Extrusion valve for flowable medium

Abstract

The invention proposes a squeeze valve (1) having a valve housing (2) in which a hose-shaped valve segment (4) extends, a plurality of squeeze elements (23, 24) being arranged in the region of a radial outer periphery (22) of the valve segment, which squeeze elements can each perform a working movement (28) in order to compress the valve segment (4) more or less strongly. The drive movement (28) can be brought about by a drive mechanism (36) having a drive shaft (42), which can be driven into a rotational drive movement (55) by means of an input drive torque. A conversion mechanism (37) having an engagement transmission (38) converts the rotational drive movement (55) of the drive shaft (42) into the linear working movement (28) of the squeeze elements (23, 24).

Description

Technical Field

[0001] The present invention relates to a queschventil for a flowable medium, having a valve housing in which a flexible, tubular valve link with a flexible peripheral wall extends and passes through a valve passage in its longitudinal direction. A plurality of queschventilating elements are arranged radially around the outer periphery of the valve link, the queschventilating elements being capable of moving toward and away from each other in a working plane perpendicular to the longitudinal axis of the valve link while performing linear working motion, so as to more or less strongly compress the valve link, and the queschventilating valve having a drive mechanism for actuating the working motion of the queschventilating elements. Background Technology

[0002] The type of squeeze valve known from EP 1 912 001 B1 has two stempelartige squeeze elements arranged linearly within the valve housing in radially displaceable guide slots, wherein the squeeze elements abut against the outer periphery of a hose-shaped valve link in a region diametrically opposed to each other. The squeeze elements can be driven by a drive mechanism to perform working movements in a working plane, thereby more or less strongly compressing the valve link to affect the flow cross-section of the valve passage through the valve link. The drive mechanism has a sleeve-shaped reversing element surrounding the valve link and the squeeze elements, having a tapered groove structure at its inner periphery, by means of which the reversing element can slidably abut against the squeeze elements. By means of a fluid-loadable drive piston, also part of the drive mechanism, the reversing element can move back and forth against the force of a spring mechanism to adjust the desired working position of the squeeze elements. For the drive mechanism, other drive mechanisms can also be considered, such as electromagnetic types and / or drive mechanisms with rod drives.

[0003] The squeeze valve known from EP 2 663 794 B1 has a hose-shaped valve link surrounded laterally by two squeeze elements, which are surrounded by a sleeve-shaped actuating element. The actuating element has multiple grooves on its inner side, constructed according to a multi-start thread type, into which the squeeze elements engage. A twisting process occurs when the actuating element is twisted, during which the multi-start thread moves over the squeeze elements. Because the grooves of the multi-start thread have varying depths, the twisting process causes the squeeze elements to be radially displaced about the valve link, wherein the valve link is more or less strongly compressed.

[0004] DE 10 2013 012 158 A1 discloses a squeeze valve having two rod-shaped squeezing elements arranged on opposite diametrically opposed sides of a hose-shaped valve segment and passing through a sleeve-shaped actuating element coaxial with the valve segment. The actuating element acts on the squeezing elements via linear movement of a slotted opening, causing the squeezing elements to move laterally to the valve segment. The squeezing elements also pass through a sleeve-shaped valve housing of the squeeze valve, wherein the protruding end section of the squeezing element from the valve housing is held in place by a fixing body and secured to prevent it from falling out. A drive mechanism is provided to actuate the actuating element, which can be configured for electric or manual operation. A lever mechanism can be provided as the transmission mechanism. Summary of the Invention

[0005] The present invention is based on the objective of providing a squeeze valve that can be easily and precisely operated with a simple and compact structure.

[0006] To solve the aforementioned task, in the case of a squeeze valve incorporating the features mentioned at the beginning, the drive mechanism is configured such that it has a drive shaft that is torsionally supported on the valve housing about a rotation axis extending longitudinally along the drive shaft, and the drive shaft has an operating section into which the drive torque causing the rotational drive motion of the drive shaft can be introduced. Furthermore, the drive mechanism has a conversion mechanism with a meshing transmission mechanism that converts the rotational drive motion of the drive shaft into the linear working motion of the squeeze element.

[0007] The squeeze valve according to the invention allows for the control of the flow of any flowable medium, such as, for example, liquid, gas, or powder. By means of a drive mechanism, the squeeze element can be driven to perform a working movement transverse to the longitudinal axis of the valve segment, so as to more or less strongly compress the valve segment with its flexible peripheral walls. In this way, the working position of the squeeze element can be adjusted, either allowing the medium to pass through the valve passage or closing the valve passage to prevent the medium from passing through. In other words, the flow cross-section provided by the valve passage can be changed and / or adjusted by the squeeze element. The driving force necessary for the adjustment and positioning of the squeeze element can be easily introduced as torque into a drive shaft rotatably supported at the valve housing, the drive shaft having an operating section configured for introducing torque. Smooth and precise operation of the squeeze element is ensured by a conversion mechanism that converts the rotational drive motion of the drive shaft into the linear working motion of the squeeze element, equipped with a meshing transmission mechanism. The meshing transmission mechanism can be easily implemented with the desired transmission ratio and, despite this, placed in a small space, thus achieving an overall compact size for the squeeze valve. The low wear of the meshing drive mechanism results in a long service life and thus corresponding customer advantages. The drive mechanism can be optionally configured for digitally operated "on / off" or for stepless adjustment of the flow cross-section provided by the valve passage between fully closed and fully open. In this way, stepless flow regulation is particularly possible. In particular, the valve body can be cost-effectively made of plastic or, for demanding applications, of stainless steel.

[0008] Advantageous improvements of the invention are derived from the dependent claims.

[0009] Of particular advantage is the implementation of the squeeze valve in a manually operated structural type. The squeeze valve can then be conveniently and manually operated with self-sufficiency. The manually operable squeeze valve has a handle arranged in the operating section of the drive shaft, outside the valve housing and easily gripped, to introduce the adjusted drive torque that causes rotation of the drive shaft. A handle is considered particularly suitable as a lever with at least one, and preferably exactly one, lever arm that can be manually gripped. This achieves operation with very little force consumption and also allows inference of the current adjusted operating state of the squeeze valve based on the current swing position. Instead of a lever, a compact handle or handwheel can also be provided, for example. The manually operable squeeze valve can be manufactured and operated at a very low cost.

