JP2017206965A - Pump device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To suppress deterioration of discharge performance and reduce a friction loss by properly adjusting the fluid pressure supplied to back pressure chambers in each of suction sections and discharge sections.SOLUTION: In an oil pump 20 formed as a vane pump, discharge side back pressure ports (first discharge side back pressure ports 27a, 27b), which communicate with back pressure chambers RB in closing sections (first closing section, second closing section) and discharge sections (first discharge section, second discharge section), are connected to an oil passage L2 for a line pressure, and suction side back pressure ports (first suction side back pressure ports 26a, 26b), which communicate with the back pressure chambers RB in suction sections (first suction section, second suction section), are connected to an oil passage L4 for a modulator pressure. In the other words, the line pressure PL discharged from discharge ports 25a, 25b is supplied to the back pressure chambers RB in the discharge sections and the closing sections, and the modulator pressure Pmod, which is generated by reducing the line pressure PL with a modulator valve, is supplied to the back pressure chambers RB in the suction sections.SELECTED DRAWING: Figure 2

Description

  The invention of the present disclosure disclosed in the present specification relates to a pump device.

  Conventionally, this type of pump device includes a cam ring having a cam surface on the inner peripheral surface, a rotor having a plurality of radial vane receiving grooves, and a radially outer side inserted into each vane receiving groove as the rotor rotates. A pump chamber defined by the vane whose tip moves to the cam surface, the cam surface of the cam ring, the outer peripheral surface of the rotor, the vane and the side plate, and the volume of the pump chamber as the rotor rotates. The suction port communicates with the pump chamber in the suction section where the pressure increases, the discharge port communicates with the pump chamber in the discharge section where the volume of the pump chamber decreases as the rotor rotates, and the vane receiving groove on the back pressure side of the vane. In a vane pump having a back pressure chamber formed, a pressure reducing valve that inputs hydraulic pressure (line pressure) discharged from a discharge port through a throttle, reduces the pressure, and then supplies the pressure to the back pressure chamber is provided. It has been proposed (e.g., see Patent Document 1). The pressure reducing valve is configured as a spring-type pressure reducing valve having a valve spool having a pressure receiving surface for receiving line pressure and a return spring for biasing the valve spool in a direction opposite to the pressure receiving direction of the pressure receiving surface. When the rotor pressure is low and the hydraulic pressure acting on the pressure receiving surface is lower than the spring biasing force, the spring biasing force moves the valve spool in the valve opening direction, and the rotor speed is high and acts on the pressure receiving surface. When the hydraulic pressure to overcome the urging force of the spring, the valve spool moves in the closing direction. As a result, the hydraulic pressure supplied to the back pressure chamber can be shut off and the hydraulic pressure supplied to the back pressure chamber can be shut off at the time of high rotation of the rotor where the force that presses the vane against the cam surface only by centrifugal force is applied. It is said that fuel resistance can be improved by reducing dynamic resistance.

  A pump device having a discharge side back pressure port communicating with the back pressure chamber of the discharge section and a suction side back pressure port (suction side back pressure port) communicating with the back pressure chamber of the suction section is also proposed. (For example, refer to Patent Document 2). The discharge-side back pressure port is formed over the entire discharge section, the suction-side back pressure port communicates with the discharge-side back pressure port through the narrow groove, and the low-pressure port formed in the first half area of the suction section; It is divided into a high-pressure port formed in the second half region of the suction section. The hydraulic oil discharged from the discharge port is first guided to the high pressure port and further guided to the discharge side back pressure port via the narrow groove. The hydraulic fluid guided to the high pressure port and the discharge side back pressure port is guided to the back pressure chamber immediately before the end of the suction section and the back pressure chamber of the discharge section, respectively, and presses the vane toward the cam surface. On the other hand, the hydraulic oil in the suction passage connected to the suction port is guided to the low pressure port, and the hydraulic oil guided to the low pressure port is guided to the back pressure chamber in the suction section.

