Throttling device, fluid equipment and fluid system

Abstract

According to the invention, a throttle device (50) is proposed, which has a retaining structure (56), to which a throttle reed (57) is fastened with a proximal end section (72), which reed protrudes with a distal end section (73) in a free-terminating manner into a throttle channel (59) and divides the throttle channel (59) into two throttle channel sections (59a, 59b). According to the invention, the throttle spring (57) can be pivoted from a neutral position (74a) into different pivoting positions (74b, 74c) by means of a rubber elastic reversible deformation occurring as a function of the pressure difference between the two throttle channel sections (59a, 59b) in order to automatically adapt the free flow cross-section (80) to the respective requirement.

Description

Technical Field

[0001] The invention relates to a throttling device having a throttling element arranged on a retaining structure and extending into a throttling channel through which a pressure fluid can flow, wherein the throttling element is movable relative to the retaining structure for presetting free flow cross sections of different sizes in the throttling channel.

[0002] The present invention further relates to a fluid device having at least one fluid channel configured for flow of a pressurized fluid, the fluid channel being at least partially configured as a throttling channel, the throttling channel belonging to a throttling device assigned to the fluid channel, through which free flow cross-sections of different sizes of the throttling channel can be predetermined.

[0003] The present invention further relates to a fluid system comprising a fluid-operated drive and a fluid device in the form of a valve device for fluidically controlling the fluid-operated drive, having at least one fluid pipeline connecting the valve device to the fluid-operated drive for transferring a pressure fluid, and having at least one throttling device for causing throttling of a fluid flow between the valve device and the fluid-operated drive that causes a stroke movement of an output element of the fluid-operated drive. Background Art

[0004] According to DE 10 2009 056 496 A1, a throttle device of the type mentioned above is integrated into a fluid device configured as a throttle valve. The throttle valve can be used, for example, for speed regulation of an output element of a fluid-operated drive, wherein there is an alternative possibility for integrating the throttle device directly into the fluid-operated drive. The throttle device has a throttle element extending into a throttle channel, which can be linearly displaced by means of a setting element in order to predetermine free flow cross sections of different sizes of the throttle channel in an application-specific manner. The set free flow cross section defines the throttle strength with respect to the pressure fluid flowing through, and can therefore influence the flow rate of the pressure fluid. In order to change the throttle strength, it is necessary to manually operate the setting element.

[0005] DE 10 2005 032 853 B3 and DE 10 2009 016 198 A1 each describe a fluid device of the type mentioned in the introduction, which is a working cylinder or a fluid-operated linear drive and which is equipped with a throttle device which is used for end-stage damping.

[0006] DE 197 11 227 A1 is concerned with a valve device in which a valve unit having a plurality of valve modules is mounted on a plate-shaped mounting base through which fluid channels, referred to as consumer channels, pass, to which fluid function units, such as throttle devices or pressure regulators, are assigned.

[0007] From DE 10 2014 002 142 A1 a non-return valve is known which has a curved-resilient diaphragm element which is supported on one side by a supporting web and about which the curved-resilient diaphragm element can bend in order to release a fluid flow.

[0008] According to the applicant's internal knowledge, a fluid system can be arranged in fluid technology, for example in the hydraulic field and especially in the pneumatic field, which contains a fluid-operated drive device and a fluid device in the form of a valve device connected to each other by means of one or more fluid pipelines. The fluid-operated drive device is constructed, for example, according to DE 10 2009 016 198 A1, and the valve device is constructed, for example, according to DE 197 11 227 A1. At least one other component of the fluid system (the at least one other component is a fluid pipeline) establishes a fluid connection between the valve device and the fluid-operated drive device and allows a fluid flow of a pressure fluid controlled by the valve device, through which a stroke movement of an output element of the fluid-operated drive device can be caused. At least one component of the fluid system is equipped with a throttling device, which enables the throttling of the fluid flow required to drive the output element, which ultimately means narrowing the free flow cross section provided by the fluid channel for influencing the flow rate or flow rate, which is usually simply referred to as the flow rate, which is simplified. Such a cross-sectional narrowing causes the establishment of a back pressure and is conducive to a gentle, as smooth as possible movement of the output element of the fluid-operated drive device. However, generally speaking, finding the most appropriate throttle setting for a given application is difficult and time consuming. Summary of the invention

[0009] The object of the present invention is to provide measures which make it possible to adjust the throttling intensity of a fluid flow simply, quickly and reliably in a cost-effective manner.

[0010] This object is achieved in the case of a throttling device in combination with the features mentioned at the outset in that the throttling element is constructed as a throttling spring fixed to a retaining structure with a proximal end section, the throttling spring extending from the proximal end section and terminating freely with a distal end section into the throttling channel and dividing the throttling channel into two throttling channel sections which are consecutive in the longitudinal direction of the channel, wherein the throttling spring can be swung into different swivel positions depending on the pressure difference existing between the two throttling channel sections from a neutral position assumed in a state of pressure equilibrium between the two throttling channel sections while changing the free flow cross-section of the throttling channel by utilizing a reversible rubber-elastic deformation that occurs in the direction toward one or the other of the two throttling channel sections.

[0011] This object is also achieved by a fluid device of the type mentioned at the outset, in which the throttle device is designed in the aforementioned sense.

[0012] Finally, the object is also achieved by a fluid system in which, in combination with the features mentioned at the outset, at least one throttling device contained is again designed in the aforementioned sense such that the fluid flow of the pressurized fluid can be throttled by a free flow cross section that is adaptive as a function of the pressure difference.

[0013] A valve device included in a fluid system preferably has a valve section, which is penetrated by multiple fluid channels, among which there is at least one working fluid channel which is provided for fluid connection with a fluid-operated drive device to be controlled, wherein the valve section has at least one electrically operable bypass valve, by which a fluid flow of a pressure fluid occurring in at least one working fluid channel can be controlled, wherein at least one and preferably each working fluid channel is equipped with a throttling device.

[0014] According to the invention, a throttling device which can be installed or mounted in a fluid device and / or a fluid system once or multiple times preferably comprises a throttling element in the form of a throttling spring, which is fixed to a retaining structure and can be swung by the pressure resulting from the pressure difference applied to it during operation. The throttling spring extends into the assigned throttling channel transversely to the longitudinal direction of the channel from a proximal end section, and divides the throttling channel into two throttling channel sections which are consecutive in the longitudinal direction of the channel, in the region of the proximal end section, the throttling spring is fixed to the retaining structure. Since the throttling spring ends freely at its distal end section which is opposite to the proximal end section, the throttling spring can be swung not only in the direction toward one throttling channel section but also in the direction toward the other throttling channel section by the pressure difference applied thereto via the two throttling channel sections, wherein the swinging direction is determined by the pressure difference and is oriented toward the throttling channel section in which the lower fluid pressure exists. During the swinging movement of the throttle spring, the distance between the throttle spring and the channel wall surface of the throttle channel changes at least partially, which occurs with the change of the free flow cross section of the throttle channel, which is available for the pressure fluid flowing in the throttle channel. The throttle spring located in the flow path of the pressure medium usually causes the throttling of the fluid flow, wherein the larger the current free flow cross section, the smaller the throttling intensity, and the correspondingly larger the possible flow rate. If there is no pressure difference between the two throttle channel sections and therefore there is a pressure balance state between the two throttle channel sections, the throttle spring is located in a position called the neutral position, from which the throttle spring can swing to different swing positions when a pressure difference occurs. This swinging is carried out within the range of rubber elastic reversible deformation, resulting in: when the throttle spring is deflected from the neutral position, a rubber elastic restoring force is established, which resists the pressure in the direction of the neutral position obtained by the existing pressure difference. According to the design scheme adopted, a decreasing or linear or progressive restoring force establishment related to the degree of deflection of the throttle spring can be predetermined, for example. In the case of the throttle device according to the invention, the free flow cross section of the throttle channel, which can also be referred to as the opening cross section, is expressed as an especially continuous or permanent function of the prevailing pressure difference, so that in the case of large pressure differences corresponding to high fluid requirements, a larger opening cross section is automatically set, and in the case of small pressure differences corresponding to low fluid requirements, a smaller opening cross section is set. When the throttle device is used in conjunction with the fluid control of the fluid-operated drive, this leads to a certain counterpressure always occurring, regardless of the size of the drive, which facilitates a smooth stroke movement of the output element of the drive. At the same time, rapid exhaust is ensured at the start of operation of the fluid-operated drive in the case of large pressure differences.Since the free flow cross section is automatically set by the flexibly pivotable throttle spring without mechanical access from the outside solely due to the prevailing pressure difference, an adaptive system is provided, which can avoid time-consuming setting and verification measures when using the adaptive system. In addition, the bidirectional flowability of the throttle channel is coupled with the pivotability in opposite directions in relation to the pressure difference, wherein adaptive throttling occurs in both flow directions, so that, for example, in conjunction with the fluid control of a fluid-operated drive, the same throttle device can bring about both supply air throttling and exhaust air throttling. The throttle device always adapts itself to the required fluid flow within wide limits.

