Diagram of the hydraulic drive control for continuously variable transmission

 

The invention relates to mechanical engineering and can be used in hydraulic drive control for a continuously variable transmission. Diagram of the hydraulic drive control for a continuously variable transmission includes a first control valve V1for regulating the pressure of the working fluid injected under the piston actuator rollers continuously variable transmission, and a second control valve V2to adjust the hydraulic pressure of the working fluid injected into the switching device for coupling the gearbox. Valves V1and V2connected to flow sequentially through the first distribution valve mechanism3(S1, S2provide direction of flow of the working fluid from each of the pumps Pland Prin the first point, R1located in the direction of flow above the valve V1or the second point of the P2located in the direction of flow below the valve V1but above the valve V2. The technical result is to create a diagram of the hydraulic control drive continuously variable transmission, which provides independent control of the clutch class="ptx">

The invention relates to a hydraulic circuit of the drive control for a continuously variable transmission, and relates in particular, but not limited to, the scheme, which is intended for transmission, usually called “fully toroidal” stepless transmission /BKP/.

Such BKP comprises a drive shaft receiving power, for example, from the internal combustion engine, and has mounted on it a pair of spaced interval with respect to each other leading drives and a pair of driven disks installed back by the parties to one another between the said leading drives. Leading the disks rotate together with the shaft, and driven disks are mounted with capability of free rotation on the shaft by means of bearing or any other similar device of this kind. Facing each other, the end surface of the master and slave drives have such a profile, which provides a receiving concave surface or a front surface that is a mirror image of the end surface facing towards her. These end surfaces are thus, Thu between which laid many of rollers, designed for power transmission from the master to the slave drive. At least in the fully toroidal design discs loaded in the axial direction by means of hydraulic impact so as to ensure the continued availability of appropriate adhesion forces between the discs and the roller. In addition, these rollers, while maintaining a certain freedom of their movement, are to some extent modify their position is influenced by the hydraulic power cylinder is carried out through the use of both higher and lower pressures created in the schema of the hydraulic actuator, for example, what is disclosed in the description of the invention for PCT application GB/00956, or to the United Kingdom patent No. 2282196.

The above system is illustrated in Fig. 1, which positions 12 and 14 marked wheel drives, position 16 marked the drive shaft, and items 13, 20 marked the slave drives. The rollers indicated by the position 22, and the corresponding impact on them, leading to change their position, thus ensuring the regulation of the transmission ratio of the gearbox, is carried out by means of the piston 24 Gidravlika, created in connected to this cylinder diagram of a hydraulic drive. Hydraulic axial load created by the hydraulic chamber 26 which, when receiving pressurized working fluid of the hydraulic system operates so that the master disk 14 when this was created, the load in the direction to another master drive 12, through which constantly ensures proper adhesion forces.

The hydraulic actuator suitable for use with the above system is disclosed in the description, to our own application filed under the patent cooperation Treaty under the number PCT GB/00956, and the basic structure of this hydraulic actuator shown in Fig. 2, which is appended to the present description of the invention. Although this system does not require detailed it here considering, however it should be noted that the valves 99 and 100 connected in parallel to each other in such a way as to be able to engage either separately or together with each other and adjusting the pressure in the hydraulic circuit of the drive control so that the tell when this is applied to one or the other of the two clutches 37, 43. Management is carried out independently, i.e., the change in hydraulic pressure in the clutch has no effect on the position of these rollers, and Vice versa.

The aim of the present invention is to provide such a circuit hydraulic drive control for a continuously variable transmission, which would be more perfect as compared with the above construction, because the scheme of the actuator, can provide a more rapid response in the event of adverse conditions.

In accordance with this invention proposes a framework for a hydraulic drive control for a continuously variable transmission /BKP/ with the variator and many couplings (ClCrto switch modes of operation, contains:

the first and second hydraulic pressure pipelines;

the first and second hydraulic pumps (PLPR,),

connected to the aforementioned first and second discharge pipes respectively and are intended for pumping the working fluid of the hydraulic system on these pipelines and to increase the pressure of the working fluid;

the first and second klirovaniya pressure of the working fluid of the hydraulic system, injected under the piston actuator rollers of the specified variable and for regulating the hydraulic pressure of the working fluid injected into the switching device for the specified clutch gearbox containing coupler (ClCr) modes, in which the first and second valves (V1) and (V2connected to flow sequentially relative to each other, and using the first distribution valve mechanism (S1, S2for the working fluid in such a way as to provide the ability to selectively direct the flow from the pumps (PL, RRin the first point (P1located in the direction of flow above relative to the first valve (V1), or to a second point (P2located in the direction of flow is lower relative to the first valve (V1), but is higher relative to the second valve (V2), whereby the first valve (V1) regulates the pressure of the working fluid acting on the main piston, regulating the position of the rollers, and the second valve (V2) regulates the pressure of the working fluid injected into the switching device of the transmission.

