• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The present invention provides an apparatus for controlling a hydraulic pressure usable for a clutch wherein the appratus is employed for a transmission mounted on a construction machine or the like in such a manner that it is provided separately for a plurality of clutches 1 and it is controlled individually. The apparatus includes a first valve 3 for allowing a large amount of hydraulic oil to flow in the clutch and a second valve 4 for electronically controlling a clutch pressure so that the termination of filling and the clutch pressure are detected by a simple structural arrangement on the basis of a displacement of a spool 21 for the first valve 3 and a separately disposed piston. In addition, appearing of an overshoot pressure on the termination of filling is prevented by providing a difference in pressue receiving areas on the spool 21 for the first valve.
    公开号:SU1753958A3
    申请号:SU884613164
    申请日:1988-11-24
    公开日:1992-08-07
    发明作者:Асаямо Есио；Тсубота Макио；Окура Ясунори；Сато Такаюки
    申请人:Кабусики Кайся Комацу Сейсакусе (Фирма)；
    IPC主号:
    专利说明:

    a hydraulic cylinder for the drive of a friction clutch made in accordance with the third embodiment of the invention; in fig. 7 are timing diagrams illustrating, by way of example, a valve operation for adjusting hydraulic pressure in accordance with a third embodiment of the present invention; in fig. 8 is a block diagram illustrating a design group counteracting by means of pressure detection switches; in fig. 9 is a timing diagram illustrating clutch pressure during a gearshift period at which pressure is released; in fig. 10 is a hydraulic diagram illustrating a fourth embodiment of the invention; in fig. 11 is a timing diagram illustrating clutch pressure during a gearshift period in accordance with the fourth embodiment of the present invention; in fig. 12 is a hydraulic diagram illustrating a fifth embodiment of the invention; in fig. 13 shows an internal valve arrangement for adjusting the hydraulic pressure in the hydraulic cylinder of the friction clutch actuator in accordance with the fifth embodiment; in fig. 14 is a timing diagram, respectively illustrating, by way of example, the operation of a valve for adjusting hydraulic pressure, performed in accordance with the fifth variant; Fig. 15 is a hydraulic circuit showing the couplings, for each of the WHICH a valve is provided for controlling the hydraulic pressure with electronic control.
    Figures 1 and 2 show a first embodiment of the invention, Fig. 1 is a hydraulic diagram of a valve for controlling hydraulic pressure with electronic control suitable for actuating the clutch hydraulic cylinder 1, Fig. 2 schematically shows a section through valve 2.
    As shown in FIG. 1 and 2, valve 2 contains valve 3 for detecting the flow rate of the working fluid, valve 4 for controlling pressure with electronic control and filling detection switch 9, receiving pressure control clamp 4 is activated in response to an electrical signal from control unit 5 The valve 2 for regulating the hydraulic pressure allows the working fluid coming from the pump 6 to flow into it through the inlet 10 and supplies it to the hydrocydial 1 through the outlet 11, At this moment the opening 12 is closed.
    The electronically controlled valve 4 contains a spool 13, the right end of which is in contact with the core 15 of the proportional solenoid 14, and the left end has an elastic support provided by means of a coil spring 16. The hydraulic pressure in the hydraulic
    0 channel 19 enters the hydraulic chamber 18 formed by a spool 13 and a piston 17,
    Valve 3 for flow detection contains spool 21, on the side of which,
    5 facing the outlet 11, a passage 7 is formed. A piston 22 is pressed against the left end surface of the spool 21 to detect filling by means of a coil spring 23.
    0 A cover 25, made of nepii iro metal, is attached to the left surface of the valve housing AO, and an electrical insulating gasket 24 is attached between the cover and the housing. Thus, the cover
    5 25 is electrically isolated from the valve body 40 in the presence of an insulating gasket 24. In addition, several screws 26 for fastening the cover are electrically isolated from the cover 25 by means of several insulating sleeves 27. To the cover 25 are connected a lead wire 28, which in turn is connected to point, and between the resistances RI and R2, which are connected to each other in series.
    5 The opposite ends of the resistors RI and R2 supply a predetermined magnitude (for example, 12 V) to the DC voltage. It should be noted that the valve body 40 is closed to ground.
    0 With this design, the piston 22 is always in contact with the housing 40. However, the piston 22 is usually not in contact with the ferrous metal cover 25, but comes into contact with it
    5 When moving s in the left direction, as seen in the drawing.
    In accordance with another embodiment, the spool 21, having a hinged pin 22 attached thereto, can rest on the spring
    0 13 directly.
    FIG. 4 shows a second embodiment of the present invention. This variant is characterized in that the cover 34 of the housing 40 of the valve 2 is equipped with an electro5 magnetic sensor 35, which serves to detect the movement of the spool 21. In particular, the induced voltage generated by the electromagnetic sensor 35 changes as the spool 21 moves and, therefore, the movement of the spool 21 can be detected by detecting the induced voltage. In this case, since the spool 21 of the flow detection valve 3 returns to the position shown in FIG. 4, by the return force of the spring 23, when the hydraulic cylinder 1 is filled with the working fluid in the same way as in the previous embodiment, the end of filling can be accurately detected by detecting the return movement of the spool 21 by means of an electromagnetic sensor.
    FIG. 5 and 6, a third embodiment of the present invention is shown, and components that are the same as those in the previous ones, or similar ones, are denoted by the same reference numbers. Therefore, the description is not necessary to repeat.
    As shown in FIG. 5 and b, the valve 2 for adjusting the hydraulic pressure in the corresponding hydraulic cylinder 1, besides the flow detection valve 3 and the electronically controlled pressure control valve 4, which have the same design as in the previous embodiments, is also equipped with a pressure detection switch 50.
    In this case, the pressure control valve 4 contains the same spool 13 as in the previous embodiments, the right end of which is in contact with the core 15 of the proportional solenoid 14, and the left end has an elastic support in the form of a helical spring 16 The hydraulic pressure in the hydraulic channel 19 flows into a hydraulic chamber 18 formed by a spool 13 and a piston 17.
    Similarly, the flow detection valve 3 comprises the spool 21, which is the same as in the previous embodiments. In the spool 21, the passage opening 7 is made on the side of the outlet opening 11, and the left end of the spool 21 has an elastic support in the form of a helical spring 23.
