JP2012202508A - Pressure control device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a pressure control device that can be equipped with functions of a pressure sensor and relief valve without causing increase of the number of parts and increase of the size thereof.SOLUTION: This pressure control device includes: a sensor body having a sensor part which converts a detected fluid pressure to an electrical signal to output it from a terminal; a first member having a housing part for housing the sensor body; a second member in which a flow passage is formed, and which has an opening for providing communication between the flow passage and housing part; an elastic member which biases the sensor body toward the second member; a seal part 104a which is provided in the sensor body, and seals a space between the flow passage and housing part by bringing the elastic member into abutment with the second member while surrounding the sensor part and the opening; and a drain passage formed in the housing part.

Description

  The present invention relates to a pressure control device that controls fluid pressure.

  Conventionally, Patent Document 1 discloses a configuration in which a control valve unit of an automatic transmission includes a hydraulic pressure sensor and a relief valve. The relief valve has a function of reducing the pressure by forcibly opening when the hydraulic pressure in the corresponding oil passage is equal to or higher than a predetermined value.

JP 2006-161850 A

However, the technique described in Patent Document 1 has a problem that no specific arrangement or the like is disclosed. In general, the pressure sensor and the relief valve are individually provided for the corresponding oil passage of the valve body of the control valve unit. In this case, not only the number of parts is increased, but also an arrangement space has to be secured, which causes a problem of increasing the cost and increasing the size.
The present invention has been made paying attention to the above-described problems, and an object of the present invention is to provide a pressure control device in which a pressure sensor and a relief valve can be arranged without causing an increase in the number of parts or an increase in size.

  In order to achieve the above object, according to the present invention, a sensor main body having a sensor unit that converts a detected fluid pressure into an electrical signal and outputs the electric signal, and a first member having a mounting unit for mounting the sensor main body, A second member having an opening that communicates the flow channel and the housing portion, an elastic member that urges the sensor body toward the second member, and the sensor A seal portion that is provided in the main body, surrounds the sensor portion and the opening, and seals between the flow path and the collection portion by contacting the second member by the elastic member; And a drain channel formed in the mounting portion.

  That is, the fluid pressure in the flow path is detected by the sensor unit, and when the fluid pressure is excessive, the sensor body is pushed up against the urging force of the elastic member, and the fluid in the flow path flows out from the gap of the seal part. Then, the fluid is discharged from the drain flow path formed in the collecting portion. As described above, the sensor body, the elastic member, the seal portion, and the drain flow path can perform both functions of the pressure sensor and the relief valve. Compared to the case where the pressure sensor and the relief valve are provided individually, Miniaturization can be achieved while suppressing the number of parts of the control device.

It is the schematic showing the structure of the power train of the vehicle to which the pressure control apparatus of Example 1 was applied. FIG. 3 is a top view of the vicinity of a hydraulic sensor installation position in the first valve body of the first embodiment. FIG. 3 is a partially enlarged cross-sectional view of the first valve body according to the first embodiment near a hydraulic sensor installation position. It is a figure showing the structure of the hydraulic sensor of Example 1. FIG. FIG. 3 is a diagram illustrating a configuration of a first valve body according to the first embodiment. It is the schematic showing the relief valve function of the hydraulic pressure sensor of Example 1. FIG.

  FIG. 1 is a schematic diagram illustrating a configuration of a power train of a vehicle to which the pressure control device according to the first embodiment is applied. The driving force of the engine 1 as a power source is transmitted to the automatic transmission 2 and drives driving wheels (not shown) via the transmission output shaft 7. The driving force of the engine 1 input into the automatic transmission 2 is input into the transmission mechanism 5 via the torque converter 3. The oil pump 4 is also driven by the driving force of the engine 1. A control valve unit 6 is mounted below the transmission mechanism 5, and the hydraulic pressure boosted by the oil pump 4 is appropriately adjusted and supplied to various hydraulic actuators in the transmission mechanism 5. The corresponding gear ratio is achieved. The various hydraulic actuators include a friction engagement element when the speed change mechanism 5 is a stepped automatic transmission, and a pulley and a forward / reverse switching mechanism when the speed change mechanism 5 is a belt type continuously variable transmission. Moreover, even if it is the structure of another automatic transmission, if a hydraulic actuator is provided, application of a pressure control apparatus will not be specifically limited.

