WO2011070097A1 - Damping valve and air spring - Google Patents

Abstract

The invention relates to a damping valve, comprising an outer housing, a housing bottom (211), an inner valve opening (217), which is arranged opposite the housing bottom, and a peripheral housing wall (213), which is arranged between the housing bottom and the inner valve opening and comprises a plurality of outer valve openings (215), which are arranged at varying distances from the inner valve opening. The valve further comprises a valve body (221, 223) having a plurality of through passages (229), which is arranged movably inside the outer housing as a mass oscillator. The plurality of through passages are arranged such that the outer valve openings are closed by the valve body when the valve body is in the idle position and the outer valve openings and the through passages overlap at least partially, such that a fluid flow (373, 473) is possible between the inner valve opening and the plurality of outer valve openings when the valve body is in a first deflected position in the direction of the housing bottom or in a second deflected position in the direction of the inner valve opening. At least one flexible spring (231, 233) is connected to the outer housing and the valve body in order to return the valve body from the first and the second deflected position into the idle position.

Description

 Damping valve and air spring

The present invention relates to a damping valve and to an air spring, which can be used for example in an air suspension of a vehicle.

Air springs can be used to dampen vehicle axles. In this case, an air flow within the air spring can be controlled by a damping valve.

It is the object of the present invention to provide an improved damping valve and an improved air spring.

This object is achieved by a damping valve according to claim 1 and 1 1 and an air spring according to claim 12.

The core of the invention is a valve variant of a damping valve in the form of a mass oscillator. The damping valve is characterized by a large switchable cross section, which is realized by a plurality of valve openings, which can be switched simultaneously. The fact that many valve openings are provided, a small Aussteuerweg for a full valve opening can be realized. Further advantages of the approach according to the invention lie in a friction-free mass suspension, a low-friction, pressure-neutral valve switching and a high degree of robustness, which enables a high number of switching cycles.

The present invention provides a damping valve, comprising: an outer housing having a housing bottom, an inner valve opening disposed opposite the housing bottom and a circumferential housing wall disposed between the housing bottom and the inner valve opening and having a plurality of outer valve openings; which are arranged at different distances to the inner valve opening; a valve body having a plurality of through openings and being movably disposed within the outer housing as a mass oscillator, wherein the plurality of passage openings are arranged so that the outer valve openings are closed by the valve body when the valve body is in the rest position and the outer valve openings and the passage openings at least partially overlap, so that a fluid flow between the inner valve opening and the plurality of outer valve openings is possible, when the valve body in a direction of the housing bottom first deflected Position or a second deflected in the direction of the inner valve opening position is located; and at least one flexure spring connected to the outer housing and the valve body to return the valve body from the first and second deflected positions to the rest position. The damping valve has a large number of outer valve openings which can be opened and closed simultaneously by movement of the valve body relative to the outer housing. Due to the large number of outer valve openings, a large connection cross-section can be switched with an already small valve movement.

The damping valve can be used in conjunction with an air spring. Thus, the fluid that may flow through the inner and outer valve ports may be a gas, and more particularly, may be air. The housing wall may be cylindrical, wherein a first end region is closed by the housing bottom, while a second end region has the inner valve opening and is thus open. Via the inner valve opening, the fluid can flow into an inner space of the damping valve which is enclosed by the housing wall. The outer valve openings may be evenly or non-uniformly distributed over a surface of the housing wall. In this case, a plurality of outer valve openings can be arranged adjacent to one another both along a height of the housing wall and along a circumference of the housing wall. The outer valve openings may have any suitable shape. In this case, all the outer valve openings may have the same shape or different shapes. The distances between adjacent outer valve openings can be equal. The valve body may be formed to terminate an outer surface of the valve body with an inner surface of the housing wall. In this case, the outer surface of the valve body and the inner surface of the housing wall can touch directly or via one or more sliding surfaces. The valve body and the housing wall are formed and arranged so that the valve body and the housing wall can move relative to each other as possible without friction. The passage openings of the valve body are opposite to the outer valve openings of Housing wall arranged. Here, an arrangement pattern of the through holes may correspond to a pattern of arrangement of the outer valve openings, wherein the through holes and the outer valve openings are offset from each other when the valve body is in the rest position. Thus, the outer valve openings are closed by the valve body when it is in the rest position. When the valve body has moved relative to the housing wall by a predetermined distance in the direction of the inner valve opening, the outer valve openings overlap each with through openings arranged in the direction of the housing bottom so that the fluid flows from the interior of the valve body through the outer valve Valve openings, or vice versa can flow. When the valve body has moved so far towards the inner valve opening that it assumes the second deflected position, the outer valve openings can be opened to the maximum. When the valve body has moved in a corresponding manner by a predetermined distance in the direction of the housing bottom relative to the housing wall, the outer valve openings overlap each with through openings arranged in the direction of the inner valve opening, so that the fluid in turn flows from the interior of the housing Valve body through the outer valve openings, or vice versa can flow. When the valve body has moved so far in the direction of the housing bottom that it assumes the first deflected position, the outer valve openings can be opened again maximum. The valve body may have at least in the region of the inner valve opening an opening or a cavity, which are connected to the through openings of the valve body, so that the fluid via the inner valve opening to the through holes, or vice versa, can flow. Thus, the valve body may constitute a hollow body. A required for the function of the damping valve oscillating mass may be distributed to an outer region of the valve body or disposed in the interior of the valve body.

The damping valve may include a compression spring connected to the outer housing and the valve body for balancing the valve body in the rest position. The compression spring may exert a force acting in the direction of the inner valve opening on the valve body and a weight force acting in the direction of the housing bottom balance the valve body. The compression spring may be formed as a helical spring. Furthermore, the damping valve may have a first bending spring which spans an interior of the circumferential housing wall on a side facing the inner valve opening. The first bending spring may be connected to a first end of the valve body. Furthermore, the damping valve may have a second bending spring, which spans the interior of the encircling housing wall on a side facing the housing bottom. The second bending spring may be connected to a second end of the valve body opposite the first end. The bending springs can be designed as disc coil springs. By means of the bending springs, the valve body can be held within the outer housing. For this purpose, the valve body can be attached on both sides in each case at a midpoint of the spiral springs.

According to one embodiment, the valve body may have a mass body and a circumferential inner wall with the plurality of passage openings, wherein the mass body of the circumferential inner wall surrounds and is connected via at least one connecting element with the peripheral inner wall. In this way, the flywheel mass required as a mass oscillator can be arranged centrally within the valve body. The circumferential inner wall can be made thin-walled and made of a lightweight material in this case. Between the circumferential inner wall and the mass body may be a cavity which forms a connection between the passage openings and the inner valve opening.

