JP7091634B2 - Hydraulic control valve - Google Patents

Description

The present disclosure relates to a hydraulic control valve whose set pressure can be changed.

A relief valve is known as a hydraulic control valve. The relief valve suppresses an increase in the pressure of the hydraulic circuit by opening an oil discharge port (relief path) provided inside the relief valve when the pressure of the hydraulic circuit exceeds a set pressure. Some relief valves of this type can change the set pressure, that is, the relief pressure.

For example, Patent Document 1 discloses a relief valve provided with a valve body and a spring for urging the valve body from a position where oil can be discharged to a position where oil cannot be discharged in an internal space of a valve body. In this relief valve, a first introduction port and a second introduction port are formed in the valve body. The pressure of the oil introduced into the internal space only through the first introduction port or through both the first and second introduction ports is received by one or two pressure receiving surfaces formed on the valve body, and as a result, the valve body. When the oil is moved from the non-dischargeable position to the dischargeable position, the oil introduced into the internal space from the first introduction port is discharged to the suction flow path (upstream from the relief valve) through the discharge port. The relief valve of Patent Document 1 is in a high set pressure state and a low set pressure state by switching the introduction of oil into the internal space and the cutoff of oil introduction through the second introduction port by the switching operation of the auxiliary valve. It is configured so that the relief pressure can be switched between.

Japanese Unexamined Patent Publication No. 2011-208651

By the way, in the above relief valve of Patent Document 1, the valve body has a first end surface that abuts on a spring and a second pressure receiving surface for receiving oil introduced into the internal space from the second introduction port in the axial direction thereof. It includes a formed second end face and a reduced diameter portion provided between the end faces and facing the first introduction port. Therefore, the valve body of the relief valve has a second introduction port at an axial extension of the valve body. As described above, the relief valve of Patent Document 1 adopts a configuration long in the axial direction of the valve body in order to form the second introduction port.

On the other hand, from the viewpoint of improving the mountability of the relief valve, there is a demand for miniaturization of the relief valve. However, it is not easy to reduce the size of the relief valve having the above configuration because of the arrangement of the second introduction port and the second pressure receiving surface.

The technique of the present disclosure is intended to provide a hydraulic control valve having a novel configuration in which a set pressure can be changed.

In order to achieve the above object, the technique of the present disclosure has a first introduction port and a second introduction port capable of partitioning an internal space and introducing hydraulic oil into the internal space, and an operation flowing into the internal space. A valve body that separately forms a discharge port capable of discharging oil, and a valve body movably arranged in the internal space in the axial direction of the internal space, capable of discharging hydraulic oil from the discharge port. A valve body and a valve body that is movable between a first position of the valve body and a second position that makes it impossible to discharge hydraulic oil from the discharge port, and the valve body from the first position side to the second position side. The valve body includes an urging member configured to urge the second introduction port and an introduction amount variable device configured to change the amount of hydraulic oil introduced into the second introduction port. A first pressure receiving surface configured to receive a force from the hydraulic oil introduced into the internal space from the introduction port to the first position side, and introduced into the internal space from the second introduction port. Provided is a hydraulic control valve including a second pressure receiving surface configured to receive a force from the hydraulic oil to the second position side.

Preferably, the first pressure receiving surface is formed so as to face the direction opposite to the second pressure receiving surface.

The valve body has a first end portion positioned on the second position side and a second end portion positioned on the first position side in the internal space, and the first end portion side thereof. It is preferable to have one pressure receiving surface, the second pressure receiving surface on the second end side, and a contact surface on the second end side to which the urging member abuts.

When the valve body further includes an inflow port through which the hydraulic oil can flow in, the discharge port may be configured to be able to discharge the hydraulic oil that has flowed into the internal space through the inflow port.

When the valve body has a substantially cylindrical shape and has a first diameter portion having a first diameter and a second diameter portion having a diameter shorter than the first diameter, the valve body is in the internal space. When in the second position, the inflow port is closed at the first diameter portion, and when the valve body is in the first position in the internal space, the inflow port passes through the circumference of the second diameter portion. It should be connected to the discharge port.

According to the above technique of the present disclosure, a hydraulic control valve having a novel configuration is provided, and in this hydraulic control valve, the set pressure can be changed according to the novel configuration.

