Stop valve, pressure medium system and rail vehicle

Abstract

Pressure medium system for a pressure medium system of a rail vehicle, pressure medium system for a rail vehicle and rail vehicle. The invention relates to a shut-off valve (100) for a pressure medium system (10) of a rail vehicle (1), having a first connection section (I) for conducting a pressure medium into and / or out of the shut-off valve (100), a second connection section (II) which is fluidically connected to the first connection section (I) for conducting the pressure medium out of and / or into the shut-off valve (100), a control piston (130) which is movable in the interior of the shut-off valve (100) and which comprises a first piston side (130a) and an opposite second piston side (130b), a section (151) which is configured as a piston seat or a piston receptacle between the first connection section (I) and the second connection section (II), on which the first piston side (130a) of the control piston (130) is sealingly placed in a closed position or into which a section with the first piston side (130a) of the control piston (130) is sealingly received in a closed position, such that the first piston side or the section with the first piston side (130a) interrupts the fluid connection between the first connection section (I) and the second connection section (II) and in an open position the first piston side or the section with the first piston side is lifted from the piston seat or the piston receptacle and allows the connection.

Description

Technical Field

[0001] The present invention relates to a pressure medium system for a rail vehicle, a pressure medium system for a rail vehicle including such a shut-off valve, and a rail vehicle including a corresponding pressure medium system. Background Technology

[0002] For pressure medium consumers in rail vehicles, such as braking systems, or even buffer devices, lavatories, door operating devices, and the like, hose connectors can be used to transmit the pressure medium, through which the pipelines of one rail vehicle car can be connected to the next. In the event of a breakage or other damage to the hose connector, it must be ensured that the pressure medium in the pipelines connected to it is not discharged uncontrollably. Therefore, the compressed air supply for the braking system of rail vehicles, as is known in the prior art, uses a safety device comprising two hose connectors in case of hose connector failure. The two hose connectors of this redundancy-based safety device are connected to the corresponding compressed air lines using double check valves. In the event of failure of one of the two hose connectors, the exhaust path through the double check valves is now blocked.

[0003] The disadvantages here include the necessity of two hose connectors and the requirement for a bidirectional check valve with a relatively large cross-section. Furthermore, the use of a bidirectional check valve creates an overlap area where all connections are made, resulting in high sensitivity for switching even with an unsealed hose connector, and consequently, potentially relatively slow switching characteristics. Summary of the Invention

[0004] In view of the above embodiments, the object of the present invention is to provide a shut-off valve for a pressure medium system, a pressure medium system including such a shut-off valve, and a corresponding rail vehicle, wherein pipeline interlocking can be achieved in a compact structure.

[0005] This task is solved by the shut-off valve according to the present invention, the pressure medium system according to the present invention, and the rail vehicle according to the present invention.

[0006] According to the present invention, a shut-off valve for a pressure medium system of a rail vehicle comprises: a first connecting section for introducing and / or exporting pressure medium into or from the shut-off valve; a second connecting section fluidly connected to the first connecting section for exporting and / or importing pressure medium into or from the shut-off valve; a control piston movable within the shut-off valve, including a first piston side and an opposite second piston side; and a section between the first and second connecting sections configured as a piston seat or piston receiving portion. The first piston side of the control piston can be sealed on the piston seat in the closed position, or the section of the control piston having the first piston side can be sealed in the piston receiving portion in the closed position, thereby disconnecting the fluid connection between the first and second connecting sections, and in the open position, lifting the first piston side or the section having the first piston side from the piston seat or piston receiving portion and allowing the connection.

[0007] Therefore, the pressure medium introduced through the first connecting section can be discharged from the second connecting section and vice versa via a fluid connection between the first and second connecting sections. This fluid connection is disconnectable, corresponding to the movement of the control piston to the closed position. The control piston can thus divide the volume disposed in the shut-off valve between the first and second connecting sections into a first pressure medium receiving volume connecting the first connecting section and a second pressure medium receiving volume connecting the second connecting section.

[0008] In a configuration where the section between the first and second connecting sections is configured as a piston seat, a valve disc is formed by a control piston through a first piston side and a second piston side, wherein the fluid connection is disconnected when the first piston side is placed on the piston seat. This configuration can also be referred to as a seat valve configuration. In an alternative configuration where the section between the first and second connecting sections is configured as a piston receiving portion, the control piston functions as a spool valve piston, wherein an end section having the first piston side is received in the piston receiving portion to disconnect the fluid connection. This configuration can also be referred to as a spool valve piston configuration. The seat valve configuration differs from the spool valve piston configuration in that the disconnection of the fluid connection between the first and second connecting sections is achieved by an axial seal between the first piston side and the piston seat about the longitudinal axis of the control piston, which corresponds to the extension direction of the control piston from the first piston side to the second piston side. In contrast, a radial seal is achieved in the closed position in the spool valve piston configuration.

[0009] Therefore, according to the above embodiment, the first piston side is the side facing the section between the first and second connecting sections, and the second piston side is the side facing away from said section. This need not be considered when assigning the first and second piston sides with respect to the section, as long as the control piston also has a control piston pin, which will be described later.

