WO2015072302A1

WO2015072302A1 - Oil pump device and relief valve

Info

Publication number: WO2015072302A1
Application number: PCT/JP2014/078187
Authority: WO
Inventors: 樋口　賢一; 文彦豊田
Original assignee: アイシン精機株式会社
Priority date: 2013-11-12
Filing date: 2014-10-23
Publication date: 2015-05-21
Also published as: JP6264850B2; JP2015094296A

Abstract

This oil pump device is equipped with a first oil passage, a second oil passage, a relief oil passage, and a relief valve. The relief valve includes a valve body that moves inside a valve housing section so as to switch the second oil passage disposed on a second discharge port side and the first oil passage disposed on a first discharge port side between a communicating state and a non-communicating state and switch the second oil passage and the relief oil passage between a communicating state and a non-communicating state.

Description

Oil pump device and relief valve

The present invention relates to an oil pump device and a relief valve.

2. Description of the Related Art Conventionally, an oil pump device having a relief valve for relieving oil when oil discharged from an oil pump main body has a predetermined oil pressure (discharge pressure) is known. Such an oil pump device is disclosed in, for example, Japanese Patent Application Laid-Open No. 2005-140022.

JP-A-2005-140022 discloses a pump body including a suction port and a pair of discharge ports, a first oil path connected to one discharge port, and a second oil path connected to the other discharge port. A hydraulic control valve (relief valve) that operates in response to hydraulic pressure (discharge pressure), and includes a valve body having a pair of relief oil passages for relieving (returning) oil and a first valve chamber and a second valve chamber An oil supply device (oil pump device) is disclosed. In the hydraulic control valve described in Japanese Patent Laid-Open No. 2005-140022, the valve body moves in accordance with the oil pressure of the oil, so that the oil from the second oil passage is in either the first valve chamber or the second valve chamber. It is comprised so that it may discharge to at least any one of a 1st oil path and one relief oil path via either. Thus, when the oil pressure (discharge pressure) is a predetermined oil pressure, the oil discharge pressure and the discharge amount are reduced by discharging the oil from the second oil passage to the relief oil passage. It is configured to reduce energy (work). Note that the first valve chamber and the second valve chamber of the valve body described in JP-A-2005-140022 are arranged side by side in the direction in which the valve body moves.

JP-A-2005-140022

However, in the oil supply device described in Japanese Patent Application Laid-Open No. 2005-140022, the first valve chamber and the second valve chamber are arranged side by side in the direction in which the valve body moves. My body grows bigger. For this reason, there exists a problem that a hydraulic control valve will enlarge. When the hydraulic control valve is increased in size, the degree of freedom of arrangement of the hydraulic control valve in the oil supply device is reduced, and the oil supply device itself is increased in size.

The present invention has been made to solve the above-described problems, and one object of the present invention is to reduce oil discharge pressure and discharge amount to reduce energy (work) for oil discharge. It is another object of the present invention to provide an oil pump device and a relief valve capable of reducing the size of the relief valve.

In order to achieve the above object, an oil pump device according to a first aspect of the present invention sucks oil from a suction port and feeds oil from a first discharge port and a second discharge port provided independently of each other. An oil pump body that discharges; a first oil passage that is connected to the first discharge port, supplies oil discharged from the first discharge port to the supplied portion; and a second oil passage connected to the second discharge port; A relief oil passage that at least relieves oil discharged from the second oil passage, and a relief valve, the relief valve being connected to the first oil passage, the second oil passage, and the relief oil passage. By forming a single valve chamber in the valve body housing portion in a state of being housed in the valve body housing portion and the valve body housing portion, and moving in the valve body housing portion according to the pressure of the discharged oil, Second discharge Switching between the communication state and non-communication state of the second oil passage on the port side and the first oil passage on the first discharge port side, and switching of the communication state and non-communication state between the second oil passage and the relief oil passage Valve body to perform.

In the oil pump device according to the first aspect of the present invention, as described above, the relief valve is connected to the second oil path on the second discharge port side and the first oil path on the first discharge port side, and is not in communication. By providing a valve body for switching the state and switching between a communication state and a non-communication state between the second oil passage and the relief oil passage, the oil discharge pressure is reduced from the second oil passage and the relief by the valve body of the relief valve. When the discharge pressure is such that the oil passage communicates, the oil discharged to the second oil passage can be sufficiently relieved (returned) through the relief oil passage, so that the oil is discharged from the oil pump body. It is possible to reduce the discharge pressure and discharge amount of the oil. Thereby, energy (work) for oil discharge in the oil pump main body can be reduced. In addition, since the valve body forms a single valve chamber in the valve body housing portion, the length of the relief valve in the longitudinal direction (movement direction) can be increased compared to the case where the valve body forms a plurality of valve chambers. Since it can be made smaller, the relief valve can be made smaller accordingly. Thereby, the degree of freedom of arrangement of the relief valve in the oil pump device can be improved, and the oil pump device can be miniaturized as much as the relief valve is miniaturized. As a result, when the oil pump device is mounted on a vehicle, the mounting property on the vehicle can be improved.

In the oil pump device according to the first aspect, the oil pump body is configured to discharge oil from the first discharge port and the second discharge port provided independently of each other, and the first oil passage Is connected to the first discharge port, and the second oil passage is connected to the second discharge port. Accordingly, since the first oil passage and the second oil passage are connected to different discharge ports, all of the oil discharged from the second discharge port can be used as the oil discharged to the second oil passage. . As a result, by increasing the discharge amount of oil discharged from the second discharge port, the discharge amount of oil discharged from the second oil passage can be controlled to increase accurately.

In the oil pump device according to the first aspect, preferably, in the direction in which the valve body moves, the length from the tip of the valve body to the single valve chamber is equal to or less than the length of the valve chamber. If comprised in this way, since the length from the front-end | tip part of a valve body to a single valve chamber can be made small enough, a relief valve can be reduced more in size. On the other hand, since the length of the valve chamber is larger than the length from the tip of the valve body to the single valve chamber, the length of the valve body can be secured to some extent. As a result, it is possible to suppress an increase in the flow resistance of oil in the valve chamber due to an excessively small volume of the valve chamber. Thereby, since it can suppress that the discharge pressure for discharging oil through a valve chamber becomes large, it can control that energy (work) for oil discharge in an oil pump main part becomes large. it can.

In this case, preferably, the valve body is formed on the opposite side of the first valve portion formed on the distal end side of the valve body and the distal end portion of the valve body with the valve chamber sandwiched with respect to the first valve portion. And a constricted portion formed at a position corresponding to the valve chamber between the first valve portion and the second valve portion and having an outer diameter smaller than that of the first valve portion and the second valve portion. And the length of the first valve portion is equal to or less than the length of the constricted portion in the direction in which the valve body moves. If comprised in this way, a single valve chamber can be easily formed by the constriction part between a 1st valve part and a 2nd valve part. Moreover, since the length of the 1st valve part can fully be made small by making the length of a 1st valve part below the length of a constriction part, a relief valve can be reduced more in size. Moreover, since the length of the constricted portion is larger than the length of the first valve portion, the length of the constricted portion can be ensured to some extent. As a result, it is possible to suppress an increase in oil flow resistance in the valve chamber due to an excessively small volume of the valve chamber corresponding to the constricted portion.

In the configuration in which the valve body includes the first valve portion, the second valve portion, and the constricted portion, the valve body preferably does not communicate the second oil passage and the relief oil passage by the second valve portion in the low speed region. In addition, the first oil passage and the second oil passage are in communication with each other via the valve chamber. If comprised in this way, since the oil from a 2nd oil path is supplied to a 1st oil path in a low speed area, without being discharged to a relief oil path, the discharge pressure of the oil of a 1st oil path is enlarged. Can do. Thereby, the discharge pressure required for moving the valve body can be easily secured from the stage where the driving force applied to the oil pump main body is small.