Providing the specific advantages first is sub>, each of which has first and second outlet openings, each first outlet connected in such a way as to ensure the supply of the working fluid in the first mentioned point located in the direction of flow is higher relative to the valve V1/, and each of the second outlets connected in such a way as to ensure the supply of the working fluid in the above-mentioned second point located between the valves V1and V2/. Preferably, the valve V1represented such a valve, which increases the air pressure and is used to control the pressure on the section located upstream with respect to it in the direction of flow, providing a supply of working fluid to the variator, and in which any flow through the said valve V1is combined with any other stream which is sent directly mentioned in the second point for the subsequent supply of it in the above-mentioned second valve V2/providing the appropriate switching clutches/.

Providing the specific advantages of this approach additionally includes restricting the flow of funds R designed for sub>, S2for the working fluid in the above-mentioned second point, which is carried out so that the resistance in each branch was essentially equal to the total resistance value with the passage of the supplied fluid through the valve V1.

In the embodiment of the present invention provide particular advantages, this scheme includes an additional limiter r, located on the way of supplying the working fluid into the valve V1moreover , the total resistance value of the limiter g and valve V1essentially equal to the total resistance value R and any resistance is provided within each branch between the distribution valve mechanism (S1, S2and the second point of the P2.

Providing the appropriate facilities specified circuit additionally includes a corresponding control device that is triggered when the deceleration of the vehicle, and the switching mechanism is performed by providing the possibility to engage in such a way as to switch the first distribution valve mechanism for fluid in this paragraph is ub>1after detection of the transition of the vehicle on the mode of slow motion.

In addition, providing the specific advantages of this approach includes also the corresponding switch mechanism performed by providing the possibility to engage in such a way as to switch the first distribution valve mechanism for fluid in such a situation, in which all the working fluid coming from the pump PLand PRshall be made in the above-mentioned second point, not mentioned in the first point.

In one of the embodiments of the present invention described scheme includes first and second clutch change modes, respectively, WithRand CLand each of these couplings, WithRand CLconnected in such a way as to ensure that the receipts in it working fluid from a point located in the direction of flow below respectively in relation to the pump PRand RL.

In addition, providing the specific advantages of this approach includes also the flow limiter, rL, rRlocated on the way of supply Rabita couplings, supported preset pressure.

Preferably, in the supply line of each of these couplings provided having an inlet valve FLFRensuring completion of relevant couplings and located in the area between the respective pump and said clutch, whereby the flow of the working fluid supplied to the valve from the respective pump or through the primary point of filling RFPlocated in the direction of flow mentioned below regarding the second point, but above relative to the valve V2or through a secondary point of filling SFPlocated in the direction of flow below regarding the above pumps, but above relative to the first mentioned point R1.

Even in one of the embodiments of the present invention, a secondary point of filling SFPis located in the direction of flow above mentioned valve /V3/ first distribution valve mechanism (S1, S2for the working fluid.

Due to the fact that this scheme is equipped with a clutch, preferably it would be to include in its membership and also the pressure relief valve flow of working fluid directed in the above-mentioned respective coupling and in its second position operates so that the working fluid therefrom merged, but this would be equivalent to receipt of the over-flow of fresh fluid.

In addition to providing certain advantages of this approach includes also the appropriate controls designed to switch the valve position FLand FRthus, to ensure the flow of working fluid from the primary fill point RFPduring the stage of filling of the coupling and from the secondary fill point SFPduring the stage of inclusion clutch.

In addition, this scheme may include in its membership and appropriate controls designed to switch the positions of the first distribution valve mechanism (S1, S2for the working fluid so that the working fluid directed from both pumps P1and R2in the corresponding clutch CLWithRthrough the mentioned secondary point of filling in Addition, providing the specific advantages of this approach additionally includes in its composition and also the drive of the working fluid prednaznachen occhialino it would also, for the drive has been working fluid from the tertiary fill point TFPlocated in the direction of flow is higher relative to the valve V2but below regarding the primary point of filling PFP.