[0015] Advantageous developments of the invention are apparent from the dependent claims.

[0016] In principle, the inner contours of the throttle spring and the throttle channel can be adapted to each other so that the throttle channel is closed in the neutral position of the throttle spring, in other words, there is no free flow cross section through which flow can occur in the area of ​​the throttle spring. However, it is considered advantageous if the throttle spring is adapted to the inner contour of the throttle channel in terms of shaping so that a free flow cross section of the throttle channel is already present even in the neutral position of the throttle spring. This free flow cross section present in the neutral position is in particular a minimum free flow cross section, i.e. a free flow cross section which is numerically smaller than each free flow cross section which is open in the possible pivoting positions of the throttle spring. The advantage associated with this is that even at a minimum pressure difference between the two throttle channel sections, wherein the minimum pressure difference is still insufficient to pivot the throttle spring in a rubber-elastic manner, a small flow through is possible, so that in combination with the fluid-operated drive to be controlled, a particularly gentle stroke movement of the output element can be caused.

[0017] In the case of a particularly simple construction of the throttle device, the channel wall of the fluid channel formed in the fluid device serves directly as a retaining structure by forming there, for example, a fastening groove into which the throttle spring is inserted in the region of its proximal end section and, for example, clamped.

[0018] However, a structure is preferred in which the holding structure of the throttle device is structured in a frame-like manner and thus forms a holding frame that completely surrounds the throttle channel peripherally, which is conducive to securely fixing the throttle device, for example in the fluid channel. The inner peripheral surface of the holding frame expediently forms a channel wall surface of the throttle channel, which together with the pivotable throttle spring limits the variable free flow cross section of the throttle channel.

[0019] It is considered to be advantageous if the holding frame has a rectangular cross-sectional profile on the inside, wherein the throttle spring has a rectangular outer profile that is adapted to the inner profile of the holding frame when viewed in the channel longitudinal direction of the throttle channel. The corner regions are expediently rounded in each case. The throttle spring of the outer rectangular profile preferably has a first rectangular side that is fixed to the holding structure in the region of the proximal end section and three movable rectangular sides, one of which is in the region of the distal end section. During a pivoting movement of the throttle spring, the three movable rectangular sides can be freely moved relative to the holding frame in the case of a change in the free flow cross section according to the value, and the movable rectangular sides together with the inner profile of the holding frame define the free flow cross section.

[0020] Preferably, the holding frame also has a rectangular cross-sectional contour on its outer side, which is expediently rounded in the corner regions, so that the holding frame is designed both internally and externally as a rectangle with rectangular sides assigned in pairs.

[0021] It is advantageous if the retaining frame is constructed in a sleeve-shaped manner and extends between two mutually opposite end faces, referred to as frame end faces, in the longitudinal direction of the throttling channel through the retaining frame. The throttling spring can be fixed to the retaining frame, for example, in the region of one of the two frame end faces. However, it is advantageous if the throttling spring is fixed to the retaining frame with its proximal end section in a fastening region spaced apart from the two frame end faces. Thus, the two throttling channel sections extend in the retaining frame between the throttling spring and one of the two frame end faces, respectively. In particular, the length dimension of the retaining frame is selected so that the throttling spring is completely arranged in the retaining frame not only in the neutral position but also in every possible swinging position. The retaining frame preferably has the basic shape of a rectangular tube, in particular with rounded corners.

[0022] As already mentioned above, a feature of the throttle spring according to the invention is that the swivel motion from the neutral position in two possible swivel directions occurs with a rubber-elastic reversible deformation. During the swivel motion, a rubber-elastic restoring force is thus established, which can be exerted or overcome by the existing pressure difference in order to maintain a larger free flow cross section compared to the neutral position. When the pressure difference is eliminated, the throttle spring returns to its stress-neutral neutral position.

[0023] One possible design of the throttle device provides that the throttle spring is designed as a whole to be rigid and resistant to bending and is designed to be rubber-elastic only in the fastening area between the proximal end section and the retaining structure. In this case, when the throttle spring is swung, it behaves like a valve flap. However, a design is preferred in which the throttle spring has rubber-elastic properties in its entirety, so that it can be elastically bent when it swivels, which causes a change in the free flow cross section. This property has the effect, in particular, that when the throttle spring is deflected or swung in one direction or the other, the throttle spring acquires an arcuate curvature across its length starting from a linear extension that is preferably present in the neutral position. This behavior allows a change in the opening to be simply and specifically predetermined depending on the degree of deflection of the throttle spring, in other words, a change in the free flow cross section to be predetermined depending on the level of the existing pressure difference.

[0024] In order to obtain the rubber-elastic properties, the throttle spring is expediently made of an elastomeric material, preferably an elastomeric material with viscoelastic properties, which advantageously contributes to a slow or delayed opening of the free flow cross section.

[0025] In the case of a throttle spring that is designed to be rigid in the manner of a flap, the rubber-elastic properties are expediently limited to the deformable pivoting region for fixing the proximal end section to the holding structure.

[0026] The rubber-elastic properties are advantageously obtained by using polyurethane, in particular thermoplastic polyurethane, which can be easily and precisely shaped by injection molding.

[0027] The throttle spring is preferably configured so that the throttle spring has a bending stiffness that decreases from its proximal end section toward its distal end section, wherein the bending stiffness is particularly continuously reduced. In order to achieve these characteristics, it is particularly provided that the cross section of the throttle spring is reduced from the proximal end section fixed at the holding structure toward the distal end section. For example, the thickness and / or width of the throttle spring can have a maximum value in the region of the proximal end section and from there until at least approximately reduced toward the distal end section. The effect of this design is that the free flow cross section does not change in a jumpy manner when the pressure changes, but only gradually changes over a wide range of pressure differences, which are, for example, in one bar or more. By constituting the throttle spring, the opening behavior can be very simply adapted to specific conditions of use. Preferably, the change in the free flow cross section is a continuous or continuous function of the pressure difference present at the throttle spring, wherein the correlation with the pressure difference can, for example, be designed as decreasing or linear or progressive. In this way, for example, it can be predetermined that the increase in the free flow cross section becomes smaller as the pressure difference increases.

[0028] If the throttle device is constructed as a throttle unit that can be manipulated in a uniform manner, in which the throttle leaf and the retaining structure are integrated into the throttle unit, it is particularly advantageous for the assembly and stability of the throttle device. The throttle leaf and the retaining structure are preferably constructed in one piece with each other, wherein the throttle unit can preferably be implemented as a one-piece injection-molded elastomer component as a whole. However, the overall structure can also be realized, for example, by a material-fit connection between the throttle leaf and the retaining structure, for example, by bonding or laser beam welding. In general, it is advantageous if the throttle unit is composed of a material with rubber-elastic properties as a whole, in particular, by an elastomeric material.