JP 2006-63904 A JP 2014-173449 A

  However, in the former pump device, since the hydraulic oil is uniformly supplied to and discharged from the back pressure chamber in both the suction section and the discharge section, the vane pressing force is excessive in the suction section and the sliding resistance is increased. In the discharge section, the vane pressing force may be insufficient and the discharge capacity may be reduced. In the latter pump device, since the suction passage communicates with the back pressure chamber in the suction section, no back pressure acts on the back pressure chamber in the suction section, and the vane pressing force is insufficient in the suction section when the rotor rotates at a low speed. However, the discharge capacity may be reduced.

  The main purpose of the pump device of the present disclosure is to appropriately adjust the fluid pressure supplied to the back pressure chamber in each of the suction section and the discharge section to suppress a decrease in discharge performance and reduce friction loss. .

  The pump device of the present disclosure employs the following means in order to achieve the above-described main object.

The pump device of the present disclosure includes:
A rotor having a plurality of radially formed slits, a vane movably accommodated in each of the slits, and a cam ring including a cam surface that is disposed so as to surround the rotor and on which a tip of the vane can slide. A pump chamber defined by the rotor, the vane, and the cam ring, the volume of which changes as the rotor rotates, and a suction port that communicates with the pump chamber in a suction section whose volume increases as the rotor rotates, A pump device having a vane pump including a discharge port communicating with the pump chamber in a discharge section whose volume is reduced as the rotor rotates, and a back pressure chamber defined by a base end side of the vane in the slit. Because
A pressure reducing valve that inputs a working fluid that is a first fluid pressure discharged from the discharge port, and outputs the working fluid by reducing the pressure to a second fluid pressure that is a pressure lower than the first fluid pressure;
A suction-side back pressure port that communicates with the back pressure chamber in a suction section and that is supplied with the working fluid of the second fluid pressure output from the pressure reducing valve;
A discharge-side back pressure port that communicates with the back pressure chamber in a discharge section and is supplied with the working fluid of the first fluid pressure discharged from the discharge port;
It is a summary to provide.

  In the pump device of the present disclosure, a vane pump having a rotor, a vane, a cam ring, a pump chamber, and a back pressure chamber, a suction port communicating with the pump chamber in the suction section, a discharge port communicating with the pump chamber in the discharge section, A suction side back pressure port communicating with the back pressure chamber in the suction section and a discharge side back pressure port communicating with the back pressure chamber in the discharge section are provided. In addition, a pressure reducing valve is provided for inputting the working fluid that is the first fluid pressure discharged from the discharge port, reducing the working fluid to a second fluid pressure that is lower than the first fluid pressure, and outputting the reduced pressure. The working fluid with the second fluid pressure output from the valve is supplied to the suction side back pressure port, and the working fluid with the first fluid pressure discharged from the discharge port is supplied to the discharge side back pressure port. As a result, by supplying a high pressure (first fluid pressure) to the back pressure chamber in the discharge section, the centrifugal force acting on the vane is reduced, and at the time of low rotation of the rotor, the vane is sufficiently pressed against the cam surface in the discharge section. It is possible to suppress the discharge performance from being lowered by applying a force. In addition, since a stable low pressure (second fluid pressure) can be supplied from the pressure reducing valve to the back pressure chamber in the suction section, it is possible to suppress excessive pressing force of the vane against the cam surface, and to reduce friction loss. Can be reduced. As a result, in each of the suction section and the discharge section, the fluid pressure supplied to the back pressure chamber can be appropriately adjusted to suppress a decrease in discharge performance and reduce a friction loss.

It is a block diagram which shows the outline of a structure of the hydraulic control apparatus 10 containing the pump apparatus which concerns on embodiment of this indication. 2 is a configuration diagram illustrating an outline of a configuration of an oil pump 20. FIG. It is explanatory drawing which shows the relationship between line pressure PL and engine rotational speed Ne. It is explanatory drawing which shows the relationship between modulator pressure Pmod and engine rotational speed Ne. It is explanatory drawing which shows the relationship between the vane pressing force and engine rotational speed Ne in a confinement area and a discharge area. It is explanatory drawing which shows the relationship between the vane pressing force in an intake area, and engine rotational speed Ne.