The damping valve may have a partition which may be disposed adjacent to the housing bottom. The partition may provide a damper chamber disposed between the housing bottom and the valve body. In the damper chamber, a damper disc can be movably arranged. The damper disk may be connected to the valve body through a damper bolt through the partition wall. As a result, an air damper can be formed, which can damp a movement of the valve body in the direction of the inner valve opening and in the direction of the housing bottom.

In this case, the housing bottom may have a depression of the damper disc opposite, which is formed so that a bending of the damper disc in the direction of the housing bottom is made possible. The bending can take place when at least one edge region of the damper disc contacts the housing bottom and the Valve body moves in the direction of the housing bottom. By bending the damper disc, the movement of the valve body can be slowed down.

According to one embodiment, the plurality of outer valve openings may be arranged in a plurality of columns and a plurality of rows in the housing wall. In this way, very many outer valve openings can be arranged on the available surface of the housing wall. A large number of outer valve openings increases the switching speed of the damping valve and the flow rate of the fluid flow.

According to the invention, adjoining surfaces of the housing wall and the valve body may touch via at least one common sliding surface. By the sliding surface, a frictional resistance between the housing wall and the valve body can be reduced. The housing wall and the valve body may be so close to each other that no or only a very small leakage current can flow between the housing wall and the valve body when the outer valve openings are closed by the valve body.

According to one embodiment, a distance between one of the inner valve opening nearest and one of the inner valve opening at the remotely located outer valve opening is at least ten times as large as a distance between the first and the second deflected position. As a result, a large number of outer valve openings can be switched by means of a small deflection of the valve body with respect to an expansion of the damper valve.

According to a further embodiment, the damping valve may have a locking device which is coupled to the valve body. About the locking device, a movement of the valve body can be prevented relative to the outer housing. The locking device can be controlled by a valve movement or by an external control valve.

The present invention further provides a damping valve, comprising: an outer housing, a housing bottom, an inner valve opening, which is arranged opposite the housing bottom and a circumferential housing wall which is arranged between the housing bottom and the inner valve opening and a A plurality of outer valve openings which are arranged at different distances to the inner valve opening; a valve body having a plurality of through holes and movably disposed within the outer housing as a mass oscillator, wherein the plurality of through holes are arranged such that the outer valve openings are closed by the valve body when the valve body is deflected in a direction first toward the housing bottom Position or one in the direction of the inner valve opening second deflected position, and the outer valve openings and the through holes at least partially overlap, so that a fluid flow between the inner valve opening and the plurality of outer valve openings is possible when the valve body is in the rest position ; and at least one bending spring connected to the outer housing and the valve body.

In this embodiment, an undesirable resonance behavior of the damping valve during operation can be prevented. For this purpose, the damping valve may be designed so that a movement of the movable mass is opposed to a friction which is greater than a restoring force of the springs acting in their entirety. A coil spring with a small spring constant can be designed to balance a dead weight of the valve body. The minimization of the spring constant can be achieved by the coil spring takes a great length compared to the movement path of the valve while the other bending spring 231 also has a low spring constant. The friction can be caused by a contact between the housing wall and the valve body. Additionally or alternatively, at least one friction element may be provided, which is arranged between the housing wall and the valve body and on which the valve body moves along when it performs a relative movement to the outer housing. The friction element can extend over an entire length between the first and the second deflected position or can also be arranged only in the edge regions which correspond to the deflected positions.

The present invention further provides an air spring, comprising: a first volume of air and a second volume of air; and a damping valve according to one of the preceding claims, which is arranged so that the inner valve opening with the first volume of air and the plurality of outer valve openings are connected to the second volume of air. For example, the air spring can have bellows and a storage volume and the damping valve may be disposed between the bellows and the storage volume.

Preferred embodiments of the present invention will be explained in more detail below with reference to the accompanying drawings. Show it:

Fig. 1 is an illustration of switching operations of a damping valve;

FIG. 2 shows an illustration of a damping valve, according to an exemplary embodiment of the invention; FIG.

3 shows an illustration of passage openings, according to an embodiment of the invention; 4 shows a further illustration of the damping valve;

5 shows a further illustration of the damping valve;

6 shows an illustration of a damping valve, according to a further exemplary embodiment of the invention;

7 shows an illustration of a damping valve, according to a further embodiment of the invention; 8 shows an illustration of a bending spring, according to a further exemplary embodiment of the invention;

Fig. 9 is a plan view of a damping valve, according to another embodiment of the invention, as shown in Figures 2 to 7;

10 is a sectional view of a damping valve, according to another

 Embodiment of the invention, as shown in Figure 1 1 to 15;

1 shows a further illustration of a damping valve, according to an embodiment of the invention; 12 shows a further illustration of switching operations of a damping valve, according to an embodiment of the invention; 13a shows a representation of a damping valve with a locking device, according to an embodiment of the invention;

Fig. 13b is another illustration of the damping valve shown in Fig. 13a; Fig. 13c is another illustration of the damping valve shown in Fig. 13a;

14 shows an illustration of a damping valve with a locking device, according to a further embodiment of the invention; FIG. 15 shows a further illustration of the damping valve shown in FIG. 14; FIG.

16 shows an illustration of a bending spring, according to a further exemplary embodiment of the invention; and FIG. 17 shows an illustration of a spiral spring, according to a further exemplary embodiment of the invention.

In the following description of the preferred embodiments of the present invention, the same or similar reference numerals are used for the elements shown in the various drawings and similar, and a repeated description of these elements will be omitted.

Fig. 1 shows a basic operation of the damping valve according to the invention, according to an embodiment of the present invention. The damping valve controls according to this embodiment, an air flow between an air spring bellows and an external memory of an air spring. Shown is a characteristic curve 101, which represents a compression travel x of the air spring over the time t. Maximum values and minimum values of the characteristic 101, which are identified by a ring, represent real opening operations or actual closing operations of the damping valve. The damping valve acts as a switching valve according to the principle of the mass oscillator, so that the valve opening takes place according to the principle of inertia or the mass deceleration or mass acceleration. During a constant compression travel speed, the valve is closed and only opens at the time of a change in direction of the compression travel. The one-way signal shown as characteristic curve 101 illustrates such a typical time profile of the compression travel. The aim of a maximum damping work is to switch the valve only in the short period of maximum or minimum, corresponding to the circled in Fig. 1 signal peaks of the characteristic curve 101, thereby enabling pressure equalization between the air spring bellows and the external memory ,

Fig. 2 shows a sectional view of a damping valve according to an embodiment of the present invention. The damping valve is arranged according to this embodiment between an inner space 202 of an air spring and an additional volume 204, for example, an external memory. By means of the damping valve, a fluid flow between the interior 202 and the external memory 204 can be enabled or prevented.

