JP2014234829A - Hydraulic control apparatus - Google Patents

Abstract

PROBLEM TO BE SOLVED: To downsize a hydraulic control apparatus configured so as to share one body by a plurality of valves.SOLUTION: A hydraulic control apparatus 10 includes: a regulator valve 12 for reducing initial hydraulic pressure (line pressure) caused by hydraulic oil; a solenoid valve 14 for converting the reduced hydraulic pressure into solenoid pressure; and a control valve 16 for converting the line pressure caused by the hydraulic oil to driving pressure corresponding to the solenoid pressure. These three valves 12, 14, 16 share one body 54 and are parallel-arranged in parallel along a horizontal direction so that axial lines are parallel with each other. The regulator valve 12 is arranged between the solenoid valve 14 and the control valve 16.

Description

  The present invention relates to a hydraulic control device that obtains a driving pressure for controlling a clutch or the like from an initial hydraulic pressure (line pressure) by hydraulic oil input from an input port.

  As a hydraulic control device for a clutch mounted on an automobile, one described in Patent Document 1 is known. This hydraulic control device has a differential clutch control valve and a solenoid modulator valve as pressure regulating valves, and one solenoid valve. In this configuration, the initial hydraulic pressure (line pressure) due to the hydraulic oil is reduced to a predetermined pressure by the solenoid modulator valve, and this reduced hydraulic pressure is supplied to the linear solenoid valve.

  The linear solenoid valve generates a solenoid pressure based on the current supplied to the solenoid, and this solenoid pressure is supplied to the differential clutch control valve. The differential clutch control valve converts the line pressure based on the solenoid pressure and supplies hydraulic oil to the clutch as a predetermined clutch pressure (drive pressure).

  In Patent Document 1, for the three valves functioning as described above, a differential clutch control valve and a solenoid modulator valve are arranged in parallel with each other in a valve body configured by combining a lower valve body and an upper valve body. In addition, it has been proposed that the linear solenoid valve be arranged between the two pressure regulating valves in such a posture that its axial direction is orthogonal to the two pressure regulating valves. The hydraulic oil passage is provided in the upper valve body.

JP-A-5-345528

  Although Patent Document 1 has a description that three valves are provided in one valve body, the valve body is a combination of two members vertically as described above. In addition, the linear solenoid valve extends in a direction orthogonal to the two pressure regulating valves, that is, in the stacking direction of the lower valve body and the upper valve body.

  For this reason, in the technique of patent document 1, the malfunction that it is difficult to make the dimension (thickness) along a lamination direction small is obvious.

  The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a hydraulic control device that employs a valve arrangement that can be miniaturized.

In order to achieve the above object, a hydraulic control device according to the present invention includes a first pressure regulating valve for reducing an initial hydraulic pressure by hydraulic oil input from an input port;
A solenoid valve for converting the hydraulic pressure reduced by the first pressure regulating valve into a solenoid pressure corresponding to a current supplied to the solenoid;
A second pressure regulating valve that is supplied with the solenoid pressure and converts an initial hydraulic pressure by hydraulic fluid input from the input port into a driving pressure corresponding to the solenoid pressure;
Have
One body is formed with a first valve hole, a second valve hole, and a third valve hole in which axes are arranged in parallel along the horizontal direction, and the first valve hole, the second valve hole, and In each of the third valve holes, a first valve rod of the first pressure regulating valve, a second valve rod of the solenoid valve, and a third valve rod of the second pressure regulating valve are accommodated so as to be capable of reciprocating,
The first valve hole is interposed between the second valve hole and the third valve hole, and the first pressure regulating valve is disposed between the solenoid valve and the second pressure regulating valve. It is characterized by that.

  In other words, in this hydraulic control device, the three valves are arranged in parallel so that their axes are parallel along the horizontal direction. For this reason, in the hydraulic control device, the dimension in a direction other than the axial direction of the valve can be reduced. That is, it is possible to reduce the size of the hydraulic control device.

  In addition, since the first pressure regulating valve is disposed in the center and the solenoid valve is adjacent to the first pressure regulating valve, the outlet of the first valve hole and the inlet of the second valve hole are provided in the body. Can be close. That is, the oil path connecting the first pressure regulating valve and the solenoid valve can be shortened.

  Moreover, the 1st pressure regulation valve and the 2nd pressure regulation valve are adjacent. The first pressure regulating valve and the second pressure regulating valve are supplied with high-pressure hydraulic oil, but the first hydraulic pressure valve and the second pressure regulating valve are adjacent to each other so that the hydraulic oil inlet of the first valve hole is provided. It is also possible to shorten the length of the oil passage connected to the hydraulic oil inlet of the third valve hole.

  The fact that the oil passage can be shortened as described above also contributes to downsizing of the hydraulic control device. In addition, since the oil passage is shortened, the hydraulic oil quickly circulates in the body and reaches the downstream valve. For this reason, the response speed of each valve improves.

  The body is formed with a plurality of fastening member insertion holes for passing fastening members (for example, connecting bolts) for attaching the body to a predetermined member. Here, in the present invention, as described above, the first pressure regulating valve and the second pressure regulating valve to which high pressure hydraulic oil is supplied are adjacent to each other. Therefore, it is preferable to reduce the separation distance (pitch) of the fastening member in the vicinity of the first valve hole and the third valve hole. Thereby, the surface pressure in the vicinity of the first valve hole and the third valve hole, which are high pressures, is increased, so that the sealing performance can be ensured. For this purpose, the distance between the fastening member insertion holes may be reduced in the vicinity of the first valve hole and the third valve hole.

  Since the solenoid valve (second valve hole) side has a relatively low pressure, the hydraulic oil is difficult to leak. For this reason, when sufficient sealing performance can be ensured, the distance between the fastening member insertion holes may be increased in the vicinity of the second valve hole.

  The body further includes an output flow path for leading the hydraulic oil that has been driven to the drive pressure from the third valve hole, and an output port that is connected to the downstream side of the output flow path and opens at the end face of the body. . Here, it is preferable that the output flow path is formed in a straight line so as to extend from the output port along the thickness direction of the body and is orthogonal to the third valve hole.

  In this case, the hydraulic oil led out from the third valve hole can be led out of the body via the output flow path and the output port extending along the thickness direction of the body. That is, it is not necessary to provide an oil passage for circulating the hydraulic oil led out from the third valve hole on the end face of the body. For this reason, it becomes possible to shorten the output flow path. Of course, this also contributes to downsizing of the hydraulic control device.

