Hydraulic arrangement with a metering orifice and at least one valve for hydraulically controlling a metering orifice, through which a hydraulic consumer can be supplied with pressure medium.

Abstract

Hydraulic arrangement with a hydraulically adjustable metering orifice (100) through which a hydraulic consumer can be supplied with hydraulic fluid, which has a closed position and a first flow position in which it releases an opening cross-section, and which has a housing (102) with a housing interior (104) and therein a hydraulically adjustable control spool (106) which delimits a control pressure chamber (110, 114) in the housing interior (104), and with a valve (2) with a valve housing (4) which has an axially extending interior (6), characterized by a displacement device (20) which is axially movable in the interior (6) along a stroke (16), which divides a first and a second pressure chamber (10, 12) in the interior (6) and which has a throttling device (40) through which the first pressure chamber (10) can be brought into hydraulic fluid communication with the second pressure chamber (12). is and is trained in this waythat for at least one stroke direction of the displacement device (20) and over the entire stroke (16) of the displacement device (20) a pressure medium exchange between the first and the second pressure chamber (10, 12) takes place exclusively via the one throttle device (40), wherein the control pressure chamber (110, 114) is connected to the second pressure chamber (12), wherein the control pressure chamber (110, 114) has a metering volume (V, T ) to be supplied in order to move the metering orifice (100) from the closed position to the first flow position, wherein the displacement device (20) has a displacement volume associated with the stroke (16) which is dimensioned such that it is not larger than the metering volume (V T ) the measuring aperture (100).

Description

[0001] The invention relates to a hydraulic arrangement according to the preamble of claim 1 comprising a metering orifice and a valve.

[0002] In this context, a metering orifice valve is a hydraulically actuated control valve for regulating the flow of pressure medium to supply a hydraulic consumer. Such a metering orifice valve comprises a housing with an interior chamber and a hydraulically adjustable control spool located therein. This spool can assume a pre-positionable closed position and at least one first flow position, in which an opening cross-section opens. Within the housing chamber, the control spool defines at least one control pressure chamber associated with the opening cross-section. The opening of the opening cross-section in the flow position, or the control of the opening cross-section, is typically achieved through the interaction of a section of the housing's inner wall with a control edge or a control notch on the movable control spool.The metering orifice can be designed as a longitudinal or rotary slide; accordingly, the control slide can be axially displaceable or rotatable within the housing. The position of the control slide is adjusted by filling or releasing control fluid from the control pressure chamber.

[0003] The technical problem solved by the present invention is explained below using the example of a metering orifice in a longitudinal slide design with a control slide that is axially hydraulically displaceable in a longitudinal bore of the housing. The control slide has a first control pressure surface at one axial end, which defines a first control pressure chamber inside the housing. Annular grooves are formed in the wall of the bore, into which a pressure medium channel opens. This channel can be controlled via the metering orifice, i.e., closed or opened, and / or regulated, i.e., opened with an adjustable opening cross-section.

[0004] Circumferential grooves are formed in a cylindrical outer surface of the control valve, which interact with annular grooves in the bore wall. Depending on the axial position of the control valve, an annular groove in the bore wall can be aligned with a groove in the control valve, thus establishing a pressure medium connection to the pressure medium channel opening into the annular groove. Conversely, the annular groove can be aligned with a section of the outer surface, thus interrupting a pressure medium connection to the pressure medium channel opening into the annular groove. In an intermediate position (control position), an annular groove can be in pressure medium contact with a groove in the bore wall via an adjustable flow resistance or flow cross-section, thus establishing a pressure medium connection with adjustable flow resistance to the pressure medium channel opening into the annular groove.

[0005] Adjustable flow resistances or flow cross-sections are typically achieved via control chamfers or notches formed in the outer surface of the control valve. These chamfers or notches open into corresponding grooves and extend axially from their end to the groove opening. The seal between the groove and the control chamfer or notch opening into it is created by a gap between the outer surface and the bore wall. The effective length of this gap is determined by the axial distance between the end of the chamfer or notch and the annular groove. If the control valve is moved axially so that the groove approaches the annular groove, the gap length initially decreases, i.e., the axial distance between the end of the chamfer or notch and the annular groove.With further displacement, the chamfer or notch end enters the region of the annular groove and begins to open a hydraulic connection from the annular groove, via the control chamfer or notch, into the circumferential groove. If the control valve is displaced axially further, the throttling effective length of the control chamfer or notch shortens, and its effective flow cross-section increases, until the circumferential groove itself enters the region of the annular groove, thereby completely opening the hydraulic connection. The axial distance between the chamfer or notch end and the annular groove is sometimes referred to in technical terminology as dead stroke or the area of ​​positive overlap (of the outer surface and the bore wall), and in the following, as the measuring stroke. As long as the control valve is displaced from its closed position by a distance less than this measuring stroke, the hydraulic connection between the annular groove and the circumferential groove remains closed.The axial length of the control chamfer or notch corresponds to the geometric control range of the control spool, because if the control spool is offset from its closed position by a distance that is greater than the metering stroke but less than the sum of the metering stroke and the length of the control chamfer or notch, then the flow resistance effective via the control chamfer or notch depends on the hydraulically controllable axial position of the control chamfer or notch, i.e., of the control spool, in relation to the annular groove.

[0006] Such metering orifices are used, for example, for the hydraulically controlled movement of heavy equipment. Examples include hydraulic travel motors for excavators, hydraulic drive motors for rotating the upper structure of an excavator, or hydraulic drive motors for an excavator boom.

[0007] The valves for controlling the adjustment movement of the control slide of the metering orifice are conventionally designed as a throttle valve with one throttling point - also known to those skilled in the art as a control pressure shuttle valve -, as a throttle check valve with one throttling point or as a throttle valve with two throttling points acting differently in different flow directions - also known to those skilled in the art as a load sensing or LS shuttle valve.

[0008] Especially when a control valve has a relatively large control pressure area, requiring a relatively large amount of control fluid to be supplied to or discharged from the associated control pressure chamber to move the control spool by a specific stroke, the throttling point is designed to be relatively restrictive. This ensures the control spool moves slowly and prevents pressure spikes. Due to this strong restriction, it takes a relatively long time, e.g., several tenths of a second, for a sufficient amount of control fluid to flow through the throttling point to the control pressure chamber and overcome the metering stroke of the control spool. Response delays of several tenths of a second are very inconvenient for an operator of a hydraulically driven machine.

[0009] From DE 34 40 262 A1 a pressure limiting arrangement is known in which the valve piston of a seat valve forms a displacement device that separates two pressure chambers from each other, wherein the valve piston includes a throttling device.

[0010] From DE 10 2008 008 092 A1 a valve arrangement is known which can be part of the hydraulic arrangement according to the invention, in particular forming the metering orifice, the control valve and the control pressure chamber.

[0011] In contrast to known designs of valves, the invention is therefore based on the objective of creating a hydraulic arrangement with a valve for which, in conjunction with a metering orifice, the response time, i.e. the time to overcome the metering stroke of the control slide of the metering orifice, is at least reduced or zero, so that the response time is hardly noticeable.

[0012] To solve this problem, a valve is provided according to a first aspect of the invention, comprising a valve housing with an axially extending interior. According to the invention, the valve further comprises a displacement device that is axially movable in the interior along a stroke, that separates a first pressure chamber from a second pressure chamber in the interior, and that has a throttling device via which the first pressure chamber can be brought into contact with the second pressure chamber, and which is designed such that, for at least one stroke direction of the displacement device and over the entire stroke of the displacement device, a pressure medium exchange between the first and the second pressure chamber takes place exclusively via the throttling device.