  The control valve unit 6 (corresponding to a pressure control device) includes a first valve body 61 (corresponding to a first member) in which an oil passage and a valve housing part are formed on one side surface, and the same as the first valve body 61 In addition, an oil passage, a valve housing portion, and the like are formed on one side surface, and a second valve body 62 (second member) that is assembled to face the oil passage forming surface of the first valve body 61 is provided. The first valve body 61 and the second valve body 62 are fastened and fixed by a plurality of bolts not shown. Above the first valve body 61, a control board 63 that transmits and receives electrical signals to and from solenoids and sensors provided in the valve body is attached. In the first valve body 61, the hydraulic pressure sensor 10 for detecting the hydraulic pressure in the oil passage 62a (corresponding to the flow passage) formed in the second valve body 62 is housed.

  FIG. 2 is a top view of the vicinity of the hydraulic sensor installation position in the first valve body of the first embodiment, and FIG. 3 is a partially enlarged sectional view of the vicinity of the hydraulic sensor installation position in the first valve body of the first embodiment. 4 is a diagram illustrating the configuration of the hydraulic sensor according to the first embodiment, and FIG. 5 is a diagram illustrating the configuration of the first valve body according to the first embodiment. In the following description, the control board side in FIG. 3 will be described as “upper” and the second valve body 62 side will be described as “lower”.

  The hydraulic sensor 10 is a terminal 101 that transmits and receives electrical signals to and from the control board 63, a sensor unit 100a that converts detected pressure into an electrical signal, and a sensor body that holds the terminals 101 and the sensor unit 100a. And a cylindrical portion 102. The terminal 101 has three pins arranged in series, is urged upward by a coil spring (not shown), and is in contact with and electrically connected to a terminal contact portion 63 a formed on the control board 63. The terminal 101 is not limited to electrical connection by contact, but may be connected by soldering, and the terminal itself may be provided with an elastic force by forming a bent portion or the like.

  The oil pressure sensor 10 is housed in the housing portion 610 of the first valve body 61 and is biased downward by the wave washer 11, while being upwardly lifted by a separate plate 64 and a second valve body 62 from a seal portion 104a described later. It is assembled in a pressed state. Details will be described later. The wave washer 11 is a disc spring that is deformed so as to wave within a predetermined height range x2 in the circumferential direction, and is an elastic member that can generate an equal pressing force in the circumferential direction.

  The separate plate 64 is interposed between the first valve body 61 and the second valve body 62, and when the oil passage formed in each body is connected, the sealing performance of the oil passage is ensured, If necessary, the diameter of the through hole is adjusted to function as an orifice. In the first embodiment, a pressure detection sensor through hole 64 a (corresponding to an opening) is formed at a position corresponding to the hydraulic sensor 10 of the separate plate 64. The sensor through hole 64a opens to the line pressure oil passage 62a having the highest pressure in the second valve body 62, and detects the oil pressure in the line pressure oil passage 62a.

  4A is a top view of the hydraulic sensor 10, FIG. 4B is a front view of the hydraulic sensor 10, FIG. 4C is a side view of the hydraulic sensor 10, and FIG. 4D is a first view of the hydraulic sensor. It is the schematic which shows the relationship between a 2nd rotation prevention part and a wave washer. The hydraulic sensor 10 includes a cylindrical portion 102 having a cylindrical shape, a large-diameter enlarged portion 103 formed so as to protrude from the side surface below the cylindrical portion 102, and an enlarged diameter having substantially the same diameter as the cylindrical portion 102. An annular drain oil passage groove constituting portion 104 extending downward from the diameter portion 103 and a first portion erected along the axis of the cylindrical portion 102 on the outer periphery of the cylindrical portion 102 and on the terminal side of the enlarged diameter portion 103. It has a first detent portion 105 and a second detent portion 106. The circumferential width of the first detent portion 105 is y1, and the circumferential width of the second detent portion 106 is y2 (<y1). As a result, rotation of the hydraulic sensor 10 is restricted, and erroneous assembly during assembly to the storage unit 610 is prevented.

