阅读说明：本技术 阀线性驱动装置和阀 (Valve linear drive and valve ) 是由 弗洛里安·菲舍尔 拉尔夫·施特拉斯维默尔 迈克·富克斯 格奥尔格·默尔 维诺特·帕特马纳坦 于 2021-06-03 设计创作，主要内容包括：本发明提供了一种阀线性驱动装置,该阀线性驱动装置用于连接至具有阀座(30)的阀本体,该阀线性驱动装置包括驱动壳体、阀闭合构件(32)、致动器以及弹簧装置(60)。阀闭合构件(32)能够借助于致动器(36)和致动器件(38)沿着调节轴线(V)在打开位置与关闭位置之间进行调节。弹簧装置(60)将致动器件(38)推动到打开位置中或推动到关闭位置中。此外,弹簧装置(60)包括多个弹簧(62)和用于弹簧(62)的接纳单元(64)。在此,每个弹簧(62)具有该弹簧(62)自身的形成在接纳单元(64)中的弹簧腔室(78),相关联的弹簧(62)插入弹簧腔室(78)中。此外,提供了一种具有这种阀线性驱动装置的阀。(The invention provides a valve linear drive for connection to a valve body having a valve seat (30), the valve linear drive comprising a drive housing, a valve closure member (32), an actuator and a spring arrangement (60). The valve closing member (32) is adjustable between an open position and a closed position along an adjustment axis (V) by means of an actuator (36) and an actuating means (38). Spring means (60) urge the actuating means (38) into the open position or into the closed position. Furthermore, the spring device (60) comprises a plurality of springs (62) and a receiving unit (64) for the springs (62). In this case, each spring (62) has its own spring chamber (78) formed in the receiving unit (64), the associated spring (62) being inserted into the spring chamber (78). Furthermore, a valve having such a linear valve drive is provided.)

1. Valve linear drive for connection to a valve body (12) having a valve seat (30), wherein the valve linear drive (20) comprises a drive housing (34), a valve closure member (32), an actuator (36) and a spring device (60), wherein the valve closure member (32) is adjustable along an adjustment axis (V) between an open position and a closed position by means of the actuator (36) and a force-transmitting actuating means (38), the actuating means (38) being interposed between the valve closure member (32) and the actuator (36), wherein the spring device (60) urges the actuating means (38) into the open position or into the closed position, wherein the spring device (60) comprises a plurality of springs (62) and a receiving unit (64) for the springs (62), and wherein each spring (62) has its own spring chamber (78) formed in the receiving unit (64), the associated spring (62) being inserted in the spring chamber (78).

2. Linear valve drive according to claim 1, characterized in that the spring (62) bears at one end (84) against the drive housing (34, 40).

3. Linear valve drive according to claim 1 or 2, characterized in that the receiving unit (64) comprises an axial lead-through (72), through which axial lead-through (72) the actuating means (38) extends, a clearance fit being provided between the actuating means (38) and the receiving unit (64).

4. Linear valve drive device according to one of the preceding claims, characterized in that the receiving unit (64) comprises a sleeve element (68), in particular wherein the spring (62) bears at one end (86) against the sleeve element (68) and/or wherein the spring device (60) engages the actuating means (38) in axial direction by means of the sleeve element (68).

5. Linear drive device according to claim 4, characterized in that the receiving unit (64) comprises a spring cartridge (66) with the spring chamber (78).

6. Linear drive device for a valve according to claim 5, characterized in that the spring cartridge (66) has an axial opening (76), the sleeve element (68) extending through the axial opening (76) with a clearance fit.

7. Linear valve drive according to one of claims 4 to 6, characterized in that the sleeve element (68) comprises a radially protruding collar (74), the spring (62) bearing at one end (86) against the collar (74).

8. Linear drive device for a valve according to any one of the preceding claims, characterized in that the spring (62) is received in the spring chamber (78) with a clearance fit in the radial direction.

9. Linear valve drive device according to one of the preceding claims, characterized in that each spring chamber (78) is a recess in the form of a cylinder, the height (H) of the spring chamber (78) in the axial direction being smaller than the height of the unloaded spring (62).

10. Linear drive device for a valve according to any one of the preceding claims, characterized in that the spring (62) is arranged in such a way that the central axis (80) of the spring (62) lies on a circle (82), which circle (82) is arranged concentrically to the adjustment axis (V), in particular wherein the springs (62) are distributed equidistantly on the circle (82).

