Valve for a fluid line, valve system and method for operating a valve

Abstract

Valve (100) for a fluid line, comprising - a housing (10) with a fluid inlet (11), a fluid outlet (12) and a fluid line (13) for conveying a fluid from the fluid inlet (11) to the fluid outlet (12), - a piston (15) arranged in the housing with a sealing surface (16) which, in an open position, releases the fluid outlet (12) for the passage of the fluid and, in a closed position, closes the fluid outlet (12) to block the passage of the fluid, - wherein the piston (15) is guided axially and rotatably or rotatably for movement between the open position and the closed position via a drive shaft (14) of a valve system (200), - a first through-body (17) arranged in the fluid line (13), which is statically fixed inside the housing (10) and which has at least one static through-opening (18) for conveying the fluid from the fluid inlet (11) to the fluid outlet (12), - a second passage body (19) which is guided axially and rotatably or rotatably within the first passage body (17) via the piston (15) and / or via the drive shaft (14) and which has at least one dynamic passage opening (20) for conveying the fluid from the fluid inlet (11) to the fluid outlet (12), - wherein the piston (15) and the second through-body (19) are coupled to the drive shaft (14) of the valve system (200), and - wherein the second passage body (19) can be axially displaced and rotated or rotated relative to the first passage body (17) by means of the piston (15) and / or the drive shaft (14) such that in a flow position of the second passage body (19) the at least one dynamic flow opening (20) of the second passage body (19) for the passage of the fluid is at least partially aligned with the at least one static flow opening (18) of the first passage body, and that in a blocking position of the second passage body (19) the second passage body (19) closes the at least one static flow opening (18) of the first passage body (17) to block the passage of the fluid.

Description

[0001] The invention relates generally to the field of fluid lines, in particular high-pressure fluid lines, such as high-pressure fluid lines for power plants or steam turbines. Specifically, the invention relates to a valve for a fluid line, a valve system with such a valve, and a method for operating such a valve.

[0002] Valves for regulating, closing, and opening a fluid flow in a fluid line, according to current technology, generally operate with a piston that can move axially between a closed and an open position in the high-pressure fluid line. Two different valve designs are primarily used for this purpose.

[0003] In one known variant, a piston is extended from a sealing seat to open the valve. Depending on the piston's position, a corresponding opening gap is created, through which the fluid flow rate is regulated. To stop the fluid flow, i.e., to close the outlet, the piston is retracted back into its sealing seat.

[0004] In a second known variant, a through-flow body is provided, which is installed between a valve train and a valve outlet. In this variant, the piston moves axially within the through-flow body. The further the piston moves from a valve outlet, the larger the flow cross-section of the through-flow body becomes.

[0005] From EP 3 708 884 A1, a valve with dynamic flow control is known that uses a combination of axially movable and rotatable valve elements to control the fluid flow. The valve has two coaxial valve elements, the inner valve element being both axially and rotatably movable, and the outer valve element being axially displaceable. The inner valve element is rotatable relative to the outer valve element to change the overlap of the flow openings. Simultaneously, both valve elements are axially movable and can be moved together with a piston to open the valve. The piston itself moves exclusively axially and regulates the flow through its interaction with the valve seat.

[0006] A throttling device with a collector is known from DE 10 2012 006 624 A1. The collector has an inlet and several outlets. A control element in the form of a movable sleeve is arranged in the collector and changes the cross-sections of the openings corresponding to the outlets by means of an axial and / or rotatable movement. Various drives, including a rotatable shaft, are provided for the control.

[0007] WO 89 / 11 609 A1 discloses a control valve consisting of a valve cone assembly with a hollow, cylindrical body and a control slide rotatably arranged therein. Both the cylindrical body and the control slide have openings over an arc-shaped area, the overlap of which regulates the flow rate. The control slide can be rotated to various positions via a spindle. The cylindrical body has a peripheral sealing surface that interacts with the valve seat, corresponding to a piston. To open the valve, the cylindrical body and the control slide are moved axially via the spindle, followed by a rotational movement of the control slide, which regulates the flow rate of the valve in the open position. The cylindrical body is axially movable.

[0008] However, with known valve designs, very long axial piston travel distances are necessary to completely interrupt or fully release the fluid flow. Long piston travel distances bring many disadvantages, affecting wear, response and control times, as well as efficiency, costs, and risks.

[0009] The object of the present invention is to at least partially overcome the disadvantages described above for valves in fluid lines. In particular, the object of the present invention is to improve the control of valves in fluid lines, especially in high-pressure fluid lines, particularly by making them faster and more precise.

[0010] The foregoing problem is solved by a valve for a fluid line having the features of claim 1, by a valve system for a fluid line having the features of claim 7, and by a method for operating a valve for a fluid line having the features of claim 14. Further features and details of the invention will become apparent from the dependent claims, the description, and the drawings. Features and details described in connection with the valve according to the invention naturally also apply in connection with the valve system and / or method according to the invention, and vice versa, so that the disclosure regarding the individual aspects of the invention always refers to, or can refer to, each other.

[0011] With embodiments of the invention, an improved valve for a fluid line, particularly for a high-pressure fluid line, can advantageously be provided. Such a valve allows for better, and especially faster and more precise, control of the flow rate in a high-pressure fluid line. Furthermore, such a valve can increase the safety of a fluid line.

[0012] A first aspect of the present invention relates to a valve for a fluid line, in particular for high-pressure fluid lines, such as high-pressure fluid lines for power plants or steam turbines. The valve has the following features: - a housing with a fluid inlet, a fluid outlet and a fluid line for conveying a fluid from the fluid inlet to the fluid outlet, - a piston arranged in the housing with a sealing surface, which in an open position releases the fluid outlet for the passage of the fluid and in a closed position closes the fluid outlet to block the passage of the fluid, wherein the piston is guided axially and rotatably or rotatably for movement between the open position and the closed position via a drive shaft of a valve system, - a first through-body arranged in the fluid line, which is statically fixed inside the housing and which has at least one static through-opening for conveying the fluid from the fluid inlet to the fluid outlet, - a second passage body which is guided axially and rotatably or rotatably within the first passage body via the piston and / or via the drive shaft and which has at least one dynamic passage opening for conveying the fluid from the fluid inlet to the fluid outlet.

