• 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:
    Hydraulic controls in a transmission for engaging a clutch for the F-R, or forward or reverse, direction before a clutch for first, second, or third speed. Flow of hydraulic fluid to each direction clutch and to each speed clutch is by way of a reducing valve which modulates fluid pressure in controlled way by throttling the flow. After the power unit for the clutch for the F-R clutches and the power unit for the clutch for first, second or third speed are filled with fluid by the reducing valve, pressure in the power units is then slowly raised by the valve linearly toward its maximum; for this purpose the hydraulic controls are supplied by a single source of hydraulic fluid and operate therefrom to provide a pair of modulated pressure outputs which are maintained with varying differences throughout their range of operation, and which operate the selected one of the F-R clutches and the selected one of the first second or third clutches. The F-R clutches are the ones which receive the higher modulated pressure output and which are constructed, proportioned in size, and arranged to have a higher speed capability and smaller energy absorbing capacity in their design, and they operate so as to be fully hydraulically engaged at the higher pressure output, and hence slightly before, the speed clutches.
    公开号:SU959615A3
    申请号:SU762416108
    申请日:1976-10-26
    公开日:1982-09-15
    发明作者:Хорш Иоахим
    申请人:Интернэшнл Харвестер Компани (Фирма)；
    IPC主号:
    专利说明:

    39 A disadvantage of the known valve device is the low accuracy of the signal output in the process of gear shifting. The purpose of the invention is to improve the accuracy in the process of gear shifting. The goal is achieved by the fact that the valve device is provided with a return spring and a throttle installed in the hollow piston for communicating its internal cavity with the back pressure chamber, two bypass channels, one of which is connected to the back pressure chamber and with the said slide valve. an overflow channel communicated with the cavity of the regulating piston, the latter being made with overflow calibrated holes made on its lateral surface along its length, and returning Atna spring is mounted between the adjusting piston and said sleeve thus-formed channel in the housing, communicating with the hydraulic reservoir and arranged opposite the overflow of said calibrated orifices. FIG. 1 shows the proposed device in a neutral position; in fig. 2 - the same, in the mode of vehicle motion on any gear; in fig. 3 the same, when switching ranges; in fig. - the same, when filling at the time of switching ranges; in fig. 5 - the same, in the mode of the beginning of regulation (rate of increase of pressure) when switching ranges; in fig. 6 - the same, in the mode of regulation when switching ranges; in fig. 7 the same, when returning to the starting position when switching directions; in fig. 8 - the same when filling during the switching direction; in fig. 9 pressure chart when shifting gears; in fig. 10 - pressure graph when switching directions. The valve device consists of a housing 1, in which a first chamber 2 is made, into which a liquid is fed through channel 3, creating an initial constant pressure of 18.3 kg / cm. Via another channel 4, nocTynaeft fluid into the second chamber 5 through a lower pressure choke 6. 54 An inlet 7 for the nominal pressure in this valve device forms a groove in one of two parallel valve openings (top 8 or bottom 9). A coaxial pair of parts is accommodated in the upper bore 8 for reciprocating movement. A hollow piston 10 and a regulating hollow piston 11. A coaxial pair of spool parts 12 and a plunger 13 are arranged for a reciprocating motion of the coaxial pair of the upper 8 and 9 lower holes. . each other through the outlet opening I of the hollow piston 10 extending into the chamber 15 through the groove 16 in the opening, the transverse channel 17 and the groove 18. in the lower opening and through the second chamber S, which is part of the upper opening 8, the transverse channel 19 and the groove 20 in the bottom hole. Between the groove 21 in the upper opening and the second chamber 5 there is a jumper 22 forming part of the upper opening 8, and a groove 21 communicating with the drain 23. The cylindrical side wall of the hollow piston 10 has four throttling openings 2 communicating with the input 7 and supplying adjustable pressure to the outlet when the valve is in the throttling position with openings 2k extending beyond the adjacent edge of the inlet groove. The valve opening spring 25 pushes the piston 10 from the throttling position to the open position shown in FIG. 1 solid lines. The end wall of the piston 10 has a coaxial uncontrollable bore 26 formed in the center of the piston end 27 and provides flow restriction to