Valve disc with integrated quick-release coupling device

Abstract

Valve assembly (10) comprising a one-piece first housing part (30) with a first and a second flat contact surface (31; 32), wherein the first and the second contact surfaces (31; 32) are arranged parallel to each other at a distance from each other by a disk width (33), pointing away from each other and oriented perpendicular to a transverse axis (12), wherein a main valve (70) is linearly movably received in the first housing part (30) parallel to a longitudinal axis (11), the longitudinal axis (11) being oriented perpendicular to the transverse axis (12), wherein the first housing part (30) has two first, two second, one third and one fourth connection point (21; 22; 23; 24), wherein the first to fourth connection points (21; 22; 23; 24) are fluidically connectable to each other depending on the position of the main valve (70), wherein the first and the second connection points (21; 22) are each two mouth openings (35;36) are formed, which are arranged parallel to the transverse axis (12) in alignment in the first and second contact surfaces (31; 32), wherein a quick-coupling device (140) is received in the first housing part (30) at the third and fourth connection points (23; 24), wherein the quick-coupling devices (140) each have a separate coupling bushing (141) which is movable parallel to a vertical axis (13), wherein the vertical axis (13) is aligned perpendicular to the longitudinal and transverse axes (11; 12), wherein the coupling bushings (141) are located between the first and second contact surfaces (31;32) are arranged, characterized in that the first housing part (30) has at least one actuation chamber (37) extending parallel to the longitudinal axis (11), in which at least one actuation axis (143) is rotatably received, wherein the at least one actuation axis (143) is each provided with at least one actuation cam (144), wherein both coupling bushings (141) can be brought into contact with an associated actuation cam (144), wherein the at least one actuation chamber (37) is arranged off-center between the first and the second contact surfaces (31; 32) in the direction of the transverse axis (12) to the first contact surface (31).

Description

The invention relates to a valve assembly according to the preamble of claim 1. The datasheet "Load-sensing control block in sandwich plate design SB33-EHS1" from Bosch Rexroth AG (order number RE66136; edition 05 / 2013) describes a valve assembly, also referred to as a valve disc. This valve assembly comprises a one-piece first housing part with a first and a second contact surface. The first and second contact surfaces are arranged parallel to each other by one disc width, pointing away from each other and perpendicular to a transverse axis. Several valve assemblies can be connected at these contact surfaces to form a valve block. The first housing part is typically made of cast iron to withstand the high internal fluid pressures. A main spool is linearly mounted within the first housing part, moving parallel to a longitudinal axis that is perpendicular to the transverse axis.The main valve, together with the first housing section, forms several orifices whose free cross-sectional area can be adjusted by moving the main valve. The first housing section has two first, two second, one third, and one fourth connection point, with the first through fourth connection points being fluidically interconnected depending on the position of the main valve. The corresponding fluid flows are directed through the aforementioned adjustable orifices. The third and fourth connection points are provided for connecting an actuator, for example, a hydraulic cylinder. The first and second connection points serve for the supply and discharge of pressurized fluid, respectively, with the pressurized fluid preferably being hydraulic oil. The first and second connection points are each formed by two outlet openings arranged parallel to the transverse axis and aligned in the first and second contact surfaces.All valve assemblies of a valve block together form a continuous pump or tank channel, which is connected to the pump or tank only once. Furthermore, US Patent 6 016 835 A discloses a quick-coupling device which has a linearly movable coupling bushing which can be moved by an actuating cam. A valve disc for use with compressed air is known from US 5,586,570 A. A quick-release coupling is provided at both the third and fourth connection points. Since significantly lower pressures are used in pneumatics than in hydraulics, the release mechanism using an actuating cam shown in US 6,016,835 A is unnecessary. It is accepted that the corresponding pneumatic hose will spring away from the quick-release coupling if it is released without holding the hose. In hydraulics, this behavior would pose a significant risk to the user. Another hydraulic valve disc is known from US 2005 / 0 211 320 A1. WO 2009 / 095 038 A1 and DE 698 18 177 T2 describe further pneumatic valve discs. An advantage of the present invention is that the valve assembly is particularly compact, especially