[0013] The piston and the second passage body are coupled to the drive shaft of the valve system. Furthermore, the second passage body can be axially displaced and rotated, or rotated, relative to the first passage body by means of the piston and / or the drive shaft such that, in a flow-through position of the second passage body, the at least one dynamic flow-through opening of the second passage body for the passage of fluid is at least partially aligned with the at least one static flow-through opening of the first passage body, and that, in a blocked position of the second passage body, the second passage body closes the at least one static flow-through opening of the first passage body to block the passage of fluid.

[0014] In other words, a valve can be provided for a high-pressure fluid line that can allow or interrupt the flow of fluid by means of a piston on the one hand and a movable second passage element on the other. Both the piston and the second passage element can be guided axially and rotationally, or rotationally.

[0015] The valve housing can be part of a fluid line or a high-pressure fluid line. Generally, the housing can refer to a pipe, a conduit, or a section of a sewer or channel. The housing can be a single piece. It is provided with a fluid inlet and a fluid outlet, the fluid inlet being located upstream of the fluid outlet in the direction of fluid flow. The housing also includes a fluid line, which can refer to a volume within the housing, a section, or a region of the housing through which the fluid can flow. The housing can accommodate a drive shaft for a valve system, which may be mounted for axial and rotational movement or rotational movement. Alternatively, the drive shaft of a valve system can be located outside the housing.

[0016] The fluid inlet can be defined as an opening in the housing. The fluid inlet preferably has a round cross-section. The fluid inlet can have a larger cross-section than the fluid outlet of the housing.

[0017] The housing itself can have a round and / or oval cross-section. The housing geometry can be freely chosen. The fluid channel of the housing can be designed to facilitate fluid flow. Fluid-dynamically advantageous geometries, for example with straight and / or rounded contours, may be preferred.

[0018] In the context of this disclosure, the term axial can denote a direction or orientation that runs along a longitudinal axis of the housing. This longitudinal axis can pass through the fluid inlet and outlet of the housing. In the context of this disclosure, a rotary motion can denote a tangential motion about the longitudinal axis of the housing. In other words, an axial motion can denote a motion parallel or coaxial to the longitudinal axis of the housing, and a rotary motion can denote a rotation about the longitudinal axis. An axial and rotary motion can correspond to a screw motion.

[0019] The valve is further equipped with a piston. The piston is preferably designed to completely close the fluid outlet. When the fluid outlet is closed or sealed by the piston, the piston is in a closed position. The closed position can refer to a position and / or orientation of the piston in which the fluid outlet is closed. The piston has a sealing surface for closing the fluid outlet, and in particular for sealing it. From the closed position, the piston can be axially and rotationally movable, or rotatably movable, via the drive shaft to release the fluid outlet. The flow rate or volumetric flow of the fluid can be changed by an axial and rotational movement or rotational movement of the piston.In other words, pressure differences in the fluid line of the housing can be controlled and / or regulated quickly and very precisely by movements of the piston. The piston is coupled directly or indirectly to the drive shaft. For example, the piston can be coupled to the drive shaft via a drive piston. The piston and the drive shaft can form a single unit.

[0020] In the context of the present disclosure, the piston can be referred to as a sealing piston or a piston rod. The piston can be designed as a single piece or as a two-piece piston with a drive piston of the drive.

[0021] Furthermore, a second through-body is indirectly or directly coupled to the drive shaft. The second through-body can be attached to the piston. The second through-body is movably arranged within the first through-body and can therefore be referred to as the inner through-body.

[0022] The first flow-through element can be described as a static flow-through element because, unlike the second flow-through element, the first flow-through element is not movable relative to the piston and / or relative to the valve housing. The first flow-through element can be fixed to the housing. The first flow-through element can be fixed to the housing in such a way that it is replaceable. The first flow-through element can be a component of the valve through which the fluid can flow, preferably with a defined maximum flow rate.

[0023] The first passage body has at least one static opening. This opening allows the fluid to flow from one side of the passage body to the other. Essentially, the opening enables the fluid to flow through the first passage body. In the direction of fluid flow, a region upstream of the first passage body, i.e., upstream of the opening, can be considered outside the passage body. Conversely, a region downstream of the first passage body, i.e., after the opening, can be considered inside the passage body.

[0024] The terms "opening position" and "blocking position" are to be understood broadly in the context of this disclosure. Both the opening position and the blocking position can denote a position, location, arrangement, or location of the second passage body relative to the first passage body. This is because the second passage body can move relative to the first passage body in such a way that at least one dynamic opening of the second passage body can move relative to at least one static opening of the first passage body.

[0025] In the through-flow position, the second passage body can be positioned such that at least one dynamic through-flow opening of the second passage body is at least partially aligned with the static through-flow opening of the first passage body. In other words, the through-flow position can describe a position of the second passage body in which the fluid can flow through both the first and the second passage body.

[0026] In the blocked position, the second passage body can be positioned such that no fluid, or as little fluid as possible, can flow between the first and second passage bodies. In the blocked position, the second passage body can be positioned such that its dynamic opening is not aligned with the static opening of the first passage body. In the blocked position, the outer wall of the second passage body closes at least one static opening of the first passage body.

[0027] It should be noted that the second passage body is preferably movable in such a way that a transition from the blocking position to the allowing position and vice versa can be made steplessly.

[0028] The second flow body can be designed as a flow regulator. The second flow body can be described as a dynamic flow body because it can move relative to the first flow body and / or relative to the housing, in particular axially and rotationally. With movement of the second flow body, the dynamic flow opening can also move relative to the first flow body.

[0029] Through movement of the dynamic passage opening, i.e., the second passage body, the flow between the fluid inlet and fluid outlet of the valve can be better, i.e., faster and more precisely, regulated, controlled and / or changed.

[0030] The term "through opening" in the context of this disclosure, whether referring to a dynamic or a static through opening, is to be understood broadly. It can refer to holes, bores, and / or incisions. Generally, a through opening is to be understood as one in which the fluid can penetrate or flow through the first—and correspondingly the second—translucent body via at least one through opening.

[0031] The term "fluid" is to be understood broadly in the context of this disclosure. It can refer to both liquids and gases. Examples of fluids include gases, natural gases, methane, oil, and water.