[0013] The valve according to the invention can be used for the hydraulic control of an adjustment movement of a control spool of a hydraulically adjustable metering orifice, through which a hydraulic consumer can be supplied with pressure medium. The axial mobility of the displacement device and the throttling device, which establishes a pressure medium connection between the first and second pressure chambers, enable the displacement device, when one pressure chamber (e.g., the first) is pressurized with control pressure medium, to move immediately axially towards the other pressure chamber (e.g., the second) under the influence of the control pressure medium pressure, thereby displacing control pressure medium from the other pressure chamber.Only after this immediate movement of the displacement device does new control fluid flow from one pressure chamber through the throttling device into the other pressure chamber, with a comparatively slower displacement of control fluid from the other pressure chamber than during the immediate movement. If the valve is fluidically connected to the metering orifice to be controlled, with the other pressure chamber of the valve and the control pressure chamber of the metering orifice being in pressure fluid communication, the immediate ejection of control fluid from the other pressure chamber of the valve, resulting from the immediate movement of the displacement device, can also immediately initiate the stroke movement of the control spool, i.e., without any response delay, and immediately adjust it by an initial adjustment range that at least partially bridges the metering stroke of the control spool. The subsequent movement due to the throttling or...The relatively slow damping action of the new control pressure fluid flowing through the throttling device propels the adjustment movement of the control spool forward accordingly. The immediate adjustment of the control spool by the initial adjustment range reduces or eliminates the response delay, i.e., the time it takes for the control spool to move through its metering stroke.

[0014] According to the invention, the metering orifice has a closed position and at least one first flow position, in which the metering orifice releases an opening cross-section. Furthermore, the control valve defines at least one control pressure chamber, which is to be supplied with a metering volume, i.e., a specific volume of control fluid, in order to move the control valve from its closed position to the first flow position. The displacement device has a displacement volume associated with its stroke, i.e., a volume of control fluid that is displaced from the pressure chamber, which decreases in size during movement, when the displacement device moves over its stroke. According to the invention, this displacement volume is dimensioned such that it is not larger than the metering volume of the metering orifice, in other words, less than or equal to the metering volume.This design allows the control valve to be adjusted during the immediate adjustment movement just enough to ensure that the opening cross-section opens instantly and no pressure spike occurs at the hydraulic consumer. Instead, the immediate adjustment movement bridges a portion of the metering stroke or the associated metering volume, thus shortening the response time. Preferably, the displacement volume is adapted to the metering volume so that it is approximately equal to the metering volume. This adaptation allows the immediate adjustment movement to bridge approximately the entire metering stroke or the associated metering volume instantly, reducing the response time to approximately zero. The effective displacement volume is defined as the product of the pressure area acting in the displacement direction and the stroke length.Thus, the adjustment of the displacement volume to the measuring volume of the measuring orifice can be achieved by dimensioning the displacing pressure area and / or the stroke length that can be traveled.

[0015] The valve can have a first and second stop surface, which are formed within the valve housing at a predetermined distance from each other along the longitudinal axis. The first stop surface can be located on the side of the first pressure chamber and the second stop surface on the side of the second pressure chamber. The stroke of the displacement device is defined by this distance minus a piston length of the displacement device measured along the longitudinal axis. This design allows the displacement volume of the displacement device to be precisely adjusted and adapted to the metering volume of the metering orifice being controlled.

[0016] The initial position of the displacement device can be pre-positioned, in particular pre-tensioned, to a position in which the volume of one of the pressure chambers, for example, the first pressure chamber, is minimal. To achieve this pre-positioning of the displacement device, the valve can include a first spring element. This spring element can be designed to press the displacement device into its initial position against the stop surface located on the side of one of the pressure chambers. Due to the pre-positioned initial position of the displacement device, it always travels the same stroke distance during a subsequent stroke movement; that is, the stroke distance is always well-defined.

[0017] One throttling device can be effective in a pressure medium flow path directed from the first pressure chamber to the second pressure chamber, to which a first pressure medium flow direction is assigned. In this case, the valve is permeated with control pressure medium in the first pressure medium flow direction, exhibiting the throttling effect associated with the throttling device. Here, the term throttling effect is to be understood as the pressure loss that occurs at a given volume flow rate of the control pressure medium through the throttling device.

[0018] The displacement device can further comprise a poppet valve, in particular a check valve, which is arranged fluidically in series with one throttling device. The displacement device can also comprise another poppet valve, in particular another check valve, which is arranged fluidically in parallel with one throttling device. The opening and closing directions of the poppet valves can be opposite to each other. In this configuration, the flow of control fluid through the valve occurs essentially without restriction in the direction of flow opposite to the first flow direction.

[0019] The displacement device can include a further throttling device that is effective for the pressure medium flow path opposite to the pressure medium flow path for which the first throttling device is effective. In this configuration, the valve is permeated with control pressure medium in the pressure medium flow direction opposite to the first pressure medium flow direction, with the throttling effect associated with the further throttling device. The throttling effect of the further throttling device can be smaller or, if desired, larger than the throttling effect of the first throttling device. The further throttling device ensures that, even after an initial application of control pressure medium, the movement of the control spool of the metering orifice in the stroke direction opposite to the initial stroke direction is dampened by the second throttling device.

[0020] The poppet valve can be located in an axially extending interior space of the displacement device, comprising a valve seat and a valve body that is axially movable within the interior space and interacts with the valve seat. In this configuration of the displacement device, a throttling device arranged fluidically in series with the poppet valve can be formed by a notch or a flat on the valve body or the valve seat. Designing the throttling device as a notch allows for very fine and precise adjustment of the throttling cross-section, i.e., the throttling effect, and thus the degree of damping of the control spool's stroke movement, by appropriately dimensioning the effective flow cross-section of the notch. The valve body can interact with the valve seat by being preloaded against it. To achieve this preload, a second spring element can be provided, which preloads the valve body against the valve seat.

[0021] The displacement device can have an outer surface, and the valve housing can have an inner surface complementary to the outer surface. The tolerances of these surfaces can be configured such that, during a stroke of the displacement device, a transfer of pressure medium between the first and second pressure chambers via a gap between the outer and inner surfaces is prevented. In particular, the outer surface of the displacement device can be at least partially cylindrical, and the valve housing can have a bore complementary to this, in which the displacement device is slidably mounted. This ensures stable longitudinal guidance of the displacement device.

[0022] The valve can be installed in a control pressure hose, control pressure line, or control pressure channel. In the configuration where the valve can be installed in a control pressure channel of the metering orifice, an end stop for the orifice's scraper gate can be formed on an outer surface section of the valve housing, in particular on an end face or end face section of the valve housing. Thus, various mounting, installation, and / or integration options are available for the valve on or in the metering orifice it controls or in the associated control pressure supply lines.

[0023] The valve housing can have a first and a second housing part. The first and second housing parts can be screwed together. In one embodiment, the first and second housing parts can be screwed directly together. This embodiment allows for easy installation of the displacement device and the first spring element inside the valve housing. In this embodiment, the valve is designed for installation in a pilot pressure line or pilot pressure hose.

[0024] In an alternative embodiment, the first and second housing parts can be indirectly screwed together, for example via a sleeve that can be screwed between the first and second housing parts. In this alternative embodiment, the valve is designed for installation in the metering orifice to be controlled, and it can form an end stop for the orifice's scraper slide. In this embodiment, an end face of the valve housing can be designed as an end stop surface for the control slide, in particular for a pressure surface of the control slide.