11. Linear drive of a valve according to any of the preceding claims, characterized in that the valve closing member (32) comprises a diaphragm (50), which diaphragm (50) is moved by the actuation means (38), in particular wherein the diaphragm (50) transitions into the actuation means (38) in one piece.

12. Valve, in particular normally closed valve, comprising a valve linear drive (20) according to any of the preceding claims and a valve body (12) having a valve seat (30).

13. Valve according to claim 12, characterized in that the actuating means (38) comprises a tappet (44), which tappet (44) is coupled to the valve closure member (32) and has a radial shoulder (88), against which shoulder (88) the receiving unit (64) is pressed in an axial direction, in particular wherein the shoulder (88) is aligned with the valve seat (30) as seen in the axial direction.

14. Valve according to claim 12 or 13, comprising a valve linear drive (20) according to claim 11, characterized in that the diaphragm (50) has an outer annular sealing section (48), the annular sealing section (48) being clamped between the valve body (12) and the drive housing (34, 40) and/or the annular sealing section (48) being welded to the valve body (12) and/or the drive housing (34, 40).

15. The valve according to any one of claims 12 to 14, wherein the valve closure member (32) fluidly separates a fluid space (26) formed between the valve body (12) and the valve closure member (32) from a control space (58) formed between the drive housing (34) and the valve closure member (32).

Technical Field

The present invention relates to a valve linear drive device for connection to a valve body having a valve seat, and to a valve having such a valve linear drive device.

Background

Valves for open-loop or closed-loop control of a fluid are known in the prior art, which comprise a valve body and a valve linear drive formed separately from the valve body. The valve linear drive and the valve body are connected to each other to form a valve.

The valve linear drive comprises a drive unit, for example a piezo actuator. The drive unit may adjust the valve closing member by means of an actuating means or an actuating mechanism provided in the valve linear drive. In this way, the valve linear drive may move at least the valve closure member to an open position and/or a closed position in which the valve closure member rests on and seals against a valve seat formed in the valve body such that no fluid may flow through the valve.

It is also known from the prior art to employ spring means to urge the actuating means into the open position in the case of a so-called normally open valve (NO valve) or into the closed position in the case of a so-called normally closed valve (NC valve) to ensure a defined valve position in the event of a failure of the drive unit.

Due to temperature-related or service-life-related changes or manufacturing-related tolerances, in particular in the case of NC valves, it is challenging to ensure a long-term and reliable sealing of the valve seat by means of a spring device.

Disclosure of Invention

It is therefore an object of the present invention to provide a linear valve drive and a valve in which a defined valve position can be reliably ensured even in the event of a failure of the drive unit.

In order to achieve this object, a linear valve drive is proposed for connection to a valve body having a valve seat. The valve linear drive device has a drive housing, a valve closing member, an actuator, and a spring device. The valve closing member is adjustable between an open position and a closed position along an adjustment axis by means of an actuator and force transmitting actuation means, which are interposed between the valve closing member and the actuator. The spring means urge the actuating means into the open position or into the closed position. Furthermore, the spring device comprises a plurality of springs and a receiving unit for the springs. Here, each spring has its own spring chamber formed in the receiving unit, into which the associated spring is inserted. Furthermore, a valve having such a linear valve drive is provided.

It has been found that in the case of a spring arrangement with a single spring, the lateral forces occurring in the spring when the spring arrangement or the spring is loaded impair the return of the actuating means to a defined valve position. By providing a spring arrangement with a plurality of springs, the load is distributed between the springs and a lateral force occurs in each spring. These transverse forces can at least partially compensate each other compared to a single spring, whereby the transverse forces generated are minimized and a defined valve position can be reliably ensured. The spring chamber ensures an optimal arrangement of the springs relative to each other and relative to the valve seat. Furthermore, the spring chamber serves as a guide and thus the lateral forces occurring in the spring can be limited. The receiving unit also allows keeping the assembly work at a lower level.

In this way, in particular, seat tightness in NC valves is improved.

The spring means preferably comprises at least three springs to effectively minimize the occurring lateral forces.

The spring is in particular a helical spring or more generally a compression spring.

Furthermore, the spring means engage the actuation means, in particular in the axial direction.

In one embodiment, the actuator is a piezoelectric actuator.

