Valve components

Abstract

The invention relates to a valve assembly (1) having a valve body (3), in which a fluid channel (7) is formed, which connects a fluid inlet (FE) to a fluid outlet (FA), wherein a closing body (10) which is movably supported in the flow channel (7) is subjected to a preload force (FVS) in the direction of a valve seat (5) formed in the valve body (3), wherein a fluid force (FF) acts on the closing body (10) against the preload force (FVS) to open the valve seat (5). The closing body (10) is guided axially and / or radially by at least one guide ball (12), wherein the guide ball (12) is arranged between the closing body (10) and the lateral boundary of the fluid channel (7).

Description

Technical Field

[0001] The present invention relates to a valve assembly having a valve body, in which a fluid channel is constructed for connecting a fluid inlet and a fluid outlet, wherein a closing body movably supported in the flow channel is loaded with a preload in the direction of a valve seat constructed in the valve body, wherein in order to open the valve seat, a fluid force acts on the closing body overcoming the preload. Background Art

[0002] Known vehicle brake systems with ABS and / or ESP functions provide additional functions that support the driver, for example, when maintaining a distance to the vehicle traveling ahead. This is done by actively intervening in the vehicle brake system due to the additional function by building up pressure at the wheel brake calipers without the driver having to operate the brake pedal himself. In order to prevent the driver from hearing disturbing noises, hydraulic damping measures are used, which reduce the pressure pulsations of the device of the delivery unit of the vehicle brake system. The damping measures can consist of hydraulic resistance and capacity. For the effectiveness of such hydraulic shock absorbers, large throttling generated by hydraulic resistance is used. Here, it can be considered disadvantageous that with large hydraulic resistance and the large pressure drop associated with it, the load on the drive of the delivery unit increases, the speed decreases and thus the delivery power or hydraulic build-up dynamics decreases. As a countermeasure, a hydraulic resistance can be used, which is a variable flow cross section related to the flow rate. Therefore, in the case of high volume flow, the flow cross section of the flow can be enlarged, so that a further increase in the pressure drop can be reduced.

[0003] If a variable throttle in the form of a valve is designed with a stroke that is dependent on the flow rate, flow forces can act which can cause translational and rotational vibrations of the closing body, which is loaded, for example, by a spring or a magnet. This can result in pressure vibrations that propagate in the hydraulic system and, due to the line connection to the vehicle body, can lead to noise problems in the passenger compartment.

[0004] DE 102 24 430 A1 DE discloses a valve assembly of this type which is designed as a non-return valve and which consists of a housing with an inlet opening and an outlet opening, in which an interior space is formed, which interior space has a valve seat on the inlet side and in which a closing body is movably supported, the movement of which in the opening direction is limited by a stop and on which a valve spring acting in the closing direction of the non-return valve acts. Here, the resultant force acting on the closing body when the non-return valve is opened by the flow has a transverse component with respect to the opening direction. Furthermore, the closing body is designed asymmetrically.

[0005] What is considered disadvantageous here is that the effect of vibration damping is dependent on the flow velocity and fluid properties. Therefore, this effect is only achieved for a certain temperature range and volume flow. Switching to a different fluid would lead to a different behavior.

[0006] DE 10 2013 202 588 A1 discloses a valve assembly which consists of a valve housing in which a longitudinal channel is provided which connects a valve inlet to a valve outlet. A closing body is inserted into the longitudinal channel and is loaded by a closing spring in the direction of a valve seat formed in the valve housing. In order to bypass the closing body, a hydraulic partition is preferably provided in parallel with the closing body. In order to damp vibrations of the closing body, an elastic friction element is provided in the valve housing upstream or downstream of the closing body and is accommodated in a friction-fitting manner between the valve housing and the closing body. The elastic friction element is preferably embodied as an O-ring.

[0007] It is considered disadvantageous here that the vibration damping effect cannot be guaranteed over the entire service life of the vehicle. Wear therefore reduces the lateral guidance and geometry changes of the elastic friction elements and negatively affects the opening behavior due to fluid absorption (expansion). Summary of the invention

[0008] The valve assembly according to the invention has the advantage that vibrations of the closing body can be prevented or at least reduced by axially and radially guiding the closing element. Furthermore, this function can be achieved over the entire service life of the vehicle. Furthermore, embodiments of the valve assembly according to the invention can be cheaper and easier to install and more independent of operating temperature.

[0009] An embodiment of the present invention provides a valve assembly having a valve body, in which a fluid channel is formed that connects a fluid inlet to a fluid outlet. A closing body movably supported in the fluid channel is loaded with a preload in the direction of a valve seat formed in the valve body, wherein a fluid force acts on the closing body to open the valve seat overcoming the preload. In this case, the closing body is guided axially and / or radially by at least one guide ball, wherein the at least one guide ball is arranged between the closing body and a lateral boundary of the fluid channel.

