CN118369511A - Shuttle valve, reversing slide valve module and pneumatic or hydraulic assembly - Google Patents

Abstract

The invention relates to a shuttle valve for selecting the maximum pressure in two separate control pressure lines, comprising: a first input pressure port and a second input pressure port for a first control pressure; a third input pressure port and a fourth input pressure port for a second control pressure; a first output pressure port for coupling to a first control pressure line and a second output pressure port for coupling to a second control pressure line; a first valve body in a connection of the flow guide between the first and second inlet pressure connections on the one hand and the first outlet pressure connection on the other hand, and a second valve body between the third and fourth inlet pressure connections on the one hand and the second outlet pressure connection on the other hand; wherein the first valve body is subjected to a first control pressure from the first inlet pressure port on a first side, to a first control pressure from the second inlet pressure port on a second side opposite thereto, and the second valve body is subjected to a second control pressure from the third inlet pressure port on the first side, to a second control pressure from the fourth inlet pressure port on a second side opposite thereto; wherein the first control pressure acts on first and second pressure-controlled surfaces of the first valve body, respectively, and the second control pressure acts on third and fourth pressure-controlled surfaces of the second valve body, respectively, the first and second pressure-controlled surfaces being larger than the third and fourth pressure-controlled surfaces, respectively, and the first valve body and the second valve body are forcibly coupled for common movement.

Description

Shuttle valve, reversing slide valve module and pneumatic or hydraulic assembly

Technical Field

The invention relates to a shuttle valve for selecting the maximum pressure in two separate control pressure lines, a shuttle valve module having two redundant shuttle valves and a shuttle valve, and a pneumatic or hydraulic assembly having a double-acting cylinder and a shuttle valve module.

Background

In practical use, a generic reversing slide valve module with two electrohydraulic positioning regulators, each having a continuously controllable reversing valve, is used to actuate a single-acting cylinder. The corresponding hydraulic assembly is shown in fig. 1. The first directional valve 31 provides a first control pressure to the input pressure port 11 of the shuttle valve 10 and the second directional valve 32 provides a first control pressure to the input pressure port 13 of the shuttle valve 10 redundantly. The shuttle valve 10 converges the two applied control pressures of the directional valves 31, 32 via a maximum selection to a common control pressure line 1, wherein the control pressure line 1 is coupled to a unidirectional cylinder 40 'in order to charge the piston chamber 41 with a first control pressure, so that the first control pressure actuates the piston 42 of the cylinder 40' against the force of the piston spring 43.

Thus, for example, the cylinder 40 equipped with a positioning sensor can be positioned steplessly with little hysteresis by spring return.

As a result of the provision of the two directional valves 31, 32, a redundantly constructed control system is provided, which has two controlled variable outputs which act on a common output. In the event of a fault, defective switching valves 31, 32 or components associated with switching valves 31, 32, such as pressure gauges or pressure measuring transducers, can be replaced by a backup device during operation of the hydraulic assembly.

If the two directional valves 31, 32 are set to be identical in terms of their transmission function, for example, by letting the two controlled variable outputs of the higher-level redundantly constructed regulating system form the target value for the directional valves 31, 32, if the function of one of the two directional valves 31, 32 fails, for example, due to a broken line in the contained electromagnetic drive, the actuating force of that directional valve 31, 32 becomes zero, and the return spring 35 of the respective directional valve 31, 32 pushes the directional valve piston 34 into the load-free position, so that the respective input pressure connection 11, 13 of the shuttle valve 10 is switched "to tank", i.e., is connected to the tank connection T of the directional valve 31, 32. The valve body 17 of the shuttle valve 10 autonomously closes the inlet pressure connection 11, 13 connected to the defective directional control valve 31, 32. The other reversing valve 31, 32 will automatically take over the control pressure regulation in the control pressure line 1, so that operation is continued. The pressure gauge or pressure measuring transducer on the defective directional valve 31, 32 shows the pressure at the tank return line, in particular 0 bar, and after closing the ball tap (P1 or P2) of the respective pressure supply, the defective directional valve 31, 32 can be removed and replaced in operation.