Besides providing the certain advantages when used above the drive valve V2is a solenoid valve.

In the embodiment of the present invention provide particular advantages, the circuit additionally includes an adjustable relief valve, the valve V2is a solenoid valve, and the said valve V2while in its first position, operates so that the flow of working fluid directed through the said valve and then into the sump, and being in its second position, operates so that the working fluid directed in the above-mentioned adjustable relief valve.

In addition, preferably it would be for the adjustable relief valve was a spring-loaded pressure reducing valve having a path limiter adjust shutter speed”, is the ons, where is the spring, which results in an additional force in the direction of action of the spring, providing increased pressure in the hydraulic circuit.

Providing the defined benefits mentioned pressure reducing valve includes a drain hole intended for draining the working fluid in the case of accumulation it with the side of the drive, where the spring is.

In one of the embodiments of the present invention, providing the relevant facilities, the scheme includes corresponding hydraulic mechanism, creating a continuously variable transmission of axial load, and said circuit includes also the appropriate tool /election valve that is configured to identify a higher pressure, designed to ensure supply in the above-mentioned mechanism, creating an axial load, the working fluid under a higher pressure, selected from two of its values generated by pumps PLand PR.

Preferably it would be that, in the above embodiment, the present invention provided for the presence of souvienne scheme so to ensure receipt by him of the working fluid of the hydraulic system from both pumps PLand PRand out of the working fluid directed to the mechanism that creates the thrust would be all the time under the higher of the two different pressures developed in these pumps.

In addition to the aforementioned mechanism, creating an axial load, the declared scheme can also be supplied with the appropriate tool in order to ensure supply in the above-mentioned mechanism, creating an axial load, the working fluid contained in a scheme under a lower pressure, which is alternative to that option, which provides for the flow of operating fluid under higher pressure selected from two different values generated by the pump PLand RR.

In addition, providing the specific benefits claimed diagram of the hydraulic actuator additionally includes also the corresponding switching mechanism to switch from a working fluid under a lower pressure when its mesukim pressure.

In accordance with an alternative embodiment of the present invention, it is proposed continuously variable transmission having a hydraulic circuit of the drive control is executed as described here above brief description.

The essence of the present invention is illustrated more specifically in this section the following detailed description when considering the supplied only for example the respective drawings, with reference to which it is conducted, and in which:

Fig.1 is a schematic illustration of a continuously variable transmission.

Fig.2 is a schematic diagram of the hydraulic actuator made in accordance with the current level of technology.

Fig.3 is a schematic illustration of one of the variants is a schematic hydraulic actuator designed for progressive transmission and adapted for use in at least one embodiment of the present invention.

Fig.4-12 represents the corresponding schema hydraulic actuator made in accordance with the various individual features of the present invention, b is nnow in Fig.3, so when it was necessary or desirable.

As shown in the accompanying drawings, and more specifically in Fig.3, it should be understood that this device is one of the modifications of the present invention discussed herein above brief description, but for which adopted the same principles of management as disclosed herein below detailed description. Based on the particular variant of implementation of the present invention shown in Fig.3, it should be understood that the present invention is a 30 actuator having first and second pumps PLand RRfor pumping the working fluid, each of which supplies the working fluid from a reservoir or sump 32 and directs it respectively in the first and second discharge pipes 34 and 36. On the bottom in the direction of flow of the end of each of the pipes 34 and 36 is located the valve mechanism V3that can be done in one or two separate solenoid valves, respectively, S1and S2. In any of these two variants mentioned valve or valves made/s/ thus, in the first point, R1located in the direction of flow is higher relative to the control valve V1or the second point of the P2located in the direction of flow below mentioned valve, but above another such valve V2. Valves V1and V2/in some embodiments, implementation of the present invention is/ are the valves, increasing pressure, i.e., when their work is limited to passing through them flow and increases the pressure supplied to him pipelines, while the valve V3and/or valves S1and S2represent a simple solenoid valves that do not have any influence on the pressure in these pipes. It is important to note that the control valves V1and V2connected to flow successively one relative to another, as opposed to their parallel connection opened in the description of the invention to the above-mentioned PCT application GB/00956. It should be understood that these solenoid valves provide connecting any one of the discharge pipes 34 and 36, or both of them at once to the valve V1or V2and in a variant of the connection shown in the drawing when R2>P1provides the connection between them is of aulaniP at the inlet and outlet of the valve V2set the absolute value of the pressure in the circuit of the drive control with the exception of any influence on the pressure differenceR developed by the pumps, as well as any effect on the valve V1/unless there is a change of flow parameters at the output of the pumps, for example, as a result of actuation of the safety valves/. Therefore, the valve V1can be used as a valve control variable, while the valve V2can be used as control valve couplings. In this embodiment, the present invention may ensure trouble-free operation by setting solenoid valves S1and S2on the same point of operation, providing a zero pressure difference developed by the pumps, resulting countervailing power in the variator does not occur. While a detailed explanation of how to work the valves V1and V2by changing the position of the rollers and/or switching clutch should be here following description, it is appropriate at this stage to note that the change in the value of the back pressure generated by each of the CFT. It is obvious that in this embodiment of the present invention, any change in the value of the back pressure created by the valve control2switching clutch, will not have a absolutely no effect on the magnitude of the back pressure created by the valve1as to control the variator uses the pressure differential. Therefore, the switching of the coupling can be carried out without any influence on the position of the variator rollers.