with a very narrow disc width. The dimensions perpendicular to the transverse axis are essentially the same as those of previously known valve assemblies. Furthermore, the flow paths between the various individual components (load-holding valves, pressure balance, etc.) are particularly short, allowing the corresponding fluid channels to be designed with a large cross-sectional area without difficulty. The quick-coupling device can be equipped with the release mechanism commonly used in hydraulics. According to the independent claim, it is proposed that a quick-coupling device is provided at the third and fourth connection points in the first housing part, wherein the quick-coupling devices each have a separate coupling bushing that is movable parallel to a vertical axis, the vertical axis being oriented perpendicular to the longitudinal and transverse axes, and wherein the coupling bushings are arranged between the first and second contact surfaces. Preferably, the two first and the two second connection points are directly fluidically connected to each other. Several valve assemblies are preferably assembled to form a valve block, with their contact surfaces abutting each other in such a way that corresponding first and second connection points overlap. Preferably, the coupling bushings are arranged within the outer outline of the first and / or the second contact surface when viewed in the direction of the transverse axes.Preferably, the coupling bushings are arranged completely between the first and the second contact surface. It is provided that the first housing part has at least one actuation chamber extending parallel to the longitudinal axis, in which at least one actuation shaft is rotatably mounted, wherein each of the at least one actuation shaft is provided with at least one actuation cam, and wherein both coupling bushings can be brought into contact with an associated actuation cam, and wherein the at least one actuation chamber is arranged eccentrically between the first and second contact surfaces in the direction of the transverse axis to the first contact surface. The actuation cams and the actuation shaft serve to actuate the two quick-release coupling devices. With the proposed arrangement of the actuation chamber, the disc width can be made particularly small. The dependent claims specify advantageous further developments and improvements of the invention. The actuation area can extend from a side surface of the first housing part parallel to the longitudinal axis, passing by both coupling bushings. This means that only one actuation area is required for both quick-coupling devices. Furthermore, both quick-coupling devices can be actuated with a single actuating lever, which is preferably located on the outside of the aforementioned side surface. It can be designed that the main slide valve is positioned off-center between the first and second contact surfaces in the direction of the transverse axis towards the second contact surface. This means that the main slide valve is positioned off-center in the opposite direction to the operating area. This results in a particularly narrow disc width. The coupling bushings can be arranged centrally or, at most, eccentrically by 15% of the disc width in the direction of the transverse axis between the first and second contact surfaces. The proposed arrangement of the coupling bushings also contributes to minimizing the disc width. It can be provided that a load-holding valve is assigned to each of the third and fourth connection points, which can be opened with an actuating plunger. The actuating plunger extends parallel to the vertical axis and is movable in this direction, and can be brought into contact with the main valve. At least one connecting channel is arranged in the first housing part, which fluidically connects the main valve to an assigned load-holding valve. The first connecting channel, viewed along the longitudinal axis, curves around the at least one actuating chamber. The proposed mechanical actuation of the load-holding valve with the main valve requires that the actuating plunger extends parallel to the vertical axis as proposed. The actuating plunger preferably bypasses the actuating chamber so that the valve assembly requires minimal installation space.The proposed arrangement of the first connecting channel prevents it from intersecting the actuating chamber. It should be noted that hydraulically actuated load-holding valves are also known, which can be arranged much more flexibly within the valve assembly, thus preventing the aforementioned collision problem between the first connecting channel and the actuating chamber from occurring in the first place. However, hydraulically actuated load-holding valves are significantly more expensive than the proposed mechanically actuated load-holding valves. The load-holding valves are preferably arranged directly adjacent to the associated coupling bushing, so that the flow paths between the load-holding valves and the associated coupling bushing are short. The corresponding channel cross-sections can therefore be made particularly