In a further embodiment, the springs each bear against the drive housing at one of their ends, which ensures a defined force transmission and allows a particularly compact design of the valve linear drive.

The receiving unit may comprise an axial lead-through which the actuating means extends. Here, a clearance fit is provided between the actuating means and the receiving unit, so that the receiving unit has a play perpendicular to the adjustment axis relative to the actuating means. When the spring is loaded, the lateral force in the spring may cause that the relative position of the receiving unit with respect to the actuating means will correspondingly change slightly and the resulting lateral force is reduced.

Further, the following may be set: the receiving unit comprises a sleeve element. In particular, the springs are each supported against the sleeve element at one of their ends and/or the spring device is engaged with the actuating means in the axial direction by means of the sleeve element. In this way, the linear valve drive can have a particularly compact design. In addition, this configuration ensures an effective operative connection of the spring with the actuating means.

According to one embodiment, the receiving unit comprises a spring cartridge having a spring chamber.

The spring sleeve can have an axial opening through which the sleeve element extends with a clearance fit. The clearance fit allows the relative position of the spring cartridge with respect to the sleeve element to be correspondingly slightly changed perpendicular to the adjustment axis, so that the transverse forces generated thereby are reduced when the spring is loaded.

According to another embodiment, the sleeve element comprises a radially projecting collar against which the springs are each supported at one end, whereby the springs are effectively supported on the sleeve element and the spring force of the springs is introduced into the sleeve element.

The following settings may be made: the spring may be received in the spring chamber with a clearance fit in the radial direction. This clearance fit ensures that the spring can be deformed and/or displaced in the spring chamber to a limited extent perpendicular to the adjustment direction when the spring is loaded, as a result of which a small transverse force can occur in the spring. At the same time, the clearance fit ensures that the spring chamber guides the spring radially, thus ensuring a defined action of the spring.

In particular, the spring is not fixed in position by means of a pin engaged in the spring in the case of a helical spring, but for example via the end of the spring.

Furthermore, each spring chamber may be a recess in the form of a cylinder, the height of the spring chamber in the axial direction being smaller than the height of the unloaded spring. In this way, the spring chamber can constitute a guide for a considerable part of the spring without the spring losing its function.

In one embodiment, the spring is arranged in such a way that its central axis lies on a circle, which is arranged concentrically to the adjustment axis. Here, in particular, the springs are distributed equidistantly on the circle, so that all springs have the same angular distance from the spring adjacent to it. This symmetrical arrangement of the springs ensures an even distribution of the load on the springs and a valve position defined by the springs.

The valve closing member for example comprises a diaphragm which is moved by the actuating means when the actuating means is adjusted between the open and the closed position. In particular, the diaphragm transitions into the actuation means in one piece. The advantage of this configuration is that the linear valve drive is composed of a particularly small number of individual components and exhibits a particularly high degree of tightness.

In order to achieve the object defined above, according to the invention, a valve, in particular an NC valve, is also provided, which has a valve linear drive according to the invention and a valve body with a valve seat and which has the advantages mentioned above.

Here, the actuating means may comprise a tappet which is coupled to the valve closing member and has a radial shoulder against which the receiving unit is pressed in the axial direction. In particular, the shoulder is aligned with the valve seat when viewed in the axial direction, so that a particularly high seat tightness is ensured in the closed position.

According to one embodiment, the diaphragm has an outer annular sealing section that is clamped between the valve body and the drive housing. In this way, a reliable attachment can be produced in a simple manner.

Additionally or alternatively, the annular sealing section may be welded to the valve body and/or the drive housing to ensure a particularly tight connection.

In addition, according to another embodiment, the valve closing member fluidly separates a fluid space formed between the valve body and the valve closing member from a control space formed between the drive housing and the valve closing member. In this way, an effective and permanent medium separation between the fluid space and the control space can be ensured.

Furthermore, the valve body comprises at least one inflow duct and/or at least one outflow duct. These conduits are sealed in the closed position by means of a valve closing member.

Drawings

Other advantages and features of the present invention will become apparent from the following description and the accompanying drawings, in which:

fig. 1 shows a schematic view of a valve according to the invention with a linear valve drive according to the invention;

figure 2 shows an exploded view of a part of the valve according to figure 1;

figure 3 shows a cross-sectional view of a portion of the valve according to figure 1, with the valve linear drive in the closed position;

figure 4 shows a perspective view of a portion of the valve according to figure 1 with the valve body and the partially exposed housing portion; and

fig. 5 shows a top view of the spring device of the valve according to fig. 1.