[0010] In valve assemblies known from the prior art, the distance between the damping element and the lateral boundaries of the fluid channel can be changed by tolerances, but also by material wear. This can lead to a guide drop or tensioning or overpressure of the elastic friction element. In contrast, in an embodiment of the valve assembly according to the invention, at least one guide ball is automatically readjusted. In addition, coaxiality errors or tolerances of the lateral boundaries of the fluid channel can also be compensated. As a result, the dimensional requirements for the components are lower, which leads to lower manufacturing costs overall. The effect of radial clearance compensation and the reduction of the vibration tendency of the closing body can be set via the geometry of the closing body and the guide balls and via the preload. At least one guide ball is preferably designed as a steel ball.

[0011] Embodiments of the valve arrangement according to the invention can be used, for example, as a non-return valve or a dynamic throttle valve in a hydraulic vehicle brake system.

[0012] It is particularly advantageous if the preload acts on the closing body via at least one guide ball at an angle and the at least one guide ball is tensioned by means of the closing body so that the resultant force acting on the closing body has an axially acting closing component and a transverse component acting perpendicularly thereto.

[0013] In an advantageous embodiment of the valve assembly, the hysteresis behavior during the closing process can be preset by the friction forces acting between the at least one guide ball and the lateral boundaries of the fluid channel. The acting friction forces can be preset and adapted to the respective application, for example, via the number and size of the guide balls and the embodiment of the lateral boundaries of the fluid channel.

[0014] In another advantageous design of the valve assembly, at least one guide ball can be arranged on a ball holder, which is movably guided in the fluid channel. Here, the acting preload can act on at least one guide ball via the ball holder. The shape of the ball holder can be selected arbitrarily in order to prevent at least one guide ball from "migrating" downstream. When using multiple guide balls, the spring force can be distributed more evenly to the guide balls through the ball holder. In addition, the ball holder has a radial gap for lateral limitation of the fluid channel and can additionally be rounded at the outer edge to prevent curling. In order to allow the fluid to flow downstream, a flow cross section is provided at the ball holder, and the design of the flow cross section can be selected arbitrarily. Therefore, the ball holder can, for example, have at least one through-hole and / or at least one recess, and the through-hole and / or the recess respectively constitute the flow cross section.

[0015] In another advantageous design of the valve assembly, a return spring and / or a magnet can provide a preload. Here, the return spring can be supported on a ball support at one end and on a spring support at the other end. The spring support can be configured, for example, as a retaining disk or a retaining cup, which at least partially accommodates and guides the return spring. The spring support is preferably pressed into the fluid channel, wherein the preload of the return spring can be preset via the pressing depth of the spring support and / or the characteristics of the return spring. When a magnet is used to generate the preload, the magnet preferably acts on a ferromagnetic ball support. Here, the magnetic force can act alone, supported by the spring force, or also react to the spring force.

[0016] In another advantageous embodiment of the valve assembly, the closing body can be designed as a sealing ball or a sealing bushing. In this case, the closing body is designed with a corresponding rounding so that radial play can be compensated by means of at least one guide ball arranged downstream. In addition, additional functions such as a static throttle as a bypass in the closing body can be implemented.

[0017] In another advantageous embodiment of the valve assembly, the closing body can have a sealing region and a guide front edge. The sealing region can be configured, for example, as a spherical cap on which the guide front edge is integrally formed.

[0018] In another advantageous design of the valve assembly, the leading edge can have a circular cross section and be configured as a cone or a truncated cone or a cylinder. Alternatively, the leading edge can have a polygonal cross section. A corresponding chamber is configured between the outer surface of the leading edge and the lateral boundary of the fluid channel.

[0019] In another advantageous design of the valve assembly, the leading edge can have a circular cross section and be configured as a cone or a truncated cone or a cylinder. Alternatively, the leading edge can have a polygonal cross section. Here, a corresponding chamber can be formed between the outside of the leading edge and the lateral boundary of the fluid channel.

[0020] In another advantageous embodiment of the valve assembly, a plurality of guide balls can be arranged in the fluid channel, which guide the closing body axially and / or radially. In this case, the guide balls can be arranged in the fluid channel in such a way that they support each other in the circumferential direction. This means that the number of balls is selected such that they support each other in the circumferential direction and uneven displacement of the balls can be prevented. This can prevent, for example, all balls from being located only on one side of the closing body.