    At the upper end of the hydraulic channel 19, a switch 50 is installed (a pressure detection relay intended to detect pressure in the hydraulic cylinder 1). The switch 50 comprises a pressure detecting piston 51 and a coil spring 52 for resiliently supporting the piston 51.
    The spring 52 acts on the piston 51 through its guide 53 with an elastic force, the magnitude of which is chosen such that the spring does not allow the piston 51 to be pushed in the opposite direction if the hydraulic pressure in the hydraulic cylinder 1, i.e. the hydraulic pressure in the hydraulic channel 19 is lower than the specified pressure lh (for example, 5 kg / cm). The piston 51 is in contact with the valve body 40, but usually does not come into contact with the ferrous metal cap 54 installed on the upper surface of the body 50. When the piston 51 moves upward against the elastic force of the spring 52
    it comes in contact with the lid 54. The lid 54, made of ferrous metal, is electrically isolated from the housing 40 by means of an insulating gasket 55 interposed between them.
    the cap mounting screws 56 are electrically isolated from the cover 54 by means of insulating sleeves 57 inserted into the cover.
    From the cover 54 leaves the lead wire
    58, connected to point b between the resistances of RI and R2 and connected to each other in series. To point b, U is supplied with a given value (for example, 12 V), the voltage U of direct current, and the case 40
    the valve is connected to ground.
    The valve 2 for adjusting the hydraulic pressure, made in accordance with the above, is connected by a hydraulic cylinder 1 of the corresponding transmission stage, each control valve 2 being provided with the pressure detection switch 50 described above.
    FIG. 12 and 13 show the fifth embodiment of the invention. According to this option, both functions — an execution detection function performed in accordance with the first and second embodiments, and a function of detecting pressure in the hydraulic cylinder, performed in accordance with the third option — through one perceiver.
    In particular, as shown in FIG. 12 and 13, the valve 60 for adjusting the hydraulic pressure comprises a valve 61 for regulating the pressure in the hydraulic cylinder 1, a valve 62 for detecting the flow rate and a sensed unit (sensor) 7 for detecting the filling and the pressure in the hydraulic cylinder 1. The valve 61 for regulating the pressure controls through the control unit 5, where the detection signal S is received from the sensing unit 7. The working fluid obtained from the pump (not shown) enters the valve 60 through the inlet 8 and then goes to the hydraulic cylinder 1 through the outlet 20. this moment, the opening 29 is closed, and the openings 30 and 31 are drain openings.
    The electronically controlled valve 61 for regulating the pressure contains the spool 32. The right end of which is in contact with the core 34 of the proportional solenoid 33, and a screw spring 35 is installed on its left end. In addition, the hydraulic pressure in the hydraulic channel 39 flows through the hydraulic channel 38 a hydraulic chamber 37 formed by the spool 32 and the piston 36.
    The flow detection valve 62 includes a spool 43 forming the hydraulic chambers 44-46. A passage opening 48 is formed between chambers 45 and 46. The spool 43 is designed in such a way that it has three different pressure sensing surfaces Si, 82 and 5z, between which there is a relation expressed by the formulas Si + S3 S2 and $ 2 Sz. At the left end of the spool 43 a screw spring 49 is installed, and at the right end of it another screw spring 59 is installed. When the hydraulic pressure does not enter the chamber 45 and 46, the spool 43 is in the neutral position shown in FIG. 12, in which both springs 49 and 59 are not compressed. Thus, when the spool 43 is in the neutral position, the working fluid entering the valve 62 from the hydraulic channel 42 through the inlet 3 is forced to remain in the hydraulic chamber 44.
    Suppose that the spring constants 49 and 59 are equal to 1 and K2, the hydraulic pressures in the hydraulic chambers 45 m 46 to Pi and 2, and the amount of movement of the spool 43 from the neutral position, then to the spool 43, when it is to the left of the neutral position shown in FIG. 3, rightward acting force
    Pi:
    F-hx + SiP2 + Pi / Sa -82 / ... O).
    Conversely, when the spool 43 is to the right of the neutral position, the left-directed force F2 acts on it, determined by the formula:
    F2 k2x-SiP2-Pi / S3-S2 / ... (2).
    By the way, in this case,
    WHAT K2 kl.
    In particular, in this case, the spring 49 acts as a return spring for the spool 43, and the spring 59 acts as a spring for setting a predetermined pressure in order to detect the hydral pressure in the hydraulic cylinder 1.
    A detection pin 65, made of metal, is mounted in the upper right side of the valve body 69 to detect movement of the spool 43 to the right of
    neutral position shown in fig. 13, against the elastic force of the spring 59. The detecting pin 65 is attached to the valve body 64 by means of a cover 63
    using an electrically insulating gasket 47, and the lead wire 41 extends from the detecting pin 65.
    The lead wire 41 is connected to a point c between the resistances RI and R2 connected to each other in series. Resistors RI and R2 are supplied with a predetermined value (for example, 12 V), the voltage U of a direct current, and the housing 64 is closed to ground. Thus, the sensor for detecting the filling and the hydraulic pressure in the corresponding hydraulic cylinder contains a spring 59 detecting a pin 65 serving as a contact for the spool 43 and a resistance RI and R2,
    A valve 60 for adjusting the hydraulic pressure, provided with a sensing unit 67, is set individually for the couplings of the respective gear stages.
    A device for adjusting the hydraulic pressure in the hydraulic cylinder of the drive of the friction clutch operates as follows.
    In the case of casting cylinder 1
    in the on state using the construction shown in Fig. 1 and, the control unit 5 is forced to turn on the solodeoid 14 of the electronically controlled control valve 4 using a rather large electric current. In doing so, the spool 13 of the control valve 4 moves to the left, with the result that the working fluid coming from the pump 6 goes to
    valve 4 through the inlet 10 and the hydraulic channel 20 The working fluid entered into the control valve 4 flows into the flow detection valve 3 through the hydraulic channel 19 and the orifice 29, and then flows through the through hole 7 in the spool and inlet 11 into the hydraulic cylinder 1. In addition , the working fluid entering through the opening 29 goes into the hydraulic chamber 31 through a hydraulic
    channel 30 in the spool 21.
    This causes the creation of a pressure differential (PD-Pb) between the left and right sides of the passage 7, and under the action of this pressure differential, the spool 21 moves to the left, causing the flow detection valve 3 to open. Consequently, the working fluid entering through the inlet 10 flows directly into the opening 2E and then goes to
    hydraulic cylinder 1 through the passage hole 7.