If a reversing spool valve module 30 of the kind shown in fig. 1 is extended for operation with a double acting cylinder 40 by providing two shuttle valves 10.1 and 10.2, the hydraulic assembly shown in fig. 2 will result. Corresponding components are denoted by corresponding reference numerals in fig. 1. If one of the reversing valves 31, 32 is now deactivated, the entire supply pressure P acts on the connected shuttle valve 10.1, 10.2 and thus on the side of the piston 42 of the cylinder 40 which is connected via the first control pressure line 1 or the second control pressure line 2. The piston 42 is always moved into the corresponding end position. The second reversing valve 31, 32, which is still working, will not be able to position the piston 42 and thus not maintain the function of the cylinder 40. The maximum pressure P of the defective directional valves 31, 32 is always on.

It is only possible to restore the function of the hydraulic assembly when the supply pressure P at the failed reversing valves 31, 32 is closed manually, for example via a ball cock. In practical applications where high availability facilities are required, such functional limitations are disadvantageous.

Disclosure of Invention

The object of the present invention is to specify a shuttle valve, a reversing slide valve module having such a shuttle valve, and a pneumatic or hydraulic assembly having such a reversing slide valve module, which can maintain the full function of an actuator, in particular a cylinder, which is acted upon by a control pressure, even in the event of failure of the reversing valve.

The object is achieved according to the invention by a shuttle valve having the features of claim 1. The dependent claims describe particularly advantageous embodiments of the invention, as well as a reversing slide valve module according to the invention and a pneumatic or hydraulic assembly according to the invention.

A shuttle valve according to the invention for selecting the maximum pressure in two separate control pressure lines, for example for actuating an actuator or actuators, in particular for actuating a double-acting cylinder, has a first and a second input pressure connection for a first control pressure. Furthermore, a third and a fourth input pressure port for the second control pressure are provided. The first control pressure may be at least temporarily greater than or less than the second control pressure. The two control pressures are in particular those which should be supplied to the double-acting cylinder, for example as control pressures, the first control pressure acting on a first side of the cylinder piston and the second control pressure acting on an opposite second side of the cylinder piston. However, the shuttle valve according to the present invention can also be used for actuators other than cylinders.

The shuttle valve according to the invention has a first output pressure connection for coupling to the first control pressure line and a second output pressure connection for coupling to the second control pressure line, so that one of the two control pressures is provided in the first control pressure line and the other of the two control pressures is provided in the second control pressure line, respectively.

A first valve body is arranged in the flow-guiding connection between the first and second inlet pressure connections on the one hand and the first outlet pressure connection on the other hand, and a second valve body is arranged between the third and fourth inlet pressure connections on the one hand and the second outlet pressure connection on the other hand. The first valve body is subjected to a first control pressure from the first inlet pressure connection on a first side and to a first control pressure from the second inlet pressure connection on a second, opposite side. The second valve body is subjected to a second control pressure from the third supply pressure connection on a first side and to a second control pressure from the fourth supply pressure connection on a second, opposite side.

According to the invention, the first control pressure acts on the first and second pressure-controlled surfaces of the first valve body and the second control pressure acts on the third and fourth pressure-controlled surfaces of the second valve body, respectively. The first and second controlled pressure loading surfaces are larger than the third and fourth controlled pressure loading surfaces, respectively, and the first valve body and the second valve body are forcibly coupled for common movement. In particular, the first and second controlled pressure loaded faces are the same size, and the third and fourth controlled pressure loaded faces are the same size.

Thanks to the forced coupling and the area ratio of the first pressure-controlled surface to the third pressure-controlled surface or the second pressure-controlled surface to the fourth pressure-controlled surface which is not equal to 1, an unobstructed flow of all supply pressure into the first or second control pressure line is prevented. When two reversing valves are connected with the shuttle valve, the nondefective reversing valve can maintain control right and maintain the control function.

Preferably, a coupling element is provided which mechanically transmits the movement of the first valve body to the second valve body. A compact design and a safe operating mode can be achieved in this way.

According to a preferred embodiment of the invention, the first valve body is multipart and comprises a first valve body part and a second valve body part. The second valve body may likewise be multi-piece and have at least a third valve body portion and a fourth valve body portion. The coupling element may then be positioned between the first valve body part and the second valve body part on the one hand and the third valve body part and the fourth valve body part on the other hand. The valve body parts can rest freely on the coupling element, in particular via the intermediate spacer element, so that a mechanically positive coupling is again achieved. Thus, a reliable functional mode is achieved with a compact design.