[0021] Alternatively, the guide balls can be positioned and guided by a suitable mechanism, i.e., for example, a cage in a ball bearing. The design of the positioning mechanism is arbitrary. Thus, for example, the ball holder can have corresponding recesses as positioning mechanisms, which at least partially accommodate and position the guide balls. The guide balls can have a defined spacing from each other via the recesses. In addition, the chambers constructed between the outer surface of the guide front edge and the lateral boundaries of the fluid channel can at least partially accommodate and position the guide balls, respectively. Through the targeted design of the guide front edge, movable positioning of the balls can therefore be achieved. In addition, the positioning mechanism can be constructed as an axial retaining groove introduced into the valve body, which can at least partially accommodate and position the guide balls, respectively.

[0022] In another advantageous design of the valve assembly, the ball holder can be designed, for example, as a retaining ball or as a disk or as a retaining capsule or as a retaining sleeve. The ball holder can be realized cheaply as a retaining ball embodiment. The retaining capsule can at least partially accommodate one end of a return spring, and the return spring can be supported on the bottom of the retaining capsule. In addition, the design as a retaining capsule or retaining sleeve enables better guidance in the fluid channel without getting stuck. In addition, the open end of the retaining capsule and the spring holder can form a stop for limiting the opening movement of the closing body. The edge of the retaining sleeve facing away from the closing body can also form a stop for limiting the opening movement of the closing body with the spring holder or an additional stop disk.

[0023] In another advantageous embodiment of the valve assembly, the static throttle valve can form a permanent fluid connection between the fluid inlet and the fluid outlet. The static throttle valve can be configured, for example, in a sealing bushing or a valve body.

[0024] In another advantageous design of the valve assembly, the fluid channel between the valve seat and the fluid outlet can have a cylindrical fluid channel section or a stepped fluid channel section. Since the lateral force is related to the design of the lateral boundary of the fluid channel in addition to the geometry of the closing body, at least one guide ball, and the preload, the desired valve characteristics can be achieved. Therefore, the transition between the different cross-sections of the stepped fluid channel section can, for example, have a linear or curved trend in the opening direction, which has an increasing or decreasing opening cross section. Alternatively, the transition between the different cross-sections of the stepped fluid channel section can have a linear or curved trend with a decreasing opening cross section in the opening direction until the turning point, and can have a linear or curved trend with an increasing opening cross section from the turning point. In addition, at least one guide ball can be arranged in the region of the transition between the different cross-sections of the stepped fluid channel section.

[0025] Embodiments of the invention are shown in the drawings and explained in more detail in the following description.In the drawings, the same reference numerals represent components or elements that perform the same or similar functions. BRIEF DESCRIPTION OF THE DRAWINGS

[0026] Figure 1 A schematic cross-sectional view shows a first embodiment of a valve assembly according to the invention in a closed state.

[0027] Figure 2 Shows the open state Figure 1 A schematic cross-sectional view of a valve assembly according to the present invention is shown in FIG.

[0028] Figure 3 A schematic cross-sectional view shows a second embodiment of a valve assembly according to the invention in a closed state.

[0029] Figure 4 A schematic cross-sectional view shows a third embodiment of a valve assembly according to the invention in a closed state.

[0030] Figure 5 A schematic cross-sectional view shows a fourth embodiment of a valve assembly according to the invention in a closed state.

[0031] Figure 6 A schematic cross-sectional view shows a fifth embodiment of a valve assembly according to the invention in a closed state.

[0032] Figure 7 A schematic cross-sectional view shows a sixth embodiment of a valve assembly according to the invention in a closed state.

[0033] Figure 8 A schematic cross-sectional view shows a seventh embodiment of a valve assembly according to the invention in a closed state.

[0034] Fig. 9 A schematic sectional view shows an eighth embodiment of a valve assembly according to the invention in an open state.

[0035] Figures 10 to 12 A schematic top view of an exemplary embodiment of a ball carrier for a valve assembly according to the invention is shown in each case.

[0036] Fig.13 A cross-sectional view of a valve body for a valve assembly according to the invention with a further embodiment of a ball bearing is shown.

[0037] Fig.14 A schematic sectional view shows an exemplary embodiment of a closing body for a valve arrangement according to the invention.

[0038] Figures 15 to 18 Shown respectively for Fig.14Schematic cross-sectional view of an embodiment of a guiding leading edge of a closing body in FIG.