[0010] Nevertheless, it is feasible without problems to provide a squeeze valve with a structure that can be operated by a motor. Here, a drive motor is particularly considered as the drive source. The drive motor particularly relates to an electric motor, although a fluid motor, such as a fluid-operated rotary actuator, can also be considered. The electrically operated drive motor is particularly implemented as a stepper motor or a servo motor, which facilitates very precise rotational positioning of the drive shaft for the purpose of adjusting the desired flow cross-section of the valve passage.

[0011] The drive motor is suitably mounted as a rotor on the valve housing and has an output shaft that can be rotatably driven, which is connected to the operating section of the drive shaft to transmit torque. In a particularly cost-effective configuration, the operating section is formed directly from the output shaft of the drive motor, thereby eliminating the need for a shaft connection.

[0012] In principle, a squeeze valve can have any number of squeeze elements. It is considered particularly suitable that the squeeze valve is equipped with only two squeeze elements, which are located in diametrically opposed peripheral regions on the outer periphery of the valve element. The two squeeze elements can move along a common, perpendicular to the longitudinal axis of the valve element and within the working plane, to perform their respective working movements. Suitablely, when viewed along the longitudinal direction of the valve element, the working axis extending through the two squeeze elements is spaced apart from and orthogonal to the rotation axis of the drive shaft along the longitudinal direction of the valve element.

[0013] For the drive shaft, an eccentric arrangement with respect to the valve link is recommended, so that its axis of rotation is spaced apart from the longitudinal axis of the valve link. The drive shaft is particularly positioned in the longitudinal region of the valve body. The axis of rotation of the drive shaft is suitably aligned with its longitudinal axis.

[0014] The engagement transmission mechanism of the conversion mechanism suitably has an input tooth that is anti-rotationally connected to the drive shaft and thus performs the drive motion of its rotation, and further has an output tooth that is continuously engaged with the input tooth, the output tooth being kinematically coupled to the extrusion element so as to cause the working motion of the extrusion element.

[0015] A feasible configuration of the squeeze valve is one in which the output teeth of the engagement transmission mechanism are directly located at the squeeze element. In this case, each squeeze element has a section with output teeth. However, a preferred embodiment of the squeeze valve is one in which the output teeth are not directly located at the squeeze element, but rather located at at least one other structural component of the conversion mechanism that connects between the drive shaft and the squeeze element. This allows for the manufacture of the squeeze element at a particularly cost-effective rate.

[0016] Preferably, the switching mechanism includes a reversing element disposed within the valve housing and between the extrusion element and the drive shaft. The reversing element, driven by the drive shaft, is capable of displacement relative to the valve housing and also relative to the valve segment along its longitudinal direction during a linear reversing motion, referred to as a linear reversing motion. It has a groove structure at which the extrusion element can slidably abut, thereby sliding along the groove structure during the linear reversing motion of the reversing element. Thus, the extrusion element is driven to perform a working motion perpendicular to the longitudinal axis of the valve segment during the linear reversing motion of the reversing element.

[0017] Particularly suitable is that the output teeth are arranged at the commutation stage. The commutation stage is preferably a one-piece body, with the output teeth directly integrated into said body. Such a commutation stage can be cost-effectively manufactured from plastic, for example, by injection molding.

[0018] Preferably, the reversing element is sleeve-shaped and arranged in the valve housing such that it coaxially surrounds the valve element. A groove structure is suitably constructed at the inner periphery of the reversing element.

[0019] Within the range of the reversing motion, the reversing element can be suitably displaced between two axial end positions opposite each other. One of the two axial end positions represents a locked position that causes the valve passage to close and thereby prevents the medium from flowing through the valve passage, while the other end position represents a released position that is responsible for releasing the maximum flow cross-section of the valve passage.

[0020] Preferably, the reversing element can be steplessly positioned between the end positions of the two axes to adjust the free flow cross-section of the valve passage between its maximum open and closed positions.

[0021] A spring mechanism is suitably arranged in the valve body, which continuously preloads the reversing element to one of its two axial end positions. This preload is suitably carried to the locked position, thereby forcing the valve into a "normally closed" type. Alternatively, the spring mechanism can also be arranged such that the reversing element is continuously preloaded to the release position. The spring mechanism particularly relates to a mechanical spring mechanism, although it can also alternatively be constructed as an air spring.

[0022] The squeeze valve can also be implemented without a spring mechanism, so that only an externally introduced adjusting force acts on the reversing link and thus on the squeeze element.

[0023] The output teeth of the meshing transmission mechanism are suitably located at the outer periphery of the reversing element. In principle, they can extend around the reversing element along the periphery of the valve element; however, preferably, they occupy only a limited periphery section of the outer periphery of the reversing element along the periphery of the valve element.

[0024] The meshing transmission mechanism is preferably constructed as a rack and pinion mechanism, wherein the input teeth are constructed as arc-shaped curved toothed rings, and the output teeth are constructed as racks with linear extensions. In this case, the output teeth have a plurality of teeth that are axially sequential along the longitudinal direction of the valve element and spaced apart from each other by the tooth space, wherein the arc-shaped curved toothed rings of the input teeth can roll under the driving motion of the rotation of the drive shaft. Regarding the sleeve-shaped reversing element, the rack is preferably integrated into the reversing element in one piece by the corresponding contour of the reversing element.

[0025] Preferably, by simultaneously engaging the gear ring and the rack, the reversing element equipped with the rack is torsionalally fixed with respect to the valve housing, thereby reliably ensuring the desired meshing engagement even if the rack extends only a portion of the outer periphery of the reversing element along the circumferential direction of the valve element.

[0026] The arc length of the gear ring in the input section is, in principle, arbitrary; however, it is preferably less than 360 degrees. The arc length of the gear ring is particularly chosen such that the meshing engagement extends to a rotation angle of the drive shaft corresponding to the maximum travel of the reversing element between its two axial end positions.

[0027] Advantageously, the squeeze valve has a stop mechanism by which two opposing end positions of the drive motion of the drive shaft rotation are mechanically preset. These two end positions, depending on the rotation angle, correspond in particular to the two axial end positions of the reversing element, in which the squeeze element either occupies the closed position of the closed valve passage or the open position of the release valve passage with the largest flow cross-section.