the backpressure chamber 28, which includes a groove 1b in the top bore and part of the upper bore 8 between the grooves 16 and 21. When the hollow piston 10 occupies the extreme position of throttling, in which the pressure at the outlet of the orifice 1 f grows linearly, with a constant growth rate, the unregulated orifice 26 plays a crucial role in controlling the low flow rate through the outlet orifice 1. Not Much of the fluid flow is limited through the opening 26 into the backpressure chamber 28, and the resulting increase in pressure in the chamber 28 is prevented, 5 9596 spring 25 to overcome the outlet pressure at the outlet of the opening 1 and move the hollow piston 10 to the left (see Fig. 1 ), always providing a small increase in the passage created by the throat holes 2 in the side wall of the hollow piston, i.e. the pressure in chamber 28 determines whether pressure build-up in the clutch cylinders xc of the gears is relative to
    but quickly or relatively slowly. The main 29 and auxiliary 30 springs for returning to the initial position of the regulating piston 11 are arranged so that their inner ends are connected in series with each other by means of a common seat 31. The outer end of the main spring 29 rests inside the piston 11 on its end wall spring 30 - on the end cap 32 on the valve body. The cylindrical side wall of the piston 11 has a series of uncontrollable openings 33-35 having gradually increasing size in the direction from the left opening 33 to the middle 3 and further to the right opening 35 (see Fig. 1). Since the jumper 22 is in the path of movement of the control piston 11 from left to right, there is a restriction of flow in the drain groove 21, which will be the smallest when the hole 35 at the beginning of the stroke of the piston is aligned with the smaller one when it is further aligned with the version the stroke of the piston 11, and small, when the opening 33 is aligned with it at the end of the stroke of the piston 11 to the right (see FIG. 1). Accordingly, when the piston 11 moves to the right, the pressure in the second chamber 5 between the throttle 6 and the effective orifices 33-35 increases. At the same time, the piston 11 significantly increases the volume of the backpressure chamber 28 and at the same time causes the pressure in chamber 5 to rise and, consequently, the pressure in chamber 28 rises. The reason for increasing the volume of chamber 28 is the need to slow down the rate of pressure rise at the outlet of the opening H to the required constant magnitudes, and the successive change in the size of the nerves of the guided openings 33-35, preventing excessive acceleration of the piston 11 during movement and an increase in pressure at the outlet de apertures 1 not linearly.
    may allow fluid to flow both into conduit 36 and into conduit 37.
    The spool 12 also controls the operation of the bypass bridge 40, the KOTOp is part of the lower opening 9 and is located between the transverse channels 17 and 19 in the valve arrangement. The operation of this geremychki 40 and transverse channels 17, 19 156 spool 12, occupying the position shown in solid lines in figure 1. may allow fluid to flow into the ST pipeline, leading to directional couplings, and not pipeline 37. leading to gear-up couplings. But in a different position, in which the throttle bore 38 in the cylindrical side wall of spool 12 coincides with the edge of chamber 39, the spool 12 determines the stroke of the regulating piston 11 in the upper bore 8 and returns it to its original position. The annular groove k} in the spool 12 can provide a bypass pass of the “rfchki 0 as one, and together with the radial and longitudinal channels C2 in this valve. On the right side (see FIG. 1), the spring of the spring “acts on the plunger 13 and pushes it to the left. At the left end, which protrudes into the chamber 5, 13, perceives the force from the outlet pressure supplied to the pipeline 36, and the force due to the differential pressure on both sides of the spool 12 acting on the opposite end surface of the spool. Valve device operates as follows. When the valve device is in the zero position (neutral), any single directional signal from the system piping (not shown), regardless of whether there is an accompanying transmission actuation signal, is sufficient to ensure the transfer of the nominal pressure of the SG to the pipeline k6 and to input 7. Thus, the valve device is actuated when the initial pressure of the first chamber | eu 2 of a constant initial pressure is applied simultaneously and through the throttle 6 to the second chamber of the alternating initial pressure; No vehicle in any gear spool 12 in the bottom hole 9 is dynamically held in an intermediate throttle position, the control piston 11 is hydraulically held at the end of its steering stroke in the top-5 of the hole 8, and the hollow piston 10 is held back by the spring in the open position , allowing the additional flow of liquid from the pipeline 46, leading from the central valve, through the valve device to replenish the cylinders of the selected gearbox couplings 7 and, thus compensating for natural leakage from them. 1 Such additional fluid flow through the BZ pipeline passes only one limitation, implemented by choke holes 2k in the piston and causing the first small difference between the nominal pressure P) and the outlet pressure of 1, kg / cm in one embodiment of the invention. Replenishing fluid flow to the pipeline 37, 25