It is particularly preferred that the first valve body portion cooperates with the first valve seat to form a first closure site, the second valve body portion cooperates with the second valve seat to form a second closure site, the third valve body portion cooperates with the third valve seat to form a third closure site, and the fourth valve body portion cooperates with the fourth valve seat to form a fourth closure site. The sealing points can each be formed by a valve seat in a common one-piece or multi-piece housing of the shuttle valve, wherein the valve body parts respectively rest in a sealed state against the associated valve seats.

The first input pressure port may be sealed by a first sealing site, the second input pressure port may be sealed by a second sealing site, the third input pressure port may be sealed by a third sealing site, and the fourth input pressure port may be sealed by a fourth sealing site. The function according to the invention of the shuttle valve is thus particularly easy to implement.

In order to be able to properly regulate the pressure applied at one or both of the supply pressure connections and to avoid leakage even if an error occurs in the pressure applied at one or both of the supply pressure connections, as described herein, for example, as a result of a failure in the upstream reversing valve, the third valve body part can preferably cooperate with the fifth valve seat to form a fifth sealing point, and the fourth valve body part can cooperate with the sixth valve seat to form a sixth sealing point, and the fifth valve seat can be axially opposite the third valve seat, and the sixth valve seat can be axially opposite the fourth valve seat, so that the third supply pressure connection can be sealed by means of the third sealing point and the fifth sealing point as a function of the position of the fourth valve body part, and the fourth supply pressure connection can be sealed by means of the fourth sealing point and the sixth sealing point as a function of the position of the fourth valve body part. However, depending on the pressure difference applied via the valve body part, the valve body part which is not permanently pressed against the third or fourth valve seat can also be lifted from the two axially opposite valve seats associated therewith into the intermediate position.

In order to achieve a particularly advantageous construction, the first valve body part, the coupling element and the second valve body part can be arranged one after the other in a first direction, and the third valve body part, the coupling element and the fourth valve body part can be arranged one after the other in a second direction extending perpendicular or oblique to the first direction.

According to one embodiment, the coupling element is spherical.

Additionally or alternatively, the valve body portion may also be spherical.

If a spacer element is provided between the coupling element and at least one, several or all valve body parts, the coupling element is supported on the respective valve body part via the spacer element, the spacer element may also be spherical.

Preferably, the coupling element and the valve body, in particular the valve body part, rest freely against one another, for example via a spacer element arranged in between. If necessary, the pretensioning can be achieved by means of one or more spring elements, in particular compression springs, but this is not mandatory. According to a further embodiment, the contact is achieved solely by the pressure applied at the input pressure interface.

The reversing slide valve module according to the invention has two redundantly implemented reversing valves and a shuttle valve of the type indicated here, wherein both reversing valves respectively supply a first control pressure and a second control pressure and are respectively connected to the two supply pressure connections in a pilot-control-pressure manner, i.e. the first reversing valve is connected to the first and third supply pressure connections of the shuttle valve and the second reversing valve is connected to the second and fourth supply pressure connections.

The selector valves are each preferably embodied as continuously operable selector valves having an electromagnetic actuating mechanism.

In particular, the reversing valves each have an electromagnet as a drive device, which moves the valve piston against the force of a return spring of the reversing valve.

The pneumatic or hydraulic assembly according to the invention is provided with a double-acting cylinder comprising a piston chamber and a piston movable in the piston chamber, and with a reversing slide valve module of the type indicated, wherein a first outlet pressure connection is connected to the piston chamber on a first side of the piston in a pilot-pressure manner via a first control pressure line, and a second outlet pressure connection is connected to the piston chamber on an opposite second side of the piston in a pilot-pressure manner via a second control pressure line.

For the operation of the reversing slide valve module according to the invention, an electrical and hydraulic auxiliary energy source can be provided. All the electrical actuators and circuits required for operating the reversing slide valve module can be provided in the associated actuating magnet or actuating magnet arrangement, which is hydraulically and electrically connected to the reversing valve on the input side. When the double-acting cylinder is actuated, all control loop parameters and parameters for calibrating the piston position or piston rod position can be set on the control magnet by means of a potentiometer and/or software in the case of digital control electronics.

Drawings

The invention is exemplarily described below in connection with two embodiments and fig. 3 and 4.