[0028] The stop mechanism suitably has two stop surfaces arranged at the drive shaft and thus rotating together in a drive motion, and two mating stop surfaces arranged on the valve housing in the swing path of the stop surfaces, wherein the two stop surfaces are preferably formed by the tooth flanks of two closed toothed rings on opposite sides. The latter has the advantage that the teeth can perform a dual function, namely, for transmitting driving force on the one hand, and for presetting the end position of the drive shaft according to the rotation angle on the other hand.

[0029] Preferably, the drive shaft is equipped with a manually operable locking mechanism for disengagingly locking the drive shaft to different rotational positions. This provides the advantage of being able to disengage and fix the valve passage at different sizes of released flow cross-sections, including a completely closed valve passage, without having to continuously supply torque to the drive shaft to maintain a fixed rotational position. In this way, it is particularly possible to fix the valve passage in an intermediate position between the closed position and the open position where the maximum flow cross-section is released. The locking action of the locking mechanism also helps to resist the operating force of the spring mechanism acting on the reversing element.

[0030] To achieve an advantageous design for the locking mechanism, the drive shaft is suitably capable of restricted axial movement relative to the valve housing. In a coaxial arrangement, the drive shaft has an axially oriented annular surface, and an annular mating locking surface disposed on the valve housing is axially opposed to this annular surface. Furthermore, the locking mechanism in this case includes a manually operable tensioning element acting on the drive shaft. Operation of this tensioning element causes axial adjustment of the drive shaft and the locking surface together, so that the locking surface can be optionally positioned in a locking position where it cannot be torsionally clamped to the mating locking surface and thus cannot torsionally lock the drive shaft, or in a disengaged position that allows for torsion of the drive shaft.

[0031] The tensioning element is specifically configured as a tensioning nut screwed onto the drive shaft, which is supported on the outer surface of the valve housing during rotational operation relative to the drive shaft, so as to apply an axial tension to the drive shaft and clamp the locking face with the mating locking face by the tension.

[0032] The locking surface and mating locking surface can be implemented for the combined effect of frictional engagement, which is beneficial for steplessly locking the drive shaft in different rotational positions. In other particularly advantageous embodiments, the locking surface and mating locking surface are toothed, so that they engage with each other in a form-fitting manner in the locking position of the locking surface. This type of locking provides particularly effective protection against unintentional disengagement, even when the valve is subjected to vibration during its use. Attached Figure Description

[0033] The invention will then be explained in more detail with reference to the accompanying drawings. Wherein: Figure 1 An isometric diagram showing a preferred embodiment of the squeeze valve according to the invention in its operating state in the open position for maximum flow through the valve element. Figure 2 Shown from Figure 1 The squeeze valve in operation in the closed position, used to interrupt flow in the case of a locked valve link. Figure 3 Showing the occupation basis Figure 1 The opening position of the squeeze valve is based on the Figure 4 The cross-section of section line III-III, in which the portion of the drive shaft framed by dashed lines is also described separately again without sectioning. Figure 4 Showing according to from Figure 3 The longitudinal section along section line IV-IV, Figure 5 The squeeze valve in the operating state in the closed position is shown based on... Figure 6 The cross-section of the cutting line VV, Figure 6 The basis for showing the squeeze valve comes from Figure 5 The longitudinal section along section line VI-VI, Figure 7 The squeeze valve is shown according to the information from... Figure 3 The side view without showing the valve housing, showing the line of sight of arrow VII-VII, and Figure 8 The isometric diagram shows the source from Figure 7 Components. Detailed Implementation

[0034] The squeeze valve, generally labeled with reference numeral 1, has a valve body 2 and extends along an imaginary longitudinal axis 3. The axial direction of the longitudinal axis 3 is also referred to below as the longitudinal direction 3 of the squeeze valve 1, using the same reference numerals.

[0035] Within the internal space 10 of the housing surrounded by the valve housing 2, a flexible hose-shaped element, functioning as a valve link 4, extends between two media connection portions 6 and 7 constructed at the valve housing 2. This element is longitudinally traversed by a flexible hose passage, referred to as the valve passage 5, which communicates with the two media connection portions 6 and 7. When the valve passage 5 has a free flow cross-section, as in this… Figure 3 and 4 As described, the flowable medium delivered at one of the medium connection parts 6 or 7 can flow through the valve passage 5 and then flow out from the squeeze valve 1 at the opposite connection part 7 or 6.

[0036] Valve element 4 has a longitudinal axis 9, which overlaps with the longitudinal axis 3 of the squeeze valve 1. The two media connection parts 6 and 7 are suitably constructed in the closed walls 14a and 14b of the two opposite ends of the valve body 2 along the longitudinal direction 3.

[0037] The flowable media whose flow can be controlled by the squeeze valve 1 are particularly liquids or gases. Liquids include, for example, water or process fluids, and gases include, for example, compressed air. However, the squeeze valve is also suitable for controlling media in the form of powders, granules, or pastes, as long as they have flowable characteristics.

[0038] The flexible valve element 4 is capable of elastic deformation, at least radially. The valve element has a flexible peripheral wall 8 surrounding the valve passage 5, which is capable of elastic deformation, particularly rubber-like, at least laterally and especially perpendicular to the longitudinal axis 9. Preferably, the valve element 4 is made of an elastic material. To improve compressive strength, reinforcing structures can be embedded in the peripheral wall 8.

[0039] Extending between the two end-side closed walls 14a, 14b is a radially externally tubular wall section 14c of the valve housing 2 that surrounds the internal space 10 of the housing. This wall section is exemplaryly connected in one piece to one of the end-side closed walls 14b, thereby forming, in particular, a cup-shaped housing section of the valve housing 2. The other end-side closed wall 14a is fixed to the open end of the tubular wall section 14c, for example, by ultrasonic welding. The valve housing 2 is preferably made entirely of plastic material; however, it can also be made of metal, for example.

[0040] Exemplarily, valve link 4 has flange sections 4a and 4b at the two axial end sides, respectively, which are pressed from the axial interior to the closing walls 14a and 14b of the adjacent end sides in a sealed manner in the transition region to a corresponding medium connection of the two medium connection parts 6 and 7.