It is a schematic block diagram of the hydraulic system provided with the relief valve as the hydraulic control valve which concerns on 1st Embodiment, and is the figure when the relief valve is in a high set pressure state. It is a schematic block diagram of the hydraulic system of FIG. 1, and is the figure when the relief valve is in a high set pressure state. It is a schematic block diagram of the hydraulic system of FIG. 1, and is the figure when the relief valve is in a low set pressure state. It is a schematic block diagram of the hydraulic system of FIG. 1, and is the figure when the relief valve is in a low set pressure state. It is a schematic block diagram of the hydraulic system provided with the relief valve as the hydraulic control valve which concerns on 2nd Embodiment, and is the figure when the relief valve is in a high set pressure state. It is a schematic block diagram of the hydraulic system of FIG. 5, and is the figure when the relief valve is in a high set pressure state. It is a schematic block diagram of the hydraulic system of FIG. 5, and is the figure when the relief valve is in a low set pressure state. It is a schematic block diagram of the hydraulic system of FIG. 5, and is the figure when the relief valve is in a low set pressure state.

Hereinafter, this embodiment will be described with reference to the attached drawings. The same parts (or configurations) are designated by the same reference numerals, and their names and functions are also the same. Therefore, detailed explanations about them will not be repeated.

First, the relief valve 10 as the hydraulic control valve according to the first embodiment will be described with reference to FIGS. 1 to 4. The present disclosure is not limited to the application to the relief valve, and can be applied to various hydraulic control valves.

1 to 4 show a hydraulic system provided with a relief valve 10 according to the first embodiment. The relief valve 10 is a valve with a relief pressure changing function (set pressure changing function). The relief valve 10 is installed in the hydraulic system of the vehicle in order to adjust and control the pressure of the supply flow path 12 that supplies hydraulic oil (hereinafter referred to as oil) to the clutch device CA of the automatic transmission (AT). However, this does not limit the use of the relief valve 10, and the relief valve 10 may be used for adjusting the pressure of the oil supply flow path to each part of the engine. As described above, the hydraulic control valve according to the present disclosure can be used for various purposes.

As shown in FIGS. 1 to 4, in the engine operating state, the oil pump 14 sucks the oil OIL stored in the oil pan 16 through the suction flow path 18 (via the oil filter 19), and the supply flow path 12 Discharge toward the clutch device CA through. The relief valve 10 is arranged in the path of the supply flow path 12 on the downstream side of the oil pump 14. The oil pump 14 is configured to be operated by power from the drive shaft of the engine, but may be of an electric type, for example.

The relief valve 10 includes a valve body 20, a valve body 22, a coil spring 24, and an introduction amount variable device 26.

The valve body 20 includes a body body 28 and a cap member 30. By attaching and fixing the cap member 30 to the body body 28, they are integrated and an internal space 32 is partitioned between them. The internal space 32 of the valve body 20 is substantially columnar and has an axis line 32a thereof. In the internal space 32, the valve body 22 is movably arranged in a direction (axial direction) along the axis line 32a. The valve body 22 has an axis that substantially coincides with the axis 32a when it is in the internal space 32.

The valve body 20 is further divided into a first introduction port 34, a second introduction port 36, an inflow port 38, and an discharge port 40. In addition, the valve body 20 is partitioned by a pressure relief hole 42 for releasing the back pressure acting on the valve body 22. The pressure relief hole 42 is provided along the axis 32a of the internal space 32, but may be provided at various positions so that the valve body 22 can be appropriately moved in the internal space 32. Each of these ports 34, 36, 38, 40 and the pressure relief hole 42 is individually formed so as to communicate with the internal space 32. However, the ports 34, 36, 38 in the axial direction of the internal space, as shown in FIGS. 1 to 4, so as to ensure a suitable flow of oil from the ports 34, 36, 38, 40 to the internal space 32. A substantially annular space through which oil can flow is formed around the internal space at a position facing each of the 40 and 40. The first introduction port 34, the second introduction port 36, the inflow port 38, and the discharge port 40 are formed in the body main body 28, and the pressure relief hole 42 is formed in the cap member 30. These do not limit the configuration of each member.