In some circumstances it would be advisable to provide some form of throttling the flow of the working fluid passing through the specified schema, denoted by the constraints R and r shown in Fig.4, but for simplicity of exposition to repeat it here below the description will not be anymore. The presence of such resistance would serve the purpose of damping the movement of the variator rollers and shown in this drawing option of connecting at zero flow rate at the valve V1, the flow resistance at zero flow rate equal to1= RV1and zero anti /zero pressure differenceR developed by the pumps/ resistance left article is on the throttle, presented to the limiter r, should be made the condition that R is equal to r + RV1, i.e., the effect of throttling + minimum flow resistance provided by the valve. However, during an emergency stop, when the back pressure resulting from movement of the variator rollers should be kept to a minimum, this system can be configured to the minimum resistance to the change of the gear ratio by switching both solenoid valves S1and S2the hole H, which allows to provide free reverse flow and unimpeded flow through them of the working fluid flow from one pipeline to another, resulting in possible to avoid problems associated with excessive or insufficient pressure, which is typical for similar systems known from the existing level in the art. In addition, we provide when applying throttling zero resistance can be obtained, and switching both solenoid valves S1and S2the hole L. in order to obtain this effect, in this embodiment, this izobreteny the deceleration of the vehicle and shown schematically position 16, and a switching mechanism responsive to a signal received from a specified control device 16, and is shown schematically position 18, which enables the control valves S1and S2to switch them in that position in which all the working fluid coming from the pump PLand PRis communicated to the valve V1after detection of the transition of the vehicle in the braking mode or slow motion. For greater clarity, all of these items are shown only in Fig.5.

In the embodiment of the present invention shown in Fig.5 shows one possible connection of the coupling to the schema of the hydraulic actuator, in which the coupling for high and low modes /referred to later in this description as clutch CRand CL/ is connected directly to the discharge pipes 12 and 14 in the direction of flow immediately behind the pump PLand PR. This execution scheme can ensure that the impact on clutches absolute pressure created in the branches of this circuit hydraulic actuator. For shown in this drawing, the version of the schema the corresponding coupling WithLby changing the provisions of the solenoid valves S1and S2on the opposite, so that the clutch CLconnected to that branch of N, which is at a higher pressure. As shown, the pressure in the clutch CLset depending on the pressure differentialP at the inlet and outlet of the valve V2and this is the valve that is used to control the inclusion of any of these couplings, without any impact on other, already included clutch /CR/. During operation exceeding the normal speed, i.e., when the power developed by the vehicle, is transmitted through the wheels and load motor/ solenoid valves1and S2can be switched in the opposite direction, but to control the variator requires only a small pressure drop, and therefore operating in this mode, the clutch, upon reaching the valve V2the point of low pressure, which will require higher values of absolute pressure, will not cause any operational problems. Of course, at this stage it is not possible to change the operation mode, so as to include the clutch cannot be filled is the mode when exceeding the normal speed can be simply removed without any serious deterioration in the ability of the vehicle to move.