[0041] Preferably, the valve link 4 is surrounded in the region of its radially outer periphery 22 by a support structure 15 separated from the valve housing 2, the support structure being arranged within the housing's internal space 10. In the state of maximum radial expansion of the valve passage 5, providing the medium flowing through with the maximum possible free flow cross-section, the flexible peripheral wall 8 of the valve link 4 is supported at the support surface 16 of the support structure 15 extending around the valve link 4, thereby preventing the peripheral wall from overstretching.

[0042] Exemplarily, the support structure 15 has two corresponding semi-shell-shaped support elements 17a and 17b with arcuate cross-sections, which are placed radially from opposite sides onto the outer peripheral surface of the flexible peripheral wall 8 in the case of forming a sleeve-shaped structure. Each support element 17a and 17b has a face section of a support surface 16. To hold the two support elements 17a and 17b together, the two support elements, together with the valve link 4 surrounded therefrom, are inserted into a support tube 18, which extends within the housing interior space 10 between the two end-side closing walls 14a and 14b, and is fixed to the closing wall by one of its two axial end sections 18a and 18b, respectively.

[0043] Preferably, the support structure 5, depending on the type of sleeve (Patrone), is inserted into the internal space 10 of the housing.

[0044] A plurality of elements, referred to as extrusion elements 23, 24 and preferably constructed in a punch-like shape, are arranged around the radial outer periphery 22 of the valve link 4. These elements are capable of linear reciprocating motion in a working plane 25 perpendicular to the longitudinal axis 9 of the valve link 4. Preferably, exactly two such extrusion elements 23, 24 are involved, as is the case in this embodiment. The two extrusion elements 23, 24 are placed in peripheral regions of the radial outer periphery 22 of the valve link 4 that are diametrically opposed to each other and lie on a common, imaginary axis 26 that overlaps with the working plane 25, which should be referred to as the working axis 26. The working axis 26 extends perpendicular to and intersects the longitudinal axis 9 of the valve link 4.

[0045] Each extrusion element 23, 24 has an extrusion surface 27 at its end facing the flexible peripheral wall 8, wherein the extrusion surfaces 27 of the two extrusion elements 23, 24 face each other along the axial direction of the working axis 26.

[0046] Each extrusion element 23, 24 is capable of performing a linear working motion 28 oriented along the axial direction of the working axis 26 and illustrated by a double arrow. The working motion 28 is capable not only of pointing inward (that is, along the direction toward the flexible peripheral wall 8), but also of pointing outward with respect to it (that is, away from the longitudinal axis 9 of the valve link 4).

[0047] Preferably, each extrusion element 23, 24 has a plate-shaped base shape with a main extension plane perpendicular to the longitudinal axis 3 of the extrusion valve 1.

[0048] The extrusion elements 23 and 24 are capable of moving toward and away from each other within the range of their linear working motion 28, so as to more or less strongly compress the valve link 4 in order to change the current flow cross-section provided by the valve passage 5. The extrusion force is applied through the extrusion surface 27 to the opposing peripheral wall sections 8a and 8b of the flexible peripheral wall 8 along the axial direction of the working axis 26.

[0049] Through the working motion 28, the extrusion elements 23 and 24 can be positioned so that they can move from... Figure 3 and 4 In the open position shown, the spacing between them has a maximum value, and in the open position, the flexible peripheral wall 8 is not or only slightly compressed, so that the valve passage 5 has a maximum flow cross-section, which allows for the maximum flow of the medium to be controlled.

[0050] The extrusion elements 23 and 24 can also be positioned within the range of the working motion 28 to be able to move from Figure 5 and 6 In the closed position, as seen in the diagram, the compression elements, while compressing the flexible peripheral wall 8, are brought close to each other to such an extent that the opposing peripheral wall segments 8a and 8b of the flexible peripheral wall 8 along the axial direction of the working axis 26 are pressed together with a sealing effect, thereby closing the valve passage 5 and no longer providing a free flow cross-section for the medium to be controlled to pass through the valve link 4. Along the axial direction of the transverse axis 32 (which is perpendicular not only to the longitudinal axis 9 of the valve link 4 but also to the working axis 26), the compression elements 23 and 24 have a sufficiently large length in the region of their compression surfaces 27 to compress the flexible peripheral wall 28 across its entire diameter.

[0051] Preferably, the extrusion elements 23 and 24 can also be positioned in any intermediate position between the open and closed positions to release the flow cross-section of the valve passage 5 between its zero flow cross-section and the maximum flow cross-section released in the open position.

[0052] It can be seen that the flow of the medium necessary for the current use of the squeeze valve 1 can be adjusted by positioning the selected squeeze elements 23 and 24.

[0053] The support structure 15 has a preferably slotted wall perforation 33 in the region of each of the two extrusion elements 23, 24, through which the respective associated extrusion elements 23, 24 can slide and shift to achieve the working movement 28. Preferably, the limiting surface of each wall perforation 33 forms a guide surface for linearly guiding the associated extrusion elements 23, 24 during their working movement 28.

[0054] Each extrusion element 23, 24 has a loading head 34 on its back side opposite the extrusion surface 27 in the axial direction along the working axis 26. An adjustment force 35 can be introduced into the loading head 34 to shift the associated extrusion valve 23, 24 from the open position to the closed position. When the adjustment force 35 is removed, the extrusion elements 23, 24 are back-pressed in the direction toward the open position by the peripheral wall 8, which expands due to the internal pressure present in the valve passage 5.

[0055] To generate the working motion 28 and, in particular, the adjusting force 35, the squeeze valve 1 is equipped with a drive mechanism 36. The drive mechanism 36 includes a conversion mechanism 37, which in turn has an engagement transmission mechanism 38.

[0056] The drive mechanism 36 has a drive shaft 42 supported on the valve housing 2 such that it can be twisted relative to the valve housing 2 about a rotation axis 43 extending in the longitudinal direction of the drive shaft 42. The drive shaft 42 has a longitudinal axis 44, and the rotation axis 43 suitably overlaps with the longitudinal axis.

[0057] The drive shaft 42 suitably extends within a drive space 45 surrounded by the valve housing 2, which is longitudinally connected to the interior space 10 of the housing and opens into the interior space 10 of the housing through a window-shaped perforation 46. To form the drive space 45, the housing wall of the valve housing 2 suitably has a localized bulge 47.