Detailed Description

FIG. 1 illustrates a valve 10, the valve 10 being employed for open loop or closed loop control of a fluid. In the illustrated embodiment, the valve 10 is of a multi-piece configuration and includes: a valve body 12, the valve body 12 having a base body 14 and a flange section 16 projecting from the base body 14; and a valve linear drive 20, the valve linear drive 20 having an axial end coupled to the flange section 16.

The base body 14 has a fluid inlet 22 through which fluid to be open-loop controlled or closed-loop controlled is supplied to the valve 10, and a fluid outlet through which fluid can exit the valve 10. Here, the fluid outlet is located opposite the fluid inlet 22 in the base body 14 and is not shown in fig. 1.

The flange section 16 (see fig. 3) also has an inflow conduit 24 formed in the flange section 16, the inflow conduit 24 being in fluid communication with the fluid inlet 22. In the switching position, which is not shown in fig. 3, the inflow duct 24 leads to a fluid space 26, which fluid space 26 in turn is in fluid communication with four outflow ducts 28 (see fig. 2) leading to fluid outlets.

In alternative embodiments, the flange section 16 may of course include any desired number of inflow conduits 24 and/or outflow conduits 28.

More specifically, the valve body 12 is formed of a corrosion resistant material. In particular, the inner surfaces of the fluid-carrying conduits and spaces are made of corrosion-resistant materials.

Further, the inflow conduit 24 has a valve seat 30 (see fig. 3) associated with the inflow conduit 24, and a valve closure member 32 of the valve linear drive 20 cooperates with the valve seat 30 to provide open-loop or closed-loop control of flow through the valve 10, as will be discussed further below.

The valve linear drive device 20 includes a drive housing 34 (see fig. 1), an actuator 36, and an actuating means 38 (see fig. 2).

The drive housing 34 has a multi-piece configuration, and the drive housing 34 includes a pot-shaped lower portion 40 and a sleeve-shaped upper portion 42 seated on the lower portion 40, with the actuator 36 received in the upper portion 42.

The actuator 36 is intended to function as a drive unit, and the actuator 36 is force-transmittingly coupled to the valve closing member 32 by means of an actuating means 38.

In the present exemplary embodiment, the actuator 36 is a piezoelectric actuator in the form of a stacked actuator.

However, in principle, the actuator 36 may be any desired actuator, in particular any desired piezoelectric actuator.

The change in length of the actuator 36 is transmitted to the valve closing member 32 by means of the actuating means 38, whereby the valve closing member 32 can be adjusted along the adjustment axis V in the axial direction between an open position, in which the valve seat 30 is open and the inflow duct 24 is fluidly connected to the outflow duct 28, and a closed position, in which the valve seat 30 is closed and the inflow duct 24 is fluidly separated from the outflow duct 28.

The actuating means 38 here comprises a tappet 44 (see fig. 3), which tappet 44 extends in the axial direction as far as the valve closing member 32, and for example the tappet 44 continues into the valve closing member 32.

The valve closure member 32 comprises a valve sealing section 46 in the axial extension of the tappet 44, the valve sealing section 46 being associated with the inflow duct 24 or the valve seat 30 and being opposite to the inflow duct 24 or the valve seat 30 in the axial direction. In the closed position, the valve sealing section 46 is pressed against the valve seat 30 such that the valve seat 30 is closed.

In addition, the valve closure member 32 includes a radially outer annular seal section 48 and a diaphragm 50, the diaphragm 50 extending radially from the annular seal section 48 to the valve seal section 46 and defining the fluid space 26.

In an alternative embodiment, the valve sealing section 46 may be part of the diaphragm 50, i.e. the diaphragm 50 extends over the entire area enclosed by the annular sealing section 48.

The annular seal section 48 has a greater axial thickness D than the diaphragm 50 extending radially inward from the annular seal section 48.

In the illustrated embodiment, the tappet 44 is formed in one piece with the valve closure member 32, for example by welding the tappet 44 to the valve sealing section 46. Thus, diaphragm 50 integrally transitions into actuation means 38.

Of course, in alternative embodiments, the valve closure member 32 and the actuation means 38 may be provided as separate components that are suitably coupled to each other.