    On the other hand, since the piston 22 also moves to the left when the spool 21 moves in the left direction, the left end surface of the piston 22 comes into contact with the cap 25. Since at this moment the piston 22 is in contact with the valve body 40, the potential is at and falls to the level of mass potential, as shown in FIG. 3, with the result that there is no voltage at point a.
    The supply of working fluid to the hydraulic cylinder 1 through the flow detection valve 3 continues until the fluid fills it. When the working fluid completely fills the hydraulic cylinder 1, the filling stops, causing the working fluid to stop flowing, causing the pressure differential between the left and right sides of the bore 7 to disappear. Consequently, under the effect of the spring 23 returns, the spool 21 in the flow detection valve 3 moves to the right causing the valve 3 to return to the closed state. On the other hand, when the spool 21 moves to the right after the completion of filling, the piston 22 also moves to the right under the action of the elastic force of the spring 23, and the left end surface of the piston 22 separates from the cover 25, as a result of which U. That is, the end point of the filling can be recognized by detecting the moment of potential increase at point a.
    The voltage signal supplied from point a is inputted to control unit 5, which in turn, upon detecting an increase in the voltage signal, thereby detects the end of filling. After the control unit 5 detects the completion of filling, the force of the electric current supplied to the solenoid 14 is gradually increased, thereby ensuring a gradual increase in pressure acting on the hydraulic cylinder 1. By the way, the control unit 5 is actuated so that the spool 13 moved to the left by a large distance, applying a large force for this electric current to the solenoid 14 at the beginning of the gear shift, after which the spool 21 is kept in the waiting state until the filling is completed, and the current strength odavaemogo the solenoid 14, reduced to a suitable initial level. When control unit 5 detects the end of filling, it then gradually increases the current strength from this initial level. Thus, in accordance with the first embodiment of the present invention, the end of filling can
    to be easily and accurately detected by phasing out through the piston 22 the movement of the spool 21 of the flow detection valve 3 operating depending on the presence or absence of flow
    0 working fluid into the hydraulic cylinder 1, in the form of moving the piston 22 into contact with the cover 25 or moving it from the cover 25 and then electrically detecting the previous movement. In the interim, in this embodiment, the spool 21 rests on the spring 23 through the piston 22. The operation of the device shown in FIG. 5 and 6, with reference to the timing diagrams shown in FIG.
    0 7 to activate the hydraulic cylinder 1 connected to the valve 2 to adjust the hydraulic pressure, the control unit 5 is directed to send the command to the solenoid 14 of the valve 2
    5 start (Fig. 7 a). After the start command is given, the control unit 5 is kept in the waiting state until the end of filling, and the command current is reduced to the level corresponding to the initial value of Pa
    0 hydraulic pressure in the corresponding cylinder.
    In response to the start command, the spool 13 of the pressure regulating valve 3 is moved to the left, and the working fluid coming from the pump 6. flows into the valve 4 through the inlet 10 and the hydraulic channel 20. The working fluid flowing into the valve 4 flows into the flow detection valve 3 through the hydraulic channel 19 and the orifice 29 and further into the hydraulic cylinder 1 through the passage opening 7 and the outlet opening 11. In addition, the working fluid entering through the opening 29 flows into the hydraulic chamber 31 through the hydraulic channel 30 in the spool 21.
    As a result, a pressure differential (Pd - Pb) occurs between the left and right sides of the passage opening 7. and the spool 21 moves under the action of a differential pressure in the left direction, with the result that the flow detection valve 3 opens. The working fluid entering through the inlet 10, flows at the same time directly into the hole 29 and further
    5 through the passage opening 7 into the hydraulic cylinder 1. The flow of the working fluid in this way continues until it completely fills the hydraulic cylinder 1.
    During the time tf of filling the hydraulic cylinder 1 with the working fluid, the hydraulic pressure in the hydraulic cylinder is zero and does not reach the pressure Th set by spring 52, as a result of which the upper end surface of the piston 51 of the switch 50 cannot come into contact with the lid 54 made of ferrous metal . In this operating state, the potential at point b is equal to the magnitude of the voltage resulting from the voltage U by means of resistance RI and R2, as shown in FIG. 7 sec.
    After the completion of filling the hydraulic cylinder 1 with the working fluid, the flow of the liquid is stopped. In this case, the pressure differential on both sides of the passage opening 7 disappears, as a result of which the spool 21 of the flow detection valve 3 moves to the right under the action of the elastic force of the spring 23 and, therefore, the valve 3 returns to the closed state. After the completion of filling, the control unit 5 is made to supply current to the solenoid 14 g by gradually increasing it from the command current value corresponding to the initial pressure, as shown in FIG. 7 a.
    This makes it possible to gradually increase the pressure in the corresponding hydraulic cylinder 1 from the initial pressure Pa (for example, about 2 kg / cm2}, as shown in Fig. 7 in. Since the pressure Th given by the spring 52 considerably exceeds the initial pressure Pa, then when the pressure will exceed the specified value Th, it will force the piston 51 to move against the action of the elastic force of the spring 52. Consequently, the upper face of the piston 51 will come into contact with the cover 54. This will allow the cover 54, made of ferrous metal, about to drive electricity to body 40 closed at ground through piston 51, as a result of which the potential at point b drops to zero, as shown in Fig. 7. Consequently, there will be no voltage at point b,
    In accordance with a third embodiment of the invention, the presence or absence of hydraulic pressure in the hydraulic cylinder 1 is manifested in the form of moving the pressure detecting piston 51 at the upper end of the hydraulic channel 19 until it touches the cover 54 or moves it in the direction away from the cover, the covers 54 can be electrically detected by the change in voltage at point b. Consequently, the presence or absence of hydraulic pressure in the corresponding hydraulic cylinder can be detected by checking the presence or absence of potential at point b.
