Shuttle valve, directional control valve module, and pneumatic or hydraulic assembly

Abstract

The invention relates to a shuttle valve for selecting a maximum pressure in two mutually separate control pressure lines; having a first inlet pressure port and a second inlet pressure port for a first control pressure; having a third inlet pressure port and a fourth inlet pressure port for a second control pressure; having a first outlet pressure port for connecting to the first control pressure line and having a second outlet pressure port for connecting to the second control pressure line; having a first valve element fluidically connected between the first and the second inlet pressure port, on the one hand, and the first outlet pressure port, on the other hand, and having a second valve element between the third and the fourth inlet pressure port, on the one hand, and the second outlet pressure port, on the other hand; wherein the first control pressure from the first inlet pressure port acts on a first side of the first valve element and the first control pressure from the second inlet pressure port acts on a second side, situated opposite said first side, of the first valve element, and the second control pressure from the third inlet pressure port acts on a first side of the second valve element and the second control pressure from the fourth inlet pressure port acts on a second side, situated opposite said first side, of the second valve element; wherein the first control pressure acts on each of a first and a second control-pressure-charged surface of the first valve element, and the second control pressure acts on each of a third and a fourth control-pressure-charged surface of the second valve element, the first and the second control-pressure-charged surface are larger than the third and the fourth control-pressure-charged surface, and the first valve element and the second valve element are positively coupled for conjoint movement.

Description

[0001] The present invention relates to a changeover valve for selecting the maximum pressure in two separate control pressure lines, a directional control module with two redundant directional control valves and a changeover valve, and a pneumatic or hydraulic arrangement with a double-acting cylinder and a directional control module.

[0002] In practice, directional control modules of this type are used with two parallel electro-hydraulic position controllers, each with a continuously actuated directional control valve for controlling a single-acting cylinder. A corresponding hydraulic arrangement is shown in the Figure 1The first directional control valve 31 provides a first control pressure at an inlet pressure port 11 of the changeover valve 10, and the second directional control valve 32 provides the first control pressure redundantly at an inlet pressure port 13 of the changeover valve 10. The changeover valve 10 combines the two applied control pressures of the directional control valves 31 and 32 into a common control pressure line 1 via a maximum selector, with the control pressure line 1 being connected to the single-acting cylinder 40' to supply the piston chamber 41 with the 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.

[0003] This allows the cylinder 40, which is equipped with a position sensor, for example, to be positioned steplessly and practically without hysteresis using spring return.

[0004] Due to the provision of two directional control valves 31, 32, a redundant control system with two actuator outputs acting on a common output is created. In the event of a fault, a defective directional control valve 31, 32 or a component associated with the directional control valve 31, 32, such as a pressure gauge or pressure transmitter, can be replaced with a spare device during operation of the hydraulic system.

[0005] If the two directional control valves 31, 32 are set to the same transfer function, for example, by two actuator outputs of a higher-level, redundant control system defining the setpoints for the directional control valves 31, 32, then, as a result of a failure of one of the two directional control valves 31, 32, for example, due to a broken wire in the contained electromagnetic actuator, the actuating force of the directional control valve 31, 32 becomes zero, and the return spring 35 of the corresponding directional control valve 31, 32 pushes the directional control valve piston 34 into the relief position, so that the corresponding inlet pressure port 11, 13 of the changeover valve 10 is switched "to tank," that is, connected to the tank port T of the directional control valve 31, 32. The valve body 17 of the changeover valve 10 automatically closes the inlet pressure port 11, 13 to which the faulty directional control valve 31, 32 is connected.The other directional control valve 31, 32 automatically takes over the control pressure regulation in the control pressure line 1, so that operation continues. A pressure gauge or pressure transmitter on the defective directional control valve 31, 32 indicates the pressure at the tank return line, in particular 0 bar, and after closing a corresponding ball valve of the pressure supply (P1 or P2), the defective directional control valve 31, 32 can be removed and replaced during operation.

[0006] If such a directional control module 30, as it is in the Figure 1 As shown, if the operation with a double-acting cylinder 40 were extended by providing two changeover valves 10.1, 10.2, the following would result: Figure 2 The hydraulic arrangement shown is shown. The corresponding components are identified by their respective reference symbols as in the Figure 1If a directional control valve 31, 32 fails, the full supply pressure P acts on the connected changeover valve 10.1, 10.2 and thus on the side of piston 42 of cylinder 40 connected via the first control pressure line 1 or second control pressure line 2. Piston 42 would always move to the corresponding end position. The second, still functional directional control valve 31, 32 would have no way of maintaining the position of piston 42 and thus the function of cylinder 40. The maximum pressure P of the defective directional control valve 31, 32 always prevails.