Referring now again to Fig.6, note that when the clutch WithRfill the clutch WithLis done by opening the valve 20 in the inlet line 22 leading to this clutch, which allows the pump PLto complete the coupling of the working fluid under a lower pressure of the two existing values in the considered scheme. To ensure that during all stages of filling of the coupling to maintain the appropriate pressure dropP in the variable-speed drive may be used the corresponding limiter rLproviding the necessary resistance to the flow. The limitation in certain circumstances - and full overlap/ orifice valve V2will cause flow from the pump PRwill take the left branch 26, thereby complementing the stream coming down from the pump PL. The magnitude of the pressure in the system is required to fill the clutch, change depending on the specific viscosity of the working fluid. While this option scheme provides a perfectly acceptable course of the process of inclusion of the coupling, however, may desire and the th coupling with the pinning its disks to each other with the to avoid jerks when turning on the clutch.

An alternative, and possibly more reliable variant of implementation of the present invention shown in Fig.7, on which the scheme in the above execution complemented by appropriate intake valves FLand FRensuring the filling of the respective clutches and located in the area between the respective pump and clutch. The flow of the working fluid is supplied to these valves from the respective of these pumps either through primary point of filling RFPlocated in the direction of flow mentioned below regarding the second point, R2but above relative to the valve V2or from the secondary fill point SFPlocated in the direction of flow below regarding the above pumps PLand RRbut above relative to the first mentioned point R1. In addition to the valves fland freach pair is supplied with a pressure relief valve, denoted ELor ER. The purpose of these latter valves E is to provide a connection to the flow of working fluid with the inclusion of an appropriate coupling or disconnecting it from the mentioned thread, and exercise is exploitatie full inclusion clutch croccurs when connecting it with the valve FRto the pump PRand dividing through valve ERdrain it with the pallet 30, causing the entire flow is directed into the coupler. Off clutch clby using the valve ELconnecting it with the pallet 30, allowing the working fluid may be discharged from the clutch, but when this valveLconnected to the primary point of filling PFP, resulting in the filling pipe 26 with fluid under pressure, which actuates the valve V2. Fill the clutch WithLbegins with a switching valve ELso that has been connecting it to the valveL, resulting in the disconnection of the drain into the sump 30, allowing the flow of working fluid directed from the primary points of filling RFPthrough the valves FLand EL. Valve V2can be used for regulating the pressure of filling, and in their extreme positions he may overlap and be sent to the clutch WithLthe entire flow from both pumps. Of course, in the process of filling of the coupling will be a change /the awn pressure, developing these pumps and so the mode of operation of the variator will not in any way influence the process of filling of the coupling. When the clutch WithLwill completely fill the working fluid in the hydraulic system under a lower pressure, will switch solenoid valve FLin the position in which the pump connection is the same as for clutchR, i.e., it will be connecting directly to a secondary point of filling SFPand then valve V2will be able to regulate the pressure in the system in such a way as to ensure full inclusion without influence on the magnitude of the opposing forces in the variator, which is regulated by means of valve V1. To fully enable coupling WithLused working fluid under higher pressure, and as such inclusion occurs, the valve S1switch in position N, which provides the transition transmission on a synchronous setting, and the process of changing the mode of operation continues by simply disabling the supply of the working fluid in the coupling, which becomes unnecessary. It should be understood that the entire filling cycle-inclusion occurs when continuous streams of working is to and on the other hand considered the following drive control. Therefore, the magnitude of the reactive pressure regulator will not change as long as no work relief valve or other pump having their respective impact on the flow in this circuit. To switch the valves ELand FLand valves FRand ERto such an extent and then, when necessary, may provide adequate control of the device together with the control device 31. Under normal operating conditions, the valve V2is configured to create a relatively high pressure during the entire filling process, reducing the time to fill the clutch, thus greatly restricting the flow of the working fluid flowing from the scheme. Therefore, when there will be a complete filling of the clutch, the pressure in the circuit will increase dramatically, because the termination revenue stream in the coupling will lead to “sudden removal of the load from the pumps. This problem can be overcome by using a number of different ways, one of which is shown in Fig.8.

In the embodiment of the present invention, presented at pacoste, once completed the inclusion of the corresponding clutch. The drive 32 is connected to the circuit in the tertiary point of filling TFPlocated in the direction of flow below regarding the primary point of filling RFPbut above relative to the valve V2. Preferably, the drive 32 represented such a drive, which has a variable resistance is provided, for example, by means of a spring 34 acting on the upper surface of plate 35 of the drive so that the flow of the working fluid entering the accumulator 32, opposed, at least partially compressive force of the spring. Choosing an appropriate value of the stiffness coefficient of the spring and/or by using a spring with variable stiffness, it will be possible to provide automatic control of the magnitude of the pressure at which it is filled clutch. For example, it would be low spring stiffness at the initial stage of the process of filling the drive and increased stiffness of the spring at the final stage of completion.

