KR100629553B1 - Valve device, especially a combined proportional-directional control valve - Google Patents

Abstract

Disclosed is a proportional control-directional valve device. The valve device has a valve body having at least one supply pipe and one return pipe, mounted inside the valve body, and having a control edge for opening and closing a connection between the side end portions of the supply pipe and the return pipe in an axial direction. A movable valve piston, an actuator for providing a driving force to the valve piston, an opening formed in the valve piston, at least partly mounted inside the opening, and thus axially movable relative to each other with the valve piston. A plunger, formed between an opening of the valve piston and an outer circumferential surface of the valve piston, the inlet of which is disposed on the outer circumference of the valve piston and is in direct communication with the return pipe so as to apply pressure of the return pipe to the plunger Force is applied to the orifice, the plunger mounted inside the valve body Limiting the movement of the plunger in the direction of rotation, the limit stop allowing the magnitude of the force to be determined by the return tube internal pressure, and a second energy store for generating a force opposite to the driving force on the plunger inside the valve body. A part is provided.

Description

VALVE DEVICE, ESPECIALLY A COMBINED PROPORTIONAL-DIRECTIONAL CONTROL VALVE}

The present invention relates to a valve device, and more particularly, to a valve device that combines the functions of a proportional valve and a directional control valve.

Proportional valves, also called directional control valves, have been designed and applied in many applications. The valve piston of the directional control valve, also called the control plunger, moves to various deformation positions to connect different hydraulic connections to control the working fluid, and a change in direction in the flow of the fluid can be achieved. The valves are characterized by their nominal width, nominal pressure, and possible distribution options. The main module of the directional control valve is the control device. Valve pistons mounted inside the valve body or control housing directly switch fluid flow. An actuator is attached to at least one end surface of both end surfaces of the valve piston to generate an operating force required to move the valve piston. The design change is often applied to so-called spool valves where the closing of the valve is initiated by partial overlap as a result of the relative movement of the individual valve components, in particular the valve piston inside the valve body. The valves are classified into rotary spool valves, longitudinal spool valves, and the two types of combined valves by shape and movement type. The control unit or valve unit is appropriately classified by the number of connections, the number of possible hydraulic lines, and the number of possible shift positions. Control edges and the valve body of the valve piston have a particularly important effect on the precision of shift events. These affect the throttling of the flow area, and therefore usually the speed of the consumer, a machine. Various flow characteristics can be obtained by appropriately modifying the shape of the control edge. The directional control valve provides a predetermined shift position.

The proportional directional control valve is preferably defined as an electrically controlled continuous variable directional control valve, wherein the axial movement of the valve of the valve piston is preferably in proportion to the value input by the pressure of the closed actuator. Or controlled in pressure control mode. The actuator of the electrically continuous variable control valve is designed as control magnets (solenoids), which allows the valve piston to facilitate axial movement in proportion to the electrical input value. Since the valve piston is continuously adjustable at any position within the two stop positions provided by the valve body, it is advantageous in controlling and adjusting the speed of the hydraulic consumer. Such valves are for example introduced in the following data.

1) Sales literature by Mannesmann Rexrodt:

RD 29 586 / 09.89

RD 29 175 / 03.93

2) Sales literature by the Herion-Werke KG-Fluidtechnik Nr. 7502263,0503.92

Proportional valves of this type have the disadvantage that the activation force generated by electromagnetic, hydraulic, mechanical, or any other means is the greatest hope that occurs downstream of the valve's consumer. The pressure must be chosen so that it can be maintained on a long term basis. The size of the effective area exposed to that pressure is determined by these requirements. However, this has the consequence that low pressures must be controlled according to appropriately low operating forces. At the lower pressures desired, greater pressure variability is expected during the control process. Increasing the range of operating forces usually results in an increase in the size of the actuator. For example, if the actuator is designed in the electromagnet manner, the basic increase in magnetic force results in an increase in the size of the magnetizing coil, which in turn requires more space. Furthermore, the cost of the electric conductor coupled to the magnetized coil increases in size, and the power consumption also increases. In general and in terms of applications using these valves, there are limitations on the size of the valves and actuators, so precise control of pressure in hydraulic consumers is not always feasible.

It is an object of the present invention to further develop a valve arrangement of the type mentioned above so as to avoid the disadvantages mentioned above. In particular, the present invention minimizes pressure fluctuations at very low target pressure set points. Furthermore, the present invention is an automatic transmission having such requirements that the clutch elements need to deliver high torque while operating in the converter range, and that the fluid clutch needs to be controlled as precisely as possible at a relatively low pressure. It is to provide a valve device applicable to the.