  In addition, since the output flow path can be shortened, it is possible to improve the pressure responsiveness in a downstream device (for example, a clutch) connected to the output port.

  By the way, when an orifice is provided in the input flow path, it is necessary to make the input flow path sufficiently long. This is because an orifice cannot be provided if the input flow path is short. However, for this reason, the input flow path becomes longer, and the body becomes larger correspondingly.

  Therefore, the input flow path connected to the downstream side of the input port extends linearly along the thickness direction of the body, communicates with the body, communicates with the input flow path, and supplies initial hydraulic pressure to the first valve hole. An oil passage having a first valve hole line pressure inlet for introducing the hydraulic oil and a third valve hole line pressure inlet for introducing the hydraulic oil of the initial hydraulic pressure into the third valve hole, It is preferable that the input flow path and the oil path communicate with each other via a communication path inclined with respect to the thickness direction of the body.

  The inclined communication path can reduce the length of the body in the thickness direction as compared with, for example, a case where a lateral hole extending along the axial direction is formed. Accordingly, the body can be prevented from becoming large.

  In this configuration, a filter is provided at the input port, and an orifice for restricting the flow rate of the hydraulic oil is provided in the communication path. That is, the orifice is disposed on the downstream side of the filter (in other words, the filter is disposed on the upstream side of the orifice).

  Since the flow path area is narrowed by the orifice, the flow speed of the hydraulic oil after passing through the orifice is higher than before passing through the orifice. Here, in the above configuration, the hydraulic oil whose flow rate has increased does not come into contact with the filter. This is because the filter is disposed on the upstream side of the orifice. Therefore, an excessive load does not act on the filter.

  The body has a first valve hole outlet for deriving the reduced hydraulic oil from the first valve hole, and a hydraulic oil derived from the first valve hole outlet for introducing the hydraulic oil into the second valve hole. It is preferable to provide an oil passage in which the second valve hole inlet is formed. In this case, it is not necessary to produce the member provided with the oil passage separately from the body. Therefore, the configuration of the hydraulic control device is simplified.

  The first valve hole (first pressure regulating valve) and the second valve hole (solenoid valve) are adjacent to each other. Therefore, the oil passage in which the first valve hole outlet and the second valve hole inlet are formed can be formed in a linear shape. Also in this case, the oil passage can be shortened, and the hydraulic control device can be downsized.

  For the same reason as described above, a second valve hole outlet for deriving hydraulic oil having a solenoid pressure from the second valve hole and a hydraulic oil derived from the second valve hole outlet are supplied to the body. It is more preferable to provide an oil passage formed with a solenoid pressure inlet for introduction into the three valve holes.

  According to the present invention, the first pressure regulating valve for reducing the initial hydraulic pressure (line pressure) by the hydraulic oil, the solenoid valve for converting the reduced hydraulic pressure to the solenoid pressure, and the line pressure by the hydraulic oil according to the solenoid pressure. The hydraulic pressure control device is configured such that the second pressure regulating valves that convert to the driving pressure are arranged in parallel along the horizontal direction so that the axes of the valves are parallel to each other. With such an arrangement, in the hydraulic control device, directions other than the axial direction of each valve can be shortened.

  Moreover, the solenoid valve and the second pressure regulating valve are arranged so as to sandwich the first pressure regulating valve. For this reason, the oil passage for supplying the line pressure to the first pressure regulating valve and the second pressure regulating valve and the oil passage for supplying the hydraulic oil derived from the first pressure regulating valve to the solenoid valve are shortened. You can also plan. This also contributes to downsizing of the hydraulic control device.

1 is a system diagram of a hydraulic control apparatus according to an embodiment of the present invention. It is a horizontal cross-sectional perspective view of the said hydraulic control apparatus. It is a top view by the side of the open end surface of the body which comprises the said hydraulic control apparatus. FIG. 4 is a cross-sectional view taken along line IV-IV in FIG. 3. FIG. 5 is a cross-sectional view taken along line VV in FIG. 3. FIG. 6 is a sectional view taken along line VI-VI in FIG. 3. It is a VII-VII line arrow directional cross-sectional view in FIG. It is a VIII-VIII line arrow directional cross-sectional view in FIG. It is a principal part longitudinal cross-sectional view of the relief valve vicinity. It is a top view by the side of the closure end face of the body. It is a principal part enlarged plan view by the side of the closure end surface of the body.

  Preferred embodiments of the hydraulic control apparatus according to the present invention will be described below in detail with reference to the accompanying drawings.

  FIG. 1 shows a system diagram of a hydraulic control apparatus 10 according to the present embodiment. The hydraulic control device 10 includes a regulator valve 12 (first pressure regulating valve), a solenoid valve 14, and a control valve 16 (second pressure regulating valve). The hydraulic oil is under the action of an oil pump (not shown). Are input from the input port 18 to the regulator valve 12 and the control valve 16 from the first oil passage 20.

  The regulator valve 12 functions to reduce the initial hydraulic pressure (line pressure) due to the hydraulic oil input from the input port 18 to a predetermined pressure. That is, the first valve rod 22 constituting the regulator valve 12 is elastically urged in the first valve hole 24 by the first pressure regulating spring 26 so that the regulator valve 12 is closed. The first valve rod 22 can reciprocate in the first valve hole 24 in accordance with the magnitude of the difference between the first pressure regulating spring 26 and the feedback hydraulic pressure acting on the regulator valve 12. The first valve rod 22 stops at a position where the first pressure regulating spring 26 and the feedback hydraulic pressure acting on the first valve rod 22 are balanced, whereby the hydraulic pressure is regulated (depressurized).

  The decompressed hydraulic oil is supplied to the solenoid valve 14 via the second oil passage 28. Here, the solenoid valve 14 includes a solenoid 30 that receives a command current from a control unit such as an ECU. The solenoid 30 generates a thrust according to the value of the supplied command current. The second valve rod 32 of the solenoid valve 14 is provided in the second valve hole 34 with this thrust, the elastic biasing force of the second pressure regulating spring 35 accommodated in the spring chamber 35a, and the second valve rod 32. It is held at a position where the acting feedback hydraulic pressure is balanced. Thereby, the hydraulic pressure is adjusted (reduced pressure), and a predetermined solenoid pressure is obtained.

