JP4244346B2 - Hydraulic control valve - Google Patents

Description

  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 first port, a second port, and a third port, and the spool is closed between the second port and the third port at the retreat limit of the spool. The ports are electrically connected, the first port and the second port are blocked by the advance of the spool, and the second port and the third port are electrically connected. The valve body includes the spool. A reaction force oil chamber into which hydraulic pressure is applied in a direction opposite to the urging force of the return spring or the output of the linear solenoid portion, and one end surface of the spool face the spool. An improvement of the hydraulic control valve provided with a damper oil chamber for damping Le.

  An example of such a conventional hydraulic control valve is shown in FIG. In this type, at least the tip of the valve body opposite to the linear solenoid is immersed in oil in the oil tank, and a damper oil chamber communicating with the oil through the orifice is provided in the valve body. The chamber is always filled with oil, and when the spool vibrates, the spool is damped by the squeezing resistance against the oil of the orifice.

  The conventional hydraulic control valve as described above has an arrangement restriction that the damper oil chamber must be immersed in the oil in the oil tank in order to fill the damper oil chamber with oil. In addition, since the drop between the oil level in the oil tank and the damper oil chamber is relatively small, the oil supply from the oil tank to the damper oil chamber using the drop is lacking in speed, and the hydraulic control valve There is a risk that a delay in the operation of the damper oil chamber may occur in the early stage of operation. In addition, since the components of the hydraulic control valve are completely different between the normally open type and the normally closed type, when manufacturing both types of hydraulic control valves, the cost of each is reduced. Is difficult.

  The present invention has been made in view of such circumstances. There is no restriction on the arrangement with respect to the oil tank, and the oil can be quickly supplied to the damper oil chamber at the initial stage of operation. It is an object of the present invention to provide the hydraulic control valve that does not cause a delay and that can be easily configured as both a normally closed type and a normally open type.

In order to achieve the above object, the present invention provides a linear solenoid part, a spool driven forward by the output of the linear solenoid part, a valve body in which the spool is slidably fitted, and the spool attached in the backward direction. The valve body is provided with a first port, a second port, and a third port, and the spool is closed between the second port and the third port at the retreat limit of the spool. The first port and the second port are electrically connected, the first port and the second port are blocked by the advance of the spool, and the second port and the third port are electrically connected, The valve body includes a reaction oil chamber into which a hydraulic pressure is introduced to press the spool in a direction opposite to the biasing force of the return spring or the output of the linear solenoid portion, and the spool. In the hydraulic control valve provided with a damper oil chamber for damping the spool by facing one end surface of the valve body, the first port, the second port, and the third port of the valve body are connected to the linear solenoid portion side from the side. The spool is arranged in order, and the spool has a first land portion that slides in the valve body so as to cut off and conduct between the first port and the second port according to the advance / retreat thereof, and the advance thereof. A second land portion that slides in the valve body so as to conduct / cut off between the second port and the third port in response to retreat, and the inside of the valve body with a diameter different from that of the second land portion. Are formed in order from the linear solenoid part side, and a hydraulic operation part is connected to the second port, and the valve body has a boundary part between the second and third land parts. Faced A reaction oil chamber that communicates with the second port, and a damper oil chamber adjacent to the reaction oil chamber with the third land portion interposed therebetween, and oil leaks from the reaction oil chamber to the damper oil chamber. A sliding gap that can be supplied is provided between the third land portion and the valve body, and the opening of the recess formed in the joint surface of the valve body is closed by the mounting surface of the transmission case to which the valve body is joined, An oil sump chamber is defined around the damper oil chamber, and the oil sump chamber (49) and the upper portion of the damper oil chamber (36) are communicated with each other through an orifice (50). The first feature is that the axis (L) is disposed so as to pass through the opening of the recess (51) .

  According to the present invention, in addition to the first feature, the first port is opened to an oil tank, the second port is connected to a hydraulic operation unit, the third port is connected to a hydraulic source, and the second port A second feature is that the third land portion is formed to have a smaller diameter than the land portion.

  In addition to the first feature of the present invention, a hydraulic pressure source is connected to the first port, the third port is opened to an oil tank, and the third land portion has a larger diameter than the second land portion. The formation is the third feature.