[0010] During normal operation of the pressurized medium transport, the same pressure exists in both connection sections. The shut-off valve is configured such that the control piston is in the open position. This can be achieved, for example, by setting the pressure acting on the first piston side during normal operation, or the resulting pressure, greater than the reaction force caused by the weight of the control piston. This force involves a force component that acts along the direction of movement of the control piston to disconnect or open the fluid connection. The reaction force of the control piston by its own weight acts in the direction of the closed position. Alternatively or supplementarily, the control piston can also be held in the open position by other mechanisms, such as by applying a magnetic force or a mechanical retaining element, wherein the retaining can be released to reach the closed position.

[0011] When the pressure drops in the second connection section, for example, when the hose connector connected thereto fails, the pressure acting on the first piston side suddenly decreases. This causes the control piston to move to the closed position. This can be achieved via the reaction force caused by the weight of the control piston, as exemplified above with respect to the simple design of the shut-off valve. The movement of the control piston to the closed position is therefore automatic in this case when the corresponding pressure drops. The feasibility of other designs for the automatic movement of the control piston to the closed position is then explained with respect to the corresponding design and further configuration, wherein these designs and further configurations are not mutually exclusive and can also be used in combination with each other. This also relates to the automatic movement of the control piston to the open position, as will also be explained with reference to other designs. Instead of or supplementing the automatic movement, a drive mechanism for moving the control piston can also be provided, wherein these drive mechanisms are then operated by the detected pressure drop to move the control piston to the closed and / or open position.

[0012] In one design, the pressure medium is compressed air.

[0013] Compressed air is often used due to its simple availability. However, the pressure medium can also be a liquid in a hydraulic system.

[0014] In a further configuration, the control piston is supported by a spring elastic element, the spring force of which acts in the direction of the open position.

[0015] The spring-elastic element can induce or assist in the movement of the control piston to the open position. As long as the spring force is less than the reaction force caused by the weight of the control piston, further pressure loading on the first piston side is required to move the control piston to the open position. Conversely, a spring force larger than the reaction force caused by the weight of the control piston requires additional pressure loading on the second piston side, as will be further explained, and / or requires an additional motion mechanism to overcome the spring force for moving the control piston to the closed position. That is, through the spring-elastic element, the control piston can automatically or at least in conjunction with minimum pressure on the second connection section move to the open position or remain there to provide or maintain fluid connection.

[0016] The spring-elastic element can be disposed, for example, between the first piston side and the second connecting section. The spring-elastic element is thus supported on the second connecting section and allows the control piston to move relative to the second connecting section along the extension direction of the spring-elastic element or the direction of the spring force, which points along the longitudinal axis of the control piston. As the spring-elastic element, a compression spring can be used, for example, in the arrangement on the first piston side. Alternatively or supplementarily, a tension spring can also be used, in which case it can be disposed on the second piston side.

[0017] Alternatively, the spring-elastic element can also act in the direction of the closed position. This, for example, can ensure or at least assist in a reliable seal to ensure the disconnection of the fluid connection between the first and second connecting sections. In the arrangement of the spring-elastic element between the first piston side and the second connecting section, as described above, the spring-elastic element can then be implemented, for example, as a tension spring. A similar effect can also be achieved by using a compression spring, wherein this compression spring is located on the second piston side.

[0018] According to one design, the shut-off valve is equipped with a radial guide, such that the control piston is guided at least partially radially within the shut-off valve about its longitudinal axis during movement between open and closed positions, the longitudinal axis corresponding to the direction of extension of the control piston from a first piston side to a second piston side.

[0019] Therefore, the axial movement of the control piston about the longitudinal axis of the control piston between the open and closed positions is guided by the radial surface segment.

[0020] In particular, the at least partial radial guidance of the control piston is carried out in conjunction with the housing section of the shut-off valve by a radially planar section of the control piston about the longitudinal axis between the first piston side and the second piston side.

[0021] Therefore, the piston can be guided without the need for other guiding elements.

[0022] Alternatively or additionally, the control piston has a control piston pin on the side facing the second connecting section, the control piston pin extending into the piston seat or piston receiving portion and being at least partially guided by a guide element in conjunction with at least one section of the piston seat or piston receiving portion facing the inner surface of the control piston pin as the control piston moves between the open and closed positions in the direction of the longitudinal axis.

[0023] The control piston pin therefore extends from the first piston side. In particular, by combining radial guidance via a radially spaced surface section between the first and second piston sides, and in conjunction with the housing section of the shut-off valve, tilting or misalignment of the control piston can be prevented or the corresponding risks minimized. Such tilting or misalignment can impede the movement of the control piston and / or also result in a lack of seal when the fluid connection is broken.

[0024] In a further configuration, a space is provided on the second piston side of the shut-off valve, the space being in fluid connection with the first connection section, so as to transmit the corresponding pressure to the second piston side of the control piston.