[0025] According to a second aspect of the invention, a hydraulic arrangement is provided which includes a hydraulically adjustable metering orifice for regulating the pressure medium supply to a hydraulic consumer. The metering orifice has a closed position and at least one first flow position in which the metering orifice releases an opening cross-section. The metering orifice has a housing with an interior and a hydraulically adjustable control spool arranged therein. The control spool defines at least one control pressure chamber within the housing interior. According to the invention, the hydraulic arrangement includes at least one valve according to the first aspect of the invention, wherein the first or the second pressure chamber of the valve is connectable, and in particular connected, to the control pressure chamber of the metering orifice via a pressure medium.Thus, the valve can exert its effect described above with regard to the first aspect in accordance with the invention in an inlet control or in an outlet control with regard to the control pressure chamber.

[0026] The control pressure chamber of the metering orifice can be supplied with control fluid of a specific metering volume to move the control spool from its closed position to the first flow position. Furthermore, the valve's displacement device can be assigned a displacement volume corresponding to the volume of control fluid displaced from the pressure chamber, which decreases in size during axial movement of the displacement device over its entire stroke. The displacement volume of the displacement device can be dimensioned such that it is not greater than, in other words, less than or equal to, the metering volume. Preferably, the displacement volume is dimensioned to be at least approximately equal to the metering volume.

[0027] According to a third aspect of the invention, a hydraulic arrangement is provided comprising a hydraulically actuated metering orifice, through which a hydraulic consumer can be supplied with hydraulic fluid via the adjustment of a control spool, and a valve for the throttled hydraulic actuation of the adjustment movement of the control spool of the metering orifice. The metering orifice has a closed position and at least one first flow position in which it releases an opening cross-section. The metering orifice has a housing with an interior and the hydraulically adjustable control spool arranged therein, which defines at least one control pressure chamber within the housing interior. The control pressure chamber is supplied with control hydraulic fluid with a predetermined metering volume in order to move the control spool from the closed position to the first flow position.The valve has a valve body with an axially extending interior space and a displacement device that is axially movable within this interior space along a stroke and separates a first and a second pressure chamber within the interior space. One pressure chamber, for example the first, can be connected to a control pressure medium source or sink. The other pressure chamber, for example the second, is connected to the control pressure chamber of the metering orifice. The displacement device has a throttling device, particularly for the throttled supply of the control pressure chamber, through which the first pressure chamber can be brought into contact with the second pressure chamber. Furthermore, a displacement volume is associated with the displacement device.This corresponds to the volume of control pressure fluid that is displaced during an axial movement of the displacement device over its entire stroke, particularly from the pressure chamber which decreases during the movement.

[0028] According to the invention, the displacement volume of the valve is dimensioned such that it is not greater than, i.e., less than or equal to, the metering volume. Preferably, the displacement volume is dimensioned to be approximately the same size as the metering volume. With such dimensioning, the control slide of the metering orifice, when one pressure chamber (for example, the first) is pressurized with control fluid, can be adjusted from the closed position, at least close to, preferably into, the first flow position, via an immediately initiated stroke movement of the displacement device. This occurs almost instantaneously with the stroke movement, i.e., without time delay and with a high displacement volume per unit of time. After this almost instantaneous stroke movement, control fluid flows through the throttling device into the other pressure chamber (for example, the second).This ensures that the control pressure chamber continues to be supplied with control pressure medium and that the control valve continues to be adjusted, but at a relatively lower adjustment speed due to the throttling by the throttle device.

[0029] In the use of a valve according to the first aspect in a hydraulic arrangement according to the second or third aspect of the invention, the control spool of the metering orifice can define a control pressure chamber within the housing interior and be pre-positioned in a closed position. This pre-positioning can be achieved by means of a control spool spring element. The pressure chamber of the valve, which decreases during a quasi-instantaneous movement of the displacement device caused by control pressure, can be in communication with the control pressure chamber via the pressure medium. In such an assembly, the regulated control pressure medium acts against the elastic force (tension) of the control spool spring element, thus achieving inlet control for the metering orifice.

[0030] In another use of a valve according to the first aspect in a hydraulic arrangement according to the second or third aspect of the invention, the metering orifice can be designed as a control spool valve. The control spool can separate a first and a second control pressure chamber within the housing interior and can be pre-positioned in a closed position between the first and second control pressure chambers. This pre-positioning can be achieved by means of a control spool spring element or by means of a pressure equilibrium. In one embodiment, a first valve with its second pressure chamber can be in pressure medium communication with the first control pressure chamber, and a second valve with its second pressure chamber can be in pressure medium communication with the second control pressure chamber.In an alternative embodiment, a first valve with its first pressure chamber can be in communication with the first control pressure chamber, and a second valve with its first pressure chamber can be in communication with the second control pressure chamber. In both embodiments, the valves act symmetrically with respect to the control spool, in one embodiment in an inlet configuration and in the other in an outlet configuration.

[0031] Embodiments of the invention are explained in more detail below with reference to schematic drawings. These show: Fig. 1A Schematic longitudinal sections of a valve according to the invention and a control slide valve controlled by it in combination, Fig. 1B a schematic longitudinal section of a valve according to the invention, Fig. 2A in functional representation a first embodiment of the throttling function of the displacement device of a valve according to the invention, Fig. 2B in functional representation a second embodiment of the throttling function of the displacement device of a valve according to the invention, Fig. 2C in functional representation a third embodiment of the throttling function of the displacement device of a valve according to the invention, Fig. 3. Schematically, the damping behavior of a conventional valve with a throttling function according to the one described in the Fig. 2A shown design, Fig. 4 schematically the damping behavior of a valve according to the invention, in which the throttling device according to the one shown in the Fig. 2A shown embodiment is arranged in a displacement device that is axially movable within the valve, Fig. 5 a longitudinal section of a first embodiment of a valve according to the invention, Fig. 6 schematically an interconnection according to the invention of a control slide valve with two valves, which control the control slide valve symmetrically with respect to the stroke movement of the control slide and each in inlet configuration, Fig. 7 schematically a further interconnection according to the invention of a control slide valve with two valves, which control the control slide valve symmetrically with respect to the stroke movement of the control slide and each in a sequential circuit, and Fig. 8 a longitudinal section of a second embodiment of a valve according to the invention.

[0032] With reference to the Fig. Sections 1 to 4 explain the basic structure of a valve 2 according to the invention and its mode of operation by way of example in conjunction with a metering orifice designed as a control slide valve. The valve 2 is described in the Fig. Figure 1A, showing a control slide valve 100 as an example of a metering orifice, comprises a housing 102 having a housing interior 104 and a slide axis 108, a control slide 106 arranged to be linearly displaceable in a longitudinal bore 148 of the housing interior 104 in the direction of the slide axis 108, and a control slide spring element 118. The control slide 106, by means of its slide pressure surface 112, delimits a control pressure chamber 110 in the housing interior 104 and is held in a closed position by means of the control slide spring element 118, in which it is in the Fig. As shown in Figure 1, the control valve spring element 118 is pre-positionable. The control valve spring element 118 is arranged in a sub-chamber of the control pressure chamber 104, located at the opposite end of the housing interior 104. An end stop 130 for the control valve 106 is also formed in this sub-chamber. A circumferential pump inlet groove 142, a circumferential consumer outlet groove 144, and a control notch 150 opening into the consumer outlet groove 144 are formed in the outer surface 140 of the control valve 106. The pump inlet groove 142 is associated with a pump pressure annular groove 135 formed in the cylindrical inner wall of the longitudinal bore 148, into which a pump inlet channel 134 opens, and the consumer outlet groove 144 is associated with a consumer pressure annular groove 137 formed in the inner wall, into which a consumer supply line 136 opens.In the locked position defined by the spring element 118, the pump inlet groove 142 is opposite the pump pressure ring groove 135, meaning that the pump pressure ring groove 135 is fully open, and the consumer pressure ring groove 137 is closed by a section of the outer shell surface 108. The control notch 150 extends from its opening into the consumer outlet groove 144 to its notch end 152 (in the . Fig. 1A to the right), which is axially spaced from the pump inlet groove 142 by a distance that defines the measuring stroke 122 of the control valve 106.