The damping valve has an outer housing, with a housing bottom 21 1 and a circumferential housing wall 213. The housing wall 213 has a plurality of

Through openings, the outer valve openings 215 form. The outer valve openings 215 can be realized as circular passage slots. The outer housing wall may be cylindrical. An open end region of the circumferential housing wall 213 lying opposite the housing bottom 21 1 can form an inner valve opening 217, through which a fluid can flow or flow out of the inner space 202 into the damping valve. The housing bottom 21 1 may form a lower side and the inner valve opening 217 form an upper side of the damping valve.

The damping valve also has a mass oscillator in the form of a valve body. The valve body according to this embodiment has a circumferential inner wall 221, a mass body 223 and guide plates 225. The mass body 223 is rigidly connected via the guide plates 225 to the circumferential inner wall 221, so that the mass body 223, the guide plates 225 and the circumferential inner wall 221 form a unit. The circumferential inner wall 221 may have a shape that is adapted to a shape of the housing wall 213. According to this embodiment the circumferential inner wall 221 is formed as a cylindrical valve body and has an outer diameter which is slightly smaller than an inner diameter of the housing wall 213. In this way, the valve body can be arranged within the housing wall 213, the relative movements of the valve body indicated by the arrow 227 parallel to a longitudinal extent of the housing wall 213, ie toward the housing bottom 21 1 or toward the inner valve opening 217, is possible. The circumferential inner wall 221 has a plurality of passage openings 229. The damping valve further comprises two bending springs 231, 233. The first bending spring 231 spans an opening of the housing wall 213 on the side facing the interior 202 and the second bending spring 233 spans an interior of the outer housing on a side facing the housing bottom 21 1. The valve body is disposed between the bending springs 231, 233 and connected thereto. According to this embodiment, a first end portion of the mass body 223 is connected to the first bending spring 231 and an opposite second end portion of the mass body 223 is connected to the second bending spring 233. The first bending spring 231 spans the first valve opening 217 and has passage openings, so that a fluid flow between the inner space 202 and an interior of the damping valve, that is to say an interior of the valve body, is made possible.

The damping valve also has a compression spring 235. The compression spring 235 is disposed between the mass body 223 and the outer housing and coupled to both, so that the compression spring can transmit a force between the mass body 223 and the outer housing. According to this embodiment, the compression spring is connected to an intermediate bottom 241. Alternatively, the compression spring 235 may be connected to the housing bottom 21 1.

The damping valve further comprises a damping device having a through the intermediate bottom 241, the housing bottom 21 1 and the housing wall 213 delimited chamber in which an air damper disk 243 is arranged to be movable. The intermediate bottom 241 spans an interior of the outer housing between the housing bottom 21 1 and the second bending spring 233. The intermediate bottom 241 may be arranged parallel to the second bending spring 233 and the housing bottom 21 1. The air damper disk 243 is rigidly connected through an opening of the intermediate bottom 241 the valve body, here the mass body 223 connected. The air damper disk 243 is arranged parallel to the intermediate bottom 241 and has a diameter which is smaller than the inner diameter of the housing wall 213. Movement of the valve body causes movement of the air damper disk 243. A fluid, for example air, disposed within the damper flows upon movement of the air damper disk 243 along its edges, as indicated by arrows, to provide pressure equalization between both sides of the air damper disk 243. This causes a damping of the movement of the air damper disk 243 and thus of the valve body.

The housing wall 213 has a plurality of outer valve openings 215. In this case, a plurality of outer valve openings 215 are arranged adjacent to each other over a height or a length of the housing wall 213. According to this embodiment, fifteen outer valve openings 215 are provided on each side of the housing wall 213. Further outer valve openings 215 are arranged in regions of the housing wall 213 which are not shown.

The inner wall 221 has a plurality of passage openings 229. In this case, a plurality of passage openings 229 are arranged adjacent to each other over a height or a length of the inner wall 221. According to this embodiment, fourteen through holes 229 are provided on each side of the inner wall 221. Further passage openings 229 are arranged in not shown areas of the inner wall 221. The passage openings 229 may have a slot width 251 of 2mm. Between adjacent passage openings 229, webs of the inner wall 221 may have a web width 252 of 4 mm and a web spacing of 6 mm. This may result in an adjustment 254 of 3mm.

When the valve body is in a rest position in which the bending springs 231, 233 can be relaxed, the inner wall 221 is aligned with the housing wall 213 so that the outer valve openings 215 are closed by the webs of the inner wall 221. The passage openings 229 are thus each located in a region between two outer valve openings 215. Thus, no fluid flow between the interior 202 of the air spring and the inner space 204 of the additional volume through the outer valve openings 215 and the through openings 229 is possible. When the valve body carries out a movement 227 out of the rest position, the inner wall 221 is displaced relative to the housing wall 213. During a minimum displacement, the outer valve openings 215 may continue to be closed by the webs of the inner wall 221. When the displacement exceeds the minimum displacement, with respect to the direction of movement 227, adjacent ones of the through holes 229 and the outer valve holes 215 respectively begin to overlap. At a predetermined Aussteuerweg, which may correspond to a maximum possible displacement, there may be a maximum overlap of the passage openings 229 and the outer valve openings 215, so that a maximum opening cross-section of the damping valve is achieved. When the

Through openings 229 and the outer valve openings 215 overlap, so a fluid flow between the inner space 202 of the air spring and the inner space 204 of the additional volume through the outer valve openings 215 and the through holes 229 therethrough is possible.