[0025] A pressure medium flowing through or residing in the first connecting section can be supplied to the space via a fluid connection between the first connecting section and the space on the second piston side. The outlet of the pressure medium can also be achieved. The space here forms a third pressure medium receiving volume. The fluid connection can be configured such that the dominant pressure on the second piston side in the space directly corresponds to the pressure of the first pressure medium receiving volume. Alternatively, the pressure of the first pressure medium receiving volume can be proportionally transmitted to the space or the third pressure medium receiving volume via the fluid connection through a pressure reducer or similar pressure regulating element. Similar to the direct or proportional pressure transmission between the first and third pressure medium receiving volumes, the space on the second piston side can similarly directly or proportionally transmit the dominant pressure there to the second piston side controlling the piston. The corresponding proportional pressure transmission thus corresponds to indirect pressure transmission. However, the indirect pressure transmission is not limited to proportional pressure transmission, but can also transmit the same pressure as in the first pressure medium receiving volume, wherein the conceptual indirect transmission involves the components involved in the pressure transmission.

[0026] Instead of forming the space by receiving a volume through a third pressure medium on the second piston side, the space can also be formed or surrounded by a volume receiving a first pressure medium on the second piston side.

[0027] Because the second piston side is the side of the section opposite to the piston seat or piston receiving portion of the control piston, the control piston can be moved to and / or held in the closed position by pressure in the space on the second piston side. For example, when the pressure transmitted to the second piston side through the space decreases on the first piston side, the control piston can be moved toward the piston seat or piston receiving portion to the closed position. When the fluid connection between the first and second connecting sections is broken by reaching the closed position, the pressure in the space on the second piston side can further act on the control piston and hold it in the closed position. The holding force for holding the control piston in the closed position, determined by the pressure in the space on the second piston side, can be reduced or eliminated as needed, for example, by venting, as reconsidered later, thereby avoiding, for example, looseness due to vibration. The use of the concept of "venting" is not limited to compressed air as the pressure medium; when using a liquid as the pressure medium, it also includes the desorption of such liquid for pressure reduction.

[0028] In particular, the fluid connection configured in this way between the space on the first connecting section and the second piston side causes pressure compensation for the time delay between the first connecting section and the space. In a preferred embodiment, the fluid connection is configured as a nozzle.

[0029] The fluid connection between the first and second connecting sections can cause a pressure drop in the second connecting section, and perhaps also a pressure drop in the first pressure medium receiving volume. By compensating for the pressure delay between the space on the first connecting section and the second piston side, or between the first and third pressure medium receiving volumes, a sufficiently high pressure can be applied to the space on the second piston side to move the control piston to the closed position. Even if the pressure between the space on the first connecting section and the second piston side subsequently equalizes, the control piston can remain in the closed position because the pressure on the second piston side is further reduced due to the pressure drop relative to the second connecting section.

[0030] Based on the distinguishability of the first and third pressure medium receiving volumes listed above, corresponding configurability becomes apparent through fluid connection via a nozzle or other design for pressure compensation for time delay. In other words, in the exemplary use of the nozzle, the first pressure medium receiving volume is the volume with respect to the nozzle facing the first connection section, and the third pressure receiving volume is the volume in the shut-off valve facing away from the first connection section. The above refers to the one or more volumes that are separated from the second pressure medium receiving volume when the control piston moves to the closed position.

[0031] For example, the nozzle diameter for pressure compensation of the time delay between the space on the first connecting section and the second piston side is 0.5 mm. This diameter is specifically chosen such that it is not so small that the nozzle is less susceptible to clogging by dirt or other particles. The upper limit of the nozzle diameter is coordinated with a sufficient time delay. This coordination is, for example, derived according to the gradient on the second connecting section for insensitivity of <0.5 bar / s, or normal air consumption and sensitivity of >0.65 bar / s. At the sensitivity threshold, the response time is, for example, <2 s. In the event of hose rupture, a significantly higher gradient is assumed because the exhaust cross-section of the separated hose connector is significantly larger. The response time can be correspondingly shortened, wherein the time delay by the coordinated nozzle diameter is sufficient to move the control piston to the closed position. It should be added here that the volume of the space on the second piston side can also affect the pressure compensation of the time delay. Preferably, the volume should be kept as small as possible with respect to the most compact construction.

[0032] In one design, the shut-off valve has a housing section for receiving a control piston and a housing section for at least partially receiving a space on the second piston side.

[0033] The shut-off valve can be modularly constructed by dividing it into at least two housing sections. Thus, for example, it can be achieved in a simple manner by providing different spaces on the second piston side to accommodate varying pressure ratios. Alternatively or supplementarily, different control pistons can also be combined with spaces on the second piston side.

[0034] When using the aforementioned spring-elastic element and the corresponding space, as explained above, in one design, at least the force caused by the weight of the control piston in the direction toward the second connecting section is less than the maximum positional change of the shut-off valve relative to its initial position and the angular change therefrom, which is less than the force of the spring-elastic element in the opposite direction.