  The hydraulic oil adjusted to the solenoid pressure reaches the control valve 16 via the third oil passage 36. Here, the hydraulic oil distributed from the first oil passage 20 as described above is supplied to the control valve 16 at a line pressure. The third valve rod 38 of the control valve 16 balances the elastic urging force by the third pressure regulating spring 42, the solenoid pressure, and the feedback hydraulic pressure acting on the third valve rod 38 in the third valve hole 40. It is held at the position to do. As a result, the line pressure input to the control valve 16 is regulated (depressurized), and the hydraulic oil is supplied from the output port 44 as a predetermined hydraulic pressure. The derived hydraulic oil is supplied to a clutch, for example.

  In the path from the control valve 16 to the output port 44, there is provided a relief valve 46 for preventing hydraulic oil from being supplied to the clutch when the clutch pressure becomes greater than a predetermined threshold pressure. That is, the spherical valve body 48 of the relief valve 46 is normally seated on the valve seat 52 by receiving the elastic urging force of the closing spring 50 (the elastic member). When the clutch pressure becomes excessively large, the spherical valve body 48 is pressed by the hydraulic oil. When the spherical valve body 48 is separated from the valve seat 52 and the closing spring 50 is compressed, the relief valve 46 is opened, and hydraulic oil is led out of the hydraulic control device 10 through the relief valve 46.

  Next, the actual configuration of the hydraulic control device 10 will be described.

  2 and 3 are respectively a horizontal sectional perspective view of the hydraulic control apparatus 10 according to the present embodiment, and a plan view of the open end face side of the body 54 constituting the hydraulic control apparatus 10. In the following description, the width direction, the axial direction, and the thickness direction of the body 54 correspond to the X direction, the Y direction, and the Z direction in FIG. 2, respectively, and the same applies to other drawings. The “open end surface of the body 54” refers to the end surface on the side where the first oil passage 20, the second oil passage 28, and the third oil passage 36 are formed, and the “closed end surface of the body 54” refers to the open end surface. The back side of the end face is designated.

  As can be understood from FIGS. 2 and 3, the regulator valve 12, the solenoid valve 14, and the control valve 16 share one body 54 as a valve body. A solenoid valve 14 and a control valve 16 are disposed at both ends with the regulator valve 12 interposed therebetween.

  That is, as shown in FIG. 2, the body 54 has three valve holes 24, 34, 40 with the first valve hole 24 at the center and the second valve hole 34 and the third valve hole 40 at both ends. Is formed. The first valve hole 24, the second valve hole 34, and the third valve hole 40 are arranged in parallel so that their axes are parallel along the width direction (X direction) of the body 54, in other words, along the horizontal direction. Has been.

  The first valve hole 24 accommodates the first valve rod 22 of the regulator valve 12. The second valve hole 34 accommodates the second valve rod 32 of the solenoid valve 14, and the third valve hole 40 accommodates the third valve rod 38 of the control valve 16. For this reason, the regulator valve 12, the solenoid valve 14, and the control valve 16 are also arranged in parallel along the width direction (X direction / horizontal direction) of the body 54 so that the axes thereof are parallel to each other. The first valve rod 22, the second valve rod 32, and the third valve rod 38 are all formed of spools.

  One ends of the first valve hole 24, the second valve hole 34, and the third valve hole 40 are closed by cap members 56, 58, and 60, respectively. The other end of the first valve hole 24 and the third valve hole 40 as shown in FIG. 4 which is a sectional view taken along the line IV-IV in FIG. 3 and FIG. 5 which is a sectional view taken along the line VV. Is occluded by the body 54 itself. Further, the solenoid 30 is exposed from the other end of the second valve hole 34 (see FIGS. 2 and 3).

  As shown in FIGS. 4 and 5, the first pressure regulating spring 26 and the third pressure regulating spring 42 are respectively provided between the first valve rod 22, the third valve rod 38 and the inner wall of the body 54. The first valve rod 22 and the third valve rod 38 are elastically biased toward the cap members 56 and 60. On the other hand, as shown in FIG. 6, which is a cross-sectional view taken along the line VI-VI in FIG. 3, the second pressure regulating spring 35 is disposed between the cap member 58 and the second valve rod 32, and the second valve The rod 32 is elastically biased toward the solenoid 30 side.

  As shown in FIG. 3, the input port 18, the first oil passage 20, the second oil passage 28, the third oil passage 36, and the output port 44 are formed on the open end surface of the body 54. Hereinafter, the wall portion that divides them is referred to as “oil passage wall”, and its reference numeral is 61.

  The input port 18 is formed in the vicinity of the first oil passage 20 and the third valve hole 40. The input port 18 is provided with a filter 62 for removing foreign substances from the hydraulic oil (see FIG. 5).

  An input flow path 64 is connected to the downstream side of the input port 18, and the input flow path 64 extends linearly along the thickness direction (Z direction) of the body 54 as shown in FIG. The depth of the input flow path 64 with respect to the top surface of the oil path wall 61 is set to be larger than the depth of the first oil path 20.

  The input flow path 64 and the first oil path 20 communicate with each other via the communication path 66. That is, the upstream end portion of the communication path 66 opens at a substantially middle portion in the height direction (Z direction) of the input flow path 64. The communication path 66 extends so as to incline with respect to the thickness direction of the body 54, and the downstream end opens at the upstream end of the first oil passage 20. An orifice 67 is provided in the vicinity of the opening of the communication passage 66 to the first oil passage 20.

  As shown in FIG. 3, the first oil passage 20 extends along the axis (Y direction) of the third valve hole 40 while being bent, and in the vicinity of the downstream end of the third valve hole 40, Bend to the valve hole 24 side. The downstream end of the first oil passage 20 is in a position straddling the first valve hole 24.

  A first line pressure inlet hole 68 (third valve hole line pressure inlet) is formed near the upstream end of the first oil passage 20 so as to be close to the downstream opening of the communication path 66. A second line pressure inlet hole 70 (first valve hole line pressure inlet) is formed at the downstream end. That is, in the first oil passage 20, the first line pressure inlet hole 68 and the second line pressure inlet hole 70 are formed in this order from the upstream side. Of course, the first oil passage 20 communicates with the third valve hole 40 via the first line pressure inlet hole 68 (see FIG. 5), and at the same time, communicates with the first valve hole 24 via the second line pressure inlet hole 70. Communicate. For this reason, the hydraulic oil introduced into the first oil passage 20 is distributed to the first valve hole 24 and the third valve hole 40.