According to this embodiment, the internal spaces 202, 204 are separated from one another by separating surfaces 219 in a fluid-tight manner. The parting surfaces 219 have an opening in which the damping valve is arranged. The damping valve is connected via at least one vertical outer housing web 261 with the separating surfaces. The outer housing web 261 extends over an outer longitudinal side of the housing wall 213. At one end, the outer housing web 261 is connected via a screw connection to one of the parting surfaces. At a further end, the outer housing web 261 is connected to the housing bottom 21 1, for example via a further screw connection. Instead of the screw connection, another separable connection of the component valve with the air spring housing can be used. The housing wall 213 is arranged such that there is a fluid-tight connection between the parting surfaces and an end of the housing wall 213 facing the parting surfaces. The torsion springs 231, 233 can be realized as disc coil springs. The first bending spring 231 rests with an edge region on an end of the housing wall 213 facing the separating surfaces 219, so that the edge region of the first bending spring 231 is arranged between the separating surfaces and the housing wall 213. The mass body 223 is connected, for example via a screw, which is guided by a center of the first bending spring 231, with the first bending spring 231. The mass body 223 has a central area extending over the length of the valve body. The central body is surrounded by a conical jacket, which extends in the direction of the first bending spring 231 rejuvenated. This creates a maximum cross section for the air exchanging between the interior 202 and the additional volume 204 in the short period of valve switching. At one of the second bending spring 233 facing the end of the conical jacket at least two opposite guide plates 225 are arranged, which provide a rigid connection in the vertical direction of movement between the mass body 223 and the inner wall 221. Regarding possible horizontal transverse movements, the two guide plates 225 form an elastic connection, so that no transverse forces of friction from the inner wall 221 of the valve press against the inside of the housing wall 213. Between the inner wall and the mass body 223, a hollow space is formed, which is connected via openings of the first bending spring 231 with the inner space 202. The mass body 223 has on the second bending spring 233 facing the end of a cylindrical recess. The recess opposite a spring support 237 is arranged. In the recess, the compression spring 235 is arranged, which rests outside of the recess on the spring support 237 and which carries the weight of the mass body 223 to take a vertical center position at rest. The spring support 237 is passed through the second bending spring 233 and is supported on the intermediate bottom 241. For this purpose, the second bending spring 233 may have corresponding openings. The torsion springs 231, 233 and the intermediate bottom 241 may be aligned parallel to each other. The mass body 223 is connected via a screw, which is guided by a center of the second bending spring 231, with the second bending spring 233. About the same screw the air damper 243 may be connected to the mass body. For this purpose, a connection sleeve can be arranged between the air damper 243 and the second bending spring 233. By attaching to the bending springs 231, 233 and the support of the dead weight by the compression spring 235, the valve body can be centrally held within the outer housing wall 213 in a kind of floating state.

As a special valve features, the damping valve has a very large switchable opening cross-section for short possible valve opening times and a low Aussteuerweg for a full opening cross-section, which is already applied at 3 mm modulation on. A friction-free mass 223 enables smooth, low-transverse-force inner cylinder actuation. This results in a high degree of robustness even for high actuation numbers. Also, a force-neutral valve switching is given on the principle of the valve spool. The damping valve also has a simple structure, resulting in a low-cost manufacturing. In the following, the essential valve structure of the damping valve shown in Fig. 2 will be described according to an embodiment in more detail. The outer valve housing 213 has a large number of circularly arranged one above the other groove openings 215, while on its inner surface a smoothly vertically movable cylindrical valve body 221 also has a plurality of horizontally extending slots 229. A mass body 223 arranged centrally between two disk spiral springs 231, 233 can be moved without friction as a function of vertical axis accelerations. The compression spring 235 provides a vertical balance of the mass body weight. By means of a vertically arranged guide plate 225, the induced by inertia vertical movement 227 of the mass body 223 is transmitted to the valve body 221. If the damping valve is used in conjunction with vehicle damping, the vertical acceleration of the valve housing 221 can be converted into a valve switching movement by deflection of a vehicle axle.

A movement damping of the damping valve, according to an exemplary embodiment of the present invention, will be described with reference to FIG. 2. For vertical displacement damping and limitation of the mass body 223 with larger compression travel, an air damper 243 is placed on the valve underside.

In the case of vertical movement 227, a sheet-metal disk 243 immovably connected to the mass body 223 displaces the air below or above the disk 243. Depending on the size of the air gap between the outer edge of the sheet-metal disk 243 and the cylinder wall 213, the damping behavior can be adjusted so that in the region the axis natural frequency, which corresponds to a typical valve movement sequence, a non-bypass soft movement limit of the mass body 223 and thus of the valve body 221 is achieved. Since virtually all the air content is displaced above or below the air damper disk 243, a good damping performance results. To a possible negative pressure "sticking" of the disc 243 after

To avoid ground contact, the disc 243 can additionally with small

Through holes are provided. As a travel limit in the case of large compression travel amplitudes, the sheet-metal disc 243 of the air damper serves in its capacity as a plate spring. In the case of a large sequence of movements in the direction of the upper disk spiral springs 231, the air damper disk 243 touches the intermediate bottom 241 over the whole area and stops the over-travel due to their common disk spring characteristic.

In the case of a large movement in the direction of the housing bottom 21 1 touches the air damper disk 243 with its outer circular edge of the housing bottom and also stops by their plate spring characteristic the way. To prevent a full-surface touchdown of the air damper disk 243 on the housing bottom 21 1 of this floor has a conical recess.

A cutout 264 of the inner wall 221, which forms the cylindrical valve body, for example in the form of a V2A tube, will be described in more detail with reference to FIG

3 shows an arrangement of a plurality of passage openings 229 in the inner wall 221, according to an embodiment of the present invention. The section of the inner wall 221 shown has 12 passage openings 229, three of which are arranged side by side in a row and four in each case in a column. According to this embodiment, the through holes 229 are formed as elongated holes, which are arranged all around in the valve body 221. A longitudinal extent of the passage openings 229 may extend parallel to a circumferential line of the circumferential inner wall 221. The outer valve openings can be designed and arranged in a corresponding manner. These outer valve openings may also consist of continuous circular passage slots.

FIG. 4 shows a further illustration of the damping valve illustrated in FIG. 2, according to an exemplary embodiment in which the mass body 223 has displaced relative to the housing wall 213 in the direction of the interior 202 of the air spring. As a result, the bending springs 231, 233 according to the deflection 227 of the mass body 223 upwards, ie in the direction of the interior 202, moved. An alternatively or in addition to the air damper disk upper stop 371 prevents further deflection 227. The air damper 243 has moved in the direction of the intermediate floor 241. postponed. A fluid flow 373 flows from the inner space 202 through the through-openings 229 and the outer valve openings 215 into the intermediate volume 204. The valve function of the damping valve according to an embodiment will be described with reference to FIG. During the compression phase of a vehicle axle, the bellows pressure of an air spring increases. Shortly before the upper turnaround point movement speed is delayed, so that the mass body 223 with respect to the valve housing 213 moves upward. Thus, the cylindrical valve body 221 is also moved upwards and thus opens all through holes 229. Already from a mass deflection of only 3 mm (with groove width 2 mm), the valve switching cross section is fully open, resulting in a cylinder diameter of 100 mm with a height of 100 mm effective valve opening area of 95 cm ² or a hole diameter of 1 1 cm corresponds. A large opening cross-section is necessary in order to produce a substantial pressure equalization of the air spring between the interior 202 and the additional volume 204 during the short opening time in the upper or lower movement turning point.