[0039] Figures 19 to 22 A schematic longitudinal section through an exemplary embodiment of a transition between different cross sections of a stepped fluid channel of a valve assembly according to the invention is shown in each case. DETAILED DESCRIPTION

[0040] As from Figures 1 to 9 It can be seen that the illustrated embodiments of the valve assembly 1 according to the present invention respectively include valve bodies 3, 3A, 3B, 3C, in which a fluid channel 7 is formed that connects a fluid inlet FE with a fluid outlet FA. A closing body 10 movably supported in the fluid channel 7 is loaded with a preload force FVS in the direction of a valve seat 5 constructed in the valve body 3, 3A, 3B, 3C, wherein a fluid force FF acts on the closing body 10 to overcome the preload force FVS to open the valve seat 5. Here, the closing body 10 is guided axially and / or radially by at least one guide ball 12. In addition, at least one guide ball 12 is arranged between the closing body 10 and the lateral boundary of the fluid channel 7.

[0041] As from Figures 1 to 9 It can also be seen that the preload force FVS acts on the closing body 10 at a certain angle via at least one guide ball 12 and at least one guide ball 12 is tensioned by means of the closing body 10, so that the resultant force acting on the closing body 10 has an axially acting closing component and a lateral component acting perpendicularly to the closing component.

[0042] As from Figures 1 to 9 It can also be seen that the valve assembly 1 is constructed as a dynamic throttle valve 1A, 1B, 1C, 1D, 1E, 1F, 1G, 1H in the illustrated embodiments. In the illustrated dynamic throttle valves 1A, 1B, 1C, 1D, 1E, 1F, 1G, 1H, the stroke of the closing body 10 is set according to the preload force FVS and the fluid force FF. In addition, the valve bodies 3, 3A, 3B, 3C in the illustrated embodiments are constructed as a cap-shaped sleeve, wherein the fluid outlet FA is introduced as an opening into the bottom of the cap-shaped sleeve, and the fluid inlet FE is arranged at the open end of the cap-shaped sleeve. The valve seat 5 is introduced as a conical seat into the bottom of the cap-shaped sleeve at the inner edge of the opening. Obviously, the valve seat 5 and / or the valve bodies 3, 3A, 3B, 3C may also have other suitable shapes.

[0043] As from Figures 1 to 9 It can also be seen that in the embodiment shown, in addition to the closing body 10, a plurality of guide balls 12 are provided in the fluid channel 7, wherein the closing body is located at the valve assembly 1. Figures 1 to 8 In the embodiment shown in FIG. 1 , the sealing ball 10A is configured as a sealing ball 10A and is disposed in the valve assembly 1. Fig. 9In the embodiment shown in the figure, the guide ball 12 is configured as a sealing bushing 10B. The number and size of the guide balls 12 can be freely selected and adapted to the structural space conditions or the design of the closing body 10 and the fluid channel 7. The guide balls 12 guide the closing body 10 radially and / or axially. This prevents or at least reduces the vibration of the closing body 10, so that the noise performance of the valve assembly 1 is significantly improved. The position of the guide balls 12 can be arbitrarily distributed on the closing body 10. In the embodiment shown, the guide balls 12 are arranged downstream of the closing body 10. The guiding performance of the guide balls 12 is improved by the preload force FVS achieved by the return spring 14 or by the magnetic force in the embodiment shown, because at least one guide ball 12 is tensioned by the closing body 10. As a result, in addition to the axial force transmission, radial forces act additionally on the guide balls 12. The radial forces counteract the axial and / or radial vibrations of the closing body 10. The effect of radial clearance compensation and the reduction of the swing tendency of the valve assembly 1 can be set via the geometry of the closing body 10 and the guide balls 12 and the preload force. The guide balls 12 are preferably designed as steel balls.

[0044] The friction between the guide ball 12 and the lateral boundaries of the fluid channel 7 can achieve a hysteresis behavior which, in the case of a high expected flow rate, causes a delayed closing of the valve assembly 1. Thus, in the case of successive pump delivery strokes, the valve assembly 1 exhibits a reduced fluid resistance.

[0045] As from Figure 1 and Figure 2 It can also be seen that the valve assembly 1 or dynamic throttle valve 1A in the embodiment shown comprises a plurality of guide balls 12 and a return spring 14, which causes a preload force FVS acting on the guide balls 12. Figure 1 and Figure 2 It can also be seen that in the embodiment shown, the return spring 14 is designed as a helical spring, which is supported at one end on the spring support 9 and at the other end on the guide ball 12. In the embodiment shown, the spring support 9 is designed as a retaining disk 9A with a central opening 9.1 and is pressed into the fluid channel 7 at the open end of the valve body 3A.

[0046] In the valve assembly 1 Figure 1 In the closed state shown, the preload force FVS of the return spring 14 is greater than the fluid force FF acting from the outside at the fluid inlet FE, so that the preload force FVS of the return spring 14 presses the closing body 10 or the sealing ball 10A into the valve seat 5 via the guide ball 12 .