    leading to the clutch transmissions, passes two limitations, successively carried out by throttle openings 2k and 38 and causing a second small pressure drop, which is about 2.5 kg / cm lower than the nominal pressure and 1.1 kg / cm lower than the pressure on output from versti 1, supplied to the pipeline Zb ;. leading to the clutch direction cylinders. Since, at equilibrium, an unregulated bore 26 in the piston 10 equalizes the pressure on the opposite sides of the end wall of the piston, the spring 25 holds the hollow pore 10 in the extreme open position. When the regulating piston is balanced 11, a series of constraints imposed by the throttle 6 and the smallest Unregulated openings 33 create a pressure in the second chamber 51 of a slightly larger half of the nominal pressure, resulting in a differential between the pressure in the chamber 5 and the pressure in the backpressure chamber 28 by means of which the regulating piston 11 is held hydraulically at the end of the control stroke. At the equilibrium of the spool 12, the differential between the pressures in the ST and 37 pipelines, applied from opposite sides of the spool 12, enables the latter to reach 9596
    Anta version of the invention, the invention of 16.8 kg / cm at one outlet for the full engagement of the directional clutches, such as a reverse clutch, and 15.7 kg / 58 of the balanced position with an emphasis on the plunger 13 which is under the influence of the mechanical force of the spring L4 and the hydraulic force differential pressure on the side of the plunger 13 between the pressure in the first chamber 2 and the pressure at the outlet of the hole W, t. e.  An undesirable increase in pressure in chamber 5 and conduit 37 entails a hydraulic release of spool 12 to the left {see  FIG.  2) with an increase in the limitation and pressure drop of the flow of fluid passing through the orifices 38, and a decrease in the pressure in the chamber kSi and the pipe 37 causes the counter-balancing movement of the spool to the right (see  fig:  2) with a decrease in the limitation and pressure drop caused by the throttling openings 28, and with rebalancing.  Thus, there are two regulated pressure outputs for two sets of clutches, which in one of the var / cm at the other outlet are for fully engaging the clutches of transmissions, for example, a direct clutch.  The working movements of the spool 12, for example moving to the right due to a drop in pressure in chamber 39, provide only a slight axial adjustment and restore the balance of the slide in its intermediate position of throttling, whereas any greater pressure drop in chamber 39, for example, as a result of a gear change in the same range causes greater change in the relative position of the elements of the valve device.  When switching ranges, for example, from third reverse gear to second reverse gear by changing the control signal of the high speed reverse gear to the signal of the average reverse speed of the vehicle (Fig.  3), the selector valve 8 toggle dia-.  Gaza relieves the pressure in the third gear coupling by disconnecting it from the pipeline 37 (FIG.  3) and then connects this conduit 37 to the second gear coupling to create pressure therein, ensuring at first that it is filled almost without resistance.  When the filling pressure is equal to 2.8 kg / cm in one embodiment of the invention, the second gear coupling can be sufficiently filled through line 37, but this reduces the chamber 45, since a significantly increased pressure drop on both sides of the spool 12 moves it to the extreme right position in chamber 5 (see  FIG.  3), as a result, the pressure in the ST pipe decreases to 5 kg / cm, supported in the cylinder, and in pipe 37 to a stable 2.8 kg / cm, ensuring the filling of the second gear coupling with a fluid flow at a steady pressure.  At the same time, the groove 41 of the spool connects, bypassing the web 40, in the lower hole 9, the transverse channels 17 and 19 and, consequently, both sides of the regulating 11.  The sharp decrease in pressure at the outlet of the hollow piston bore 14 allows the spring 25 to remain open. the position of the hollow piston 10.  