FIG. 5 shows a further illustration of the damping valve illustrated in FIG. 2, according to an exemplary embodiment in which the mass body 223 has displaced relative to the housing wall 213 in the direction of the housing bottom 21 1. As a result, the bending springs 231, 233 corresponding to the deflection 227 of the mass body 223 downward, so in the direction of the housing bottom 21 1, moved. An alternative or in addition to the air damper disk lower stop 471 prevents further deflection 227. The air damper 243 has moved in the direction of the housing bottom 21 1 and rests with edge regions on the housing bottom 21 1. The housing bottom 21 1 has a conical depression which has a greatest depth in the center of the housing bottom 21 1. This allows a deflection of the damper disc 243 in the direction of the housing bottom 21 first The housing bottom 21 1 further has a recess into which an end portion of the screw can lower, with the damper plate 243 is connected to the mass body 223. A sleeve 245 is designed in its height so that simultaneously with the contact of the outer edge of the damper disk 243 on the housing bottom 21 1, the lower edge of the mass body 223 rests on the intermediate bottom 241. This results in the same spring rigidity for the upper and lower stops and thus a similar limiting behavior. A fluid flow 473 flows from the intermediate volume 204 through the through-openings 229 and the outer valve openings 215 into the interior 202.

With reference to FIG. 5, the valve function of the damping valve according to an exemplary embodiment will be further described. During rebound by axle movement down, the Federbalgdruck decreases compared to the pressure in the additional volume 204. Shortly before the lower Wegtotpunkt delays the Bewegungsg- expiration, so that the mass body 223 relative to the valve housing 213 moves down. As a result, the cylindrical valve body 221 is moved downwards and thus opens all slot openings 215. After only 3 mm mass displacement, the switching cross-section of the valve is fully open even in this movement phase.

To avoid overstroke during rebound, the washer 243 of the air damper can be used as a deflection limiter. By their plate-spring-like bending so that a further deflection of the valve can be prevented, so that an overstroke of the mass body 223 and thus of the cylindrical valve body 221 is avoided. Optionally, the cylindrical valve body 221 complementary or alternatively have its own elastic movement stop, as is the case in the embodiment shown in Fig. 6.

The damping valve allows a low-friction valve switching. So that the valve button with its slots 215, 229 despite a high possible number of actuation has no fear of wear failures, a movement decoupling between the oscillating mass body 223 and the cylindrical tube 213 can be made. This means that with the help of the guide plate 225 only vertical movement forces from the elastic frictionless suspension of the mass 223 are transmitted to the valve switching element 221, while slight horizontal and tilting movements of the mass 223 by the bending movement of the guide plate 225 and its cardan elastic suspension are prevented , as described with reference to FIG. 7.

A relative to the weight comparatively large sliding surface of the cylindrical valve member 221 minimizes the risk of damage. Another measure to reduce friction may be the attachment of slide bands 675 which prevent direct contact with the valve buttons. If necessary, An additional elastic height stop of the cylindrical tube can prevent wear damage.

6 shows a damping valve according to a further exemplary embodiment of the present invention in a rest position. In contrast to the execution valve shown in FIG. 1, the damping valve has only one bending spring 233 for fixing the mass body 223. The bending spring 233 may in turn be designed as a disc spiral spring. The mass body 223 is designed as a compact cylindrical block and has a recess for the compression spring. The mass body is disposed in the lower half of the inner wall 221. As a further difference, the damping valve has an upper elastic height stop 371 and a lower elastic height stop 471. The height stop 371 is arranged at the upper end of the housing wall 213 and forms an inwardly projecting extension, which limits a movement of the inner wall 221 upwards. The height stop 471 is arranged on an inner wall facing side of the bending spring 233 forms an obliquely projecting in the direction of the inner wall 221 extension, which limits a movement of the inner wall 221 down. Furthermore, the inner wall 221 on one of the housing wall 213 facing side sliding bands or guide bands 675. According to this embodiment, a sliding or guide band 675 is respectively arranged at an upper and a lower end of the inner wall 221. From Fig. 6 it can be seen that the passage openings 229 are distributed in the form of elongated holes in a plurality of rows and columns over a height and a circumference of the inner wall 221.

As a possible rationalization measures, there is an omission of one of the two disk spiral springs shown in FIG. Fig. 6 shows, for example, a saving of the upper coil spring with a corresponding reinforcement of the lower coil spring 233 and a low center of gravity of the mass body 223rd

According to a further embodiment, the mass body can be integrated into the valve tube 221. This results in a mass body in the form of the tube 221 with a thick wall thickness in the event that no damage to the valve sealing surfaces occur as a result of frequent valve actuation. As a possible series solution, the housing 21 1 and the valve spool 221 can be made of aluminum or plastic. Valve opening slots 215, 229 can be sprayed thereby. In order to achieve a relatively small leak in the closed state of the valve, the valve button should only be designed as large as necessary.

Fig. 7 shows the damping valve shown in Fig. 6 at a maximum deflection. The inner wall 221 has moved upwards relative to the housing wall 213 so far that an upper edge of the inner wall 221 rests against the upper elastic height stop 371.

Fig. 8 shows a disk spiral spring 233 for mass body fixation, according to an embodiment of the present invention, in plan view. The disc spiral spring 233 has a plurality of openings through which a fluid flow is possible. Furthermore, the disc spiral spring 233 has a central attachment opening.

Fig. 9 shows a plan view of a valve, according to an embodiment of the present invention. The valve may be one of the damping valves shown in the preceding figures with a thin-walled cylindrical tube 221. Shown is a cylindrical outer housing 213 with circumferential groove openings, a guide plate 225, a cylindrical tube 221 with slots, a plurality of vertical outer housing webs 261, which are arranged distributed around the outer housing 213, a lower disc coil spring 233 and a mass body 223nd The guide plate 225 may consist of two parts, which are arranged on opposite sides of the mass body 223 and are each connected at opposite locations with the mass body 233. End region of the two guide plates can be brought together and connected to the tube 221 at two opposite points. Further, in Fig. 9, a section line A is shown, which corresponds to the sectional views of Figures 2, 4 to 7.