[0029] In its embodiment as a throttle unit, the throttle device offers the great advantage that it can be inserted very simply into the fluid channel of the fluid device for its use, so that in its use position it represents an insert component inserted into the fluid channel. For assembly, the throttle unit can be inserted into the assigned fluid channel, for example, through the channel opening. Depending on the length ratio between the throttle unit and the assigned fluid channel, the throttle channel can take the entire length of the fluid channel or only a part of the length.

[0030] In order to securely fix and seal the wall surface of the fluid channel receiving the throttling unit, the throttling unit advantageously has at least one rubber-elastic sealing projection surrounding the throttling channel, which in the use position seals against the channel wall surface of the fluid channel. When a sleeve-shaped holding frame is present, the at least one sealing projection is advantageously located at its radial outer periphery.

[0031] As already mentioned, the throttling device is preferably constructed as a component of the fluid device. The fluid device expediently comprises at least one fluid channel, into which the throttling unit is inserted as a structural unit, so that the throttling unit can be referred to as an insert component. The fluid device can have a plurality of fluid channels, each of which is equipped with a throttling unit of the described type. For assembly, the throttling unit can be placed, for example, from a port in the longitudinal direction of the channel into the assigned fluid channel, wherein the throttling unit is, for example, pressed in or engaged.

[0032] In the case of a preferred design, a fluid device equipped with at least one throttling device is constructed as a valve device. The valve device has a valve section, which is passed through by a plurality of fluid channels, wherein at least one of the plurality of fluid channels is a fluid channel that is provided for being connected to a fluid-operated drive device to be controlled, in order to better distinguish between the fluid channels referred to as working fluid channels. The valve section of the valve device has at least one electrically operable bypass valve, by which the fluid flow of the pressure fluid flowing through at least one working fluid channel can be controlled, and the fluid flow can be used to operate the drive device. Preferably, the fluid flow toward the drive device and the return flow from the drive device can be carried out through at least one working fluid channel. At least one working fluid channel has a throttling device that is preferably constructed as a throttling unit, so as to enable adaptive ventilation and exhaust of at least one drive chamber of the connected fluid-operated drive device in relation to the pressure difference. For example, at the beginning of the stroke movement of the output element of the fluid-operated drive device, a relatively low flow rate first occurs due to a certain inertia of the throttling spring and a relatively small free flow cross section even in the case of an initially large pressure difference. Therefore, the output element starts smoothly and evenly. The free flow cross section only gradually becomes larger and can remain widely open for a longer period of time until it decreases again towards the end of the stroke movement.

[0033] By means of at least one electrically actuatable bypass valve of the valve device, two working fluid channels connected to the same fluid-actuated drive can be expediently controlled, said working fluid channels preferably both being respectively equipped with a throttle device according to the inventive design.

[0034] The valve section of the valve device advantageously has a base body which is separate from the at least one bypass valve, the at least one bypass valve being mounted on the base body in a particularly detachable manner. The at least one working fluid channel extends with a channel section in the bypass valve, which is called the bypass valve section, and with a channel section in the base body, which is adjacent thereto, which is called the base body section. The throttling device can be arranged, for example, in the bypass valve section of the working fluid channel, but is preferably installed in the base body section so that the valve device can be operated with a conventionally constructed bypass valve when necessary. When it is also necessary to replace a bypass valve without a throttling device, the at least one assigned throttling device can remain in the base body.

[0035] In the case of a minimum configuration, the base body of the valve device is equipped with only a single bypass valve. However, in particular in conjunction with complex automation tasks, it is advantageous if the valve section has a plurality of bypass valves mounted in a row on the base body, each of which is designed to control a fluid flow occurring in at least one working fluid channel equipped with a throttle device.

[0036] However, there is also the possibility of easily configuring the valve device as a so-called single valve, whose valve section has a single bypass valve and, for example, does not have a separate base body. In this case, at least one working fluid channel extends completely as a valve channel in the bypass valve and expediently accommodates the throttling device according to the inventive design.

[0037] The fluid device equipped with at least one throttling device according to the invention is not necessarily a valve device, but can also be other types of fluid devices. For example, the fluid device can be a fluid-operated drive, such as a linear drive or a rotary drive, or can be an independent throttle valve that can be used in combination with other fluid devices, which can be added to the extension of a fluid line, for example.

[0038] In the case of the fluid system according to the invention, the fluid-operated drive or the valve device is expediently equipped with at least one throttle device, or a throttle device is introduced into at least one fluid line connecting the fluid-operated drive to the valve device. BRIEF DESCRIPTION OF THE DRAWINGS

[0039] The present invention will be explained in more detail below with reference to the accompanying drawings. In the drawings:

[0040] Figure 1 In a perspective view and not shown in the operationally ready state, the valve device is laterally arranged on the valve section of the valve device, from Figure 5 In a preferred embodiment, the fluid device according to the invention is shown as a valve device in the case of a shut-off module as can be seen in FIG. 1 , wherein the valve device is equipped with a plurality of electrically actuatable bypass valves mounted on a base body,

[0041] Figure 2 Again in a perspective view, one of the bypass valves is shown removed from the base body. Figure 1 A valve device, wherein two throttle devices according to the invention integrated into the valve device are shown in a preferred configuration in the state before installation, one of which is in the framed image fragment VI,

[0042] Figure 3 In accordance with Figure 1 , 4 The cross section of the cutting line III-III of 5 shows Figure 1 and 2a valve device, in which a further fluid device is additionally schematically shown, which can be fluidically controlled by the valve device and is designed as a fluid-operated drive, which is connected to a valve section of the valve device via two fluid lines, so that there is a preferred embodiment of the fluid system according to the invention, in which the fluid-operated drive is equipped with a sensor, which is connected to an optional electrical input of the valve device via a sensor cable, and in which two throttling devices integrated into the valve device and assigned to one of the bypass valves can be seen in the cross section,

[0043] Figure 4 Show according to Figure 3 and 5 Section IV-IV is the section through the valve equipment,

[0044] Figure 5 Shown according to Figure 1 and 3 The direction of the arrow V Figures 1 to 4 A top view of a valve device, in which two laterally arranged closing modules can also be seen, and a schematic representation of an electronic control unit which is expediently provided for electrically actuating the valve device,

[0045] Figure 6 A cubic single diagrammatic representation of a preferred embodiment of the throttle device according to the invention is shown, which is preferably installed multiple times in Figures 1 to 5 The valve device, and the throttling device is Figure 2 The throttling device illustrated in the image fragment VI therein,

[0046] Figure 7 Based on Figure 6 The front view in the direction of arrow VII shows the throttling device,

[0047] Figure 8 Show according to Figure 6 , 7 and 9, a longitudinal section of the throttle device along section VIII-VIII, wherein the throttle spring drawn in its neutral position is also shown in two possible pivot positions on the one hand by a dotted line and on the other hand by a dashed line, and

[0048] Fig. 9 Show according to Figure 6 and 8 Section IX-IX is a cross section of the throttling device. DETAILED DESCRIPTION

[0049] Figure 5 Yes also from Figures 1 to 4, which is connected via at least one electrical control line 3a to an optional electronic control unit 3, which is designed to control the valve device 1a in operation. According to the illustration, the electronic control unit 3 can be designed as a separate or external valve device 1 or can be integrated into the valve device 1a.