[0047] In the valve assembly 1 Figure 2In the open state shown, the preload force FVS of the return spring 14 is smaller than the fluid force FF acting from the outside at the fluid inlet FE, which causes the closing body 10 or the sealing ball 10A to be pressed out of the valve seat 5 against the preload force FVS of the return spring 14. The closing body 10 or the sealing ball 10A is guided radially and axially during the opening movement or during the closing movement by the guide ball 12.

[0048] As from Figures 3 to 9 It can also be seen that the illustrated embodiment of the valve assembly 1 comprises a ball holder 16 as an additional component, on which the at least one guide ball 12 is arranged. The ball holder 16 can have any suitable shape and is guided in the fluid channel 7 axially movably with radial play. In addition, the acting preload force FVS acts on the at least one guide ball 12 via the ball holder 16. The ball holder 16 should prevent the at least one guide ball 12 from "migrating" downstream and distribute the preload force FVS more evenly to the guide ball 12.

[0049] from Figure 3 It can also be seen that the valve assembly 1 or the dynamic throttle valve 1B in the illustrated embodiment comprises a plurality of guide balls 12 and a return spring 14 designed as a helical spring, which causes a preload force FVS acting on the guide balls 12. Figure 3 It can also be seen that the ball support 16 is arranged between the return spring 14 and the guide ball 12. In the embodiment shown, the ball support 16 is designed as a retaining ball 16A. Here, the return spring 14 is supported at one end on the spring support 9 designed as a retaining disk 9A and at the other end on the retaining ball 16A. In the embodiment shown, the spring support 9 is designed with a central opening 9.1 and is pressed into the fluid channel 7 at the open end of the valve body 3A.

[0050] As from Figure 4 and Figure 5 It can also be seen that the valve assembly 1 or the dynamic throttle valve 1C, 1D in the embodiment shown comprises a plurality of guide balls 12 and a return spring 14 configured as a helical spring, which causes a preload force FVS acting on the guide balls 12. Figure 4 and Figure 5 It can also be seen that the ball support 16 is arranged between the return spring 14 and the guide ball 12. In the embodiment shown, the ball support 16 is designed as a disk 16B. Here, the ball support 16 designed as a disk 16B has at least one flow cross section in order to achieve a fluid flow in the fluid channel 7 in the open state. Figures 10 to 12 It can also be seen that the disks 16B, 16E, 16F can have at least one opening 16.1 and / or at least one recess 16.2, each of which forms at least one flow cross section. Figure 4 , 5 It can also be seen from Fig. 10 that the disk 16B shown has a central through-hole 16.1. Fig.11 It can also be seen that the disk 16E shown has a plurality of recesses 16.2 formed at the edge. Fig.12 It can also be seen that the disk 16F shown has a central opening 16 . 1 and a plurality of recesses 16 . 2 formed at the edge.

[0051] As from Figure 4 It can also be seen that the return spring 14 in the illustrated embodiment is supported at one end on the spring support 9 designed as a retaining disk 9A and at the other end on the ball support 16 designed as a disk 16B. In the illustrated embodiment, the spring support 9 is formed with a central opening 9.1 and is pressed into the fluid channel 7 at the open end of the valve body 3A.

[0052] As from Figure 5 It can also be seen that the spring support 9 in the embodiment shown is designed as a retaining cup 9B, which is pressed into the fluid channel 7 at the open end of the valve body 3B and at least partially accommodates the return spring 14. The retaining cup 9B has a central opening 9.1 at the bottom. Figure 5 It can also be seen that the return spring 14 in the embodiment shown is supported at one end on the bottom of the holding cup 9B and at the other end on the disk 16B. In addition, the open end of the holding cup 9B forms a stop 9.2 which limits the opening movement of the closing body 10.

[0053] As from Figure 6 It can also be seen that the valve assembly 1 or the dynamic throttle valve 1E in the embodiment shown comprises a plurality of guide balls 12 and a return spring 14 designed as a helical spring, which causes a preload force FVS acting on the guide balls 12. Figure 6 It can also be seen that the ball holder 16 is arranged between the return spring 14 and the guide ball 12. In the exemplary embodiment shown, the ball holder 16 is designed as a retaining pocket 16C, which at least partially accommodates the return spring 14 and has a central opening 16.1 at the bottom. In this case, the return spring 14 is supported at one end on the spring holder 9 designed as a retaining disk 9A and at the other end on the bottom of the retaining pocket 16C. In the exemplary embodiment shown, the spring holder 9 is designed with a central opening 9.1 and is pressed into the fluid channel 7 at the open end of the valve body 3B.