According to a first aspect of the present invention, during operation of the linear solenoid portion, when the hydraulic pressure Ru is supplied to the reaction force oil chamber, the hydraulic pressure of the next through the sliding gap between the third land portion and the valve body Leakage will be actively supplied to the damper oil chamber. Therefore, since the damper oil chamber can be filled with oil from the initial operation of the hydraulic control valve without delay, the damper oil chamber can always exhibit a good damping function for the spool. In addition, the damper chamber does not need to be immersed in the oil in the oil tank as in the prior art, so there is no restriction on the arrangement of the hydraulic control valve, and the versatility can be improved.

  In addition, the hydraulic source and the oil tank are selectively connected to the first port and the third port, and the size relationship between the diameters of the second land and the third land is selected. Any type of hydraulic control valve can be easily configured, and each hydraulic control valve can be provided at low cost.

Furthermore, by closing the opening of the recess formed in the joint surface of the valve body with the mounting surface of the transmission case to which the valve body is joined, an oil sump chamber is defined around the damper oil chamber. Because the orifice communicates with the upper part of the damper oil chamber through the orifice, air bubbles generated in the damper oil chamber can be quickly discharged together with the oil through the orifice to the oil sump chamber. Since the orifice is arranged so that its axis passes through the opening of the recess formed in the joint surface of the valve body, the damper oil is not obstructed by the outer wall of the oil sump chamber. An orifice can be drilled in the partition between the chamber and the oil sump chamber, and after the drilling, no discard hole is required, so there is no need for a conventional closure plug for closing the discard hole. It may contribute to the reduction of the door.

  Further, according to the second feature of the present invention, the first port is opened to the oil tank, the hydraulic power source is connected to the third port, and the third land is formed with a smaller diameter than the second land. The type of hydraulic control valve can be easily configured, and the hydraulic control valve can be provided at low cost.

  Further, according to the third feature of the present invention, the hydraulic pressure source is connected to the first port, the third port is opened to the oil tank, and the third land is formed with a larger diameter than the second land. An open hydraulic control valve can be easily configured, and the hydraulic control valve can be provided at low cost.

  Embodiments of the present invention will be described below on the basis of preferred embodiments of the present invention shown in the accompanying drawings.

In the accompanying drawings, FIG. 1 is a bottom view of a normally closed type hydraulic control valve according to the present invention, FIG. 2 is an enlarged sectional view taken along line 2-2 in FIG. 1, and FIG. 3 is an enlarged view taken along line 3-3 in FIG. sectional view, FIG. 4 4 of FIG. 1 and FIG. 3 - 4-wire cross-sectional view, and FIG. 5 is in the form that constitutes the hydraulic control valve of the present invention to normally open, a corresponding view of the FIG.

  First, an embodiment in which the hydraulic control valve of the present invention is configured as a normally closed type will be described with reference to FIGS.

In FIG. 1, a hydraulic control valve 1 is for controlling clutch hydraulic pressure in, for example, an automatic transmission for automobiles, and is composed of a linear solenoid part S and a valve part V. The valve body 20 of the valve part V is an automobile. The transmission case 2 (see FIG. 4) is joined to the mounting surface 2f by a bolt 5.

  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.

  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.

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

  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.

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.

  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 abutment 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.

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. first and second land portions 25 _1, 25 ₂ are formed in the same diameter, the diameter D ₃ of the third land portion 25 ₃ is set to be slightly smaller than the diameter D ₂ of the second land portion 25 _2.

On the other hand, the valve hole 21 of the valve body 20 includes a working chamber 30 which abutment faces of the output rod 14 and the spool 22, freely first land portion 25 ₁ adjacent to the working chamber 30 is slid all the time The first annular land portion 31 ₁ to be fitted, the second annular land portion 31 _{2 to} which the opposing end portions of the first land portion 25 ₁ and the second land portion 25 ₂ are alternately fitted and detached, and the second land portion The third annular land portion 31 _{3 in} which 25 ₂ is always slidably fitted, the fourth annular land portion ₃ 14 in which the third land portion 25 ₃ is slidably fitted, and the first and second annular shapes The first port oil chamber 32 disposed so as to be sandwiched between the land portions 31 ₁ , 31 ₂ , and the first and second land portions 25 ₁ , 25 ₂ of the spool 22 inside the second annular land portion 31 ₂ a second port oil chamber 33 is sandwiched are sandwiched between the second and third annular land portions 31 _2, 31 ₃ A third port oil chamber 34, the second and third annular land portions 31 _2, 31 ₃ reaction force oil chamber 35 which faces the boundary of including a second annular groove 26 ₂ disposed on the spool 22 and the plug 24 is provided with a damper oil chamber 36 facing both opposed end faces, and the return spring 23 is accommodated in the damper oil chamber 36.