  The second oil passage 28 is formed so as to straddle part of the first valve hole 24 and part of the second valve hole 34 (see FIG. 3). The second oil passage 28 has a substantially linear shape extending along the width direction (X direction) of the body 54 and is shorter than the first oil passage 20 and the third oil passage 36.

  A first valve hole outlet hole 72 (first valve hole outlet) for leading hydraulic oil from the first valve hole 24 is formed at the upstream end portion of the second oil passage 28, while the downstream end portion A second valve hole inlet hole 74 (second valve hole inlet) for introducing hydraulic oil into the second valve hole 34 is formed. That is, the second oil passage 28 communicates with each of the first valve hole 24 and the second valve hole 34 via the first valve hole outlet hole 72 and the second valve hole inlet hole 74.

  A first pool 76 is recessed in the vicinity of the first oil passage 20. The third valve hole 40 and the first pool 76 communicate with each other through the first communication hole 78.

  As shown in FIG. 7, which is a cross-sectional view taken along line VII-VII in FIG. 3, a first drain hole 80 is formed through the body 54. The first pool 76 and the first drain hole 80 are separated by an overflow wall 82 whose height direction (Z direction) dimension is shorter than that of the oil passage wall 61. That is, when the amount of hydraulic oil that has entered the first pool 76 becomes an amount that cannot be blocked by the overflow wall 82, the hydraulic oil overflows from the first pool 76 and is then discharged from the first drain hole 80.

  The third oil passage 36 extends along the axial direction (Y direction) of the second valve hole 34, and is then bent toward the first valve hole 24 and the third valve hole 40. It reaches the third valve hole 40 across the bridge. That is, most of the third oil passage 36 is formed so as to extend along the width direction (X direction) of the body 54.

  In the third oil passage 36, a second valve hole outlet hole for drawing hydraulic oil from the second valve hole 34 is provided at a portion bent from the second valve hole 34 toward the first valve hole 24 side. 84 (second valve hole outlet) is formed. Further, a solenoid pressure inlet hole 86 (solenoid pressure inlet) for introducing hydraulic oil into the third valve hole 40 is formed at the downstream end. The third oil passage 36 communicates with the second valve hole 34 via the second valve hole outlet hole 84 and also communicates with the third valve hole 40 via the solenoid pressure inlet hole 86 (see FIG. 5).

  Moreover, the 2nd pool 88 is depressed and formed in the vicinity of the 3rd oil path 36 (refer FIG. 3). The second valve hole 34 and the second pool 88 communicate with each other through the second communication hole 90. A damper orifice 91 is formed in the vicinity of the second communication hole 90 so as to penetrate therethrough.

  On the other hand, a second drain hole 92 is formed through the body 54. As shown in FIG. 8, which is a cross-sectional view taken along the line VIII-VIII in FIG. 3, the second pool 88 and the second drain hole 92 are shorter in height direction (Z direction) than the oil passage wall 61. It is divided by an overflow wall 94. That is, similarly to the first pool 76, when the hydraulic oil that has entered the second pool 88 becomes an amount that cannot be blocked by the overflow wall 94, after the hydraulic oil overflows from the second pool 88, It is discharged from the drain hole 92.

  The output port 44 opens near the first oil passage 20 (see FIG. 3). An output flow path 96 is connected upstream of the output port 44. That is, the output port 44 is a downstream opening of the output flow channel 96. The output flow path 96 extends linearly along the thickness direction of the body 54, as shown in FIG. 9 (sectional view taken along the line IX-IX in FIG. The third valve hole 40 is orthogonal to the third valve hole 40 in the vicinity of the middle part in the axial direction of the third valve hole 40.

  Note that the center of the axis of the output flow channel 96 is offset from the center of the axis of the third valve hole 40. For this reason, the upstream end of the output flow channel 96 opens at the side of the third valve hole 40.

  A filter 98 is installed at the output port 44. In the body 54, for example, when wear powder is generated and mixed with the hydraulic oil, the wear powder is removed by the filter 98, and clean hydraulic oil is led out from the output port 44.

  Above the output flow path 96, the introduction port 100 of the relief valve 46 continues. That is, the output flow path 96 is branched into the output port 44 and the introduction port 100. The introduction port 100 is normally closed as the spherical valve body 48 is seated on the valve seat 52. Further, the introduction port 100 is a throttle channel whose inner diameter is narrowed compared to the output channel 96.

  More specifically, as shown in FIGS. 9 and 10, a cylindrical protrusion 102 serving as a body portion of the relief valve 46 is formed on the closed end surface of the body 54 at a portion corresponding to the upper side of the third valve hole 40. The body 54 is formed so as to protrude integrally. The spherical valve body 48 and the closing spring 50 are accommodated in a relief chamber 104 which is the inside of the cylindrical protrusion 102.

  From the introduction port 100 to the relief chamber 104, the inner wall of the body 54 protrudes inward in the diametrical direction, whereby the valve seat 52 and the guide portion 106 that guides the spherical valve body 48 with the inner peripheral wall; Is formed. Then, a relief hole 108 extending linearly along the horizontal direction is formed so as to penetrate immediately above the valve seat 52, that is, from the inner peripheral wall of the guide portion 106 to the outer wall of the cylindrical protrusion 102. That is, the relief hole 108 is a so-called lateral hole. Similar to the introduction port 100, the relief hole 108 is a throttle channel.

  A part of the spherical valve body 48 is exposed from the guide portion 106. One end portion of the closing spring 50 is seated on a part of the spherical valve body 48 exposed from the guide portion 106. The other end of the closing spring 50 is in contact with the inner surface of the lid member 110 that covers the top surface of the cylindrical protrusion 102.

  As shown in FIG. 9 and FIG. 11 in which the lid member 110 and the closing spring 50 are not shown, the bottom wall of the relief chamber 104 has three parts cut out into a substantially semicircular shape. The notch 112 is recessed. In the guide part 106, the part in which the notch groove 112 is formed has a smaller dimension in the height direction (Z direction) than other parts. That is, the guide portion 106 has a shape in which vertical grooves are formed by the cutout grooves 112 (see FIG. 9).

  Furthermore, a vertical wall 114 having a shape in which a part thereof is cut out from the top surface toward the body 54 is formed on the outer wall of the cylindrical protrusion 102 (see FIG. 11).