In the first pressure range or proportional range (which can also correspond to the total operating range of 1 to 5 bar), the valve arrangement is characterized by the highest precision and the largest In the state of actuation force, it should be possible to control at least proportionally to the current, taking full advantage of the maximum allowable actuation force. In addition, the valve must be capable of operating as a normal directional control valve in the second rising pressure range of 6 to 20 bar, which is capable of delivering the total pressure independently of the corresponding pressure level in the hydraulic consumer. That means you should be able to. In achieving these requirements, design complexity and cost should be minimized.

The solution described in this application is well represented by the features of claim 1.

The valve device includes a valve body having at least one supply channel and a return channel, and a valve piston mounted inside the valve body and axially movable. The valve piston includes an actuator for providing an actuation force to the valve piston and control edges for opening and closing a connection of cross-sectional areas of the supply and return pipes. For this invention, at least a portion of the overall operating range of the valve device is provided with means for generating a force opposite to the operating force. The opposite force is determined by the pressure inside the return tube. Within a certain pressure range that defines the first zone of the overall drive range of the valve arrangement (this first zone may also correspond to the entire drive range), the possible range of actuation force increases with respect to the pressure range in the hydraulic consumer. To promote more sensitive control of the operating force and the final pressure in the consumer. Thus, a given pressure range in the consumer or return piping requires a wider range of operating force than conventional proportional valves. This is achieved after the valve piston reaches the control position by reaching an equilibrium between the actuation force and the pressing force acting in the opposite direction to the actuation force, where the pressing force is applied to a region as a function of the pressure in the hydraulic consumer. To impose.

Means for achieving the object are formed in the interior of the valve piston and extending to the end of the valve piston located in the opposite direction to the actuator, the inner opening, mounted inside the inner opening and relative to the valve piston A movable plunger, a limit stop supporting the plunger, and a connection hole formed between an inner opening of the valve piston and an outer circumferential surface of the valve piston, wherein the mouth of the connection hole of the outer circumference of the valve piston includes: The connecting hole is arranged to be in communication with the return pipe, operating in the specified portion of its entire drive range, its proportional range.

This design makes it possible to achieve the highest possible ratio between actuation and friction. The frictional force is mainly determined by the pressure difference in the valve, the contamination level of the working fluid, the valve diameter or other design related features. The actuation force is mainly limited by the size of the actuator. In the case of an electromagnet, the size of the magnet is a limiting factor. Even at a lower operating force range, it is possible to adjust lower pressure levels in the consumer or return tube connected to the consumer.

In a preferred embodiment, the valve is designed as a combination of proportional-direction control, as outlined in the present invention. In addition to providing a function of distributing fluid, the valve device further includes a device for limiting and compensating the magnitude of the force acting against the actuation force. The device is designed in the form of an energy storage associated with a limit stop for the plunger and functions to limit the force acting on the plunger. The limit stop no longer functions as a solid stopper if the pressing force, determined by the pressure in the return tube and the plunger, is generated by the energy storage unit and exceeds the force in the opposite direction of supporting the plunger. Instead it is forcedly moved by the plunger. This movement is limited by an additional limit stop located between the plunger and the valve piston. Once the plunger has reached such a limit stop, the plunger can no longer move in the direction of the pressing force, so that only the valve piston moves alone in response to the actuation force.

According to the invention, the valve device facilitates controlling the control of at least the first low pressure range at its hydraulic consumer to a near maximum possible operating force, which determines the first part of the overall drive range of the valve device. In certain high pressure ranges, which determine the second part of the overall drive range of the valve device, the valve functions solely as a directional control valve. This means that when it comes to the second part of the entire drive range, the pressure in the return tube directly coupled to the hydraulic consumer no longer has any effect on the function of the valve arrangement. Thereby, precise control performance can be obtained in the first zone of the entire drive range of the valve device, which is in the low pressure range, despite the small command values. The switching of the valve device from the proportional function to the direction control function takes place automatically as a function of the pressure in the consumer. The timing of such a change can be determined through appropriate geometric and mechanical design considerations of the valve device.