[0035] As long as the longitudinal axis of the control piston deviates from its orientation relative to gravity by installation and / or due to the movement of the rail vehicle uphill or downhill, the aforementioned ratio of the spring force to the force caused by the weight of the control piston relates to the expected and therefore predetermined maximum angular range or the corresponding positional change of the shut-off valve relative to the initial position and thereby the angular change, along the piston's movement from the closed position to the open position and in the opposite direction. The initial position here relates to the position of the shut-off valve in a straight travel distance, i.e., a travel distance without uphill or downhill sections. In other words, the relationship between the spring force of the shut-off valve with respect to the spring elastic element and the reaction force caused by the weight of the control piston is configured in particular such that the control piston can automatically move to the open position not only at a predetermined installation angle but also with angular changes within a predetermined range. In the corresponding design, other forces acting on the spring force of the spring elastic element, such as radially guided frictional forces based on the control piston, are considered if necessary. Regarding the straight path, the shut-off valve or control piston is preferably installed such that the longitudinal axis of the control piston is parallel to gravity orientation and the second connecting section is located below the side of the first piston.

[0036] With the above configuration, the control piston can automatically move to the open position after venting from the space on the second piston side or at least after a predetermined pressure reduction in said space. The corresponding venting or pressure reduction can be performed via the first connecting section or another operable pressure relief section, regardless of its association with the aforementioned features.

[0037] For example, when the pressure on the second connecting section first decreases, the control piston moves to the closed position by the combined action of the dominant pressure in the space on the second piston side, opposite to the spring force of the spring elastic element, and the gravity caused by the weight of the control piston itself. If the space on the second piston side is now vented, the force acting on the spring force of the elastic element is reduced so much that the control piston moves to the open position by the spring force.

[0038] In a further configuration, the housing section of the shut-off valve forms a stop for the control piston, the stop restricting the movement of the control piston in a direction away from the second connecting section.

[0039] Therefore, the movement of the control piston in the direction of the open position is limited. To this end, the stroke of the control piston required to reach the closed position can be adjusted, and thus the time required to disconnect the fluid connection between the first and second connecting sections can also be adjusted. Furthermore, the cross-section of the fluid connection can be similarly adjusted to reduce, for example, the effect of pressure medium re-flowing through the second connecting section when the pressure drops in the second connecting section. By limiting the stroke of the control piston, it is possible to further prevent, or at least limit, the disconnection of the fluid connection between the space and the first connecting section if the space is located on the side of the second piston.

[0040] Another aspect of the invention relates to a pressure medium system for a rail vehicle, comprising: a shut-off valve as described above; a hose connector directly or indirectly connected to a second connection section of the shut-off valve; and a pressure medium line directly or indirectly connected to a first connection section, wherein the shut-off valve is configured such that the control piston is automatically movable to a closed position by means of a pressure gradient between the first and second connection sections caused by the failure of the hose connector.

[0041] Exemplarily, the operating principle of the pressure medium system described above is illustrated using a shut-off valve, wherein the space is located on the second piston side of the control piston, and the fluid connection between the space and the first connection section causes time-delayed pressure compensation. During normal operation, i.e., during normal air consumption and flow through the shut-off valve, the pressure in the first connection section or the first pressure medium receiving volume, the pressure in the fluidly connected space on the second piston side or the third pressure medium receiving volume, and the pressure in the second connection section or the second pressure medium receiving volume are the same. When the hose connector breaks, a rapid pressure drop occurs in the second connection section. Therefore, the pressure on the first piston side of the control piston suddenly decreases. Because the pressure in the space on the second piston side can only follow with a time delay, this pressure, and optionally combined with the weight of the control piston, causes the control piston to move to the closed position. While the control piston remains in the closed position, the pressure in the second connection section further decreases to zero due to the broken hose connector. Pressure compensation occurs between the space on the second piston side and the first connection section in parallel with this further pressure reduction in the second connection section. The pressure in the space on the second piston side acts on the second piston side but not on the first piston side where the pressure is released, and keeps the control piston in the closed position.

[0042] According to a further configuration, the pressure medium pipeline has a pressure medium discharge device that is switchable to selectively reduce the medium pressure in the first connection section, and in particular, through the pressure drop associated with this in the first connection section, the control piston of the shut-off valve is automatically movable to the open position.

[0043] The switching of the pressure medium discharge device can be electronically controlled and / or manually operated. In a simple design, a switch (cocktail) can be installed on the pressure medium line. Opening the switch allows venting of the first connection section.

[0044] The automatic movement of the control piston to the open position can be achieved, for example, by reapplying pressure to the first piston side via the second connecting section and / or using the spring-elastic element described above for the shut-off valve. For instance, the spring-elastic element can be used in the configuration of the previously exemplified pressure medium system, where it functions as a pressure spring and acts on the first piston side of the control piston. If the first connecting section or the first pressure medium is now vented, venting of the space on the second piston side is similarly performed. Therefore, there is no longer any pressure reaction acting on the spring-elastic element from the second piston side. If it is assumed that the force acting on the spring force is less than the spring force due to the weight of the control piston, and if necessary considering other reaction forces such as friction, then the control piston can now move from the closed position to the open position via the spring-elastic element.

[0045] In one design, the pressure medium system has a sensor configured such that the triggering of a shut-off valve for controlling the piston to move to the closed position can be monitored via the sensor, particularly via the sensing of the pressure switch in the second connection section and / or the stroke of the control piston.