[0054] As from Figure 5 and Figure 6It can also be seen that in the embodiment shown, the valve assembly 1 or the dynamic throttle valve 1D, 1E respectively comprises a static throttle valve 2 which forms a permanent fluid connection between the fluid inlet FE and the fluid outlet FA. Figure 5 and Figure 6 It can also be seen that the static throttle valve 2 in the illustrated embodiment example is each formed in the base of a valve body 3B which is formed as a cap-shaped sleeve.

[0055] As from Figure 7 It can also be seen that the valve assembly 1 or dynamic throttle valve 1F in the illustrated embodiment comprises a plurality of guide balls 12 and a magnet assembly 19 which causes a preload force FVS to act on the guide balls 12. Figure 7 It can also be seen that the ball support 16 is designed as a retaining sleeve 16D made of ferromagnetic material. Here, the return spring 14 is supported at one end on the spring support 9 designed as a retaining disk 9A and at the other end on the retaining ball 16A. In addition, in the illustrated embodiment, a stop disk 16.5 with a central opening is pressed into the fluid channel 7 at the open end of the valve body 3A. The stop disk 16.5 limits the opening movement of the closing body 10.

[0056] As from Figures 1 to 7 It can also be seen that the fluid channel 7 of the dynamic throttle valve 1A, 1B, 1C, 1D, 1E, 1F or the valve assembly 1 in the illustrated embodiment has a cylindrical fluid channel section 7A between the valve seat 5 and the fluid outlet FA.

[0057] As from Figure 8 It can also be seen that the valve assembly 1 or the dynamic throttle valve 1G in the illustrated embodiment comprises a plurality of guide balls 12 and a return spring 14 designed as a helical spring, which causes a preload force FVS acting on the guide balls 12. Figure 8 It can also be seen that a ball support 16 configured as a disk 16B with a central through-hole 16.1 is provided between the return spring 14 and the guide ball 12. Figure 8 It can also be seen that the spring support 9 in the embodiment shown is designed as a retaining cup 9B, which is pressed into the fluid channel 7 at the open end of the valve body 3C and at least partially accommodates the return spring 14. At the bottom, the retaining cup 9B has a central through-opening 9.1. As can be seen from Figure 8 It can also be seen that the return spring 14 in the illustrated embodiment is supported at one end on the bottom of the retaining cup 9B and at the other end on the disk 16B. In addition, the open end of the retaining cup 9B forms a stop 9.2 which limits the opening movement of the closing body 10. Figures 1 to 7 The dynamic throttle valves 1A, 1B, 1C, 1D, 1E, 1F shown are opposite, as shown in FIG. Figure 8It can also be seen that the fluid channel 7 of the dynamic throttle valve 1G and the valve assembly 1 in the illustrated embodiment has a stepped fluid channel section 7B between the valve seat 5 and the fluid outlet FA.

[0058] As from Figure 8 It can also be seen that the guide balls 12 are arranged in the region of the transition 8 between the different cross sections of the stepped fluid channel section 7B. Figures 19 to 22 It can be seen that the transitions 8 between the different cross sections of the stepped fluid channel section 7B can have different shapes in order to predetermine the desired ventilation behavior.

[0059] As from Figure 8 and 19 It can also be seen that the transition section 8A in the exemplary embodiment shown has a linear course in the opening direction with increasing opening cross section.

[0060] As from Fig. 20 It can also be seen that the transition section 8B in the exemplary embodiment shown has a linear course in the opening direction with a decreasing opening cross section.

[0061] As from Fig.21 It can also be seen that the transition section 8C in the exemplary embodiment shown has a curved course with a decreasing opening cross section in the opening direction up to the turning point and a curved course with an increasing opening cross section starting from the turning point.

[0062] As from Fig. 22 It can also be seen that the transition section 8D in the illustrated embodiment has a linear course with a decreasing opening cross section in the opening direction up to the turning point and a linear course with an increasing opening cross section starting from the turning point.

[0063] As from Fig. 9 It can also be seen that the valve assembly 1 or dynamic throttle valve 1H in the embodiment shown comprises a plurality of guide balls 12 and a return spring 14 configured as a helical spring, which causes a preload force FVS acting on the guide balls 12. Fig. 9 It can also be seen that a ball support 16 in the form of a disk 16B is provided between the return spring 14 and the guide ball 12, the ball support having a central opening 16.1. Fig. 9 It can also be seen that the spring support 9 in the embodiment shown is designed as a retaining cup 9B, which is pressed into the fluid channel 7 at the open end of the valve body 3C. In contrast to the embodiments described so far, the retaining cup 9B in the embodiment shown completely accommodates the return spring 14, the ball support 16 and the guide ball 12 and at least partially accommodates the closing body 10. At the bottom, the retaining cup 9B has a central opening 9.1. As can be seen from Fig. 9It can also be seen that the return spring 14 in the embodiment shown is supported at one end on the bottom of the retaining cup 9B and at the other end on the disk 16B. Fig. 9 It can also be seen that the fluid channel 7 has a stepped fluid channel section 7B between the valve seat 10 . 3 formed at the fluid inlet FE and the fluid outlet FA.