  A cylindrical connecting protrusion 118 is integrated with the body 54 at a portion corresponding to the upper side of the third valve hole 40 (control valve 16) on the closed end face of the body 54 so as to be adjacent to the cylindrical protrusion 102. Standing up. The connecting protrusion 118 is formed with a threaded portion 120 (see FIGS. 9 and 11), and the cylindrical protrusion 102 is compared to the cylindrical protrusion 102 and the connecting protrusion 118. And thin rib portions 122 (see FIG. 11). Of course, the rib portion 122 is also erected integrally with the body 54.

  The lid member 110 has a substantially long plate shape (see FIGS. 2 and 9), and is attached to the connecting protrusion 118 so as to cover both top surfaces of the cylindrical protrusion 102 and the connecting protrusion 118. That is, a through hole 124 (see FIG. 9) is formed through the lid member 110, and a fixing bolt 126 as a fastening member passed through the through hole 124 is screwed into the threaded portion 120 of the connecting projection 118. By doing so, the lid member 110 is fixed.

  Here, the lid member 110 is formed with a hook portion 128 so as to hang down from one end face (see FIGS. 2 and 9). The hook member 128 is locked to the vertical wall portion 114 of the cylindrical protrusion 102, thereby preventing the lid member 110 from rotating. That is, the vertical wall portion 114 functions as a locking portion for locking the hook portion 128 of the lid member 110.

  The protruding height of the cylindrical protrusion 102 is smaller than that of the connecting protrusion 118. For this reason, when the lid member 110 is fixed to the top surface of the connecting projection 118, a slight clearance 130 is formed between the lid member 110 and the top surface of the cylindrical projection 102 ( (See FIG. 9). The relief chamber 104 is open to the atmosphere through this clearance 130. The hydraulic oil leaking into the relief chamber 104 is discharged from the clearance 130.

  As shown in FIGS. 2, 3, and 10, the body 54 has a plurality of first insertion holes 132 and second insertion holes 134 (both of which are fastening member insertion holes) for passing connection bolts (not shown) that are fastening members. Hole) is formed penetrating along the thickness direction. In this case, there are seven first insertion holes 132 formed in the vicinity of the first valve hole 24 and the third valve hole 40, and the second insertion hole 134 is formed in the vicinity of the second valve hole 34. There are four.

  As can be understood with reference to FIGS. 2 and 3, the distance (pitch) P1 between the first insertion holes 132 in the axial direction Y is equal to the distance (pitch) P2 between the second insertion holes 134 in the axial direction Y. Smaller than that. That is, the plurality of first insertion holes 132 are provided relatively densely, while the plurality of second insertion holes 134 are provided relatively sparsely.

  The hydraulic control apparatus 10 according to the present embodiment is basically configured as described above. Next, the operation and effect will be described.

  The body 54 of the hydraulic control device 10 can be obtained by casting, for example. At this time, the cylindrical protrusion 102, the rib part 122, and the connecting protrusion 118 can be formed so as to extend along the mold opening direction (Z direction) of the casting mold. For this reason, the body 54 can be manufactured easily.

  In order to provide the relief valve 46 in the obtained body 54, the spherical valve body 48 and the closing spring 50 are inserted in this order into the inside of the cylindrical protrusion 102, that is, the relief chamber 104. The top surfaces of the cylindrical protrusion 102 and the connecting protrusion 118 are covered. At this time, the through hole 124 is matched with the position of the screwing portion 120, and the hook portion 128 is locked to the vertical wall portion 114.

  Next, the fixing bolt 126 is passed through the through hole 124 and screwed into the screwing portion 120. At this time, since the hook portion 128 is locked to the vertical wall portion 114, the lid member 110 is prevented from rotating around the fixing bolt 126. That is, since the lid member 110 is prevented from rotating by the above-described locking, the attachment of the lid member 110 to the body 54, in other words, the assembly of the relief valve 46 is facilitated.

  As described above, after the spherical valve body 48 and the closing spring 50 are inserted into the cylindrical protrusion 102, the simple operation of fixing the lid member 110 to the connecting protrusion 118 with the fixing bolt 126 is performed. Thus, the relief valve 46 can be easily assembled.

  The hydraulic control device 10 is attached to a predetermined mating member (not shown) via a separate plate 136. At this time, the open end face (FIG. 3) in which the first oil passage 20, the second oil passage 28, and the third oil passage 36 are formed by the connecting bolts passed through the first insertion hole 132 and the second insertion hole 134, respectively. Reference) is connected so that the side is closed, that is, the oil passage wall 61 side faces the mating member. In general, the open end face side shown in FIG. 3 is the upper side, and the closed end face side shown in FIG. 10 is the lower side. A control unit such as an ECU is electrically connected to the solenoid 30.

  The hydraulic control device operates as follows.

  First, hydraulic oil is supplied to the hydraulic control device 10 at a predetermined initial hydraulic pressure (line pressure) under the action of an oil pump (not shown). The hydraulic oil is introduced into the body 54 from the input port 18 while removing foreign matters by passing through the filter 62 (see FIG. 5), and flows in the thickness direction of the body 54 along the input flow path 64.

  Since the communication path 66 is formed in the middle of the input flow path 64 in the height direction, the hydraulic oil passes through the communication path 66 and further passes through the orifice 67. The flow rate of the hydraulic oil is restricted by the orifice 67 and the flow velocity is increased. In this state, the hydraulic oil enters the first oil passage 20.

  For example, when the communication path 66 is a horizontal hole extending along the axial direction Y, the communication distance between the input flow path 64 and the first oil path 20 is increased, and the length of the body 54 in the thickness direction Z is increased. Becomes larger. On the other hand, in the present embodiment, the communication path 66 that is the downstream flow path of the filter 62 is formed so as to be inclined with respect to the thickness direction Z of the body 54, and the downstream end of the communication path 66 The portion is opened above the starting end portion of the first oil passage 20. For this reason, the length in the thickness direction Z of the body 54 is smaller than that in the case where the lateral hole is formed, which contributes to the miniaturization of the body 54.

  Moreover, since the orifice 67 is disposed on the downstream side of the filter 62, the flow rate of the hydraulic oil increases after passing through the filter 62. Therefore, unlike the case where the orifice 67 is arranged on the upstream side of the filter 62, the hydraulic oil that has passed through the orifice 67 and has an increased flow rate does not contact the filter 62. For this reason, an excessive load does not act on the filter 62.