large. Overall, this results in low flow resistance for the pressure fluid. It can be provided that the outlet openings of the second connection points are connected to each other via a straight second connecting channel running parallel to the transverse axis, with the main valve passing through this second connecting channel. This results in a valve assembly that requires very little space in the direction of the vertical axis. Furthermore, it prevents the second connecting channel from intersecting the actuation space. The second connecting channel may have a free cross-sectional area along its entire length, dimensioned to allow pressurized fluid to flow past the main valve on two opposite sides. The second connecting channel is preferably part of a tank channel that runs through the entire valve block, which is formed by several valve assemblies according to the invention. Due to the proposed design of the second connecting channel, this tank channel has a particularly low flow resistance, which is minimally affected by the main valves. The smallest transverse dimension of the second connecting channel is preferably larger than the largest diameter of the main valve. It can be provided that the openings of the second connection points are arranged in the same plane as one of the coupling bushings, with said plane being oriented perpendicular to the longitudinal axis. This allows the second connection channel to be designed with a particularly large cross-sectional area without affecting other elements of the valve assembly. It can be provided that each coupling bushing is associated with a leakage chamber in the first housing part, wherein the leakage chambers are fluidically connected to at least two fifth connection points formed by at least two outlet openings arranged in the first and second contact surfaces in the direction of the transverse axis, the fifth connection points being designed separately from the first to fourth connection points. Leaks, which occur particularly during the coupling and uncoupling of the quick-coupling devices, are to be discharged via the fifth connection points. The corresponding pressurized fluid is typically heavily contaminated, which is why it is preferably not routed to the tank that can be connected to the second connection points. Instead, it is preferably disposed of.Each pair of fifth connection points within a valve block forms a dirt oil channel that runs through the entire valve block and through which the aforementioned contaminated pressure fluid is discharged. Each coupling bushing can be assigned a separate dirt oil channel, resulting in a total of four fifth connection points, arranged in pairs in an aligned configuration. It may be provided that two sixth connection points are included, formed by two outlet openings arranged parallel to the transverse axis and aligned in the first and second mounting surfaces, with the sixth connection points being fluidically connected to the actuating chamber. The leakage from the quick-coupling devices, which enters the actuating chamber, is to be diverted via the sixth connection points. The corresponding pressurized fluid is typically uncontaminated, which is why it is preferably routed to the tank that can be connected to the second connection points. The pair of sixth connection points within a valve block forms a leakage oil channel that runs through the entire valve block and through which the aforementioned pressurized fluid can be diverted to the tank. It may be provided that a second housing part, formed separately from the first housing part and in one piece, abuts the first housing part, wherein the second housing part is part of an actuating device for the main valve. The actuating device preferably comprises a pilot valve with which the main valve can be moved hydraulically. The pilot valve is preferably actuated by means of an electromagnet. The actuating device may have a third housing part, which abuts the second housing part on the side facing away from the first housing part. It can be provided that the at least one actuating axis has a base section which is integrally composed of a circular cylinder and a parallel rectangular profile, with the at least one actuating cam projecting from the rectangular profile. The circular cylinder and the rectangular profile preferably extend parallel to the longitudinal axis. The diameter of the circular cylinder is preferably larger than the length of the short side of the rectangular profile and smaller than the long side of the rectangular profile. The proposed shape of the actuating axis allows the diameter of the actuating chamber to be made particularly small, while still enabling easy assembly of the actuating axis. It is understood that the features mentioned above and those to be explained below can be used not only in the combinations specified, but also in other combinations or on their own, without leaving the scope of the present invention. The invention is explained in more detail below with reference to the accompanying drawings. These show: Fig. 1 a perspective view of a valve assembly according to the