At the same time, the dual springs 29 and 30 expand, causing the v adjusting piston 11 to return to the left (Fig.  3 Thus, the volume of fluid in the chamber 28 of the backpressure, which increased with limited flow of fluid into this chamber through the uncontrolled orifice 2b, is expelled at two points in the upper orifice 8 from the left to the right side of the control piston 11 (see  FIG.  H).  The first part of the period from the moment of receiving the above-mentioned control signal for range switching to the end of filling the second transmission clutch through conduit 37 (FIG.  3) is used by a control piston. 11 to make a full move FAST back to the left, as indicated by the arrow, t. e.  the opposite ends of the open side passage to bypass the piston 11, represented by the transverse channels 19 and 17, intersect with the upper bore 8 at the two extreme points of the passage, connected hydraulically, close to the corresponding opposite ends of the driving with the piston 11.  All liquid, displaced by piston 11 from chamber 28 between piston 10 and piston 11, flows downwards and then to the right {see  FIG.  H).  95 510 Since the filling pressure in the pipeline 37 is supplied to the chamber equal to 2.8 kg / cm and the anti-working surfaces of the spool 12 are 5 kg / cm equal to the outlet pressure k and 2.8 kg / cm to the pressure in the chamber 12 performs a regulating function performed by a variable choke formed between the edge 4E on the slide and the nearest side of the chamber 39.  Thus, the spool 12, which is balanced (the opposing plunger: {Era 13, continuously maintains the pressure of the filling fluid flow in the pipeline 37 equal in one yi3 embodiments of the invention to about 2.8 kg / cm.  However, the continuous opening of the bypass bridge 40 by the groove 41 in the spool allows the dual springs 29 and 3R to ensure that the control piston 11 is fully returned to the original position shown.  preparing it for the next cycle.  A small portion of the fluid from conduit 46 leading to the neutral spool passes through inlet 7 for nominal pressure, throttle bores 24, uncontrolled bore 2b, contracted backpressure chamber 28, transverse channel 17, annular groove 41 in the spool, transverse channel 19, chamber 5 and the groove 21 in the upper hole to the drain 23.  The directional clutch, such as the reverse clutch, remains filled for the entire gear shift cycle.  The selected transmission clutch, for example, the second gear clutch, is filled at a pressure that cannot start to grow until the filling is completed, since the filling does not allow the pressure in the chamber 45 to grow.  As soon as the pressure rises sharply to 6.7 kg / cm at the outlet of the hole 14 and to 5 kg / cm in chambers 39 and 45 (one of the embodiments of the invention), the piston 10 and piston 11 move slightly to the right of their shelf to fully open. the initial position, respectively, and the spool 12 is moved from the position. action of the filling edge 49 to the left, to the adjustment position (see  FIG.  five).  This is because the output pressure of 6.7 kg / cm is an increase of 1.6 kg / cm, which forces the piston 10, and with it the regulating piston 11, to move to the position at which the throttle holes 2 The hollow piston interacts with the right (with the inlet 7, providing regulation of the pressure build-up.  The pressure in chambers 39 and 5 of 5 kg / cm includes a gain of 1.5 kg / cm increase, causing the spool 12 to move to a position in which the throttle holes 38 interact with the left side of the chamber, ensuring that the pressure build-up is controlled. in the clutch speed.  In addition, the spool annular groove no longer opens the overflow jumper 0, which results in blocking the bypass around the regulating piston as well as the drain for the unregulated bore 26 in the end stack of the hollow piston 10.  As a result, the limited flow of fluid through the opening 2b causes the control piston 11, which has already started to move, to continue the control stroke to the right (see  FIG.  five) .  FIG.  6, the piston 10, the piston 12 and the regulating piston 11 are shown in the position of regulating the rate of increase of pressure at the intermediate point of the control stroke of the piston 11.  Although, according to theory, the flow of fluid to the couplings to increase their pressure to about 1 kg / cm — from filling pressure to full switching pressure — is practically not required, due to natural leaks in the cylinders of both selected couplings, the valve device provides a small but constant , an auxiliary fluid flow to the couplings during the rise in them of a controlled pressure. .  The piston 10 in the shown position continues to increase the pressure at the outlet of the bore 14, and at this moment the pressure at the outlet of the throttle bores 2 of the piston is about 6.3 kg / cm lower than the nominal pressure P.  at the entrance 7.  