  Below the cylindrical portion 102 is a hollow cylindrical shape, and a sensor portion 100a is installed in the upper portion of the hollow, and detects the pressure of oil flowing into the hollow. An annular seal portion 104 a is formed at the lower end of the annular drain oil passage groove constituting portion 104. The innermost diameter position of the seal portion 104a is smaller than the sensor through hole 64a. A seal surface is formed by contact between the separate plate 64 and the hydraulic sensor 10. The axial length from the upper surface 103a of the enlarged diameter portion 103 to the seal portion 104a, that is, the total thickness xa of the enlarged diameter portion 103 and the thickness xb of the cylindrical portion protruding downward from the enlarged diameter portion 103 is x1. It is said that.

  As shown in FIG. 4D, the first anti-rotation portion 105 and the second anti-rotation portion 106 are formed with a screw shape. This is a configuration for easily assembling the wave washer 11 to the hydraulic sensor 10. When the wave washer 11 is put on and screwed from above the hydraulic sensor 10, the wave washer 11 is gradually moved downward, and the first anti-rotation portion 105 and It is captured so as to be movable in the axial direction between the second detent portion 106 and the enlarged diameter portion 103. As a result, the hydraulic sensor 10 and the wave washer 11 are integrated without falling off, and the assembling property is improved. In the drawings other than FIG. 4D, the illustration of the screw shape is omitted.

  FIG. 5A is a top view of the vicinity of the housing portion of the first valve body 61, FIG. 5B is a partial enlarged cross-sectional view taken along the line CC in the vicinity of the housing portion, and FIG. It is a bottom view. The receiving portion 610 of the first valve body 61 is connected to the cylindrical through hole 61b penetrating from the lower surface to the upper surface of the first valve body 61, and communicates with the through hole 61b and is engaged with the first detent portion 105. The first engagement groove 61d1 for restricting the rotation about the axis of the hydraulic sensor 10 and the through hole 61b and the second anti-rotation portion 106 are engaged to rotate about the axis of the hydraulic sensor 10. And a second engagement groove 61e1 for restricting the movement. These engaging grooves have substantially the same circumferential width as the respective rotation stoppers, and have a relationship of the width of the first engaging groove 61d1> the second engaging groove 61e1. A combination of the first detent portion 105 and the first engagement groove 61d1 constitutes a first engagement mechanism, and a combination of the second detent portion 106 and the second engagement groove 61e1 constitutes a second engagement mechanism. ing.

  Further, below the through hole 61b, there is an enlarged cylindrical portion 61c1 having an axial length x3 that accommodates the enlarged diameter portion 103, and a retaining surface 61c2 is provided at the step portion between the through hole 61b and the enlarged cylindrical portion 61c1. Is formed. An annular drain oil passage 61b is formed by a closed space formed by the inner wall of the enlarged cylindrical portion 61c1, the outer peripheral wall of the annular drain oil passage groove constituting portion 104, and the lower surface of the enlarged diameter portion 103. The first engagement groove 61d1 extends to the outer peripheral surface of the enlarged cylindrical portion 61c1 with the same width, and further toward the outer periphery, the width is narrower than the first engagement groove 61d1, that is, the second engagement groove 61e1. A first drain oil passage groove 61d2 having a substantially equal width is formed. Similarly, the second engagement groove 61e1 is also extended to the outer peripheral surface of the enlarged cylindrical portion 61c1 with the same width, and further toward the outer periphery, the second drain oil passage groove having substantially the same width as the second engagement groove 61e1. 61e2 is formed. The first drain oil passage groove 61d2 and the second drain oil passage groove 61e2 are formed to penetrate from the lower surface to the upper surface of the first valve body 61 and communicate with the annular drain oil passage 61c.