  The hydraulic oil that has entered the first oil passage 20 flows along the first oil passage 20. Since the first line pressure inlet hole 68 and the second line pressure inlet hole 70 are formed in the first oil passage 20 in this order from the upstream side, the hydraulic oil is supplied to the third valve hole 40 and the first valve hole 24. Enter each of the.

  The hydraulic oil that has entered the first valve hole 24 will be described. In the first valve hole 24, as shown in FIGS. 1 and 4, the first valve rod 22 constituting the regulator valve 12 is replaced with a first pressure regulating spring 26. Is being energized. When the first valve rod 22 stops at a position where the first pressure regulating spring 26 and the feedback hydraulic pressure acting on the first valve rod 22 are balanced, the hydraulic pressure of the hydraulic oil is reduced. That is, the pressure is reduced.

  On the other hand, the hydraulic oil that has entered the third valve hole 40 is supplied to the control valve 16 while maintaining the line pressure. This point will be described later.

  The hydraulic oil decompressed under the action of the regulator valve 12 in the first valve hole 24 is led out to the second oil passage 28 via the first valve hole outlet hole 72. And it distribute | circulates along the 2nd oil path 28, and approachs into the 2nd valve hole 34 from the 2nd valve hole inlet hole 74 (refer FIG. 3).

  In the present embodiment, since the regulator valve 12 and the solenoid valve 14 are adjacent to each other, the first valve hole outlet hole 72 (the outlet port of the regulator valve 12) and the second valve hole inlet hole 74 (the inlet port of the solenoid valve 14). The second oil passage 28 that communicates with each other can be formed into a short linear shape. For this reason, since the hydraulic oil derived | led-out from the 1st valve hole 24 can arrive at the 2nd valve hole 34 rapidly, a response speed improves.

  The hydraulic fluid that has entered the second valve hole 34 via the regulator valve 12, that is, the hydraulic fluid that has been depressurized, imparts an input hydraulic pressure to the solenoid valve 14. On the other hand, a command current is sent to the solenoid 30 of the solenoid valve 14 from a control unit such as an ECU. The solenoid 30 receiving this command current gives a thrust corresponding to the value of the command current to the second valve rod 32.

  Eventually, the feedback oil pressure, the thrust by the solenoid 30, and the elastic biasing force by the second pressure regulating spring 35 act on the second valve rod 32. The second valve rod 32 is held at a position where these forces are balanced, whereby the hydraulic pressure of the hydraulic oil is further regulated (generally reduced pressure) to obtain a predetermined solenoid pressure.

  During this time, part of the hydraulic oil is led out from the second valve hole 34 through the second communication hole 90 and stored in the spring chamber 35a and the second pool 88 (see FIG. 8). The hydraulic oil stored in the spring chamber 35 a and the second pool 88 functions as a damper for the second valve rod 32. That is, when the second valve rod 32 moves, the hydraulic oil is stored in the second pool 88, when the second valve rod 32 moves by forming the second pool 88 in the upper part under the gravity of the spring chamber 35a. Or it moves through the damper orifice 91 in the opposite direction. For this reason, generation | occurrence | production of the hydraulic vibration in the 2nd valve rod 32 can be suppressed.

  Note that when a certain amount of hydraulic oil enters the second pool 88, excess hydraulic oil passes through the overflow wall 94 and is discharged from the second drain hole 92.

  The hydraulic oil that has reached the solenoid pressure is led out to the third oil passage 36 from the second valve hole outlet hole 84 (see FIGS. 1 and 3). Furthermore, it flows along the third oil passage 36 and enters the third valve hole 40 through the solenoid pressure inlet hole 86. In other words, the control valve 16 is supplied with hydraulic fluid introduced from the input port 18 and maintaining the line pressure, and hydraulic fluid derived from the solenoid valve 14 and regulated to a predetermined solenoid pressure.

  Accordingly, the third valve rod 38 of the control valve 16 is subjected to the elastic biasing force by the third pressure regulating spring 42, the solenoid pressure (pilot pressure), and the feedback hydraulic pressure acting on the control valve 16, and the third The valve stem 38 is held in a position where these forces are balanced. As a result, the line pressure input to the control valve 16 is regulated (depressurized), and the hydraulic oil becomes a predetermined hydraulic pressure, for example, a predetermined clutch pressure (driving pressure).

  An output flow path 96 is orthogonal to the third valve hole 40. Therefore, the hydraulic oil that has become the clutch pressure passes through the output flow path 96 extending along the thickness direction of the body 54 and is led out from the output port 44. The derived hydraulic oil is supplied to a clutch (not shown). Here, for example, when wear powder is generated in the first valve hole 24, the second valve hole 34, or the third valve hole 40 and flows along with the hydraulic oil, the wear powder is installed in the output port 44. Is collected by the filtered filter 98. For this reason, clean hydraulic fluid is supplied to the clutch.

  As described above, the hydraulic oil that has become the clutch pressure only flows along the thickness direction of the body 54, and does not flow through any oil passage formed on the open end surface. In short, it is not necessary to provide an oil passage for circulating the hydraulic oil having the clutch pressure on the open end face.

  Moreover, in the present embodiment, the solenoid valve 14 and the control valve 16 are arranged in parallel so that the regulator valve 12 is sandwiched therebetween. That is, since the regulator valve 12 and the control valve 16 are in a parallel positional relationship, the length of the first oil passage 20 connecting the regulator valve 12 and the control valve 16 can be reduced.

  For the reasons as described above, the first oil passage 20 and the second oil passage 28 are shortened, so that the total length of all the oil passages can be shortened. Eventually, the body 54 and, consequently, the hydraulic control device 10 can be downsized.

  Further, since the regulator valve 12, the solenoid valve 14, and the control valve 16 are arranged in parallel so that the axes thereof are parallel along the width direction (X direction) of the body 54, the hydraulic control device 10 is arranged in the thickness direction Z of the body 54. There is no increase in size. In combination with this, the hydraulic control device 10 can be further reduced in size.

  In addition, since the first oil passage 20 and the second oil passage 28 can be shortened, the hydraulic oil quickly reaches the first valve hole 24, the second valve hole 34, and the third valve hole 40. For this reason, the response speed of the regulator valve 12, the solenoid valve 14, and the control valve 16 is improved.