In the configuration in which the first oil passage and the second oil passage are in communication with each other in the low speed region, the first oil passage is preferably connected to the first oil passage, and is connected to the second oil passage through the valve chamber in the low speed region. The valve body is further configured to bring the first oil passage and the second oil passage into communication with each other via the valve chamber and the connection oil passage in a low speed range. If comprised in this way, a 1st oil path and a 2nd oil path will be connected not only via a valve chamber but via a connection oil path, so that the second oil path is connected to the first oil path via only the valve chamber. Unlike the case in which the oil is connected, the oil discharged from the first discharge port via the first oil passage and the oil discharged from the second discharge port via the second oil passage join the first oil passage Interference at each point can be suppressed. Thereby, it can suppress that the energy (work) for the oil discharge in an oil pump main body resulting from interfering increases.

In the configuration including the connection oil passage, preferably, the second oil passage is disposed between the connection oil passage and the relief oil passage in the direction in which the valve body moves. If comprised in this way, according to a valve body moving to a moving direction, the communication state of a 2nd oil path and a connection oil path and the communication state of a 2nd oil path and a relief oil path are switched easily. be able to.

In the configuration including the connection oil passage, preferably, the length of the first valve portion in the moving direction of the valve body is configured to be smaller than the inner diameter of the connection oil passage hole of the connection oil passage. . If comprised in this way, since it can suppress that the state in which a 1st valve part closes a connection oil path hole part arises, a 1st oil path and a 2nd oil path are ensured via a connection oil path. Can communicate.

In the configuration in which the valve body includes the first valve portion, the second valve portion, and the constricted portion, the valve body is preferably configured such that the first oil passage and the second oil passage are provided by the first valve portion in the first medium speed range. And the second oil passage and the relief oil passage are in communication with each other via the valve chamber. If comprised in this way, since all the oil from a 2nd oil path is discharged to a relief oil path in a 1st medium speed area, the discharge amount of the oil to be relieved is enlarged and oil is fully relieved Can do. Thereby, the energy (work) for oil discharge in the oil pump body can be sufficiently reduced.

In the configuration in which the second oil passage and the relief oil passage are in communication with each other in the first medium speed region, preferably, the valve body is in a second medium speed region that is a speed region larger than the first medium speed region. The first valve portion is configured to bring the second oil passage and the relief oil passage into a non-communication state and to bring the first oil passage and the second oil passage into a communication state. Here, at a speed range higher than the first medium speed range, it is necessary to supply a large amount of oil to the supplied portion in order to cool the supplied portion. Accordingly, in the second medium speed range, the second oil passage and the relief oil passage are brought into a non-communication state, and the first oil passage and the second oil passage are brought into a communication state, whereby oil from the second oil passage is obtained. Is supplied to the first oil passage without being discharged to the relief oil passage, so that the amount of oil discharged from the first oil passage can be increased. Thereby, a large amount of oil can be supplied to the supplied part through the first oil passage.

In the configuration in which the valve body includes the first valve portion, the second valve portion, and the constricted portion, it is preferable that the valve body communicates all of the first oil passage, the second oil passage, and the relief oil passage in a high speed range. It is configured to let you. With this configuration, in the high speed range, a part of the oil can be relieved through the relief oil passage while sufficiently supplying the oil to the supplied portion through the first oil passage, so that the oil pump It is possible to reduce energy (work) for oil discharge in the main body, and it is possible to prevent the oil passage from being damaged due to excessive oil pressure being applied to the oil passage.

In the configuration in which the first oil passage, the second oil passage, and the relief oil passage communicate with each other in the high speed region, preferably, the length of the first valve portion in the direction in which the valve body moves is the relief oil passage of the relief oil passage. It is comprised so that it may become smaller than the internal diameter of a use hole part. If comprised in this way, since it can suppress that a 1st valve part becomes large in the direction which a valve body moves, a relief oil path and a 1st oil path will be in a communication state in a high speed region. It is possible to suppress an increase in the required oil discharge pressure. Thereby, a part of the oil can be relieved through the relief oil passage from a stage where the oil discharge pressure is small, so that the energy (work) for oil discharge in the oil pump body can be reduced at an early stage. At the same time, it is possible to reliably prevent the oil passage from being damaged due to excessive oil pressure being applied to the oil passage.

In the configuration in which the valve body includes the first valve portion, the second valve portion, and the constricted portion, preferably, the outer edge portion of the first valve portion on the valve chamber side and the outer edge portion of the second valve portion on the valve chamber side At least one of them is chamfered. If comprised in this way, it can suppress that the distribution | circulation state of oil changes rapidly by the chamfered outer edge part at the time of switching of the communication state and non-communication state via a valve chamber. In other words, when switching between the communication state and the non-communication state via the valve chamber, it is possible to suppress the oil that has been flowing into the predetermined oil passage from being suddenly blocked, and the oil flows into the predetermined oil passage rapidly. You can suppress starting. Thereby, generation | occurrence | production of an unnecessary vibration (self-excited vibration) etc. can be suppressed in a valve body.

A relief valve according to a second aspect of the present invention is connected to a first discharge port through which oil is discharged from an oil pump main body, and a first oil passage that supplies oil discharged from the first discharge port to a supplied portion. The second oil passage connected to the second discharge port provided independently of the first discharge port and the single relief oil passage for relieving at least the oil discharged from the second oil passage. And a single valve chamber in the valve body housing portion in a state of being housed in the valve body housing portion, and moving in the valve body housing portion according to the pressure of the discharged oil , Switching between communication state and non-communication state between the second oil passage on the second discharge port side and the first oil passage on the first discharge port side, and communication state and non-communication state between the second oil passage and the relief oil passage And a valve body that performs switching.

In the relief valve according to the second aspect of the present invention, as described above, switching between the communication state and the non-communication state of the second oil path on the second discharge port side and the first oil path on the first discharge port side; By providing a valve body that switches between a communication state and a non-communication state between the second oil passage and the relief oil passage, the oil discharge pressure causes the second oil passage and the relief oil passage to communicate with each other by the valve body. In the case of the discharge pressure, the oil discharged to the second oil passage can be sufficiently relieved (returned) through the relief oil passage, so that the discharge pressure and discharge of the oil discharged from the oil pump body The amount can be reduced. Thereby, energy (work) for oil discharge in the oil pump main body can be reduced. In addition, since the valve body forms a single valve chamber in the valve body housing portion, the length of the relief valve in the longitudinal direction (movement direction) can be increased compared to the case where the valve body forms a plurality of valve chambers. Since it can be made smaller, the relief valve can be made smaller accordingly. Thereby, the degree of freedom of arrangement of the relief valve in the oil pump device can be improved, and the oil pump device can be miniaturized as much as the relief valve is miniaturized. As a result, when the oil pump device is mounted on a vehicle, the mounting property on the vehicle can be improved.

In the relief valve according to the second aspect, the first oil path and the second oil path are connected to the first discharge port and the second discharge port, respectively, provided independently of each other in the oil pump body. Accordingly, since the first oil passage and the second oil passage are connected to different discharge ports, all of the oil discharged from the second discharge port can be used as the oil discharged to the second oil passage. . As a result, by increasing the discharge amount of oil discharged from the second discharge port, the discharge amount of oil discharged from the second oil passage can be controlled to increase accurately.