Two ports, a first introduction port 34 and a second introduction port 36, are separately provided on the body body 28 as introduction ports configured to allow oil to be introduced into the internal space 32. The first introduction port 34 is always in communication with the supply flow path 12. The second introduction port 36 is made to communicate with the supply flow path 12 via the control valve 44. An introduction amount variable device 26 (configured to make the amount of oil introduced into the second introduction port 36 variable) including a control valve 44 and a part of an electronic control unit (hereinafter referred to as an ECU) described later. Is configured. It should be noted that orifices 34'and 36'are provided in each flow path of oil to the first introduction port 34 and the second introduction port 36. These orifices 34'and 36' are provided so as to suppress the pressure pulsation of the oil flowing through the introduction ports, and can be omitted in other configurations.

The inflow port 38 is configured so that the oil pumped from the oil pump 14 can flow in, and is always communicated with the supply flow path 12 like the first introduction port 34. The discharge port 40 is configured to be able to discharge the oil that has flowed into the internal space 32. The discharge port 40 and the pressure relief hole 42 are each communicated with the suction flow path 18, but may be directly communicated with, for example, the oil pan 16.

In the axial direction of the internal space 32, the first introduction port 34 and the second introduction port 36 are formed in the valve body 20 so as to sandwich the inflow port 38 and the discharge port 40. In the following, in the axial direction of the internal space 32, the end region of the internal space 32 on the side where the first introduction port 34 is located is defined as the first end region, and the internal space on the side where the second introduction port 36 is located is defined as the first end region. The end region of 32 is referred to as a second end region.

As described above, the valve body 22 is movably arranged in the internal space 32 in such a valve body 20 in the axial direction of the internal space 32. Corresponding to the substantially cylindrical internal space 32, the valve body 22 is also substantially cylindrical. Although the valve body 22 is movably arranged in the internal space 32, it is substantially fitted in the valve body 20. Preferably, the valve body 20 and the valve body 22 are each sized so as to have good airtightness between them.

In the internal space 32, the coil spring 24 is arranged in the second end region. The coil spring 24 is provided as an urging member that urges the valve body 22 from the second end region side to the first end region side along the axial direction of the internal space 32. The urging force of the coil spring 24 urges the valve body 22 in a direction that closes the inflow port 38. That is, the coil spring 24 urges the valve body 22 to the non-drainable position side that makes it impossible to drain the oil from the discharge port 40. On the other hand, as described below, when the pressure of the oil introduced from the first introduction port 34 exceeds the urging force of the coil spring 24, the valve body 22 is located on the non-dischargeable position side or the first end region. From the side, it is moved toward the second end region side along the axial direction. As a result, the valve body 22 can move from the non-dischargeable position side or the first end region side to the position where the inflow port 38 is opened, so that oil can flow into the internal space through the inflow port 38. As a result, the oil can be discharged from the discharge port 40. Hereinafter, the position of the valve body 22 that enables the discharge of oil from the discharge port 40 is referred to as a dischargeable position. As described above, in the internal space 32 of the valve body 20, the valve body 22 is movable between the dischargeable position and the discharge non-dischargeable position. In particular, in the relief valve 10, the valve body 22 opens the inflow port 38 at the dischargeable position to allow oil to flow into the internal space from there, closes the inflow port 38 at the non-dischargeable position, and enters the internal space from there. Block the inflow of oil. That is, the discharge possible position of the valve body 22 is the position where the inflow port and the discharge port are in a communicating state, and the discharge impossible position of the valve body 22 is the position where the inflow port and the discharge port are in a non-communication state (blocked state). It is a position that becomes. The dischargeable position corresponds to the first position in the technique of the present disclosure, and the non-dischargeable position corresponds to the second position in the technique of the present disclosure.

The valve body 22 has a first end portion 22a located on the non-dischargeable position side, that is, the first end region side, and a second end portion 22b located on the dischargeable position side, that is, the second end region side in the internal space 32. And have. As shown in FIG. 1, the valve body 22 is configured to close the inflow port 38 with a first diameter portion 22c having a maximum diameter (first diameter) D1 when in a non-dischargeable position. Further, a second diameter D2 shorter than the first diameter D1 is provided between the first end portion 22a and the second end portion 22b, particularly on the first end portion 22a side of the first diameter portion 22c. The diameter portion 22d is formed. The second diameter D2 of the second diameter portion 22d changes along the axial direction of the valve body 22. Therefore, as the valve body 22 moves from the non-dischargeable position to the dischargeable position, the inflow port 38 communicates with the space around the second diameter portion 22d of the internal space 32, and the space concerned. Can communicate with the discharge port 40 via.