  Next, embodiments for carrying out the invention of the present disclosure will be described with reference to the drawings.

  FIG. 1 is a configuration diagram illustrating a schematic configuration of a hydraulic control device 10 including a pump device according to an embodiment of the present disclosure, and FIG. 2 is a configuration diagram illustrating a schematic configuration of an oil pump 20. The hydraulic control device 10 controls, for example, a hydraulic pressure necessary for operation of a torque converter with a lock-up clutch or an automatic transmission included in a power transmission device that transmits power from an engine to drive wheels. The hydraulic oil is configured to be able to be supplied and discharged so as to engage (lock up) and release (lock up release) with respect to the lockup clutch, and a plurality of engagements for switching the shift stage of the automatic transmission The hydraulic fluid can be supplied to and discharged from the elements (clutch and brake).

  As shown in FIG. 1, the hydraulic control device 10 includes an oil pump 20 that draws hydraulic oil from the oil pan 11 through the suction oil passage L1 and discharges it to the line pressure oil passage L2 using power from the engine. The primary regulator valve 12 that adjusts the pressure of the hydraulic oil discharged from the oil pump 20 to the line pressure oil passage L2 to generate the line pressure PL, and the drain pressure drained from the primary regulator valve 12 to the secondary pressure oil passage L3 Is regulated to generate a secondary pressure Psec, a modulator valve 30 for reducing the line pressure PL to supply a substantially constant modulator pressure Pmod to the modulator pressure oil passage L4, and a modulator pressure Pmod to be regulated. Primary regulator valve 12 and secondary regulator valve A linear solenoid SLT that generates a control pressure Pslt for driving 3, a lockup control valve 14 that generates a control pressure Plcl for engaging a lockup clutch from the secondary pressure Psec of the secondary pressure oil passage L3, and torque A lock-up relay valve 15 for switching the path of hydraulic oil supplied to and discharged from the converter T / C, and a control pressure Pslu for driving the lock-up control valve 14 and the lock-up relay valve 15 by regulating the modulator pressure Pmod. A linear solenoid SLU to be generated. In addition, although not shown, the hydraulic control device 10 uses a linear solenoid for supplying and discharging hydraulic oil to and from a hydraulic servo such as a clutch provided in the automatic transmission by using the line pressure PL as an original pressure, and a modulator pressure Pmod as an original pressure. An on / off solenoid for operating the relay valve is also provided.

  The oil pump 20 is configured as a balanced vane pump, and as shown in FIG. 2, a plurality of (ten) slits 21a are radially formed in a radial direction with respect to the rotor 21 and each slit 21a has a diameter. Vane 22 inserted so as to freely reciprocate in the direction, cam ring 23 arranged so as to surround rotor 21 and having cam surface 23a on the inner peripheral surface on which the tip of vane 22 can slide, rotor 21, and cam ring 23, a side plate (not shown) that defines a plurality of pump chambers RP together with the rotor 21, the vanes 22, and the cam ring 23.

  Further, the oil pump 20 is provided in the first and second suction sections where the vane 22 protrudes from the rotor 21 toward the cam surface 23a due to the rotation of the rotor 21 (counterclockwise in the drawing) and the volume of the pump chamber RP increases. First and second suction ports 24a, 24b communicating with the pump chamber RP, and the first and second suction chambers 24a, 24b, and the rotation of the rotor 21 cause the vane 22 to be pushed into the rotor 21 from the cam surface 23a. The first and second discharge ports 25a and 25b communicate with the pump chamber RP in the two discharge sections, respectively. Note that the first suction port 24a and the second suction port 24b, the first discharge port 25a, and the first suction port 25a and the second discharge section, respectively, are provided between the first suction section and the first discharge section. It has the 1st closed section and the 2nd closed section which are not connected to any of the 2nd discharge ports 25b. In the present embodiment, the first and second suction ports 24a and 24b are connected to the suction oil passage L1, and the first and second discharge ports 25a and 25b are connected to the line pressure oil passage L2. ing. Therefore, the oil pump 20 sucks the hydraulic oil from the suction oil passage L1 through the first and second suction ports 24a and 24b, and the line pressure oil passage L2 through the first and second discharge ports 25a and 25b. It is comprised so that it may discharge to. The oil pump 20 is configured such that different hydraulic pressures can be discharged from the first discharge port 25a and the second discharge port 25b, and the line pressure oil passage L2 is connected to the discharge port for discharging high pressure, The secondary pressure oil passage L3 may be connected to a discharge port that discharges low pressure.