[0007] The hydraulic system could only be restored to function if the supply pressure P at the failed directional control valve 31, 32 were manually shut off, for example via a ball valve. This functional limitation is disadvantageous in practice, where highly available systems are required.

[0008] EP 1 953 431 A2 discloses another known changeover valve.

[0009] The present invention is based on the objective of providing a changeover valve, a directional control module with such a changeover valve and a pneumatic or hydraulic arrangement with such a directional control module, which can maintain the full function of an actuator, in particular a cylinder, under control pressure even in the event of a directional control valve failure.

[0010] The problem according to the invention is solved by a changeover valve with the features of claim 1. The dependent claims describe particularly advantageous embodiments of the invention, as well as a directional control valve module according to the invention and a pneumatic or hydraulic arrangement according to the invention.

[0011] A changeover valve according to the invention for selecting the maximum pressure in two separate control pressure lines, such as those used for controlling one or more actuators, in particular a double-acting cylinder, has a first inlet pressure port and a second inlet pressure port for a first control pressure. Furthermore, a third inlet pressure port and a fourth inlet pressure port are provided for a second control pressure. The first control pressure can be greater or less than the second control pressure, at least temporarily. The two control pressures are, in particular, those pressures that are to be supplied as control pressures to, for example, a double-acting cylinder: the first control pressure on a first side of the cylinder piston and the second control pressure on a second, opposite side of the cylinder piston.However, the changeover valve according to the invention is also applicable to actuators other than cylinders.

[0012] The changeover valve according to the invention has a first outlet pressure port for connecting the first control pressure line and a second outlet pressure port for connecting the second control pressure line, in order to provide one of the two control pressures in the first control pressure line and the other of the two control pressures in the second control pressure line accordingly.

[0013] A first valve body is provided in a flow-conducting connection between the first and second inlet pressure ports on the one hand and the first outlet pressure port on the other, and a second valve body is provided between the third and fourth inlet pressure ports on the one hand and the second outlet pressure port on the other. The first valve body can be pressurized on one side with the first control pressure from the first inlet pressure port and on a second side opposite this with the first control pressure from the second inlet pressure port. The second valve body can be pressurized on one side with the second control pressure from the third inlet pressure port and on a second side opposite this with the second control pressure from the fourth inlet pressure port.

[0014] According to the invention, the first control pressure can act on a first and second pressure-sensitive surface of the first valve body, and the second control pressure can act on a third and fourth pressure-sensitive surface of the second valve body. The first and second pressure-sensitive surfaces are each larger than the third and fourth pressure-sensitive surfaces, and the first and second valve bodies are positively coupled for common displacement. In particular, the first and second pressure-sensitive surfaces are of equal size, and the third and fourth pressure-sensitive surfaces are of equal size.

[0015] Due to the forced coupling and the area ratios (not equal to 1) of the first pressure-actuated surface to the third pressure-actuated surface, and of the second pressure-actuated surface to the fourth pressure-actuated surface, the unimpeded flow of the full supply pressure into the first or second control pressure line is prevented. When two directional control valves are connected to the changeover valve, the functioning directional control valve can retain control and continue to perform its control function.

[0016] Preferably, a coupling element is provided that mechanically transmits a displacement of the first valve body to the second valve body. This allows for a compact design and reliable operation.

[0017] According to a preferred embodiment of the invention, the first valve body is multi-part and comprises a first valve body part and a second valve body part. The second valve body can also be multi-part, with at least a third valve body part and a fourth valve body part. The coupling element can then be positioned between the first valve body part and the second valve body part on the one hand, and between the third valve body part and the fourth valve body part on the other. The valve body parts can freely rest against the coupling element, in particular via an intermediate spacer element, thereby achieving a mechanical positive coupling. This ensures reliable operation with a compact design.

[0018] Particularly preferably, the first valve body part interacts with a first valve seat to form a first sealing point, the second valve body part interacts with a second valve seat to form a second sealing point, the third valve body part interacts with a third valve seat to form a third sealing point, and the fourth valve body part interacts with a fourth valve seat to form a fourth sealing point. Each sealing point can be formed by a valve seat within a common one-piece or multi-piece housing of the changeover valve, with the valve body parts correspondingly bearing against their respective valve seats in the sealing state.