[0032] Such a valve advantageously allows the fluid flow rate in a fluid line to be precisely, quickly, and efficiently regulated, controlled, and / or regulated. In particular, the flow rate can be variably adjusted by using two interacting passages. This increases the reliability of the valve. Therefore, such a valve can be used in critical environments, such as power plants or high-pressure turbines, where critical environments can also include those exposed to a certain risk of explosion.

[0033] The valve's ability to regulate the flow rate via axial and rotary motion, or rotary motion, particularly screw motion, allows for very short piston and / or drive shaft travel distances for opening and closing. For example, travel distances of less than 20 degrees, 30 degrees, or 40 degrees can be achieved for a 0 to 100% control range of the valve. This enables extremely fast response times for transitions from an open to a closed position and vice versa, or from a flow-through to a blocked position and vice versa, for example, down to 0.5 seconds or less for emergency closure / opening. The response time may depend on the valve size.

[0034] The short movement sequence eliminates the need for a long axial travel distance of the piston and / or the drive shaft. Therefore, it is possible to significantly reduce the overall length of the valve, or the valve together with the actuator, compared to conventional valves for fluid lines or high-pressure fluid lines.

[0035] Another major advantage of the valve described here is that the requirement for hydraulic oil can be kept low. In particular, the requirement for hydraulic oil can be less than 75% compared to known valve actuators.

[0036] Furthermore, such a valve allows for a lower force to be required for opening and closing compared to conventional valves. In particular, the tangential rotary motion, especially the tangential screw motion of the piston and / or the second passage body, significantly reduces the force needed to open and close the valve compared to conventional valves. This results in lower operating costs due to reduced oil volume, minimal maintenance, and correspondingly lower energy consumption. Consequently, a durable, robust, and cost-effective valve can be provided.

[0037] According to one embodiment of the valve, the first passage body is cylindrical. Furthermore, the first passage body has a plurality of static passage openings. The second passage body is also cylindrical and has a plurality of dynamic passage openings. Additionally, the second passage body rests axially and rotationally against the first passage body inside the first passage body if the second passage body is guided axially and rotationally within the first passage body by the piston and / or the drive shaft. Alternatively, the second passage body rests rotationally against the first passage body inside the first passage body if the second passage body is guided rotationally within the first passage body by the piston and / or the drive shaft.

[0038] The first through-body can be designed as a hollow cylinder with an inner and an outer radius. The second through-body can also be designed as a hollow cylinder with an inner and an outer radius. The inner radius of the first through-body can correspond to the outer radius of the second through-body. In other words, the two through-bodies can be nested within each other, with the second through-body resting inside the first.

[0039] The first passage body can have a large number of static passage openings, which are, for example, evenly distributed on the first passage body.

[0040] Alternatively, the static openings of the first passage body are distributed only within a section of the first passage body. Within this section, however, the openings can be evenly distributed. Another alternative is that the static openings can be arranged unevenly on the first passage body.

[0041] Alternatively or additionally, the dynamic openings of the second passage body are distributed within a section of the second passage body. Within this section, the dynamic openings can again be evenly distributed. Alternatively or additionally, the dynamic openings can also be arranged unevenly on the second passage body.

[0042] In principle, it can be advantageous for the dynamic openings of the second passage body to be arranged such that, in the open position, they are completely aligned with the static openings of the first passage body. Furthermore, the dynamic openings can be arranged such that, in the closed position of the second passage body, not a single dynamic opening among the multitude of dynamic openings is aligned with a static opening of the first passage body.

[0043] The precise arrangement of the numerous static and / or dynamic through-holes can be defined by the flow characteristics for the specific application of the valve. In particular, the arrangement of the static and / or dynamic through-holes can depend on the Kv value of the valve.

[0044] The multitude of static and / or dynamic through-openings can be designed in such a way that the sum of the cross-sectional areas of the through-openings allows a predefined volume flow of the fluid.

[0045] According to one embodiment of the valve, the outer wall of the second passage body rests movably against the inner wall of the first passage body in a sealing manner.

[0046] The term "sealing" is to be understood broadly in this context. "Sealing" can be understood as meaning that, as far as possible, no fluid can flow between the first and second passage bodies. However, the relative movement of the second passage body to the first should not be impeded by a sealing connection. This allows for further improvement in the control of the fluid flow rate.

[0047] According to one embodiment of the valve, the at least one static through-opening has an elongated, spiral, oval, angular, and / or circular shape. Furthermore, the at least one dynamic through-opening has the same shape as the at least one static through-opening.

[0048] The shape of at least one static opening can be its cross-section at the outer wall of the first passage body. The at least one opening can have a constant cross-section across the thickness of the first passage body. Alternatively, the at least one static opening can have a variable cross-section across the thickness of the first passage body. The thickness of the first or second passage body can be the distance between the respective outer wall and the respective inner wall. The at least one dynamic opening can have the same shape as the at least one static opening.

[0049] This allows for a greater flow rate or volume flow when the valve is in the through position.

[0050] According to one embodiment of the valve, the cross-sectional area of ​​the at least one static through-opening decreases from the outer wall of the first through-body to the inner wall of the first through-body, in particular uniformly.

[0051] This allows the flow of fluid through the first passage body to be further reduced.

[0052] According to one embodiment of the valve, the at least one static through-opening and / or the at least one dynamic through-opening are inclined to the axis of rotation of the piston.

[0053] In particular, at least one static through-opening and / or at least one dynamic through-opening can be inclined in the direction of the flow. This reduces the force generated by the volume flow on the first and / or second through-opening body and further increases the robustness of the valve.

[0054] A second aspect of the present disclosure relates to a valve system for a fluid line, in particular a high-pressure fluid line, for regulating the flow of a fluid. The valve system comprises a valve, as described above and below, and an actuator with an axially and rotatably mounted drive shaft if the second flow body is axially and rotatably guided via the piston and / or via a drive shaft within the first flow body, or with a rotatably mounted drive shaft if the second flow body is rotatably guided via the piston and / or via a drive shaft within the first flow body. The piston of the valve is coupled, at least indirectly, to the drive shaft of the actuator.

[0055] According to one embodiment of the valve system, the actuator also has at least one spring element. This spring element is arranged within the housing such that, when the valve piston and / or an actuator piston move towards the opening position, it can be pre-tensioned to exert a force on the valve piston and the actuator piston in the direction of the closing position. This significantly increases safety during valve operation, as it allows the valve to close automatically in the event of system failure and pressure loss.