In design, the valve device has at least one valve body having a center bore for receiving an axially movable valve piston. The mesopores, in combination with the associated chambers, form so-called pressure compartments, which correspond to the supply and return lines, preferably corresponding to the position of the valve piston in the mesopores. Allows the connection between the return lines connected to the hydraulic consumer. Furthermore, the valve piston has an inner opening for receiving a plunger that is axially movable. The plunger is limited in movement in the axial direction by a limit stop supported by the energy storage unit. An end-face of the plunger, more particularly facing away from the limit stop and extending into the inner opening of the valve piston, is connected to the pressure of a return line or connection line connected to the consumer through the connection hole. Exposed. The purpose of the orifice is to provide a path for communicating the inner opening with the outer circumferential surface of the valve piston located in a proportional range within the region of the return flow. The valve is conceptually designed so that in the first end position, the connection between the supply line and the return line—the connection to the consumer—is shut off.

The ability to actuate the valve piston in the valve body is provided by an actuator. Preferred actuators are electromagnetic actuators. Other possibilities, such as electro-hydraulic actuators, are also feasible. When continuous control is desired, the valve piston is actuated by a force F _application exerted by the actuator. This allows the connection between the pressure compartments to be established, which are formed by the chamber at the outlet and the chamber connected to the inlet by the mesopores as well as the mesopores. As a result, the working fluid can flow from the supply pipe to the consumer. At the same time a certain pressure level is obtained across the connection orifice between the inner opening and the outside of the valve piston in the return region, which acts on the end of the plunger supported by the limit stop in the valve body. This creates an equilibrium condition. It means that the actuation force is equal to the pressing force, where the pressing force is a result of the pressure of the consumer acting on the plunger zone. By providing additional energy storage between the valve piston and the plunger mounted in the inner opening of the valve piston, the force obtained therefrom is added to the pressing force.

The plunger is supported by a limit stop that is part of the energy store. The force generated by the energy store corresponds to the force of the plunger at the maximum desired proportional pressure. Therefore, in the entire proportional range, the force applied by the energy storage unit or the position of the limit-stop does not change. The preload of the energy store serves as a direct setpoint for the specified maximum target proportional pressure.

However, if the pressure regulated at the consumer generates a force on the plunger that is greater than the force generated by the energy storage associated with the limit stop, the plunger is protruded and shaped as integrated into the valve piston. Compress the energy store so that the plunger rests against at least one limit stop. When this state is reached, the consumer's internal pressure no longer acts on the valve. The position of the valve piston is determined only by the external force of the actuator and the energy store, as in the case of the directional control valve.

Proportional and directional control functions and applications of valve devices having both of these functions are designed to comply with the intent of the present invention on automatic transmissions, and the shift pressure is, for example, such that all shift events are within the proportional range. And only a high pressure range can be arranged to work for the electric torque.

In addition to the more sensitive performance of the valve for regulating pressure, there are other practical advantages, such as broad applicability, whereby various design requirements can be satisfied by only one valve arrangement. These advantages include the ability to provide high pressure to the consumer and to maintain this high pressure as well as more sensitive adjustment of the operating force and the consumer's final force, especially at low pressure levels.

For example, it is advantageous to design these energy storage units in the form of pressure storage units such as individual compression springs or spring packs. It is also possible to use elastic membranes.

The valve device is operable as a pure proportional valve without an energy storage connected to the limit stop. Alternatively, the energy storage may be operated by a pure direction control valve. Thus, the actuation force immediately leads the movement of the valve piston to the end, which can be achieved by selecting a very low pre-load in the energy store. The low pre-load of the energy store produces a small proportional range, and the large pre-load of the energy store produces a large proportional range. This makes it possible to manufacture a compact base valve unit according to claim 13 which can only be adapted via minor modifications with little effort to other requirements. Thereby individual components can be designed utilizing the concept of modules.

The valve device according to the invention may comprise any type of actuator. The use of actuators by electromagnetic, mechanical, hydraulic or any other means is also possible.

The electromagnetic actuator has at least one electromagnet comprising a coil and an armature.

There are other aspects of valves in which actuation force is electromagnetically generated, which is to assign different displacement limits of the valve piston or the amateur for the functional states of the "proportional valve" and "directional control valve" respectively. Is to have the ability. This has the advantage of low current consumption of the magnetizing coil in the "directional control valve" state, which takes most of the time, and therefore, in terms of heating and coil durability as well as hardware for valve control. Most important. The maximum possible displacement in the proportional range is 80% of the total displacement. Minor deviations from this value are possible.