invention; Fig. 2 a longitudinal section of the valve assembly according to Fig. 1 without the actuating device; Fig. 3 a perspective sectional view of the first housing part; Fig. 4 a cross-section of the valve assembly according to Fig. 1; and Fig. 5 a perspective view of the actuating axis with the actuating lever. Fig. 1 shows a perspective view of a valve assembly 10 according to the invention. The valve assembly 10 has a housing 20, which is composed of a first, a second, and a third housing part 30; 50; 60, wherein the housing parts 30; 50; 60 are formed separately from one another. The second and the third housing parts 50; 60 are part of an actuating device 51, with which the main valve (No. 70 in Fig. 2) can be moved. The first housing part 30 is made of cast iron, for example, so that it can withstand the high fluid pressures inside. It has a first and a second contact surface 31; 32, which are flat and spaced parallel to each other by a disk width 33, pointing away from each other. Several valve assemblies 10 can abut directly against each other at the contact surfaces 31; 32, being held together by tie rods (not shown) that pass through the tie rod bores 28 in the first housing part 30. The contact surfaces 31; 32 are oriented perpendicular to a transverse axis 12. A longitudinal axis 11 is oriented perpendicular to the transverse axis 12. A vertical axis 13 is oriented perpendicular to both the longitudinal and the transverse axes 11; 12. In the second mounting surface 32, a total of seven outlet openings 36 are arranged. Each of these outlet openings 36 is aligned with an outlet opening (No. 35 in Fig. 4) in the first mounting surface 31 along the transverse axis 12. The aforementioned outlet openings 35; 36 each form a first, a second, a fifth, a sixth, or a seventh connection point 21; 22; 25; 26; 27. The corresponding outlet openings 35; 36 are fluidically directly connected to each other, as shown in Fig. 4 with reference to the two first connection points 21. This results in a fluid channel that passes through all valve assemblies 10 of a valve block. The orifice 36 in the second contact surface 32 is each surrounded by a sealing ring 160, with only a portion of the sealing rings 160 being shown in Fig. 1. The first contact surface 31 is flat in the area of ​​the sealing rings 160, so that it can seal against an associated sealing ring 160 on the second contact surface 32 of an adjacent valve assembly 10. Accordingly, no pressurized fluid can escape from the valve block between the contact surfaces 31 and 32. Furthermore, the first housing part 30 has a first side surface 40, which is approximately planar and oriented perpendicular to the longitudinal axis 11. An actuation chamber 37 opens into the first side surface 40 and extends parallel to the longitudinal axis 11 within the first housing part 30. An actuation shaft (No. 143 in Fig. 5) is rotatably mounted in the actuation chamber 37 and is integrally formed with an actuating lever 145, which extends perpendicular to the longitudinal axis 11. The actuating lever 145 is arranged on the outside of the housing 20 so that it can be actuated by a user of the valve assembly 10. Furthermore, the first housing part 30 has a second side surface 41, which is flat and oriented perpendicular to the vertical axis 13. The third and fourth connection points 23 and 24 open into the second side surfaces. The seventh connection points 27 form a separate control oil inlet and a separate control oil return, through which pressure fluid can flow to and from the actuating device 51. Fig. 2 shows a longitudinal section of the valve assembly 10 according to Fig. 1 without the actuating device. A main slide 70 is movably mounted in the first housing part 30 parallel to the longitudinal axis 11. The main slide 70 is essentially rotationally symmetrical with respect to the longitudinal axis 11, whereby the rotational symmetry may be interrupted, for example, by fine control notches in the area of ​​the orifices 77, 78a - 78d. Furthermore, a pressure balance 80 is movably mounted in the first housing part 30 parallel to the longitudinal axis 11. The pressure balance 80, together with the first housing part 30, forms an associated continuously adjustable orifice 81. A first fluid flow path leads from the first connection points 21 via the continuously adjustable orifice 81 of the pressure balance 80, then via the continuously adjustable orifice 77 of the main valve 70 into the third connecting channel 42. The pressure in the third connecting channel 42 loads the pressure balance 80 to the left in Fig. 2, while the pressure balance 80 is loaded in the opposite direction by the pressure upstream of the continuously adjustable orifice 77 in the main valve. The corresponding pressure difference acts on a pre-tensioned spring 82. Consequently, a pressure gradient develops at the continuously adjustable orifice 77 on the main valve 70, which depends essentially on the pre-tension of the spring 82.The continuously adjustable aperture 77 is closed in the central position of the main slide 70, whereby the free aperture cross-section