The spool 12 continues to increase the pressure in the pipeline 37, leading to the gear sleeves, and at this moment the throttle openings 38 of the spool provide pressure in chamber 39 by about 1 kg / cm below the outlet pressure of the aperture.  The coordinated action of the unregulated bore 26 and the moving piston 11 provides the pressure in the chamber 28 about 3.1 kg / cm below the control at the outlet from the versity and about 3.5 kg / cm higher than the pressure in the chamber 5 operating inside the regulating piston 11.  The last pressure is set depending on the rate at which the uncontrolled orifice 3 and other openings with it transfer to the drain the combined flow created by the movement of the piston and the flow of liquid under the nominal pressure through the throttle 6 in the end cover 32 of the valve device, t. e.  when the control piston 11 moves to the right, the effective restriction is located. the size of the openings 33-35 increases with respect to the restriction of the opening of the throttles 6 in the end cap.  Thus, the pressure in the chamber 5 rises, causing an increase in pressure in the chamber 28 of the counterpressure and an increase in its effect on the piston 10.  Gradually increasing back pressure on the piston 10 leads to an increase in pressure in the selected directional clutch, for example, in the reverse clutch, until the equilibrium state shown in FIG.  2  .  The force of the pressure differential acting on the opposite sides of the spool 12: the pressure at the outlet of the port C and the pressure in the chamber 45 is sufficient to balance the valve in the control position against the left action of the axial pressure of the ram 13.  The regulation of the rate of increase in pressure continues until the elements of the valve device have reached the steady state position (see  FIG.  2).  The sequence of steps is then repeated at the next gear shift, including the steps of returning the control piston 11 to its original position to the left and making the control stroke of the piston 11 to the right (see  FIG.  6).  By their effect on the valve gear, as shown in FIG.  3 and switching the direction as shown in FIG.  7 are characterized in that the spool 12 occupies a non-partially advanced filling position for shifting the gear, as shown in FIG.  3, and the leftmost filling position j as shown in FIG.  7, to switch directions, t. e.  when switching the valve, for example, from the rear clutch to the forward clutch, it fills the forward clutch at a relatively low pressure, for example, 2.23 kg / cm.  With such a low pressure at the outlet of the port And, when the fluid flow from it begins to fill the forward clutch, the differential pressure on both sides of the spool 12 is not able to balance the pressure 13, which moves the 12 to the extreme (FIG.  7 left) position.  Only after the coupling is filled in front of it through the pipeline Zb pressure can it be released at the outlet of the hole. may begin to grow above 2.25 kg / cm, Zolotnik 12 in the leftmost position provides a dg / angular path for the fluid, bypassing junction box 0, through which fluid flows from the backpressure chamber 28 through the transverse channel 17, the annular groove k} the spool, the radial and longitudinal channels 42 in the spool, chamber 45, the transverse channel 19, the second cam. Set 5 of an alternating initial pressure, an unregulated orifice 3, and an orifice 33 35 acting in conjunction with it, and a groove 21 in the upper orifice, from where it flows into the drain line leading to the sump.  Thus, the flow of fluid through the opening 26 to the right and the spring return of the piston 11 to its original position, as shown by the arrow in FIG.  7, counteracts essentially zero pressure.  After a quick return of the regulating piston 11 to the initial position, the fluid flow (FIG.  8) from the outlet of the piston hole 1A to the pipeline 36 continues at a pressure of 2.1 kg / cm and the flow continues to bypass the bypass jumper kQ, so that the pressure in the backpressure chamber 28 and in the second variable source pressure chamber 5 remains zero.  The flow in the ST pipeline continues until the completion of filling, after which a sharp increase in pressure to 5 kg / cm occurs in this pipeline equal to 2.8 kg / cm. providing a differential pressure, causing the spool 12 to instantly move to the right from the position shown in FIG.  8, to the partially advanced position shown in FIG.  6  With such a partially advanced position of the spool 12, its throttle openings 38 are in the reduced pressure position from 5 kg / cm at the outlet of the opening 1 to a constant pressure of 2.8 kg / cm (one of the embodiments of the invention), so that from chamber 39 comes fluid to conduit 37 to fill the cylinder of a selected transmission clutch, for example, a first gear clutch.  