The outer peripheral surface of the third land portion 25 _3, the cylindrical sliding surface 25 ₃ to be fitted to the fourth annular land portion 31 ₄
a and a tapered surface 25 ₃ b having a smaller diameter from the cylindrical sliding surface 25 ₃ a toward the reaction force oil chamber 35. The third and the land portion 25 ₃ of the cylindrical sliding surface 25 ₃ a between the fourth annular land portion 31 _4, the sliding gap g which may leak supplying oil from the reaction force oil chamber 35 in the damper oil chamber 36 Is provided.

  Further, in the valve body 20, in order from the linear solenoid part S side, a breather port 40 connected to the working chamber 30, a first port 37 connected to the first port oil chamber 32, and a third port 39 connected to the third port oil chamber 34. Is provided. The breather port 40 and the first port 37 are opened to a later-described oil sump chamber 49 (see FIGS. 1 and 4) in the valve body 20, and the second port 38 is a hydraulic operation such as a clutch in the automatic transmission. The third port 39 is connected to a hydraulic pump 42 as a hydraulic pressure source via a supply oil passage 41 of the transmission case 2.

  The second port oil chamber 33 is also communicated with the reaction force oil chamber 35 via a feedback oil passage 48 formed in the spool 22.

  Thus, when the linear solenoid portion S is not energized, the spool 22 is configured to block between the third port 39 and the second port 38 when held in the retracted position by the urging force of the return spring 23. Therefore, the hydraulic control valve 1 is a normally closed type.

  As shown in FIGS. 1 and 4, the valve body 20 is provided with an oil reservoir chamber 49 around the damper oil chamber 36. This oil sump chamber 49 is defined by closing the opening of the recess 51 formed in the joint surface 20f of the valve body 20 with the mounting surface 2f of the transmission case 2 to which the valve body 20 is joined. The uppermost portion of the damper oil chamber 36 is communicated with the oil reservoir chamber 49 through an orifice 50, and oil discharged from the damper oil chamber 36 through the orifice 50 is stored in the oil reservoir chamber 49.

  The orifice 50 is drilled into the partition wall 20a between the damper oil chamber 36 and the oil sump chamber 46 at an obliquely upward angle from the opening of the recess 51 before the valve body 20 is joined to the transmission case 2. In order to enable drilling, the axis L of the orifice 50 is arranged to pass through the opening of the recess 51.

  The transmission case 2 is provided with a drain oil hole 52 that opens the oil sump chamber 49 to the oil tank 46 so that the oil sump chamber 49 is in an atmospheric pressure state. At that time, the opening of the drain oil hole 52 to the oil reservoir chamber 49 is disposed above the orifice 50 so that the oil transferred from the orifice 50 to the oil reservoir chamber 49 sinks the orifice 50 in the oil. The oil is stored in the oil sump chamber 49 and then discharged to the drain passage 52.

  Next, the operation of the normally closed hydraulic control valve 1 configured as described above will be described.

  When the linear solenoid portion S is not energized, the spool 22 occupies the right movement limit position (retreat limit) with the urging force of the return spring 23 and shuts off the third port 39 and the second port 38 as shown in FIG. At the same time, since the second port 38 and the first port 37 are electrically connected to each other, the hydraulic operation unit 44 is communicated with the first port 37 and maintained in an inoperative state even when the hydraulic pump 42 is in operation.

When the coil 10 of the linear solenoid section S is energized during the operation of the hydraulic pump 42, an electromagnetic force corresponding to the current value acts as a leftward thrust on the spool 22 via the output rod 14, and the thrust 22 Is moved forward (to the left in FIG. 3), the second port 38 and the first port 37 are disconnected, and the third port 39 and the second port 38 are electrically connected. The hydraulic pressure is immediately supplied to the reaction force oil chamber 35 through the passage 48. Then, in this reaction force oil chamber 35, a rightward thrust obtained by multiplying the area difference between 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 by the hydraulic pressure is a linear solenoid portion. It acts as a reaction force on the spool 22 so as to oppose the output of S. Therefore, the spool 22 is moved so that the leftward thrust generated by the electromagnetic force of the linear solenoid portion S and the resultant force of the rightward biasing force of the return spring 23 and the rightward reaction force of the hydraulic force of the reaction oil chamber 35 are balanced. Move to control the opening of the third port 39. That is, when the left output of the linear solenoid portion S is large, the first land portion 25 ₁ is moved forward by the spool 22 moving forward to the left.
Shuts off between the first port 37 and the second port 38, and the second land portion 25 ₂ conducts between the second port 38 and the third port 39, so that the hydraulic pressure of the second port 38 increases. When the resultant force increases to the left, the second land portion 25 ₂ blocks the third port 39 and the second port 38 by the backward movement of the spool 22 and the first land portion 25 ₁ Since the 2 port 38 and the first port 37 are electrically connected, the hydraulic pressure of the second port 38 is reduced. By controlling the opening degree of the second port 38 in this way, the hydraulic pressure corresponding to the current value supplied to the coil 10 can be taken out from the second port 38 and supplied to the hydraulic operation unit 44. .