increases when the main slide 70 is moved away from the central position, and this is the case in each of the two possible directions of movement of the main slide 70. Starting from the third connecting channel 42, the pressure fluid can flow either via orifice 78a to the first connection point 23 or via orifice 78d to the third connection point 23. When the main slide valve in Fig. 2 is moved to the right, orifices 78a and 78c are opened, while orifices 78b and 78d are closed. When the main slide valve in Fig. 2 is moved to the left, orifices 78b and 78d are opened, while orifices 78a and 78c are closed. Another fluid flow path leads from the third connection point 23 via the orifice 78b to the second connection points 22. Yet another fluid flow path leads from the fourth connection point 24 via the orifice 78c to the second connection points 22. Thus, the first to fourth connection points 21-24 can be fluidically connected to each other depending on the position of the main valve 70. The third and fourth connection points 23 and 24 are each formed by a quick-coupling device 140, which may be designed, for example, according to US 6,016,835 A. The corresponding quick-coupling devices 140 serve to connect a hose equipped with a coupling plug adapted to the associated quick-coupling device 140. The quick-coupling devices 140 can be unlocked and locked again using the actuating lever 145. The quick-coupling devices 140 each comprise a coupling socket 141, which is movable parallel to the vertical axis 13. Typically, coupling sockets 141 in sizes 1 / 2" and 3 / 4" are used. The shape of the first housing part 30 is preferably adapted to the larger 3 / 4" coupling socket, whereby the smaller 1 / 2" coupling socket can also be installed in the first housing part 30 by means of an adapter sleeve.The coupling bushings 141 are each pressed into a locked position by an associated spring 146 in Fig. 2. They can be moved upwards into the unlocked position in Fig. 2 using the actuating lever 145. At their outer ends, the coupling bushings 141 are each surrounded by an annular leakage chamber 142, which is formed by a groove in the first housing part 30. The leakage chambers 142 are each directly fluidically connected to an associated pair of fifth connection points (No. 25 in Fig. 1). The leakage oil escaping there is usually heavily contaminated, so it is preferably not returned to the hydraulic circuit. The fifth connection points (No. 25 in Fig. 1) located at the ends of the valve block can therefore be fitted with a hose barb to which a hose leading to a waste oil container can be connected. The hose barb is preferably pressed into the associated fifth connection point, so that no special machining is required at the respective fifth connection point. Furthermore, each of the third and fourth connection points 23; 24 is assigned an unlockable load-holding valve 150. In the closed position, the load-holding valve 150 acts as a check valve, which seals off any fluid flow coming from the assigned third or fourth connection point 23; 24. For this purpose, it is designed as a poppet valve. In the opposite direction, the pressure fluid can flow through the load-holding valve 150 with minimal resistance. In the unlocked position, the pressure fluid can flow through the load-holding valve 150 in both directions with minimal resistance. The load-holding valves 150 are unlocked by an associated actuating plunger 151. The actuating plunger 151 is designed in the form of an elongated circular cylinder extending parallel to the vertical axis 13. The lower end of the actuating plunger 151, as shown in Fig. 2, rests against an associated control contour on the main valve 70.In the central position of the main slide 70, the actuating plungers 151 are in the lowest position shown in Fig. 2, in which the associated load-holding valve 150 is locked. When the main slide 70 is moved to the left or right from the central position, the actuating plungers 151 move upwards in Fig. 2, thereby unlocking the associated load-holding valve 150. The load-holding valves 150 are each fluidically connected via two associated first connecting channels 38 in parallel to two of the associated orifices 78a - 78d on the main valve 70. Furthermore, the load-holding valves 150 are fluidically connected via an associated fourth connecting channel 43 to the associated quick-coupling device 140. It should be noted that the fourth connecting channels 43 are very short and have a large cross-sectional area, thus exhibiting low flow resistance. This is made possible by the arrangement of the quick-coupling devices 140 according to the invention. Figure 2 further shows the rectangular cross-sectional shape of the second connecting channel 39, which fluidically connects the second connection points 22 in a straight line. The main valve 70 runs through the middle of the second connecting channel 39, so that pressurized fluid flowing along the second connecting channel 39 can flow past the main valve on two opposite sides. The outlet openings of the second connection points 22 are arranged in a plane with one of the coupling