  Part of the hydraulic oil that has entered the third valve hole 40 is led out from the third valve hole 40 via the first communication hole 78 and stored in the first pool 76. In addition, when hydraulic oil exceeding a certain amount enters the first pool 76, excess hydraulic oil passes through the overflow wall 82 and is discharged from the first drain hole 80.

  As can be understood from the above, in the hydraulic control device 10, high-pressure hydraulic oil is supplied to the regulator valve 12 and the control valve 16. Therefore, in the present embodiment, the pitch P1 between the first insertion holes 132 in the vicinity of the first valve hole 24 and the third valve hole 40 that are high pressure is reduced, while the second valve hole 34 that is relatively low pressure. The pitch P2 between the second insertion holes 134 in the vicinity of is increased (see FIGS. 3 and 10). Inevitably, the connection bolts on the regulator valve 12 and control valve 16 side are denser than the connection bolts on the solenoid valve 14 side.

  For this reason, when the hydraulic control apparatus 10 is attached to the mating member via the connecting bolt, a large surface pressure can be applied to the oil passage wall 61 on the regulator valve 12 and control valve 16 side. That is, the oil passage wall 61 on the regulator valve 12 and control valve 16 side is firmly attached to the mating member. Accordingly, it is possible to prevent the hydraulic oil from leaking from between the part of the body 54 near the third valve hole 40 and the counterpart member.

  The connecting bolts on the solenoid valve 14 side are sparser than the connecting bolts on the regulator valve 12 and control valve 16 side, but the solenoid valve 14 is operated at a relatively low pressure. Oil is supplied or derived. Therefore, even when a large surface pressure is not applied between the oil passage wall 61 on the solenoid valve 14 side and the mating member, the operation is performed between the portion near the second valve hole 34 of the body 54 and the mating member. Oil can be sufficiently prevented from leaking.

  Furthermore, the cylindrical protrusion 102, the rib part 122, and the connection protrusion 118 are provided at portions corresponding to the upper portions of the first valve hole 24 and the third valve hole 40, respectively. The presence of the cylindrical protrusion 102, the rib 122, and the connecting protrusion 118 increases the strength around the first valve hole 24 and the third valve hole 40. That is, the portion of the body 54 that has a relatively high pressure exhibits sufficient strength.

  As described above, since the output flow path 96 communicates with the introduction port 100 of the relief valve 46 while the hydraulic oil flows (see FIG. 9), the output flow path 96 is led out from the third valve hole 40 to the output flow path 96. The hydraulic oil also flows through the introduction port 100 side. Since the introduction port 100 is connected to the output flow path 96 and extends along the thickness direction of the body 54, the flow direction of the hydraulic oil toward the relief valve 46 is only the thickness direction of the body 54. . That is, it is not necessary to provide an oil passage for directing the working oil toward the relief valve 46 on the open end surface of the body 54. This also contributes to the shortening of the total length of all the oil passages and the miniaturization of the hydraulic control device 10. It also contributes to an improvement in the response speed of the relief valve 46.

  As described above, the spherical valve body 48 constituting the relief valve 46 is subjected to the pressing force of the hydraulic oil and the elastic biasing force of the closing spring 50. When the elastic urging force by the closing spring 50 exceeds the pressing force (clutch pressure) by the hydraulic oil, the spherical valve body 48 maintains the state of being seated on the valve seat 52. This is because the spherical valve body 48 is elastically biased toward the valve seat 52 by the closing spring 50. That is, in this case, the relief valve 46 is closed.

  Usually, the clutch pressure is set so as to be less than the elastic urging force of the closing spring 50. Therefore, since the relief valve 46 is kept closed, the flow path of the hydraulic oil in the body 54 is only the path from the input port 18 to the output port 44 described above.

  When inspecting whether the relief valve 46 operates normally, first, the first drain hole 80 is closed with, for example, a rod-shaped inspection rod (not shown). Next, the clutch pressure is increased from the output port 44 until it exceeds the elastic urging force of the closing spring 50, that is, to a predetermined threshold pressure. When the relief valve 46 is opened at the threshold pressure, it can be determined that the operation is normal, and when the relief valve 46 remains closed, the operation is abnormal.

  When the operation is normal, the relief valve 46 operates as follows and is opened.

  When the hydraulic oil that has entered the introduction port 100 exceeds a predetermined threshold pressure, for example, a predetermined threshold pressure is applied, the spherical valve body 48 is displaced by being pressed by the hydraulic oil and is separated from the valve seat 52. Accordingly, the introduction port 100 is opened and the relief valve 46 is opened. When the spherical valve body 48 is displaced, the spherical valve body 48 is guided by the guide portion 106 and the closing spring 50 is compressed.

  At that time, the hydraulic oil flows through the relief hole 108 formed as a horizontal hole and is received by the hemispherical portion of the spherical valve body 48 on the introduction port 100 side. Further, since the relief hole 108 is formed between the valve seat 52 and the guide portion 106, that is, immediately above the valve seat 52, the hydraulic oil hardly flows toward the upper part of the relief chamber 104, and the relief hole 108 is Through the body 54 quickly.

  Further, when the spherical valve body 48 receives the hydraulic oil at the hemispherical portion, the spherical valve body 48 is held at a predetermined displacement amount (lift amount). In this case, the predetermined displacement amount is a position where the pressure received by the spherical valve body 48 from the hydraulic oil in the guide portion 106 and the elastic urging force by the closing spring 50 are balanced. In other words, the holding position of the spherical valve body 48 can be adjusted by adjusting the pressure receiving force and the bullet urging force. The holding position is preferably set in the vicinity of the valve seat 52.

  The pressure receiving pressure can be adjusted by adjusting the diameters of the throttle channels of the introduction port 100 and the relief hole 108. For example, it is preferable to make the throttle channel diameter of the introduction port 100 smaller than the throttle channel diameter of the relief hole 108.

  As described above, since the spherical valve body 48 receives pressure over the entire hemispherical portion and the relief hole 108 is formed immediately above the valve seat 52, the displacement amount (lift amount) of the spherical valve body 48 is small. It becomes. Since the closing spring 50 only needs to be compressible to the extent that the displacement amount can be tolerated, a small size can be adopted as the closing spring 50. Therefore, the protrusion height (Z-direction dimension) of the cylindrical protrusion 102 in which the relief chamber 104 that accommodates the closing spring 50 is formed can be reduced. Inevitably, the protruding heights of the rib 122 and the connecting protrusion 118 can also be reduced, so that the relief valve 46 and its surroundings, and hence the hydraulic control device 10 can be downsized.