[0019] The first inlet pressure port can be sealed by means of the first sealing point, the second inlet pressure port can be sealed by means of the second sealing point, the third inlet pressure port can be sealed by means of the third sealing point, and the fourth inlet pressure port can be sealed by means of the fourth sealing point. This makes achieving the function of the changeover valve according to the invention particularly simple.

[0020] In order to be able to adequately regulate the pressure in the control pressure lines even in the event of a faulty pressure present in one or two inlet pressure ports, for example due to a failure in an upstream directional control valve, as explained here, and to avoid leaks, the third valve body part can preferably interact with a fifth valve seat to form a fifth sealing point, and the fourth valve body part can interact with a 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 opposite the fourth valve seat in such a way thatthat the third inlet pressure port can be sealed by means of the third sealing point and the fifth sealing point, depending on the position of the third valve body part, and the fourth inlet pressure port can be sealed by means of the fourth sealing point and the sixth sealing point, depending on the position of the fourth valve body part. However, depending on the pressure differential applied across it, the valve body part that is not permanently pressed against the third or fourth valve seat can also assume an intermediate position lifted from the two axially opposite valve seats to which it is assigned.

[0021] To achieve a particularly favorable design, the first valve body part, the coupling element and the second valve body part can be arranged one behind 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 behind the other in a second direction perpendicular or oblique to the first direction.

[0022] According to one embodiment, the coupling element is spherical.

[0023] Additionally or alternatively, the valve body parts can also be spherical.

[0024] If a spacer element is provided between the coupling element and at least one, several or all valve body parts, by means of which the coupling element is supported on the respective valve body part, this spacer element can also be spherical.

[0025] Preferably, the coupling element and the valve bodies, in particular the valve body parts, rest freely against each other, for example via intermediate spacers. Optionally, a preload can be achieved by means of one or more spring elements, in particular compression springs, but this is not mandatory. According to another embodiment, the contact is achieved solely by the pressures applied to the inlet pressure ports.

[0026] A directional control module according to the invention has two redundantly designed directional control valves and a changeover valve of the type shown here, wherein the two directional control valves each provide the first control pressure and the second control pressure and are connected in a control pressure-conducting manner to two input pressure ports each, namely the first directional control valve to the first and the third input pressure port and the second directional control valve to the second and the fourth input pressure port of the changeover valve.

[0027] Preferably, the directional control valves are designed as continuously actuated directional control valves with electromagnetic actuation.

[0028] In particular, the directional control valves each have an electromagnet as a drive, which moves a valve piston against the force of a return spring of the directional control valve.

[0029] A pneumatic or hydraulic arrangement according to the invention with a double-acting cylinder comprising a piston chamber and a piston displaceable in the piston chamber is provided with a directional control module of the type shown, wherein the first output pressure port on a first side of the piston is connected to the piston chamber via the first control pressure line and the second output pressure port on an opposite second side of the piston is connected to the piston chamber via the second control pressure line.

[0030] For the operation of the directional control module according to the invention, electrical and hydraulic auxiliary power can be provided. All electrical controllers and circuits necessary for the operation of the directional control module can be provided in an associated control solenoid or control solenoid device, which is hydraulically and electrically connected to the directional control valves on the input side. When the double-acting cylinder is actuated, all control loop parameters and the parameters for scaling the piston position or piston rod position can be set at the control solenoid using potentiometers and / or software in the case of digital control electronics.

[0031] The invention will be explained below with reference to two exemplary embodiments and the Figures 3 and 4 will be described using examples.

[0032] They show: Figure 1 shows a hydraulic arrangement with a directional control module according to the prior art; Figure 2 shows a hydraulic arrangement with a directional control module in a logical extension of the directional control module from the Figure 1 for controlling a double-acting cylinder; Figure 3 shows a first embodiment of a pneumatic or hydraulic arrangement according to the invention with a directional control module according to the invention and a changeover valve according to the invention; Figure 4 shows a second embodiment of a changeover valve according to the invention, as it is used, for example, in the pneumatic or hydraulic arrangement in the Figure 3 can be used.

[0033] The Figure 3Figure 1 shows a pneumatic or hydraulic arrangement according to the invention with a double-acting cylinder 40, which has a piston chamber 41 and a piston 42 that is displaceable within the piston chamber 41. On a first axial side, the piston 42 is subjected to the control pressure from the first control pressure line 1, which opens into the piston chamber 41, and on a second axial side, opposite the first axial 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 set by a directional control module 30, which comprises a changeover valve 10 and two directional control valves 31 and 32.