    In addition, in accordance with this approach, for each of the couplings, a valve 2 is provided for regulating the electronically controlled hydraulic pressure, containing the above-described pressure detection switch 50, moreover, as shown in FIG. 8, the output signals from several switches 50 are input to control unit 5. The control unit 5 checks the output signals from several switches 50 and, based on the result of this
    Verification 5 determines whether or not double activation has occurred. That is, by checking the output signals from several pressure detection switches 50, it is possible to detect which clutch is in the on state, and in the case of receiving pressure detection signals in hydraulic cylinder 1 simultaneously from two pressure switches, this can be defined as double activation. Definition that
    5 a double start occurred, the control unit 5 takes a countermeasure, consisting in issuing a command to immediately reduce the hydraulic pressure in one of the hydraulic cylinders or to an immediate
    0 Turn off all couplings to prevent breakage or damage to the respective parts or devices due to double engagement.
    With respect to the valve 2 for regulating the hydraulic pressure shown in FIG. 6, it was found that when the spool 21 is moved to the closed position of the valve 3 after the filling time tf has elapsed, as shown
    0 in FIG. 9, an excessive release (sharp abnormality) of pressure, as a result of which there is a shock when shifting gears or an abnormal sound occurs. If not reduce this overshoot
    5 pressure, any attempt to reduce the impact when shifting gears by implementing torque compensation will be futile. Therefore, reducing excessive pressure release is a serious problem. In order to absorb the pressure surge, a method of creating a battery has already been proposed. However, there is a problem that the implementation of this method is expensive, and, moreover, the structure near the valve will be cumbersome and complicated. Therefore, this known method does not find practical application.
    Excessive pressure surge occurs when the movement speed of the gold valve 21 of the flow detection valve 3 is slow.
    his return (moving to the right) after the completion of filling. In this connection, it can be said that the conventional flow detection valve 3 is designed so that the pressure sensing surface AI of the spool 21 in the hydraulic chamber 31 is substantially equal to the pressure receiving surface A2 on the left end of this spool 21. That is, with the design shown in fig. 6, since after the disappearance of the pressure difference between the left and right sides of the orifice 7, the spool 21 returns only under the action of the returning force of the spring 23, its speed of return movement is small, and there is some delay until the spool 21 is completely closed.
    In order to solve the above problems, a fourth embodiment of the present invention is proposed. In accordance with the fourth embodiment, as shown in FIG. 10, provide some difference between the areas of the pressure-receiving surface A2 at the left end of the spool 21 and the receiving surface AI of the spool in the hydraulic chamber 31 by increasing the surface A2 at the left end of the spool 21 relative to the surface AI of the spool 21 in the hydraulic chamber 31 according to the equation A2 2Ai.
    Assume that the pressure in front of the bore 7 is equal to RA, and the pressure behind this hole is equal to Pb, as shown in FIG. 5, then the differential pressure D P on both sides of the passage aperture 7 will be represented by the equation ДР Рд-Рв.
    Consequently, the force acting on the left end surface of the spool 21 will be equal to A2Pv, and the force acting on the spool 21 in the left direction in the presence of hydraulic pressure in the hydraulic chamber 31 is equal to AtRd.
    That is, the spool 21 will act to the right force F, represented by the following formula:
    F Aаrv-A1Rd;
    F 2AiPB-AiPA;
    F Ai (2PB-PA)
    Now suppose that the differential pressure differential pressure at the end of filling becomes zero. At this point, FA becomes equal to Pb, and therefore, formula (1) takes the form
    F AiPA.
    Thus, this force F acts on the slide 21 in the direction to the right, i.e. at
    the direction of closing the spool 21 It should be noted that the pressure of the RA does not drop completely to zero, because there is a resistance exerted by pipelines, a return spring in the coupling or the like. Thus, after the completion of filling, the spool 21 returns under the combined action of the force of the spring 23 and the force
    0
    F AiPA.
    whereby the spool 21 closes at high speed.
    On. FIG. Figure 11 shows a timing diagram illustrating the time dependence of the hydraulic pressure in the respective coupling provided in a valve configured as shown in FIG. 10. With this valve design
    0, the overshoot of pressure occurring after the expiration of the filling time tf may be sufficiently reduced, as shown in FIG. eleven.
    That is, shown in FIG. 10 valve design provides reliable reductions in overshoot pressure through simple and inexpensive improvements such as increasing the pressure-receiving surface of the A2 spool.
    0 21, located on the side of the force acting in the direction of closing of the flow detection valve 3, with respect to the pressure-receiving surface AI of the spool 21 located on the side;
    5 force acting in the direction of opening the valve 3 (the greater the difference in the areas of these surfaces, the more preferable it is).
    The following describes the operation of the device, performed as shown in FIG. 12 and 13, with reference to the timing diagrams shown in FIG. 14. It should be noted that in FIG. 14a shows the command electrical current from the control unit 5, FIG.
    5 14 (b) - pressure Pp of the pump; in FIG. 14c is the hydraulic pressure Pi in the hydraulic chamber 45 in front of the orifice 48, (in Fig. 14 d is the hydraulic pressure (pressure in the hydraulic cylinder) P2 in
    0, the hydraulic chamber 88 behind the passage opening 48 and in FIG. 14 e is the output signal S from the sensor 63.
    When it is required to bring a clutch intended for a certain gear stage,
    5 in the on state, actuate the control unit 5 in such a way that it supplies the starting command current 11 to the solenoid 76 of the corresponding valve 60 (time ti), later reduced the command current I to the command current IQ
    the initial pressure corresponding to the initial pressure Pa in the corresponding hydraulic cylinder 1 (Fig. 14 d) and then was in the waiting state until the completion of filling, while maintaining the previous working condition.
    When the starting electric current is supplied in this way, the spool 32 in the pressure control valve 61 moves to the left, and the working fluid coming from the pump 6 flows into the hydraulic chamber 45 of the flow detection valve 62 through the inlet 8 and the hydraulic channel 39. Entered into the hydraulic chamber 45, the working fluid flows through the passage opening 48 and then flows into the hydraulic cylinder 1 through the hydraulic channel 40 and the outlet opening 20. At this moment there is a pressure drop (Pi - P2) between the hydraulic and chambers 45 and 46, due to the presence of the passage opening 48. Since the pressure r is approximately zero, the valve 43 moves to the left under the action of a force equal to (Z - 5H) PI - (where $ 2 is greater than 3h, which is obtained by supporting condition P2 0 in the formula (2).
    As a result, the flow detection valve 62 opens, and the working fluid entering the hydraulic valve 42 flows into the hydraulic chamber 45 through the hydraulic chamber 44, and then it flows further into the hydraulic cylinder 1 through the passage 48, the hydraulic chamber 46, the hydraulic channel. 40 and the outlet 20, the flow of the working fluid continues until it completely fills the hydraulic cylinder.
    When the spool 43 is in the neutral position (Fig. 13), as well as during the filling time tf, when the spool 43 moves to the left of the neutral position, the spool 43 has no contact with the detecting pin 65,
    While maintaining the above operating condition, the potential at point c has a voltage value obtained by dividing voltage U by means of resistance RI and Ra, as shown in FIG. 14 (e).