  Further, as described above, as the three cutout grooves 112 are formed in the bottom wall of the relief chamber 104, the guide portion 106 has a shape in which vertical grooves are formed. For this reason, when higher pressure is applied and the spherical valve body 48 attempts to rise above a predetermined displacement, the hydraulic oil leaks from the notch groove 112. This leakage can limit the upward displacement of the spherical valve body 48.

  Since the upward displacement of the spherical valve body 48 is limited as described above, the deformation amount of the closing spring 50 can be reduced. As a result, it is possible to reduce the size of the closing spring 50 and hence to reduce the size of the hydraulic control device 10. The notch groove 112 is set at a position where the hydraulic oil can leak slightly above the holding position of the spherical valve body 48 described above.

  As the hydraulic oil flows, the hydraulic control device 10 obtains a solenoid pressure from one of the branched line pressures as described above, and uses the solenoid pressure as a pilot pressure to generate a predetermined pressure from one of the remaining line pressures. Plays the role of obtaining clutch pressure.

  The relief valve 46 remains closed when the clutch pressure obtained as described above falls below a predetermined threshold pressure. On the other hand, when the clutch pressure is equal to or higher than the threshold pressure, the spherical valve body 48 is separated from the valve seat 52 to be in the open state as described above. As a result, the hydraulic oil is discharged from the relief hole 108. For this reason, it is avoided that the hydraulic oil which became more than predetermined pressure is supplied to a clutch, and a clutch can be protected after all.

  The present invention is not particularly limited to the above-described embodiment, and various modifications can be made without departing from the gist of the present invention.

  For example, the supply destination of the hydraulic oil regulated by the hydraulic control device 10 is not limited to the clutch. That is, the regulated hydraulic oil may be used as drive oil for a continuously variable transmission (CVT) pulley.

DESCRIPTION OF SYMBOLS 10 ... Hydraulic control apparatus 12 ... Regulator valve 14 ... Solenoid valve 16 ... Control valve 18 ... Input port 20 ... 1st oil path 22 ... 1st valve rod 24 ... 1st valve hole 28 ... 2nd oil path 30 ... Solenoid 32 ... 2nd valve rod 34 ... 2nd valve hole 36 ... 3rd oil path 38 ... 3rd valve rod 40 ... 3rd valve hole 44 ... Output port 46 ... Relief valve 48 ... Spherical valve body 50 ... Spring for closing 52 ... Valve seat 54 ... Body 62, 98 ... Filter 64 ... Input flow path 66 ... Communication path 67 ... Orifice 68 ... First line pressure inlet hole 70 ... Second line pressure inlet hole 72 ... First valve hole outlet hole 74 ... Second valve hole Inlet hole 76 ... first pool 80 ... first drain hole 84 ... second valve hole outlet hole 86 ... solenoid pressure inlet hole 88 ... second pool 92 ... second drain hole 96 ... output flow path 100 ... inlet port 102 ... cylindrical Protrusion 1 04 ... Relief chamber 106 ... Guide portion 108 ... Relief hole 110 ... Lid member 112 ... Notch groove 118 ... Protruding portion 122 ... Rib portion 124 ... Through hole 126 ... Fixing bolt 128 ... Hook portion 130 ... Clearance 132 ... First insertion Hole 134 ... Second insertion hole 136 ... Separate plate

Claims (7)

A first pressure regulating valve for reducing the initial hydraulic pressure by the hydraulic oil input from the input port;
A solenoid valve for converting the hydraulic pressure reduced by the first pressure regulating valve into a solenoid pressure corresponding to a current supplied to the solenoid;
A second pressure regulating valve that is supplied with the solenoid pressure and converts an initial hydraulic pressure by hydraulic fluid input from the input port into a driving pressure corresponding to the solenoid pressure;
Have
One body is formed with a first valve hole, a second valve hole, and a third valve hole in which axes are arranged in parallel along the horizontal direction, and the first valve hole, the second valve hole, and In each of the third valve holes, a first valve rod of the first pressure regulating valve, a second valve rod of the solenoid valve, and a third valve rod of the second pressure regulating valve are accommodated so as to be capable of reciprocating,
The first valve hole is interposed between the second valve hole and the third valve hole, and the first pressure regulating valve is disposed between the solenoid valve and the second pressure regulating valve. A hydraulic control device characterized by that.   2. The hydraulic control device according to claim 1, wherein a plurality of fastening member insertion holes are formed in the body for passing fastening members for attaching the body to a predetermined member, and the first valve hole and the third valve. The distance between the fastening member insertion holes formed in the vicinity of the hole is set smaller than the distance between the fastening member insertion holes formed in the vicinity of the second valve hole. Hydraulic control device. 3. The hydraulic control device according to claim 1, wherein an output flow path for deriving hydraulic fluid having a driving pressure from the third valve hole to the body and a downstream side of the output flow path are connected to the body. And an output port opened at the end face of
The hydraulic control device, wherein the output flow path is formed in a straight line so as to extend from the output port along a thickness direction of the body, and is orthogonal to the third valve hole. The hydraulic control device according to any one of claims 1 to 3, wherein an input flow path connected to a downstream side of the input port extends linearly along the thickness direction of the body, A first valve hole line pressure inlet that communicates with the input flow path and introduces an initial hydraulic fluid into the first valve hole, and an initial hydraulic fluid into the third valve hole. An oil passage formed with a third valve hole line pressure inlet is provided;
The input flow path and the oil path communicate with each other via a communication path inclined with respect to the thickness direction of the body,
A hydraulic control device, wherein a filter is provided in the input port and an orifice is provided in the communication path.   5. The hydraulic control apparatus according to claim 1, wherein a first valve hole outlet and a first valve hole for deriving reduced hydraulic oil from the first valve hole to the body are provided. An oil pressure control device comprising an oil passage formed with a second valve hole inlet for introducing hydraulic oil led out from an outlet into the second valve hole.   6. The hydraulic control apparatus according to claim 5, wherein the oil passage in which the first valve hole outlet and the second valve hole inlet are formed has a linear shape.   The hydraulic control device according to any one of claims 1 to 6, wherein a second valve hole outlet for deriving hydraulic fluid having a solenoid pressure from the second valve hole to the body, and the second An oil pressure control device comprising an oil passage formed with a solenoid pressure inlet for introducing hydraulic oil led out from a valve hole outlet into the third valve hole.

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