The present invention will be described in more detail with reference to the accompanying drawings.

1A and 1B are state diagrams showing two operating states of a valve device according to the present invention;

Figure 2 is a graph comparing the operation curve of the proportional-type control valve according to the present invention and the conventional proportional valve; Uniquely, showing the relationship between the target pressure and the magnitude of the magnetic force in the consumer;

3 is a graph showing the relationship between the magnetic force and displacement of the magnetizing coil or valve piston, respectively;

4 is a graph showing the current required for the proportional valve and the direction control valve.

1 shows a simplified design and functionality of a proportional-directional control valve 1 according to the invention by a partial cross section of the valve arrangement. In one preferred embodiment, the valve is electromagnetically controlled. For this purpose, an electromagnet 2 is provided. The proportional-directional control valve 1 has a valve body 3 in which an intermediate hole 4 is formed, in which the valve piston 5 is movably mounted in the axial direction. A plurality of connecting portions, that is, at least two connecting portions, are formed around the intermediate hole 4. The plurality of connections are here shown in the form of connecting channels 6, 7, 8, which extend radially from the outer circumferential surface of the valve piston 5 to the inner intermediate hole 4.

The connecting pipe 6 is a supply pipe, and the connecting pipe 7 is a return pipe. The connectors 6, 7, 8 are connected to the intermediate hole 4 with additional chambers 9, 10, 11 located in the region of the connectors. The connecting tubes are connected to the mesopores 4 and are arranged in the direction of a circumference of a diameter larger than the diameter of the mesopores. The chambers 9, 10, 11 processed into the valve body form a control edge of the valve body 3 together with the intermediate hole 4.

In this case, the valve piston 5 is designed to have a different diameter along its axis. As shown, the valve piston is formed with two parts having smaller diameters, indicated at 12 and 13. Control edges 14, 15, 16 are formed on the valve piston 5 by different diameter differences. The control edges 14, 15 and 16 of the valve piston 5 and the control edges of the valve body 3 have a very important meaning in terms of precise control. The control edge affects the speed of the machine or consumer downstream of the proportional-directional valve device 1 by affecting the regulation of the flow section. The chambers 9, 10, 11 whose shape is determined by the external shape of the intermediate hole 4 and the valve piston 5 form variable pressure compartments. Other flow characteristics can be obtained by proper shaping of the control edges.

In this case, the valve device 1 with three connections is shown. The connecting pipe 6 connects the pressure compartment and the pressure supply source formed by the chamber 9 and the intermediate hole 4. The connecting tube 7 connects the pressure compartment formed by the chamber 10 and the intermediate hole 4 with the consumer (not shown).

The valve piston 5 is formed with an opening 20 formed parallel to the center line at its end along the axial direction. The plunger 21 is mounted inside the opening 20 so as to be movable in the axial direction. The plunger 21 may be located at different points. The plunger may be located completely inside the opening or may protrude from the opening and protrude beyond the end 22 of the valve piston 5. In order to prevent the plunger 21 from falling out of the opening 20 of the valve piston 5, the plunger has a protruding flange in the vicinity of its end 23. Thus, the end 23 faces away from the end 22 of the valve piston. The protruding flange may be designed such that a separate member, for example an annular member, is coupled, compressed or screwed to the plunger 21. However, the plunger and the flange are preferably integrated. The flange may be a single unit projecting around the periphery, or in the form of a plurality of pieces arranged along the circumference in a special manner.

In addition, the opening 20 is divided into a first zone 25 having a larger diameter and a second zone 26 having a smaller diameter. The second zone houses and guides the plunger 21. The first zone is used to receive an energy storage unit 27 which is designed in the form of a compression spring.

Around the end portion 22 of the valve piston, an axially movable limit stop 28 is mounted away from the actuator 2, in this case an electromagnet. The limit stop acts on the end of the valve piston or at least part of the end 30 of the plunger 21. Thus, the limit stop 28 is supported by the energy storage units 31, F2, in this case compression springs.

The current design shows two boundary positions. The first boundary position is shown in FIG. 1A. This representation represents a zero-flow state. Thereby, the load connected to the consumer connected to the connecting pipe (return pipe) 7 is not applied at all, and the pressure supply through the connecting pipe (supply pipe 6) is cut off. This state is the result of preventing the control edges 14 to 16 from communicating between the pressure compartment formed by the chamber 9 and the intermediate hole 4 and each pressure compartment connected to the consumer. Thus, the return tube, the connecting tube 7 which is connected to the consumer, is blocked.

