JP4176300B2 - Hydraulic control valve - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention includes a linear solenoid portion, a spool that is driven forward by the output of the linear solenoid portion, a valve body that is slidably fitted to the spool, and a return spring that biases the spool in a backward direction, The valve body is provided with a supply port connected to the hydraulic power source, an output port connected to the hydraulic operation unit, and a drain port opened to the oil tank, while the output port is provided to the spool according to its forward / backward movement. And a first land portion that cuts off and conducts between the drain ports, a second land portion that conducts and cuts off between the supply port and the output port, and an annular groove portion that connects between the first and second land portions. Further, a reaction oil chamber is provided between the valve body and the spool to receive a hydraulic pressure for urging the spool in the backward direction from the output port, and the supply From over preparative an improvement of the hydraulic control valve so as to pull out the output hydraulic pressure corresponding to the output of the linear solenoid portion in said output port.
[0002]
[Prior art]
Such a hydraulic control valve is already known as disclosed in, for example, Japanese Patent Application Laid-Open No. 8-303627.
[0003]
[Problems to be solved by the invention]
In such a hydraulic control valve, when the spool advances due to an increase in the output of the linear solenoid part, the output port and the drain port are blocked by the first land part, and the supply port and the output port are disconnected by the second land part. As a result, the output hydraulic pressure of the output port is controlled to increase, and when the spool is retracted due to the decrease of the output of the linear solenoid portion, the supply port and the output port are shut off by the second land portion, and the first By connecting the output port and the drain port with the land portion, the output hydraulic pressure of the output port is controlled to be reduced. When controlling the output oil pressure, if the amount of conduction between the conduction ports is too large relative to the amount of displacement of the spool, the output oil pressure will fluctuate greatly, and the output oil pressure corresponding to the output of the linear solenoid unit can be obtained stably. It becomes difficult.
[0004]
The present invention has been made in view of such circumstances, and the amount of conduction between the conduction ports with respect to the displacement of the spool is suppressed to a minimum, and the control characteristics of the output hydraulic pressure can be stabilized. An object is to provide a hydraulic control valve.
[0005]
[Means for Solving the Problems]
In order to achieve the above object, the present invention provides a linear solenoid portion, a spool that is driven forward by the output of the linear solenoid portion, a valve body that is slidably fitted to the spool, and the spool attached in the backward direction. The valve body is provided with a supply port connected to the hydraulic power source, an output port connected to the hydraulic operating portion, and a drain port opened to the oil tank, while the spool has a forward movement thereof. A first land portion that cuts off and conducts between the output port and the drain port in response to retreat, a second land portion that conducts and cuts off between the supply port and the output port, and between the first and second land portions And an annular groove for connecting the valve body and the spool to receive a hydraulic pressure for urging the spool in the backward direction from the output port. In the hydraulic control valve which is provided with a reaction force oil chamber and draws out the output hydraulic pressure corresponding to the output of the linear solenoid portion from the supply port to the output port, the annular groove portions of the first land portion and the second land portion A damper oil chamber in which a pressure reducing control groove and a pressure increasing control groove opening on the outer peripheral surfaces of the first land portion and the second land portion are provided on each end face adjacent to each other, and the end face of the spool faces the valve body. An oil sump chamber communicating with the oil tank is provided immediately adjacent to the damper oil chamber, and the drain port is opened to the oil tank through the oil sump chamber, while the damper oil chamber An upper part is communicated with the oil reservoir through an orifice, and an outlet of the oil reservoir to the oil tank is provided at a position higher than the orifice, so that the orifice is connected to the oil reservoir. Characterized in that is positioned under the surface.
[0006]
Incidentally, the annular groove corresponds to the first annular groove 26 ₁ of the present invention to be described later.