The filling of the cylinder of the transmission clutch continues until there is a sharp increase in the pressure and up to 4.36 kg / cm in the pipeline 37J, after which there is an adjustable constant increase in pressure to turn on both the clutches.  Adjustable.  The constant increase in pressure for switching on both couplings is shown in the graphs (Figs 9 and 10) in the form of going upward with a constant inclination of straight lines.  Due to the fact that the differential pressure on both sides of the opening 26 is automatically kept constant during the adjustment, the flow rate of the liquid through the opening 26 remains constant.  Consequently, the control piston 11 moves throughout each control stroke at a constant speed.  The pressure in the pipeline 37 leading to the clutches, gears and fed from the inlet of the hole 14 through the throttle holes 38 in the spool, always varies together, but at a lower level, with the pressure at the outlet and in the pipe B, leading to the directional clutches about as a function of this pressure throughout the regulation.  However, the pressure in the conduit 37 leading to the gear clutches is able to grow along a straight line with a steeper slope on the graph due to the significant action of the plunger 13.  When the vehicle is started up, switching from neutral to transmission in one or another speed range causes such a sequence of events in the valve device as described above.  During a controlled increase in pressure to fully activate the selected directional clutch and transfer clutch, it is essential that the pressure differential on both sides of the plunger 13 (Fig.  6) decreases with a constant speed, as the pressure in the cylinders of the directional clutch and transmission clutch increases linearly.  Consequently, the pressure in the cylinder of the transmission clutch tends to reach the pressure in the cylinder of the directional clutch, t. e.  the two linear curves in the pressure graph come closer together, not intersecting.  Before shifting gears (FIG.  10) when the pressure line 50 in the directional clutch cylinder is held constantly higher and parallel to the pressure line 51 in the cylinder of the transmission clutch, in one embodiment of the invention, the differential pressure is about 1.1 kg / cm.  Gear shifting causes a sharp decrease in pressure in the directional clutch cylinder to 5 kg / cm (flat section 52.  the curve on which the clutch cylinder on the | Board remains filled), and the pressure in the cylinder of the selected clutch in front drops sharply (flat section 53 of the corresponding curve) to 2.8 kg / cm, t. e.  the cylinder of the selected transmission clutch is filled at a constant pressure.  In it.  time in the cylinder of the directional clutch is only a flow, filling the leakage.  After the filling of the transmission clutch cylinder is completed, a sharp rise in pressure on both curves, respectively, before bending 5 and bending 55, brings the pressure in the directional clutch cylinder to 6.68 kg / cm and in the transmission clutch cylinder - to 4.57 kg / cm pressure in one of the embodiments of the invention.  Thereafter, at the end of the cycle of return to the steady state, the valve device for controlling the acceleration of build up increases the pressure along inclined lines at a constant rate of increase of each pressure and brings them closer to the steady state.  During a switch from the neutral position of the opposite direction to the {fig.  9) the pressure curve in the directional clutch cylinder has the first level section 5b, on which the cylinder of the selected directional clutch is filled, excluding the transmission clutch cylinder, and the second level section 57, on which a pressure of 5 kg / cm is maintained in the directional clutch when there is the flow of fluid to it is sufficient only to fill the leakage in the directional clutch.  At this stage, the pressure curve in the clutch transmission cylinder has a flat section 58, over which this cylinder is filled at a pressure of 2.8 kg / cm, excluding the direction clutch cylinder.  After that, with a sharp rise, respectively, to bend 59 and bend 60 and.  From here, through a controlled pressure build-up curve, the pressure in the cylinder of the clutch, the direction of the curve of pressure in the cylinder of the transmission clutch, have a relationship identical to that described in connection with FIG.  ten.  From the preceding description of the pressure graphs and from FIG.  8, it can be seen that a decrease in the size of the uncontrolled bore 26 in the piston 10 causes an increase in the total pressure build-up time and vice versa, since a slowing down of the movement of the regulating piston 11 causes a slowdown in the growth of the regulated pressure.  