Wherein:

FIG. 1 illustrates a hydraulic assembly having a reversing spool valve module according to the prior art;

FIG. 2 illustrates a hydraulic assembly having a reversing spool module logically expanded to the reversing spool module of FIG. 1 for actuating a double acting cylinder;

Fig. 3 shows a first embodiment of a pneumatic or hydraulic assembly according to the invention with a reversing slide valve module according to the invention and a shuttle valve according to the invention;

Fig. 4 shows a second embodiment of a shuttle valve according to the invention, which may be used in the pneumatic or hydraulic assembly of fig. 3, for example.

Detailed Description

Fig. 3 shows a pneumatic or hydraulic assembly according to the invention with a double-acting cylinder 40 having a piston chamber 41 and a piston 42 movable within the piston chamber 41. On the axial first side, the piston 42 is subjected to a control pressure from a first control pressure line 1 which opens into the piston chamber 41; on an axial second side, opposite the axial first side, the piston 42 is subjected to a control pressure from a second control pressure line 2 which opens into the piston chamber 41. The control pressures in the first control pressure line 1 and the second control pressure line 2 are provided or regulated by a reversing spool valve module 30 comprising a shuttle valve 10 and two reversing valves 31 and 32.

The shuttle valve 10 has a first input pressure port 11 and a second input pressure port 12 for a first control pressure. The first control pressure is provided by the first reversing valve 31 at the first input pressure connection 11 and the first control pressure is provided redundantly by the second reversing valve 32 at the second input pressure connection 12. The shuttle valve 10 also has a third input pressure port 13 and a fourth input pressure port 14 for a second control pressure, wherein the second control pressure is provided by the first directional valve 31 at the third input pressure port 13 and the second control pressure is provided by the second directional valve 32 at the fourth input pressure port 14.

The shuttle valve has a first output pressure port 15 coupled to the first control pressure line 1 and a second output pressure port 16 coupled to the second control pressure line 2.

A first valve body 17 is arranged in the flow-guiding connection between the first and second inlet pressure ports 11, 12 on the one hand and the first outlet pressure port 15 on the other hand. A second valve body 18 is arranged between the third and fourth inlet pressure connections 13, 14 on the one hand and the second outlet pressure connection 16 on the other hand. Thus, the first valve body 17 is subjected to a first control pressure from the first inlet pressure port 11 on a first side A1 and to a first control pressure from the second inlet pressure port 12 on a second side A2 opposite to the first side. The second valve body 18 is subjected to a second control pressure from the third inlet pressure connection 13 on a first side B1 and to a second control pressure from the fourth inlet pressure connection 14 on a second side B2 opposite the first side.

The first control pressure acts on the first and second pressure-controlled surfaces F1, F2 of the first valve body 17, respectively, and the second control pressure acts on the third and fourth pressure-controlled surfaces F3, F4 of the second valve body 18, respectively. The two valve bodies 17, 18 each cause a maximum pressure to be selected for the control pressure acting on them. The first face F1 and the second face F2 are larger than the third face F3 and the fourth face F4, respectively. Furthermore, the two valve bodies 17, 18 are mechanically coupled to each other such that they always move together in order to seal or release the first and third supply pressure ports 11, 13 or the second and fourth supply pressure ports 12,14, respectively, completely or partially. For this purpose, the two valve bodies 17, 18 are coupled to one another via a coupling element 19.

In order to be able to seal the inlet pressure connections 11, 12, 13, 14, the first valve body 17 cooperates with the first valve seat 20.1 and the second valve seat 20.2 in order to seal either the first inlet pressure connection 11 or the second inlet pressure connection 12. The second valve body 18 cooperates with the third valve seat 20.3 and the fourth valve seat 20.4 to seal either the third inlet pressure port 13 or the fourth inlet pressure port 14.

The first and second directional valves 31 and 32 each have an electromagnet 33 as a drive device and a directional valve piston 34 which is moved by the electromagnet 33 against the force of a return spring 35 in dependence on a controlled variable applied to the electromagnet 33, for example a control current in the range from 4 mA to 20 mA.

As long as the reversing slide valve module 30 is working properly, the same control pressure is applied to the input pressure connections 11 and 12 and to the input pressure connections 13 and 14, respectively, i.e. a first control pressure is applied to the input pressure connections 11 and 12 and a second control pressure is applied to the input pressure connections 13 and 14. The valve bodies 17, 18 are in the intermediate position, so that a first control pressure acts in the first control pressure line 1 and a second control pressure acts in the second control pressure line 2.