The pot-shaped lower portion 40 has: a bottom 52, the bottom 52 having a central lead-through 54, the actuating means 38 extending through the central lead-through 54 in the axial direction; and a circumferential wall 56, the circumferential wall 56 extending from the bottom 52 in the axial direction towards the flange section 16.

The base 52 and the valve closure member 32 define a control volume 58, the control volume 58 being permanently sealed from the fluid volume 26 by the valve closure member 32. Thus, the valve closure member 32 simultaneously constitutes a sealing barrier.

Furthermore, the valve closing member 32 is clamped with the annular sealing section 48 between the circumferential wall 56 and the flange section 16, such that the annular sealing section 48 seals both the fluid space 26 and the control space 58 from the outside.

Additionally or alternatively, after the valve linear drive 20 has been coupled to the valve body 12, the valve closure member 32 may be connected to the can-shaped lower portion 40 and/or the flange section 16 via an annular sealing section 48 by a substance-to-substance bond, in particular by welding, to reliably hermetically seal the valve 10.

The valve linear drive device 20 further includes a spring device 60, and the function and structure of the spring device 60 will be discussed below with reference to fig. 2-5.

The spring device 60 comprises seven springs 62 and a receiving unit 64, the receiving unit 64 having a spring cartridge 66 and a separate sleeve element 68.

In an alternative embodiment, the spring cartridge 66 and the sleeve element 68 may be formed together as one piece.

The sleeve member 68 has: a sleeve section 70, the sleeve section 70 having an outer diameter d₁(see fig. 3); and a central axial lead-through 72, the axial lead-through 72 having a diameter d₂And the axial lead-through 72 extends through the sleeve element 68 coaxially with the adjustment axis V; and a collar 74, the collar 74 being arranged at an axial end of the sleeve section 70 and protruding radially beyond the sleeve section 70, i.e. the collar 74 has a larger outer diameter.

Spring cartridge 66 has a central axial opening 76, the central axial opening 76 having a diameter d₃And a central axial opening 76 extends through the spring cartridge 66 coaxially with the adjustment axis V.

The sleeve element 68 and the spring cartridge 66 are arranged coaxially with each other and with the adjustment axis V. Furthermore, the sleeve section 70 is arranged radially within the axial opening 76. The outer diameter d of the sleeve section 70 is in this case₁And the diameter d of the axial opening 76₃Each having dimensions such that the spring cartridge 66 is radially mounted on the sleeve section 70 with a clearance fit.

The spring cartridge 66 also includes seven spring chambers 78, the spring chambers 78 being arranged in an annular shape about the axial opening 76. Here, each spring chamber 78 constitutes a receptacle for a respective spring 62. In other words, each spring 62 is disposed in a respective individual spring chamber 78.

The spring chambers 78 are respective cylindrical recesses that extend through the spring cartridge 66 in the axial direction, and the spring chambers 78 may be, for example, bores.

In an alternative embodiment, in particular in the case of a one-piece receiving unit 64, the spring chamber 78 cannot extend completely through the spring cartridge 66 or the receiving unit 64 in the axial direction, and the spring chamber 78 can be in the form of a blind hole, for example.

The central axis 80 (see fig. 3) of the spring chamber 78 lies on a circle 82 (see fig. 5) having a radius R, the circle 82 being arranged concentrically with the adjustment axis V. Here, each angle α between the central axes 80 of adjacent spring chambers 78 is one seventh of the circumference of a circle, i.e. approximately 51.43 degrees, so that the spring chambers 78 are evenly distributed on the circle 82.

The springs 62 are identically shaped helical compression springs, each spring 62 having a first end 84 and an opposite second end 86.

In principle, in alternative embodiments, the springs 62 may each be formed by any one or more spring elements.

The diameter of the spring chamber 78 and the diameter of the spring 62 are matched to one another such that the spring 62 is received in the spring chamber 78 with a clearance fit in the radial direction.

A spring means 60 is arranged in the control space 58 between the bottom 52 and the valve closing member 32 coaxially with the adjustment axis V. The tappet 44 extends in the axial direction through the axial leadthrough 72, and the tappet 44 has an outer diameter d in the region of the sleeve section 70₄Outer diameter d₄Diameter d of axial lead-through 72₂The mating is such that the spring means 60 is mounted on the tappet 44 with a clearance fit in the radial direction.