An increase in the size of the opening of the throttles 6 in the end cap 32 of the valve device causes an increase in the angle of inclination: on straight inclined sections of the pressure curves and vice versa due to an increase in the rate of increase of pressure in chamber 5.  A change in the number, size and location of choke holes 2k in the piston entails a change in the shape of the pressure curves in the graphs.  .  Reducing the cross-sectional size of the plunger 13 in the lower bore 9 reduces the difference between the pressure in the cylinder of the selected directional clutch and the pressure in the cylinder of the gearshift clutch, and vice versa.  By varying the initial force, alone or in combination, of the springs 25, 29, 30, and the initial pressures can be changed throughout the pressure curves.  In addition, an increase in the force of the spring 25 of the control valve reduces the angle of the sloped areas on the graph and increases the cycle time of the adjustment and vice versa.  Thus, a large variety of pressure curves can be obtained with minor mechanical changes in the proposed valve device.  The value of the aforementioned feature, according to which the difference between 5 pressure in the directional clutch and the transmission clutch is large at low pressure and decreases to a small value at high pressure.  is that the two selected muffs
    权利要求:
    Claims (1)
    [1]
    you are in a gearbox properly phased when they slip at the same time. The value of filling the directional clutch cylinder and providing it with a higher pressure than -15 the cylinder of the selected transmission engagement clutch is that the control clutch, being actually a higher clutch clutch, requires an earlier start of the clutch compared to the clutch. power up The value of the mechanism with a forced quick return to the initial position, represented by the automatic regulating piston I, is to ensure that the control piston returns to its initial position during switching, and the regulation will begin no sooner than the filling of both selected couplings is completed. The proposed invention will improve the accuracy of the system in the process of gear shifting. Claims of the invention The valve device of the hydraulic system of the automatic control of the gearbox of a vehicle, a vehicle having a gearshift and directional clutch. a vehicle comprising a housing with cavities and two cylindrical chambers, the first of which is fitted with a spring-loaded hollow piston with a throttle bore on a side surface hydraulically connected through the first cavity to an outlet of the neutral transmission distributor, whose inlet communicates with a pressure source regulating the hollow piston coaxially mounted mention 9596
    The main chamber separates the latter into two control cavities, one of which has a piston 8 which is spring-loaded relative to the housing and has a spring-loaded piston in the first cylindrical chamber and is spring-loaded relative to the sleeve pressed against the regulating hollow piston by means of an additional spring, the cavity being formed by the regulating piston and sleeve , communicated with the output of the distributor neutral transmission through throttles, a spool with a longitudinal hole installed in the second cylinder, supported on the said gold tnik. and the other cavity communicates on one side with the entrance of the switching unit of the direction of transport C of the internal means, and on the other side with the cavity of the hollow piston, the valve through the longitudinal opening communicating with one side of the input of the transmission range switching unit, and on the other side a cavity formed between the spool and the plunger, and a back pressure chamber formed by said hollow and regulating pistons, characterized in that, in order to increase the accuracy in the switching process It is equipped with a return spring and a throttle installed in the hollow piston to communicate its internal cavity with the back pressure chamber, two bypass channels, one of which is connected to the back pressure chamber and the said spool with the possibility of communication with another bypass channel, communicated with the cavity of the regulating piston, the latter being made with overflow calibrated holes, made on its lateral surface along its length, and a return spring is installed between the regulating it has a piston and said sleeve, wherein a channel is made in the housing, in communication with the hydraulic tank and located opposite the above-mentioned overflow calibrated holes. Sources of information taken into account in the examination 1. US patent V 3799308, cl. 192-87.13, 197 (prototype). lg l, n / n
    FIG. g Fig. i.1..11L 1l l y / /.
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    B / e / y / f Icvjf ax. FIG.
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    US5667453A|1997-09-16|Hydraulic control system of an automatic transmission used in a vehicle