[0033] When the control pressure chamber 110 is supplied with control pressure medium via the valve 2 and the control pressure medium pressure at the slide pressure surface 112 increases, the control slide 106 moves axially from its closed position towards the partial chamber with the spring element 118 (in the Fig. 1A to the right) against the elastic force of the spring element 118. When the control valve 106 has overcome the metering stroke 122, the control notch 150 begins to move in front of the pump pressure ring groove 135 and simultaneously the consumer outlet groove 144 moves in front of the consumer pressure ring groove 137, thereby establishing a pressure medium connection from the pump pressure ring groove 135 through the control notch 150 into the consumer outlet groove 144 and further through the consumer pressure ring groove 137 into the consumer supply line 136, this pressure medium connection being controlled by the effective flow resistance of the control notch 150. Under the influence of the building-up control pressure medium pressure, the control valve 106 can move further (in the Fig. The control valve 106 moves (1A to the right) until its end opposite the valve pressure surface 112 abuts the end stop 130. In the position of the control valve 106 determined by the position of the end stop 130, it is axially displaced relative to its closed position by the distance called the metering stroke 126. In this position, the consumer outlet groove 144 is opposite the consumer pressure annular groove 137, and the control notch 150, with its entire longitudinal extent, is opposite the pump pressure annular groove 135, so that a pressure medium connection is established between the pump pressure line 134 and the consumer supply line 136, which is minimally throttled via the control notch 150. The distance that the control valve 106 travels from the beginning of its stroke movement until the control notch 150 begins to move in front of the pump pressure annular groove 135 is the metering stroke 122 of the control valve.The measuring stroke 122 of the control valve 106 is therefore the distance by which the control valve 106 must be moved from its closed position in order to create an opening cross-section for the pressure medium connection to be controlled (in . Fig. 1: to release from the pump pressure line 134 to the consumer supply line 136). The time required to overcome the metering stroke 122 when using a conventional valve is the response delay of the control spool 106.

[0034] Fig. Figure 1B shows an enlarged schematic longitudinal section of a valve 2, which is connected to the one in the Fig. The control slide valve 100 shown in 1A is in operative connection. The one in the Fig. 1B schematically, in the Fig. 5 in a first embodiment and in the Fig. The valves 2 shown in a second embodiment have the following features in common. The valve 2 comprises a valve housing 4, which has an interior space 6 and a longitudinal axis 8, and a displacement device 20, which is axially movably guided in the interior space 6 in the direction of the longitudinal axis 8 from a pre-positionable initial position along a stroke 16 with a predetermined stroke length and separates a first pressure chamber from a second pressure chamber 10, 12 in the interior space 6. The displacement device has a throttling device 40, via which the first pressure chamber 10 is in contact with the second pressure chamber 12, and which is designed such that, for at least one stroke direction of the displacement device 20 and over the entire stroke 16 of the displacement device 20, a pressure medium exchange between the first and the second pressure chambers 10 and 12 takes place exclusively via this single throttling device 40.

[0035] In the Fig. In the valve 2 shown schematically in Figure 1A, a throttle valve 30 is formed in the displacement device 20, wherein the first and second pressure chambers 10 and 12 for the control pressure medium are in pressure medium communication with each other exclusively via this throttle valve 30. The throttle valve 30 has at least one first throttle point 40, which is effective for a first pressure medium flow direction 18 directed from the first pressure chamber 10 through the first throttle point 40 into the second pressure chamber 12. The throttle valve 30 has a throttling effect (throttle function) that depends on the flow direction and is accordingly characterized by a first and second working port 30a and 30b, wherein the first working port 30a is in pressure medium communication with the first pressure chamber 10 and the second working port 30b is in pressure medium communication with the second pressure chamber 12. Embodiments of the throttle valve 30 are described below with reference to the Fig. 2A, Fig. 2B and Fig. 2C described in more detail.

[0036] Viewed from the outside, the valve 2 has a first and a second connection channel 2a, 2b, wherein the first connection channel 2a is connected to the first working port 30a through the first pressure chamber 10 and the second connection channel 2b is connected to the second working port 30b of the throttle valve 30 through the second pressure chamber 12. The first pressure medium flow direction 18 runs from the first connection channel 2a, through the first pressure chamber 10, via the first working port 30a, through the throttle valve 30 formed in the displacement device 20, via the second working port 30b, through the second pressure chamber 12 to the second connection channel 2b. In the Fig. In the working connection shown in 1A, the second pressure chamber 12 of the valve 2 is connected to the control pressure chamber 110 of the control slide valve 100 via a pressure medium connection.

[0037] The displacement device 20 is movably mounted in the interior 6 of the valve housing 4 from a pre-positionable initial position along a stroke 16 with a predetermined stroke length in the first pressure medium flow direction 18. A first and a second stop surface 54, 56 are formed in the interior 6 of the valve housing 4 to limit the axial movement of the displacement device 20. The first stop surface 54 is spaced from the second stop surface 56 along the longitudinal axis 8 by a predetermined distance 58. The maximum stroke 16 of the displacement device 20, limited by the first and second stop surfaces 54 and 56, is defined by the distance 58 between the stop surfaces 54 and 56 minus a piston length 26 of the displacement device 20 measured along the longitudinal axis 8.

[0038] The displacement device 20 can be pre-positioned in the interior 6 of the valve housing 4 to a starting position in which the volume of the first pressure chamber 10 is minimal. In this starting position, the end of the displacement device 20 facing the first pressure chamber 10 (the first connecting channel 2a) rests against the first stop surface 54 and is pre-positioned against this stop surface 54. The pre-positioning of the displacement device 20 in the starting position is achieved by means of a first spring element 14. The first spring element 14 is arranged in the second pressure chamber 12, in particular with slight pre-tension, and is supported at one end against the inner wall of the second pressure chamber 12 and at its other end against the pressure surface of the displacement device 20 that delimits the second pressure chamber 12. The pre-tension and force exerted by the first spring element 14 on the displacement device 20 are relatively small.The first spring element 14 serves only to pre-position the displacement device 20 in its initial position when the valve 2 is depressurized and, upon the build-up of control fluid in the first pressure chamber 10 (i.e., when the first pressure chamber 10 is filled with control fluid), to yield almost without resistance and thus allow almost instantaneous movement of the displacement device 20 in the direction of the building-up control fluid pressure (i.e., in the first flow direction 18) by the predetermined stroke length 16 (defined by the distance between the stop surfaces 54, 56). This movement of the displacement device 20 ends when the end of the displacement device 20 facing the second pressure chamber 12 (the second connection channel 2b) abuts the second stop surface 56.