[0058] The drive shaft 42 has a rearward end section that functions as an actuation section 48, protruding from the drive space 45 via this end section. In the region of the drive space 45 through which the drive shaft 42 passes, a support ring 52 surrounding the drive shaft 42 is fixed in the valve housing 2, its radially inner peripheral surface suitably forming a sliding support surface for rotatably supporting the drive shaft 42. A sealing ring 53 is suitably maintained in the length section of the drive shaft 42 passing through the support ring 52, abutting against the support ring 52 and sealing the drive space 45 towards the surrounding environment.

[0059] Suitablely, in order to perform the rotational support measures, the drive shaft 42 has a support sleeve 54a coaxial with the longitudinal axis 44 at its front end section opposite the operating section 48, the support sleeve engaging into a complementary wall depth 54b of the valve housing 2 and being radially supported therein in a torsionally oriented manner.

[0060] The control section 48 is configured to introduce a drive torque that causes a drive motion 55 of the drive shaft 42 about the rotation axis 43, as indicated by the double arrows. The drive motion 55 can be performed bidirectionally.

[0061] Advantageously, corresponding to the illustrated embodiment, the squeeze valve 1 is of the type that can be manually operated. That is, the drive torque for the drive shaft 42 can be conveniently introduced manually into the operating section 48. For this purpose, a handle 56, accessible from outside the valve housing 2, is provided in the operating section 48 in a rotationally resistant manner. The handle 56 is exemplary in the form of a lever 57a having a rod arm 57a projecting radially from the axis of rotation 43. The lever 57 is fixed in a rotationally resistant manner to or on the operating section 48 via a fixed section 57b, wherein the lever can be pressed up or screwed on, for example.

[0062] In order to induce the rotational drive motion 55, the lever 57 can be gripped and swung by hand at the lever arm 57a.

[0063] According to other embodiments, the squeeze valve 1 can also be a type that can be operated by a motor. In this case, instead of a handle 56, there is a... Figure 3 The drive motor 58, illustrated by dashed lines, has a stator 58a fixed to the valve housing 2 and an output shaft 58b that can be rotatably driven thereto, wherein the output shaft 58b is drivably connected to the operating section 48 or directly forms the operating section 48 itself. The drive motor 58 is preferably an electric motor, particularly a servo motor or a stepper motor.

[0064] The aforementioned conversion mechanism 37 is designed such that it converts the rotational drive motion 55 of the drive shaft 42 into the linear working motion 28 of the extrusion elements 23 and 24.

[0065] The engagement transmission mechanism 38 and the reversing link 62, which directly cooperates with the pressing elements 23 and 24 to apply the adjustment force 35, belong to the conversion mechanism 37. The reversing link 62 is cylindrically constructed and arranged coaxially around the valve link 4 in the internal space of the valve housing 2. Here, the reversing link is preferably located in an annular spatial segment 63 of the internal space 10 of the housing, which is constructed between the support structure 15 and the tubular wall segment 14c. The reversing link 62 can linearly move back and forth relative to the valve link 4 and relative to the valve housing 2 along the longitudinal direction 9 of the valve link 4, wherein the movement that can be implemented here is referred to as linear reversing movement 64 and is illustrated by double arrows in the drawings.

[0066] Preferably, the reversing element 62 is radially supported at the radial outer peripheral surface of the support tube 18 and / or at the radial inner peripheral surface of the wall section 14c of the tube while ensuring axial displacement, so that the reversing element undergoes precise linear guidance for its reversing movement 64.

[0067] A sleeve-shaped reversing element 62 extends radially outward beyond the loading heads 34 of the extrusion elements 23 and 24. Its radially inner peripheral surface is provided with a groove structure 65, which slidably abuts against the loading heads 34 of the extrusion elements 23 and 24. The groove structure 65 is constructed such that the inner diameter of the sleeve-shaped reversing element 62 gradually changes axially between a segment with the largest inner diameter 66a and a segment with the smallest inner diameter 66b spaced axially apart.

[0068] Within the range of the linear reversing motion 64, the reversing element 62 can displace within the valve housing 2 between two opposing axial end positions. From Figure 3 and 4 The end position of the first axial direction that can be seen should be referred to as the release position of the reversing element 62 and, relative to it, from Figure 5 and 6 The end position of the second axis that can be seen in the diagram is called the locking position of the reversing link 62.

[0069] In the release position of the reversing link 62, the section 66a with the largest internal diameter of the chute structure 65 is at the same height as the loading head 34 of the extrusion elements 23 and 24, which allows the extrusion elements 23 and 24 to occupy the position from the... Figure 3 and 4 The open position can be seen in the diagram. In the locked position of the reversing link 62, the smallest diameter section 66b of the chute structure 65 is at the same axial height as the loading head 34, thereby moving the pressing elements 23 and 24 from the... Figure 5 and 6 The closed position can be seen in the middle.

[0070] In other words, it can be seen that the chute structure 65 applies the adjusting force 35, which is used to cause the working motion 28, to the two extrusion elements 23, 24.

[0071] A gradual transition occurs appropriately between the section 66a with the largest internal diameter and the section 66b with the smallest diameter, that is, the gradual change in the internal diameter of the reversing link 32, resulting in a gradual, especially smooth, change in the position of the extrusion elements 23 and 24 during the reversing motion 64.

[0072] The meshing transmission mechanism 38 has two teeth 67 and 68 that continuously engage with each other. One tooth is located at the drive shaft 42 and is referred to as the input tooth 67, while the other tooth is located at the reversing link 62 and is referred to as the output tooth 68. The input tooth 67 is fixedly positioned at the drive shaft 42, so that the input tooth together performs the rotational drive motion of the drive shaft. The output tooth 68 is fixedly positioned at the reversing link 62, so that the output tooth together performs the linear reversing motion 64 of the reversing link. During the rotational drive motion 55, the meshing engagement between the input tooth 67 and the output tooth 68 causes the rotational drive motion 55 to be converted into the linear reversing motion 64. Simultaneously, the linear reversing motion 64 of the reversing link 62, oriented in the longitudinal directions 3 and 9, is converted into the same linear working motion 28 of the pressing elements 23 and 24, but oriented at right angles to the reversing motion 64.