  Further, the oil pump 20 has a back pressure chamber RB defined by a space on the base end side of the vane 22 in the slit 21a. The oil pump 20 includes a first suction side back pressure port 26a formed so as to communicate with the back pressure chamber RB in the first suction section, and a back pressure chamber RB in the first closing section and the first discharge section. A first discharge-side back pressure port 27a formed to communicate, a second suction-side back pressure port 26b formed to communicate with the back pressure chamber RB in the second suction section, and a second confinement section And a second discharge-side back pressure port 27b formed so as to communicate with the back pressure chamber RB in the second discharge section. In the present embodiment, the first and second suction side back pressure ports 26a, 26b and the first and second discharge side back pressure ports 27a, 27b are formed in the side plate, and the first suction side back pressure port 26a. Is formed in an arc shape centering on the rotation axis of the rotor 21 so as to cover almost the entire area of the first suction section, and the first discharge-side back pressure port 27a includes the first discharge section in addition to the entire area of the first discharge section. The second suction side back pressure port 26b is rotated so as to cover almost the whole area of the second suction section. The second discharge-side back pressure port 27b is centered on the rotation axis of the rotor 21 so as to cover the second confined section in addition to the almost entire area of the second discharge section. It is formed in an arc shape. A modulator pressure oil passage L4 is connected to the first and second suction side back pressure ports 26a and 26b, and a line pressure oil passage L2 is connected to the first and second discharge side back pressure ports 27a and 27b. Has been. Accordingly, in the first and second suction sections, the pressing force of the vane 22 against the cam surface 23a is assisted by the modulator pressure Pmod supplied to the back pressure chamber RB, and the first and second confinement sections and the first and second suction sections are assisted. In the discharge section, the pressing force of the vane 22 against the cam surface 23a is assisted by the line pressure PL supplied to the back pressure chamber RB.

  The primary regulator valve 12 is a pressure regulating valve that regulates the line pressure PL by the control pressure Pslt from the linear solenoid SLT, the biasing force of the spring, and the feedback pressure. The linear solenoid SLT adjusts the modulator pressure Pmod according to the accelerator opening to generate the control pressure Pslt, and outputs the generated control pressure Pslt to the primary regulator valve 12. FIG. 3 is an explanatory diagram showing the relationship between the line pressure PL and the engine rotational speed Ne. As described above, the oil pump 20 is driven by engine power and configured to pump hydraulic oil from the first and second discharge ports 25a and 25b to the line pressure oil passage L2. Therefore, as shown in the figure, the line pressure PL increases as the engine speed Ne increases, and is held at the predetermined pressure PL * by the primary regulator valve 12 based on the control pressure Pslt from the linear solenoid SLT. Further, the control pressure Pslt from the linear solenoid SLT is also output to the secondary regulator valve 13. The secondary regulator valve 13 is configured as a pressure regulating valve that regulates the secondary pressure Psec by the control pressure Pslt, the drain pressure drained from the primary regulator valve 12, and the feedback pressure.