[0050] A preferred use of the valve device 1a is to operate at least one fluid-operated drive 1b, wherein such a fluid-operated drive 1b is Figure 3 1a is schematically depicted in a so-called double-acting configuration. The drive device 1b has a drive housing 4a and an output element 4b, which is movable in this connection when performing a stroke movement 2 indicated by a double arrow, and which separates two drive chambers 10a, 10b from one another in the drive housing 4a, which are each connected to the valve device 1a via one of two fluid lines 5a, 5b. Controlled fluid loading is possible via the two fluid lines 5a, 5b to the two drive chambers 10a, 10b and thus the output element 4b, so that the output element 4b is moved back and forth between a first stroke end position illustrated and a second stroke end position spaced apart in this connection when performing a stroke movement 2.

[0051] The two drive chambers 10a, 10b are also referred to below as first and second drive chambers 10a, 10b, and the two fluid lines 5a, 5b are also referred to below as first and second fluid lines 5a, 5b.

[0052] By way of example, the fluid-operated drive 1 b is a linear drive, in particular a working cylinder, but it can also be designed as a rotary drive, for example.

[0053] The valve device 1a and the fluid-operated drive 1b represent different types of fluid devices 1, the operation of which occurs with a fluid flow of a fluid pressure medium, referred to below as pressure fluid. The pressure fluid may be a hydraulic medium, but is preferably compressed air.

[0054] In order to fluidically control a fluid-operated drive device 1b, which is also referred to below for simplicity as drive device 1b, the valve device 1a is equipped with an electrically operable bypass valve 6. Preferably and by way of example, the valve device 1a contains a plurality of such bypass valves 6, which permit simultaneous fluid control of a plurality of drive devices 1b independently of one another. Although according to an embodiment not illustrated, the valve device 1a can also be equipped with only a single bypass valve 6, the further description is based on a valve device 1a equipped with multiple bypass valves 6.

[0055] The bypass valve 6 is a component of a valve section 7 of the valve device 1a, which is passed through a plurality of fluid channels 8 through which a pressurized fluid can flow. Of these fluid channels 8, two fluid channels 8, referred to as working fluid channels 8a, 8b, are provided for each bypass valve 6, which are each connected to the bypass valve 6 on the one hand and lead outwards on the other hand at a connection surface 22 with a working connection end 9 at the valve section 7, wherein one of the two fluid lines 5a, 5b, which are designed, for example, as hoses, leading to the fluid-operated drive 1b can be connected to or connected to the working connection end.

[0056] The bypass valves 6 are electrically operable and are each equipped with a valve drive 12 operable by an electric valve control signal. Exemplarily, each bypass valve 6 is electropneumatically piloted, wherein the valve drive 12 is composed of a pilot valve device 13 having at least one pilot valve, which is combined with a main valve 14 to form a structural unit as the bypass valve 6. The pilot valve device 13 can pneumatically operate the main valve 14 to set one of the multiple switching positions of the bypass valve 6 or the internal valve element 6a of the bypass valve 6, wherein the working fluid channels 8a, 8b are either pressure-loaded or exhausted.

[0057] The electric valve control signal can be supplied to the bypass valve 6 via a communication structure 15 arranged in the interior of the valve section 7, which is connected to an electromechanical interface 16 accessible from the outside to which the electronic control unit 3 can be connected or to which the electromechanical interface 16 is connected. The communication structure 15 is in electrical contact with the valve drive 12 of each bypass valve 6 in the interior of the valve section 7 in individual contact areas 17.

[0058] The valve device 1a is expediently equipped so that when the bypass valve 6 is electrically actuated, an electrical sensor signal can be taken into account, which comes from a sensor 18 arranged at the drive device 4. Typically, two sensors 18 are assigned to each bypass valve 6, which are position sensors arranged at the drive device 4 and can each detect at least one stroke position of the output element 4b. Exemplarily, each of the two sensors 18 can detect one of the two stroke end positions of the output element 4b and output a corresponding sensor signal.

[0059] The sensors 18 are each connected to one of a plurality of selectable electrical inputs 23 of the valve device 1a via a preferably multi-core cable, referred to as a sensor cable 19. By way of example, the valve device 1a comprises a component having an electrical input 23 and therefore referred to as an input section 24, which is fastened to the valve section 7. The electrical input 23 is electrically connected to the electrical communication structure 15 via an internal electrical conductor arrangement 26. Thus, the electrical sensor signal output by the sensor 18 can be transmitted in a sensor-specific manner via the sensor cable 19, the electrical input 23, the electrical conductor arrangement 26 and the communication structure 15 as a response signal to the electronic control unit 3, which can generate an electrical valve control signal specific to the bypass valve 6 based on the sensor signal obtained and transmit the electrical valve control signal to the bypass valve 6 via the communication structure 15.

[0060] The bypass valve 6 is designed in particular as a multi-way valve and has a 5 / 2-way valve function by way of example. The valve function is implemented in the main valve 14, which can be operated by the pilot valve device 13 using fluid force. The switching position of the bypass valve 6 can be predetermined by the valve element 6a mentioned above, which can be displaced in the valve housing 6b of the bypass valve 6 by the fluid loading caused by the pilot valve device 13 when the switching movement 11 indicated by the double arrow is implemented, and can thus be positioned in different switching positions. In each bypass valve 6, a plurality of valve channels 27 are constructed, which are fluidically connected or separated from each other in different configurations according to the switching position of the valve element 6b.

[0061] In addition to the two working fluid channels 8a, 8b respectively specifically assigned to the bypass valves, each bypass valve 6 also communicates with other fluid channels 8, including a feed fluid channel 8c connected to an external pressure source P and at least one and in particular two exhaust fluid channels 8d which are continuously connected to the atmosphere R.

[0062] Each bypass valve 6 or valve element 6a can adopt two switching positions, in which one of the two working fluid channels 8a, 8b is respectively connected to the feed fluid channel 8c and at the same time the other of the two working fluid channels 8b, 8a is connected to the exhaust fluid channel 29. In this way, a stroke movement 2 of the connected drive device 1b can be caused in one of two stroke directions 2a, 2b, respectively, which are opposite to each other.

[0063] At least one bypass valve 6 can alternatively have a 5 / 3-way valve function, wherein the bypass valve is constructed so that it can realize a third switching position, which third switching position is particularly present as an intermediate position, in which the two working fluid channels 8a, 8b are separated not only from the feed fluid channel 8c but also from each exhaust fluid channel 29.

[0064] The overall arrangement comprising the valve device 1a, the fluid-operated drive 1b and the fluid lines 5a, 5b defines a ready-to-operate fluid system 42 which enables a wide variety of applications in which an object coupled to the output element 4b can be moved and / or positioned by correspondingly controlling the drive 1b, for example in manufacturing or assembly technology.

[0065] The valve device 1a extends along an imaginary main axis 32, the axial direction of which is to be referred to as main direction 32a. Furthermore, the valve cell 2 has an axial extension along a transverse axis 33, which is referred to as transverse direction 33a, and an axial extension along a vertical axis 34, which is referred to as vertical direction 34a. The transverse axis 22 extends perpendicularly to the main axis 32, and the vertical axis 34 extends perpendicularly both to the main axis 32 and to the transverse axis 33.

[0066] The optional inlet section 24 adjoins the valve section 7 in the transverse direction 33a. The connection surface 22 equipped with the working connection 9 is expediently located on the side of the valve device 1a opposite the inlet section 24 in the transverse direction 33a.

[0067] According to the illustrated embodiment, the valve section 7 expediently comprises a base body 35 having a valve mounting surface 36, on which the bypass valves 6 are mounted with their valve base surfaces 25, in particular independently of one another. In this case, each bypass valve 6 is supported at the valve mounting surface with its valve housing 6 b having the valve base surface 25. Fixing is expediently performed by means of fastening screws 38.