[0064] As from Fig. 9 It can also be seen that at the transition between the different cross sections of the stepped fluid channel section 7B, another valve seat 5 is configured, which cooperates with the closing body 10 configured as a sealing bushing 10B. Fig. 9 It can also be seen that the closing body 10 constructed as a sealing bushing 10B has a recess and a static throttle valve 2. In the shown open state of the valve assembly 1 or the dynamic throttle valve 1H, another closing body 18 constructed as a ball is arranged in the recess, and when an undesired backflow from the fluid outlet FA to the fluid inlet FE is formed via the static throttle valve 2 in the closed state of the valve assembly 1 or the dynamic throttle valve 1H, the closing body cooperates sealingly with the valve seat 10.3 arranged at the fluid inlet FE. As can be seen from Fig. 9 It can also be seen that the static throttle valve 2 is arranged eccentrically in the sealing bushing 10B and forms a permanent fluid connection between the fluid inlet FE and the fluid outlet FA, which cannot be closed by a further closing body 18 due to the eccentric arrangement.

[0065] In addition to the described embodiments as sealing balls 10A or sealing bushings 10B, other embodiments of the closing body 10 are also possible, such as Fig.14 Visible in.

[0066] exist Fig.14 In the embodiment shown, the closing body 10C has a sealing area 10.1 and a guide front edge 11. The sealing area 10.1 in the embodiment shown is designed as a spherical cap, onto which the guide front edge 11 is molded. In the embodiment shown, the guide front edge 11 has a circular cross section and is designed as a cone 11A. Alternatively, the guide front edge 11 can also be designed as a truncated cone or a cylinder with a circular cross section.

[0067] As from Figures 15 to 18 It can also be seen that the leading edge 11 can have a polygonal cross section. Fig.15 A leading edge 11B is shown having an equilateral triangle cross section. Fig.16 A leading edge 11C is shown having a square cross-section. Fig.17 A leading edge 11D is shown having a regular pentagonal cross section. Fig.18A guide edge 11E with a regular hexagonal cross section is shown. In this case, corresponding chambers are formed between the outer surface of the guide edge 11 and the lateral boundaries of the fluid channel 7.

[0068] In the embodiments described so far, the number of guide balls 12 arranged in the fluid channel 7 is selected so that the guide balls 12 support each other in the circumferential direction. Alternatively, positioning means may be provided, which at least partially accommodate and position the guide balls 12, respectively. Thus, Fig.12 The disc 16F shown in FIG. 1 has three recesses 16.3 as positioning means, each of which at least partially accommodates and positions the guide ball 12. Fig.13 It can also be seen that the positioning means in the embodiment shown are designed as axial retaining grooves 16D introduced into the valve body 3, which each at least partially accommodate and position the guide ball 12. In the embodiment shown, three retaining grooves 16G are introduced into the valve body 3.

[0069] As from Figures 15 to 18 It can also be seen in FIG. 1 that the chamber formed between the outer surface of the guide front edge 11 and the lateral boundary of the fluid channel 7 respectively positions the guide ball 12 and at least partially accommodates it. Fig.15 The guide front edge 11B shown positions three guide balls 12. The four guide balls 12 are positioned by Fig.16 The guide front edge 11C shown in FIG. 1 is positioned, and the five guide balls 12 pass through Fig.17 The guide leading edge 11D shown in FIG. 1 is positioned, and the six guide balls 12 pass through Fig.18 The leading edge 11E shown in FIG.

Claims

1. A valve assembly (1) having a valve body (3), in which a fluid channel (7) is formed connecting a fluid inlet (FE) to a fluid outlet (FA), wherein a closing body (10) supported movably in the fluid channel (7) is loaded with a preload force (FVS) in the direction of a valve seat (5) formed in the valve body (3), wherein in order to open the valve seat (5), a fluid force (FF) acts on the closing body (10) against the preload force (FVS), characterized in that: The closing body (10) is guided axially and / or radially by at least one guide ball (12), wherein the at least one guide ball (12) is arranged between the closing body (10) and the lateral boundary of the fluid channel (7), the at least one guide ball (12) is arranged on a ball holder (16), and the ball holder is movably guided in the fluid channel (7), wherein the acting preload force (FVS) acts on the at least one guide ball (12) via the ball holder (16), and the ball holder (16) is constructed as a retaining pocket (16C), which at least partially accommodates a return spring (14) and has a central through-hole (16.1) at the bottom, and the return spring (14) is supported at one end on the spring holder (9) and at the other end on the bottom of the retaining pocket (16C).