  Next, the procedure for mounting the hydraulic sensor 10 in the control valve unit 6 will be described. First, the wave washer 11 is attached to the hydraulic sensor 10. At this time, the total height (x1 + x2) of the axial length x1 from the upper surface 103a of the enlarged diameter portion 103 to the seal portion 104a and the height range x2 where the wave washer 11 exists is the enlarged cylinder of the housing portion 610. It is longer than the axial length x3 of the part 61c1.

  Next, with respect to the housing portion 610 of the first valve body 61, the first and second detent portions 105 and 106 and the first and second engagement grooves 61d1 and 61e1 are engaged from below with the hydraulic sensor. 10 is inserted, and the retaining surface 61c2 of the receiving portion 610 and the wave washer 11 are brought into contact with each other. Next, the separate plate 64 is assembled by being sandwiched between the lower surface of the first valve body 61 and the upper surface of the second valve body 62, and both bodies are fixed by bolting.

  At this time, the seal portion 104a of the hydraulic sensor 10 is in a state of protruding from the lower surface of the first valve body 61 at the beginning of assembly ((x1 + x2)> x3), and the wave washer 11 is elastically deformed by being pressed by the separate plate 64. . A predetermined load acts between the hydraulic sensor 10 and the separate plate 64 by this elastic force, and this corresponds to the set relief pressure.

  Next, the operation will be described. FIG. 6 is a schematic diagram illustrating a relief valve function of the hydraulic sensor according to the first embodiment. A control hydraulic pressure for controlling the speed change mechanism 5 acts in the oil passage 62a. Here, when the number of revolutions of the engine 1 changes suddenly and the discharge amount of the oil pump 4 rapidly increases, or because of a delay in the operation of the control valve, the instantaneously extremely high hydraulic pressure (hereinafter referred to as surge pressure and May occur). The generation of the surge pressure causes a decrease in control quality, and may cause an impact on each component part, which causes a decrease in durability. Therefore, a relief valve is generally provided, and when a hydraulic pressure higher than the set relief pressure is generated from the relief valve, the surge pressure is reduced by draining. However, when the relief valve is configured separately, it increases the number of parts and hinders the downsizing of the space. Therefore, in the first embodiment, the relief function is set in the hydraulic pressure sensor 10.

  When surge pressure is generated in the oil passage 62a, a high pressure acts in the hollow in the cylindrical portion 102. When this high pressure exceeds the set relief pressure, the hydraulic sensor 10 itself is pushed upward. As a result, the seal is released from the state in which the space between the hydraulic sensor 10 and the separate plate 64 is sealed by the seal portion 104a by the pressing force of the wave washer 11. Then, oil flows from the oil passage 62a into the annular drain oil passage 61c. Oil flows out from the annular drain oil passage 61c into the first drain oil passage groove 61d2 and the second drain oil passage groove 61e2, and is discharged from the upper side of the first valve body 61. At this time, since the cross-sectional areas of the first drain oil passage groove 61d2 and the second drain oil passage groove 61e2 are substantially the same, when the oil flows out, it flows out equally on the left and right. Thereby, the hydraulic pressure acts on the hydraulic sensor 10 in a well-balanced manner, and a stable relief valve function can be exhibited without causing the hydraulic sensor 10 to generate an unnecessary inclination.