[0039] The quantity of control fluid displaced almost instantaneously from the second pressure chamber 12 of the valve 2 and into the control pressure chamber 110 of the control spool valve 100 during this quasi-instantaneous movement of the displacement device 20 acts directly on the control pressure surface 112 of the control spool 106 and sets it in motion almost instantaneously. According to the invention, the geometric (structural) dimensions of the displacement device 20 are adapted to the geometric (structural) dimensions of the control spool valve 100 such that the volume of control fluid displaced from the second pressure chamber 12 by the quasi-instantaneous movement of the displacement device 20, i.e., the stroke volume of the displacement device 20, corresponds at least approximately to the metering volume V. T (compare Fig. 3 and 4) of the control valve 106. Here, the metering volume V is used. TThe quantity (volume) of control fluid is meant to be supplied to the control pressure chamber 110 so that the control valve 106 just overcomes its metering stroke 122. This is achieved by adjusting the stroke volume of the displacement device 20 to the metering volume V. T The control valve 106 ensures that the amount of pressure medium displaced almost instantaneously from the second pressure chamber 12 of the valve 2 into the control pressure chamber 110 of the control valve 100 moves the control valve 106 almost instantaneously by its metering stroke 122, so that no response delay is noticeable.

[0040] Specifically, the control slide valve 100, which is actuated by valve 2, is controlled by a metering volume V. Tcharacterized by the product of the valve pressure area 112 and the metering stroke 122 of the control valve 106. Similarly, the valve 2 is characterized by the stroke volume of the displacement device 20, which is the product of the second pressure area 24, which delimits the second pressure chamber 12, and the stroke 16 of the displacement device 20. According to the invention, the product of the second pressure area 24 and the stroke 16, i.e., the stroke volume of the displacement device 20, corresponds, at least approximately, to the product of the valve pressure area 112 and the metering stroke 122 of the control valve 106, i.e., the metering volume V. T .

[0041] After the quasi-instantaneous movement of the displacement device 20 and the associated overcoming of the measuring stroke 122 of the control spool 106, the control pressure medium flows through the throttling function valve 30 formed in the displacement device 20 under the influence of the control pressure which continues to build up in the first pressure chamber 10, so that only after overcoming the measuring stroke 122 of the control spool 106 does its desired throttling effect, acting in the first flow direction 18, begin.

[0042] When the control pressure in the first pressure chamber 10 decreases, the displacement device 20 moves almost instantaneously in the opposite direction, that is, in the direction of flow opposite to the first flow direction 18, until it returns to its initial position, in which its end facing the first pressure chamber 10 abuts the first stop surface 54. Then, the throttle valve 30 is subjected to a flow of control fluid in the opposite direction, that is, from the second pressure chamber 12 towards the first pressure chamber 10, and an effect of the throttle valve 30 corresponding to this flow direction is initiated, which depends on its functional design. Possible functional designs of the throttle valve 30 are described in the Fig. 2A, Fig. 2B and Fig. 2C shown.

[0043] In the Fig. In the embodiment shown in 2A, the throttle function valve 30 is designed as a throttle check valve and comprises two flow paths arranged parallel to each other between the first and second working ports 30a and 30b. In the first (in the Fig. In the passage shown on the left (2A), a first check valve 41 opening in the first flow direction 18 and a (first) throttle point 40 arranged in series with it are formed. In the second (in the Fig. In the passage shown in Figure 2A (right), a second check valve 43 is formed that opens in the opposite direction of flow to the first flow direction 18. Thus, the first passage with the first throttling point 40 acts for the first flow direction 18, while the second passage has essentially no throttling effect for the opposite flow direction.

[0044] In the Fig. In the embodiment shown in Figure 2B, the throttle function valve 30 is designed as a throttle valve with two throttle points 40, 42 that act differently in different flow directions and comprises two flow paths arranged parallel to each other between the first and second working ports 30a and 30b. In the first (in the Fig. In the passage shown on the left (2B), a first check valve 41 opening in the first flow direction 18 and a first throttle point 40 arranged in series with it are formed. In the second (in the Fig. In the passage shown in Figure 2B (right), a second check valve 43, acting in the opposite direction to the first flow direction 18, and a second throttle point 42 arranged in series with it are formed. Thus, the first passage with the first throttle point 40 acts for the first flow direction 18, and the second passage with the second throttle point 42 acts for the opposite flow direction. Depending on the design, the second throttle point 42 can have a stronger or weaker throttling effect than the first throttle point 40.

[0045] In the Fig. In the embodiment shown in Figure 2C, the throttle function valve 30 is simply designed as a throttle valve with a throttling point 40 formed between the first and second working ports 30a and 30b. This throttling point 40 exerts essentially the same throttling effect for the first flow direction 18 and the opposite flow direction.

[0046] The Fig. Figure 3 illustrates the damping behavior of a conventional valve in the design of the Fig. 2A in conjunction with a control slide valve 100 in the case where the throttle function valve is stationary, i.e., not linearly movable, within the valve. Specifically, the Fig. 3. The damping D (throttling effect) of the control slide valve 100 caused by the conventional valve as a function of the control fluid volume V for one control cycle. Here, control fluid volume V refers to the quantity of control fluid, expressed as volume, that is supplied to or discharged from the control pressure chamber. The control cycle comprises a first sub-cycle with a build-up of the control fluid pressure (and corresponding supply of control fluid to the control pressure chamber, i.e., an increase in the control fluid volume V) and a subsequent second sub-cycle with a decrease in the control fluid pressure (and corresponding discharge of control fluid from the control pressure chamber, i.e., a decrease in the control fluid volume).

[0047] In the first sub-cycle, the fluid in the first passage of the throttle check valve is removed from the Fig. The throttle point 40, arranged in 2A, is immediately supplied with control pressure fluid upon the onset of the control pressure build-up and exerts its throttling effect continuously during the first partial cycle. This is in the Fig. 3 schematically as constant first damping D Q The control valve moves relatively slowly from its closed position through its metering stroke (corresponding to its metering volume V) under the influence of the control pressure medium flowing into the control pressure chamber (i.e., with increasing control pressure medium volume V) and through the throttling effect of the throttle point 40. T ) up to its full stroke (corresponding to its full stroke volume V) maxIn the subsequent second sub-cycle, when the control pressure reduction begins, the flow direction in the throttle check valve reverses. The check valve 41 closes the first passage, so that the throttle point 40 has no throttling effect. Simultaneously, the check valve 43 located in the second passage opens and releases the second passage, so that no throttling effect is exerted during the second sub-cycle while the control pressure is being reduced. This is described in the Fig. 3 represented as constant, unthrottled damping D0.

[0048] In contrast, the Fig. 4, in analogous representation as the Fig. 3, the damping behavior of a valve 2 according to the invention with a throttle function valve 30 formed in the linearly movable displacement device 20 in the embodiment of the Fig. 2A in conjunction with a control slide valve 100.