[0046] The monitoring can, for example, determine whether the control piston has moved to the closed position when the pressure drops in the second connecting section. Alternatively or supplementarily, the monitoring can also be used to determine whether the control piston has moved to the closed position even when there is no pressure drop in the second connecting section. For this purpose, the evaluation logic of the evaluation unit connected to the sensor can be configured such that not only the pressure in the second connecting section but also the position of the control piston according to its stroke sensing is compared. For example, the stroke sensing of the control piston can be performed by a throttle switch or a contactless Hall sensor.

[0047] In another aspect, the present invention relates to a rail vehicle including the above-described pressure medium system, wherein the rail vehicle has at least two cars, each car having at least one pressure medium pipeline, and the respective pressure medium pipeline is used to fluidly connect the end of the pressure medium pipeline of one car to the corresponding end of the pressure medium pipeline of the other car via a respective shut-off valve, the respective pressure medium pipeline being connected to a hose connector, the shut-off valve being disposed particularly close to the hose connector.

[0048] The arrangement of the corresponding shut-off valve sufficiently close to the hose connector involves a maximum distance relative to the hose connector, said maximum distance being such that the pressure drop in the second connection section due to hose connector failure occurs sufficiently rapidly and / or at a sufficient level in terms of the amount of pressure drop. In other words, the corresponding shut-off valve is positioned at a distance relative to the hose connector such that a predetermined throttling of the pressure drop gradient between the hose connector and the second connection section of the corresponding shut-off valve is not exceeded or even completely eliminated due to the stroke length or connection size.

[0049] In particular, the corresponding shut-off valve is positioned between the hose connector and the corresponding consumer in the corresponding compartment. Sufficient proximity to the hose connector is also advantageous here to improve accessibility to the pressure medium outlet device, which, for example, is positioned between the consumer and the shut-off valve. That is, the pressure medium outlet device is located here between the consumer and the corresponding shut-off valve. Attached Figure Description

[0050] The invention will now be further explained with reference to the accompanying drawings. The drawings show in detail: Figure 1 A schematic diagram of a rail vehicle including a pressure medium system is shown, the pressure medium system including a shut-off valve according to an example embodiment of the invention; Figure 2 A schematic cross-sectional view of a shut-off valve according to one example embodiment is shown, the shut-off valve being designed for use with respect to... Figure 1 The pressure medium system of the rail vehicle can be used. Detailed Implementation

[0051] Figure 1A schematic diagram of a rail vehicle 1 including a pressure medium system 10, which includes a shut-off valve 100 according to an exemplary embodiment of the invention, is shown in the figure. Only one car 2 is shown in its entirety and partly, with other cars respectively connectable to it. The pressure medium system 10 of the rail vehicle 1 has a pressure medium line 400 in each car of the car 2. The pressure medium lines 400 of the respective cars 2 are interconnected by hose couplings 200 between the cars 2. The pressure medium used in this embodiment is compressed air. However, according to alternative embodiments, other gaseous media or liquids may also be used. The operating principles described herein for a pneumatic system can be applied to a hydraulic system.

[0052] To lock the corresponding pressure medium line 400 relative to the respective connected hose connectors 200, the pressure medium line 400 has a shut-off valve 100 for each hose connector joint. In an alternative embodiment, only one shut-off valve may be provided for each compartment 2, or, according to another alternative, more than one shut-off valve 100 may be provided for each hose connector joint for redundancy. Figure 1 In the example embodiments shown, the shut-off valves 100 are respectively disposed near the hose connectors 200 to which they are connected. A first connection section I of the respective shut-off valve 100 is connected to the respective pressure medium line 400, and a second connection section II of the respective shut-off valve 100 is connected to the respective hose connector. In the illustrated embodiment, the shut-off valve 100 is not directly connected to the respective hose connector itself, but indirectly through another pressure medium line section, which may be configured to the respective hose connector 200. Alternatively, the shut-off valve 100 may also be directly connected to the hose connector 200 to minimize the distance between the respective shut-off valve 100 and the respective hose connector 200.

[0053] Furthermore, for each shut-off valve 100, the corresponding pressure medium line 400 has a vent switch (vent plug) 300 as a pressure medium discharge device. Through the corresponding vent switch 300, the pressure medium in the corresponding shut-off valve 100 can be discharged, thus reducing the pressure present in or within the first connection section I of the shut-off valve. Even though one vent switch 300 is configured for each shut-off valve 100 here, it is alternatively possible to provide only one vent switch 300 for each compartment 2. For redundancy reasons and / or for venting via multiple operating principles, multiple vent switches 300 or additional pressure medium discharge devices can also be provided for a shut-off valve 100 in another alternative. Regarding the listed operating principles, the vent switch 300 can be opened and closed manually and electrically in the illustrated embodiment. According to an alternative embodiment, the vent switch is operated manually or electrically only. The operating principle here may not only involve manual or electronic operation, but may also involve different mechanisms for opening and closing such pressure medium outlet devices, such as mechanical, pneumatic, hydraulic, electric or magnetic opening and closing mechanisms or combinations thereof.