[0056] The spring element can be one spring or several springs. It can be cylindrical. The spring element can, for example, be arranged around the drive shaft of the actuator. The spring element is generally smaller than that of conventional valves because the piston, due to its rotary motion, requires shorter travel distances than in conventional valves.

[0057] When a spring element is incorporated, this can be described as a single-acting drive. In such a drive configuration, only one of the piston's two travel paths can be achieved by means of a pressure load generated by the control fluid. The opposite travel path of the piston is made possible by spring pressure, i.e., by means of the spring element. In other words, the drive can move in one direction against an integrated spring element using the pressure load generated by the control fluid, thereby generating a corresponding spring force. When moving in the opposite direction, the hydraulic pressure relative to the control fluid can be reduced, and the spring force can decrease in the direction of the decreasing pressure load.

[0058] According to one embodiment of the valve system, connections, particularly fluid connections, are provided for driving the drive shaft, in particular the valve piston, via the drive shaft. In an embodiment in which the drive of the valve system is arranged in the valve housing, the connections can be arranged in the housing.

[0059] Such connections allow the drive shaft, and in particular the piston via the drive shaft, to be driven or controlled, at least indirectly. These connections may be hydraulic connections.

[0060] In such an embodiment, a spring element may be provided. Alternatively, a spring element may be omitted. If a spring element is omitted, the design can be described as a double-acting drive. In a double-acting drive, all travel distances can be achieved by a pressure load generated by means of a control fluid.

[0061] According to one embodiment of the valve system, the drive of the valve system for axially and rotationally moving or rotaryly driving the drive shaft is arranged within the housing of the valve.

[0062] The actuator can be arranged axially within the valve housing. This eliminates the need for a joint. Due to the reduced force required, the elimination of the deflection mechanism, and the flow control method, the entire valve system can be smaller and thus fit more compactly within the valve.

[0063] With such a valve system, only axial forces, and no radial forces, can be transmitted from the actuator to the valve housing. This allows for a robust valve or valve system.

[0064] By integrating the actuator into the valve housing, necessary maintenance openings, which can pose a high risk of leakage, can be eliminated or at least reduced. This eliminates the need for extensive sealing and inspection work.

[0065] According to one embodiment of the valve system, the actuator has a drive piston which is at least indirectly coupled to the valve piston. The drive piston and the drive shaft of the actuator each have a steep thread, which is provided with a right-hand or left-hand pitch.

[0066] This allows for a steep thread pairing, which in turn generates a rotary motion of the drive shaft during the axial movement of the piston. Therefore, the drive shaft can perform both radial and axial movements simultaneously.

[0067] According to one embodiment of the valve system, at least one hydraulic device is arranged inside the housing of the valve in such a way that it allows the piston of the valve to be moved back and forth between the closed position and the open position.

[0068] The hydraulic device can store or absorb force when the piston moves towards the closed position in order to exert a force on the piston in the closed position towards the open position of the piston.

[0069] In other words, the hydraulic device can ensure that all piston movements are achieved using pressure generated by the control fluid. The major advantage of this design is its significantly smaller size compared to a single-acting drive, i.e., a drive in which not all piston movements are achieved using pressure generated by the control fluid.

[0070] According to one embodiment of the valve system, the valve system further comprises a control unit. The control unit is configured to control the drive shaft, in particular the drive of the valve system, and in particular to control it at least indirectly, in order to move the piston of the valve, i.e., the sealing piston, between an open position and a closed position, in particular continuously, and to move the second passage body of the valve between a flow position and a blocking position, in particular continuously.

[0071] The term "continuous" is to be understood broadly in the context of this revelation. "Continuous" can be understood as continuous, constant, and / or non-discrete.

[0072] The control unit can, for example, be located outside the housing. Functional, control, and sensor lines can be routed from the internal actuator through the valve housing, and in particular to the control unit. The connection points can preferably be integrated into the housing.

[0073] All the advantages listed for the valve according to the first aspect of the invention also apply equally to the valve system for a fluid line, in particular for a high-pressure fluid line, according to the second aspect of the invention.

[0074] A third aspect of the present disclosure relates to a method for operating a valve, in particular a valve system, for a fluid line as described above and below, comprising the following steps: • A fluid is guided into the housing of the valve through a fluid inlet with a defined flow rate, • the fluid is guided to a first pressure zone, the first pressure zone being located in the direction of flow upstream of the first passage body in the housing, • The piston of the valve is driven axially and rotaryally, or rotaryally, by means of a drive mechanism. • wherein the second passage body is guided axially and rotatably via the piston and / or via a drive shaft within the first passage body, and the second passage body is guided axially and rotatably via the piston of the valve and / or via a drive shaft of a valve system, in particular a valve system according to the second aspect of the invention, in particular at least indirectly via the piston of the valve, or wherein the second passage body is guided rotatably via the piston and / or via the drive shaft within the first passage body and is guided rotatably via the piston of the valve and / or via a drive shaft of a valve system, in particular a valve system according to the second aspect of the invention, in particular at least indirectly via the piston of the valve, in order to control a first flow by which the fluid is directed from the first pressure zone to a second pressure zone,in particular to reduce, wherein the second pressure zone is arranged in the flow direction after the at least one dynamic passage opening of the second passage body, • The piston of the valve is guided axially and rotatably, or rotatably, in particular via the drive shaft of the valve system, in order to control a second flow, by which the fluid is directed from the second pressure zone through the fluid outlet of the housing, wherein, during the guidance of the second passage body, a relative movement of the at least one dynamic passage opening towards the at least one static passage opening takes place such that an overlapping area of ​​the at least one dynamic passage opening with the at least one static passage opening can be reduced or enlarged, and where there is a pressure difference between the first pressure zone and the second pressure zone.

[0075] In other words, the valve can be operated in such a way that the volume flow of the fluid can be defined, regulated or controlled via the second passage body and / or via the piston of the valve, i.e. the piston rod.

[0076] The overlapping area can generally be defined as the area in which the corresponding static passage opening is aligned with the corresponding dynamic passage opening.