[0049] In the first sub-cycle, the linear, quasi-instantaneous movement of the displacement device 20 from its initial position, as described above, and the resulting quasi-instantaneous supply of the control pressure chamber with control pressure medium begin immediately upon the onset of the control pressure build-up, and continue until the linear movement of the displacement device 20 is completed or the metering stroke 122 or the metering volume V is reached. T the resistance of the control slide 106 is overcome. During this quasi-instantaneous movement of the displacement device 20, the throttle function valve 30 unfolds from the Fig. 2A has no throttling effect. This is in the Fig. 4 as constant, unthrottled damping D0 until the measuring volume V is reached T illustrated. With a further increase in the control medium pressure, that is, with a further increase in the control medium volume V, until the full stroke volume V is reached. maxThe throttle point 40 of the throttle function valve 30, located in the first flow path, is subjected to a flow of control pressure medium and exerts its throttling effect. This is in the Fig. 4 schematically as in the area of ​​the metering volume V T up to the full stroke volume V max effective first damping D QAs shown. In the subsequent second sub-cycle, when the control pressure reduction begins, the flow direction in valve 2 reverses. The displacement device 20 moves back to its initial position in the opposite direction, then the first check valve 41, located in the first flow path, closes, so that the first throttling point 40 has no throttling effect. Simultaneously, the check valve 43, located in the second flow path, opens and releases the second flow path. Consequently, no throttling effect is exerted during the control pressure reduction in the second sub-cycle. This is shown in the Fig. 4 represents constant, unthrottled damping D0 throughout the entire swept area of ​​the control pressure medium volume V.

[0050] In the Fig. In the first embodiment shown in section 5, the valve 2 has the features of the one schematically shown in the Fig. Valve 2 shown in 1B, which is shown above with reference to the Fig. 1B are described. Specifically, this includes the Fig. 5 Valve 2 shown, a valve housing 4 surrounding an interior 6 and having a longitudinal axis 8, a displacement device 20 which is linearly movable in the interior 6 from a pre-positionable initial position in which the volume of the first pressure chamber 10 is minimal, in the direction of the longitudinal axis 8 along a stroke 16 with a predetermined stroke length in a first pressure medium flow direction 18 and separates a first pressure chamber 10 from a second pressure chamber 12 in the interior 6, a first and a second stop surface 54 and 56 which are formed in the interior 6 at a predetermined distance 58 from each other along the longitudinal axis 8, wherein the stroke 16 is defined by this distance 58 minus a piston length 26 of the displacement device 20 measured along the longitudinal axis, a first spring element 14 which is configured to hold the displacement device 20 in its initial position defined by the first stop surface 54 to pre-position,and a throttle valve 30 formed in the displacement device 20, which has a first throttle point 40 that is effective for the first pressure medium flow direction 18 directed from the first pressure chamber 10 through the first throttle point 40 into the second pressure chamber 12, and is essentially not throttling for the opposite pressure medium flow direction. The first pressure chamber 10 and the second pressure chamber 12 are essentially only connected to each other via the throttle valve 30.

[0051] As in the Fig. As shown in Figure 5, the displacement device 20 has a piston length 26 measured in the longitudinal direction 8 and comprises a piston interior 28. The throttle function valve 30 is located therein as a throttle check valve, i.e., with the [unclear] Fig. The functional structure shown in Figure 2A is formed. The throttle function valve 30 comprises a valve seat 32 formed in the displacement device 20, a valve body 34, a second spring element 44, and a sleeve 48. The valve body 34 is movably guided in the piston interior 28 in the direction of the longitudinal axis 8 and comprises a substantially cylindrical wall surrounding a valve body interior, and a valve cone 36 attached to the wall, which interacts with the valve seat 32 and in which a longitudinal groove 38 is formed. The wall comprises a thicker cylindrical section that abuts a cylindrical inner wall of the piston interior 28 and is thus linearly axially displaceable along this inner wall, and a thinner cylindrical section that adjoins the valve cone 36, which is penetrated by a transverse bore 35 and which defines a cylindrical annular space between itself and the inner wall of the piston interior 28.

[0052] The second spring element 44 is arranged in the piston interior 28 and is designed to bias the valve body 34 against the valve seat 32 in the first pressure medium flow direction 18. The sleeve 48 is screwed into the piston interior 28 in the first pressure surface 22 of the displacement device 20, which faces the first pressure chamber 10, and is penetrated longitudinally by a channel. This channel communicates with the pressure medium interior of the valve body. The sleeve 48 has an external thread 50, which is screwed into a complementary internal thread 52 formed in the inner wall of the piston interior 28. The second spring element 44 is supported with its one (in the Fig. 5 left) end on a first support surface 44a, which is formed on the side of the sleeve 48 facing the valve body 34, and with its other (in the Fig. 5 right end on a second support surface 44b, which is formed on the side of the valve body 34 facing the sleeve 48. The second spring element 44 is compressed between the sleeve 48 and the valve body 34 and arranged under preload, so that the valve body 34 is preloaded in the direction towards and into the valve seat 32 and seals against the valve seat 32 in the unpressurized state, except in the area of ​​the longitudinal groove 38. The throttling point 40 of the throttle check valve (throttle function valve 30) is formed in the shape of the longitudinal groove 38 formed in the valve cone 36.

[0053] To install the throttle function valve 30 into the displacement device 20, the valve body 34 with the valve cone 36 leading is first inserted into the piston interior 28 (specifically in the Fig. The valve cone 36 is inserted (5 from left to right) until it rests against the valve seat 32. Then the second spring element 44 is inserted. Finally, the sleeve 48 is inserted and screwed into the complementary internal thread 52 in the inner wall of the piston interior 28 via its external thread 50.

[0054] When the displacer device 20 is subjected to a flow of control fluid in the first flow direction 18, the valve cone 36 is seated in the valve seat 32, with the control fluid flowing from the first pressure chamber 10 through the longitudinal groove 38, which acts as a throttle point 40, into the second pressure chamber 12. When the displacer device 20 is subjected to a flow of control fluid in the opposite direction to the first flow direction 18, the valve body 34 is pressed against the elastic preload force of the second spring element 44, whereby the valve cone 36 disengages from the valve seat 32 and opens an annular gap between the valve seat 32 and the valve cone 36.The control pressure medium flows from the second pressure chamber 12 through this annular gap, into the cylindrical annular space, through the transverse bore 35 into the valve body interior of the valve body 34, and further through the channel passing through the sleeve 48 into the first pressure chamber 10.

[0055] The valve housing 4 comprises a first housing part 62 and a separate second housing part 72, which is directly screwed to the first housing part 62. The first housing part 62 surrounds the first connection channel 2a, the first pressure chamber 10, the displacement device 20, and a section of the second pressure chamber 12. At the end of this section, an internal thread 64 is formed in the inner wall of the first housing part 62. The second housing part 72 surrounds the second connection channel 2b and the remaining section of the second pressure chamber 12. In the region of this section, an external thread 68, complementary to the internal thread 64, is formed in the outer wall of the second housing part 72. This external thread 68 engages with the internal thread 64, and the second housing part 72 is screwed to the first housing part 62 via the engaging threads 64 and 68.An annular shoulder 70 is formed on the outer wall of the second housing part 72, in whose annular end face a groove 72 is formed. A first sealing ring 74 is inserted in this groove, which, when the first and second housing parts 62, 72 are screwed together, is pressed against an annular end face of the first housing part 62 and creates a pressure seal between the first and the second housing parts 62 and 72.

[0056] The first housing part 62 has a coaxial bore 60 in which the displacement device 20 is guided for axial displacement. At the distal end of this bore 60, the first stop surface 54 is formed, against which the displacement device 20 can be pre-positioned by means of the first spring element 14 and against which the sleeve-side end of the displacement device 20 rests in its initial position for the quasi-instantaneous movement. At the axial end of the external thread 68, the second housing part 72 has an annular end face that forms the second stop surface 56, which serves to limit the stroke length 16 for the displacement device 20. In the assembled state of the valve housing 4, the second stop surface 56 is arranged axially offset from the first stop surface 54 by a distance 58. As shown in the Fig. As can be seen in Figure 5, the stroke length 16 is determined by the axial distance 58 between the first and second stop surfaces 54 and 56, minus the piston length 26 of the displacement device 20.