2. The valve assembly (1) according to claim 1, characterized in that The preload force (FVS) acts on the closing body (10) at an angle via the at least one guide ball (12), and the at least one guide ball (12) is tensioned by means of the closing body (10), so that the resultant force acting on the closing body (10) has an axially acting closing component and a lateral component acting perpendicularly to the closing component.

3. The valve assembly (1) according to claim 1 or 2, characterized in that: During the closing process, a hysteresis behavior can be preset by means of friction forces acting between the at least one guide ball (12) and the lateral boundaries of the fluid channel (7).

4. The valve assembly (1) according to claim 1, characterized in that The return spring (14) is supported at one end on the ball support (16) and at the other end on the spring support (9).

5. The valve assembly (1) according to claim 4, characterized in that The spring support (9) is designed as a retaining disk (9A) or as a retaining cup (9B), which at least partially accommodates and guides the return spring (14).

6. The valve assembly (1) according to claim 1 or 2, characterized in that: The closing body (10) is configured as a sealing ball (10A) or as a sealing bushing (10B).

7. The valve assembly (1) according to claim 1 or 2, characterized in that The closing body (10C) has a sealing area (10.1) and a guiding front edge (11).

8. The valve assembly (1) according to claim 7, characterized in that The sealing area (10.1) is designed as a spherical cap, on which the guide edge (11) is integrally formed.

9. The valve assembly (1) according to claim 7, characterized in that The guiding front edge (11) has a circular cross section and is configured as a cone (11A) or a truncated cone or a cylinder.

10. The valve assembly (1) according to claim 7, characterized in that The guiding front edge (11) has a polygonal cross section, wherein corresponding chambers are formed between the outer surface of the guiding front edge (11) and the lateral boundaries of the fluid channel (7).

11. The valve assembly (1) according to claim 1 or 2, characterized in that A plurality of guide balls (12) are arranged in the fluid channel (7).

12. The valve assembly (1) according to claim 11, characterized in that The guide balls (12) are arranged in the fluid channel (7) so that the guide balls (12) support each other in the circumferential direction.

13. The valve assembly (1) according to claim 11, characterized in that The guide ball (12) is held in a positioning mechanism.

14. The valve assembly (1) according to claim 13, characterized in that The ball carrier (16) has corresponding recesses (16.3) as positioning means, which respectively at least partially accommodate and position the guide balls (12).

15. The valve assembly (1) according to claim 7, characterized in that The chambers formed between the outer surface of the guide front edge (11) and the lateral boundaries of the fluid channel (7) respectively at least partially accommodate and position the guide balls (12).

16. The valve assembly (1) according to claim 13, characterized in that The positioning means are designed as axial retaining grooves (16D) introduced into the valve body (3), each of which at least partially accommodates and positions a guide ball (12).

17. The valve assembly (1) according to claim 1 or 2, characterized in that The open end of the retaining bag (16C) and the spring bracket (9) form a stopper for limiting the opening movement of the closing body (10).

18. The valve assembly (1) according to claim 6, characterized in that The static throttle valve (2) forms a permanent fluid connection between the fluid inlet (FE) and the fluid outlet (FA).

19. The valve assembly (1) according to claim 18, characterized in that The static throttle valve (2) is constructed in the sealing bushing (10B) or the valve body (3).

20. The valve assembly (1) according to claim 1 or 2, characterized in that The fluid channel (7) between the valve seat (5) and the fluid outlet (FA) has a cylindrical fluid channel section (7A) or a stepped fluid channel section (7B).

21. The valve assembly (1) according to claim 20, characterized in that The transitions (8, 8A, 8B) between the different cross sections of the stepped fluid channel section (7B) have a linear or curved course in the opening direction with an increasing or decreasing opening cross section.

22. The valve assembly (1) according to claim 20, characterized in that The transitions (8, 8C, 8D) between the different cross sections of the stepped fluid channel section (7B) have a linear or curved course with a decreasing opening cross section in the opening direction up to a turning point and a linear or curved course with an increasing opening cross section from the turning point.

23. The valve assembly (1) according to claim 20, characterized in that The at least one guide ball (12) is arranged in the region of a transition (8) between different cross sections of the stepped fluid channel section (7B).

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