The springs 62 are each supported against the base 52 by a first end 84 of the spring 62 and against the radial collar 74 by a second end 86 of the spring 62.

In the closed position, the springs 62 are each at least partially compressed and pass through a spring force F in an axial direction away from the base 52_FActing on the sleeve element 68.

Thus, in the uncompressed state, the springs 62 each have an axial length that is greater than the axial height H of the spring chamber 78 such that the springs 62 will correspondingly protrude from the spring chamber 78 in the axial direction.

In this case, the spring device 60 is supported by means of the sleeve element 68 on a radial shoulder 88 of the tappet 44, and the spring device 60 uses a spring force F_FThe valve closure member 32 is pressed into the closed position.

Here, the radial shoulder 88 of the tappet 44 is arranged in alignment with the valve seat 30, i.e. the valve seat 30 intersects the radial shoulder 88 when the valve seat 30 and the radial shoulder 88 are theoretically displaced into a common plane parallel to the adjustment axis V.

Here, the radial shoulder 88 is accommodated in a coaxial, concavely shaped recess 90 (see fig. 3) in the sleeve element 68, as a result of which the valve linear drive 20 has a particularly compact design.

Due to this mounting situation, the individual springs 62 act independently of one another and can be at least partially compensated for a multidimensional stress state. In particular, the transverse force F_QReduce or be compensated for, the transverse force F_QActing radially with respect to the adjustment axis V and the transverse force F_QThe defined position of the valve closure member 32 and thus the tightness of the valve seat 30 in the closed position can be impairedOr compensated for.

In particular by transmitting the spring force F_FIs mounted in a clearance fit in such a way that any transverse forces F occurring_QEffectively reducing it.

The number of springs 62 and the nature of the springs 62 are selected according to the requirements and dimensions of the valve 10.

In the illustrated embodiment, the components, such as the tappet 44, the receiving unit 64, the spring 62, and the spring chamber 78, include portions having a circular cylindrical geometry. Of course, in alternative embodiments, each or portions of these components may be configured as desired, particularly as a cylindrical body having any desired base area.

The mode of operation of the valve 10 will be discussed below with reference to fig. 3.

The valve 10 is a normally closed valve, i.e. an NC valve. This means that the valve closure member 32 is in the closed position of the valve closure member 32 when no voltage is applied to the piezoelectric actuator 36. This closed position is shown in fig. 3.

In order to switch the valve 10 from the closed position of the valve 10 to the open position of the valve 10, a voltage is applied to the piezoelectric actuator 36, the piezoelectric actuator 36 exerting a driving force F on the actuating means 38_A。

Therefore, the driving force F from the piezoelectric actuator 36_AGreater than the spring force F of the spring means 60_FSo that the valve closing member 32 can resist the spring force F of the spring means 60_FAnd (4) shifting.

To transition the valve 10 from the open position of the valve 10 to the closed position of the valve 10, the piezoelectric actuator 36 is simply de-energized or no longer applies the previously applied voltage. This returns the piezoelectric actuator 36 to the initial position of the piezoelectric actuator 36 in terms of valve control engineering. Spring force F of spring means 60_FThe valve closure member 32 is pressed in a sealing manner against the valve seat 30. This clearly shows that the valve 10 is a normally closed valve.

In an alternative embodiment, the valve 10 may be a normally open valve, i.e. a NO valve. This means that the valve closure member 32 is at the valve closure member 32 when no voltage is applied to the piezoelectric actuator 36An open position. In this case, the valve linear drive 20 is correspondingly designed such that the spring device 60 exerts a spring force F on the actuating means 38 which pulls the valve closing member 32 away from the valve seat 30 into the open position_FThe spring means 60 exerts a spring force F on the actuation means 38 that pulls the valve closure member 32 away from the valve seat 30 into the open position, for example by configuring the spring 62 as a tension spring, or by providing the spring means 60 on the opposite side of the bottom 52 such that the bottom 52 is arranged between the valve closure member 32 and the spring means 60 and such that the spring means 60 bears against a radial shoulder 88 of the tappet 44 opposite the bottom 52_F。

Thus, in all embodiments, a valve linear drive 20 and a valve 10 having a spring device 60 are provided, the valve linear drive 20 and the valve 10 exhibiting a low lateral force F when subjected to a load_QAnd thus a defined valve position is reliably ensured.