    After the filling of the hydraulic cylinder 1 with the working fluid is completed, the flow of the working fluid is stopped. Consequently, the pressure differential on either side of the passage opening 48 disappears. That is, the pressure PI becomes equal to pressure 2.
    As a result, the spool 43 moves to the right under the action of a force, the value of which can be determined from the formula obtained by substituting the condition Pi Р P2 in formula (2), i.e., until the spool 43 returns to the neutral position, this force can be represented The following formula:
    ten
    Fi kix + P2 (Si + S3-S2).
    Since the respective pressure sensing surfaces Si, 82 and 5h on the spool 43 are related by
    Si + 83-82, then the force 43 acts on the spool 43 (Si + 83 - 82), created due to the presence of a difference in the areas of the pressure-sensing surfaces, in the same direction as the restoring force
    springs 49, as a result of which the spool 43 moves in the right direction under the joint action of the restoring force of the spring 59 and the force caused by the difference of areas of the pressure-sensing surfaces on the spool 43.
    When the spool 43 returns in the same way to the hydraulic pressure in the corresponding cylinder 1, pressure is transferred from pump 6 through hydraulic channel 42, hydraulic chamber 45, through passage 48 and hydraulic chamber 46, which results in a pressure surge, as shown in FIG. 14 d.
    The spring constant K2 59 is set such that the pressure Th is greater than the initial pressure Pa, but less than the above-mentioned pressure surge (Fig. 14 d). Thus, during the return period, the spool 43 is moved to the right of the neutral position shown in FIG. 13, and then moves far to the right in the presence of a pressure surge, overcoming the action of the force K2 of the spring 59, as a result
    which right side of the spool 43 comes in contact with the detecting pin 43. That is, in this case, the spool 43 moves in the direction to the right under the action of a force that can be determined by substituting the condition Pi Pi into the formula (3).
    Therefore, since the detecting pin 65 conducts electricity to the valve body 59 closed to ground through the valve 43, the potential at point c drops to zero, as shown in FIG. 14 e, and therefore there is no voltage at point c (time moment t2).
    The potential at point c is entered into control unit 5 as a detection signal S, whereby control unit 5 detects the end of filling by the initial potential increase at point c. Having determined the completion of filling, control unit 5 gradually increases the initial command electric current I for the corresponding coupling from the initial value of 1 ° without delay (Fig. 14a). Having determined the completion of filling, control unit 5 reduces the command electric current for the clutch of the preceding stage to zero, as indicated by the dotted line in FIG. 14 a.
    As a result, the pressure in the corresponding cylinder 1 decreases from the level of the above-mentioned pressure surge to the initial pressure Pa, and then gradually rises, as shown in FIG. 14 d. In this case, the spool 43 moves to the left to the neutral position from the working position in which it was in contact with pin 65. After that, since the pressure 2 in the hydraulic cylinder gradually rises, it exceeds the pressure Th given by the spring 59, at some point in time T. . Consequently, the spool 43 is again moved to the right against the action of the force of the spring 59, until the right face of the spool comes into contact with the detecting pin 65.
    At the same time, the potential at the point c drops to zero at the instant of time t3, after which this zero level is preserved.
    So, since the potential at point c drops to zero when the pressure in the coupling interrupts the predetermined pressure Th, and is equal to the predetermined stress value when the pressure in the hydraulic cylinder is lower than the predetermined pressure Th. the presence or absence of pressure in the hydraulic cylinder, i.e. the enabled state of the coupling can be detected by monitoring the potential at point c. In addition, since in this case the potential at point c drops to zero due to a pressure surge at the end of filling, this ending can be detected by detecting the first pressure drop.
    In accordance with this embodiment of the electronically controlled valve 60 for adjusting the hydraulic pressure, provided with a sensing device 63 attached thereto, are provided for each of the sleeves, and the output signals from several sensing states 63 are inputted to the control unit 5, as shown in FIG. 8. Control unit 5, controlling output signals from several
    the sensing devices 63, determines the completion of filling and the presence or absence of double inclusion based on the results obtained during the inspection. Thats
    there is a control unit 5 that sends a start command f to the clutch to bring it into an on state and then determines the moment of completion of filling by detecting the first decrease in the signal level S supplied to it from the clutch sensing device 63. In addition, control unit 5 determines which clutch is held in the on state, controlling output signals from several sensing devices 63, and in the case of receiving pressure detection signals in hydraulic cylinder 1 temporarily from two sensing devices 63, it defines this as a double actuation . Having determined the double activation, the control unit 5 immediately issues a command to decrease the hydraulic pressure in one of the hydraulic cylinders or immediately turns off all hydraulic cylinders in order to
    5 to prevent damage or breakage of the respective parts or devices due to double activation.
    Thus, in accordance with this option, due to the fact that
    0 opposite the return spring 49, the spring 59 is installed, and the movement of the spool 43 from the neutral position towards the spring 59 can be detected by means of a contact switching device containing the detecting pin 65 and the resistance RI and R2, it becomes possible to detect the end of filling and determine the on state couplings by means of one single sensing device containing only one spool 43.
    Further, due to the provision of the ratios Si + 83 S2 and Z3 for corresponding receptive pressures
    5 Si surfaces, 82 and 5z on the spool 43, the spool 43 is jointly affected by the force created by the difference in the areas of said surfaces, and the restoring force of the return spring 49 when the spool 43 moves to the right after the end of filling, as a result of which the spool 43 can be returned to the neutral position at high speed By the way, when returning the spool 43
    5 only by the elastic force of the spring 49, the return speed of the spool is low, which leads to an excessive release of pressure, shown by dotted lines in FIG. 14 (d), occurring after the completion of filling, and this entails the occurrence of an impact when shifting gears. In this case, an excessive pressure surge can be reduced by increasing the return speed of the spool provided by the above-mentioned difference in areas of pressure sensing surfaces.
    The design of the device for detecting the moment of the end of filling can be performed in any other way, provided that it detects the end of filling by moving the spool 21.
    In addition, the pressure detection switch 50 may be located at another suitable location if it provides the ability to detect hydraulic pressure in the respective clutch.