  The modulator valve 30 is a pressure reducing valve that reduces the line pressure PL to a substantially constant hydraulic pressure by the biasing force of the spring and the feedback pressure. The modulator valve 30 communicates and shuts off the sleeve 32 formed with various ports and the corresponding ports. A spool 34 is provided, and a spring 36 that biases the spool 34 in one direction. As the various ports, the sleeve 32 receives an input port 32a to which the line pressure oil passage L2 is connected, an output port 32b to which the modulator pressure oil passage L4 is connected, and the modulator pressure Pmod as a feedback pressure to receive the pressure of the spool 34. A feedback port 32c that applies a force against the biasing force of the spring 36 against the surface. The modulator valve 30 communicates (opens) the input port 32a and the output port 32b when the feedback pressure is less than the set pressure Pset, which is a hydraulic pressure that overcomes the urging force of the spring 36, and when the feedback pressure is greater than or equal to the set pressure Pset. The communication between the input port 32a and the output port 32b is shut off (closed). FIG. 4 is an explanatory diagram showing the relationship between the modulator pressure Pmod and the engine speed Ne. As shown in the figure, the modulator pressure Pmod increases with the increase of the line pressure PL until the feedback pressure reaches the set pressure Pset, and is held at a substantially constant pressure when the feedback pressure reaches the set pressure Pset.

  FIG. 5 is an explanatory diagram showing the relationship between the vane pressing force and the engine rotational speed Ne in the closed section and the discharge section. The discharge side back pressure ports (the first discharge side back pressure port 27a and the second discharge side back pressure port 27b) are connected to the line pressure oil passage L2, and are closed sections (first closed section, second closed section). Section) and discharge section (first discharge section, second discharge section), the vane 22 is subjected to a pressing force due to centrifugal force according to the rotation of the rotor 21 and a pressing force due to back pressure based on the line pressure PL. To do. For this reason, as shown in FIG. 5, in the closed section and the discharge section, the pressing force (necessary pressing force) necessary to bring the vane 22 into close contact with the cam surface 23a is mainly when the engine speed Ne is low. Covered by the back pressure based on the line pressure PL, and when the engine rotational speed Ne increases, the back pressure and the centrifugal force based on the line pressure PL are covered. As a result, the vane 22 can be brought into close contact with the cam surface 23a with a sufficient pressing force in the discharge section and the closing section immediately before the discharge section, and the discharge performance of the pump can be exhibited.

  FIG. 6 is an explanatory diagram showing the relationship between the vane pressing force and the engine rotational speed Ne in the intake section. The suction side back pressure ports (first suction side back pressure port 26a, second suction side back pressure port 26b) are connected to the modulator pressure oil passage L4, and in the suction section (first suction section, second suction section). The vane 22 is subjected to a pressing force by a centrifugal force according to the rotation of the rotor 21 and a pressing force by a back pressure based on the modulator pressure Pmod. For this reason, as shown in FIG. 6, in the intake section, the pressing force (necessary pressing force) required to bring the vane 22 into close contact with the cam surface 23a is mainly the modulator pressure Pmod when the engine speed Ne is low. If the engine rotational speed Ne is increased, the back pressure based on the modulator pressure Pmod and the centrifugal force are used.

  Here, in the suction section (first suction section, second suction section), it is divided into a closed section (first closed section, second closed section) and a discharge section (first discharge section, second discharge section). On the other hand, since the pressure in the pump chamber RP is low, if the line pressure PL is supplied to the back pressure chamber RB as in the discharge section and the closed section, an excessive pressing force exceeding the required pressing force is applied to the vane 22. The sliding resistance of the vane 22 increases and the driving efficiency of the pump decreases (see the dotted line in FIG. 6). In this embodiment, by supplying the modulator pressure Pmod obtained by reducing the line pressure PL with the modulator valve 30 to the back pressure chamber RB in the suction section, the pressing force acting on the vane 22 can be brought close to the necessary pressing force, and the pump The driving efficiency can be further improved (see the solid line in FIG. 6). The modulator valve 30 that generates the modulator pressure Pmod is configured to open when the feedback pressure is less than the set pressure Pset and to close when the feedback pressure is equal to or higher than the set pressure Pset. For this reason, when the engine rotational speed Ne is low and the discharge pressure from the oil pump 20 driven by the engine power is low, the line pressure oil passage L2 and the modulator pressure oil passage L4 communicate with each other to the vane 22 in the suction section. A pressure equivalent to the line pressure PL at that time acts as a back pressure. As a result, an appropriate pressing force can be applied to the vane 22 in the suction section at the time of low rotation of the rotor where the centrifugal force acting on the vane 22 is small, and the pump discharge performance can be prevented from deteriorating.