[0054] Next, refer to Figure 2 The shut-off valve 100 shown in the figure is adjusted according to... Figure 1 A more detailed explanation of the working principle of the pressure medium system 10 of the rail vehicle 1. Figure 2 For this purpose, a schematic cross-sectional view of a shut-off valve 100 according to an example embodiment is shown, the shut-off valve being for use with respect to... Figure 1 The pressure medium system 10 of the rail vehicle 1 can be used. However, the use of the shut-off valve 100 is not limited to this.

[0055] The shut-off valve 100 has a first connection section I and a second connection section II. The first connection section I and the second connection section II are in fluid connection. The fluid connection can be separated in the closed position by a control piston 130. In the illustrated embodiment, the control piston 130 here separates a first pressure medium receiving volume 110 connected to the first connection section I from a second pressure medium receiving volume 120 connected to the second connection section II. The second pressure medium receiving volume 120 is here formed by a piston seat 151, which extends as a cylindrical section from the second connection section II into the shut-off valve 100, the cylindrical section opening on the sides facing and away from the second connection section II, respectively.

[0056] The control piston 130 has a first piston side 130a facing the piston seat 151 and a second piston side 130b opposite to the piston seat 151. The longitudinal axis L of the control piston 130 extends perpendicularly to the piston sides 130a and 130b along its distance direction. The control piston 130 and piston seat 151 are configured as a valve disc, wherein the first piston side 130a is sealed onto the piston seat 151 during movement of the control piston 130 along the longitudinal axis L to the closed position. This sealing is aided by a sealing element 131 axially about the longitudinal axis L. In an alternative embodiment, the control piston 130 may also be configured as a spool piston, wherein the piston section having the first piston side is received into the piston seat 151, which then functions as a piston receiving portion. In this case, the sealing is not axial but radial, acting in conjunction with the radially surrounding inner surface of the piston seat 151. In this alternative, the piston seat 151 is strictly not a piston seat, but rather a piston receiving portion. Based on similar design feasibility, for example through a cylindrical section, an alternative sealing feasibility is illustrated here using only piston seat 151.

[0057] To guide the control piston 130 during movement along the longitudinal axis L, a surface radially surrounding the longitudinal axis L between the first piston side 130a and the second piston side 130b is radially guided within the housing section 150. This guidance prevents pressure medium from flowing from the space 110 on the second piston side 130b, which will be described later. The radial guide surface section between the first piston side 130a and the second piston side 130b has a radial sealing element 132. To prevent tilting or skewing of the control piston during the guidance described above, the control piston 130 further has a control piston pin 130c, which extends from the first piston side 130a along the longitudinal axis L toward the second connecting section II into the piston seat 151 or into the piston seat through an opening formed in the piston seat 151. A guide element 133 is provided on the control piston pin 130c, which extends radially outward about the longitudinal axis L and guides the control piston along the inner wall of the piston seat 151 during axial movement.

[0058] The control piston 130 is further supported here by a pressure spring 140, which serves as a spring-like elastic element. The pressure spring 140 is thus positioned around the piston seat 151 between the first piston side 130a and the end of the piston seat 151 facing the second connecting section II. The spring force of the pressure spring 140 acts in the direction of the longitudinal axis L. In an alternative embodiment, the spring-like elastic element may also be disposed within the section constituting the piston seat 151. In another alternative, multiple spring-like elastic elements may be used instead of a single spring-like elastic element.

[0059] The shut-off valve 100 here also has a space 110, which has been briefly mentioned, on the second piston side 130b. The space 110 This forms a third pressure medium receiving volume. The space 110 Alternatively, the third pressure medium receiving volume is fluidly connected to the first connection section I, or the first pressure medium receiving volume 110, via nozzle 161. In the space 110 Pressure compensation between the first connecting section I and the nozzle 161 is therefore performed with a time delay.

[0060] The space 110 on the second piston side 130b It is formed by a void in the second housing section 160 of the shut-off valve 100. Through the space 110 The second housing section 160 further comprises a stop 162 for controlling the piston 130b, located radially about the longitudinal axis L, or at the end of the sidewall facing the second piston side 130b. This stop correspondingly limits the control piston 130b towards the space 110. The direction of movement. The space 110 An opening is made on the side facing the second piston side 130b, thereby opening in the space 110 The pressure within can be transmitted to the control piston 130 via the second piston side 130b. The second housing section 160 further includes a nozzle 161. The space 110 is divided into a first housing section 150 and a second housing section 160. And / or nozzle 161 can be flexibly adapted by replacing the second housing section.