In the relief valve according to the second aspect, preferably, in the direction in which the valve body moves, the length from the tip of the valve body to the single valve chamber is equal to or less than the length of the valve chamber. If comprised in this way, since the length from the front-end | tip part of a valve body to a single valve chamber can be made small enough, a relief valve can be reduced more in size. On the other hand, since the length of the valve chamber is larger than the length from the tip of the valve body to the single valve chamber, the length of the valve body can be secured to some extent. As a result, it is possible to suppress an increase in the flow resistance of oil in the valve chamber due to an excessively small volume of the valve chamber. Thereby, since it can suppress that the discharge pressure for discharging oil through a valve chamber becomes large, it can control that energy (work) for oil discharge in an oil pump main part becomes large. it can.

In this case, preferably, the valve body is formed on the opposite side of the first valve portion formed on the distal end side of the valve body and the distal end portion of the valve body with the valve chamber sandwiched with respect to the first valve portion. And a constricted portion formed at a position corresponding to the valve chamber between the first valve portion and the second valve portion and having an outer diameter smaller than that of the first valve portion and the second valve portion. In the direction in which the valve body moves, the length of the first valve portion is equal to or shorter than the length of the constricted portion. If comprised in this way, a single valve chamber can be easily formed by the constriction part between a 1st valve part and a 2nd valve part. Moreover, since the length of the 1st valve part can fully be made small by making the length of a 1st valve part below the length of a constriction part, a relief valve can be reduced more in size. Moreover, since the length of the constricted portion is larger than the length of the first valve portion, the length of the constricted portion can be ensured to some extent. As a result, it is possible to suppress an increase in oil flow resistance in the valve chamber due to an excessively small volume of the valve chamber corresponding to the constricted portion.

According to the present invention, as described above, an oil pump device capable of reducing the size of the relief valve while reducing the energy (work) for oil discharge by reducing the oil discharge pressure and discharge amount, and The relief valve can be provided.

It is the figure which showed the whole structure of the oil pump apparatus by one Embodiment of this invention. It is the figure which showed typically the structure of the oil pump apparatus by one Embodiment of this invention, and a to-be-supplied part. It is the enlarged view which showed the structure by the side of the main oil path of the valve body accommodating part in the oil pump apparatus by one Embodiment of this invention. It is the figure which showed typically the operation | movement (position) of the valve body in the low speed area of the oil pump apparatus by one Embodiment of this invention. It is the figure which showed typically operation | movement (position) of the valve body in the 1st medium speed area (initial stage) of the oil pump apparatus by one Embodiment of this invention. It is the figure which showed typically the operation | movement (position) of the valve body in the 1st medium speed area of the oil pump apparatus by one Embodiment of this invention. It is the figure which showed typically operation | movement (position) of the valve body in the 2nd medium speed area (initial stage) of the oil pump apparatus by one Embodiment of this invention. It is the figure which showed typically the operation | movement (position) of the valve body in the 2nd medium speed area of the oil pump apparatus by one Embodiment of this invention. It is the figure which showed typically the operation | movement (position) of the valve body in the high-speed area of the oil pump apparatus by one Embodiment of this invention. It is the figure which showed the relationship between the discharge pressure (discharge amount) of the oil in the oil pump apparatus by one Embodiment of this invention, and an engine speed.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.

First, the configuration of an oil pump device 100 according to an embodiment of the present invention will be described with reference to FIGS. In FIG. 1, reference numerals are assigned to main components constituting the oil pump device 100, and in FIGS. 2 to 9, reference numerals are assigned to simplified configurations (structures) around the relief valve 20. Is attached.

As shown in FIG. 2, an oil pump device 100 according to an embodiment of the present invention is mounted on an automobile (not shown) including an engine (internal combustion engine) 90, and oil (engine oil) in an oil pan 91 is installed. ) 1 is supplied to a supply portion (sliding portion) 92 that requires lubrication and cooling, such as the piston 92a and the crankshaft 92b. Specifically, the oil pump device 100 includes an oil pump body 10 that sucks and discharges the oil 1.

As shown in FIG. 1, the oil pump body 10 is configured as a trochoid oil pump that is an inscribed gear type, and includes an aluminum alloy casing 2 and an inner rotor 11 that is rotatably provided in the casing 2. And an outer rotor 12 and a cover (not shown) made of an aluminum alloy that covers the casing 2. The inner rotor 11 is configured to transmit the driving force of the engine 90 (see FIG. 2). When the inner rotor 11 rotates in the arrow P direction, the outer rotor 12 also rotates in the same direction. At this time, the volume of the space S formed between the teeth 11a (mountains) and the teeth 12a (valleys) of both rotors is increased or decreased as the rotors rotate. Therefore, the oil 1 is sucked into the oil pump body 10 as the pressure in the space S decreases with the volume change from the minimum value to the maximum value of the space S, and the volume change from the maximum value to the minimum value of the space S. Accordingly, the oil 1 sucked as the pressure in the space S increases is discharged out of the oil pump main body 10. Note that the amount of oil 1 discharged by the oil pump body 10 increases in proportion to the rotational speed (rotational speed) of the engine 90.

As shown in FIGS. 1 and 2, in the oil pump main body 10, a suction port 3 for sucking oil 1, a main discharge port 4 and a sub discharge port 5 for discharging the oil 1, and a main discharge port 4, a main oil passage 6 connected to 4, a sub oil passage 7 connected to the sub discharge port 5, and a relief oil passage 8 are provided. The oil pump main body 10 sucks the oil 1 from the oil pan 91 (see FIG. 2) through the suction port 3a and the suction port 3 and generates a predetermined hydraulic pressure and the main discharge port 4 and the sub discharge port. 5 has the function of discharging. Then, the oil 1 is pumped toward an oil filter (not shown) through the discharge port 6a of the main oil passage 6. The oil 1 that has passed through the oil filter and from which relatively small foreign matter has been removed is supplied to the supplied portion 92 in the engine 90. The main discharge port 4 and the sub discharge port 5 are examples of the “first discharge port” and the “second discharge port” in the present invention, respectively. The main oil passage 6 and the sub oil passage 7 are examples of the “first oil passage” and the “second oil passage” in the present invention, respectively.

In addition, the flow path (oil path) of the oil 1 including the suction port 3, the main discharge port 4, the sub discharge port 5, the main oil path 6, the sub oil path 7, and the relief oil path 8 in the oil pump main body 10 is Each of the casings 2 (see FIG. 1) is formed with a predetermined flow path shape with a cover (not shown) attached thereto.

Further, as shown in FIG. 1, the main discharge port 4 and the main oil passage 6 are formed on the Y1 side of the oil pump main body 10, and the sub discharge port 5 and the sub oil passage 7 are abbreviations of the oil pump main body 10. The relief oil passage 8 is formed in the center, and is formed on the Y2 side of the oil pump main body 10. The main discharge port 4 and the sub discharge port 5 are provided independently of each other with a partition wall 10a formed on the casing 2 and a cover (not shown). Similarly, the main oil passage 6 and the sub oil passage 7 are provided independently of each other across the partition wall 10a. Thus, the hydraulic pressure generated in the oil pump main body 10 is configured to be generated individually in each of the main discharge port 4 and the main oil passage 6 and the sub discharge port 5 and the sub oil passage 7. The oil pump device 100 has an internal relief structure in which the oil 1 flowing through the relief oil passage 8 is returned to the suction port 3.