  According to the pump device of the present disclosure described above, the oil pump 20 serving as the vane pump includes a closed section (first closed section, second closed section) and a discharge section (first discharge section, second discharge section). The discharge-side back pressure ports (first discharge-side back pressure ports 27a, 27b) communicating with the back pressure chamber RB in the are connected to the line pressure oil passage L2, and the suction section (first suction section, second suction section). The suction-side back pressure ports (first discharge-side back pressure ports 26a, 26b) communicating with the back pressure chamber RB are connected to the modulator pressure oil passage L4. That is, the hydraulic pressure discharged from the discharge ports 25a and 25b is supplied to the back pressure chamber RB in the discharge section and the closed section, and the hydraulic pressure discharged from the discharge ports 25a and 25b to the back pressure chamber RB in the suction section. Is supplied after the pressure is reduced by the modulator valve 30. Accordingly, since a high line pressure PL is supplied to the back pressure chamber RB in the discharge section, the cam surface 23a is applied to the vane 22 in the discharge section when the rotor 21 is rotated at a low speed. It is possible to suppress the discharge performance from being lowered by applying a sufficient pressing force to the nozzle. Further, since a stable low pressure is supplied from the modulator valve 30 to the back pressure chamber RB in the suction section, an excessive pressing force of the vane 22 against the cam surface 23a is suppressed, and friction loss is reduced. be able to.

  Further, according to the pump device of the present disclosure, as a pressure reducing valve for applying a back pressure to the vane 22 in the suction section, the valve is opened when the feedback pressure is lower than the set pressure Pset, and when the feedback pressure is equal to or higher than the set pressure Pset. A modulator valve 30 is used that is configured to close. As a result, an appropriate pressing force can be applied to the vane 22 in the suction section at the time of low rotation of the rotor where the centrifugal force acting on the vane 22 is small, and the pump discharge performance can be prevented from deteriorating.

  Further, according to the pump device of the present disclosure, the pressure reducing valve for applying the back pressure to the vane 22 in the suction section is shared with the modulator valve 30 for operating the primary regulator valve 12 and the secondary regulator valve 13. It is not necessary to provide a dedicated pressure reducing valve only for applying a back pressure to the vane 22 in the suction section, and it is possible to prevent the apparatus from becoming large.

  In the present embodiment, the pressure reducing valve for supplying hydraulic oil to the back pressure chamber RB in the suction section (first suction section, second suction section) is used as the control pressure Pslt for operating the primary regulator valve 12 and the secondary regulator valve 13. Although it is assumed that it is shared with the modulator valve 30 for generating the modulator pressure Pmod that is the original pressure of the pressure, a dedicated pressure reducing valve may be used.

  In the present embodiment, the oil pump 20 is configured as a balanced vane pump. However, the oil pump 20 is not limited to this, and may be configured as an unbalanced vane pump.

  As described above, the pump device of the present disclosure includes the rotor (21) in which a plurality of slits (21a) are radially formed, and the vane (22) slidably accommodated in each of the slits (21a). A cam ring (23) disposed around the rotor (21) and including a cam surface (23a) on which a tip of the vane (22) is slidable; the rotor (21) and the vane (22); The pump chamber (RP) defined by the cam ring (23) and having a volume that changes as the rotor (21) rotates, and the pump chamber (RP) in a suction section in which the volume increases as the rotor (21) rotates. RP) and a discharge port (25a) communicating with the pump chamber (RP) in a discharge section in which the volume decreases as the rotor (21) rotates. 25b) and a back pressure chamber (RB) formed in the slit (21a) on the base end side of the vane (22), the pump device having a vane pump (20), the discharge port (25a 25b), a pressure reducing valve (30) that inputs the working fluid that is the first fluid pressure discharged from the second fluid pressure, and reduces the working fluid to a second fluid pressure that is smaller than the first fluid pressure. A suction-side back pressure port (26a, 26b) that communicates with the back pressure chamber (RB) in the suction section and is supplied with the working fluid of the second fluid pressure output from the pressure reducing valve (30); A discharge-side back pressure port (27a, 27b) that communicates with the back pressure chamber (RB) in a section and is supplied with the working fluid of the first fluid pressure discharged from the discharge port (25a, 25b); It is intended to provide .