[0007]
According to the above feature of the present invention, when the output hydraulic pressure is controlled to be increased, that is, when the supply port and the output port are electrically connected by the second land portion of the spool, the supply port is controlled by the pressure increase control groove of the second land portion. When the output hydraulic pressure is controlled to be reduced, that is, when the output port and the drain port are connected by the first land portion of the spool, the output port and the drain are connected by the pressure reduction control groove of the first land portion. will be between ports Ru is conductive, thus, the amount of conduction between conductive port to the movement of the spool in the minimum, the increase and decrease control of the output pressure can be stably performed well. In addition, the pressure increase / decrease control groove can bring about a relatively large flow rate change with a slight change in the opening degree, and thus enables quick control of the output hydraulic pressure with a small stroke of the movable core.
[0008]
Since the oil in the sump chamber also fills the damper oil chamber through the orifice, if the spool vibrates in the axial direction while controlling the output hydraulic pressure, the damper oil chamber Since the hydraulic oil flows between the oil sump chambers through the orifice, the vibration of the spool in the axial direction can be suppressed by the damping effect of the orifice. Can be ensured. In addition, since the oil sump chamber communicates with the damper oil chamber via an orifice located at the top of the damper oil chamber, the oil sump chamber can be disposed directly beside the damper oil chamber. The valve body can be made compact compared to the case where it is arranged in the upper part of the oil chamber .
[0009]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, embodiments of the present invention will be described based on examples of the present invention illustrated in the accompanying drawings.
[0010]
In the accompanying drawings, FIG. 1 is a longitudinal sectional view of a hydraulic control valve according to an embodiment of the present invention, FIG. 2 is an enlarged view of a linear solenoid part of FIG. 1, and FIG. 3 is an enlarged view of a valve part of FIG. 4 is a sectional view taken along line 4-4 in FIG. 3, FIG. 5 is a plan view of the spool, FIG. 6 is a sectional view taken along line 6-6 in FIG. 3, FIG. 7 is a sectional view taken along line 7-7 in FIG. It is an enlarged view corresponding to FIG. 3 which shows the operating state of a valve part.
[0011]
First, in FIG. 1, a hydraulic control valve 1 is for controlling clutch hydraulic pressure in, for example, an automatic transmission for automobiles, and includes a linear solenoid part S and a valve part V. A valve body 20 of the valve part V is shown in FIG. Is fixed to the upper surface of the transmission case 2 of the automobile by a bolt 5 (see FIG. 6).
[0012]
As shown in FIG. 2, the linear solenoid part S is integrally formed with a bottomed cylindrical housing 3 having one end opened of a magnetic material, a coil assembly 4 accommodated in the housing 3, and a closed end wall of the housing 3. A cylindrical yoke 6 arranged in series with the coil assembly 4 and coupled to the open end of the housing 3 and opposed to the yoke 6 with a predetermined distance inside the coil assembly 4. And a movable core 8 slidably fitted to the yoke 6 and the fixed core 7. The coil assembly 4 includes a synthetic resin bobbin 9, a coil 10 wound around the bobbin 9, and a synthetic resin coil case 11 molded so as to accommodate them. A coupler 12 protruding outward from the housing 3 is integrally provided at one end, and a connection terminal 13 connected to the coil 10 is disposed in the coupler 12.
[0013]
The surface of the yoke 6 facing the fixed core 7 is formed perpendicular to the axis thereof, and the surface of the fixed core 7 facing the yoke 6 is formed in a conical shape.
[0014]
The movable core 8, the central portion is secured the output rod 14 extending through the one end portion of the output rod 14, the first bearing hole 15 ₁ provided in the closed end wall pouched housing 3 is slidably supported via _a first bushing 16, the other end is slidably supported by the second bearing hole 15 ₂ passing through the center portion of the fixed core 7 via the second bushing 16 ₂ The
[0015]
Thus, electromagnetic thrust proportional to the current value flowing through the coil 10 can be applied to the output rod 14 via the movable core 8.
[0016]
The first bushing 16 _1, intended to be secured by press-fitting the first inner circumferential surface of the bearing hole 15 _1, the first bushing 16 ₁ outer peripheral surface, the axial communicating between its two end faces 1 A communication groove 17 ₁ is provided. The second bushing 16 ₂ is fixed by being press-fitted into the inner peripheral surface of the second bearing hole 15 _2. The second bushing 16 ₂ is also fixed to the outer peripheral surface of the second bushing 16 ₂ in the axial direction communicating between both end surfaces. Two communication grooves 17 ₂ are provided. More outer peripheral surface of the movable core 8, the third communication groove 17 _third axial communicating between its end faces is provided.