[0034] The changeover valve 10 has a first inlet pressure port 11 and a second inlet pressure port 12 for a first pilot pressure. The first pilot pressure is provided at the first inlet pressure port 11 by the first directional control valve 31, and the first pilot pressure is redundantly provided at the second inlet pressure port 12 by the second directional control valve 32. The changeover valve 10 further has a third inlet pressure port 13 and a fourth inlet pressure port 14 for a second pilot pressure, wherein the second pilot pressure is provided at the third inlet pressure port 13 by the first directional control valve 31 and at the fourth inlet pressure port 14 by the second directional control valve 32.

[0035] The changeover valve has a first outlet pressure port 15 to which the first control pressure line 1 is connected, and a second outlet pressure port 16 to which the second control pressure line 2 is connected.

[0036] A first valve body 17 is arranged in a flow-conducting 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. A second valve body 18 is arranged between the third and fourth inlet pressure ports 13, 14 on the one hand and the second outlet pressure port 16 on the other. The first valve body 17 is accordingly subjected on a first side A1 to the first control pressure from the first inlet pressure port 11 and on a second side A2 opposite to this to the first control pressure from the second inlet pressure port 12. The second valve body 18 is subjected on a first side B1 to the second control pressure from the third inlet pressure port 13 and on a second side B2 opposite to this to the second control pressure from the fourth inlet pressure port 14.

[0037] The first control pressure acts on the first and second control pressure-bearing surfaces F1 and F2 of the first valve body 17, and the second control pressure acts on the third and fourth control pressure-bearing surfaces F3 and F4 of the second valve body 18. The two valve bodies 17 and 18 each determine the maximum pressure applied to the control pressures acting upon them. The first surface F1 and the second surface F2 are each larger than the third surface F3 and the fourth surface F4. Furthermore, the two valve bodies 17 and 18 are mechanically coupled to each other such that they always move together to either fully or partially seal or open the first and third inlet pressure ports 11 and 13, or the second and fourth inlet pressure ports 12 and 14. For this purpose, the two valve bodies 17 and 18 are coupled to each other via a coupling element 19.

[0038] To seal the inlet pressure ports 11, 12, 13, 14, the first valve body 17 interacts with a first valve seat 20.1 and a second valve seat 20.2 to seal either the first inlet pressure port 11 or the second inlet pressure port 12. The second valve body 18 interacts with a third valve seat 20.3 and a fourth valve seat 20.4 to seal either the third inlet pressure port 13 or the fourth inlet pressure port 14.

[0039] The first directional control valve 31 and the second directional control valve 32 each have an electromagnet 33 as an actuator and a directional control valve piston 34, which is moved by the electromagnet 33 against the force of a return spring 35, depending on the control current of the manipulated variable applied to the electromagnet 33, for example in the range of 4 to 20 mA.

[0040] As long as the directional control module 30 is functioning correctly, the same control pressures are present at the inlet pressure ports 11 and 12 and at the inlet pressure ports 13 and 14, namely the first control pressure at inlet pressure ports 11 and 12 and the second control pressure at inlet pressure ports 13 and 14. The valve bodies 17, 18 are in a neutral position, so that the first control pressure is present in the first control pressure line 1 and the second control pressure is present in the second control pressure line 2.

[0041] If, for example, the second directional control valve 32 fails, its return spring 35 pushes the directional control valve piston 34 into the zero position and connects the pressure port P to the fourth inlet pressure port 14. The second inlet pressure port 12 is connected to the tank port T of the second directional control valve 32. Since the first valve body 17 has larger pressure-sensitive areas F1, F2 than the second valve body 18, the first valve body 17 forces the second valve body 18 into the fourth valve seat 20.4, thus sealing the fourth inlet pressure port 14. The full control pressure P, which is forcibly applied to the fourth inlet pressure port 14, cannot reach the piston chamber 41. The changeover valve 10, together with the first valve body 17, can independently control or maintain the control pressures in the first control pressure line 1 and the second control pressure line 2.

[0042] If, in the other case, the first directional control valve 31 fails, its return spring 35 pushes its directional control valve piston 34 into the zero position and connects its pressure port P to the third inlet pressure port 13. The tank port T of the first directional control valve 31 is connected to the first inlet pressure port 11. Since the first valve body 17 has larger areas F1, F1 for the applied control pressures than the second valve body 18, 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 port P on the first directional control valve 31 cannot propagate into the rod-side piston chamber 41. The second directional control valve 32 assumes control and solely regulates the control pressures in the first control pressure line 1 and the second control pressure line 2.