Assuming that the change of mode, or filling, or turn on, coupling occurs at relatively small is to provide for the regulation of the process of its incorporation into sufficiently for in order to allow replacement of the valve V2a solenoid valve 36, as best shown in Fig.9. In this embodiment of the present invention, the valve 36 is a two-position valve which when in its first position, directs the working fluid in the sump 30, and when in its second position, closes off the outlet, through which the working fluid is sent to the drive 32. During operation of the filling process, or enable, the coupling is carried out by preventing the release of working fluid from the hydraulic circuit as long as such inclusion will not be completed. Prihvatyvaya drive coupling leads to a corresponding change in the relative positions of the working elements of the variator, making the proper gear ratio is achieved in it before this will enable the clutch.

An alternative implementation of the present invention is to replace the drive 32 adjustable relief valve, it should be noted that the pressure in the coupling, which is in an enabled state, has a relatively low value, because the gearbox of this type is not required to vkluchaya Fig.10, and the safety valve shown here schematically and indicated by the position 38. In the embodiment of the present invention shown in Fig.10, a relief valve connected to the valve 38 by means of the inlet pipe 40 having a first branch 40A connected to the safety valve with the hand, to which is applied the pressure, and the second branch 40B, attached to that side where the spring is. This spring is shown schematically and indicated by the numeral 42. In the specified second branch includes a so-called limiter setting of shutter 44, which contributes to the creation of a variable back pressure. This pressure has a basic minimum value at the zero moment of time, and then begins to increase in accordance with the desired plot. To ensure filling of the safety valve, solenoid valve 36 is connected to the safety valve so that the working fluid of the hydraulic system came to this valve directly with the hand, to which is applied the pressure, and accumulated in it with such intensity, which depends on the pressure and the size of the exhaust hole the pressure inside the safety valve, the flow coming through the limiter setting of shutter 44, to reach the specified pressure relief valve into the space above the spring, while additional efforts, acting in the direction of application of force of the compression spring. The pressure in the circuit will over time be increased, but without the occurrence in this case the so-called effect of “sudden removal of load in any of the existing two pumps. When completed the process of integrating the corresponding clutch, solenoid valve 36 will then be returned in such a position, which is shown in Fig.9, which results in the return of the working fluid of the hydraulic system into the sump 30. To ensure the possibility of draining the working fluid of the hydraulic system on the side of the drive, where the spring is, requires the presence of a small drain holes 46 passing through the body of the piston. The size of the holes is chosen in such a way that it had so little effect on the pressure in the drive, so they could be ignored, but it would also be quite bol is pytela, where is the spring, once the process is complete turn on the clutch.

An alternative connection of the coupling shown in Fig.11, from which it should be understood that a supply of working fluid under high pressure to enable the coupling is carried out from the second primary fill point SPFPlocated in the direction of flow is higher relative to the valve V1but lower relative to the point p1. The diagram shown in this drawing, configured to operate the left side and provided with valves FRand ERin which the clutch CRconnected to the valve V1and the pump PRis a pump that develops higher pressure. CouplingLdesigned to be filled with working fluid under a lower pressure, i.e., the valve ELconnected directly to the coupling WithLand the valve FLconnected to the point PFP, i.e., to the source of lower pressure. In the case when the direction of torque transmitted in this transmission is changed to the opposite, respectively, is carried out and then switching valvesLand SRso that they SIP is the normal speed may be here in any mode of operation, and reverse mode of operation is possible by connecting the corresponding coupling to a source of fluid under high pressure through the valve V1/. On Decel valves S2and SRcan be connected to the valve V1without changing the operating conditions of the clutch.

In addition, the control sleeve can be advanced by changing the valve position F so that it is connected to the primary point of filling RFP.

In order to ensure that the variator corresponding hydraulic axial load, can be used variant of implementation of the present invention shown in Fig.12. In this embodiment, the present invention provides for the application of the corresponding valve, commonly called “selective valve configured to identify a higher pressure”, 50, which is connected between the two discharge pipes, connecting them with each other, and operates in such a way as to ensure the flow of operating fluid under high pressure, using it in order to create an axial load. Conventional valve “is configured on the RS of the invention to PCT application GB/00956, in this embodiment, the present invention is not applied, because there is already a point PFPserving as a source of working fluid under the lower of the two generated pressure which controls the operation of the variator given formed in the scheme of differential pressure, and can be applied to the working fluid in the hydraulic system under a lower pressure, to fill her camera, creating thrust. The mechanism that creates the thrust will be in this case to occur exactly the same as in the previous scheme, but given the fact that the hydraulic Luggage in our case is filled from the electoral valve 50 that is configured to identify a higher pressure, which corresponds to the value at the point RFPadjusted through current in the circuit of the valve V1.