[0017]
Next, as shown in FIG. 3, the valve portion V has a valve body 20 that is caulked and coupled to the housing 3 on the fixed core 7 side, and a valve hole 21 that is coaxially formed with the output rod 14 in the valve body 20. The spool 22 that is fitted and abuts against the front end of the output rod 14, the return spring 23 that urges the spool 22 in its retreating direction, that is, the abutting direction with the output rod 14, and the valve body 20 are press-fitted and returned. The plug body 24 is configured to support the outer end of the spring 23, and the set load of the return spring 23 is adjusted by the press-fitting depth of the plug body 24 into the valve body 20.
[0018]
The spool 22 is provided with a first land portion 25 ₁ , a first annular groove portion 26 ₁ , a second land portion 25 ₂ , a second annular groove portion 26 ₂ , and a third land portion 25 _{3 in this} order from the linear solenoid portion S side. The first and second land portions 25 ₁ and 25 ₂ are formed to have the same diameter, and the third land portion 25 ₃ is formed to have a smaller diameter than the second land portion 25 ₂ .
[0019]
In FIGS. 3-5, the end face adjacent to the first annular groove 26 ₁ of the second land portion 25 _2, pressure increase control groove 27 opens to the second land portion 25 _second outer peripheral surface, also the first land the end surface adjacent to the first annular groove 26 ₁ parts 25 _1, a reduced pressure control groove 28 which opens to the first annular groove 26 ₁ outer peripheral surface is provided. The cross-sectional shape of each of the control grooves 27 and 28 can be a crescent shape (see FIG. 5) or a channel shape, but the bottom surface of the control grooves 27 and 28 extends from the outer peripheral surface of each land portion 25 ₁ , 25 ₂ to the first annular groove portion 26. _The slope is inclined toward ₁ . The number of the control grooves 27 and 28 is arbitrary, but as shown in FIG. 4, it is preferable that a pair of control grooves 27 and 28 are provided on the diameter lines of the end faces of the corresponding land portions 25 ₁ and 25 ₂ with the center therebetween.
[0020]
More first outer peripheral surface of the annular groove 26 _1, starting on the end face of the second land portion 25 ₂ adjacent along with continuously subsequent termination ends with the first annular groove 26 ₁ of the intermediate portion, the groove bottom Is provided with an annular groove 29 curved in a U-shape.
[0021]
On the other hand, the valve hole 21 of the valve body 20, the output rod 14 and the working chamber 30 for exposing the contact portion of the spool 22, freely first land portion 25 ₁ adjacent to the working chamber 30 is slid all the time Second annular land portion 31 ₂ , second land portion 25 in which the first annular groove portion 26 ₁ side end portion of the first annular land portion 31 ₁ and the first land portion 25 ₁ to be fitted is fitted or detached. ₂ , a third annular land portion 31 ₃ on which the first annular groove portion 26 ₁ side end portion is fitted or detached, and a fourth annular land portion 31 on which the second land portion 25 ₂ is slidably fitted. _4, the fifth annular land portion 31 _5, third and fourth annular land portion 31 _3, 31 supply oil chamber which is arranged to be sandwiched between ₄ third land portion 25 ₃ is slidably fitted constantly 32, second and third annular land portions 31 _2, 31 ₃ between the output hydraulic chamber 33 arranged to be sandwiched, 1 and a second annular land portions 31 _1, 31 drain oil chamber 34 which is arranged so as to be interposed between the _two, the fourth and fifth annular land portions 31 _4, 31 ₅ to the reaction force oil disposed so as to be sandwiched between A damper oil chamber 36 facing the chamber 35 and the opposite end surfaces of the spool 22 and the plug body 24 is provided, and the return spring 23 is accommodated in the damper oil chamber 36.