Further, the volume of the main discharge port 4 is formed to be larger than the volume of the sub discharge port 5, and the volume of the main oil passage 6 is formed to be larger than the volume of the sub oil passage 7. ing. As a result, the volume of the main region Q1 constituted by the main discharge port 4 and the main oil passage 6 is configured to be larger than the volume of the sub region Q2 constituted by the sub discharge port 5 and the sub oil passage 7. Has been.

Also, the oil pump body 10 is provided with a relief valve 20 that operates when the pressure of the oil 1 exceeds a specified value. The relief valve 20 is disposed at a portion connecting the main oil passage 6 and the sub oil passage 7 and the relief oil passage 8, and the relief valve 20 of the relief oil passage 8 according to the pressure of the main oil passage 6 (pressure of the oil 1). It has a function to open and close. In addition, the relief valve 20 has a function of preventing the oil pressure from rising more than necessary when the engine 90 is rotating at high speed (high speed range) and causing oil leakage or breakage in the oil passage. Furthermore, when the engine 90 is started at a low temperature, the oil pressure increases significantly as the viscosity of the oil 1 increases, and the resistance of the oil pump body 10 may increase, causing damage. The relief valve 20 also has a function of preventing damage to the oil pump main body 10 by operating in such a case and maintaining the hydraulic pressure within a specified value.

As shown in FIGS. 1 and 2, the relief valve 20 urges the valve body 21, the valve body housing portion 22 that houses the valve body 21, and the valve body 21 toward the main oil passage 6 (Y1 side). A coiled spring 23. The valve body accommodating part 22 is formed in an axial hole shape along the central axis A extending in the Y direction, and the valve body 21 is configured to be movable (slidable) in the axial direction (Y direction) inside. .

Further, the main oil passage 6 is disposed on the Y1 side of the valve body housing portion 22, and the relief oil passage 8 is disposed on the Y2 side of the valve body housing portion 22. Further, the valve body accommodating portion 22 is formed so as to extend in the Y direction so as to connect the main oil passage 6, the sub oil passage 7 and the relief oil passage 8.

In addition, the periphery of the opening end on the Y1 side of the valve body housing portion 22 is formed such that the inner diameter of the valve body housing portion 22 gradually decreases toward the Y1 side. As a result, Y1 of the valve body housing portion 22 is formed. An inclined portion 22a is formed around the opening end on the side. In addition, the valve body accommodating portion 22 is formed with a hydraulic pressure introduction hole portion 22b at the opening end on the Y1 side, and in order from the main oil passage 6 side (Y1 side) to the relief oil passage 8 (Y2 side). A connecting oil passage hole 22c, a sub oil passage hole 22d, and a pair of relief oil passage holes 22e (see FIG. 1) are formed.

The hydraulic introduction hole 22 b is connected to the main oil passage 6. The connection oil passage hole 22c is formed on the X2 side of the valve body housing portion 22, and is connected to a connection oil passage 6b formed so as to extend to the Y1 side after extending to the X2 side. Further, the connection oil passage 6b is connected to the main oil passage 6 at an end portion on the Y1 side. At this time, the connection oil passage 6b is connected to the main oil passage 6 so as to go around from the X2 side (bypassing to the X2 side).

The sub oil passage hole 22 d is connected to the sub oil passage 7. The pair of relief oil passage holes 22e are formed on the X1 side and the X2 side of the valve body housing portion 22, respectively, and are both connected to the relief oil passage 8. In FIG. 2 and subsequent figures, only one of the pair of relief oil passage holes 22e is shown in a simplified manner.

As shown in FIG. 3, in the Y direction in which the valve body 21 moves, the distance L1 between the hydraulic pressure introduction hole 22b and the relief oil passage hole 22e is equal to the sub oil passage hole 22d and the relief oil. It is formed to be larger than the sum (L2 + D3) of the distance L2 between the passage hole 22e and the inner diameter D3 of the sub oil passage hole 22d (sub oil passage 7). That is, the hydraulic oil introduction hole 22b is formed closer to the main oil passage 6 (Y1 side) than the sub oil passage hole 22d, so that the sub oil passage 7 is in the Y direction in which the valve body 21 moves. It is arranged between the connecting oil passage 6 b and the relief oil passage 8. The distance L2 between the sub oil passage hole 22d and the relief oil passage hole 22e is formed to be smaller than the inner diameter D3 of the sub oil passage 7.

Here, in the present embodiment, the valve body 21 is switched between a communication state and a non-communication state with the sub oil passage 7 with the main oil passage 6, and a communication state and a non-communication between the sub oil passage 7 and the relief oil passage 8. It has a function of switching the state. Specifically, the valve body 21 includes

valve portions

21a and 21b formed on the Y1 side and the Y2 side, respectively, and a constricted portion 21c formed between the valve portion 21a and the valve portion 21b and extending in the Y direction. Have. The

valve portions

21a and 21b perform switching between a communication state and a non-communication state with the sub oil passage 7 with the main oil passage 6, and switching between a communication state and a non-communication state between the sub oil passage 7 and the relief oil passage 8. Provided to do.

The valve portion 21a on the Y1 side is formed in a disk shape while being formed in a region from the tip portion 21d of the valve body 21 to the constricted portion 21c. Further, the valve portion 21a is configured to abut on the inclined portion 22a of the valve body housing portion 22 in an initial position (a state where no hydraulic pressure is applied). Moreover, the valve part 21b is formed in the Y2 side on the opposite side to the front-end | tip part 21d through the constriction part 21c with respect to the valve part 21a. The valve portion 21b is formed in a bottomed cylindrical shape having a bottom surface on the Y1 side, and is configured so that the Y1 side of the spring 23 is inserted and fixed therein. The

valve portions

21a and 21b are examples of the “first valve portion” and the “second valve portion” in the present invention, respectively.

The

valve portions

21a and 21b both have substantially the same outer diameter D1, and the outer diameter D1 is formed to be larger than the inner diameter of the valve body housing portion 22 by a minute amount. Thereby, the outer peripheral surfaces of the

valve portions

21 a and 21 b are configured to slide smoothly with respect to the inner peripheral surface of the valve element housing portion 22. Further, the outer diameter D1 of the

valve portions

21a and 21b is configured to be larger than the outer diameter D2 of the constricted portion 21c. As a result, the

valve portions

21a and 21b, the constricted portion 21c, and the valve body accommodating portion 22 are configured. A single valve chamber 24 is formed in a region corresponding to the constricted portion 21c surrounded by the inner peripheral surface. The valve chamber 24 is formed in a ring shape around the constricted portion 21c.

In the valve portion 21a, the outer edge portion 121a on the valve chamber 24 side (Y2 side) is chamfered circumferentially, and in the valve portion 21b, the outer edge portion 121b on the valve chamber 24 side (Y1 side) is circumferentially shaped. It is chamfered.

In this embodiment, the length L3 of the valve portion 21a is formed to be equal to or shorter than the length L4 of the valve chamber 24 (neck portion 21c) in the Y direction in which the valve body 21 moves. The length L3 of the valve portion 21a is preferably about one third or less of the length L4 of the valve chamber 24. Further, the length L3 of the valve portion 21a is configured to be smaller than the inner diameter D3 of the sub oil passage hole 22d, the inner diameter D4 of the connection oil passage hole 22c, and the inner diameter D5 of the relief oil passage hole 22e. Has been. Accordingly, the valve portion 21a is configured not to cover all of the connecting oil passage hole portion 22c, the sub oil passage hole portion 22d, or the relief oil passage hole portion 22e. The length L4 of the valve chamber 24 is configured to be larger than the inner diameter D3 of the sub oil passage hole 22d.