The first end 22a of the valve body 22 is formed to include a third diameter portion 22f having a third diameter D3 shorter than the first diameter D1. An intermediate diameter portion 22c'having a first diameter is formed between the third diameter portion 22f and the second diameter portion 22d. When the valve body 22 is in the internal space 32, the axially oriented surface (hereinafter, the first axial direction surface) 22af between the third diameter portion 22f and the intermediate diameter portion 22c'is inside from the first introduction port 34. It can function as a first pressure receiving surface 22e capable of receiving a force from the non-dischargeable position side to the dischargeable position side from the oil introduced into the space 32. The first axial plane 22af is formed so as to face the first axial direction in the axial direction when the valve body 22 is in the internal space 32. The first axial plane 22af is an annular plane. When the valve body 22 moves from the non-dischargeable position to the dischargeable position side, the end surface 22a'of the first end portion 22a is in contact with the inner surface of the valve body 20 (that is, the surface forming the internal space 32). Since it is in a separated state from the above, the end surface 22a'also functions as the first pressure receiving surface 22e. Actually, both the non-dischargeable position and the dischargeable position of the valve body 22 have a certain range (axial stroke). Therefore, even when the valve body 22 is in the position where it cannot be discharged, the end surface 22a'can function as the first pressure receiving surface. That is, in the valve body 22 in the non-dischargeable position, when the end surface 22a'of the first end portion 22a of the valve body 22 is separated from the inner surface of the valve body 20, the first pressure receiving surface 22e becomes the first axial surface 22af. It is composed of an end face 22a'. In the relief valve 10, the end surface 22a'is circular and is formed so as to be parallel to the first axial direction surface 22af and to face the same direction (first axial direction) as the first axial direction surface 22af.

Further, the second end portion 22b side of the first diameter portion 22c of the valve body 22 is formed as a fourth diameter portion 22g having a fourth diameter D4 shorter than the first diameter D1. When the valve body 22 is in the internal space 32, the surface facing the axial direction (second axial surface) between the first diameter portion 22c and the fourth diameter portion 22g is from the second introduction port 36 to the internal space 32. It functions as a second pressure receiving surface 22h capable of receiving a force from the introduced oil from the dischargeable position side to the non-dischargeable position side. Here, the second axial direction surface is formed so as to face the second axial direction opposite to the first axial direction in the axial direction when the valve body 22 is in the internal space 32. Hereinafter, the surface in the second axial direction is referred to as a second pressure receiving surface 22h. The second pressure receiving surface 22h is an annular surface. The end of the fourth diameter portion 22g is movably arranged in the cylindrical guide portion 30a arranged in the internal space 32 in the cap member 30, and is arranged in the axial direction of the internal space 32 by the guide portion 30a. Be guided. A coil spring 24 is arranged around the fourth diameter portion 22 g. The second pressure receiving surface 22h is also formed as a contact surface with which one end of the coil spring 24 abuts. The other end of the coil spring comes into contact with the end surface of the guide portion 30a of the cap member 30. As described above, the second pressure receiving surface 22h is formed on the valve body 22 on the second end 22b side of the first end 22a with respect to the first pressure receiving surface 22e, and can receive the urging force by the coil spring 24. , It is configured to be able to receive the pressure of oil, that is, the oil pressure.

As is clear from FIG. 1, the first pressure receiving surface 22e is formed so as to face the direction opposite to the second pressure receiving surface 22h. Therefore, when the valve body 22 is in the internal space 32, the first pressure receiving surface 22e is in the second axial direction from the non-dischargeable position side to the dischargeable position side from the oil introduced into the internal space from the first introduction port 34. The second pressure receiving surface 22h can receive the force of the oil introduced into the internal space from the second introduction port 36, from the dischargeable position side to the non-dischargeable position side (opposite to the second axial direction). It can receive a force in the first axial direction.