[0073] In an advantageous design of the exemplary implementation of the meshing transmission mechanism 38, the drive shaft 42 is oriented such that its rotation axis 43, which overlaps with the longitudinal axis 44, extends parallel to the working plane 25. The drive shaft 42 is eccentrically positioned about the valve link 4, wherein the rotation axis 43 is spaced apart from the valve link 4 in a radial direction about the longitudinal axis 9 of the valve link 4. Preferably, the rotation axis 43 is spaced apart from the working plane 25 and correspondingly also from the working axis 26 in the longitudinal direction of the valve link 4. Exemplarily and preferably, the drive shaft 42 is arranged such that the rotation axis 43 extends parallel to the working plane 25 in a radial direction about the longitudinal axis 9 of the valve link 4. Figure 3 and 5 When observing the longitudinal direction 3, it is perpendicular to the working axis 26 orientation.

[0074] In other words, the rotation axis 43 is suitably parallel to the transverse axis 32 of the valve link 4, which is further explained above.

[0075] Suitably, the meshing transmission mechanism 38 is constructed as a rack and pinion mechanism, as is the case in the illustrated embodiment. The input tooth 67 here includes an arcuately curved toothed ring 72 with its curvature center located on the rotation axis 43, while the output tooth 68 is constructed as a rack 73 having a straight extension and a rack longitudinal axis 74 that runs parallel to the longitudinal axis 3.

[0076] The rack 73 is arranged in the radially outer peripheral region at the reversing link 62 and is particularly integrated into the reversing link 62. The reversing link 62 particularly relates to a one-piece body having the rack 73 directly shaped.

[0077] The teeth 73a of the rack 73 are arranged linearly to each other along the axial direction of the rack's longitudinal axis 74, while retaining the space between the teeth. Each of the teeth 73a has a longitudinal extension with a tooth longitudinal axis 75, which runs transversely to the rack's longitudinal axis 74 and, in a preferred embodiment, is arranged particularly perpendicular to it. Accordingly, the rack 73 is preferably straight-toothed.

[0078] In this case, the toothed ring 72 arranged at the drive shaft 42 also has a corresponding straight tooth portion. The teeth 72a of the toothed ring are arranged successively along the circumferential direction of the longitudinal axis 44 and each has a longitudinal extension with a tooth longitudinal axis 76 extending parallel to the rotation axis 43.

[0079] Unlike the illustrated embodiment, the input tooth 67 and the output tooth 68 can also be implemented as helical teeth. This makes it particularly possible to orient the drive shaft 42 such that its rotation axis 43 overlaps with the longitudinal axis 3 of the squeeze valve 1. This achieves a particularly fine construction of the squeeze valve 1.

[0080] Through the meshing engagement between the input tooth 67 and the output tooth 68, the commutation element 62 simultaneously undergoes torsional fixation with respect to the valve housing 2. This provides an exemplary feasibility of limiting the peripheral extension of the output tooth 68 around the central longitudinal axis 9 of the valve element 4. The rack 73 occupies only a portion of the periphery of the commutation element 62 and is located only in the outer peripheral region of the commutation element 62 facing the drive space 45.

[0081] The input tooth 67 can extend through the window-shaped perforation 76 into the annular space section 63 so as to engage with the output tooth 68 there.

[0082] The torsion of the drive shaft 42 causes the reversing element 62 to move linearly in the valve body 2 while performing a linear reversing motion 64, wherein the direction of motion of the reversing element 62 depends on the rotation direction of the drive shaft 42.

[0083] Essentially, the toothed ring 72 can be a full ring extending around the drive shaft 42. However, preferably, the toothed ring is constructed as a partial ring with a peripheral extension of less than 360 degrees about the longitudinal axis 44, wherein the arc length between the two teeth 72a, referred to as the closing teeth 77, is selected for the application and is exemplarily 90 degrees.

[0084] The toothed ring 72, as a partial ring design, provides an advantageous implementation of a stop mechanism 78 for mechanically presetting the drive motion 55 of the drive shaft 42 to two opposing end positions. In one of these end positions, the reversing element 62 is in a locked position, and in the other end position, it is in a released position. Thus, the pressing elements 23 and 24 can be precisely positioned in the open or closed position by simply limiting the rotation angle of the drive shaft 42 without additional monitoring measures.

[0085] Preferably, the stop mechanism 78 has two stop surfaces 82, formed by the tooth sides of the two closing teeth 77 facing away from each other in the rotational direction of the drive shaft 42. Furthermore, the stop mechanism 78 has two mating stop surfaces 83 fixed to the housing, exemplary constructed at one or more wall protrusions of the valve housing 2 and extending into the drive space 45 such that a corresponding mating stop surface 83 exists in the movement track of one of the stop surfaces 82. Depending on the rotational direction of the drive shaft 42, either one or the other closing tooth 77 strikes the mating stop surface 83 in its movement track to limit the rotational angle, thereby positioning the drive shaft 42 according to the rotational angle.

[0086] The squeeze valve 1 can be implemented such that the reversing movement 64 of the reversing link 62 can be caused solely by the adjusting force introduced by means of the engagement transmission mechanism 38. In this way, a stable axial end position of the reversing link 62 can be easily achieved.

[0087] However, preferably, the squeeze valve 1 is equipped with a spring mechanism 84 that induces or at least supports the reversing movement 64 along one of the two possible directions of movement. The described squeeze valve 1 is accordingly equipped with a mechanical spring mechanism 84 that continuously preloads the reversing element 62 into a locked position, the closing position of the squeeze elements 23, 24 accompanying the locked position. This provides a safety aspect, as the squeeze valve 3 automatically closes in the event of damage to the engagement transmission mechanism 38. Furthermore, the spring mechanism 84, acting in the closing direction, ensures that the squeeze elements 23, 24 are pressed against the valve element 4 in the closed position by a predetermined squeezing force, thereby ensuring reliable closure of the valve passage 5 without overloading the flexible, and particularly rubber-elastic, peripheral wall 8.

[0088] In embodiments not described, the spring mechanism 84 is installed such that it continuously preloads the reversing element 62 to the release position.

[0089] Preferably, the spring mechanism 84 is a compression spring mechanism. The spring mechanism is particularly designed as a helical spring, but it can also include, for example, a disc spring assembly.

[0090] The spring mechanism 84 is preferably located within the internal space 10 of the housing, and particularly within the annular spatial segment 63. Exemplarily, the spring mechanism is axially and centrally engaged between the reversing element 62 and a closed wall 14a on one end side. The spring mechanism, for example, comprises a tapered spring that gradually tapers in the direction toward the reversing element 62.