[0061] Figure 2 Shown in Figure 1 The pressure medium system 10 shown in the diagram has a shut-off valve 100 in normal operation. During normal operation, the pressure medium line 400 is fluidly connected to the hose connector 200 via the shut-off valve 100. The pressure medium is guided through connection section I and connection section II. The first pressure medium receiving volume 110, the second pressure medium receiving volume 120, and the third pressure medium receiving volume, or space 110, are all located within these three sections. The pressure in the space is the same in this state. The control piston 130 is in the open position and is held there by the spring force of the pressure spring 140. If the hose connector 200 breaks, the pressure acting on the first piston side 130a, and the pressure below the control piston 130 in the accompanying drawings, suddenly decreases. However, based on the nozzle 161, in the space 110 The pressure initially remains substantially constant or decreases only slightly, such that the pressure gradient between the second piston side 130b and the first piston side 130a is sufficient to move the control piston 130 toward the piston seat 151 to a closed position, in which the first piston side 130a is sealed onto the piston seat 151. Therefore, the fluid connection between the first connection section I and the second connection section II, and thus with respect to the pressure medium system 10, between the pressure medium line 400 and the hose connector 200, is separated by the control piston 130. Due to the breakage of the hose connector 200, the pressure in the second pressure medium receiving volume drops to zero, and the first pressure medium receiving volume 110 and the third pressure medium receiving volume, or space 110, are separated. The pressure phases within the space are equalized. Following this equalization, in space 110... The dominant pressure keeps the control piston 130 in the closed position. Correspondingly, the pressure spring 140 is configured such that its spring force is less than the sum of the pressure exerted on the second piston side 130b by the pressure in the balanced state and the force exerted by the weight of the control piston 130 in the closing direction. Simultaneously, here, the spring force is greater than the force exerted by the weight of the control piston 130 in the closing direction, so that the automatic movement of the control piston to the open position, as described later, can be achieved.

[0062] To allow the control piston 130 to automatically move from the closed position to the open position, the exhaust switch 300 provided for the corresponding shut-off valve 100 is opened. This allows the first pressure medium receiving volume 110 and the space 110 to... Exhaust is achieved through the first connecting section I. Correspondingly, the pressure acting on the second piston side 130b is released. As mentioned above, because the spring force of the pressure spring 140 is greater than the force exerted by the weight of the control piston 130 in the direction of the closed position, the control piston 130 moves back to the open position via the pressure spring.

[0063] In the illustrated embodiment, the shut-off valve 100 further includes a sensor 170 on the second connection section II. The sensor 170 here functions as a pressure switch and switches when a predetermined pressure drop occurs. The sensor 170 senses the venting of pressure in the second connection section II and thereby indicates venting of the connection towards the pressure medium line 400 and, if necessary, locking. This can be determined by the shut-off valve 100 itself or by the position of the vent switch 300. Furthermore, the pressure switch can sense that the pressure level of the entire pressure medium line 400 is too low. Therefore, the closed shut-off valve can be deduced by ruling out more than two other causes. Thus, the breakage of the hose connector 200 and the predetermined triggering of the shut-off valve 100 can be monitored. In an alternative embodiment, this monitoring can be performed, alternatively or supplementarily, by sensing the stroke of the control piston 130. By sensing the stroke, for example, it can be detected that the control piston 130 is in an open or closed position. Therefore, by sensing the stroke, the meaning of the position of the control piston 130 is directly applicable to the actual triggering of the shut-off valve. By comparing the signal with that of the pressure switch, the appropriate triggering for closure can be determined in the event of a pressure drop or a failure of the shut-off valve 100. A failure exists, for example, in the case where the stroke is sensed and a pressure drop is detected, but the control piston is in the open position, or conversely, the control piston has moved to the closed position, but no pressure drop exists.

[0064] This invention is not limited to the described embodiments. In particular, the described embodiments, designs, and further features can be combined with each other, provided that they are not reasonably excluded from each other.

[0065] List of reference numerals

[0066] 1. Rail vehicles

[0067] 2 carriages

[0068] 10 Compressed air system (pressure medium system)

[0069] 100 shut-off valve

[0070] 110 First compressed air receiving volume (regarding the first pressure medium receiving volume of connecting section I;)

[0071] 110 The third compressed air receiving volume (the third pressure medium receiving volume relative to the first compressed air receiving volume 110)

[0072] 120 Second compressed air receiving volume (regarding the second pressure medium receiving volume of connecting section II)

[0073] 130 Control Piston

[0074] 130a First Piston Side

[0075] 130b Second Piston Side

[0076] 130c Control Piston Pin

[0077] 131 Axial sealing element

[0078] 132 Radial sealing element

[0079] 133 Guiding element

[0080] 140 (Compression) Spring (Spring Elastic Element)

[0081] 150 First housing section (control piston)

[0082] 151 Piston Seat

[0083] 160 Second shell section (third compressed air receiving volume 110) )

[0084] 161 Nozzle

[0085] 162 Control piston stop section

[0086] 170 sensor

[0087] 200 Hose Connector

[0088] 300 Exhaust Switch (Pressure Medium Discharge Device)

[0089] 400 Compressed Air Line (Pressure Medium Line)

[0090] I. First Connecting Section

[0091] II. Second Connecting Section

[0092] L (Longitudinal axis, controlling the piston)