[0022]
Further, the valve body 20 is provided with a supply port 37 connected to the supply oil chamber 32, an output port 38 connected to the output oil chamber 33, a drain port 39 connected to the drain oil chamber 34, and a breather port 40 connected to the working chamber 30. The supply port 37 is connected to a hydraulic power source 42 such as a hydraulic pump via a supply oil path 41 of the mission case 2, and an output port 38 is an output oil path directly connected to a hydraulic operation unit 44 such as a clutch in the automatic transmission. The drain port 39 is connected to an oil sump chamber 49 (see FIG. 7), which will be described later, in the valve body 20 through the communication passage 45, and the breather port 40 is connected to the oil tank 46 through the breather passage 47. Connected to.
[0023]
The output oil chamber 33 is communicated with the reaction force oil chamber 35 via a feedback oil passage 48 formed in the spool 22.
[0024]
As shown in FIGS. 6 and 7, the valve body 20 is provided with an oil sump chamber 49 adjacent to the side of the damper oil chamber 36, and the uppermost portion of the damper oil chamber 36 is interposed via a horizontal orifice 50. And communicated with the oil sump chamber 49. The orifice 50 is drilled by using a large-diameter drill hole 51 formed on the outer wall of the oil sump chamber 49 at a position coaxial with the orifice 50. The plug 52 is closed and the outer peripheral edge of the drill hole 51 is caulked to the plug 52 side. By doing so, the orifice 50 can be formed in the partition wall between the damper oil chamber 36 and the oil reservoir chamber 46 without being obstructed by the outer wall of the oil reservoir chamber 46.
[0025]
The oil sump chamber 49 is provided with a drain pipe 53 erected from the upper surface of the mission case 2 to a position higher than the orifice 50, and the oil sump chamber 49 has a ceiling from the orifice 50 side to the drain pipe 53 side. A rising slope 54 is formed. The lower end of the drain pipe 53 is opened to the oil tank 46 through the drain oil passage 55 of the mission case 2.
[0026]
Next, the operation of this embodiment will be described.
[0027]
When the linear solenoid portion S is not energized, the spool 22 occupies the right movement limit position (retreat limit position) with the urging force of the return spring 23 and shuts off the supply port 37 and the output port 38 as shown in FIG. Since the output port 38 and the drain port 39 are electrically connected, the output oil passage 43 of the mission case 2 is opened to the oil sump chamber 49 via the drain port 39 and the communication passage 45.
[0028]
Further, when the linear solenoid portion S is energized, an electromagnetic thrust proportional to the current value acts on the spool 22 from the movable core 8 via the output rod 14. Accordingly, when the spool 22 advances to the left against the repulsive force of the return spring 23, the drain port 39 and the output port 38 are shut off, and the supply port 37 and the output port 38 are electrically connected to each other. The hydraulic pressure of the hydraulic pressure source 42 in the case 2 is supplied to the hydraulic operation unit 44 through the supply oil passage 41, the supply port 37, the output port 38, and the output oil passage 43, and the reaction force oil chamber 35 through the feedback oil passage 48. Also communicate. In the reaction oil chamber 35, the opposed end surfaces of the large-diameter second land portion 25 ₂ and the small-diameter third land portion 25 ₃ of the spool 22 face each other. The pressing force acts as a reaction force on the spool 22 together with the repulsion force of the return spring 23. As a result, the spool 22 moves left and right so as to balance the electromagnetic thrust of the output rod 14 and the reaction force. That is, when the electromagnetic thrust wins, the spool 22 moves to the left (advance) to increase the amount of conduction between the supply port 37 and the output port 38, and when the reaction force wins, the spool 22 moves to the right ( The supply port 37 and the output port 38 are shut off, and the amount of conduction between the output port 38 and the drain port 39 is increased. As a result, a hydraulic pressure proportional to the value of the current flowing through the linear solenoid unit S can be supplied to the hydraulic operation unit 44.