    权利要求:
    Claims (13)
    [1]
    1. A device for adjusting the hydraulic pressure in the hydraulic cylinder of the friction clutch actuator, comprising a first valve with a spool installed in the housing cavity to form control cavities and having a through opening, the inlet of which is connected to one of the control cavities, its output is connected to the outlet of the device and another control cavity equipped with a spring, the second valve is made with an electric actuator, the output of which is connected to the control cavity of the first valve connected to the inlet -stand holes, characterized in that, in order to increase the accuracy and reliability of control, it comprises means for detecting completion of filling of the hydraulic cylinder actuator a friction clutch, mounted to contact the first valve spool.
    [2]
    2. Device pop. 1, characterized in that the means for detecting the end of filling is made in the form of a piston attached to the spool of the first valve, and a piston displacement detecting unit.
    [3]
    3. The device according to claim 2, wherein the piston movement detecting assembly comprises an element attached to the device body and a sensor-detector of contact between the piston and the element.
    [4]
    4. The device according to claim 3, which is designed so that the element is made in the form of an electrically conductive cover mounted on the device case, between which the electrically insulating material is located, and the sensor-detector is configured to supply electrical signal when the piston is in contact with the cover.
    [5]
    5. A device for adjusting the hydraulic pressure in the hydraulic cylinder of the friction clutch actuator comprising a first valve with a spool mounted in the housing cavity to form control cavities and having a through hole, the inlet of which is in communication with one of the control cavities, and
    its output is connected to the outlet of the device and another control cavity equipped with a spring, the second valve is made with an electric actuator, the output of which is connected to the control cavity of the first valve connected to the inlet of the through passage, characterized in that, in order to improve the accuracy and reliability of the regulation / contains spring loaded piston mounted
    in the housing with the ability to move under the action of fluid pressure;
    [6]
    6. The device according to Claim 5, is designed so that the pressure detection means comprises an element attached to the device body and a sensor-detector of the contact between the piston and the element
    [7]
    7. The device according to claim 6, wherein the element is made in the form of an electrically conductive cover mounted on the housing, between which the electrically insulating material is located, and the dstch-detector is configured to supply electrical signal when the piston is in contact with the cap,
    [8]
    8.Device for adjusting the hydraulic pressure in the hydraulic cylinder
    a friction clutch actuator comprising a first valve with a spool mounted in the housing cavity with formation of control cavities and having a through hole, the inlet of which is in communication with one of the control cavities, and its output is connected to the outlet of the device and another control cavity equipped with a spring, the second the valve is made with electric drive, the output of which
    connected to the control cavity of the first valve connected to the inlet of the through-hole, characterized in that, in order to increase the accuracy and reliability of the adjustment, the spool of the first valve
    made with a different area of the ends forming with the body of the control cavity, and the cavity with a larger area of the end connected to the outlet of the device.
    [9]
    9, Device for adjusting hydraulic pressure E to hydraulic cylinder
    a friction clutch actuator comprising a first valve with a spool mounted in the housing cavity with formation of control cavities and having a through hole, the inlet of which is in communication with one of the control cavities, and its output is connected to the outlet of the device and another control cavity equipped with a spring, the second the valve is made with an electric drive, the output of which is connected to the control cavity of the first valve, which is connected to the inlet of the passage orifice, characterized in that, in order to improve accuracy and NOSTA control, it is provided with a second spring mounted on the other end of the first valve spool, and means for detecting completion of the filling cylinder drive friction clutch and clutch engagement pressure.
    [10]
    10. The device according to claim 9, that is, so that the stiffness of the second spring is greater than the stiffness of the first spring.
    [11]
    11. The device according to claim 9, wherein the means for detecting filling and pressure comprises an element attached to the body of the device, and
    sensor-detector of the contact between the spool and the element.
    [12]
    12. The device according to claim 11, is distinguished, ee with the fact that the element is made in the form
    an electrically conductive probe mounted on the housing of the device, between which there is an electrically insulating material, and the sensor-detector is configured to supply an electrical signal
    when contacting the valve with the probe.
    [13]
    13. The device according to claim 9, that is, so that the spool of the first valve is made with a different area of the ends of the spool forming control bands with the body i, and a cavity with a larger end face is communicated with the outlet from-1 version of the device.
    . Phi 1
    -f-V
    26
    Potential 6 point
    1753958 40
    U
    J
    i End of filling Fig. 3
    that oh oh oh oh oh oh
    at
    .go
    U)
    N
    AND
    oh
    of
    t
    l
    -ft
    Yu
    R
    about
    go
    VPCU
    Knn-
    | and
    N
    with
    h
    I
      about
    - O. CO 43
    ate with
    tn-4PUT f
    g / opsons
    or
    896CS / .1

    d
    I

    five
    four
    gtfffMi / nfrodgm # dMdtrgoy
    4J
    i
    NV {
    with „ь
    R
    64
    L
     /.