    同族专利:
    公开号 | 公开日
    JPS5294974A|1977-08-10|
    DE2704325A1|1977-09-15|
    US4046160A|1977-09-06|
    PL121772B1|1982-05-31|
    DE7702999U1|1979-02-08|
    US4138004A|1979-02-06|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US2796879A|1953-08-28|1957-06-25|Gen Electric|Liquid flow control apparatus|
    US2935999A|1954-12-03|1960-05-10|Zahnradfabrik Friedrichshafen|Delay action pressure by-pass systems and valves therefor for hydraulic transmissions|
    US3198027A|1961-11-06|1965-08-03|Caterpillar Tractor Co|Hydraulic transmission control|
    US3181394A|1962-03-19|1965-05-04|Caterpillar Tractor Co|Hydraulic controls|
    FR1371195A|1963-04-03|1964-09-04|Bronzavia Sa|Hydraulic pressure regulator|
    US3389770A|1966-02-01|1968-06-25|Caterpillar Tractor Co|Transmission hydraulic control|
    US3469472A|1967-01-26|1969-09-30|Case Co J I|Transmission control|
    US3468194A|1967-05-10|1969-09-23|Caterpillar Tractor Co|Hydraulic pressure modulating transmission control system|
    US3583422A|1967-10-19|1971-06-08|Zahnradfabrik Friedrichshafen|Valve construction for controlled pressure buildup in fluid-operated brake or clutch|
    US3550507A|1968-08-16|1970-12-29|Allis Chalmers Mfg Co|Hydraulic valve|
    US3640360A|1969-10-17|1972-02-08|Case Co J I|Differential lock with pressure modulating exhaust valve|
    US3597010A|1969-11-21|1971-08-03|Trw Inc|Pressure control valve|
    US3752188A|1971-03-30|1973-08-14|A Sage|Valve with controlled flow characteristics|
    US3946760A|1971-07-08|1976-03-30|Aisin Seiki Kabushiki Kaisha|Hydraulic modulator valve|
    US3882980A|1973-04-27|1975-05-13|Caterpillar Tractor Co|Transmission control system with dual purpose modulating|
    US3882738A|1973-12-03|1975-05-13|Caterpillar Tractor Co|Simplified fluid circuit for shifting a transmission|
    US3991865A|1974-02-28|1976-11-16|Kabushiki Kaisha Komatsu Seisakusho|Device for gradually increasing hydraulic pressure|
    US3990553A|1975-02-10|1976-11-09|Caterpillar Tractor Co.|Transmission control system with improved modulating valve|US4262554A|1978-08-18|1981-04-21|S.R.M. Hydromekanik Aktiebolag|Hydraulic valve system for controlling particularly a vehicle gearbox|
    FR2437654B1|1978-09-29|1983-02-25|Renault|
    US4387731A|1979-05-10|1983-06-14|Dresser Industries, Inc.|Modulated transmission with modulator-load-piston loading at linear rate after full reset|
    US4311068A|1979-05-10|1982-01-19|International Harvester Company|Modulated transmission with converter and modulator-load-piston which fully resets and dumps converter|
    JPS56143848A|1980-04-10|1981-11-09|Nissan Motor Co Ltd|Oil pressure control device for transmission|
    US4345508A|1980-06-02|1982-08-24|Caterpillar Tractor Co.|Control system for sequentially actuating fluid actuators|
    US4422536A|1981-05-08|1983-12-27|Deere & Company|Transmission control system with improved modulation rate regulating valve|
    US4475641A|1981-10-21|1984-10-09|Allis-Chalmers Corporation|Double acting hydraulic accumulator for power shift transmission|
    JPS58184323A|1982-04-23|1983-10-27|Toyota Motor Corp|Drive means for synchronizing device of transmission gears|
    US4506773A|1983-01-31|1985-03-26|Allis-Chalmers Corporation|Electrically controlled hydraulic clutch for a front wheel drive|
    US4583624A|1984-12-10|1986-04-22|Caterpillar Tractor Co.|Fluid system with selective differential pressure control|
    US4637504A|1985-04-03|1987-01-20|Borg-Warner Corporation|Combination range and master clutch assembly|
    US4817770A|1985-07-12|1989-04-04|Caterpillar Inc.|Control system for independent control of fluid actuated devices|
    US4684004A|1986-02-27|1987-08-04|Dresser Industries, Inc.|Method and apparatus for controlling hydraulic vehicle transmission|
    US4751866A|1986-10-03|1988-06-21|Caterpillar Inc.|Ratio valve to control unloading of modulating relief valve|
    US4742731A|1986-12-18|1988-05-10|Payhauler Corp.|Transmission range selector valve|
    US4871048A|1987-09-21|1989-10-03|Dresser Industries, Inc.|Control system for vehicle transmissions|
    US4942787A|1988-03-03|1990-07-24|Honda Giken Kogyo Kabushiki Kaisha|Apparatus for and method of controlling hydraulic clutch operation in an automatic transmission|
    JPH085394Y2|1988-05-11|1996-02-14|株式会社小松製作所|Clutch hydraulic control device|
    JP2806462B2|1992-07-03|1998-09-30|株式会社クボタ|Work vehicle traveling speed change structure|
    US5377801A|1992-12-09|1995-01-03|Case Corporation|Control apparatus for a transmission and the like|
    DE102007035298A1|2007-07-27|2009-01-29|Zf Friedrichshafen Ag|Method for operating an automatic transmission of a vehicle|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    US05/654,427|US4046160A|1976-02-02|1976-02-02|Transmission clutches with sequence valve and piston-controlled pressure modulator|
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