[0029]
By the way, at the time of pressure increase control of the output hydraulic pressure in which the supply port 37 and the output port 38 are electrically connected by the second land portion 25 ₂ of the spool 22, the supply port 37 and the output are controlled by the pressure increase control groove 27 of the second land portion 25 _2. During the pressure reduction control of the output hydraulic pressure in which the ports 38 are electrically connected and the output port 38 and the drain port 39 are electrically connected by the first land portion 25 ₁ of the spool 22, the output is output by the pressure reduction control groove 28 of the first land portion 25 _1. The port 38 and the drain port 39 are electrically connected. At that time, since the hydraulic oil first flows through the openings of the control grooves 27 and 28, the increase / decrease control of the output hydraulic pressure is performed stably, and a relatively large flow rate with a slight change in the opening degree of the control grooves 27 and 28. A change can be brought about, which means that a small flow of the movable core 8 enables a large flow control of the output, that is, a quick control of the output hydraulic pressure. Therefore, a desired hydraulic pressure can be rapidly supplied to the hydraulic operation unit 44, which can contribute to an improvement in response of the operation.
[0030]
Further, the pressure reduction control groove 28 of the first land portion 25 _{1 and} the pressure increase control groove 27 of the second land portion 25 ₂ are provided in pairs on the diameter line of the end surface of the corresponding land portion, so that each pair is provided. The hydraulic fluid flows through the pressure reduction control groove 28 and the pressure increase control groove 27, thereby preventing the hydraulic oil from drifting around the first and second land portions 25 ₁ , 25 ₂ , and the side thrust against the spool 22 due to the drift. Occurrence can be avoided, the smooth operation of the spool 22 can be ensured, and the man-hours of the control grooves 27 and 28 can be minimized to improve productivity.
[0031]
During the control of the output hydraulic pressure, the hydraulic oil discharged from the output port 38 to the drain port 39 moves to the oil sump chamber 49 through the communication path 45. Even when the coil 10 is de-energized and the spool 22 returns to the initial retreat limit position by the urging force of the return spring 23, the high-pressure hydraulic fluid on the output port 38 side passes through the drain port 39 and the communication passage 45. It is discharged into the oil sump chamber 49. As a result, the oil sump chamber 49 is filled with the working oil, and when the oil level becomes equal to or higher than the upper end of the drain pipe 53, the working oil in the sump chamber 49 flows out to the drain pipe 53 and returns to the oil tank 46. Therefore, the oil sump chamber 49 is always filled with hydraulic oil up to the upper end level of the drain pipe 53.
[0032]
Since the orifice 50 connected to the damper oil chamber 36 is submerged below the oil level, the oil in the oil reservoir chamber 49 also fills the damper oil chamber 36 through the orifice 50. If bubbles are present in the oil in the damper oil chamber 36, the bubbles move from the orifice 50 to the oil sump chamber 49, guided to the slope 54 on the ceiling of the chamber 49, toward the drain pipe 53, and drained. The oil that flows out to the pipe 53 is discharged to the oil tank 46. Thus, the damper oil chamber 36 is always filled with oil that does not contain bubbles.
[0033]
Therefore, if the spool 22 undergoes axial vibration due to a sudden change in the output of the output rod 14 or a sudden change in the output hydraulic pressure while controlling the output hydraulic pressure, the damper oil chamber 36 and the oil oil are Since hydraulic oil flows back and forth between the reservoir chambers 49 through the orifice 50, the vibration of the spool 22 in the axial direction can be suppressed by the damping effect of the orifice 50. Therefore, the pulsation of the output hydraulic pressure due to the vibration of the spool 22 can be prevented in advance. A stable operating state of the operating unit 44 can be ensured.
[0034]
By the way, the oil sump chamber 49 communicates with the damper oil chamber 36 through the horizontal orifice 50 located at the uppermost portion of the damper oil chamber 36, so that the oil sump chamber 49 is disposed directly beside the damper oil chamber 36. Therefore, the valve body 20 can be made more compact than when the oil sump chamber 49 is disposed above the damper oil chamber 36. In addition, since the slope 54 rising from the orifice 50 toward the drain pipe 53 is formed on the ceiling of the oil sump chamber 49, the bubbles that have flowed from the damper oil chamber 36 through the orifice 50 to the oil sump chamber 49 are smoothly drained. The discharge from the drain pipe 53 can be promoted.