Furthermore In conjunction to the advancement of the spool 22, the hydraulic pressure counter-force oil chamber 35 from the third port 39 as described above is supplied, a part of the hydraulic pressure, between the third land portion 25 ₃ and the valve body 20 Leakage is positively supplied to the adjacent damper oil chamber 36 through the sliding gap g. Therefore, the damper oil chamber 36 can be filled with oil without delay from the initial operation of the hydraulic control valve 1. Therefore, the damper oil chamber 36 can function normally without delay from the initial operation of the hydraulic control valve 1. That is, when the spool 22 vibrates, the spool 22 can be damped by the restriction resistance of the orifice 50 generated when the oil in the damper oil chamber 36 moves back and forth along the orifice 50, and the output hydraulic pressure due to the vibration of the spool 22 is controlled. Thus, a stable operation state of the hydraulic operation unit 44 can be ensured.

  When the damper oil chamber 36 is filled with the leak oil from the reaction force oil chamber 35, excess oil is discharged from the orifice 50 to the adjacent oil reservoir chamber 49 and stored. Then, when the oil level in the oil sump chamber 49 reaches a predetermined level until the orifice 50 is submerged below the oil level, it overflows from the drain oil hole 52 and returns to the oil tank 46.

  As described above, the damper oil chamber 36 is positively supplied with leak oil from the reaction oil chamber 35, and the orifice 50 is then discharged into the oil reservoir chamber 49 and immersed in the accumulated oil. As a result, the damper oil chamber 36 can always be reliably filled with oil, and a good damping function of the damper oil chamber 36 can be obtained.

  Further, since the orifice 50 is opened at the uppermost part of the damper oil chamber 36, bubbles generated in the damper oil chamber 36 can be quickly discharged together with the oil through the orifice 50 to the oil reservoir chamber 49 side. A better vibration suppression function can be obtained.

  By the way, the axis L of the orifice 50 is disposed so as to pass through the downward opening of the recess 51 of the valve body 20, so that the damper oil chamber 36 and the oil sump are not obstructed by the outer wall of the oil sump chamber 46. Since the orifice 50 can be drilled in the partition wall 20a between the chambers 46 and no drilling hole is required after the drilling process, a conventional closure plug for closing the discarding hole is unnecessary, which reduces the cost. Can contribute.

On the other hand, the outer peripheral surface of the third land portion 25 _3, as described above, the cylindrical sliding surface 25 ₃ a to be fitted to the fourth annular land portion 31 _4, the reaction force oil from the cylindrical sliding surface 25 ₃ a since is composed of a tapered surface 25 ₃ b whose diameter toward the chamber 35, the third land portion 25 due to the leakage oil through the third land portion 25 ₃ and the fourth sliding gap g between the annular land portion 31 _{4 3} even when it is biased to one side of the fourth annular land portion 31 ₄ receives the side thrust, one side of the cylindrical sliding surface 25 ₃ a skilled on the inner peripheral surface of the fourth annular land portion 31 ₄ contact but tapered surface 25 ₃ b is never in contact with the fourth annular land portion 31 ₄ over the entire circumference. Accordingly, the hydraulic pressure of the reaction force oil chamber 35 acts on the entire circumferential surface of the tapered surface 25 ₃ b, will be given a third land portion 25 ₃ two aligning force, the third land portion 25 ₃ a it is possible to ensure smooth sliding with respect to 4 annular land portion 31 _4.

  Next, an embodiment in which the hydraulic control valve of the present invention is configured as a normally open type will be described with reference to FIG.