Further, the relief valve 20 starts from the initial position on the Y1 side (see FIG. 4) where the valve body 21 abuts against the inclined portion 22a of the valve body housing portion 22 according to the pressure of the oil 1, and the main oil passage 6 and the sub oil It is comprised so that it may move to the position (refer FIG. 9) of the Y2 side in the high speed area which makes the path 7 and the relief oil path 8 a communication state. Here, the valve body 21 is biased to the Y1 side that resists the pressure of the oil 1 by the spring 23, and when the pressure of the oil 1 exceeds a specified value and exceeds the biasing force of the spring 23, the valve body 21 21 is configured to be moved to the Y2 side by receiving the pressure of the oil 1 through the valve portion 21a (see FIGS. 5 to 9).

Next, the switching operation between the communication state and the non-communication state by the movement of the valve body 21 of the oil pump device 100 will be described with reference to FIGS.

(Low speed range)
First, in a low speed range where the engine speed is small, such as immediately after the start of the engine 90, the discharge pressure from the oil pump body 10 is small and the discharge pressure of the oil 1 acting on the valve portion 21a of the valve body 21 as shown in FIG. Is less than the biasing force of the spring 23. At this time, the valve portion 21 a (tip portion 21 d) of the valve body 21 is in contact with the inclined portion 22 a of the valve body housing portion 22, whereby the hydraulic pressure introduction hole portion 22 b is closed by the valve portion 21 a of the valve body 21. ing. Further, the connection oil passage hole 22c and the sub oil passage hole 22d are opened, so that the main oil passage 6 and the sub oil passage 7 are in communication with each other via the valve chamber 24 and the connection oil passage 6b. To be. Further, the relief oil passage hole 22e is closed by the valve portion 21b, whereby the sub oil passage 7 and the relief oil passage 8 are brought into a non-communication state.

As a result, in the low speed range, not only the oil 1 from the main discharge port 4 but also the oil 1 from the sub discharge port 5 passes through the sub oil passage 7, the valve chamber 24 and the connection oil passage 6 b. To be supplied. That is, the discharge amount of the oil 1 discharged to the supplied portion 92 is the total amount of the oil 1 from the main discharge port 4 and the oil 1 from the sub discharge port 5. Thereby, in the low speed range such as immediately after the engine 90 is started, the amount of oil 1 supplied to the supplied portion 92 can be sufficiently increased, so that the amount of oil 1 in the supplied portion 92 is insufficient. It is possible to suppress. Note that, in the low speed range, as shown in FIG. 10, the discharge amount of the oil 1 increases in proportion to the rotational speed of the engine 90.

(First medium speed range)
In the first medium speed range where the engine speed exceeds N1, the discharge pressure from the oil pump body 10 increases, and the driving force based on the discharge pressure of the oil 1 exceeds the urging force of the spring 23. Thereby, as shown in FIG. 5, the valve body 21 moves to the Y2 side to a position where the driving force of the oil 1 and the biasing force of the spring 23 are balanced. Here, when the valve portion 21a is located on the Y1 side of the Y2 side end portion of the connecting oil passage hole portion 22c (initial stage of the first medium speed range), the hydraulic pressure introduction hole portion 22b, for the connecting oil passage All of the hole 22c, the sub oil passage hole 22d, and the relief oil passage hole 22e are opened. Accordingly, the main oil passage 6 and the sub oil passage 7 are brought into communication with each other via the valve chamber 24 and the connection oil passage 6b, and the sub oil passage 7 and the relief oil passage 8 are connected with each other via the valve chamber 24. Communicated.

As a result, at the initial stage of the first medium speed range, the discharge amount of the oil 1 discharged to the supplied portion 92 is the connection oil of the oil 1 from the main discharge port 4 and the oil 1 from the sub discharge port 5. This is the total amount of oil 1 (α) supplied to the main oil passage 6 via the passage 6b. That is, of the oil 1 from the sub discharge port 5, the discharge amount discharged to the supplied portion 92 is reduced by the amount of oil 1 supplied to the relief oil passage 8.

As shown in FIG. 10, when the engine speed is in the vicinity of N1, the discharge amount of the oil 1 required for the driving force based on the discharge pressure of the oil 1 to exceed the urging force of the spring 23 is determined from the main discharge port 4. The total amount of the oil 1 and the oil 1 from the sub discharge port 5 is required (region indicated by V in FIG. 10). Therefore, the oil pump device 100 according to the present embodiment is configured such that the slopes of the G1-G2 line and the G2-G3 line exceed the required oil amount V in the first medium speed range. On the other hand, in the first medium speed range where the engine speed is higher than N1 and the driving force based on the discharge pressure of the oil 1 exceeds the urging force of the spring 23, the oil 1 from the main discharge port 4 and the sub discharge port 5 The amount of oil 1 discharged may be smaller than the total amount of oil 1 from Thereby, the discharge amount discharged to the supplied part 92 is reduced by the amount of the oil 1 supplied to the relief oil passage 8. The energy (work) and discharge pressure required for the oil 1 when passing through the relief oil passage 8 and returning to the suction port 3 again are the energy and discharge required for the oil 1 when supplied to the supplied portion 92. Less than pressure. Thereby, the discharge pressure of the oil pump main body 10 is also reduced.

Thereafter, when the engine speed exceeds N2 larger than N1, the discharge pressure from the oil pump main body 10 becomes larger, and a part of the valve portion 21a is connected to the Y2 side end of the connecting oil passage hole 22c. When the valve body 21 is moved to the Y2 side (first medium speed range), the main oil passage 6 and the sub oil passage 7 are not communicated with each other by the valve portion 21a as shown in FIG. To be. Further, the sub oil passage hole 22 d and the relief oil passage hole 22 e are opened, and the sub oil passage 7 and the relief oil passage 8 are brought into communication with each other through the valve chamber 24.

As a result, in the first medium speed range, the discharge amount of the oil 1 discharged to the supplied portion 92 is only the oil 1 from the main discharge port 4. That is, the discharge amount discharged to the supplied portion 92 is reduced by the amount of oil 1 from the sub discharge port 5. Thereby, the discharge pressure of the oil 1 is kept low in the first medium speed range, and as a result, the energy (work) for oil discharge in the oil pump body 10 is reduced.

Note that, as shown in FIG. 10, in the first medium speed range, the discharge amount of the oil 1 increases in proportion to the rotational speed of the engine 90. Note that, in the first medium speed range, the increase amount of the discharge amount of the oil 1 corresponding to the rotation speed of the engine 90 is smaller than the increase amount of the discharge amount of the oil 1 corresponding to the rotation speed of the engine 90 in the low speed region.

(Second medium speed range)
Then, in the second medium speed range where the engine speed exceeds N3 larger than N2, as shown in FIG. 7, the discharge pressure from the oil pump main body 10 further increases, and the center in the Y direction of the valve portion 21a is sub The valve body 21 moves until it is located near the center of the oil passage hole 22d in the Y direction. At this time (initial stage of the second medium speed range), all of the hydraulic pressure introduction hole 22b, the connection oil passage hole 22c, the sub oil passage hole 22d, and the relief oil passage hole 22e are opened. Accordingly, the main oil passage 6 and the sub oil passage 7 are brought into communication, and the sub oil passage 7 and the relief oil passage 8 are brought into communication through the valve chamber 24.

As a result, at the initial stage of the second medium speed range, the discharge amount of the oil 1 discharged to the supplied portion 92 is the main oil passage of the oil 1 from the main discharge port 4 and the oil 1 from the sub discharge port 5. 6 and the total amount of oil 1 (β) supplied to 6. That is, of the oil 1 from the sub discharge port 5, the discharge amount discharged to the supplied portion 92 is reduced by the amount of oil 1 supplied to the relief oil passage 8.