[0077] The first and second pressure zones can be areas where the fluid pressure is to be, or can be, regulated. Generally, the first pressure zone can refer to a volume or area within the housing or fluid line where a first fluid pressure exists, which may differ from a second fluid pressure in the flow direction downstream of the valve, the second passage, and / or the fluid outlet of the valve. A first fluid pressure can exist in the first pressure zone, and a second fluid pressure can exist in the second pressure zone. It can be advantageous to regulate, monitor, and / or measure both the first and second fluid pressures. Pressure sensors, for example, can be used for this purpose.

[0078] This method allows for precise and efficient regulation of the flow rate in a fluid line, and especially in a high-pressure fluid line. It also enables safer operation of a valve in a fluid line.

[0079] All the advantages listed for the valve according to the first aspect of the invention also apply equally to the method for operating a valve for a fluid line according to the third aspect of the invention.

[0080] The pressure difference between the zones described above can be monitored by means of a sensor. Depending on the pressure difference, the valve can be controlled accordingly, i.e., it can initiate a stepless transition from a closed position to an open position or vice versa, and / or a stepless transition from a flow position to a blocking position or vice versa.

[0081] According to one embodiment of the method, the pressure difference between the first pressure zone and the second pressure zone is regulated by controlling the second passage body and / or the piston of the valve.

[0082] According to one embodiment of the method, the second passage body and the piston of the valve are guided synchronously axially and rotationally via the drive shaft of a / the valve system if the second passage body is guided axially and rotationally via the piston and / or via the drive shaft within the first passage body, or rotationally guided if the second passage body is guided rotationally via the piston and / or via the drive shaft within the first passage body.

[0083] The term "synchronous" is to be understood broadly in the context of this disclosure. "Synchronous" in this context can be understood to mean that the piston and the second passage body are operated at the same frequency. However, the closing position of the piston does not necessarily have to occur simultaneously with the blocking position of the second passage body. The closing and blocking positions may be reached with a slight time offset. Likewise, the opening position may be reached with a time offset from the passage position.

[0084] Since both the second flow body and the valve piston can be coupled to the drive shaft, either directly or indirectly, both elements can operate synchronously. In other words, an axial movement of the valve piston generally corresponds to a corresponding axial movement of the second flow body. A rotary movement of the piston generally corresponds to the same rotary movement of the second flow body.

[0085] According to one embodiment of the method, the valve piston is moved from the open position to release the fluid outlet to the closed position to block the fluid outlet, and vice versa. Alternatively or additionally, the second flow body is moved from the open position to the closed position.

[0086] Furthermore, a computer-readable medium may be provided on which a computer program product is stored. Such a computer program product may comprise instructions which, when executed by a computing unit, cause the computing unit to execute a method as described above in accordance with the third aspect of the invention.

[0087] All revelations described above and below in relation to one aspect of the present revelation apply equally to all other aspects of the present revelation.

[0088] Further advantages, features, and details of the invention will become apparent from the following description, in which exemplary embodiments of the invention are described in detail with reference to the drawings. The features mentioned in the claims and in the description can each be essential to the invention individually or in any combination.

[0089] Exemplary embodiments of the invention are described below with reference to the figures. The figures show: Fig. 1 a schematic perspective view of a valve according to an exemplary embodiment, Fig. 2a to 2d schematic sectional views of valve systems according to exemplary embodiments, and Fig. 3a to 3d schematic sectional views of valve systems according to exemplary embodiments.

[0090] Similar, similar-looking, identical, or equivalent elements are identified by the same reference symbols in the figures. The figures are shown schematically and not to scale.

[0091] Fig. Figure 1 shows a schematic perspective view of a valve 100 according to an exemplary embodiment. The fluid can flow into the valve 100, in particular into the housing 10 of the valve 100, through the fluid inlet 11. The housing 10 of the valve also has a fluid line 13 through which the fluid can flow. The fluid can flow out of the housing 10 or out of the valve 100 through the fluid outlet 12. The fluid outlet 12 of the valve 100 Fig. 1 has a smaller cross-section than the fluid inlet 11. Both the fluid outlet 12 and the fluid inlet 11 of the Fig. They have a round cross-section. The housing 10 of the valve 100 of the Fig. 1 is predominantly cylindrical. At least a first through-flow body 17, a second through-flow body 19, a piston 15, and a drive shaft 14 are arranged in the housing 10 of the valve 100. It should be noted that in the present exemplary embodiment, the drive shaft 14 is arranged in the housing 10 of the valve 100 because the actuator 23 is also arranged in the housing of the valve 100. If, in an alternative embodiment, the actuator is arranged outside the housing 10 of the valve 100, the drive shaft 14 is also located outside the housing 10 of the valve 100.

[0092] Both the piston 15, also referred to as the piston rod, and the second through-body 19 are coupled to the drive shaft 14. The piston 15 can be moved axially back and forth via the drive shaft 14. Simultaneously, the second through-body 19 can also be moved axially via the drive shaft 14. The drive shaft 14 can be fixed together with the second through-body 19 and the piston 15, forming a single assembly. The second through-body 19 and the piston 15 can, in conjunction, provide the control, closing, and opening functions.

[0093] The piston 15, i.e., the piston rod, can be moved continuously back and forth, particularly from an open position to a closed position. For this purpose, the piston 15 can have a sealing surface 16. In the closed position, the sealing surface 16 of the piston 15 can be positively engaged in the fluid outlet 12, preventing fluid from flowing through the fluid outlet 12. In the closed position, the sealing surface 16 of the piston 15 can bear against a static sealing surface 27 of the housing 10 or the first through-body 17. The seal in the closed position can be achieved by the two matching sealing surfaces 16 and 27. The sealing surface 16 on the piston can be referred to as the dynamic sealing surface 16. The static sealing surface 27 can be located in the valve seat, i.e., in the fluid outlet 12. The surfaces of the sealing surfaces can be designed to minimize wear and provide a seal against each other. When closing valve 100, i.e.Upon reaching the closed position, the piston can rotate or slide into the valve seat, i.e., into the fluid outlet 12, and can generate a corresponding closing force through a screw effect. The tightness can be determined by the design of the valve seat, i.e., the fluid outlet 12, and the corresponding screw forces.

[0094] In the open position, the sealing surface 16 of the piston 15 is preferably not in contact with the housing 10 of the valve 100 and / or not in contact with the first passage body 17 of the valve 100.