[0068] A plurality of bypass valves 6 are arranged adjacently along a row direction 37, which is indicated by a dot-dash line and coincides with the main direction 32a, and are respectively located at an installation position of the base body 35 formed by a partial surface of a valve installation surface 36. The row direction 37 is indicated by a dot-dash line and coincides with the main direction 32a by way of example. The feed fluid channel 8c and each exhaust fluid channel 8d extend in the row direction 37 in the base body 35 and lead to each installation position at the valve installation surface 36, respectively, where they are respectively communicated with one of the plurality of internal valve channels 27 of the bypass valve 6 mounted at the relevant installation position.

[0069] The communication structure 15 is preferably designed in a cord-like manner and extends in the interior of the base body 35 along the row direction 37 of the bypass valves 6. The communication structure is preferably formed by a printed circuit board arrangement. The communication structure 15 expediently has an electrical contact surface in the contact area 17, with which the pilot valve device 13 is electrically contacted.

[0070] The valve section 7 expediently has a first and a second closing module 46a, 46b, which are respectively mounted on one of the two end faces of the base body 35 pointing in the row direction 37. The closing modules 46a, 46b close the feed fluid channel 8c and the exhaust fluid channel 8d. The electromechanical interface 16 is exemplarily arranged outside the first closing module 46a and communicates with the communication structure 15 inside.

[0071] A connection opening 47 communicating with the feed fluid channel 8c and at least one exhaust opening 48 communicating with at least one exhaust fluid channel 8d are located at at least one of the two closing modules 46a, 46b, exemplarily located at the first closing module 46a. An external pressure source P providing a pressure fluid is connected via the connection opening 47, and exhaust is exhausted to the atmosphere R through the exhaust opening 48.

[0072] The base body 35 is designed as a single piece by way of example, but according to an exemplary embodiment (not shown) it can be segmented in the row direction 37 and consist of a plurality of connected base body modules which are each equipped with one or more bypass valves.

[0073] The valve device 1 a can also be designed in such a way that the valve housing 6 b of the at least one bypass valve 6 forms an integral structural unit with the main body 35 .

[0074] As for the working fluid channels 8a, 8b, a fluid channel pair consisting of a first working fluid channel 8a and a second working fluid channel 8b is individually assigned to each bypass valve 6. Each working fluid channel 8a, 8b has a channel section formed in the base body 35, which is called the base body section 28, and a channel section adjacent thereto, which is formed in the assigned bypass valve 6, which should be called the bypass valve section 39.

[0075] The base segment 28 is connected to one of the working connection ends 9 at one end and leads to the assigned installation position of the valve installation surface 36 with a passage opening called the base segment opening 28a at the other end. Each bypass valve segment 29 forms one of the valve channels 27 and leads to the valve base surface 25 with a passage opening called the bypass valve segment opening 29a, which is opposite to one of the base segment openings 28a. In this way, the bypass valve segments 39 and the base segments 28 of the fluid working channels 8a, 8b are fluidically connected to each other in pairs.

[0076] The valve channel 27 leads in the interior of the valve housing 6b at a mutual spacing to a valve element receiving space 43 formed in the valve housing 6b, in which the valve element 6a, which is exemplarily formed as a valve slide and is movable relative to the valve housing 6b, extends. By operating the valve drive 12 side, the valve element 6a can be positioned in the two switching positions already mentioned, which should be referred to as the first and second switching positions. Figure 3 In the first switching position as can be seen in the figure, the first working fluid channel 8a is connected only to the feed fluid channel 8c, while the second working fluid channel 8b is connected only to one of the exhaust fluid channels 8d. In the second switching position, this is the second working fluid channel 8b, which is connected only to the feed fluid channel 8c, while the first working fluid channel 8a is connected to one of the exhaust fluid channels 8d. Therefore, in the first switching position, the first drive chamber 10a connected to the first working fluid channel 8a via the first fluid line 5a is ventilated, while the second drive chamber 10b connected to the second working fluid channel 8b via the second working fluid channel 5b is exhausted. As a result, the output element 4b is driven into a stroke motion 2 in the exit direction 2a from the first stroke final position. In the second switching position, the second drive chamber 10b is ventilated and the first drive chamber 10a is exhausted, so that the output element 4b performs a stroke motion 2 in the entry direction 2b opposite to the exit direction 2a from the second switching position.

[0077] Depending on the switching position of the valve element 6a, each working fluid channel 8a, 8b is thus flowed through by the used pressure fluid either in a first flow direction 44 or in a second flow direction 45 which is opposite thereto, wherein these flow directions 44, 45 are Figure 4 and 8 This is illustrated diagrammatically in the accompanying drawings by arrows.

[0078] During the stroke movement 2 of the output element 4b of the drive device 1b, a fluid flow therefore occurs between the valve device 1a and the drive device 1b, by which one of the two drive chambers 10a, 10b is ventilated, and at the same time the other of the two drive chambers 10a, 10b is exhausted, depending on the direction of movement of the stroke movement 2. These fluid flows are formed in the two working fluid channels 8a, 8b and in the fluid lines 5a, 5b connecting the working fluid channels 8a, 8b to the drive chambers 10a, 10b.

[0079] Compared to the maximum possible flow rate due to the nominal cross-sectional geometry of the working fluid channels 8a, 8b and the fluid lines 5a, 5b, the aforementioned fluid flow is expediently a throttled fluid flow with a reduced flow rate or a reduced flow rate, which is manifested, for example, in a gentle, smooth and non-abrupt stroke movement 2 of the output element 4b. The reason for the throttling is at least one throttling device 50, with which the fluid system 42 or at least one fluid device 1 is equipped. Exemplarily, each fluid connection existing between the bypass valve 6 and the assigned drive device 1b contains such a throttling device 50, which includes one of the two working fluid channels 8a, 8b and one of the two fluid lines 5a, 5b. Each of these throttling devices 50 is characterized in that the throttling device is configured to be adaptive according to the pressure difference, and based on the pressure difference of the pressure fluid existing at the throttling device, a free flow cross section that is optimal in size for the fluid flow and, accordingly, an optimal flow rate of the pressure fluid toward the drive device 1b and back from the drive device 1b can be achieved.

[0080] In principle, a structure is possible in which an adaptive throttling device 50 is included in only one of the aforementioned fluid connections 8a, 5a; 8b, 5b, but it is advantageous if - according to the illustrated embodiment - both fluid connections 8a, 5a; 8b, 5b are each equipped with such a throttling device 50.

[0081] The corresponding throttle device 50 is preferably designed as a component of the valve device 1a, which applies to the illustrated embodiment. By way of example, each of the two working fluid channels 8a, 8b is equipped with a sample of the described throttle device 50. In this case, it is particularly advantageous if the throttle device 50 is arranged in the base section 28 of the assigned working fluid channel 8a, 8b, i.e. in the base body 35 of the valve section 7 of the valve device 1a. Alternatively, the throttle device 50 can be arranged in accordance with Figure 3 The placement indicated by dash-dot lines at 52 in FIG. 1 can also be arranged, for example, in the bypass valve section 29 of the working fluid channel 8 a , 8 b and thus in the associated bypass valve 6 .

[0082] Another possible placement for the throttle device 50 is integration into a fluid-operated drive 1b, which also represents the fluid device 1, as indicated by dash-dotted lines at 53. In this case, the throttle device 50, 53 can be located, for example, outside the drive housing 4a or installed in the drive housing 4a.

[0083] An equally possible location for placing the throttle device 50 is in the course of the fluid lines 5a, 5b, which is indicated by dash-dotted lines at 54. In this case, the throttle device 50, 54 is expediently a component of the fluid device 1 designed as an independent throttle valve 1c.

[0084] For example, the preferred structure of the adaptive throttling device 50 installed once or multiple times in the fluid device 1 can be described in detail. Figures 6 to 9 and explained in more detail below.

[0085] The throttle device 50 has a holding structure 56 and a throttle element 58 fixed to the holding structure 56 , wherein the throttle element 58 is designed as a throttle spring 57 that is pivotally movable relative to the holding structure 56 .