    4c 45 A3 44/59
    ooooooo p
    oooeoooo
    I
    r
    Qj
    46
    01
    J
    W-62
    -60
    five
    city / 2
    §one
    /
    33
    /
    7
    r lo 0
    fycxoSa team
    FIG M
    类似技术:
    公开号 | 公开日 | 专利标题
    SU1753958A3|1992-08-07|Device for controlling hydraulic pressure in friction clutch hydraulic drive
    CA1238552A|1988-06-28|Electrohydraulic control of a spool valve forenergizing a heavy duty automatic transmission clutch
    JPH0615286Y2|1994-04-20|Proportional pressure reducing valve
    GB2339249A|2000-01-19|Hydraulic system with a single pressure transducer monitoring recharging and operating pressure
    JP2001343032A|2001-12-14|Fluid pressure control valve of clutch or brake and fluid pressure control method
    EP1508731B1|2007-12-19|Electric fluid servo valve and method of making same
    EP1235005A2|2002-08-28|Self-diagnosing pressure regulator apparatus
    US20080149446A1|2008-06-26|Hydraulic clutch circuit
    US4993285A|1991-02-19|Method and apparatus for controlling speed changing unit
    US5800130A|1998-09-01|Pressure control system for a variable displacement hydraulic pump
    GB2334766A|1999-09-01|Fluid actuated clutches with end-of-fill detection arrangement
    JP2006526740A|2006-11-24|Proportional pressure control valve
    EP0351095A3|1991-02-20|Accumulator control for hydraulic actuating pressure of automatic transmission friction clutch or brake
    US5119717A|1992-06-09|Method of controlling solenoid valves for a hydraulic actuator, with a time delay between closing a normally open valve and opening a normally closed valve
    US5129500A|1992-07-14|Control valve for timed clutch engagement
    EP0611687B1|1997-05-02|Antilock modulator
    US5326230A|1994-07-05|Closed loop control circuit for variable hydraulic pump
    EP0515381B1|1994-11-23|A clutch control system
    US5119914A|1992-06-09|Accumulator and relay valve
    JPH0680054U|1994-11-08|Transmission clutch hydraulic control valve
    US7513269B2|2009-04-07|Hydraulic control system for automatic transmission
    JP2844504B2|1999-01-06|Electromagnetic proportional control valve
    JP4510174B2|2010-07-21|Variable margin pressure controller
    JP2595753Y2|1999-06-02|Hydraulic valve device
    JP2816898B2|1998-10-27|Flow control valve
    同族专利:
    公开号 | 公开日
    EP0308509A4|1989-11-07|
    DE3787468T2|1994-01-13|
    EP0308509B1|1993-09-15|
    AU601537B2|1990-09-13|
    WO1988007636A1|1988-10-06|
    DE3787468D1|1993-10-21|
    EP0308509A1|1989-03-29|
    US5035312A|1991-07-30|
    AU8320987A|1988-11-02|
    US5168973A|1992-12-08|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    EA011981B1|2007-09-07|2009-06-30|Общество С Дополнительной Ответственностью "Стрим"|Method for controlling hydraulically driven devices and automatic multiposition valve|US3566716A|1969-07-22|1971-03-02|Int Harvester Co|Clutch cylinder circuit and charging valve therefor|
    US3618424A|1969-09-02|1971-11-09|Caterpillar Tractor Co|Transmission control system|
    US3874255A|1970-06-30|1975-04-01|Komatsu Mfg Co Ltd|Hydraulic speed change control device|
    US3809201A|1970-10-30|1974-05-07|Kobe Steel Ltd|Modulating valve for vehicle transmission systems|
    JPS548424Y2|1971-02-27|1979-04-18|
    US3722646A|1971-03-12|1973-03-27|Honda Motor Co Ltd|Apparatus for controlling the pressure of a fluid fed to a clutch of a transmission|
    JPS5427622Y2|1971-11-30|1979-09-07|
    JPS5548209Y2|1973-12-18|1980-11-11|
    GB1450816A|1974-01-10|1976-09-29|Komatsu Mfg Co Ltd|Hydraulic apparatus|
    US3991865A|1974-02-28|1976-11-16|Kabushiki Kaisha Komatsu Seisakusho|Device for gradually increasing hydraulic pressure|
    JPS554969B2|1974-12-11|1980-02-02|
    US4000795A|1976-03-29|1977-01-04|Clark Equipment Company|Apparatus for controlling the pressure of a fluid fed to a clutch|
    DE3050078A1|1979-11-29|1982-03-18|Nissan Motor|Hydraulic control type automatic transmission|
    DE3010865C2|1980-03-21|1988-08-11|Robert Bosch Gmbh, 7000 Stuttgart, De|
    US4465168A|1981-11-25|1984-08-14|Kabushiki Kaisha Komatsu Seisakusho|Pressure control system for a transmission|
    JPS6084850U|1983-11-18|1985-06-11|
    US4648496A|1985-04-12|1987-03-10|Borg-Warner Automotive, Inc.|Clutch control system for a continuously variable transmission|US5417622A|1987-05-22|1995-05-23|Kabushiki Kaisha Komatsu Seisakusho|Apparatus for controlling lock-up clutch|
    US4949264A|1988-09-29|1990-08-14|Kubota, Ltd.|Transmission having electromagnetic proportional reduction valve|
    US5270930A|1990-11-30|1993-12-14|Mitsubishi Jidosha Kogyo Kabushiki Kaisha|Four wheel driving vehicle of a front/rear wheel differential operation limiting type|
    US5054599A|1990-12-24|1991-10-08|Caterpillar Inc.|End of fill detector for a hydraulic clutch|
    US5105922A|1991-04-01|1992-04-21|Dana Corporation|Hydraulic clutch and transmission actuating system|
    US5119697A|1991-04-29|1992-06-09|General Motors Corporation|Control apparatus for regulating engagement of a fluid operated torque transmitting device|
    DE4124384C1|1991-07-23|1993-01-28|Mercedes-Benz Aktiengesellschaft, 7000 Stuttgart, De|
    US5481187A|1991-11-29|1996-01-02|Caterpillar Inc.|Method and apparatus for determining the position of an armature in an electromagnetic actuator|
    DE4142744C2|1991-12-22|1996-05-09|Hydraulik Ring Gmbh|Coupling device for vehicles|
    DE69306470T2|1992-05-19|1997-06-26|Mitsubishi Motors Corp|Fluid pressure control device for an automatic motor vehicle transmission|
    US5301783A|1992-06-24|1994-04-12|General Motors Corporation|Dual pressure accumulator|
    FR2692942B1|1992-06-25|1995-07-28|Valeo|ELECTRO-HYDRAULIC ACTUATOR, IN PARTICULAR FOR THE CONTROL OF A CLUTCH OF A MOTOR VEHICLE.|
    US5343994A|1993-03-23|1994-09-06|Caterpillar Inc.|End of fill detector for a hydraulic clutch|
    US5337871A|1993-10-18|1994-08-16|Deere & Company|Calibration method for transmission control clutches|
    US5467854A|1994-06-07|1995-11-21|Caterpillar Inc.|Method of controlling clutch-to-clutch shifts for a powershift transmission|
    US5505100A|1994-09-29|1996-04-09|Caterpillar Inc.|Method of controlling interrupted shifts for a powershift transmission|