Thereafter, when the engine speed exceeds N4 which is larger than N3, the discharge pressure from the oil pump main body 10 further increases, and a part of the valve portion 21a is located at the Y2 side end of the sub oil passage hole 22d. When the valve body 21 moves to the Y2 side (second intermediate speed range), the relief oil passage 8 is closed by the valve portion 21a as shown in FIG. The relief oil passage 8 is brought into a non-communication state. Further, the main oil passage 6 and the sub oil passage 7 are brought into communication.

As a result, not only the oil 1 from the main discharge port 4 but also the oil 1 from the sub discharge port 5 is supplied to the main oil path 6 via the sub oil path 7 in the second medium speed range. That is, the discharge amount of the oil 1 discharged to the supplied portion 92 is the total amount of the oil 1 from the main discharge port 4 and the oil 1 from the sub discharge port 5. As shown in FIG. 10, in the second medium speed range, the discharge amount of oil 1 increases in proportion to the rotational speed of engine 90.

(High speed range)
Then, in a high speed range where the engine speed exceeds N5 larger than N4, as shown in FIG. 9, the discharge pressure from the oil pump main body 10 further increases, and the distal end portion 21d of the valve body 21 becomes a relief oil passage hole. The valve body 21 moves until it is located on the Y2 side of the end portion on the Y1 side of the portion 22e. At this time, all of the oil pressure introduction hole 22b, the connection oil passage hole 22c, the sub oil passage hole 22d, and the relief oil passage hole 22e are opened. Therefore, the main oil passage 6, the sub oil passage 7, and the relief oil passage 8 are brought into communication.

As a result, in the high speed range, the discharge amount of the oil 1 discharged to the supplied portion 92 is supplied to the relief oil path 8 out of the oil 1 from the main discharge port 4 and the oil 1 from the sub discharge port 5. This is the total amount of oil 1 (γ) supplied to the main oil passage 6 excluding the oil 1. That is, of the oil 1 from the sub discharge port 5, the discharge amount discharged to the supplied portion 92 is reduced by the amount of oil 1 supplied to the relief oil passage 8.

As shown in FIG. 10, when the engine speed is near N5, the number of sliding of the piston 92a increases due to the increase in the speed of the engine 90, and as a result, the temperature of the piston 92a rises. For this reason, a large amount of cooling oil 1 is required to be injected from the oil jet (not shown) of the crankshaft 92b to the piston 92a. At this time, as a required discharge amount of oil 1 (oil amount for jet: region indicated by W in FIG. 10), the total amount of oil 1 from the main discharge port 4 and oil 1 from the sub discharge port 5 Is required. For this reason, the oil pump device 100 of the present embodiment is configured such that the slopes of the G5-G6 line and the G6-G7 line exceed the jet oil amount W in the high speed range. On the other hand, in the high speed range where the engine speed is higher than N5 and the cooling oil 1 is sufficiently supplied to the supplied portion 92 (piston 92a and crankshaft 92b), the oil 1 from the main discharge port 4 The discharge amount of the oil 1 may be smaller than the total amount of the oil 1 from the discharge port 5. Thereby, the discharge amount discharged to the supplied part 92 is reduced by the amount of the oil 1 supplied to the relief oil passage 8.

As a result, in the oil pump device 100, when the oil 1 is not relieved via the relief oil passage 8 (when the oil 1 is always supplied from both the main discharge port 4 and the sub discharge port 5 to the supplied portion 92). When the engine speed is between N1 and N4 and after N5, the discharge amount of oil 1 can be reduced by the amount of the thick diagonal line shown in FIG. It is possible to reduce energy (work) supplied from the engine 90 to drive the pump body 10. In this way, the three-stage variable oil pump device 100 that changes in three stages of a low speed region, a medium speed region, and a high speed region is configured.

In the present embodiment, the following effects can be obtained.

In the present embodiment, as described above, on the Y1 side and Y2 side of the valve body 21, the sub oil passage 7 with the main oil passage 6 is switched between the communication state and the non-communication state, and the sub oil passage 7 and the relief oil passage are provided.

Valve portions

21a and 21b for switching between a communication state and a non-communication state with 8 are formed. As a result, when the discharge pressure of the oil 1 is such that the sub oil passage 7 and the relief oil passage 8 are communicated with each other by the valve body 21 of the relief valve 20 (first medium speed region), the sub oil passage The oil 1 discharged to 7 can be sufficiently relieved (refluxed) via the relief oil path 8, so that the discharge pressure and discharge amount of the oil 1 discharged from the oil pump body 10 can be reduced. . Thereby, the energy (work) for oil discharge in the oil pump main body 10 can be reduced. As a result, the driving force from the engine 90 necessary for operating the oil pump main body 10 can be reduced, and the fuel efficiency of the engine 90 can be improved accordingly.

Moreover, in this embodiment, the relief valve 20 is formed compared with the case where the valve body 21 forms a some valve chamber by forming the single valve chamber 24 in the valve body accommodating part 22 with the valve body 21. FIG. Since the length in the longitudinal direction (movement direction, Y direction) can be reduced, the relief valve 20 can be reduced in size accordingly. As a result, the degree of freedom of arrangement of the relief valve 20 in the oil pump device 100 can be improved, and the oil pump device 100 can be downsized as the relief valve 20 is downsized. As a result, the mountability of the oil pump device 100 on a vehicle can be improved.

Further, in the present embodiment, the main discharge port 4 and the sub discharge port 5 are provided independently of each other with a partition wall 10 a therebetween, and are connected to the main oil passage 6 and the sub discharge port 5 connected to the main discharge port 4. The sub oil passages 7 are provided independently of each other across the partition wall 10a. As a result, the main oil passage 6 and the sub oil passage 7 are connected to different discharge ports (main discharge port 4 and sub discharge port 5), so that all of the oil 1 discharged from the sub discharge port 5 is sub-oiled. The oil 1 discharged to the path 7 can be used. As a result, by increasing the discharge amount of the oil 1 discharged from the sub discharge port 5, the discharge amount of the oil 1 discharged from the sub oil passage 7 can be controlled to increase accurately.

In the present embodiment, the valve body 21 is constricted with respect to the valve section 21a and the valve section 21a formed in the region from the tip 21d of the valve body 21 to the constricted section 21c (single valve chamber 24). A valve portion 21b formed on the Y2 side opposite to the tip portion 21d via the portion 21c, and a constricted portion 21c formed between the valve portion 21a and the valve portion 21b and extending in the Y direction are provided. Thereby, the single valve chamber 24 can be easily formed by the constriction part 21c between the valve part 21a and the valve part 21b.

Further, in the present embodiment, in the Y direction in which the valve body 21 moves, the length L3 of the valve portion 21a is formed to be smaller than the length L4 of the valve chamber 24 (constricted portion 21c). Since the length L3 from the distal end portion 21d of the body 21 to the single valve chamber 24 (valve portion 21a) can be sufficiently reduced, the relief valve 20 can be further downsized. Further, since the length L4 of the valve chamber 24 (constricted portion 21c) is larger than the length L3 of the valve portion 21a, the length L4 of the valve chamber 24 can be ensured to some extent. As a result, it is possible to prevent the flow resistance of the oil 1 in the valve chamber 24 from increasing due to the volume of the valve chamber 24 becoming excessively small. Thereby, since it can suppress that the discharge pressure for discharging the oil 1 through the valve chamber 24 becomes large, it suppresses that the energy (work) for oil discharge in the oil pump main body 10 becomes large. can do.