[0035]
Further, since the space above the drain pipe 53 in the oil sump chamber 49 is inevitably reduced in volume due to the formation of the inclined surface 54, the amount of residual air in the space can be reduced. Enables early discharge of residual air.
[0036]
Furthermore, since the damper oil chamber 36 also serves as a spring chamber that houses the return spring 23 of the spool 22, there is no need to provide a dedicated spring chamber, which can contribute to the compactness of the hydraulic control valve 1.
[0037]
On the other hand, in the linear solenoid portion S, when the output rod 14 is operated and retracted, the output rod 14 is slid by the first and second bushes 16 ₁ and 16 ₂ fitted in the first and second bearing holes 15 _2. In this case, the first and second bushes 16 ₁ and 16 ₂ have first and second communication grooves 17 ₁ and 17 ₂ on their outer peripheral surfaces, respectively. distribution of air or oil occurs between the groove 17 _1, 17 ₂ through the first and second bushes 16 _1, 16 ₂ of the two ends, it is possible to ensure smooth sliding of the output rod 14. Since also the movable core 8 comprises a third communication groove 17 ₃ on the outer circumferential surface, and the outer peripheral surface of the movable core 8, it is set to the minimum gap between the inner peripheral surface of the yoke 6 and the fixed core 7, the movable operation of the core 8, when retracted, cause circulation of air or oil in across the movable core 8 through the third communication groove 17 _3, can ensure smooth movement of the movable core 8.
[0038]
The present invention is not limited to the above-described embodiments and modifications, and various design changes can be made without departing from the gist thereof.
[0039]
【The invention's effect】
As described above, according to the present invention, the linear solenoid portion, the spool that is driven forward by the output of the linear solenoid portion, the valve body that is slidably fitted to the spool, and the spool is biased in the backward direction. The valve body is provided with a supply port connected to the hydraulic pressure source, an output port connected to the hydraulic operation unit, and a drain port opened to the oil tank, while the spool is moved forward and backward. The first land portion that cuts off / conducts between the output port and the drain port according to the condition, the second land portion that conducts / cuts off between the supply port and the output port, and connects the first and second land portions. And a reaction oil that receives from the output port hydraulic pressure that urges the spool in the backward direction between the valve body and the spool. Each of the first land portion and the second land portion adjacent to the annular groove portion in a hydraulic control valve that draws output hydraulic pressure in accordance with the output of the linear solenoid portion from the supply port to the output port. A pressure reduction control groove and a pressure increase control groove that are open on the outer peripheral surfaces of the first land portion and the second land portion are provided on the end face, respectively , and a damper oil chamber is provided on the valve body so that the end face of the spool faces. An oil sump chamber that communicates with the oil tank is provided directly adjacent to the damper oil chamber, and the drain port is opened to the oil tank through the oil sump chamber, while an orifice is provided on the upper portion of the damper oil chamber. The oil reservoir chamber is communicated with the oil reservoir chamber, and the outlet of the oil reservoir chamber to the oil tank is provided at a position higher than the orifice so that the orifice is below the oil level of the oil reservoir chamber. Since then location, when the pressure increase control of the output hydraulic pressure, that is, when the inter-supply port and the output port is turned by the second land portion of the spool, between the supply and output ports by pressure-increase control grooves of the second land portion When the output hydraulic pressure is reduced, that is, when the output port and the drain port are connected by the first land portion of the spool, the output port and the drain port are connected by the pressure reduction control groove of the first land portion. to result in Ru, therefore, the amount of conduction between conductive port to the movement of the spool in the minimum, the increase and decrease control of the output pressure can be stably performed well. In addition, the pressure increase / decrease control groove can bring about a relatively large flow rate change with a slight change in the opening degree, and thus enables quick control of the output hydraulic pressure with a small stroke of the movable core.