For example, if the second directional valve 32 is now disabled, its return spring 35 pushes the directional valve piston 34 to the zero position and connects the pressure port P with the fourth input pressure port 14. The second inlet pressure connection 12 is connected to a tank connection T of the second directional valve 32. Since the first valve body 17 has a larger active surface F1, F2 for pressure than the second valve body 18, the first valve body 17 forces the second valve body 18 into the fourth valve seat 20.4, sealing the fourth input pressure port 14. All control pressure P forced at the fourth input pressure port 14 will not be conducted up to the piston chamber 41; the shuttle valve 10 may take over or maintain control or regulation of the control pressure in the first control pressure line 1 and the second control pressure line 2 solely through the first valve body 17.

In another case, if the first reversing valve 31 fails, its return spring 35 pushes the reversing valve piston 34 to the zero position and connects its pressure port P with the third input pressure port 13. The tank connection T of the first reversing valve 31 is connected to the first supply pressure connection 11. Since the first valve body 17 again has a larger surface F1, F1 than the second valve body 18 for the applied control pressure, the first valve body 17 forces the second valve body 18 into the third valve seat 20.3, so that the control pressure of the pressure connection P on the first directional valve 31 cannot continue into the rod-side piston chamber 41. The second reversing valve 32 is given control and takes over the regulation of the control pressure in the first control pressure line 1 and the second control pressure line 2 alone.

Since in practical use the solution shown in fig. 3 with the connection of the two valve bodies 17, 18 via a rod or similar requires a relatively complex seal, an improved embodiment of the shuttle valve 10 is proposed according to fig. 4. In this embodiment, the first valve body 17 and the second valve body 18 each have a plurality of valve body parts, i.e. the first valve body 17 has a first valve body part 17.1 and a second valve body part 17.2, and the second valve body 18 has a third valve body part 18.1 and a fourth valve body part 18.2. The coupling element 19 is positioned between the first valve body part 17.1 and the second valve body part 17.2 and between the third valve body part 18.1 and the fourth valve body part 18.2. For example, as shown, the first valve body part 17.1, the coupling element 19 and the second valve body part 17.2 are arranged one after the other in a first direction, and the third valve body part 18.1, the coupling element 19 and the fourth valve body part 18.2 are arranged one after the other in a second direction, wherein the second direction is perpendicular or oblique to the first direction.

In the exemplary embodiment shown, the valve body parts 17.1, 17.2, 18.1, 18.2 do not rest directly on the coupling element 19, but via the intermediate spacer element 21.

For example, all valve body parts 17.1, 17.2, 18.1, 18.2, spacer element 21 and coupling element 19 are spherical. However, other shapes, in particular cylindrical or polygonal, are also conceivable.

The first valve body part 17.1 seals the first inlet pressure connection 11 with the first valve seat 20.1, the second valve body part 17.2 seals the second inlet pressure connection 12 with the second valve seat 20.2, the third valve body part 18.1 seals the third inlet pressure connection 13 with the third valve seat 20.3, and the fourth valve body part 18.2 seals the fourth inlet pressure connection 14 with the fourth valve seat 20.4, provided that a corresponding pressure ratio is applied to the inlet pressure connections 11,12,13 and 14.

Due to the size of the valve body parts 17.1, 17.2, 18.1, 18.2, the first valve body 17 comprising the valve body parts 17.1, 17.2 has a larger pressure-loaded surface F1, F2 than the second valve body 18 with the valve body parts 18.1, 18.2 has a pressure-loaded surface F3, F4.

If the first valve body part 17.1 is displaced via the spacer element 21 by the correspondingly higher control pressure at the first inlet pressure connection 11, so that the second valve body part 17.2 is pressed into the second valve seat 20.2, the fourth valve body part 18.2 is simultaneously pressed into the fourth valve seat 20.4 via the coupling element 19, while the pressure at the third inlet pressure connection 13 lifts the third valve body part 18.1 off the third valve seat 20.3. Thus, as is shown in fig. 3, control of the control pressure in the control pressure lines 1 and 2 is effected, which are respectively coupled to the shuttle valve 10, so that the first valve body 17 or the valve body parts 17.1, 17.2 of the first valve body 17 are positioned between the first control pressure line 1 and the first two input pressure connections 11,12, while the second valve body 18 or the valve body parts 18.1, 18.2 are positioned between the second control pressure line 2 and the input pressure connections 13, 14.