Figure 1b shows a proportional-directional control valve in a modified position that functions as a proportional valve. The actuator comprising an electromagnet 2 is integrated into a coil which is magnetized by at least one conductor, for example a current, which is part of the electromagnet. The electrical current value corresponds to a target setting value that meets the desired target value of the consumer. The specification of the desired target pressure value in the consumer is also referred to as the adjusted pressure W _pASoll and can be completed by simple calculations or lookup tables or by execution curves stored in the memory device. The methodology described below is not shown in the drawings and is only one of many. The pressure regulation or pressure regulation by the valve device 1 is generated, for example, by means of the first control circuit, which is not described herein. The value input to this control circuit includes not only the continuously updated actual value of the pressure P _{A 1st} adjusted in the return tube but also the preferably adjusted pressure value W _{PA soll} targeted in the return or return tube. The valve device 1 here serves as the final control element for the regulation of the (regulated) pressure. The command value affecting this final control element in this case is the value of the magnetic force F _magnet which affects the position of the valve piston 5. The magnetic force F _magnet corresponds to the required operating force required to shift the position of the valve piston 5 of the valve device 1 to open each flow section between the connecting tubes 6, 7, 8. The adjustment of the magnetic force F _magnet is performed by another control circuit which is an auxiliary circuit of the pressure control circuit. The numerical value input to the second control circuit is a reference variable for the magnetic force F _magnet generated by the pressure regulator. According to the magnetic force F _magnet , the valve piston is moved axially relative to the plunger 21. Thereby, the respective pressure compartments formed by the chamber 9 and the intermediate hole 4, the chamber 10 and the intermediate hole 4 are connected. The connection between the pressure compartments makes it possible to connect the supply tube 6 and the connecting tube 7 (connected to the consumer). A certain pressure P _1st acts on the connecting pipe 7 by the connection between each of the chambers 9 and 10 and the pressure compartments formed by the intermediate holes 4. The predetermined pressure is transmitted through a connecting orifice 36 extending radially inwardly from the outer surface of the valve piston 5 toward the inner compartment 20.

The pressure is applied to the plunger zone defined by the end 23. By the above process, the _acting force in the form of magnetic force F _magnet is the pressure F _{druck which} is the sum of the force generated by the energy storage unit F1 and the product of the pressure P _1st of the consumer and the area A of the plunger in the end 23 region. By correspondence, they are always balanced.

The plunger 21 is supported by the preload energy storage units 31 and F2 designed as spring units in the form of compression springs. By matching the preload of the spring unit to the force of the plunger 21 at the desired maximum proportional pressure, no change occurs in the spring unit during the entire proportional range.

To the plunger 21, more precisely, as soon as the adjusted pressure P _1st is applied to the surface A of the end of the plunger 21 higher than the pre-load force of the spring unit 31, the plunger 21 ) Compresses the spring unit 31, more specifically, the spring pack until the plunger stops at the limit stop of the region around the end of the shoulder S or the valve piston 5. As soon as this state is reached, the pressure in the connecting pipe connecting the consumer or the consumer to the connecting pipe 7 can no longer affect the valve device 1. Now as in the case of the directional valve, the valve piston 5 is solely external force acted by a magnet, in particular by an electromagnet and by the energy storages 31, F2, more specifically by the spring unit. Depends on

The valve piston 5 continuously moves axially towards the limit stop 28 as the magnetic force F _magnet increases slightly and opens the flow path to the consumer for hydraulic oil such as oil without obstruction.

Compared to the case where there is no plunger that directly acts on the valve piston, the plunger 21 acts on the surface of the valve 7 so that in the proportional range the actuation force on the valve piston 5 is always associated. With a counter force, which results in the need for a masticating force to move the valve piston axially.

2 is a graph showing the driving characteristics of the proportional-directional control valve according to the present invention reflecting the relationship between the return pressure or the internal pressure of the connecting pipe 7 connected to the consumer and the magnetic force F.

For this purpose, the magnetic force F is shown on the X axis and the return pressure is shown on the Y axis. To compare the objectives, a drive curve of a conventional proportional valve is shown, which is denoted by the letter I. From this graph, it is clear that the pressure P _1st changes linearly with the magnetic force F.

However, the solution provided in the present invention allows a wider range of proportionality. This means that the slope of the line in this zone is gentler, as shown by the drive curve II. Adjacent to the proportional range is the so-called directional control range, in which no pressure limitation occurs.