  In the pump device of the present disclosure, a vane pump (20) having a rotor (21), a vane (22), a cam ring (23), a pump chamber (RP), and a back pressure chamber (RB) is connected to a pump chamber ( Suction port (24a, 24b) communicating with RP), discharge port (25a, 25b) communicating with pump chamber (RP) in the discharge section, and suction side back pressure communicating with back pressure chamber (RB) in the suction section Ports (26a, 26b) and discharge-side back pressure ports (27a, 27b) communicating with the back pressure chamber (RB) in the discharge section are provided. Further, the working fluid that is the first fluid pressure discharged from the discharge ports (25a, 25b) is input, and the pressure is reduced by outputting the working fluid to the second fluid pressure that is a pressure lower than the first fluid pressure. A first fluid pressure provided from the discharge port (25a, 25b) by supplying the working fluid having the second fluid pressure output from the pressure reducing valve to the suction side back pressure port (26a, 26b). The working fluid is supplied to the discharge-side back pressure ports (27a, 27b). Thus, by supplying a high pressure (first fluid pressure) to the back pressure chamber (RB) in the discharge section, the centrifugal force acting on the vane (22) is reduced, and the vane (22 ) Can be exerted with a sufficient pressing force on the cam surface (23a) to prevent the discharge performance from deteriorating. In addition, since a stable low pressure (second fluid pressure) can be supplied from the pressure reducing valve (30) to the back pressure chamber (RB) in the suction section, the vane (22) is supplied to the cam surface (23a). An excessive pressing force can be suppressed and friction loss can be reduced. As a result, in each of the suction section and the discharge section, it is possible to appropriately adjust the fluid pressure supplied to the back pressure chamber (RB), thereby suppressing a decrease in discharge performance and reducing friction loss.

  In such a pump device of the present disclosure, between the suction section and the discharge section, the suction port (24a, 24b) and the discharge port (25a, 25b) are closed so as not to communicate with the pump chamber (RP). The discharge side back pressure ports (27a, 27b) may be configured to communicate with the back pressure chamber (RB) in the discharge section and the closed section. If it carries out like this, a comparatively big pressing force can be made to act on a vane (22) also in the closed area immediately before a discharge area, and the fall of the discharge performance of a vane pump (20) can be suppressed.

  In the pump device of the present disclosure, the pressure reducing valve (30) feeds back the reduced fluid pressure, and opens when the feedback pressure is lower than the set pressure, and closes when the feedback pressure is equal to or higher than the set pressure. It can also be comprised as follows. Thereby, at the time of the rotor low rotation with a small centrifugal force acting on the vane (22), the feedback pressure becomes less than the set pressure, and the working fluid discharged from the discharge ports (25a, 25b) flows into the back pressure chamber ( RB), the pressing force of the vane (22) against the cam surface (23a) can be assisted, and the fluid pressure can be quickly raised to improve the responsiveness. Of course, at the time of high rotor rotation at which the centrifugal force acting on the vane (22) increases, the feedback pressure becomes equal to or higher than the set pressure, and the fluid pressure of the working fluid discharged from the discharge ports (25a, 25b) is reduced. ), The excessive pressing force of the vane (22) against the cam surface (23a) can be suppressed, and the friction loss can be reduced.