It should be understood that the valve V1may be included in the work in such a way as to ensure that the change in the value of the back pressure, and therefore, to regulate the pressure acting on the main piston 52 and 54, regulating polio, it should also be understood that provision may be made for the use of a single electronic component, combining as a control device and control device, and designed for performing all functions of the control device and control functions disclosed herein above the description. Such a control device, combined with the control device, shown schematically in Fig.3, where it is designated by the position 56.

Claims

1. Diagram of the hydraulic drive control for a continuously variable transmission /BKP/ with the variator and many couplings (ClCrto switch modes of operation, containing the first and second hydraulic pressure pipelines, the first and second hydraulic pumps (PLPR) connected to the aforementioned first and second discharge pipes respectively and are intended for pumping the working fluid of the hydraulic system on these pipelines and to increase the pressure of the working fluid, the first and second control valves (V1) and (V2) to adjust the hydraulic pressure designed to regulate pressure for regulating the hydraulic pressure of the working fluid injected into the switching device for the specified clutch gearbox containing coupler (ClCr) modes, in which the first and second valves (V1) and (V2connected to flow sequentially relative to each other, and using the first distribution valve mechanism (S1, S2for the working fluid in such a way as to provide the ability to selectively direct the flow from the pumps (PLPRin the first point (P1located in the direction of flow above relative to the first valve (V1), or to a second point (P2located in the direction of flow is lower relative to the first valve (V1), but is higher relative to the second valve (V2) whereby the first valve (V1) regulates the pressure of the working fluid acting on the main piston, regulating the position of the rollers, and the second valve (V2) regulates the pressure of the working fluid injected into the switching device of the transmission.

2. Diagram of the hydraulic actuator under item 1, in which the first distribution valve mechanism for fluid contains two two-way valves, each of which has first and wthout fluid input in the above-mentioned first point (P1and each of the second outlets connected in such a way as to ensure the supply of the working fluid in the above-mentioned second point (P2).

3. Diagram of the hydraulic actuator under item 1 or 2, in which the first valve (V1) is a valve that allows the pressure to increase and is designed to regulate the pressure on the section located upstream with respect to it in the direction of flow, providing a supply of working fluid to the variator, and in which any flow through the first valve (V1), combined with any other stream which is sent directly to the second point R2for subsequent supply it to the second valve (V2).

4. Diagram of the hydraulic actuator according to any one of paragraphs.1-3, which further comprises limiting the flow of funds (R), designed to limit the flow of the working fluid supplied directly by the corresponding branch from the first distribution valve mechanism for fluid in the second period (P2), which is carried out so that the resistance in each branch was essentially equal to the total resistance value when progogine on p. 4, which contains limiter (r) located on the path for supplying the working fluid in the first valve (V1), as well as the fact that the total resistance value of the limiter (r) and the resistance in the first valve (V1) essentially equal to the total value of resistance restricts the flow of funds (R) and any other resistance within each of the inlet branch.

6. Diagram of the hydraulic actuator according to any one of paragraphs.4 and 5, which further comprises a corresponding control device that is triggered when the deceleration of the vehicle, and the switching mechanism is performed by providing the possibility to engage so that the first distribution valve mechanism for fluid switched in such a situation, in which all the working fluid coming from the pump (PL,RR), is routed to the first valve (V1after detection of the transition of the vehicle on the mode of slow motion.

7. Diagram of the hydraulic actuator according to any one of the preceding paragraphs, which also contains the corresponding switch mechanism, implemented with software in the lowland to the working fluid in such a position, in which all the working fluid coming from the pump (PLPR), is sent to the second point (P2), and not in the first point (P1).

8. Diagram of the hydraulic actuator according to any one of the preceding paragraphs, which contains the first and the second clutch switch modes, respectively (CR) and (CL), and each of the clutches (CRand CLconnected in such a way as to ensure that the receipts in it working fluid from a point located in the direction of flow below the pumps (PRPL).