[0095] The first flow-through body 17 is arranged in the fluid line 13 of the valve 100 and attached to the housing 10. The first flow-through body 17 can define the cross-section of the fluid outlet 12. The first flow-through body 17 can delineate a first pressure zone Z1. A first pressure zone Z1 can be defined upstream of the first flow-through body 17 in the direction of flow. The pressure or fluid pressure in the first pressure zone Z1 can be detected by means of a pressure sensor (not shown here).

[0096] Adjacent to the first flow body 17 is a second flow body 19, which is movable relative to the first flow body 17, in particular axially and rotationally movable. The second flow body 19 can also define or delimit a pressure zone. Downstream of the second flow body 19, a second pressure zone Z2 can be defined. A pressure sensor (not shown here) can be arranged in the second pressure zone Z2 to detect the pressure or fluid pressure in the second pressure zone Z2.

[0097] The first passage body 17 and the second passage body 19 each have a plurality of passage openings 18, 20. The fluid can flow through these passage openings 18, 20 from the first pressure zone Z1 to the second pressure zone Z2. In particular, the fluid can flow from the first pressure zone Z1 to the second pressure zone Z2 when the second passage body 19 is in a flow-through position, i.e., when the dynamic passage openings 20 of the second passage body 19 are arranged to allow at least partial flow to the static passage openings 18 of the first passage body 17. In the closed position of the second passage body 19, the dynamic and static passage openings 18, 20 are arranged relative to each other such that the fluid cannot flow, or at least almost cannot flow, from the first pressure zone Z1 to the second pressure zone Z2.The transition from the closed position of the second passage body 19 to the open position of the second passage body 19, and vice versa, is generally stepless. This transition can be achieved by mounting the second passage body 19 axially and rotatably, or rotatably, on the drive shaft 14.

[0098] As the Fig. As can be seen from Figure 1, the numerous dynamic through-openings 20 of the second through-body 19 are not uniformly arranged on the outer wall of the second through-body 19. Rather, the dynamic through-openings 20 are uniformly distributed in sections. However, in the axial direction of the second through-body 19, the dynamic through-openings are uniformly distributed. On the circumference of the second through-body 19, sections in the tangential direction are free of through-openings 20.

[0099] The static through-openings 18 are preferably not arranged over the entire axial length of the first through-body 17. Rather, the static through-openings 18 are arranged over a defined section in the axial direction. In contrast to the second through-body 19, the first through-body has no areas without openings in the tangential direction within the defined section. The arrangement of the through-opening depends on the intended application.

[0100] In housing 10 of valve 100 of the Fig. A drive 23 is further arranged in housing 10, which is configured to drive the drive shaft 14 axially and rotationally or rotationally. The drive 23 is also arranged axially in the housing 10. Fluid connections 22 are also arranged in the housing for driving the drive shaft 14 via the drive. Such fluid connections 22 are typically hydraulic connections for a control fluid. The pressure supply to the drive can be provided via such a fluid connection 22.

[0101] The housing 10 of the valve 100 of the Fig. 1 can be part of a high-pressure line. In particular, the housing 10 can be integrated into a high-pressure line system. For this purpose, the housing 10 can have connection sections 34.

[0102] In Fig. Figure 1 further shows that the housing 10 has a support structure 24, for example, a support structure for the actuator 23. The support structure 24 can also provide a flow opening 26. The flow opening 26 can also define the first pressure zone Z1 by reducing its cross-sectional area. The actuator 23 can be attached to the support structure 24. The first passage body 17 can also be attached to the support structure 24. The support structure 24 can have an opening to accommodate the drive shaft 14.

[0103] Fig. Figures 2a to 2d show schematic sectional views of valve systems 200 according to exemplary embodiments. Unless otherwise described, the respective valves 100 of the Fig. 2a to 2d the same elements and / or components as valve 100 of the Fig. 1 on.

[0104] In the Fig. In 2a to 2d, the actuator 23 of the valve system 200 is arranged outside the housing 10 of the valve 100.

[0105] The valve systems 200 of the Fig. 2a to 2d differ fundamentally in the drives 23, whereby the different drives 23 of the valve systems 200 can lead to different movements of the piston 15 of the valve 100.

[0106] In Fig. 2a is a single-acting, steep-thread screw drive. With such a drive 23, the piston 15 of the valve can be guided in a screw-like manner. The drive of the Fig. 2a has a spring element 21. The spring element 21 is pre-tensioned when the valve 100 is opened, i.e., in the direction of the opening position, and thus builds up a force in the direction of the closing position.

[0107] The drive shaft 14 of the drive 23 is provided with a steep thread. The drive 23 also has a drive housing 36, which is likewise provided with a steep thread. The piston 15 of the valve 100 is coupled to the drive shaft 14 via a drive piston 35. The piston 15 of the valve 100 and the drive piston 35 of the drive can be formed as a single unit. With such a drive, the piston can be guided axially and rotationally. The axial movement and the rotational movement of the piston of the valve 100 and / or the drive piston 35 of the drive are coupled together.

[0108] In Fig. 2b is a single-acting lifting screw drive. With such a drive 23, the piston 15 of the valve 100 and / or the second passage body 19 can be guided axially and rotationally, at least indirectly, via the drive shaft 14 of the drive, whereby the axial movement and the rotational movement can be carried out with a time offset.

[0109] The drive 23 of the Fig. 2b can be divided into two partial drives 23', 23"". The drive 23 thus has a radial drive (partial drive 23') and an axial drive (partial drive 23"). By means of the axial drive (partial drive 23"), which has a spring element 21, a drive piston 35 can be guided axially. The drive piston 35 is coupled to the piston 15 of the valve 100, preferably directly coupled. The axial drive (partial drive 23") can interact with the radial drive (partial drive 23') by means of a toothed connection 28. The toothed connection 28 has teeth for the radial movement of the drive piston 35 and / or the piston 15 of the valve 100. The toothed connection 28 of the Fig. 2b can also contribute to the axial movement of the drive piston 35 and / or the piston 15 of the valve 100. The drive shaft 14 of the Fig. 2b has a steep thread. Through the drive 23 of the Fig. 2b the axial movement and the rotary movement of the piston 15 and / or the second passage body 19 can occur both simultaneously and at different times.