[0043] Since in practice the in the Figure 3The solution shown, with a connection of the two valve bodies 17, 18 via a rod or the like, requires a comparatively complicated seal, according to the Figure 4An improved embodiment of the changeover valve 10 is proposed in this respect. In this embodiment, the first valve body 17 and the second valve body 18 each have several valve body parts, namely the first valve body 17 the first valve body part 17.1 and the second valve body part 17.2, and the second valve body 18 the third valve body part 18.1 and the 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 behind 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 behind the other.2 are arranged one behind the other in a second direction, with the second direction being perpendicular or oblique to the first direction.

[0044] In the illustrated embodiment, the valve body parts 17.1, 17.2, 18.1, 18.2 do not lie directly against the coupling element 19, but via intermediate spacer elements 21.

[0045] For example, all valve body parts 17.1, 17.2, 18.1, 18.2, the spacer elements 21 and the coupling element 19 are spherical. However, other shapes are also possible, in particular a cylindrical shape or even an angular shape.

[0046] The first valve body part 17.1, together with the first valve seat 20.1, seals the first inlet pressure port 11; the second valve body part 17.2, together with the second valve seat 20.2, seals the second inlet pressure port 12; the third valve body part 18.1, together with the third valve seat 20.3, seals the third inlet pressure port 13; and the fourth valve body part 18.2, together with the fourth valve seat 20.4, seals the fourth inlet pressure port 14, provided that corresponding pressure conditions are present at the inlet pressure ports 11, 12, 13, and 14.

[0047] Due to the size of the valve body parts 17.1, 17.2, 18.1, 18.2, the first valve body 17, which includes the valve body parts 17.1, 17.2, has larger control pressure-actuated areas F1, F2 than the second valve body 18 with the valve body parts 18.1, 18.2, which have the control pressure-actuated areas F3 and F4.

[0048] If, due to a sufficiently high control pressure at the first inlet pressure port 11, the first valve body part 17.1 displaces the coupling element 19 and the second valve body part 17.2 via the spacer elements 21, so that the second valve body part 17.2 is pressed into the second valve seat 20.2, then the fourth valve body part 18.2 is simultaneously pressed into the fourth valve seat 20.4 via the coupling element 19, whereas the pressure at the third inlet pressure port 13 lifts the third valve body part 18.1 from the third valve seat 20.3. This is analogous to the illustration in the Figure 3the control of the control pressures in the control pressure lines 1 and 2, which are connected accordingly to the changeover valve 10, is achieved such 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 inlet pressure ports 11, 12 and 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 inlet pressure ports 13, 14.

[0049] Preferably, fifth and sixth valve seats 20.5 and 20.6 are provided for the third and fourth valve body parts 18.1 and 18.2 to seal the third inlet pressure port 13 and the fourth inlet pressure port 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 seat 20.3 due to the pressure at the third inlet pressure port 13, the third valve body part 18.1, together with the fifth valve body seat 20.5, seals the third inlet pressure port 13, 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, together with the sixth valve body seat 20.6, seals the third inlet pressure port 13.6 seals the fourth inlet pressure port 14, each in the position of the coupling element 19, in which such lifting of the valve body parts 18.1, 18.2 from the respective valve seat 20.3, 20.4 is released and with a sufficient pressure difference across the respective valve body part 18.1, 18.2. In a space to 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 space for the immersion of the spacer element 21 to the side of the third valve body part 18.1 or the fourth valve body part 18.2 is released.

[0050] Sealing at the fifth and sixth valve body seats 20.5, 20.6 can prevent leakage at the inlet pressure ports 13 and 14 respectively and reduce the overall leakage. Reference symbol list

[0051] 1 First control pressure line 2 Second control pressure line 10 Changeover valve 10.1, 10.2 Changeover valve 11 First inlet pressure port 12 Second inlet pressure port 13 Third inlet pressure port 14 Fourth inlet pressure port 15 First outlet pressure port 16 Second outlet pressure port 17 First valve body 17.1 First valve body part 17.2 Second valve body part 18 Second valve body 18.1 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 spacer element 30 directional control module 31 first directional control valve 32 second directional control valve 33 solenoid 34 directional control valve piston 35 return spring 40, 40' cylinder 41 piston chamber 42 piston 43 piston spring A1 first side of first valve body A2 second side of first valve body B1 first side of second valve body B2 second side of second valve body F1 first control pressure-bearing surface of first valve body F2 second control pressure-bearing surface of first valve body F3 third control pressure-bearing surface of second valve body F4 fourth control pressure-bearing surface of second valve body.