In the present embodiment, the connection oil passage hole 22c and the sub oil passage hole 22d are opened in the low speed region, thereby allowing the main oil passage 6 to pass through the valve chamber 24 and the connection oil passage 6b. And the sub oil passage 7 are brought into communication. Further, the relief oil passage hole 22e is closed by the valve portion 21b, whereby the sub oil passage 7 and the relief oil passage 8 are brought into a non-communication state. As a result, in the low speed range, the oil 1 from the sub oil passage 7 is supplied to the main oil passage 6 without being discharged to the relief oil passage 8, so that the discharge pressure of the oil 1 in the main oil passage 6 can be increased. it can. As a result, the driving force applied to the oil pump main body 10 is the amount of oil 1 discharged (the region indicated by V in FIG. 10) required for the driving force based on the discharge pressure of the oil 1 to exceed the biasing force of the spring 23. Can be secured from a small stage.

In this embodiment, the main oil passage 6 and the sub oil passage 7 are connected not only to the valve chamber 24 but also from the X2 side (bypassing to the X2 side) to connect to the main oil passage 6. Unlike the case where the sub oil passage 7 is connected to the main oil passage 6 only through the valve chamber 24 by being connected via the passage 6b, the oil is discharged from the main discharge port 4 via the main oil passage 6. It is possible to suppress the oil 1 and the oil 1 discharged from the sub discharge port 5 via the sub oil passage 7 from interfering with each other at the joining point (hydraulic introduction hole 22b) of the main oil passage 6. Thereby, it is possible to suppress an increase in energy (work) for oil discharge in the oil pump main body 10 due to interference.

In the present embodiment, the valve body 21 moves in the Y direction by disposing the sub oil passage 7 between the connection oil passage 6b and the relief oil passage 8 in the Y direction in which the valve body 21 moves. Accordingly, the communication state between the sub oil passage 7 and the connection oil passage 6b and the communication state between the sub oil passage 7 and the relief oil passage 8 can be easily switched.

Further, in the present embodiment, the valve portion 21a is formed by making the length L3 of the valve portion 21a in the Y direction in which the valve body 21 moves smaller than the inner diameter D4 of the connection oil passage hole 22c of the connection oil passage 6b. Since it can suppress that the state which block | closes the connection oil path hole 22c arises, the main oil path 6 and the sub oil path 7 can be reliably connected via the connection oil path 6b.

In the present embodiment, in the first medium speed range, the main oil passage 6 and the sub oil passage 7 are disconnected from each other by the valve portion 21a, and the sub oil passage 7 and the relief oil are connected via the valve chamber 24. The road 8 is brought into communication. As a result, in the first medium speed range, all of the oil 1 from the sub oil passage 7 is discharged to the relief oil passage 8, so that the discharge amount of the oil 1 to be relieved is increased and the oil 1 is sufficiently relieved. Can do. Thereby, the energy (work) for oil discharge in the oil pump body 10 can be sufficiently reduced.

Further, in the present embodiment, in the second medium speed region that is larger than the first medium speed region, the valve portion 21a causes the sub oil passage 7 and the relief oil passage 8 to be disconnected from each other by the valve portion 21a. The oil passage 6 and the sub oil passage 7 are brought into communication. As a result, the oil 1 from the sub oil passage 7 is supplied to the main oil passage 6 without being discharged to the relief oil passage 8 in the second medium speed range, so the amount of oil 1 discharged from the main oil passage 6 is increased. can do. Thereby, a large amount of the cooling oil 1 injected from the oil jet to the piston 92 a can be supplied to the supplied portion 92 via the main oil passage 6.

In the present embodiment, the main oil passage 6, the sub oil passage 7, and the relief oil passage 8 are brought into communication with each other in the high speed region, so that the oil 1 is supplied to the supplied portion 92 via the main oil passage 6. Since a part of the oil 1 can be relieved through the relief oil passage 8 while being sufficiently supplied, energy (work) for oil discharge in the oil pump body 10 can be reduced, and the oil passage It is possible to prevent the oil passage from being damaged due to excessive hydraulic pressure being applied to the oil passage.

Further, in the present embodiment, the length L3 of the valve portion 21a in the Y direction in which the valve body 21 moves is made smaller than the inner diameter D5 of the relief oil passage hole 22e of the relief oil passage 8, thereby making the valve in the Y direction. Since the increase in the portion 21a can be suppressed, the increase in the discharge pressure of the oil 1 necessary for the relief oil passage 8 and the main oil passage 6 to communicate with each other in the high speed range is suppressed. Can do. As a result, a part of the oil 1 can be relieved through the relief oil passage 8 from a stage where the discharge pressure of the oil 1 is small, so that energy (work) for oil discharge in the oil pump body 10 can be reduced at an early stage. In addition, the oil passage can be reliably prevented from being damaged due to excessive oil pressure being applied to the oil passage.

Further, in the present embodiment, the outer edge portion 121a on the valve chamber 24 side (Y2 side) is chamfered circumferentially in the valve portion 21a, and the outer edge portion 121b on the valve chamber 24 side (Y1 side) is circumferentially formed in the valve portion 21b. Chamfer. Thereby, at the time of switching between the communication state and the non-communication state via the valve chamber 24, it is possible to suppress a rapid change in the flow of the oil 1 in the chamfered

outer edge portions

121a and 121b. That is, it is possible to prevent the oil 1 flowing in the connection oil passage 6b (relief oil passage 8) from being suddenly blocked when switching between the communication state and the non-communication state via the valve chamber 24, and the connection oil It is possible to suppress the oil 1 from suddenly starting to flow into the path 6b (relief oil path 8). Thereby, it is possible to suppress unnecessary vibration (self-excited vibration) or the like from occurring in the valve body 21.

In addition, it should be thought that embodiment disclosed this time is an illustration and restrictive at no points. The scope of the present invention is shown not by the above description of the embodiments but by the scope of claims for patent, and further includes all modifications within the meaning and scope equivalent to the scope of claims for patent.

For example, in the above-described embodiment, the example in which the constricted portion 21c having the outer diameter D2 smaller than the outer diameter D1 of the

valve portions

21a and 21b is provided at the position corresponding to the valve chamber 24 is described. Not limited. For example, instead of the constricted portion, a cylindrical (hollow) barrel portion having the same outer diameter as the pair of valve portions may be provided at a position corresponding to the valve chamber. At this time, the internal space of the hollow body portion can be used as a valve chamber. In addition, it is necessary to provide the hole for connecting a valve chamber (internal space of a trunk | drum) and the exterior (oil path) in the side surface of a trunk | drum.

In the above embodiment, the example in which the length L3 of the valve portion 21a on the tip portion 21d side (Y1 side) is set to be equal to or shorter than the length L4 of the valve chamber 24 (constriction portion 21c) is shown. Not limited to. In the present invention, the length of the valve portion on the distal end side may be larger than the length of the valve chamber.

In the above-described embodiment, the outer edge 121a on the valve chamber 24 side (Y2 side) is chamfered circumferentially in the valve portion 21a, and the outer edge portion 121b on the valve chamber 24 side (Y1 side) is circumferential in the valve portion 21b. However, the present invention is not limited to this. In the present invention, for example, the outer edge portion of the valve portion may not be chamfered, or only one outer edge portion of the pair of valve portions may be chamfered. Thereby, it is possible to simplify the manufacturing process of an oil pump apparatus. On the other hand, in the valve portion on the tip portion side, not only the outer edge portion on the valve chamber side but also the outer edge portion on the tip portion side may be chamfered.