bushings 141, wherein the said plane is oriented perpendicular to the longitudinal axis 11. Fig. 3 shows a perspective sectional view of the first housing part 30. The corresponding section plane runs perpendicular to the longitudinal axis 11, with the section position being chosen so that the course of a first connecting channel 38 and the load pressure channel 44 becomes visible. The longitudinal axis 11 forms the central axis 11 of the main slide valve (No. 70 in Fig. 2), which is arranged eccentrically between the first and second contact surfaces 31 and 32 in the direction of the transverse axis (No. 12 in Fig. 1) towards the second contact surface 32. The actuating chamber 37, on the other hand, is arranged eccentrically between the first and second contact surfaces 31 and 32 in the direction of the transverse axis (No. 12 in Fig. 1) towards the first contact surface 31. The actuating chamber 37 is displaced relative to the main slide valve (No. 70 in Fig. 1) towards the second side surface 41 in the direction of the vertical axis (No. 13 in Fig. 1). The actuation chamber 37 extends with the circular cross-sectional shape shown in Fig. 3 from the first side surface (No. 40 in Fig. 1) parallel to the longitudinal axis 11, passing by both coupling bushings (No. 141 in Fig. 2). In the area of ​​the coupling bushings, the actuation chamber 37 can have a rectangular cross-sectional shape.The first connecting channel 38 runs curved in the direction of the longitudinal axis 11 around the at least one actuation space 37. Figure 3 further shows the elongated cross-sectional shape of the fourth connecting channel 43, which has a comparatively large area. Also noteworthy is the load pressure channel 44, which runs parallel to the transverse axis (No. 12 in Figure 1) through the first housing part 30. The load pressure channel 44 opens into a recess 45 on the second contact surface 32 in the first housing part 30, into which the load pressure channel 44 of the adjacent valve assembly also opens. The pressure in the third connecting channel 42, which is taken directly from the pressure compensator 80, is also connected to the recess 45. A changeover valve (not shown) is installed in the recess 45. The changeover valves of all valve assemblies of a valve block form a changeover valve cascade, with which the highest pressure in all third connecting channels 42 is determined.This pressure is essentially equal to the highest load pressure of all actuators connected to the valve block. The pump's delivery pressure is typically regulated to a pressure that is a predetermined pressure differential above the maximum load pressure. Fig. 4 shows a cross-section of the valve assembly 10 according to Fig. 1. The corresponding section plane runs perpendicular to the longitudinal axis (No. 11 in Fig. 1), passing through the central axis of the coupling bushing 141 at the fourth connection point 24. The internal structure of the quick-coupling device is not shown in Fig. 4; for this, reference is made, for example, to US 6,016,835 A. Any other quick-coupling device 140 with a coupling bushing 141 can also be used. Corresponding quick-coupling devices are known, for example, from the catalog that was available on March 13, 2015, at the internet address http: / / www.faster.it / catalogs / europe / files / assets / common / downloads / Catalogue_Europe.pdf. Figure 4 shows in particular that the coupling bushing 141 of the quick-coupling device 140 is arranged between the first and second contact surfaces 31; 32 on the first housing part 30. The position of the actuating shaft 143 and the actuating cam 144 within the actuating chamber 37 is also shown. The axis of rotation (No. 143a in Figure 5) of the actuating shaft 143 coincides with the central axis of the actuating chamber 37. Figure 4 shows the unactuated position of the actuating cam 144, in which it rests against an associated stop 46 on the first housing part 30, maintaining a distance from the associated coupling bushing 141. By pivoting the actuating lever (No. 145 in Fig. 1), the actuating cam 144 is moved towards the associated coupling bushing 141 until it moves the bushing upwards in Fig. 4, thus unlocking it. This compresses the coil spring 146. Figure 4 further shows how the outlet openings 35; 36 of the first and sixth connection points 21; 26 are aligned in the direction of the transverse axis 13, being directly fluidically connected to each other via a straight connecting channel. The corresponding connecting channel of the sixth connection point 26 intersects the actuation chamber 37, so that the leakage oil from the actuation chamber 37 can be discharged to the tank via the sixth connection point 26. Reference should also be made to the previously mentioned seals 160, which are arranged only at the outlet opening 36 of the second contact surface 32. Figure 4 also clearly shows that the pressure balance is arranged in the direction of the vertical axis 13 in line with the main slide 70. It can also be seen that the coupling bushings 141 are arranged approximately centrally between the first and second contact surfaces 