[0110] In Fig. 2c provides a double-acting, high-helix screw drive. The drive 23 comprises a drive piston 35, which is preferably directly coupled to the piston 15 of the valve 100, and a drive shaft 14. The drive shaft 14 and the drive piston 35 are provided with a high-helix thread. The drive 23 further comprises a drive housing 36, which may have a rigid high-helix thread. Pressure chambers may be present in the drive 23.

[0111] In Fig. 2d is a double-acting lifting screw drive. Such a drive 23 does not have a spring element 21, unlike the drive 23 of the Fig. 2c, on. Similar to the drive of the Fig. 2b, can the drive 23 of the Fig. 2d can be divided into two partial drives 23', 23", wherein the two partial drives 23', 23" can interact by means of a tooth connection 28.

[0112] In summary, different actuators 23 can be used for a valve system 200. A distinction can be made between two categories of actuators. The actuators 23 of the Fig. 2a and Fig. 2c An axial movement of the piston 15 of the valve 100 cannot be decoupled from a rotary movement of the piston 15 of the valve 100. In contrast, the axial movement and the rotary movement of the piston 15 of the valve 100 can be decoupled by means of a drive such as one of the Fig. 2b and Fig. 2d can be decoupled. That is, it is with a drive 23, as in Fig. 2b or Fig. As shown in Figure 2d, it is possible to perform the rotary movement of the piston 15 of the valve 100 and / or of the second passage body 19 at a time offset from an axial movement of the piston 15 of the valve 100.

[0113] Fig. Figures 3a to 3d show schematic sectional views of valve systems 200 according to exemplary embodiments. Unless otherwise described, the respective valves 100 of the Fig. 3a to 3d the same elements and / or components as valve 100 of the Fig. 1 or Fig. 2a to 2d. In contrast to the Fig. 2a to 2d the respective drives 23 of the valve systems 200 are arranged in the housing 10 of the valve 100.

[0114] Due to its size and the type of actuator 23, the entire actuator assembly can be installed inside the valve housing. Therefore, unlike actuators that are typically mounted outside the valve 100, no moving connections are required from the inside of the valve 100 to the outside. This eliminates the need for maintenance or sealing.

[0115] Operating a valve 100 via an actuator 23 located outside the housing 10 typically requires redirection mechanisms. These must enable both force and motion transmission from a radial or axial actuator movement to an axial movement, often by approximately 90°. A joint mechanism, for example, can be used for this purpose.

[0116] By incorporating the actuator 23 into the housing 10 of the valve 100, it is also possible, in contrast to the valve systems 200 of the Fig. 2a to 2d, the fluid outlet 12 is axially aligned with the fluid inlet 11.

[0117] Joint mechanisms are subjected to strong bending, frictional, and shear forces during operation and are therefore highly susceptible to wear and malfunctions. Likewise, the power losses due to motion and force transmission can be substantial, potentially requiring a correspondingly large drive unit to compensate for these losses. Such power losses can occur with an internal drive 23, as in the Fig. Figure 3 is completely omitted. By eliminating this power and motion transmission, the drive 23 can be designed to be correspondingly small and thus efficient and energy-saving.

[0118] It should be noted that a long service life of the drive 23 can be ensured by forced lubrication and nitrided surfaces of the steep thread and / or the tooth connection 28.

[0119] It should be further noted that the terms "comprising" and "comprising" do not exclude other elements, and the indefinite articles "a" or "an" do not exclude a plurality. It should also be noted that features and steps described with reference to one of the above embodiments may also be used in combination with other features and steps of other embodiments described above. Reference numerals in the claims are not to be considered as a limitation. Reference symbol list 100 valve 200 valve system 10 cases 11 Fluid inlet 12 Fluid outlet 13 Fluid line 14 Drive shaft 15 pistons 16 sealing surface 17 first through body 18 static passage openings 19 second passage body 20 dynamic through-opening 21 Spring element 22 Connection / Fluid connection 23 Drive 24 Support structure 26 Flow opening 27 static sealing surface 28 tooth connection 34 Connecting section 35 drive pistons 36 drive housings Z1 first pressure zone Z2 second pressure zone