10 shows a top view of an interior region of a damping valve, according to an embodiment of the present invention. Shown are a cylindrical outer housing 213 with circumferential groove openings, a mass body 223, a vertical inner housing web 221 and a vertical outer housing web 261st A cylindrical run the Innenventilköper ring 221 may be made in this embodiment of thicker plastic, instead of a perforated thin-walled steel tube, as it can be used for example in the embodiment shown in Fig. 9. Further, the connecting rod 1 181 and the section line A are shown.

Fig. 1 1 shows a side view of the damping valve shown in Fig. 10 along the section line A. Also shown is a section line B, which corresponds to the sectional view shown in Fig. 10. The mass body 223 is connected to a plurality of vertical inner housing webs 225 via a connecting rod 1 181 for valve spool actuation. The inner housing webs 221 are connected to an upper end of the connecting rod 1 181, in the region of an upper end of the inner wall 221, with the same. The inner housing webs 221 may be connected to the same over an entire length of the inner wall 221. A movement of the inner wall 221 upwards may be limited by upper limits. At an upper and a lower end region, the inner wall 221 can each have a sliding and / or guide band. The vertical outer web 261 may form a unit with the housing wall and the valve housing bottom 21 1. It can only be a bending spring 233, which may be formed as a disc spiral spring, are used in the lower valve area for ground fixation. The connecting rod 1 181 may protrude beyond a lower end of the inner wall and the mass body 223 and passed through the intermediate bottom 241. An attachment of the mass body 223 to the connecting rod 1 181 can be made via a resilient pad 1 183 for a bending decoupling to the connecting rod 1 181. The damper disk 243 of the air damper is connected to a lower end portion of the connecting rod 1 181. According to this embodiment, the weight balance spring 235 is disposed between the valve housing bottom 21 1 and the damper disk 243. The valve housing bottom 21 1 has a corresponding centrally disposed recess which can receive and guide the spring 235. The cylindrical round Innenventilköper 221 with the inner housing webs 221 may be made of thicker plastic.

Fig. 12 shows a basic operation of the damping valve according to the invention, according to another embodiment of the present invention. The damping valve is suitable according to this embodiment for damping a vehicle body. The damping valve can control an air flow between an air spring bellows and an external reservoir of an air spring. Shown is a diagram, at on the abscissa the time t in seconds and on the ordinate of the compression travel x is plotted. Shown is a characteristic curve 101, which represents the spring deflection x of the air spring, with 12 Hz axis oscillations, plotted over the time t. Further, a buildup swing 1202 is applied at a frequency of 1 Hz over time. The body swing 1202 represents a vibration of the vehicle body. Also shown are a vehicle body height value 1204 and a damper threshold 1206 for valve switching of the damping valve. According to this embodiment, valve switching 1208 of the damping valve takes place only when the vehicle body is at a height that is above or at least near the barrier 1206. If the vehicle body is below the blocking threshold 1206, valve shifting is prevented at least during the period of the lower direction reversal of the axle vibrations.

According to this exemplary embodiment, for better damping of the vehicle body, it is helpful to damp the vibrations 101 of the axial natural frequency only in one direction of movement by opening the valve. Although this reduces the damping performance of the Axis excitation, but reinforced on the other hand, the damping performance of the vehicle body vibrations. By means of the embodiments of a damping valve shown in the following figures, it is possible to prevent unwanted opening of the damping valve. For example, the opening may be prevented or enabled depending on a position of the vehicle body. 13a shows a side view of a further embodiment of the damping valve shown in FIG. 10 along the section line A in the rest position closed. Shown is also a section line B, which corresponds to the sectional view shown in Fig. 10. The embodiment shown in Fig. 13a corresponds to the embodiment shown in Fig. 1 1 with the differences that the intermediate bottom 241 according to this embodiment is movably mounted and the damping valve additionally has a locking device 1391, 1393, 1395, 1397. The locking device 1391, 1393, 1395, 1397 is disposed between the housing bottom and the mass body 223 and connected to the housing wall. The locking device has two curved disc springs 1391, which are provided with slots, so that a fluid flow through the disc springs 1391 is possible therethrough. The slots also reduce the bending force required to deflect the disc springs 1391. The plate springs 1391 are arranged between the bending spring 233 for fixing the mass body 223 and the intermediate bottom 241. At its outer edge, the disc springs 1391 are rigidly connected to the housing wall of the outer housing. The plate springs 1391 have centrally a through opening, in which a sliding bushing 1393 is arranged, which is connected to the disc springs 1391. The two plate springs 1391 can touch each other in the region of the slide bushing 1393, so that the plate springs 1391 are bent toward each other in a rest position. The slide bush 1393 encloses a portion of the connecting rod 1 181 projecting beyond a lower end of the mass body 223 or a sleeve enclosing the connecting rod 1 181 and fixedly connected to the connecting rod 1 181 or the mass body 223. When the plate springs 1391 are in the rest position, the connecting rod 1 181 can move relative to the sliding bushing 1393. There is a slight play between the sliding bush 1393 and the connecting rod 1 181. On the other hand, when the plate springs 1391 are in an extended position, they press against the sliding bushing 1393, thereby causing the sliding bush 1393 to become jammed against the connecting rod 1 181, so that movement of the connecting rod 1 181 relative to the sliding bush 1393 is prevented , The slide bushing 1393 can be slotted with a clamping option based on a self-locking wedge insertion principle. Between the plate springs 1391, an intermediate piece 1395 is arranged. The intermediate piece 1395 is rigidly connected at one end to the housing wall and extends into the space enclosed by the housing wall interior. The intermediate piece 1395 may be annular. The intermediate piece 1395 can taper starting from the housing wall, so that the plate springs 1391 can be bent starting from a rest position in the direction of the intermediate piece 1395 and thereby can be stretched so that they can press against the slide bushing 1393. According to one embodiment, the angle deviating from the horizontal plane, relative to the coefficient of friction of the sliding bush 1393 relative to the sleeve 245, must act as a supercritical wedge angle and thus self-locking. On one of the housing wall opposite the free end, the intermediate piece 1395 circumferentially on a plurality of through holes, in which locking pins 1397 are arranged to be movable. The locking pins 1397 are each passed through the disc springs 1391 and have entrainment at their ends. meeinrichtungen, for example in the form of thickening. The locking pins 1397 are aligned parallel to a direction of movement of the mass body 223. If the locking pins 1397 move downwards, that is to say in the direction of the housing bottom, they also take the upper of the plate springs 1391, that is, the plate springs 1391 facing the bending spring 233, and push them downwards towards the intermediate piece 1395. As a result, the upper plate spring 1391 is stretched and presses against the sliding bush 1393, whereby a friction with respect to the sleeve 245 is formed. Due to the supercritical support angle of the elongated plate spring 1391, a self-locking closed movement of the valve is created in the further course of motion. When the locking pins 1397 move upwardly, they entrain the lower of the Belleville springs 1391 and push them upward toward the intermediate piece 1395. As a result, the lower plate spring 1391 is stretched and presses against the sliding bushing 1393, whereby here also a self-locking and thus locking of the connecting rod 1 181 is effected. The movable intermediate bottom 241 facing ends of the locking pins 1397 may be fixedly connected to the intermediate bottom 241 so that they can absorb both pressure and tensile forces from the intermediate bottom 241. By a movement of the movable intermediate floor 241 upwards, the locking pins 1397 can also be moved upwards. By moving the movable shelf downward, the locking pins 1397 can be moved downwardly.