31; 32, being slightly off-center towards the second contact surface 32. This is intended to provide sufficient space for the actuation chamber 37. Fig. 5 shows a perspective view of the actuating axis 143 with the actuating lever 145. In the present invention, a single actuating axis 143 is provided. However, a valve assembly is known from German patent application number 102015202916.6 in which a separate actuating axis is provided for each of the two coupling bushings, which can be arranged concentrically to each other. This embodiment can also be used with the present invention. The actuating shaft 143 is formed integrally with the actuating lever 145. Both sections 143 and 145 are straight, forming an angle of approximately 90°. The actuating shaft 143 has a base section 147 from which two actuating cams 144 project. These cams are arranged along the longitudinal axis (No. 11 in Fig. 1) at the location of an associated coupling bushing (No. 141 in Fig. 2). The base section 147 is integrally composed of an elongated circular cylinder 148 and a rectangular profile 149, with the actuating cams 144 projecting from the rectangular profile 149. The central axis of the circular cylinder 148 forms the axis of rotation 143a of the actuating axis 143. The circular cylinder 148 extends in the direction of the longitudinal axis (No. 11 in Fig. 1) slightly beyond the rectangular profile 149, so that it can be rotatably mounted in a suitable bore in the first housing part (No. 30 in Fig. 1).The second rotary bearing is formed by the sealing flange 162 at the opposite end of the actuating shaft 143. The circular sealing flange 162 has the same diameter as the actuating chamber (No. 37 in Fig. 3) and is rotatably mounted within it. The sealing flange 162 is arranged concentrically with respect to the circular cylinder 148, so that the actuating shaft 143 can rotate with minimal resistance. A circumferential groove is provided on the outer circumferential surface of the sealing flange 162, in which a sealing ring (not shown) is received, which seals the actuating chamber (No. 37 in Fig. 3) to the outside. It should be noted that the pressure in the actuating chamber (No. 37 in Fig. 3) is essentially equal to the ambient pressure. The actuating axis 143 has an installation dimension 161, which is measured in the area of ​​an actuating cam 144. The installation dimension 161 is the largest dimension of the actuating axis 143 transversely to the longitudinal axis (No. 11 in Fig. 1). The installation dimension 161 is chosen to be slightly smaller than the diameter of the actuating chamber (No. 37 in Fig. 3), so that the actuating axis 143 can be pushed through the actuating chamber (No. 37 in Fig. 3) in the direction of the longitudinal axis (No. 11 in Fig. 1). Only at the end of this linear installation movement does a transverse movement of the actuating axis 143 take place, with which the rotary axis 143a is brought into its final position. Reference sign 10 Valve assembly 11 Longitudinal axis 12 Transverse axis 13 Vertical axis 20 Housing 21 First connection point 22 Second connection point 23 Third connection point 24 Fourth connection point 25 Fifth connection point 26 Sixth connection point 27 Seventh connection point 28 Tie rod bore 30 First housing part 31 First contact surface 32 Second contact surface 33 Disc width 35 Outlet opening in the first contact surface 36 Outlet opening in the second contact surface 37 Actuating chamber 38 First connecting channel 39 Second connecting channel 40 First side surface 41 Second side surface 42 Third connecting channel 43 Fourth connecting channel 44 Load pressure channel 45 Recess 46 Stop 50 Second housing part 51 Actuating device 60 Third housing part 70 Main slide 77 Continuously adjustable orifice 78a Orifice 78b Orifice 78c Orifice 78d Orifice 80 Pressure balance 81 continuously adjustable aperture 82 spring 140 quick-coupling device 141 coupling bushing 142 leakage chamber 143 actuating axis 143a pivot axis of theActuating shaft 144 Actuating cam 145 Actuating lever 146 Spring 147 Base section 148 Circular cylinder 149 Rectangular profile 150 Load holding valve 151 Actuating plunger 160 Sealing ring 161 Mounting dimension 162 Sealing flange

Claims

Valve assembly (10) comprising a one-piece first housing part (30) with a first and a second flat contact surface (31; 32), wherein the first and the second contact surfaces (31; 32) are arranged parallel to each other at a distance from each other by a disk width (33), pointing away from each other and oriented perpendicular to a transverse axis (12), wherein a main valve (70) is linearly movably received in the first housing part (30) parallel to a longitudinal axis (11), the longitudinal axis (11) being oriented perpendicular to the transverse axis (12), wherein the first housing part (30) has two first, two second, one third and one fourth connection point (21; 22; 23; 24), wherein the first to fourth connection points (21; 22; 23; 24) are fluidically connectable to each other depending on the position of the main valve (70), wherein the first and the second connection points (21; 22) are two mouth openings each (35;36) are formed, which are arranged parallel to the transverse axis (12) in alignment in the first and second contact surfaces (31; 32), wherein a quick-coupling device (140) is received in the first housing part (30) at the third and fourth connection points (23; 24), wherein the quick-coupling devices (140) each have a separate coupling bushing (141) which is movable parallel to a vertical axis (13), wherein the vertical axis (13) is aligned perpendicular to the longitudinal and transverse axes (11; 12), wherein the coupling bushings (141) are located between the first and second contact surfaces (31;32) are arranged, characterized in that the first housing part (30) has at least one actuation chamber (37) extending parallel to the longitudinal axis (11), in which at least one actuation axis (143) is rotatably received, wherein the at least one actuation axis (143) is each provided with at least one actuation cam (144), wherein both coupling bushings (141) can be brought into contact with an associated actuation cam (144), wherein the at least one actuation chamber (37) is arranged off-center between the first and the second contact surfaces (31; 32) in the direction of the transverse axis (12) to the first contact surface (31). Valve assembly according to claim 1, wherein the actuation chamber (37) extends from a side surface (40) of the first housing part (30) parallel to the longitudinal axis (11), passing by both coupling bushings (141). Valve assembly according to one of the preceding claims, wherein the main slide (70) is arranged off-center between the first and the second contact surface (31; 32) in the direction of the transverse axis (12) towards the second contact surface (32). Valve assembly according to one of the preceding claims, wherein the coupling bushings (141) are arranged centrally or at most 15% of the disk width (33) off-center in the direction of the transverse axis (12) between the first and the second contact surface (31; 32). Valve assembly according to one of the preceding claims, wherein a load-holding valve (150) is assigned to each of the third and fourth connection points (23; 24), which can be opened with an actuating plunger (151), wherein the actuating plunger (151) extends parallel to the vertical axis (13) and is movable in this direction, wherein it can be brought into contact with the main valve (70), wherein at least one first connecting channel (38) is arranged in the first housing part (30), which fluidically connects the main valve (70) to an assigned load-holding valve (150), wherein the first connecting channel (38) is curved around the at least one actuating chamber (37) when viewed in the direction of the longitudinal axis (11). Valve assembly according to one of the preceding claims, wherein the outlet openings (35; 36) of the second connection points (22) are connected to each other via a straight second connecting channel (39) running parallel to the transverse axis (12), wherein the main valve (70) passes through the second connecting channel (39). Valve assembly according to claim 6, wherein the second connecting channel (39) has a free cross-sectional area over its entire length which is dimensioned to allow pressure fluid to flow past the main valve (70) on two opposite sides. Valve assembly according to one of the preceding claims, wherein the outlet openings (35; 36) of the second connection points (22) are arranged in a plane with one of the coupling bushings (141), wherein said plane is oriented perpendicular to the longitudinal axis (11). Valve assembly according to one of the preceding claims, wherein each coupling bushing (141) is associated with a leakage chamber (142) in the first housing part (30), wherein the leakage chambers (142) are fluidically connected to at least two fifth connection points (25) formed by at least two openings (35; 36) arranged in the direction of the transverse axis (12) in the first and second contact surfaces (31; 32), wherein the fifth connection points (25) are formed separately from the first to fourth connection points (21 - 24). Valve assembly according to one of the preceding claims, wherein two sixth connection points (26) are provided, which are formed by two openings (35; 36) arranged parallel to the transverse axis (12) in alignment in the first and second contact surfaces (35; 36), wherein the sixth connection points (26) are fluidically connected to the actuating chamber (37). Valve assembly according to one of the preceding claims, wherein a one-piece second housing part (50) formed separately from the first housing part (30) abuts the first housing part (30), wherein the second housing part (50) is part of an actuating device (51) for the main valve (70). Valve assembly according to one of the preceding claims, wherein the at least one actuating axis (143) has a base section (147) which is integrally composed of a circular cylinder (148) and a parallel rectangular profile (149), wherein the at least one actuating cam (144) projects out of the rectangular profile (149).

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