The extended proportional range for the larger magnetic force range F allows more sensitive control of the target pressure at the consumer for the magnetic force F.

Figure 3 is a graph showing the drive curve of the magnetic force required for the operating device according to the present invention further improved. The operating force is electromagnetically generated.

The actuator has at least one electromagnet having a coil and an amateur. Thereby, the armature is movable in the magnetic field generated by the coil. As a result of the different use of the drive curve of the magnetic force in each functional state of the "proportional valve" and "directional control valve", the flow of current applied to the magnetizing coil while the actuator is operating in the "directional control valve" state There is a possibility of lowering. Reducing the current applied to the magnetizing coil is of particular advantage, since the second zone of the entire operating range is intended for controlling the valve since the "directional control valve" function generally takes the largest part of the time. This is because it is the most meaningful part in terms of durability and heating of the coil as well as hardware. This is achieved through other displacement limits. Thus, as shown by way of example, a displacement range of 3.2 to 0.7 is utilized in the "proportional valve" functional state, and in the "directional valve" state the limit stop is used at displacement zero. Thereby, the displacement is referred to herein as the displacement of the armature or the displacement of the valve piston coupled to the armature.

By means of the targeted raising means of the magnetic force in the limit stop position, the current applied to the magnet coil can be greatly reduced without the occurrence of a draw back for acting as a proportional valve.

In the first zone of the entire operating range, in the "proportional valve" functional state, the magnetic force is approximately constant, a function of only the current flowing through the coil, and severely in the second zone in the "directional control valve" functional state. It is evident from FIG.

From the design perspective, these limitations can be solved by the realization of the displacement limit for the "proportional valve" function via the pre-load spring pack of the valve, and in the "directional valve" state the second limiter stop at the magnetizing coil. This becomes valid. The spring pack of the valve exerts a force on the plunger in the opposite direction of the force generated by the pressure of the return tube and on the end of the plunger.

As shown in the graph, in the first zone of the entire operating range, ie the “proportional valve function”, the displacement range of the valve piston uses 80% or more of the entire operating range, whereas the “direction The control valve "functional state uses approximately 20% or less range. Minor deviations from these figures are possible.

In the "proportional valve" function, the control position of the valve piston is mainly in the middle of its displacement range. During control or for example after filling, the pressure must be determined independently of the specific position of the control spool. This means that the pressure finds the desired value without overshoot during the transition from filling to control.

Figure 4 shows the characteristic pressure curve for the flow of current for the "proportional valve" and "directional control valve" functions, where in the graph, the current flow required for the magnetizing coil to reliably block the directional control valve. The range is indicated by I. The current flow required to operate the directional control valve is indicated by II and the characteristic line representing the critical current flow for causing the directional control valve to lose its active force is indicated by III.

When the valve device is mounted on an automatic transmission, the valve device is active while maintaining the "proportional valve" functional state in at least two areas during a) filling and b) during the synchronization process.

In the filling process, a predetermined initial pressure is specified as a condition. The filling process itself can be a) controlled, b) uncontrolled. In this first case, the valve piston is located at the limit stop during the intercharger, for example at the limit stop 0.7 as shown in FIG. 3. In the case of a regulated filling process, the valve piston is in the control position during the filling.

In the synchronizing process, the valve device transverses to the control position or remains at the same position at the limit stop. It is then possible to adjust to any pressure increase or pressure decrease.

In the control after the synchronization process, by applying a strong current for a short time, the valve is reliably moved to the " directional control valve " state. The magnetizing coil moves to the zero position and the pressure effect of the valve is deactivated. The current flow can be lowered to the level of holding current as a result of the increased magnetic force in the 0-position.

Claims (16)