The movable intermediate floor 241 may move to compensate for a pressure difference existing on both sides of the intermediate floor 241. According to this embodiment, there is a pressure difference between the pressure prevailing in the inner space 202 and the mean pressure which exists in the air damper chamber, which is limited according to this embodiment by the intermediate bottom 241, the housing wall and the housing bottom. Since the intermediate bottom 241 has only small air exchange openings in relation to the interior 202, this space below the intermediate bottom 241 contains the mean pressure and thus corresponds to an average construction height 1204. Alternatively, a corresponding reference chamber can be arranged at another point of the damping valve. If the pressure in the reference chamber is less than the pressure in the interior 202, the intermediate bottom 241 is pressed down. On the other hand, if the pressure in the reference chamber is greater than the pressure in the inner space 202, the intermediate bottom 241 is pushed upwards. According to an embodiment, the damping valve may be configured to dampen an axle movement of a vehicle. For this purpose, the damping valve can be tuned to an axial frequency, for example 12 Hz. By a movement of a vehicle body, the axle movement can be superimposed by a movement of the body. For example, a body vibration may have a frequency of 1 Hz. By moving the assembly out of a mid-position, a momentary pressure in the interior 202 may change with respect to a mean pressure. If the damping valve remains closed in such a case, then the air spring bellows acts as a pure spring. As a result, the structure can quickly return to the middle position.

By the locking device 1391, 1393, 1395, 1397, an undesirable opening of the damping valve can be prevented for this case.

FIG. 13b shows the damping valve shown in FIG. 13a in a position in which the sliding bush 1393 prevents a downward movement of the connecting rod 1 181 to the sliding operation. From Fig. 13b it can be seen that the movable intermediate floor 241 is raised. As a result, the locking pins are shifted upward and the lower of the two plate springs 1391 stretched. The extension of the disc springs 1391, in particular the lower of the plate springs 1391, causes a force indicated by arrows, which is exerted by the disc springs 1391 on the slide bushing and causes a locking of the sliding bush 1393.

In Fig. 13b there is shown a direction of movement 1399 indicating a direction of movement of a vehicle axle that can be damped by the damping valve. The vehicle axle moves down in this case. Thereby, the pressure p1 in the inner space 202, for example, a bellows, lower than in the reference space between the movable intermediate bottom 241 and the housing bottom. This leads to a pressure on the ceiling, so the movable intermediate floor 241, whereby this moves upwards. According to this exemplary embodiment, a pressure p1 prevails in the interior 202 and a pressure p2 in the additional volume 204, the pressure p1 being smaller than the pressure p2.

Fig. 13c shows the damping valve of Fig. 13b, in which case a direction of movement 1399 of the axle is directed upwards. This increases the pressure p1 in the interior 202. This causes a lowering of the movable intermediate floor 241 to provide a pressure equalization.

FIG. 14 shows a side view of a further embodiment of the damping valve shown in FIG. 10 along the section line A in the inoperative position. The embodiment shown in Fig. 14 corresponds to the embodiment shown in FIG. 12 with the differences that the intermediate bottom 241 according to this embodiment is rigid and the intermediate piece of the locking device has no locking pins, but an electric coil 1495. The electrical coil 1495 may comprise a plurality of windings, which may be wound in a circle and thus guided parallel to the housing wall. Thus, the connecting rod 1 181 may be located at the center of the electrical coil 1495. In the position shown in Fig. 14, the electric coil 1495 is not current flowing through. The sliding bush 1393 is not locked, thus allowing movement of the connecting rod 1 181.

Fig. 15 shows the damping valve shown in Fig. 14 in a position in which the slide bushing 1393 prevents any valve opening. From Fig. 15 it can be seen that the disc springs 1391 bear against the intermediate piece and are thereby stretched. The stretching of the plate springs 1391 causes a force indicated by arrows, which is exerted by the plate springs 1391 on the slide bushing, and causes a locking of the sliding bushing 1393. A current flows through the electric coil, whereby a magnetic field is built up around the windings of the coil whose field lines pass through the plate springs 1391. As a result, the plate springs 1391 are attracted to the intermediate piece and thus stretched. Due to the supercritical angle of the stretched disc springs 1391 a self-locking effect is achieved which requires a comparatively small Zuspannkaft the disc springs on the slide bush 1393. The damping valve may include electrical contacts for providing the current to the electrical coil. The current through the electrical coil may be controlled by a controller monitoring, for example, a pressure in the interior 202. For example, the current through the coil may be provided when the pressure in the internal space 202 deviates from a mean pressure.

Figures 16 and 17 show further embodiments of bending springs 233. Figure 16 shows a Federflapplayout with a meandering arrangement with the possibility of a linear bend. This allows avoiding a plate spring characteristic. 17 shows a spring flapplayout with a large web length with a maximum web width for a minimum bending load.

By the plate springs, starting from a circumferential edge region, extending in the direction of the center slots, a bending force required for bending the disc springs is significantly reduced.

The same principle applies to the exercise book, in which case has a lower peripheral edge with upwardly extending slots.

Each of the springs of the damping valves has a natural frequency. This results in a resonance frequency of the valve body of the damping valves shown. The resonant frequency of the valve body may be set to be between an axle frequency and a body frequency when used for vehicle damping. The resonance frequency can be influenced by a friction between the valve body and, for example, the outer housing.