[0086] The retaining structure 56 is preferably constructed in a frame-like manner and is therefore also referred to below as a retaining frame 60. The retaining frame 60 peripherally surrounds the flow channel of the throttling device 50, which is called the throttling channel 59, so that the radial inner peripheral surface 61 of the retaining frame 60 forms a channel wall surface 62 that completely surrounds the throttling channel 59 peripherally.

[0087] The throttle channel 59 has a channel longitudinal direction 63, which is indicated by a dot-dash line and which extends exemplarily in the axial direction of a central frame longitudinal axis 64 of the holding frame 60. According to a non-illustrated embodiment, the holding frame 60 can be designed as an annular shape with a small dimension in the channel longitudinal direction 63. However, a sleeve-shaped structure of the holding frame 60 is preferred, in particular with a structural length that is greater than the maximum diameter of the throttle channel 59. This applies to the illustrated embodiment.

[0088] The holding frame 60 extends between two mutually opposite and axially directed first and second frame end faces 65a, 65b in the channel longitudinal direction 63. The throttle spring 57 is arranged in the throttle channel 59 and is fixed to the holding frame 60 in a fastening area 66 spaced apart from the two frame end faces 65a, 65b.

[0089] The throttle spring 57 preferably has a flat outer shape with a central main expansion plane 71. The main expansion plane 71 is spanned by the longitudinal axis 67 and the transverse axis 68 orthogonal thereto of the throttle spring 57. The throttle spring 57 also has a vertical axis 69, which is orthogonal to the longitudinal axis 67 and the transverse axis 68, in the axial direction of which the thickness of the throttle spring 57 is measured, wherein the spring thickness is expediently always smaller than the spring length measured in the axial direction of the longitudinal axis 67 and the spring width measured in the axial direction of the transverse axis 68.

[0090] The throttle spring 57 has, on the rear side, a proximal end section 72 oriented axially along the longitudinal axis 67, also referred to below as the longitudinal direction 67a, and, on its front side, a distal end section 73 opposite thereto in the longitudinal direction 67a. The throttle spring 57 is fastened to the holding frame 60 with its proximal end section 72 in the fastening region 66. Starting from the distal end section 73 or the fastening region 66, the throttle spring 57 extends transversely to the channel longitudinal direction 63 or transversely to the frame longitudinal axis 64 into the throttle channel 59, wherein the throttle spring ends freely with its distal end section 73 in the interior of the throttle channel 59 without any fixing measures.

[0091] As can be seen from the figure, the throttle spring 57 Figure 8 In the neutral position, which is drawn in solid lines, the main expansion plane 71 preferably runs at least substantially orthogonally to the channel longitudinal axis 63 or the frame longitudinal axis 64 .

[0092] Apart from its proximal end section 73, the throttle spring 57 is not connected to the holding structure 56. Accordingly, the throttle spring 57 is freely movable relative to the holding structure 56 or the holding frame 60 both at its distal end section 73 and at two lateral spring edge sections 75a, 75b extending between the proximal end section 72 and the distal end section. In this way, the throttle spring 57 can perform a swiveling movement 76 relative to the holding structure 56, which is Figure 8 Indicated by a double arrow and for better distinction also referred to below as the reed oscillating movement 76. The reed oscillating movement 76 is expediently at least substantially carried out in a oscillating plane 77 coinciding with the longitudinal direction 63 of the channel or the longitudinal axis 64 of the frame. The longitudinal axis 67 of the throttle reed 57 is located in the oscillating plane 77.

[0093] The throttle channel 59 is divided into two throttle channel sections 59a, 59b which are arranged one after another in the longitudinal direction 63 of the channel by a throttle spring 57 which extends into the throttle channel 59 and is preferably designed similarly to a web, and which are also referred to below as first and second throttle channel sections 59a, 59b. Starting from the neutral position 74a, the spring pivoting movement 73 is continuously possible both in the direction toward the first throttle channel section 59a and in the direction toward the second throttle channel section 59b. The positions which can be adopted by the throttle spring 57 are referred to as pivoting positions, in which the throttle spring 57 is in the neutral position 74a. Figure 8 In order to illustrate two possible pivot positions, a first pivot position 74b deflected in the direction of the first throttle channel section 59a is indicated by a dotted line on the one hand, and a second pivot position 74c deflected in the direction of the second throttle channel section 59b is indicated by a dashed line on the other hand. The second pivot position 74c is also indicated in FIG. Fig. 9 Indicated by dotted line.

[0094] The first throttle channel section 59a extends between the throttle spring 57 and the first frame end face 65a, and the second throttle channel section 59b extends between the throttle spring 57 and the second frame end face 65b. The distance of the fastening area 66 measured in the channel longitudinal direction 63 from the two frame end faces 65a, 65b is preferably determined so that the throttle spring 57 is completely arranged in the throttle channel 59 not only in the neutral position but also in every possible pivot position.

[0095] In the illustrated embodiment, the throttle spring 57 has rubber-elastic properties in its entirety. Therefore, the throttle spring can be reversibly bent in a rubber-elastic manner, in particular transversely to the main expansion plane 71, so that the throttle spring has an arcuate curvature in a curvature plane 82 orthogonal to the main expansion plane 71. The curvature plane 82 coincides with the swing plane 77. When the throttle spring 57 swings in the direction toward the first throttle channel section 59a, the throttle spring has a concave arch structure at the first spring main surface 83a facing the first throttle channel section 59a, and has a convex arch structure at its opposite second spring main surface 83b facing the second throttle channel section 59b. When the throttle spring 57 swings from the neutral position 74a in the direction of the second throttle channel section 59b, the first spring main surface 83a is convexly arched and the second spring main surface 83b is concavely arched.

[0096] The rubber-elastic properties of the throttle spring 57 are therefore preferably caused by the fact that the throttle spring 57 consists of an elastomeric material, in particular of thermoplastic polyurethane. It is advantageous if the elastomeric material used has viscoelastic properties.

[0097] The retaining structure 56 preferably also has rubber-elastic properties, wherein the retaining structure exemplarily consists of the same material as the throttle spring 57. The throttle spring 57 and the retaining structure 56 are preferably integrated into a resultant unit that can be handled in a unified manner and is referred to as a throttle unit 84. The throttle unit 84 is expediently a one-piece body in which the throttle spring 57 and the retaining structure 56 are designed as one piece with each other in the fastening area 66. The entire throttle unit 84 is produced, in particular, as a die-cast part from a thermoplastic elastomer material.

[0098] When it is used as intended, the throttle device 50 expediently assumes a use position in which it is arranged in the course of the fluid channel 8 of the fluid device 1. Such a use position of the throttle device 50 can be Figure 3 and 4This can be seen clearly in the case of the valve device 1a. Here, a sample (exemplar) of the throttling device 50, which is designed for the throttling unit 84, is inserted into each working fluid channel 8a, 8b. Due to this use as an insert, the throttling unit 84 can be referred to as an insert component. In particular, the throttling unit is assembled in the assigned working fluid channel 8a, 8b in the following manner, that is, according to Figure 2 When the bypass valve 6 is removed from the valve mounting surface 36, the throttling unit is inserted through the thus freely accessible bypass valve section opening 29a according to the assembly arrow 85 and in particular is placed into one of the bypass valve sections 29 of the working fluid channels 8a, 8b, so that the throttling unit assumes the use position.

[0099] Preferably, the holding frame 60 is coordinated at its outer circumference 86 radially opposite the throttling channel 59 with the inner contour of the longitudinal section of the assigned working fluid channel 8a, 8b which receives the holding frame in the use position, so that a press-fit fixation occurs, which causes a safe, axially immovable stop of the throttling unit 84 regardless of the prevailing pressure conditions. It goes without saying that, alternatively or additionally, a form-fit fixation in the longitudinal direction 63 of the channel can also be provided in the use position.