The operation of the control valve 44 in the relief valve 10 having the above configuration is controlled by the above-mentioned ECU (not shown). The ECU includes an arithmetic unit (for example, a CPU), a storage device (for example, ROM, RAM), an A / D converter, an input / output port, and the like, and has a configuration as a so-called computer. Various sensors such as an engine rotation speed sensor and an engine load sensor are connected to the input port (because the engine is mounted on the vehicle as a power source). Then, here, the ECU adjusts the hydraulic pressure of the supply flow path 12 according to a predetermined program according to the value detected (acquired) based on the output of the engine rotation speed sensor, the engine load sensor, or the like. Controls the operation of the control valve 44. The relief valve 10 of the first embodiment is configured to have a variable set pressure in two stages of a high set pressure state and a low set pressure state. Switching between the high set pressure state and the low set pressure state is performed by controlling the operation of the control valve 44. The switching control between the high set pressure state and the low set pressure state is executed based on the result of comparing the engine torque calculated (acquired) based on the outputs of the above various sensors with the predetermined torque. To. The predetermined torque is determined based on whether or not the engagement pressure of the clutch device CA needs to be equal to or higher than the predetermined pressure. Then, when the engine torque is a torque that requires the clutch engagement pressure to be equal to or higher than a predetermined pressure, the control valve 44 is controlled so as to be in a high set pressure state, and the engine torque determines the clutch engagement pressure. The control valve 44 is controlled so as to be in a low set pressure state when the torque may be less than the pressure. More specifically, here, the control valve 44 is de-energized when the high set pressure state is set, and the control valve 44 is energized when the low set pressure state is set. As described above, a part of the ECU functions as a valve control means configured to control the operation of the control valve 44. The ECU also controls the operation of each part such as the injector of the engine according to a predetermined program according to the engine operating state.

1 and 2 show a relief valve 10 in a state where the set pressure of the relief pressure is high, that is, in a high set pressure state, and show an operating state of the control valve 44 in the high set pressure state. 3 and 4 show a relief valve 10 in a state where the set pressure of the relief pressure is low, that is, in a low set pressure state, and show an operating state of the control valve 44 in the low set pressure state. The control valve 44 is a spool type solenoid valve provided with a supply port 44a for communicating the second introduction port 36 with the supply flow path 12 and a drain port 44b for communicating the second introduction port 36 with the drain flow path 44c. .. However, the control valve 44 may be a solenoid valve having another configuration.

In the high set pressure state of FIGS. 1 and 2, the control valve 44 is opened, and oil is introduced into the second introduction port 36 as shown by the arrow A1. Therefore, the resultant force RF of the urging force F of the coil spring 24 and the hydraulic pressure (hereinafter referred to as the closing pressure) by the oil introduced from the second introduction port 36 (pressure P1 per unit area × area of the second pressure receiving surface 22h) CP. The valve body 22 is located at a position corresponding to the balance between the hydraulic pressure due to the oil introduced from the first introduction port 34 (hereinafter, release pressure) (pressure P1 per unit area x area of the first pressure receiving surface 22e) OP. Can be moved and positioned in the internal space 32. FIG. 1 shows a relief valve 10 in a state where the release pressure OP is defeated by the resultant force RF and the valve body 22 is in a position where the valve body 22 cannot be discharged. In this state, the inflow port 38 is closed by the first diameter portion 22c of the valve body 22. FIG. 2 shows a relief valve 10 in a state where the valve body 22 is in the dischargeable position as a result of the release pressure OP winning the resultant force RF when the valve body 22 is in the dischargeable position. In this state, the inflow port 38 opens and oil can flow into the internal space through the inflow port 38, so that the inflowing oil is discharged to the upstream side of the pump 14 through the discharge port 40 (FIG. 2). See arrow A2). As described above, in the high set pressure state, the closing pressure CP is applied to the urging force F of the coil spring 48 as a force against the release pressure OP, so that the set pressure of the relief pressure becomes high.

On the other hand, in the low set pressure states of FIGS. 3 and 4, the control valve 44 is closed and no oil is introduced into the second introduction port 36. In this case, the oil that has reached the control valve 44 does not reach the second introduction port 36, while the oil that has already reached the second introduction port 36 goes from the drain flow path 44c to the oil pan 16 via the drain port 44b. Will be back. Therefore, only the urging force F of the coil spring 24 opposes the hydraulic pressure, that is, the release pressure due to the oil introduced from the first introduction port 34. FIG. 3 shows a relief valve 10 in a state where the release pressure OP is defeated by the urging force F and the valve body 22 is in a position where the valve body 22 cannot be discharged. FIG. 4 shows a relief valve 10 in a state where the valve body 22 is in the dischargeable position as a result of the release pressure OP surpassing the urging force F when the valve body is in the dischargeable position. As described above, in the low set pressure state, only the urging force F of the coil spring 24 acts on the valve body 22 as the force against the release pressure OP, so that the set pressure of the relief pressure becomes low.