In this embodiment, in the valve body 20, the connection state of the second port 38 to the hydraulic operation unit 44 is the same as that in the above embodiment, but the first port 37 is connected to the hydraulic pump 42 and the third port 39 is the oil tank 46. Released. In the spool 22, the second land portion 25 ₂ of diameter D ₂ and the third diameter D ₃ of the land portion 25 ₃ is set as D ₂ <D _3. Since other configurations are the same as those of the normally closed hydraulic control valve 1 of the above embodiment, the same reference numerals are given to portions corresponding to those of the above embodiment in FIG.

  The operation of the normally open hydraulic control valve 1 configured in this way will be described.

When the linear solenoid part S is not energized, the spool 22 occupies the right movement limit position (retreat limit) with the urging force of the return spring 23, and conducts between the first port 37 and the second port 38, and the second port 38 and Since the third port 39 is shut off, when the hydraulic pump 42 is driven by the engine to generate hydraulic pressure, the hydraulic pressure is transmitted to the reaction force oil chamber 35 through the supply oil passage 41, the first port 37 and the feedback oil passage 48. To do. Then, in this reaction force oil chamber 35, the leftward thrust obtained by multiplying the area difference between the opposed end surfaces of the small-diameter second land portion 25 ₂ and the large-diameter third land portion 25 ₃ of the spool 22 by the hydraulic pressure is returned to the return spring 23. It acts on the spool 22 as a reaction force so as to oppose the urging force.

On the other hand, when the coil 10 of the linear solenoid unit S is energized, an electromagnetic force corresponding to the current value acts on the spool 22 via the output rod 14 as a leftward thrust. As a result, the spool 22 balances the three forces of the leftward thrust generated in the reaction oil chamber 35 and the resultant leftward thrust due to the electromagnetic force of the linear solenoid portion S, and the rightward thrust by the return spring 23. The spool 22 moves to control the opening degree of the first port 37. That is, when the resultant force of the left is larger than the right thrust, by advancing to the left of the spool 22, the first land portion 25 ₁ is cut off between the first port 37 and second port 38, a second land portion 25 ₂
Since the second port 38 and the third port 39 are electrically connected to each other, the hydraulic pressure of the second port 38 is decreased. On the contrary, when the leftward thrust becomes larger than the leftward resultant force, the spool 22 is retracted to the right. , The second land portion 25 ₂ blocks between the second port 38 and the third port 39 and the first land portion 25 ₁ conducts between the first port 37 and the second port 38. Hydraulic pressure increases. By controlling the opening degree of the second port 38 in this way, the hydraulic pressure corresponding to the current value supplied to the coil 10 can be taken out from the second port 38 and supplied to the hydraulic operation unit 44. .

Since the hydraulic control valve 1 is normally a normally open type in which the first port 37 is opened, when the hydraulic pump 42 is operated, the generated hydraulic pressure is immediately supplied to the reaction force oil chamber 35 as described above. . Moreover, this reaction force oil chamber 35, the damper oil chamber 36 adjacent thereto, because they communicate with each other through the third land portion 25 ₃ and the fourth sliding gap g between annular land portions 31 _4, anti When hydraulic pressure is supplied to the hydraulic oil chamber 35, an oil leak from the reaction force oil chamber 35 to the damper oil chamber 36 immediately occurs, and the damper oil chamber 36 can be filled with oil. Accordingly, as in the case of the normally closed hydraulic control valve 1, the damper oil chamber 36 can function normally without delay from the initial operation of the hydraulic control valve 1. The vibration can be suppressed, and the pulsation of the output hydraulic pressure due to the vibration of the spool 22 can be prevented, and a stable operation state of the hydraulic operation unit 44 can be ensured.

As described above, the hydraulic pump 42 and the oil tank 46 are selectively connected to the first port 37 and the third port 39 of the valve body 20, and the second land portion 25 ₂ and the third land portion 25 _{3 are connected.} By selecting the magnitude relationship of the diameters, both the normally closed type and the normally open type hydraulic control valves 1 can be easily configured, and the respective hydraulic control valves 1 can be provided at low cost.

  In addition, in both the normally closed type and the normally open type hydraulic control valve 1, when the linear solenoid part S is operated, when the hydraulic pressure is supplied to the reaction force oil chamber 35, the hydraulic pressure is supplied to the third land part and the valve body. As a result, the damper oil chamber 36 can be filled with oil without delay from the initial operation of the hydraulic control valve 1. The damper oil chamber 36 can always exhibit a good vibration damping function with respect to the spool 22, and the damper oil chamber 36 does not need to be immersed in oil in the oil tank as in the prior art. There is no restriction on the arrangement of 1 and versatility can be improved.