[0057] The first spring element 14 is arranged in the second pressure chamber 12. It is supported with one (in the Fig. 5 left) end on a first support surface 14a, which is formed in the second pressure surface 24 bounding the second pressure chamber 12, and its other (in the Fig. 5 right) end at a second support surface 14b, which is designed as an annular shoulder in the second housing part 72.

[0058] On the cylindrical wall-shaped end section of the first housing part 62, which surrounds the first connection channel 2a, a first connection thread 80 is provided (in the Fig. 5 (shown as an example external thread). Furthermore, an annular shoulder with a circumferential groove is formed there, in which a second sealing ring 84 is inserted. The first connection thread 80 serves to connect a hydraulic hose or hydraulic line, or to connect (screw on) the valve 2 to a housing wall of another component, in which case the second sealing ring 84 creates a seal against the housing wall. For analogous purposes, a second connection thread 82 is provided on the cylindrical end section of the second housing part 72, which surrounds the second connection channel 2b (in the Fig. (5 shown as an example of an external thread). The connection threads 80 and 82 can be designed as internal or external threads, depending on the connection requirements. They allow the valve 2 to be installed in a hydraulic hose or hydraulic line.

[0059] In contrast to the one in the Fig. The combination of a valve 2 with a control slide valve 100 shown in Figure 1A is described in the Fig. 6 and Fig. In the 7 combinations shown, the control slide valve 100 is modified and each is connected to two valves 2, 2'. In the combinations shown in the Fig. 6 and Fig. In the seven shown combinations, the control slide valve 100 includes a first control pressure chamber 110 and a second control pressure chamber 114, which are formed in the axially opposite end sections of the control slide valve 100 and which are separated by a control slide 106. The control slide 106 has a first control pressure surface 112 at one end, which delimits the first control pressure chamber 110, and a second control pressure surface 116 at its opposite end, which also delimits the first control pressure chamber 110. Therefore, the control slide 106 can be selectively controlled by applying control pressure to the first control pressure chamber 110 in a first longitudinal direction (in the Fig. 8 from left to right) or by applying control pressure to the second control pressure chamber 114 in an opposite longitudinal direction (in the Fig. 8 from right to left). When the first and second control pressure chambers 110 and 114 are pressurized with the same control pressure, the control valve 106 is pressure-centered in its closed position. The outer surface 140 of the control valve 106 features a circumferential pump inlet groove 142, a circumferential first consumer outlet groove 144, a circumferential second consumer outlet groove 146, a first control notch 150 opening into the first consumer outlet groove 144 with a notch end 152, and a second control notch 154 opening into the second consumer outlet groove 146 with a notch end 156.

[0060] In the closed position of the control valve 106, the pump inlet groove 142 is opposite a pump pressure annular groove 135 formed in the inner wall of the bore 148, into which a pump pressure line 134 opens. If the first control pressure chamber 110 is now supplied with control pressure medium, the control valve 106 is moved from its closed position in the direction of the second control pressure chamber 114. In doing so, the first control notch 150 approaches the pump pressure annular groove 135 until a first measuring stroke 122 associated with the first notch end 152 is overcome and a pressure medium connection is established by the first control notch 150 from the pump pressure line 134 through the first consumer outlet groove 144 into a first consumer supply line 136. In the second control pressure chamber 114 a first end stop 130 is formed, which limits the maximum stroke of the control slide 106 in this (with respect to the locking position) first direction of displacement.

[0061] Conversely, if the second control pressure chamber 114 is supplied with control fluid, the control valve 106 is displaced from its closed position in the direction towards the first control pressure chamber 110. In doing so, the second control notch 154 approaches the pump pressure ring groove 135 until a second metering stroke 124, associated with the second notch end 156, is overcome, and a pressure fluid connection is established via the second control notch 154 from the pump pressure line 134 through the second consumer outlet groove 146 into a second consumer supply line 138. A second end stop 132 is formed in the first control pressure chamber 110, which limits the maximum stroke of the control valve 106 in this second direction of displacement (relative to the closed position).

[0062] In the Fig. In the circuit shown in Figure 6, a first valve 2 is connected to the first control pressure chamber 110 such that its second pressure chamber 12 is in control pressure medium communication with the first control pressure chamber 110, and that the first control pressure chamber 110 can be supplied with control pressure medium via the first valve 2. Similarly, a second valve 2' is connected to the second control pressure chamber 114 such that its second pressure chamber 12' is in control pressure medium communication with the second control pressure chamber 114, and that the second control pressure chamber 114 can be supplied with control pressure medium via the second valve 2'.

[0063] To control the displacement of the control slide 106 in the first displacement direction (in the Fig. (6 from left to right) the first control pressure chamber 110 is supplied with control pressure medium via the first valve 2, and simultaneously control pressure medium from the second control pressure chamber 114 is discharged via the second valve 2'. The first valve 2 is supplied with control pressure medium in its first flow direction 18, in which the quasi-instantaneous movement of its displacement device 20 according to the invention is effective, and the second valve 2' is supplied with control pressure medium in the flow direction opposite to its first flow direction 18. Conversely, to control the displacement of the control spool 106 in the second displacement direction (in the Fig. (6 from right to left) the second control pressure chamber 114 is supplied with control pressure medium via the second valve 2' and simultaneously control pressure medium from the first control pressure chamber 110 is discharged via the first valve 2. The second valve 2' is subjected to the control pressure medium flowing through it in its first flow direction 18, in which the quasi-instantaneous mobility of its displacement device 20 according to the invention is effective, and the first valve 2 is subjected to the control pressure medium flowing through it in the opposite flow direction to its first flow direction 18. In the Fig. In the circuit shown in section 6, the valve supplying each control pressure chamber is operated in so-called inlet control.

[0064] During the Fig. In the circuit shown in Figure 7, a first valve 2 is connected to the first control pressure chamber 110 such that its first pressure chamber 12 is in control pressure medium communication with the first control pressure chamber 110, and that the first control pressure chamber 110 can be supplied with control pressure medium via the first valve 2. Similarly, a second valve 2' is connected to the second control pressure chamber 114 such that its second pressure chamber 12' is in control pressure medium communication with the second control pressure chamber 114, and that the second control pressure chamber 114 can be supplied with control pressure medium via the second valve 2'. The control functionality of the [connection shown in the] Fig. The interconnection shown in section 7 corresponds to the one in the Fig. 6 shown interconnection, except that the valve supplying each control pressure chamber is operated in so-called sequence control.

[0065] The one in Fig. Figure 8, the second embodiment of a valve 2 according to the invention, has a structure that is fundamentally and functionally comparable to that shown in Figure 8. Fig. The first embodiment shown in Figure 5 differs, however, in the design and configuration of the valve housing 4 and the resulting connection and / or installation options for the valve 2. In the second embodiment, the valve housing 4 comprises a substantially cup-shaped first housing part 86, a substantially cup-shaped second housing part 96, and a sleeve part 90 arranged axially between these, via which the first and second housing parts 86 and 96 are indirectly screwed together.

[0066] As in the Fig. The first embodiment shown in section 5 contains in the Fig. In the second embodiment shown in Figure 8, the first housing part 86 comprises the first pressure chamber and the displacement device 20, which is displaceable in the longitudinal direction 8. The displacement device 20 includes a throttle check valve in the configuration of the throttle function valve 30. Fig. 2A functional structure shown and essentially the one in the Fig. 5 arranged in the constructive structure shown.