According to a further embodiment of the invention, the damping valve is operated in a mode in which no resonance of movement of the valve body occurs. The damping valve may have a structure as shown in the figures, with the difference that the damping valve is opened when the valve body is in the middle position corresponding to the rest position of the other embodiments. In contrast, the damping valve may be closed when the valve body is in the first or the second deflected position, ie at the respective lower or upper stop. The spring hardness of the springs used are chosen so that a frictional force or static friction between the valve body and the outer housing is greater than a restoring force caused by the springs. The friction between the valve body and the outer housing can be adjusted by guide belts, which are arranged between the valve body and the outer housing. The friction is so great that the moving mass of the valve body only comes into motion relative to the outer housing at the point of inflection of a compression movement. In order to achieve a suitable spring rate, the spring can have a large length, whereas the spring stroke is very small with respect to the length of the spring. If the valve body is in a deflected position, it remains in this position due to the high frictional force. Only when a change in direction of the compression travel takes place after a constant compression travel speed, the friction force is overcome and the valve body moves through the central position in which the valve is opened to the opposite stop. In this position, the valve body remains during the subsequent oppositely directed constant compression travel speed. Only with a renewed change of direction of the compression travel of the valve body moves back through the center position through to the turn opposite stop. Thus, with the same acceleration due to friction, the valve body does not return to the middle position. Only when reaching the next dead center of the acceleration curve, the friction is overcome and the valve body reaches the center position in which the valve is opened.

The described embodiments are chosen only as examples and can be combined with each other. Also, the damping valve may be provided for other applications. Said measures are only given as examples and can be adapted according to the respective requirements.

LIST OF REFERENCE NUMBERS

101 characteristic

 202 interior

204 additional volume

 21 1 caseback

 213 housing wall

 215 outer valve openings

 217 inner valve opening

219 separating surface

 221 inner wall

 223 mass bodies

 225 guide plate (for vertical force coupling)

 226 valve body stiffening (denoted 225 in FIG. 11, 13a, 13b, 13c, 14, 15)

 227 movement

 229 passage opening

 231, 233 spiral springs

 235 compression spring

237 spring support

 241 intermediate floor

 243 air damper disk

 245 sleeve

 261 outer housing bridge

262 spring support

 264 detail

 371, 471 attacks

 373, 473 fluid flows

 675 sliding belt

1 181 connecting rod (for vertical force coupling, similar to 225)

 1202 extension brackets

 1204 average construction height

 1206 Valve switching threshold

 1208 valve switching

1391 disc springs 1393 Sliding bush 1395 Intermediate piece 1397 Locking pin 1399 Direction of movement 1495 Electric coil

Claims

claims An attenuation valve comprising: an outer housing having a housing bottom (21 1), an inner valve opening (217) disposed opposite the housing bottom and a circumferential housing wall (213) disposed between the housing bottom and the inner valve port and a plurality outer valve openings (215) arranged at different distances from the inner valve opening; a valve body (221, 223) having a plurality of through holes (229) and movably disposed within the outer housing as a mass oscillator, the plurality of through holes being arranged such that the outer valve openings are closed by the valve body when the valve body is in the rest position and the outer valve openings and the through openings at least partially overlap, so that a id id flow (373, 473) between the inner valve opening and the plurality of outer valve openings is possible, when the valve body in a direction towards the housing bottom is the first deflected position or a second deflected in the direction of the inner valve opening second position; and at least one flexure spring (231, 233) connected to the outer case and the valve body for returning the valve body from the first and second deflected positions to the rest position. A damping valve according to claim 1, comprising a compression spring (235) connected to the outer housing (21 1, 213) and the valve body (223) for balancing the valve body in the rest position. Damping valve according to one of the preceding claims, comprising a first bending spring (231) which spans an interior of the circumferential housing wall (213) on a side facing the inner valve opening (217) and is connected to a first end of the valve body (223) and with a second spiral spring (233), which is the interior of the encircling housing wall on one of the housing bottom (21 1) facing side spanned and connected to a first end opposite the second end of the valve body. Damping valve according to one of the preceding claims, wherein the valve body has a mass body (223) and a circumferential inner wall (221) with the plurality of through holes (229), wherein the mass body of the circumferential inner wall and surrounds at least one connecting element (225) the circumferential inner wall is connected. Damping valve according to one of the preceding claims, comprising a partition wall (241) which is arranged adjacent to the housing bottom (21 1) in order to create a damper chamber arranged between the housing bottom and the valve body and with a damper disc (243) movably arranged in the damper chamber. , which is connected via a damper bolt through the partition wall with the valve body (223). Damping valve according to claim 5, wherein the housing bottom (21 1) has a recess opposite the damper disc (243), which is formed so as to allow bending of the damper disc in the direction of the housing bottom, if at least one edge region of the damper disc contacts the housing bottom. A damping valve according to any one of the preceding claims, wherein the plurality of outer valve openings (215) are arranged in a plurality of columns and a plurality of rows in the housing wall (213). Damping valve according to one of the preceding claims, in which abutting surfaces of the housing wall (213) and of the valve body (221) contact via at least one common equal area. A damping valve according to any one of the preceding claims, wherein a distance between one of the inner valve opening (217) nearest and one of the inner valve opening farthest outer valve opening (215) is at least ten times as large as a distance between the first and second deflected Position. 10. Damping valve according to one of the preceding claims, with a locking device (1391, 1393, 1395, 1397) which is coupled to the valve body (221, 223) to a movement of the valve body relative to the outer housing (21 1, 213) prevent. 1 1. An attenuation valve comprising: an outer housing having a housing bottom (21 1), an inner valve opening (217) disposed opposite the housing bottom, and a circumferential housing wall (213) disposed between the housing bottom and the inner valve port and a plurality of outer valve openings (215) arranged at different distances from the inner valve opening; a valve body (221, 223) having a plurality of through holes (229) and movably disposed within the outer housing as a mass oscillator, the plurality of through holes being arranged such that the outer valve openings are closed by the valve body when the valve body in a first deflected towards the housing bottom or a position deflected in the direction of the inner valve opening second position, and the outer valve openings and the through holes at least partially overlap, so that a fluid flow (373, 473) between the inner valve opening and the A plurality of outer valve openings is possible when the valve body is in the rest position; and at least one bending spring (231, 233) connected to the outer housing and the valve body. 12. An air spring, comprising: a first volume of air (202) and a second volume of air (204); and a damping valve according to one of the preceding claims, arranged such that the inner valve opening (217) is connected to the first volume of air and the plurality of outer valve openings (215) are connected to the second volume of air.