9. Diagram of the hydraulic actuator under item 8, which also includes a flow limiter (rLand rRlocated on the way of supply of working fluid to each of the clutches (CRand CL), resulting in the corresponding supply line leading to one or another of these couplings, supports preset pressure.

10. Diagram of the hydraulic actuator according to any one of paragraphs.1-9, in which the inlet line of each of the coupling requires the presence of the inlet valve (FLFR), providing for the filling of the respective coupling the working fluid and located on the Uch is drasti enters the valve from the respective pump or through the primary point of filling (PFRlocated in the direction of flow below regarding the second point (P2), but is higher relative to the second valve (V2), or through a secondary point of filling (SFPlocated in the direction of flow below regarding the above pumps (PLPR), but is higher relative to the first point of the P1.

11. Diagram of the hydraulic actuator under item 10, in which the secondary point of filling SFPis located in the direction of flow is higher relative to the first valve distribution valve mechanism (S1,S2for the working fluid.

12. Diagram of the hydraulic actuator according to any one of paragraphs.8-11, which further comprises a valve (ELER) pressure relief for each of the clutches (CLWithR), who in his first position acts in such a way that the flow of working fluid directed to the appropriate coupler (CL) or (CR), and in its second position operates so that the working fluid therefrom merged, but this would be equivalent to receipt of back flow of fresh fluid.

13. Diagram of the hydraulic actuator according to any one of paragraphs.11 and 12, which contains the appropriate environment to ensure the flow of working fluid from the primary fill point RFPduring the stage of filling of the coupling and from the secondary fill point SFPduring the stage of inclusion of the specified clutch.

14. Diagram of the hydraulic actuator according to any one of paragraphs.10-13, which contains the appropriate controls designed to switch the positions of the first distribution valve mechanism (S1, S2for the working fluid so that the working fluid directed from both pumps (P1and R2), in an appropriate coupling (ClCrthrough secondary point of SFPfill in.

15. Diagram of the hydraulic actuator according to any one of the preceding paragraphs, which further comprises a drive fluid, designed to receive flow of the working fluid will be completed as soon as the inclusion of the corresponding clutch.

16. Diagram of the hydraulic actuator under item 15, in which the drive receives the working fluid from the tertiary fill point (TFPlocated in the direction of flow is higher relative to the second valve V2but lower relative to the primary fill point (PFP).

17. Diagram of the hydraulic actuator under item 16, in which the second to the WMD of PP.1-14, which further comprises an adjustable relief valve, and second valve V2is a solenoid valve and the second valve2while in its first position, operates so that the flow of working fluid directed through the valve and then into the sump, and being in its second position, operates so that the working fluid went in adjustable relief valve.

19. Diagram of the hydraulic actuator under item 18, in which the adjustable relief valve is a spring-loaded pressure reducing valve having a path limiter adjust shutter speed, intended to receive part of the flow of the incoming fluid in order to send it to the safety valve from the side where the spring is, which results in an additional force applied in the direction of action of the spring and providing a corresponding pressure increase in the hydraulic circuit.

20. Diagram of the hydraulic actuator under item 19, in which the pressure reducing valve includes a drain hole intended for draining the working fluid in the case soplelebma of PP.1-20, in which if the transmission of the corresponding hydraulic mechanism, creating thrust in this gearbox, in the above-mentioned mechanism is used to supply fluid under higher pressure selected from two values generated by the pumps (PLPR).

22. Diagram of the hydraulic actuator under item 21, which further comprises a suitable valve /NW/ reacting to input pressure, which is connected to the circuit so as to ensure receipt by him of the working fluid of the hydraulic system from both pumps (PLPR), a recovering working fluid directed to the mechanism that creates thrust in the gearbox, was all the time only under the higher of the two different pressure developed by the pumps.

23. Diagram of the hydraulic actuator according to any one of paragraphs.1-22, in which if the transmission of the corresponding hydraulic mechanism, creating thrust in this gearbox, the mechanism that creates the thrust is used to supply the working fluid in the hydraulic circuit of the actuator under lower developonline contains the corresponding switch mechanism, designed to switch from a working fluid under a lower pressure when its the mechanism that creates thrust in the gearbox, on the supply in the mechanism of the working fluid under a higher pressure, choose from the two different values that are created in the schema.

25. Continuously variable transmission having a hydraulic circuit of the drive control in accordance with any of paragraphs.1-24.

 

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