Further, fifth and sixth valve seats 20.5 and 20.6 are preferably also provided for the third and fourth valve body parts 18.1 and 18.2 in order to seal the third and fourth inlet pressure ports 13 and 14. The fifth valve body seat 20.5 is axially opposite the third valve body seat 20.3 and the sixth valve body seat 20.6 is axially opposite the fourth valve body seat 20.4, so that when the third valve body part 18.1 is lifted from the third valve body seat 20.3 due to the pressure of the third inlet pressure port 13, the third valve body part 18.1 seals the third inlet pressure port 13 together with the fifth valve body seat 20.5 and when the fourth valve body part 18.2 is lifted from the fourth valve seat 20.4 due to the pressure at the fourth inlet pressure port 14, the fourth valve body part 18.2 seals the fourth inlet pressure port 14 together with the sixth valve body seat 20.6, wherein the coupling element 19 is in such a position that the lifting of the valve body parts 18.1, 18.2 from the respective valve seats 20.3, 20.4 is released and there is a sufficient pressure difference over the respective valve body parts 18.1, 18.2, respectively. In the intermediate space laterally on the side of the coupling element 19 on the side of the first valve body part 17.1 or on the side of the second valve body part 17.2, a recess space is correspondingly released for the insertion of the spacer element 21 on the side of the third valve body part 18.1 or on the side of the fourth valve body part 18.2.

The sealing of the fifth and sixth valve body seats 20.5, 20.6 prevents leakage at the input pressure port 13 or 14 and reduces overall leakage.

List of reference numerals

1. First control pressure line

2. Second control pressure line

10. Shuttle valve

10.1, 10.2 Shuttle valve

11. First input pressure interface

12. Second input pressure interface

13. Third input pressure interface

14. Fourth input pressure interface

15. First output pressure interface

16. Second output pressure interface

17. First valve body

17.1 First valve body part

17.2 Second valve body part

18. Second valve body

18.1 A third valve body part

18.2 Fourth valve body part

19. Coupling element

20.1 First valve seat

20.2 Second valve seat

20.3 Third valve seat

20.4 Fourth valve seat

20.5 Fifth valve seat

20.6 Sixth valve seat

21. Spacing element

30. Reversing slide valve module

31. First reversing valve

32. Second reversing valve

33. Electromagnet

34. Reversing valve piston

35. Reset spring

40. 40' Jar

41. Piston chamber

42. Piston

43. Piston spring

A1 First side of the first valve body

A2 Second side of the first valve body

B1 First side of the second valve body

B2 Second side of the second valve body

F1 A first pressure-controlled surface of the first valve body

F2 Second controlled pressure-loaded face of first valve body

F3 Third pressure-controlled surface of second valve body

F4 Fourth pressure-controlled surface of second valve body

Claims (16)

1. Shuttle valve (10) for selecting the maximum pressure in two separate control pressure lines (1, 2), having:

A first input pressure port (11) and a second input pressure port (12) for a first control pressure;

a third inlet pressure connection (13) and a fourth inlet pressure connection (14) for a second control pressure;

A first output pressure port (15) for coupling the first control pressure line (1) and a second output pressure port (16) for coupling the second control pressure line (2);

A first valve body (17) in a connection of a flow guide between a first and a second inlet pressure port (11, 12) on the one hand and the first outlet pressure port (15) on the other hand, and a second valve body (18) between a third and a fourth inlet pressure port (13, 14) on the one hand and the second outlet pressure port (16) on the other hand; wherein,

The first valve body (17) is subjected to a first control pressure from the first inlet pressure connection (11) on a first side (A1), to a first control pressure from the second inlet pressure connection (12) on a second opposite side (A2), and the second valve body (18) is subjected to a second control pressure from the third inlet pressure connection (13) on a first side (B1), to a second control pressure from the fourth inlet pressure connection (14) on a second opposite side (B2); wherein,

The first control pressure acts on a first and a second pressure-controlled surface (F1, F2) of the first valve body (17), respectively, and the second control pressure acts on a third and a fourth pressure-controlled surface (F3, F4) of the second valve body (18), respectively, the first and second pressure-controlled surfaces (F1, F2) being larger than the third and fourth pressure-controlled surfaces (F3, F4), respectively, and the first valve body (17) and the second valve body (18) being positively coupled for mutual displacement.

2. A shuttle valve (10) according to claim 1, wherein a coupling element (19) is provided, which mechanically transmits the movement of the first valve body (17) to the second valve body (18).