[0040]
Since the oil in the sump chamber also fills the damper oil chamber through the orifice, if the spool vibrates in the axial direction while controlling the output hydraulic pressure, the damper oil chamber Since the hydraulic oil flows between the oil sump chambers through the orifice, the vibration of the spool in the axial direction can be suppressed by the damping effect of the orifice. Can be ensured. In addition, since the oil sump chamber communicates with the damper oil chamber via an orifice located at the top of the damper oil chamber, the oil sump chamber can be disposed directly beside the damper oil chamber. The valve body can be made compact compared to the case where it is arranged in the upper part of the oil chamber.
[Brief description of the drawings]
FIG. 1 is a longitudinal sectional view of a hydraulic control valve according to an embodiment of the present invention.
FIG. 2 is an enlarged view of the linear solenoid portion of FIG.
3 is an enlarged view of the valve portion of FIG. 1 (resting state).
4 is a cross-sectional view taken along line 4-4 of FIG. 3;
FIG. 5 is a plan view of a spool.
6 is a sectional view taken along line 6-6 in FIG. 3;
7 is a cross-sectional view taken along line 7-7 in FIG.
8 is an enlarged view corresponding to FIG. 3, showing the operating state of the valve portion.
[Explanation of symbols]
S ... Solenoid part V ... Valve part 1 ... Hydraulic control valve 20 ... Valve body 22 ... Spool 23 ... Return spring 25 _1. First land part 25 _2.・ Second land portion 26 ₁・ ・ Annular groove (first annular groove)
27 ... Pressure increase control groove 28 ... Pressure reduction control groove 29 ... Ring groove 35 ... Reaction force oil chamber
36 ... Damper oil chamber 37 ... Supply port 38 ... Output port 39 ... Drain port 42 ... Hydraulic power source 44 ... Hydraulic actuator 46 ... Oil tank
49 ... Oil sump chamber
50 ... Orifice

Claims (1)

A linear solenoid part (S), a spool (22) driven forward by the output of the linear solenoid part (S), a valve body (20) for slidably fitting the spool (22), and the spool (22 ) In the backward direction, and the valve body (20) has a supply port (37) connected to the hydraulic power source (42) and an output port (connected to the hydraulic operating part (44)). 38) and a drain port (39) opened to the oil tank (46), while the spool (22) is provided with the output port (38) and the drain port (39) according to its forward / backward movement. A first land portion (25 ₁ ) that cuts off and conducts between them, a second land portion (25 ₂ ) that conducts and cuts off between the supply port (37) and the output port (38), and the first and second run Part (25 _1, 25 ₂₎ annular groove connecting the (26 ₁₎ and a provided further wherein between the valve body (20) and the spool (22), the hydraulic pressure for biasing the backward direction the spool (22) A reaction force oil chamber (35) for receiving the pressure from the output port (38) is provided, and the output hydraulic pressure corresponding to the output of the linear solenoid part (S) is drawn from the supply port (37) to the output port (38). In the hydraulic control valve
The first land portion (25 ₁ ) and the second land portion (25 ₂ ) are formed on the end faces of the first land portion (25 ₁ ) and the second land portion (25 ₂ ) adjacent to the annular groove portion (26 ₁ ). ) Are provided with a pressure-reducing control groove (28) and a pressure-increasing control groove (27) that are opened on each outer peripheral surface ,
The valve body (20) is provided with a damper oil chamber (36) facing the end surface of the spool (22), and the oil communicated with the oil tank (46) is directly adjacent to the damper oil chamber (36). A reservoir chamber (49) is provided, and the drain port (39) is opened to the oil tank (46) through the oil reservoir chamber (49), while an upper portion of the damper oil chamber (36) is provided as an orifice (50). The oil reservoir chamber (49) is communicated with the oil reservoir chamber (49), and the outlet port of the oil reservoir chamber (49) to the oil tank (46) is provided at a position higher than the orifice (50). A hydraulic control valve, which is located below the oil level in the oil sump chamber (49) .

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