A valve body (3) having at least one supply tube (6) and one return tube (7); A valve piston which is axially movable inside the valve body 3 and has control edges 14, 15, 16 for opening and closing the connection of the cross sections of the supply pipe 6 and the return pipe 7. 5); An actuator for providing an actuation force to the valve piston (5); Under the action of the pressure in the return pipe 7 there is provided a means for generating a force opposite to the actuation force through at least one first portion of the entire actuation range of the valve device 1, which means, An opening 20 formed in the valve piston 5; A plunger (21) disposed at least partially within the opening (20) and movable relative to each other with the valve piston (5) axially; A connecting office 36 formed between the opening 20 of the valve piston 5 and the outer peripheral surface of the valve piston 5, wherein the inlet of the connecting orifice 36 on the outer peripheral surface of the valve piston 5 is at least A connection orifice (36) disposed indirectly in communication with the return tube (7) in the first portion of the entire operating range and for applying pressure of the return tube (7) to the plunger (21); An energy storage unit (F2) for exerting a force opposite to the actuation force and / or the force exerted by the plunger (21) to the plunger (21) inside the valve body (3); It is associated with the plunger 21 in the valve body 3, can be determined by the internal pressure of the return pipe and in the direction of the action of the force acting on the plunger 21 supported by the energy storage unit (F2) A limit stop 28 for limiting movement of the plunger in the axial direction, The plunger 21 has at least one shoulder S on an outer circumferential surface of a portion disposed in the opening 20, a stop inside the valve piston 5 is associated with the shoulder S, and the valve piston (5) is axially displaced in the first part of the entire operating range, and both the plunger 21 and the valve piston 5 on the stop inside the valve piston 5 allow the entire Valve arrangement (1), characterized in that it is displaced axially in the second part of the operating range. 2. The device of claim 1, wherein the means further comprises an energy storage unit F1 disposed in the opening 20 of the valve piston 5 between the valve piston 5 and the plunger 21. Valve device (1). 3. Valve arrangement (1) according to claim 1 or 2, characterized in that the means generates a force that is directly proportional to the pressure in the return tube (7) and opposite to the pressure in the return tube (7). 3. Valve device (1) according to claim 1 or 2, characterized in that the energy storage (F2, F1) comprises at least one compression spring unit. 3. Valve device (1) according to claim 1 or 2, characterized in that the energy storage (F2, F1) comprises an elastic membrane. 3. Valve arrangement (1) according to claim 1 or 2, characterized in that the plunger (21) and the opening (20) of the valve piston (5) have a circular cross section. 3. Valve arrangement (1) according to claim 1 or 2, characterized in that the actuator is electromechanically operated. 3. The valve device (1) according to claim 1 or 2, wherein the actuator is a hydraulic actuator. 3. Valve arrangement (1) according to claim 1 or 2, characterized in that the actuator is designed as an electromagnetic actuator (2) with an electromagnet having an associated conductor. 3. Valve device (1) according to claim 1 or 2, characterized in that the deflection force of the energy store (F2) is consistent with the force of the plunger when it is at a maximum proportional pressure. A valve body (3) having at least one supply tube (6) and one return tube (7); A valve piston (5) which is axially movable within the valve body (3) and has control edges for opening and closing the connection of the cross sections of the supply pipe (6) and the return pipe (7); An actuator for providing an actuation force to the valve piston (5); An opening 20 formed in the valve piston 5 and extending toward an end of the valve piston 5 away from the actuator; A plunger (21) disposed at least partially within the opening (20) and movable axially with respect to the valve piston (5); A connecting office 36 formed between the opening 20 of the valve piston 5 and the outer circumferential surface of the valve piston 5, wherein the inlet of the connecting orifice 36 is on the outer circumferential surface of the valve piston 5. A connecting orifice (36) arranged at least indirectly in communication with the return tube (7) and for applying a pressure of the return tube (7) to the plunger (21); A limit stop (28) associated with the plunger (21) inside the valve body (3), The plunger (21) has at least one shoulder on the outer circumferential surface of the portion disposed in the opening, and the stop in the valve piston (5) is associated with the shoulder. 12. An energy storage unit (F2) according to claim 11, having an energy storage (F2) associated with said limit stop (28) and said plunger (21) in said valve body (3) and at least indirectly supporting said plunger (21). Base valve unit characterized in that. 13. The energy storage of claim 11 or 12, wherein an energy storage portion for generating a second force opposite to the operating force is further provided in the opening portion 20 of the valve piston (5), and the further energy storage portion is provided to the operating force. A base valve unit, characterized in that it is installed between the inner wall of the opening (20) and the plunger (21) to generate an opposite second force. 13. The base valve unit according to claim 11 or 12, wherein the energy storage units are designed in the form of compression spring units. The base valve unit according to claim 11 or 12, wherein the energy storage units are designed in the form of an elastic membrane. 13. The energy storage of claim 11 or 12, wherein the energy storage associated with the limit stop is selected in such a way that the bearing force that can be generated at the mounting position matches the force of the plunger at the maximum proportional pressure. Base valve unit.