[0100] The retaining structure 56 expediently has at least one rubber-elastic sealing projection 87 extending around the throttle channel 59 and protruding radially in the area of ​​the outer circumference 86. The sealing projection 87 is pressed against the wall surface 89 of the working fluid channel 8a, 8b that receives the throttle unit 84 in the use position of the throttle unit 84, so that no leakage flow can occur between the outer circumference 86 and the wall surface 89 of the working fluid channel 8a, 8b.

[0101] When no external forces act on the throttle spring 57, the throttle spring 57 is in its neutral position due to its inherent stability. This can be the case, for example, as long as the throttle device 50 has not yet been properly assembled in its use position or when the use position is adopted, when the associated working fluid channels 8a, 8b are completely vented and the two throttle channel sections 59a, 59b are accordingly pressure-free or atmospheric pressure is present there.

[0102] If there is an overpressure in the throttle channel 59 and the fluid pressures in the two throttle channel sections 59a, 59b are of equal magnitude, the throttle spring 57 also assumes a neutral position. Thus, there is a pressure equilibrium state between the two throttle channel sections 59a, 59b, wherein the pressure acting on the throttle spring 57 is of equal magnitude in both flow directions 44, 45.

[0103] Starting from the neutral position, the throttle spring 5 can be caused to perform the above-mentioned spring pivoting movement 76 by the pressure fluid present in the throttle channel 59, depending on the pressure difference between the two throttle channel sections 59a, 59b, within the scope of which the throttle spring is pivoted into a pivoting position in the direction of the throttle channel sections 59a, 59b with lower fluid pressure. In this way, for example, a first pivoting position 74b or a second pivoting position 74c is possible. The greater the pressure difference, the greater the pivoting angle of the spring pivoting movement and the corresponding degree of deflection of the throttle spring 57.

[0104] By pivoting the throttle spring 57, the free flow cross section 80 of the throttle channel 59 that is available for the pressure fluid to flow past the throttle spring 57 changes. The outer contour of the throttle spring 57 is preferably adapted to the inner contour of the throttle channel 59, so that in the neutral position of the throttle spring 57, there is already a free flow cross section 80, which is however relatively small in value. In this case, it is particularly about the minimum or least free flow cross section for each possible position of the throttle spring 57. Each free flow cross section 80 that is opened in the possible pivoting positions of the throttle spring 57 is greater in value than the minimum free flow cross section in the neutral position of the throttle spring 57.

[0105] In principle, the throttle device 50 can be configured such that the throttle channel 59 is closed in the neutral position of the throttle spring 57 by the contact existing between the throttle spring 57 and the channel wall surface 62, and the free flow cross section 80 appears only when the throttle spring 57 is swung. However, a configuration with a free flow cross section that exists not only in the neutral position but also in each swung position is preferred, which applies to the illustrated embodiment.

[0106] The throttle spring 57 swivels out of the neutral position with a reversible rubber-elastic deformation, which occurs not only in the fastening area 66 but also in the entire throttle spring 57, and by which a restoring force is established that is opposite to the pressure difference force that exists. By the material selection and / or shaping of the throttle spring 57, a certain dependence of the restoring force that occurs on the swivel angle of the spring swivel movement 76 can be predetermined. In this way, it is possible to influence which cross-sectional changes the free flow cross section 80 undergoes during the spring swivel movement 76 and correspondingly at different pressure differences.

[0107] For example, there is the possibility of a design in which the cross-sectional variation of the free flow cross section 80 is a continuous function of the pressure difference, wherein the cross-sectional variation depends on the pressure difference, for example, in a decreasing, linear or progressive manner. In any case, the pressure-dependent oscillability of the throttle spring 57 causes a certain degree of self-adaptation of the free flow cross section 80 to the prevailing pressure difference, so that, for example, a large free flow cross section is set at a large pressure difference and a correspondingly high fluid demand, whereas a smaller free flow cross section is set at a small pressure difference together with a correspondingly small fluid demand. When using Figure 3 4, a certain back pressure always occurs, regardless of the size of the drive device 1b and the capacity of its drive chamber 10a, 10b, which causes a smooth movement process of the stroke movement 2. However, at the same time, in the case of a large pressure difference, at the beginning of the stroke movement 2, a rapid exhaust of the drive chamber 10a or 10b currently connected to the exhaust fluid channel 8d is also ensured. The throttle device 50 itself adapts within wider limits to the fluid flow and in particular the compressed air flow required for operating the connected drive device 1b.

[0108] The shaping of the throttle spring 57 achieved in this embodiment is characterized by a continuously decreasing bending stiffness of the throttle spring 57 starting from the proximal end section 72 toward the distal end section 73. This is achieved in particular in that the spring cross section, viewed in a plane orthogonal to the longitudinal axis 67 of the throttle spring 57, decreases, in particular at least substantially continuously, starting from the proximal end section 72 toward the distal end section 73. In this way, in particular, a decreasing deformation characteristic curve of the throttle spring 57 can be achieved.

[0109] Exemplarily, the reed width of the throttle reed 57 is constant over the entire reed length, which is particularly evident from Fig. 9 The decreasing bending stiffness towards the distal end section results from the decreasing tongue thickness, which is greatest in the proximal end section 72 and smallest in the distal end section 73, which can be seen in particular from Figure 8 It can be seen very well.

[0110] The throttle channel 59 expediently has a rectangular channel cross section, which results, for example, from the fact that the holding frame 60 has a rectangular cross-sectional profile on the inside, which is particularly evident from the fact that the holding frame 60 has a rectangular cross-sectional profile on the inside. Figure 7 and 9 55a. The channel cross section has a central cross-sectional longitudinal axis 55a and a central cross-sectional transverse axis 55b orthogonal thereto. The length of the channel cross section of the throttling channel 59 measured axially along the cross-sectional longitudinal axis 55a is preferably greater than the width measured axially along the cross-sectional transverse axis 55ba. However, for example, a square channel cross section can also be realized.

[0111] In this respect, the throttle spring 57 preferably has a rectangular outer contour when viewed in the channel longitudinal direction 63. The proximal end section 72 and the distal end section 73 on the one hand and the two lateral spring edge sections 75a, 75b on the other hand each define two opposite rectangular sides of the throttle spring 57 in pairs.

[0112] The throttle spring 57 is arranged in particular in the throttle channel 59 such that its longitudinal axis 67 coincides with the longitudinal cross-sectional axis 55a of the throttle channel 59 and its transverse axis 68 coincides with the transverse cross-sectional axis 55b of the throttle channel 59 .

[0113] The throttle spring 57 is fixed to the holding frame 60 only in the region of the proximal end section 72, while the throttle spring 57 is freely movable at the other three rectangular sides 73, 75a, 75b. In the neutral position of the throttle spring 57, a U-shaped flow gap 88 predetermining the above-mentioned minimum free flow cross section extends along the two lateral spring edge sections 75a, 75b and the distal end section 73. The flow gap is obtained by the distance greater than zero between the three rectangular sides 73, 75a, 75b and the channel wall surface 62. The cross-sectional increase of the free flow cross section 80 when the throttle spring 57 is swung is obtained in particular by the increase in the distance between the distal end section 73 and the wall surface section 62a of the rectangular profile channel wall surface 62 opposite thereto.

[0114] By way of example, the holding frame 60 is also rectangular in profile in the region of its outer periphery 86. Thus, the holding frame 60 has, for example, a shape comparable to a rectangular tube. The working fluid channels 8a, 8b are also provided with a rectangular cross section, at least in those regions in which the throttling device 50 is provided, which is adapted to the outer contour of the holding frame 60.