[0067] The sleeve part 90 has a first external thread 92 at its end facing the first housing part 86 and a second external thread 94 at its end facing the second housing part 96. The first housing part 86 has an internal thread 88 at its end facing the sleeve part 90, which is complementary to the first external thread 92 and into which the first external thread 92 can be screwed. The second housing part 96 has a cylindrical inner wall in which an internal thread 98 is formed, which is complementary to the second external thread 94 and into which the second external thread 94 can be screwed. The sleeve part 90 can pass through an opening in a housing wall of another component as shown in the Fig.Figure 8 shows the first housing part 86 being screwed onto an interior space and the second housing part 96 being screwed onto an exterior space of the other component. The first end face 76, containing the first connection channel 2a, can serve as a stop surface (end stop) for a slide pressure surface 112 of a control slide 106. However, the sleeve part 90, and thus the valve 2 according to the second embodiment, can also be mounted in the opposite installation direction on a housing wall of another component, with the first housing part 86 being screwed onto an exterior space and the second housing part 96 being screwed onto an interior space of the other component. Reference symbol list: 2 valve 2a first connection channel 2b second connection channel 4 valve housings 6 Interior 8 Longitudinal direction 10 first printing room 12 second printing room 14 first spring element 14a first support surface 14b second support surface 16 Hub travel 18 First direction of pressure medium flow 20 displacement device 22 first printing area 24 second printing area 26 piston length 28 Piston interior 30 Throttle function valve 30a first working connection 30b second working connection 32 Valve seat 34 Valve bodies 35 Cross bore 36 valve cones 38 Longitudinal notch 40 first throttle point 41 first check valve 42 second throttle point 43 second check valve 44 second spring element 44a first support surface 44b second support surface 46 Outer shell area 48 Sleeve 50 external threads 52 internal threads 54 first stop surface 56 second stop surface 58 distance 60 bore 62 first housing part 64 internal threads 66 second housing part 68 external threads 70 Ring shoulder 72 Nut 74 first sealing ring 76 first front surface 78 second front face 80 first connection thread 82 second connection thread 84 second sealing ring 86 first housing part 88 internal threads 90 sleeve part 92 first external thread 94 second external thread 96 second housing part 98 internal threads 99 Sealing ring 100 Metering orifice, control slide valve 102 cases 104 Case interior 106 control valves 108 Slider axle 110 first control pressure chamber 112 first slide pressure surface 114 second control pressure chamber 116 second slide pressure surface 118 Control valve spring element 120 Locking position 122 first measuring stroke 124 second measuring stroke 126 first full metering stroke 128 second full metering stroke 130 first end stop 132 second end stop 134 Pump pressure line 135 Pump pressure ring groove 136 first consumer supply line 137 first consumer pressure ring groove 138 second consumer supply 139 second consumer pressure ring groove 140 outer shell area 142 Pump inlet groove 144 first consumer flow 146 second consumer drainage groove 148 bore 150 first tax notch 152 Notch end 154 second tax notch 156 notch end D damping D Q first damping, unrestricted damping V Control pressure medium volume V T Metering volume V max Full stroke volume

Claims

[1] Hydraulic arrangement with a hydraulically adjustable metering orifice (100) through which a hydraulic consumer can be supplied with pressure medium, which has a closed position and a first flow position in which it releases an opening cross-section, and which has a housing (102) with a housing interior (104) and therein a hydraulically adjustable control spool (106) which delimits a control pressure chamber (110, 114) in the housing interior (104), and with a valve (2) with a valve housing (4) which has an axially extending interior (6), characterized byA displacement device (20) which is axially movable in the interior (6) along a stroke (16), which divides a first and a second pressure chamber (10, 12) in the interior (6) and which has a throttling device (40) via which the first pressure chamber (10) can be brought into contact with the second pressure chamber (12) and which is designed such that for at least one stroke direction of the displacement device (20) and over the entire stroke (16) of the displacement device (20) a pressure medium exchange between the first and the second pressure chamber (10, 12) takes place exclusively via the one throttling device (40), wherein the control pressure chamber (110, 114) is connected to the second pressure chamber (12), wherein the control pressure chamber (110, 114) has a metering volume (V T) to be supplied in order to move the metering orifice (100) from the closed position to the first flow position, wherein the displacement device (20) has a displacement volume associated with the stroke (16) which is dimensioned such that it is not larger than the metering volume (V T ) the measuring aperture (100). [2] Hydraulic arrangement according to claim 1, comprising a first spring element (14) by which the displacement device (20) is pre-positioned in a starting position in which the volume of one of the pressure chambers (10) is minimal. [3] Hydraulic arrangement according to one of the preceding claims, wherein the one throttling device (40) is effective in a pressure medium flow path directed from the first pressure chamber (10) to the second pressure chamber (12). [4] Hydraulic arrangement according to one of the preceding claims, wherein the displacement device (20) has a seat valve (41) which is arranged fluidically in series with the one throttling device (40). [5] Hydraulic arrangement according to claim 4, wherein the displacement device (20) has a further seat valve (43) which is arranged fluidically parallel with the one throttling device (40), wherein the opening directions and closing directions of the seat valves (41, 43) are opposite to each other. [6] Hydraulic arrangement according to one of the preceding claims, wherein the displacement device (20) has a further throttling device (42) which is effective in a pressure medium flow path which is directed opposite to the pressure medium flow path in which the one throttling device (40) is effective. [7] Hydraulic arrangement according to one of claims 4 to 6, wherein the seat valve (41, 43) is formed in an axially extending interior space (28) of the displacement device (20) via a valve seat (32) and a valve body (34) that is axially movable in the interior space (28) and that can interact with the valve seat (32), and wherein a throttling device (40, 42) arranged fluidically in series with the seat valve (41, 43) is formed via a notch (38) or a flattening on the valve body (34) or on the valve seat (32). [8] Hydraulic arrangement according to claim 7, with a second spring element (44) by which the valve body (34) can be preloaded against the valve seat (32). [9] Hydraulic arrangement according to one of the preceding claims, wherein the displacement device (20) has an outer shell surface and the valve housing (4) has a complementary inner shell surface, the tolerance position of which is designed such that, during a stroke of the displacement device (20), a pressure medium exchange between the first and the second pressure chamber (10, 12) is prevented via a gap between the outer shell surface and the inner shell surface. [10] Hydraulic arrangement according to one of the preceding claims, wherein the valve housing (4) has a first and a second housing part (62, 72; 86, 96), wherein the first housing part (62; 86) is screwed directly or indirectly to the second housing part (72; 96). [11] Hydraulic arrangement according to one of the preceding claims, wherein an end stop for the control slide (106) is formed over an outer surface section of the valve housing (4). [12] Hydraulic arrangement according to any one of the preceding claims, characterized by , that the metering orifice is designed as a control slide valve (100), wherein the control slide (106) divides a first and a second control pressure chamber (110, 114) in the housing interior (104) and can be pre-positioned in a blocking position between these (110, 114), and that either a first valve (2) with its second pressure chamber (12) is in pressure medium communication with the first control pressure chamber (110) and a second valve (2') with its second pressure chamber (12') is in pressure medium communication with the second control pressure chamber (114), or that a first valve (2) with its first pressure chamber (10) is in pressure medium communication with the first control pressure chamber (110) and a second valve (2') with its first pressure chamber (10') is in pressure medium communication with the second control pressure chamber (114).

Images