As described above, the relief valve 10 according to the first embodiment has the above configuration, and in particular, the second pressure receiving surface 22h that receives the hydraulic pressure introduced through the control valve when the control valve 44 is opened is always present. It is formed so as to face the direction opposite to the first pressure receiving surface 22e that receives hydraulic pressure. The direction of the force acting on the valve body 22 from the coil spring 24 and the direction of the force acting on the valve body 22 via the second pressure receiving surface 22h are generally the same. A control valve 44 is provided so that the amount of oil introduced into the second introduction port 36 is variable. Therefore, the relief valve 10 has a configuration in which the set pressure, that is, the relief pressure is variable, and has a configuration different from that of the relief valve of Patent Document 1 in that configuration, that is, has a novel configuration.

Further, the relief valve 10 has a first pressure receiving surface 22e on the first end portion 22a side and a second pressure receiving surface 22h on the second end portion 22b side, and the second pressure receiving surface 22h is the coil spring 24. It serves as a contact surface to which one end of the coil abuts. In this way, the surface that receives the force from the coil spring 24 and the second pressure receiving surface 22h that receives the hydraulic pressure from the oil introduced through the second introduction port 36 are made the same, so that the relief valve 10 is miniaturized. Is excellent.

Further, in the relief valve 10, an inflow port 38 is provided separately from the first introduction port 34. Therefore, when the valve body 22 is in the non-discharged position, the inflow port 38 can be closed by the first diameter portion 22c of the valve body 22 having the first diameter D1 which is the maximum diameter. Therefore, in the relief valve 10, when the valve body 22 is in the non-dischargeable position, it is possible to prevent oil from being introduced into the internal space 32 through the inflow port 38, and the valve body 22 is excessive from the oil. It is possible to prevent receiving force. In the aspect of the present disclosure, the oil introduced into the internal space 32 from the first introduction port 34 is provided so that the first introduction port 34 also functions as an inflow port and the valve body is in the dischargeable position. The relief valve 10 can be modified in this way without excluding the configuration discharged from the discharge port. This also applies to the relief valve 110 of the second embodiment described below.

Next, the relief valve 110 as the hydraulic control valve according to the second embodiment will be described with reference to FIGS. 5 to 8. Hereinafter, the difference between the relief valve 10 of the first embodiment and the relief valve 110 of the second embodiment will be mainly described. Unless otherwise specified, the relief valve 110 of the second embodiment also has the same effect as the relief valve 10 of the first embodiment.

In the relief valve 110 according to the second embodiment, in the second end portion 22b positioned on the dischargeable position side of the valve body 22, the second pressure receiving surface 22h is independent of the contact surface 22j with which the coil spring 24 abuts. It is formed. A contact surface 22j is formed on the end surface 22b'of the second end portion 22b. Here, the end surface 22b'of the second end portion 22b is parallel to the second axial direction surface, that is, the second pressure receiving surface 22h, and faces the same direction (second axial direction) as the second pressure receiving surface 22h. It is formed. The coil spring 24 is arranged in the cylindrical guide portion 30a arranged in the internal space 32 in the cap member 30. The end face 22b'is circular here.

In the relief valve 110, the second pressure receiving surface 22h is formed separately from the contact surface 22j, so that the axial length of the fourth diameter portion 22g is shorter than that of the relief valve 10 of the first embodiment. This makes it possible to reduce the size of the valve body 22. On the other hand, from the viewpoint of securing the arrangement region (operating space) of the coil spring 24 in the guide portion 30a, the total length of the relief valve 110 tends to be longer than that of the relief valve 10 according to the first embodiment. The degree of reduction of the valve body 22 and the degree of reduction of the entire relief valve may be set in consideration of cost, selection design of members, and the like. This also applies to the relief valve 10 according to the first embodiment.

In the relief valve 110 according to the second embodiment, FIGS. 5 and 6 show an operating state in a state where the set pressure of the relief pressure is high, that is, a high set pressure state, and FIGS. 7 and 8 show the set pressure of the relief pressure. Indicates a low state, that is, an operating state in a low set pressure state. 5 and 7 show a state in which the valve body 22 is in a non-dischargeable position, and FIGS. 6 and 8 show a state in which the valve body 22 is in a dischargeable position. The oil flow in each state of FIGS. 5 to 8, the control of the control valve 44, and the like are as described with respect to the relief valve 10 of the first embodiment based on FIGS. 1 to 4, so that the description thereof will be described. Omit.