[0115] The bidirectional swivelability of the throttle spring 57 from the neutral position enables the pressure fluid to flow in both directions, both in the first flow direction 44 and in the second flow direction 45, wherein adaptive throttling is performed in each case. Thus, when using the fluid system 42, a variable adaptation of the flow rate of the pressure fluid can be performed in both flow directions, i.e., both when the fluid flows from the valve device 1a to the drive device 1b and when the fluid flows from the drive device 1b back to the valve device 1a.

[0116] Depending on requirements, the throttle device 50 can also be installed at a different point than in the course of the working fluid channels 8a, 8b in the fluid device 1 or fluid system 42. In principle, it is possible to install it in any existing fluid channel 8 in which a throttling function is desired.

Claims

1. A throttling device comprising a throttling element (58) arranged on a retaining structure (56) and extending into a throttling channel (59) through which a pressure fluid can flow, wherein the throttling element is movable relative to the retaining structure (56) for predefining free flow cross sections (80) of different sizes for the throttling channel (59), characterized in that The throttle element (58) is designed as a throttle spring (57) which is fixed to the holding structure (56) with a proximal end section (72), the throttle spring protruding from the proximal end section (72) and terminating freely with a distal end section (73) into the throttle channel (59) and dividing the throttle channel (59) into two throttle channel sections (59a, 59b) which are consecutive in the longitudinal direction (63) of the channel. The throttle spring (57) can be swung into different swiveling positions (74b, 74c) depending on the pressure difference between the two throttle channel sections (59a, 59b) starting from a neutral position (74a) assumed in a state of pressure equilibrium between the two throttle channel sections (59a, 59b) by changing the free flow cross section (80) of the throttle channel (59) using reversible rubber-elastic deformation that occurs in the direction toward one or the other of the two throttle channel sections (59a, 59b).

2. The throttling device according to claim 1, characterized in that: The throttle spring (57) is adapted to the inner contour of the throttle channel (59) in a molded manner so that a free flow cross-section (80) of the throttle channel (59) exists in the neutral position (74a) of the throttle spring (57), and the free flow cross-section is preferably a minimum free flow cross-section, which is smaller than the free flow cross-section (80) existing in each possible pivot position (74b, 74c) of the throttle spring (57).

3. The throttling device according to claim 1 or 2, characterized in that: The retaining structure (56) is constructed as a retaining frame (60) that completely surrounds the throttling channel (59), wherein the inner peripheral surface (61) of the retaining frame (60) suitably constitutes a channel wall surface (62) of the throttling channel (59), and the channel wall surface together with the pivotable throttling spring (57) limits the free flow cross section (80) of the throttling channel (59).

4. The throttling device according to claim 3, characterized in that: The holding frame (60) has a rectangular cross-sectional contour at least on the inside and expediently also on the outside, wherein the throttle spring (57) expediently has a rectangular outer contour when viewed in the longitudinal direction (63) of the throttle channel (59).

5. The throttling device according to claim 3 or 4, characterized in that: The retaining frame (60) is designed in a sleeve-shaped manner and extends between two mutually opposite frame end faces (65a, 65b), wherein the throttle spring (57) is fixed to the retaining frame (60) with its proximal end section (72) in a fastening area (66) spaced apart from the two frame end faces (65a, 65b).

6. The throttling device according to any one of claims 1 to 5, characterized in that: The throttle spring (57) has rubber-elastic properties as a whole, so that it can bend elastically when it oscillates, which causes a change in the free flow cross section (80), wherein the throttle spring (57) is preferably composed of an elastomeric material, wherein the elastomeric material has in particular viscoelastic properties.

7. The throttling device according to claim 6, characterized in that: The throttle spring (57) is designed with a bending stiffness that decreases, in particular continuously, starting from its proximal end section (72) toward its distal end section (73), wherein the spring cross section of the throttle spring expediently decreases starting from the proximal end section (72) toward the distal end section (73), in particular due to a decreasing spring thickness.

8. The throttling device according to any one of claims 1 to 7, characterized in that: The throttle spring (57) is designed so that when it oscillates from a neutral position (74a), a decreasing or linear or progressive cross-sectional change of the free flow cross-section (80) of the throttle channel (59) occurs depending on the pressure difference existing between the two throttle channel sections (59a, 59b).

9. The throttling device according to any one of claims 1 to 8, characterized in that: The throttling device is constructed as a throttling unit (84), which has a throttling spring (57) and a retaining structure (56) as integral components, wherein the throttling spring (57) and the retaining structure (56) are constructed in one piece with each other or are connected to each other by material bonding, and wherein the throttling unit (84) is preferably composed as a whole of a material with rubber-elastic properties.

10. The throttling device according to claim 9, characterized in that: The throttling unit (84) is constructed as an insert component which can be inserted or inserted into a fluid channel (8) of a fluid device (1) in order to use the throttling unit in a use position, wherein the throttling unit preferably has at least one rubber-elastic sealing protrusion (87) surrounding the throttling channel (59) and resting in a sealing manner on a wall surface (89) of the fluid channel (8) in the use position.

11. A fluid device having at least one fluid channel (8) configured for a pressure fluid to flow through, the fluid channel being configured at least partially as a throttling channel (59), the throttling channel belonging to a throttling device (50) assigned to the fluid channel (8), by means of which free flow cross sections (80) of different sizes of the throttling channel (59) can be predetermined, characterized in that: The throttle device (50) is designed according to any one of claims 1 to 10.

12. The fluid device according to claim 11 in combination with claim 10, characterized in that: The throttle unit (84) is inserted into the at least one fluid channel (8) as an insert component.

13. The fluid device according to claim 11 or 12, characterized in that: The fluid device is constructed as a valve device (1a), which has a valve section (7), the valve section (7) is penetrated by a plurality of fluid channels (8), among which there is at least one working fluid channel (8a, 8b) which is provided for fluid connection with a fluid-operated drive device (1b) to be controlled, wherein the valve section (7) has at least one electrically operable bypass valve (6), by which the fluid flow of a pressure fluid occurring in at least one working fluid channel (8a, 8b) can be controlled, wherein at least one working fluid channel (8a, 8b) is equipped with a throttling device (50).

14. The fluid device according to claim 13, characterized in that: Two working fluid channels (8a, 8b) of the valve section (7) can be controlled by the at least one electrically actuatable bypass valve (6), both working fluid channels being respectively equipped with a throttle device (50).

15. The fluid device according to claim 13 or 14, characterized in that: The valve section (7) has a base body (35) which is separate from the at least one bypass valve (6), on which at least one bypass valve (6) is mounted, in particular in a detachable manner, wherein at least one working fluid channel (8a, 8b) extends with a bypass valve section (29) in the bypass valve (6) and with an adjacent base section (28) in the base body (35), wherein a throttling device (50) is suitably arranged in the base section (28) or in the bypass valve section (29) of at least one working fluid channel (8a, 8b).

16. The fluid device according to claim 15, characterized in that: The valve section (7) has a plurality of bypass valves (6) mounted in a row on the base body (35), each of which is designed to control a fluid flow of a pressure fluid occurring in at least one working fluid channel (8a, 8b) equipped with a throttle device (50).

17. A fluid system having a fluid device (1) in the form of a fluid-operated drive device (1b) and a valve device (1a) for fluidically controlling the fluid-operated drive device (1b), having at least one fluid pipeline (5a, 5b) connecting the valve device (1a) to the fluid-operated drive device (1b) for transferring pressure fluid, and having at least one throttling device (50) for causing throttling of the fluid flow between the valve device (50) and the fluid-operated drive device (1b) causing a stroke movement (2) of an output element (4b) of the fluid-operated drive device (1b), characterized in that At least one throttling device (50) is constructed according to any one of claims 1 to 10 so that the fluid flow of the pressure fluid can be throttled by a free flow cross section (80) that is adaptively adapted as a function of the pressure difference, wherein the valve device (1a) is suitably constructed according to any one of claims 13 to 16.

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