[0091] The spring mechanism 84 preferably has an annular cross-section and is preferably arranged coaxially with the longitudinal axis 3.

[0092] The meshing transmission mechanism 38 is suitably equipped with such tooth flank clearance that, in the closed position of the pressing elements 23, 24, the optional spring mechanism 84 is responsible for generating the pressing force acting on the valve link 4 with its spring force.

[0093] The squeeze valve 1 is suitably equipped with a manually operable locking mechanism 85, which locks the drive shaft 42 relative to the valve housing 2 in a non-rotatable manner into different rotational positions adjustable by the rotational drive motion 55. Thus, the intermediate positions of the squeeze elements 23 and 24 between the open and closed positions can be fixed for any length of time.

[0094] According to a preferred configuration of the locking mechanism 85 (which is achievable in the illustrated embodiment), the drive shaft 42 is axially movable relative to the valve housing 2 along its longitudinal axis 44. The drive shaft 42 has a radially projecting annular flange 86 within the drive space 45, the annular flange being arranged coaxially with the support ring 52 and having an annular locking surface 87 at its axially facing end side towards the support ring 52. The annular flange 86 is anti-rotatably connected to the drive shaft 42 and is exemplaryly formed by an annular body anti-rotatably inserted onto the drive shaft 42. An annular mating locking surface 88 is axially opposed to the locking surface 87, the mating locking surface being constructed at the support ring 52.

[0095] The drive shaft 42 is not only able to rotate about the valve housing 2, but also to be slightly axially displaced, wherein linear motion is limited in one direction by the combined action between the locking surface 87 and the mating locking surface 88, and in another direction by the combined action between the base surfaces of the support sleeve 54a and the wall deepening portion 54b.

[0096] The manually operable tensioning element 92 of the locking mechanism 85 applies a tension 93 to the drive shaft 42 and thus also to the locking surface 87 on which it is supported. This causes the entire drive shaft 42, including the locking surface 87, to be axially adjusted in the direction toward the support ring 52 and pressed against the mating locking surface 88 with its locking surface 87. By correspondingly tightening the tensioning element 92, the locking surface 87 and the mating locking surface 88 can be fixedly clamped together such that the drive shaft 42 is locked with respect to the valve housing 2 in a non-torsional manner. The position occupied by the locking surface 87 with respect to the valve housing 7 should be referred to as the locked position. To release the rotatable movement of the drive shaft 42, the tensioning element 92 can be manually disengaged, thereby removing the locking surface 87 from the mating locking surface 88 to occupy the disengaged position. The drive shaft 42 can then be rotated unimpeded.

[0097] Exemplarily, the tensioning element 92 is implemented as a tensioning nut 92a, which is screwed onto the external thread 94 of the end section of the drive shaft 42 protruding from the valve housing 2. By manually rotating according to the double arrow 95, the tensioning nut 92a can be tightened onto the external thread 94 such that it rests on the support surface 96 of the support ring 92 facing it, thereby applying the tension 93 described above to the drive shaft 42, which is not rotating together. As a result, the locking surface 87 moves into the locking position. By rotating the tensioning nut 92a in the opposite direction of rotation, the tension 93 can be released, and the locking surface 87 can return to the disengaged position.

[0098] Unlike the embodiments described below, in the embodiments, the support surface 96 is implemented at a separate support ring 52 inserted into the valve housing 2, or the support surface 96 can be directly constructed on the valve housing 2.

[0099] Preferably, not only the locking surface 87 but also the mating locking surface 88 are toothed, so that the locking surface 87 engages with the mating locking surface in the locked position with a form-fit that acts in the rotational direction of the drive shaft 42. This locking mechanism 85 provides high security against unintentional twisting of the drive shaft 42. Even when the tension nut 92a should be slightly disengaged, the form-fitting engagement between the engaging locking surface 87 and the engaging mating locking surface 88 remains maintained and prevents twisting of the drive shaft 42. This is also true when a spring mechanism 84 is present, which applies torque to the drive shaft 42 via the engagement transmission mechanism 38.

[0100] Exemplarily, not only the locking surface 87 but also the mating locking surfaces 87 have annular toothed rings 87a and 88a coaxial with the rotation axis 43, the toothed rings having correspondingly alternating and successively arranged teeth and tooth spaces. The toothed rings 87a and 88a are constructed to complement each other. The toothed rings have the same diameter and are opposed to each other along the axial direction of the rotation axis 43 with their tooth crowns facing each other. In the locked position, the teeth of the corresponding toothed ring 87a axially engage with the tooth spaces of the corresponding toothed ring 88a.

[0101] It is understood that, despite this, there is an alternative possibility that the locking surface 87 and the mating locking surface 88 are constructed as purely frictional surfaces, which are in purely frictional contact with each other in the locking position of the locking surface 87.

[0102] In the illustrated embodiment, the current operating state of the squeeze valve 1 can be easily read from the current swing position of the lever 57. Nevertheless, it is advantageous to provide a reading scale for confirming the current operating state. This, in particular, simplifies the adjustment of the flow path intermediate position.

Claims

1. A squeeze valve for a flowable medium, comprising a valve housing (2) having a flexible peripheral wall (8) extending therein, and a hose-shaped valve link (4) having a flexible peripheral wall (8) and passing through a valve passage (5) in its longitudinal direction, wherein a plurality of squeeze elements (23, 24) are arranged distributed around the radial outer periphery (22) of the valve link, the squeeze elements being capable of moving toward and away from each other in a working plane (25) perpendicular to the longitudinal axis (9) of the valve link (4) while performing a linear working motion (28) to more or less strongly compress the valve link (4), and the squeeze valve having a drive mechanism (36) for actuating the working motion (28) of the squeeze elements (23, 24), characterized in that, The drive mechanism (36) has a drive shaft (42) that is torsionally supported on the valve housing (2) about a rotation axis (43) extending longitudinally along the drive shaft, and the drive shaft has an operating section (48) into which the driving torque of a drive motion (55) causing rotation of the drive shaft (42) can be introduced. The drive mechanism (36) further has a conversion mechanism (37) with a meshing transmission mechanism (38) that converts the rotational drive motion (55) of the drive shaft (42) into a linear working motion (28) of the pressing elements (23, 24). The drive shaft (42) is equipped with a manually operable locking mechanism (85) for disengagingly locking different rotational positions of the drive shaft (42). The device is capable of limited axial movement relative to the valve housing (2) and has an annular locking surface (87) axially oriented in a coaxial arrangement with respect to the locking mechanism (85). An annular mating locking surface (88) of the locking mechanism (85) is axially opposed to the locking surface. A manually operable tensioning element (92) of the locking mechanism (85) is applied at the drive shaft (42). The operation of the tensioning element causes an axial adjustment of the drive shaft (42) together with the locking surface (87), whereby the locking surface (87) can be selectively positioned in a locking position in which it cannot be twistedly clamped to the mating locking surface (88) and thus cannot be twistedly locked to the drive shaft (42), or in a disengaged position that allows the drive shaft (42) to be twisted.

