping motor 20 rotation speed sensing valve 201 spool 211 land portion 215 spring 2 housing 21 pressure introduction passage 22 suction side passage 23 communication passage 26 flow control valve 27 pressure chamber 28 suction chamber 29 Bypass passage 3 Side plate 31 First discharge port 31 'Second discharge port 32 Check valve 33 Discharge passage 39 Rotation speed sensitive throttle 4 Side plate 41 First suction port 41' Second suction port 5 Cam ring 6 Rotor 7 Vane 8 Sub-plate 81 Discharge port 82 Guide 9 Valve 99 Spring

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Kazuya Ando 1-1 Asahi-cho, Kariya city, Aichi Toyota Koki Co., Ltd. In the company

Claims (1)

[Scope of utility model registration request] 1. A rotor that is housed in a housing and driven to rotate, a vane that slides in a slit of the rotor, and a cam ring that is outside the vane and forms a pump chamber with the rotor, the vane, and the like. , The above rotor,
A vane, a side plate on the side of the cam ring that contributes to the formation of a pump chamber, a vane pump including a plurality of sets of suction ports and a discharge port provided on the side plate, and a pressure chamber connected to each of the discharge ports. A hydraulic pump device comprising: a flow control valve for bypassing the excess discharge oil to a bypass passage connected to the suction port when the discharge flow rate of the discharge oil (working oil) exceeds a predetermined value. A suction passage that is connected to a suction chamber provided on the port side, has a communication passage that communicates with a specific one of the discharge ports, and has a discharge passage that connects the specific discharge port and the pressure chamber. In addition to having a check valve at the tip of the discharge passage, the check valve operates only to cause discharge oil to flow from the specific discharge port side to the pressure chamber side. In a variable displacement vane pump device comprising a pressure sensing type switching valve that switches so as to cut off the communication state between the communication passage and the suction side passage by the pressure of the pressure chamber, A switching mechanism that operates according to the rotation speed is provided between the specific suction port and the specific discharge port, and the operation of the switching mechanism is shut off between the switching valve and the specific port when the rotation speed is low. A variable displacement vane pump device, characterized in that a control means for controlling so as to provide a rotation speed sensor for inputting a rotation speed signal to the control means is further provided.