3. A shuttle valve (10) according to claim 2, wherein the first valve body (17) is multi-piece having a first valve body portion (17.1) and a second valve body portion (17.2), and the second valve body (18) is multi-piece having a third valve body portion (18.1) and a fourth valve body portion (18.2), and the coupling element (19) is positioned between the first valve body portion (17.1) and the second valve body portion (17.2) and between the third valve body portion (18.1) and the fourth valve body portion (18.2).

4. A shuttle valve (10) according to claim 3, wherein the first valve body portion (17.1) cooperates with the first valve seat (20.1) to form a first enclosed site, the second valve body portion (17.2) cooperates with the second valve seat (20.2) to form a second enclosed site, the third valve body portion (18.1) cooperates with the third valve seat (20.3) to form a third enclosed site, and the fourth valve body portion (18.2) cooperates with the fourth valve seat (20.4) to form a fourth enclosed site.

5. A shuttle valve (10) according to claim 4, wherein the first input pressure port (11) is sealable by means of the first sealing site, the second input pressure port (12) is sealable by means of the second sealing site, the third input pressure port (13) is sealable by means of the third sealing site, and the fourth input pressure port (14) is sealable by means of the fourth sealing site.

6. A shuttle valve (10) according to claim 4 or 5, wherein the third valve body portion (18.1) cooperates with a fifth valve seat (20.5) to form a fifth sealing point, and the fourth valve body portion (18.2) cooperates with a sixth valve seat (20.6) to form a sixth sealing point, and the fifth valve seat (20.5) axially opposes the third valve seat (20.3) and the sixth valve seat (20.6) axially opposes the fourth valve seat (20.4) such that the third input pressure port (13) is sealable by means of the third and fifth sealing points depending on the position of the third valve body portion (18.1) and the fourth input pressure port (14) is sealable by means of the fourth and sixth sealing points depending on the position of the fourth valve body portion (18.2).

7. A shuttle valve (10) according to any of claims 3-6, wherein the first valve body portion (17.1), the coupling element (19) and the second valve body portion (17.2) are arranged one after the other in a first direction, and the third valve body portion (18.1), the coupling element (19) and the fourth valve body portion (18.2) are arranged one after the other in a second direction perpendicular or oblique to the first direction.

8. A shuttle valve (10) according to any of claims 2-7, wherein the coupling element (19) is spherical.

9. A shuttle valve (10) according to any of claims 3 to 8, wherein the valve body portion (17.1, 17.2, 18.1, 18.2) is spherical.

10. A shuttle valve (10) according to any of claims 3 to 9, wherein a spacer element (21) is provided between the coupling element (19) and at least one, more or all valve body parts (17.1, 17.2, 18.1, 18.2), via which spacer element the coupling element (19) is supported on the valve body parts (17.1, 17.2, 18.1, 18.2).

11. A shuttle valve (10) according to claim 10, wherein the spacer element (21) is spherical.

12. A shuttle valve (10) according to any one of claims 2 to 11, wherein the coupling element (19) and the valve body (17, 18), in particular the valve body part (17.1, 17.2, 18.1, 18.2), and in particular one or more spacer elements (21) can freely rest against each other.

13. Reversing slide valve module (30) with two redundant reversing valves (31, 32) and a shuttle valve (10) according to any one of claims 1 to 12, wherein,

Both reversing valves (31, 32) each provide a first control pressure and a second control pressure and are each coupled to the two input pressure connections (11, 12, 13, 14) of the shuttle valve (10) in a pilot control pressure manner.

14. The reversing slide valve module (30) according to claim 13, wherein the reversing valves (31, 32) are each arranged as continuously operable reversing valves with electromagnetic actuating means.

15. The reversing slide valve module (30) according to claim 14, wherein the reversing valves (31, 32) each have an electromagnet (33) as a drive, which moves a reversing valve piston (34) against the force of a return spring (35) of the reversing valve (31, 32).

16. -A pneumatic or hydraulic assembly having a double acting cylinder (40) with a piston chamber (41) and a piston (42) movable in the piston chamber (41);

The pneumatic or hydraulic assembly having a reversing slide valve module (30) according to any one of claims 13 to 15, wherein,

The first outlet pressure connection (15) is connected to the piston chamber (41) on a first side of the piston (42) in a pressure-guided manner, and the second outlet pressure connection (16) is connected to the piston chamber (41) on an opposite second side of the piston (42) in a pressure-guided manner.