  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.

The bottom view of the form which constituted the hydraulic control valve of the present invention in the normally closed type. 2-2 line expanded sectional view of FIG. FIG. 3 is an enlarged sectional view taken along line 3-3 in FIG. 1. FIG. 3 is a cross-sectional view taken along line 3-3 in FIGS. 1 and 3. FIG. 4 is a view corresponding to FIG. 3 in a form in which the hydraulic control valve of the present invention is configured as a normally open type. It is sectional drawing which shows an example of the conventional hydraulic control valve.

Explanation of symbols

L ・ ・ ・ ・ ・ ・ (Orifice) axis
S ・ ・ ・ ・ ・ ・ Solenoid 1 ・ ・ ・ ・ ・ ・ Hydraulic control valve
2 ・ ・ ・ ・ ・ ・ Mission case
2f: Mounting surface 20: Valve body
20 f ··· Joint surface 22 ··· Spool 23 · · · Return spring 25 ₁ ··· First land portion 25 ₂ ··· Second land portion 25 ₃ ··· Third Land 35 ... Reaction force chamber 36 ... Damper oil chamber 37 ... First port 38 ... Second port 39 ... Third port 42 ... ... Hydraulic sources (hydraulic pumps)
44 ...... Hydraulic operation part 46 ...... Oil tank 49 ...... Oil sump chamber 50 ...... Orifice
51 ... concave portion
g ・ ・ ・ ・ Sliding gap

Claims (3)

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 reverse direction, the valve body (20) is provided with a first port (37), a second port (38) and a third port (39), and the spool (22), at the retreat limit of the spool (22), the second port (38) and the third port (39) are disconnected and the first port (37) and the second port (38) are electrically connected. The first port (37) and the second port (38) are blocked by the advancement of the spool (22), and the second port (38) and the third port (39) are electrically connected. The valve body 20) includes a reaction force oil chamber (35) into which hydraulic pressure is introduced to push the spool (22) in a direction opposite to the biasing force of the return spring (23) or the output of the linear solenoid part (S); , A hydraulic control valve provided with a damper oil chamber (36) for damping the spool (22) by facing one end surface of the spool (22),
The first port (37), the second port (38), and the third port (39) of the valve body (20) are arranged in that order from the linear solenoid part (S) side, and are connected to the spool (22). The first land portion (25 ₁ ) that slides in the valve body (20) so as to cut off and conduct between the first port (37) and the second port (38) according to the forward and backward movement. And a second land portion (25 ₂ ) that slides in the valve body (20 2) so as to conduct and block between the second port (38) and the third port (39) according to the forward / backward movement. ) And a third land portion (25 ₃ ) sliding in the valve body (20) with a diameter different from that of the second land portion (25 ₂ ) are sequentially formed from the linear solenoid portion (S) side. The hydraulic port (4) is connected to the second port (38). ) With connecting, wherein the valve body (20), the second and third land portion (25 _2, 25 ₃₎ a reaction force oil which communicates with the second port (38) to face a boundary of A chamber (35) and a damper oil chamber (36) adjacent to the reaction force oil chamber (35) with the third land portion (25 ₃ ) sandwiched between the chamber and the damper oil chamber (35). A sliding gap (g) capable of leaking oil into the chamber (36) is provided between the third land (25 ₃ ) and the valve body (20) .
By closing the opening of the recess (51) formed in the joint surface (20f) of the valve body (20) with the mounting surface (2f) of the transmission case (2) to which the valve body (20) is joined, An oil reservoir chamber (49) is defined around the damper oil chamber (36). The oil reservoir chamber (49) and the upper portion of the damper oil chamber (36) are communicated with each other through an orifice (50). 50) is arranged such that its axis (L) passes through the opening of the recess (51) . The hydraulic control valve according to claim 1,
The first port (37) is opened to the oil tank (46), and a hydraulic pressure source (42) is connected to the third port (39) so that the third land portion is connected to the second land portion (25 ₂ ). A hydraulic control valve characterized in that (25 ₃ ) has a small diameter. The hydraulic control valve according to claim 1,
A hydraulic pressure source (42) is connected to the first port (37), the third port (39) is opened to an oil tank (46), and the third land portion (25 ₂ ) is connected to the third land portion (25 ₂ ). A hydraulic control valve characterized in that 25 ₃ ) has a large diameter.

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