Although the techniques of the present disclosure have been described above based on the two embodiments, the techniques of the present disclosure are not limited to those embodiments. For example, the first pressure receiving surface and the second pressure receiving surface are not limited to being formed so as to face opposite to each other, and the first pressure receiving surface is from the hydraulic oil introduced into the internal space from the first introduction port. It can be changed to have various configurations that can receive the force from the non-dischargeable position side to the dischargeable position side, and the second pressure receiving surface can be discharged from the hydraulic oil introduced into the internal space from the second introduction port. It can be changed to have various configurations that can receive a force from the position side to the non-dischargeable position side. Specifically, the first pressure receiving surface and the second pressure receiving surface, respectively, were planes orthogonal to the axis of the valve body or the axis of the internal space of the relief valve in the above embodiment, but were inclined diagonally to them. It can also be a face.

Further, a plurality of second introduction ports may be provided, and a second pressure receiving surface may be provided for each second introduction port to configure a relief valve so that the set pressure can be switched and set in three or more stages. In that case, the second introduction port additionally provided may be formed in the valve body in the same manner as the inflow port. Then, the additional pressure receiving surface that receives hydraulic pressure from the oil introduced from the second introduction port provided additionally is formed by providing the valve body with an additional diameter portion having a diameter shorter than the maximum diameter. be able to.

Although the typical embodiment of the technique of the present disclosure has been described above, the technique of the present disclosure can be changed in various ways. Various substitutions and modifications are possible without departing from the spirit and scope of the present disclosure as defined by the claims of the present application.

10, 110 Relief valve 12 Supply flow path 14 Oil pump 16 Oil pan 18 Suction flow path 20 Valve body 22 Valve body 24 Coil spring 26 Introductory amount variable device 28 Body body 30 Cap member 32 Internal space 34 First introduction port 36 Second Introductory port 38 Inflow port 40 Discharge port 42 Depressurization hole 44 Control valve

Claims (2)

It ’s a hydraulic control valve.
The internal space of the hydraulic control valve is partitioned, and the inflow port, the first introduction port and the second introduction port capable of introducing hydraulic oil into the internal space, and the operation of flowing into the internal space through the inflow port. A valve body and a valve body, which partitions and has an accommodating part with a discharge port capable of discharging oil.
A valve body movably arranged in the internal space in the longitudinal direction of the hydraulic control valve, the first position in the longitudinal direction in which hydraulic oil flowing from the inflow port can be discharged from the discharge port, and the said. A valve body and a valve body, in which hydraulic oil flowing from the inflow port cannot be discharged from the discharge port and is movable in the longitudinal direction between the first position and the second position farther from the accommodating portion.
An urging member housed in the accommodating portion and configured to urge the valve body from the first position side to the second position side.
It is provided with an introduction amount variable device configured to make the introduction amount of hydraulic oil into the second introduction port variable.
The valve body is
A first diameter portion having a cylindrical shape and a first diameter larger than the inner diameter of the accommodating portion,
A second diameter portion having a diameter smaller than the first diameter,
It has a cylindrical shape, is coupled to the accommodating portion side of the first diameter portion, has a diameter smaller than that of the first diameter portion, and is accommodated in the accommodating portion by the urging member. A protrusion urged from the 1st position side to the 2nd position side,
A first pressure receiving surface configured to receive a force from the hydraulic oil introduced into the internal space from the first introduction port toward the first position side.
A second pressure receiving surface configured to receive a force from the hydraulic oil introduced into the internal space from the second introduction port toward the second position side, and the protrusion on the first diameter portion. The second pressure receiving surface, which is the surface of the area where the portion is not provided,
Have,
When the valve body is in the second position in the internal space, the inflow port is closed at the first diameter portion.
When the valve body is in the first position in the internal space, the inflow port is connected to the discharge port via the periphery of the second diameter portion.
Hydraulic control valve. The hydraulic control valve according to claim 1, wherein the first pressure receiving surface is formed so as to face the direction opposite to the second pressure receiving surface.

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