  In this case, the pump device is attached to the automatic transmission, and adjusts the fluid pressure of the working fluid discharged from the discharge ports (25a, 25b) to operate the friction engagement element of the automatic transmission. A regulator valve (12) for generating a line pressure required for the regulator, and the pressure reducing valve (30) is a modulator that is a source pressure of a control pressure for reducing the line pressure and operating the regulator bubble (12) A modulator valve that generates pressure, wherein the first fluid pressure may be the line pressure, and the second fluid pressure may be the modulator pressure. Since the pressure reducing valve (30) is shared with the modulator valve used for the operation of the regulator valve (12), it is not necessary to provide a dedicated pressure reducing valve, and the apparatus can be prevented from being enlarged.

  As mentioned above, although the embodiment of the invention of the present disclosure has been described, the invention of the present disclosure is not limited to such an embodiment and can be implemented in various forms without departing from the gist of the invention of the present disclosure. Of course you can.

  The invention of the present disclosure can be used in the manufacturing industry of pump devices.

  DESCRIPTION OF SYMBOLS 10 Hydraulic control apparatus, 11 Oil pan, 12 Primary regulator valve, 13 Secondary regulator valve, 14 Lockup control valve, 15 Lockup relay valve, 20 Oil pump, 21 Rotor, 21a Slit, 22 Vane, 23 Cam ring, 23a Cam surface 24a First suction port, 24b Second suction port, 25a First discharge port, 25b Second discharge port, 26a First suction side back pressure port, 26b Second suction side back pressure port, 27a First discharge side back pressure Port, 27b Second discharge-side back pressure port, 30 Modulator valve, 32 Sleeve, 32a Input port, 32b Output port, 32c Feedback port, 34 Spool, 36 Spring, RP Pump chamber, RB back pressure chamber, T / C Torque Inverter, SLT, SLU linear solenoid, L1 oil passage for suction, L2 oil passage for line pressure, L3 oil passage for secondary pressure, L4 oil passage for modulator pressure.

Claims (4)

A rotor having a plurality of radially formed slits, a vane movably accommodated in each of the slits, and a cam ring including a cam surface that is disposed so as to surround the rotor and on which a tip of the vane can slide. A pump chamber defined by the rotor, the vane, and the cam ring, the volume of which changes as the rotor rotates, and a suction port that communicates with the pump chamber in a suction section whose volume increases as the rotor rotates, A pump device having a vane pump including a discharge port communicating with the pump chamber in a discharge section whose volume is reduced as the rotor rotates, and a back pressure chamber defined by a base end side of the vane in the slit. Because
A pressure reducing valve that inputs a working fluid that is a first fluid pressure discharged from the discharge port, and outputs the working fluid by reducing the pressure to a second fluid pressure that is a pressure lower than the first fluid pressure;
A suction-side back pressure port that communicates with the back pressure chamber in a suction section and that is supplied with the working fluid of the second fluid pressure output from the pressure reducing valve;
A discharge-side back pressure port that communicates with the back pressure chamber in a discharge section and is supplied with the working fluid of the first fluid pressure discharged from the discharge port;
A pump device comprising: The pump device according to claim 1,
Between the suction section and the discharge section, there is a closed section where neither the suction port nor the discharge port communicates with the pump chamber,
The discharge-side back pressure port is configured to communicate with the back pressure chamber in the discharge section and the closed section. The pump device according to claim 1 or 2,
The pressure reducing valve feeds back the reduced fluid pressure, and opens when the feedback pressure is lower than a set pressure, and closes when the feedback pressure is equal to or higher than the set pressure. The pump device according to claim 3, wherein the pump device is attached to the automatic transmission.
A regulator valve that regulates the fluid pressure of the working fluid discharged from the discharge port to generate a line pressure necessary for the operation of the friction engagement element of the automatic transmission;
The pressure reducing valve is a modulator valve that generates a modulator pressure that is a source pressure of a control pressure for reducing the line pressure and operating the regulator bubble.
The first fluid pressure is the line pressure,
The second fluid pressure is the modulator pressure;
Pump device.

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