Claims

1. A shut-off valve (100) for a pressure medium system (10) of a rail vehicle (1), the shut-off valve having: The first connection section (I) is used to introduce and / or export pressure media into and / or out of the shut-off valve (100). A second connection section (II) fluidly connected to the first connection section (I) is used to discharge and / or introduce the pressure medium from the shut-off valve (100). A control piston (130) movable within the shut-off valve (100), the control piston comprising a first piston side (130a) and an opposite second piston side (130b), and In the section between the first connecting section (I) and the second connecting section (II), which is configured as a piston seat (151) or piston receiving portion, the first piston side (130a) of the control piston (130) can be sealed on the section in the closed position, or the section of the control piston (130) having the first piston side (130a) can be sealed into the section in the closed position, thereby disconnecting the fluid connection between the first piston side or the section having the first piston side (130a) and the second connecting section (II), and in the open position, the first piston side or the section having the first piston side is lifted from the piston seat or piston receiving portion and the connection is allowed. in, A space (110) is provided on the second piston side (130b) of the shut-off valve (100). The space is in fluid connection with the first connection section (I) so that the corresponding pressure can be transmitted to the second piston side (130b) of the control piston (130), and Among them, in the first connecting section (I) and the space (110) The fluid connection between the two is configured such that the fluid connection causes a fluid connection between the first connection section (I) and the space (110). Pressure compensation for the time delay between the two, so that when the pressure drops on the second connecting section (II), the pressure is compensated through the space (110) on the second piston side (130b). Then apply a sufficiently high pressure to move the control piston (130) to the closed position.

2. The shut-off valve (100) according to claim 1, wherein, The pressure medium is compressed air.

3. The shut-off valve (100) according to claim 1 or 2, wherein, The control piston (130) is supported by a spring elastic element (140), the spring force of which acts in the direction of the open position.

4. The shut-off valve (100) according to claim 1 or 2, wherein, The shut-off valve is equipped with a radial guide, such that the control piston (130) is guided at least partially radially about its longitudinal axis (L) in the shut-off valve (100) during its movement between the open and closed positions, the longitudinal axis corresponding to the direction of extension of the control piston from the first piston side (130a) to the second piston side (130b).

5. The shut-off valve (100) according to claim 4, wherein, The control piston (130) is guided at least partially radially by the interaction of a radially radial surface segment of the control piston (130) between the first piston side (130a) and the second piston side (130b) about the longitudinal axis (L) with the housing segments (150, 160) of the shut-off valve (100).

6. The shut-off valve (100) according to claim 4, wherein, The control piston (130) has a control piston pin (130c) on the side facing the second connecting section (II), the control piston pin extending into the piston seat (151) or piston receiving portion and being at least partially guided by a guide element (133) in conjunction with at least one section of the piston seat (151) or piston receiving portion facing the inner surface of the control piston pin (130c) when the control piston (130) moves between the open and closed positions along the longitudinal axis (L).

7. The shut-off valve (100) according to claim 1 or 2, wherein, In the first connecting section (I) and the space (110) The fluid connection between the nozzle and the ...

8. The shut-off valve (100) according to claim 1 or 2, wherein, The shut-off valve (100) has a first housing section (150) for receiving the control piston (130) and a space (110) for at least partially receiving the control piston on the second piston side (130b). The second shell section (160).

9. The shut-off valve (100) according to claim 3, wherein, The force exerted by the weight of the control piston (130) toward the second connecting section (II) is less than the force exerted by the spring elastic element (140) in the opposite direction, until the maximum positional change and therefore angular change of the shut-off valve (100) relative to its initial position is less than the force exerted by the spring elastic element (140) in the opposite direction.

10. The shut-off valve (100) according to claim 1 or 2, wherein, The housing sections (150, 160) of the shut-off valve (100) form a stop (162) for the control piston (130), which restricts the movement of the control piston (130) in a direction away from the second connecting section (II).

11. A pressure medium system (10) for a rail vehicle (1), the pressure medium system having: The shut-off valve (100) according to any one of claims 1 to 10. A hose connector (200) is directly or indirectly connected to the second connection section (II) of the shut-off valve (100), and A pressure medium pipeline (400) is directly or indirectly connected to the first connection section (I). in, The shut-off valve (100) is configured such that the control piston (130) can automatically move to the closed position due to the pressure gradient caused by the failure of the hose connector (200) between the first connection section (I) and the second connection section (II).

12. The pressure medium system (10) according to claim 11, wherein, The pressure medium pipeline (400) has a pressure medium discharge device (300) that is switchable so as to selectively reduce the medium pressure in the first connection section (I).

13. The pressure medium system (10) according to claim 12, wherein, By reducing the pressure drop in the first connection section (I) caused by the pressure medium discharge device (300), the control piston (130) of the shut-off valve (100) can automatically move to the open position.

14. The pressure medium system (10) according to claim 11 or 12, wherein, The pressure medium system (10) has a sensor (170) configured to monitor the triggering of a shut-off valve (100) used to control the piston (130) to move to the closed position.

15. A rail vehicle (1) comprising a pressure medium system (10) according to any one of claims 11 to 14, wherein, The rail vehicle (1) has at least two carriages (2), each carriage having at least one pressure medium line (400), and in order to fluidly connect the end of the pressure medium line (400) of one carriage to the corresponding end of the pressure medium line (400) of the other carriage through a corresponding shut-off valve (100), the corresponding pressure medium line (400) is connected to a hose connector (200).

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