2. The squeeze valve according to claim 1, characterized in that, The squeeze valve is configured to be manually operated, wherein a handle (56) accessible outside the valve housing (2) is arranged at the operating section (48) of the drive shaft (42).

3. The squeeze valve according to claim 2, characterized in that, The handle (56) is a lever (57) with a lever arm (57a).

4. The squeeze valve according to claim 1, characterized in that, The squeeze valve is configured to be operated by a motor, wherein a drive motor (58) is disposed in the valve housing (2), and the output shaft (58b) of the drive motor is connected to the operating section (48) of the drive shaft (42) to transmit torque.

5. The squeeze valve according to any one of claims 1 to 4, characterized in that, The squeeze valve has only two squeeze elements (23, 24) placed in the radially opposite peripheral region of the outer periphery (22) of the valve link (4), and the squeeze elements are capable of moving along a common working axis (26) that is perpendicular to the longitudinal axis (9) of the valve link (4) and located in the working plane (25) in order to carry out their working motion (28).

6. The squeeze valve according to claim 5, characterized in that, The working axis (26) is spaced apart from the rotation axis (43) of the drive shaft (42) along the longitudinal direction of the valve link (4) and is orthogonal to the rotation axis (43) of the drive shaft (42).

7. The squeeze valve according to any one of claims 1 to 4, characterized in that, The drive shaft (42) is eccentrically arranged about the valve link (4), wherein its rotation axis (43) is spaced apart from the longitudinal axis (9) of the valve link (4).

8. The squeeze valve according to any one of claims 1 to 4, characterized in that, The meshing transmission mechanism (38) has an input tooth (67) that is anti-rotationally connected to the drive shaft (42) and performs a drive motion (55) that rotates together with it, and an output tooth (68) that is engaged with the input tooth (67) and is kinematically coupled to the pressing elements (23, 24) to cause the working motion (28).

9. The squeeze valve according to claim 8, characterized in that, The switching mechanism (37) has a reversing element (62) arranged in the valve housing (2), which is capable of being displaced along the longitudinal direction of the valve element (4) during a linear reversing motion (64) by a drive motion (55) of the rotation of the drive shaft (42), and the reversing element has a groove structure (65) in which the pressing elements (23, 24) are slidably displaced against the groove structure, such that the pressing elements are driven to perform their working motion (28) by their groove structure (65) during the linear reversing motion (64) of the reversing element (62).

10. The squeeze valve according to claim 9, characterized in that, The output tooth (68) is located at the reversing link (62).

11. The squeeze valve according to claim 9 or 10, characterized in that, The reversing element (62) is sleeve-shaped and coaxially surrounds the valve element (4).

12. The squeeze valve according to claim 11, characterized in that, The chute structure (65) is constructed at the inner periphery of the reversing link (62).

13. The squeeze valve according to claim 9 or 10, characterized in that, The reversing element (62) can be shifted between two opposing axial end positions by the linear reversing motion (64), wherein one of the two axial end positions represents a locking position that causes the valve passage (5) to close and the other of the two axial end positions represents a release position that is responsible for releasing the maximum flow cross section of the valve passage (5).

14. The squeeze valve according to claim 13, characterized in that, A spring mechanism (84) is arranged in the valve housing (2) to continuously preload the reversing element (62) to one of its two axial end positions.

15. The squeeze valve according to claim 14, characterized in that, The reversing link (62) is continuously pre-tightened to the locked position by the spring mechanism (84).

16. The squeeze valve according to claim 10, characterized in that, The output tooth (68) is constructed at the radial outer periphery of the commutation link (62).

17. The squeeze valve according to claim 16, characterized in that, The output tooth (68) extends only along a restricted section of the outer periphery of the reversing link (62) along the peripheral direction of the longitudinal axis (9) of the valve link (4).

18. The squeeze valve according to claim 8, characterized in that, The meshing transmission mechanism (38) is configured as a rack and pinion transmission mechanism, wherein the input tooth (67) is configured as an arc-shaped curved toothed ring (72) and the output tooth is configured as a rack (73) with a linear extension.

19. The squeeze valve according to claim 18, characterized in that, The toothed ring (72) extends through an arc length of less than 360 degrees.

20. The squeeze valve according to claim 19, characterized in that, The toothed ring (72) has an arc length of 90 degrees.

21. The squeeze valve according to claim 18, characterized in that, The squeeze valve has a stop mechanism (78) for presetting two opposing end positions of the drive motion (55) of the rotation of the drive shaft (42), the stop mechanism having two stop surfaces (82) arranged on the drive shaft (42) and two mating stop surfaces (83) fixedly arranged with respect to the valve housing (2).

22. The squeeze valve according to claim 21, characterized in that, The two stop surfaces (82) are formed by the tooth sides of the teeth (72a, 77) of the toothed ring (72) that close on opposite sides of each other.

23. The squeeze valve according to claim 1, characterized in that, The tensioning element (92) is configured as a tensioning nut (92a) screwed onto the external thread (94) of the drive shaft (42), which is supported on a support surface (96) fixed in position with respect to the valve housing (2) during rotational operation (95) so as to apply an axial tensile force to the drive shaft (42) to clamp the locking surface (87) with the mating locking surface (88).

24. The squeeze valve according to claim 1 or 23, characterized in that, The locking surface (87) and the mating locking surface (88) are toothed so that they engage with each other in a form-fitting manner in the locking position of the locking surface (87).

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