Claims

1. Shuttle valve (10) for maximum pressure selection in two separate control pressure lines (1, 2); with a first inlet pressure connection (11) and a second inlet pressure connection (12) for a first control pressure; with a third inlet pressure connection (13) and a fourth inlet pressure connection (14) for a second control pressure; with a first outlet pressure connection (15) for connecting the first control pressure line (1) and a second outlet pressure connection (16) for connecting the second control pressure line (2); with a first valve body (17) in a flow-conducting connection between the first and the second inlet pressure connection (11, 12) on the one hand and the first outlet pressure connection (15) on the other hand and with a second valve body (18) between the third and the fourth inlet pressure connection (13, 14) on the one hand and the second outlet pressure connection (16) on the other hand; wherein the first valve body (17) can be subjected to the first control pressure from the first inlet pressure connection (11) on a first side (A1) and can be subjected to the first control pressure from the second inlet pressure connection (12) on a second side (A2) opposite thereto, and the second valve body (18) can be subjected to the second control pressure from the third inlet pressure connection (13) on a first side (B1) and can be subjected to the second control pressure from the fourth inlet pressure connection (14) on a second side (B2) opposite thereto; wherein the first control pressure can act in each case on a first and second control-pressure-loaded surface (F1, F2) of the first valve body (17) and the second control pressure can act in each case on a third and fourth control-pressure-loaded surface (F3, F4) of the second valve body (18), the first and second areas (F1, F2) subject to control pressure are each larger than the third and fourth areas (F3, F4) subject to control pressure and the first valve body (17) and the second valve body (18) are positively coupled for joint displacement.

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

3. Shuttle valve (10) according to claim 2, wherein the first valve body (17) is multi-part, with a first valve body part (17.1) and a second valve body part (17.2), and the second valve body (18) is multi-part, with a third valve body part (18.1) and a fourth valve body part (18.2), and 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).

4. A shuttle valve (10) according to claim 3, wherein the first valve body part (17.1) co-operates with a first valve seat (20.1) to form a first sealing point, the second valve body part (17.2) co-operates with a second valve seat (20.2) to form a second sealing point, the third valve body part (18.1) co-operates with a third valve seat (20.3) to form a third sealing point, and the fourth valve body part (18.2) co-operates with a fourth valve seat (20.4) to form a fourth sealing point.

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

6. Shuttle valve (10) according to claims 4 or 5, wherein the third valve body part (18.1) co-operates with a fifth valve seat (20.5), to form a fifth sealing point, and the fourth valve body part (18.2) co-operates with a sixth valve seat (20.6) to form a sixth sealing point, and the fifth valve seat (20.5) is axially opposite the third valve seat (20.3) and the sixth valve seat (20.6) is axially opposite the fourth valve seat (20.4) in such a way that the third inlet pressure connection (13) can be sealed by means of the third sealing point and by means of the fifth sealing point depending on the position of the third valve body part (18.1) and the fourth inlet pressure connection (14) can be sealed by means of the fourth sealing point and by means of the sixth sealing point depending on the position of the fourth valve body part (18.2).

7. Shuttle valve (10) according to one of claims 3 to 6, wherein the first valve body part (17.1), the coupling element (19) and the second valve body part (17.2) are arranged one behind 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 behind the other in a second direction perpendicular or oblique to the first direction.

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

9. Shuttle valve (10) according to any one of claims 3 to 8, wherein the valve body parts (17.1, 17.2, 18.1, 18.2) are spherical.

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

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

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

13. Spool valve module (30) with two redundant directional control valves (31, 32) and a shuttle valve (10) according to one of claims 1 to 12, wherein the two directional control valves (31, 32) each provide the first control pressure and the second control pressure and are connected to two inlet pressure connections (11, 12, 13, 14) of the shuttle valve (10) in a control pressure-conducting manner.

14. Directional spool valve module (30) according to claim 13, wherein the directional control valves (31, 32) are each arranged as a continuously actuable directional control valve with electromagnetic actuation.

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

16. Pneumatic or hydraulic arrangement having a double-acting cylinder (40) which has a piston chamber (41) and a piston (42) which can be displaced in the piston chamber (41), with a directional spool valve module (30) according to one of claims 13 to 15, wherein the first outlet pressure connection (15) is connected to the piston chamber (41) in a pressure-conducting manner on a first side of the piston (42) and the second outlet pressure connection (16) is connected to the piston chamber (41) in a pressure-conducting manner on an opposite second side of the piston (42).

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