As described above, the effects listed below can be obtained in the first embodiment.
(1) The first valve body 61 (first member) having a sensor main body having a sensor unit 100a that converts the detected fluid pressure into an electrical signal and outputs the electric signal from the terminal 101, and an accommodation unit 610 that accommodates the sensor main body. ), A separation plate 64 and a second valve body 62 (second member) in which a flow path 62a, a sensor through-hole 64a (opening) are formed, and a cylindrical portion 102 which is a sensor body are separated into a separation plate 64 (second A wave washer 11 (elastic member) that is pressed toward the member) by an elastic force, and a sensor body that surrounds the sensor portion 100a and the sensor through-hole 64a, and is separated by the wave washer 11 (elastic member). A seal portion 104a that seals between the sensor through-hole 64a and the receiving portion 610 by contacting the second member); Annular drain oil passage 61c which communicates with the section 610, a first drain oil passage grooves 61d2 and the second drain oil passage grooves 61E2 (drain passage), with a.

  That is, the fluid pressure in the flow path is detected by the sensor unit 100a, and when the fluid pressure is excessive, the sensor body is pushed up against the urging force of the wave washer 11, and the gap in the seal part 104a The fluid flows out, and the fluid is discharged from the drain flow path formed in the storage unit 610. Thus, it becomes possible to fulfill both functions of the pressure sensor and the relief valve, and it is possible to achieve downsizing while suppressing the number of parts of the pressure control device as compared with the case where the pressure sensor and the relief valve are individually provided. it can.

  (2) The sensor body includes a cylindrical portion 102 having a cylindrical shape and a large-diameter enlarged portion 103 formed to protrude from the side surface of the cylindrical portion 102, and the seal portion 104 a is a separate part of the cylindrical portion 102. The wave washer 11 is a leaf spring interposed between the collecting portion 610 and the enlarged diameter portion 103 and formed on the end surface on the plate side. Therefore, the function of the relief valve can be exhibited with a simple configuration.

  (3) The terminal 101 is provided on the end surface opposite to the end surface of the cylindrical portion 102 on which the seal portion 104a is formed. Therefore, a stable electrical connection can be ensured by pressing the terminal 101 against the terminal contact portion 63a.

  (4) The outer periphery of the cylindrical portion 102 and on the terminal 101 side with respect to the enlarged diameter portion 103 are formed on the anti-rotation portions 105 and 106 erected along the axis of the cylindrical portion 102 and the receiving portion 610. Engaging grooves 61d1 and 61e1 that engage with the stoppers 105 and 106 and restrict rotation about the axis of the cylindrical part 102 are provided. Therefore, the rotation of the hydraulic sensor can be prevented.

  (5) The engagement mechanism including the rotation stopper and the engagement groove includes a first engagement mechanism including a first rotation stopper 105 and a first engagement groove 61d1 at two opposing positions on the outer periphery of the cylindrical portion, The second anti-rotation portion 106 and the second engagement mechanism including the second engagement groove 61e1 are included, and the circumferential width y1 of the first engagement mechanism is larger than the circumferential width y2 of the second engagement mechanism. Is also big. Therefore, it is possible to prevent erroneous assembly when the hydraulic sensor 10 is mounted on the receiving portion 610 of the first valve body 61.

  (6) The drain flow path includes a first drain flow path 61d2 formed by extending the radial depth of the first engagement groove 61d1 to the outer peripheral side from the enlarged diameter portion 103, and the second engagement groove 61e1. A second drain passage 61e2 formed to extend to the outer peripheral side of the enlarged diameter portion 103 with substantially the same circumferential width as the first engagement groove 61d1. Therefore, the flow passage cross-sectional areas of the drain flow passages can be made substantially the same, and it becomes possible to prevent the inclination by maintaining the balance of the hydraulic pressure acting on the hydraulic pressure sensor 10, and exhibit a stable relief valve function. At the same time, the influence on the terminal 101 can be suppressed.

  (7) The valve body includes a second valve body 62 in which a groove for fluid flow is formed, and a separate plate 64 that covers the groove of the second valve body 62 to form a flow path, and passes through the sensor. The hole 64 a is a through hole provided in the separate plate 64. Therefore, the sensor body can be assembled while being pressed by the separate plate 64, and the ease of assembly can be secured. Further, since the sensor through hole 64a is provided in the separate plate 64, the oil pressure can be detected with a simple oil passage configuration without forming a new oil passage in the valve body.