    US5551930A|1995-04-13|1996-09-03|Caterpillar Inc.|Adaptive control method for an automatic transmission|
    US5580332A|1995-04-13|1996-12-03|Caterpillar Inc.|Method for determining the fill time of a transmission clutch|
    JPH09280348A|1996-04-10|1997-10-28|Komatsu Ltd|Method and device for detecting wear of clutch of transmission|
    US6088645A|1996-07-08|2000-07-11|Komatsu Ltd.|Control device and control method for transmission with clutch|
    US5934431A|1996-12-30|1999-08-10|Dana Corporation|Plateau control algorithm for an electro-hydraulic actuator|
    US5871074A|1997-09-04|1999-02-16|Deere & Company|Control circuit for a powershift transmission|
    US5941358A|1997-12-16|1999-08-24|Caterpillar Inc.|End-of-fill detector arrangement for a fluid actuated clutch|
    DE19813982C2|1998-03-28|2002-06-20|Bosch Gmbh Robert|clutch control|
    US6115661A|1998-04-09|2000-09-05|Caterpillar Inc.|End-of-fill detector for a fluid actuated clutch|
    US5950789A|1998-04-27|1999-09-14|Caterpillar Inc.|End of fill detector for a fluid actuated clutch|
    US6461918B1|1999-12-20|2002-10-08|Fairchild Semiconductor Corporation|Power MOS device with improved gate charge performance|
    JP2001343032A|2000-06-01|2001-12-14|Komatsu Ltd|Fluid pressure control valve of clutch or brake and fluid pressure control method|
    US7368777B2|2003-12-30|2008-05-06|Fairchild Semiconductor Corporation|Accumulation device with charge balance structure and method of forming the same|
    US6655138B2|2001-05-01|2003-12-02|Delphi Technologies, Inc.|System and method for actuating and controlling a transfer case|
    JP2003083428A|2001-09-10|2003-03-19|Komatsu Ltd|Fluid pressure control valve device for clutch or brake|
    US6677641B2|2001-10-17|2004-01-13|Fairchild Semiconductor Corporation|Semiconductor structure with improved smaller forward voltage loss and higher blocking capability|
    US7061066B2|2001-10-17|2006-06-13|Fairchild Semiconductor Corporation|Schottky diode using charge balance structure|
    US6640950B2|2001-12-28|2003-11-04|Caterpillar Inc.|Fluid clutch fill detection system and method|
    KR100859701B1|2002-02-23|2008-09-23|페어차일드코리아반도체 주식회사|High voltage LDMOS transistor and method for fabricating the same|
    DE10210877A1|2002-03-12|2003-11-27|Wabco Gmbh & Co Ohg|Valve device for actuating cylinders|
    KR100440332B1|2002-06-28|2004-07-15|현대자동차주식회사|two way orifice check valve device for hydraulic circuit|
    US7576388B1|2002-10-03|2009-08-18|Fairchild Semiconductor Corporation|Trench-gate LDMOS structures|
    US7132712B2|2002-11-05|2006-11-07|Fairchild Semiconductor Corporation|Trench structure having one or more diodes embedded therein adjacent a PN junction|
    JP4269999B2|2003-06-30|2009-05-27|トヨタ自動車株式会社|Load element status detection device|
    US7352036B2|2004-08-03|2008-04-01|Fairchild Semiconductor Corporation|Semiconductor power device having a top-side drain using a sinker trench|
    US20060068969A1|2004-09-27|2006-03-30|Caterpillar Inc.|Transmission having an electronically controlled main relief valve|
    US7265415B2|2004-10-08|2007-09-04|Fairchild Semiconductor Corporation|MOS-gated transistor with reduced miller capacitance|
    KR20120127677A|2005-04-06|2012-11-22|페어차일드 세미컨덕터 코포레이션|Trenched-gate field effect transistors and methods of forming the same|
    US7385248B2|2005-08-09|2008-06-10|Fairchild Semiconductor Corporation|Shielded gate field effect transistor with improved inter-poly dielectric|
    US7319256B1|2006-06-19|2008-01-15|Fairchild Semiconductor Corporation|Shielded gate trench FET with the shield and gate electrodes being connected together|
    KR100780897B1|2006-09-28|2007-11-30|볼보 컨스트럭션 이키프먼트 홀딩 스웨덴 에이비|Pressure control device of heavy equipment|
    DE102006061344A1|2006-12-22|2008-06-26|Robert Bosch Gmbh|Clutch hydraulic circuit|
    JP4386122B2|2007-10-05|2009-12-16|株式会社デンソー|Hydraulic control device|
    US7772668B2|2007-12-26|2010-08-10|Fairchild Semiconductor Corporation|Shielded gate trench FET with multiple channels|
    US8172060B2|2008-04-02|2012-05-08|Saturn Electonics & Engineering, Inc.|Dynamic pressure control system with solenoid valve command current trimming|
    US9527367B2|2014-04-14|2016-12-27|L & B Manufacturing, Inc.|Pneumatic actuators|
    DE102014221038A1|2014-10-16|2016-04-21|Schaeffler Technologies AG & Co. KG|Actuator for actuating a clutch and clutch for a motor vehicle|
    US9618064B2|2014-12-10|2017-04-11|Cnh Industrial America Llc|System and method for preventing centrifugal clutch lock-ups within a transmission of a work vehicle|
    KR101713794B1|2015-10-21|2017-03-09|현대오트론 주식회사|Apparautus for caculatiing filling time in automatic transmission and control method thereof|
    US10801612B1|2019-04-26|2020-10-13|Caterpillar Inc.|Machine transmission with clutch element hydraulic control|
    RU2761977C1|2021-04-21|2021-12-14|Федеральное государственное унитарное предприятие "Центральный ордена Трудового Красного Знамени научно-исследовательский автомобильный и автомоторный институт "НАМИ"|Two-way gearbox hydraulic clutch|
    RU2761962C1|2021-04-21|2021-12-14|Федеральное государственное унитарное предприятие "Центральный ордена Трудового Красного Знамени научно-исследовательский автомобильный и автомоторный институт "НАМИ"|Vehicle hydraulic control system of the toothed clutch of gearbox|
    RU2761963C1|2021-06-17|2021-12-14|Федеральное государственное унитарное предприятие "Центральный ордена Трудового Красного Знамени научно-исследовательский автомобильный и автомоторный институт "НАМИ"|Hydraulic control system of the two-way gear coupling of the transmission|
    RU2762838C1|2021-06-17|2021-12-23|Федеральное государственное унитарное предприятие "Центральный ордена Трудового Красного Знамени научно-исследовательский автомобильный и автомоторный институт "НАМИ"|Hydraulic control system of the gear coupling of the transmission of a vehicle|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    JP62070991A|JP2649347B2|1987-03-25|1987-03-25|Clutch hydraulic control device|
    JP62070992A|JP2649348B2|1987-03-25|1987-03-25|Clutch hydraulic control device|
    JP62070993A|JPH0565731B2|1987-03-25|1987-03-25|
    JP62070990A|JP2649346B2|1987-03-25|1987-03-25|Clutch hydraulic control device|
    [返回顶部]