In the above embodiment, the example in which the oil pump device 100 is configured to have the internal relief structure in which the oil 1 flowing through the relief oil passage 8 is returned to the suction port 3 has been described, but the present invention is not limited thereto. Absent. In the present invention, the oil pump device may be configured to have an outer relief structure in which the other end (return port) of the relief oil passage is disposed on the oil pan (91, see FIG. 2).

In the above embodiment, an example in which the valve body accommodating portion 22 is formed in the shape of a shaft hole is shown, but the present invention is not limited to this. For example, the inner diameter of the portion of the valve body housing portion where the spring other than the movable area of the valve body is inserted may be smaller than the inner diameter of the movable area of the valve body. Further, outside the movable range of the valve body, a stepped process or the like may be applied to the valve body housing portion.

In the above embodiment, the oil pump body 10 is shown as an example of a trochoid oil pump that is an inscribed gear type, but the present invention is not limited to this. In the internal gear type, the oil pump main body may be configured by applying an inscribed involute tooth mold. Further, the oil pump main body may be configured not only as an internal gear type but also as an external gear type oil pump having a circumscribed involute tooth shape, for example.

In the above embodiment, the example in which the present invention is applied to the oil pump device 100 that supplies the oil 1 to the engine 90 has been described, but the present invention is not limited thereto. For example, the present invention may be applied to an oil pump device for supplying AT fluid (AT oil) to an automatic transmission (AT) that automatically switches the gear ratio according to the rotational speed of the internal combustion engine. Further, unlike the AT (multi-stage transmission) that changes gears by changing the gear combination, the lubricating oil is supplied to the sliding portion in the continuously variable transmission (CVT) capable of changing the gear ratio continuously and continuously. You may apply this invention to the oil pump apparatus for this. Further, the present invention may be applied to an oil pump device for supplying power steering oil to a power steering device that drives a steering (steering device) in a vehicle.

In the above embodiment, an example in which the oil pump device 100 is mounted on a vehicle such as an automobile provided with the engine 90 has been described. However, the present invention is not limited to this. For example, you may apply this invention with respect to the oil pump apparatus mounted in equipment other than the vehicle provided with the internal combustion engine (engine). Moreover, as an internal combustion engine, a gasoline engine, a diesel engine, a gas engine, etc. are applicable.

1 Oil 3 Suction port 4 Main discharge port (first discharge port)
5 Sub discharge port (second discharge port)
6 Main oil passage (first oil passage)
6b Connection oil passage 7 Sub oil passage (second oil passage)
8 Relief oil passage 10 Oil pump body 20 Relief valve 21 Valve body 21a Valve part (first valve part)
21b Valve part (second valve part)

21c Constricted portion

21d Tip portion 22 Valve body accommodating portion 22c Connection oil passage hole portion 22e Relief oil passage hole portion 24 Valve chamber 92 Supplyed portion 100 Oil pump device 121a Outer edge portion 121b (second valve portion) Outer edge of valve

Claims

An oil pump main body that sucks oil from the suction port and discharges oil from the first discharge port and the second discharge port provided independently of each other;
A first oil path connected to the first discharge port and supplying oil discharged from the first discharge port to a supply portion;
A second oil passage connected to the second discharge port;
A single relief oil passage for relieving at least oil discharged from the second oil passage;
A relief valve,
The relief valve is
A valve body accommodating portion connected to the first oil passage, the second oil passage, and the relief oil passage;
By forming a single valve chamber in the valve body housing portion in a state of being housed in the valve body housing portion, and moving in the valve body housing portion according to the pressure of oil to be discharged, the second Switching between a communication state and a non-communication state between the second oil passage on the discharge port side and the first oil passage on the first discharge port side, a communication state between the second oil passage and the relief oil passage, and non-connection An oil pump device including a valve body that switches a communication state.
2. The oil pump device according to claim 1, wherein a length from the tip of the valve body to the single valve chamber is equal to or less than a length of the valve chamber in a direction in which the valve body moves.
The valve body is formed on the opposite side of the first valve portion with respect to the first valve portion, with the valve chamber interposed therebetween with respect to the first valve portion. The second valve portion is formed at a position corresponding to the valve chamber between the first valve portion and the second valve portion, and has an outer diameter smaller than that of the first valve portion and the second valve portion. Having a constriction,
The oil pump device according to claim 2, wherein a length of the first valve portion is equal to or less than a length of the constricted portion in a direction in which the valve body moves.
In the low speed region, the valve body causes the second oil passage and the relief oil passage to be in a non-communication state by the second valve portion, and the first oil passage and the second oil passage are connected to the valve chamber. The oil pump device according to claim 3, wherein the oil pump device is configured to be in communication with each other.
In addition to being connected to the first oil passage, in a low speed region, further comprising a connection oil passage connected to the second oil passage through the valve chamber,
5. The valve body according to claim 4, wherein the valve body is configured to bring the first oil passage and the second oil passage into a communication state via the valve chamber and the connection oil passage in a low speed region. Oil pump device.
The oil pump device according to claim 5, wherein the second oil passage is disposed between the connection oil passage and the relief oil passage in a direction in which the valve body moves.
The length of the said 1st valve part in the direction to which the said valve body moves is comprised so that it may become smaller than the internal diameter of the hole part for connection oil paths of the said connection oil path. Oil pump device.
In the first medium speed region, the valve body causes the first oil passage and the second oil passage to be disconnected from each other by the first valve portion, and the second oil passage and the relief oil passage are connected to each other. The oil pump device according to any one of claims 3 to 7, wherein the oil pump device is configured to be in a communication state via the valve chamber.
The valve body is in a non-communication state between the second oil passage and the relief oil passage by the first valve portion in a second medium speed region that is a speed region larger than the first medium speed region, The oil pump device according to claim 8, wherein the first oil passage and the second oil passage are configured to be in communication with each other.
The valve body according to any one of claims 3 to 9, wherein the valve body is configured to communicate all of the first oil passage, the second oil passage, and the relief oil passage in a high speed range. Oil pump device.
The oil pump according to claim 10, wherein a length of the first valve portion in a direction in which the valve body moves is configured to be smaller than an inner diameter of a relief oil passage hole portion of the relief oil passage. apparatus.
The at least one of the outer edge portion of the first valve portion on the valve chamber side and the outer edge portion of the second valve portion on the valve chamber side is chamfered. The oil pump device described in 1.
A first oil passage connected to a first discharge port through which oil is discharged from the oil pump main body and supplying oil discharged from the first discharge port to a supplied portion, and the first discharge port are independent of each other A valve body accommodating portion connected to a second oil passage connected to the provided second discharge port, and a single relief oil passage for relieving at least oil discharged from the second oil passage;
By forming a single valve chamber in the valve body housing portion in a state of being housed in the valve body housing portion, and moving in the valve body housing portion according to the pressure of oil to be discharged, the second Switching between a communication state and a non-communication state between the second oil passage on the discharge port side and the first oil passage on the first discharge port side, a communication state between the second oil passage and the relief oil passage, and non-connection A relief valve provided with a valve body for switching the communication state.
The relief valve according to claim 13, wherein a length from the tip of the valve body to the single valve chamber is equal to or less than a length of the valve chamber in a moving direction of the valve body.
The valve body is formed on the opposite side of the first valve portion with respect to the first valve portion, with the valve chamber interposed therebetween with respect to the first valve portion. The second valve portion is formed at a position corresponding to the valve chamber between the first valve portion and the second valve portion, and has an outer diameter smaller than that of the first valve portion and the second valve portion. Including a constriction,
The relief valve according to claim 14, wherein a length of the first valve portion is equal to or less than a length of the constricted portion in a direction in which the valve body moves.