Claims

Valve (100) for a fluid line, comprising: - a housing (10) with a fluid inlet (11), a fluid outlet (12) and a fluid line (13) for conveying a fluid from the fluid inlet (11) to the fluid outlet (12); - a piston (15) arranged in the housing with a sealing surface (16), which in an open position releases the fluid outlet (12) for the passage of the fluid and in a closed position closes the fluid outlet (12) to block the passage of the fluid; - wherein the piston (15) is guided axially and rotatably or rotatably for movement between the open position and the closed position via a drive shaft (14) of a valve system (200); - a first passage body (17) arranged in the fluid line (13), which is statically fixed within the housing (10) and which has at least one static passage opening (18) for conveying the fluid from the fluid inlet. (11) to the fluid outlet (12),- a second passage body (19) which is guided axially and rotatably or rotatably within the first passage body (17) via the piston (15) and / or the drive shaft (14) and which has at least one dynamic passage opening (20) for conveying the fluid from the fluid inlet (11) to the fluid outlet (12), - wherein the piston (15) and the second passage body (19) are coupled to the drive shaft (14) of the valve system (200), and - wherein the second passage body (19) can be axially displaced and rotated or rotated relative to the first passage body (17) by means of the piston (15) and / or the drive shaft (14) such that, in a flow position of the second passage body (19), the at least one dynamic passage opening (20) of the second passage body (19) for conveying the fluid is at least partially aligned with the at least one static passage opening (18) of the first passage body is arranged,and that in a blocked position of the second passage body (19) the second passage body (19) closes the at least one static passage opening (18) of the first passage body (17) to block the passage of the fluid. Valve (100) according to claim 1, characterized in that the first through-body (17) is cylindrical and has a plurality of static through-openings (18) and that the second through-body (19) is cylindrical and has a plurality of dynamic through-openings (20), wherein the second through-body (19) is guided axially and rotatably within the first through-body (17) via the piston (15) and / or via the drive shaft (14) and rests axially and rotatably against the first through-body (17) inside the first through-body (17), or wherein the second through-body (19) is guided rotatably within the first through-body (17) via the piston (15) and / or via the drive shaft (14) and rests rotatably against the first through-body (17) inside the first through-body (17). Valve (100) according to claim 1 or 2, characterized in that the outer wall of the second passage body (19) movably abuts the inner wall of the first passage body (17) in a sealing manner. Valve (100) according to at least one of the preceding claims, characterized in that the at least one static through-opening (18) has an elongated, a spiral, an oval, an angular and / or a circular shape and that the at least one dynamic through-opening (20) has a shape similar to that of the at least one static through-opening (18). Valve (100) according to at least one of the preceding claims, characterized in that the cross-sectional area of ​​the at least one static through-opening (18) decreases from the outer wall of the first through-body (17) to the inner wall of the first through-body (17), in particular decreases uniformly. Valve (100) according to at least one of the preceding claims, characterized in that the at least one static through-opening (18) and / or the at least one dynamic through-opening (20) is / are inclined to the axis of rotation of the piston (15). Valve system (200) for a fluid line for controlling the flow of a fluid, comprising a valve (100) according to one of claims 1 to 6, wherein the second passage body (19) is guided axially and rotatably within the first passage body (17) via the piston (15) and / or via a drive shaft (14), and a drive (23) with a drive shaft (14) mounted axially and rotatably, wherein the piston (15) of the valve (100) is coupled at least indirectly to the drive shaft (14) of the drive (23), or, a valve (100) according to one of claims 1 to 6, wherein the second passage body (19) is guided rotatably within the first passage body (17) via the piston (15) and / or via a drive shaft (14), and a drive (23) with a drive shaft (14) mounted rotatably, wherein the piston (15) of the valve (100) is at least indirectly coupled to the drive shaft (14) of the drive (23). Valve system (200) according to claim 7, wherein the actuator (23) has at least one spring element (21), and wherein the at least one spring element (21) is arranged within the actuator (23) such that it can be pre-tensioned when the piston (15) of the valve and / or a drive piston (35) of the actuator (23) is moved in the direction of the opening position, in order to exert a force on the piston (15) of the valve and / or on the drive piston (35) of the actuator (23) in the direction of the closing position of the piston (15). Valve system (200) according to one of claims 7 and 8, characterized in that connections (22), in particular fluid connections, are provided for driving the drive shaft (14). Valve system (200) according to at least one of claims 7 to 9, characterized in that the drive (23) of the valve system (200) for axially and rotatably or rotatably driving the drive shaft (14) is arranged within the housing (10) of the valve (100). Valve system (200) according to at least one of claims 7 to 10, characterized in that the drive has a drive piston (35) which is coupled at least indirectly to the piston (15) of the valve (100), wherein the drive piston (35) and the drive shaft (14) of the drive (23) each have a steep thread which is provided with a right-hand or left-hand pitch. Valve system (200) according to at least one of claims 7 to 11, characterized in that at least one hydraulic device is arranged within the housing (10) of the valve (100) such that the piston (15) of the valve (100) can be moved back and forth between the closed position and the open position by means of it. Valve system (200) according to at least one of claims 7 to 12, characterized in that the valve system (200) further comprises a control unit, wherein the control unit is configured to control the drive shaft (14), in particular the drive (23) of the valve system (200), in order to move the piston (15) of the valve (100) between an opening position and a closing position, in particular continuously, and to move the second passage body (19) of the valve (100) between a flow position and a blocking position, in particular continuously. Method for operating a valve (100), in particular a valve system (200) according to at least one of the preceding claims 7 to 13, for a fluid line according to at least one of the preceding claims 1 to 6, comprising the following steps: • a fluid is passed with a defined flow into the housing (10) of the valve (100) through a fluid inlet (11), • the fluid is passed to a first pressure zone (Z1), wherein the first pressure zone (Z1) is arranged in the flow direction upstream of the first passage body (17) in the housing (10), • the piston (15) of the valve (100) is driven axially and rotatably or rotatably by means of a drive (23),• wherein the second passage body (19) is guided axially and rotatably within the first passage body (17) via the piston (15) and / or via a drive shaft (14), and the second passage body (19) is guided axially and rotatably via the piston (15) of the valve (100) and / or via a drive shaft (14) of a valve system (200), in particular a valve system (200) according to at least one of the preceding claims 7 to 13, or wherein the second passage body (19) is guided rotatably within the first passage body (17) via the piston (15) and / or via a drive shaft (14), and is guided rotatably via the piston (15) of the valve (100) and / or via a drive shaft (14) of a valve system (200), in particular a valve system (200) according to at least one of the preceding claims 7 to 13, in order to allow a first flow, with in which the fluid is directed from the first pressure zone (Z1) to a second pressure zone (Z2),to control, in particular to reduce, wherein the second pressure zone (Z2) is arranged in the flow direction downstream of the at least one dynamic through-opening (20) of the second through-body (19), the piston (15) of the valve (100) is guided axially and rotatably, or rotatably, in particular via the drive shaft (14) of the valve system (200), in order to control a second flow, by which the fluid is directed from the second pressure zone (Z2) through the fluid outlet (12) of the housing (10), wherein, in the guidance of the second through-body (19), a relative movement of the at least one dynamic through-opening (20) to the at least one static through-opening (18) takes place such that an overlapping area of ​​the at least one dynamic through-opening (20) with the at least one static through-opening (18) can be reduced or enlarged,and wherein there is a pressure difference between the first pressure zone (Z1) and the second pressure zone (Z2). Method according to claim 14, characterized in that the pressure difference between the first pressure zone (Z1) and the second pressure zone (Z2) is controlled by the control of the second passage body (19) and / or the piston (15). Method according to one of claims 14 or 15, characterized in that the second passage body (19) is guided axially and rotatably within the first passage body (17) via the piston (15) and / or via the drive shaft (14), and the second passage body (19) and the piston (15) of the valve are guided synchronously axially and rotatably via the drive shaft (14) of a / the valve system (200), or that the second passage body (19) is guided rotatably within the first passage body (17) via the piston (15) and / or via the drive shaft (14), and the second passage body (19) and the piston (15) of the valve are guided synchronously rotatably via the drive shaft (14) of a / the valve system (200). Method according to at least one of claims 14 to 16, characterized in that the piston (15) of the valve (100) is guided from the opening position to release the fluid outlet (12) to the closing position to block the fluid outlet (12) and vice versa, and / or that the second passage body (19) is guided from the passage position to the blocking position.

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