Although the first embodiment has been described above, other configurations are also included in the present invention. For example, in the first embodiment, an example is shown in which the present invention is applied to a hydraulic sensor mounted on a control valve unit of an automatic transmission, but the present invention can be similarly applied to a control valve unit in other hydraulic equipment.
Further, in the first embodiment, the example in which the rotation preventing portion is integrally formed with the hydraulic sensor main body is shown, but it may be configured as a separate member and attached to the hydraulic sensor.
In the first embodiment, the wave washer is used as the elastic member. However, the wave washer may be urged by another disc spring or a plurality of coil springs.

6 Control valve unit 10 Hydraulic sensor 11 Wave washer (biasing member)
61 First valve body 61b Through hole 61c Toroidal drain oil passage 61c1 Enlarged cylindrical portion 61c2 Retaining surface 61d1 First engagement groove 61d2 First drain oil passage groove 61e1 Second engagement groove 61e2 Second drain oil passage groove 62 Second Valve body 62a Oil passage 63 Control board 63a Terminal contact portion 64 Separate plate 64a Sensor through hole (oil passage)
101 Terminal 102 Cylindrical portion 103 Diameter expanding portion 104 Annular drain oil passage groove constituting portion 104a Seal portion 105 First detent portion 106 Second detent portion 610 Containment portion

Claims (7)

A sensor body having a sensor unit that converts the detected fluid pressure into an electrical signal and outputs the electrical signal;
A first member having a receiving portion for receiving the sensor body;
A second member having a flow path and an opening communicating the flow path and the receiving portion;
An elastic member that biases the sensor body toward the second member;
A seal part that is provided in the sensor body, surrounds the sensor part and the opening, and seals between the flow path and the housing part by contacting the second member by the elastic member;
A drain passage formed in the storage section;
A pressure control device comprising: The pressure control device according to claim 1,
The sensor main body has a cylindrical portion having a cylindrical shape, and a large-diameter enlarged portion formed to protrude from the side surface of the cylindrical portion,
The seal portion is formed on an end surface of the cylindrical portion on the second member side,
The pressure control device according to claim 1, wherein the elastic member is a leaf spring interposed between the housing portion and the enlarged diameter portion. The pressure control device according to claim 1 or 2,
The pressure control device according to claim 1, wherein the terminal is provided on an end surface opposite to an end surface of the cylindrical portion where the seal portion is formed. The pressure control device according to claim 3.
An outer periphery of the cylindrical portion, and on the terminal side of the enlarged diameter portion, a detent portion erected along the axis of the cylindrical portion;
An engagement groove that is formed in the housing portion and engages with the rotation preventing portion and restricts rotation about the axis of the cylindrical portion;
A pressure control device comprising: The pressure control device according to claim 4.
The engagement mechanism including the rotation stopper and the engagement groove includes a first engagement mechanism including a first rotation stopper and a first engagement groove at two opposing positions on the outer periphery of the cylindrical portion, and a second rotation. It is composed of a stop and a second engagement mechanism comprising a second engagement groove,
The pressure control device according to claim 1, wherein a circumferential width of the first engagement mechanism is larger than a circumferential width of the second engagement mechanism. The pressure control device according to claim 5,
The drain channel includes a first drain channel formed by extending a radial depth of the first engagement groove to an outer peripheral side of the enlarged diameter portion, and the second engagement groove. A pressure control device comprising: a second drain channel formed so as to extend to the outer peripheral side with respect to the enlarged diameter portion with substantially the same circumferential width as the engagement groove. In the pressure control device according to any one of claims 1 to 6,
The second member includes a valve body in which a groove through which the fluid flows is formed, and a separate plate that covers the groove of the valve body to form the flow path,
The pressure control device according to claim 1, wherein the opening is a through hole provided in the separate plate.

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