CN209892680U - Adjustable damping valve device - Google Patents

Abstract

The invention relates to a damping valve device comprising a valve housing in which an axial reciprocating movement is carried out by means of a solenoid-driven valve armature and a pump device is actuated by means of this reciprocating movement in order to expel gas inclusions from the valve housing, wherein the valve housing has an outlet channel, the connection of which is arranged axially at least close to a sealing point for the coil in the region of the valve housing that is filled with damping medium, so that the connection is axially higher than the deepest suction point of the pump device.

Description

Adjustable damping valve device

Technical Field

The utility model relates to a damping valve device that can adjust. The damping valve device comprises a valve housing in which an axial reciprocating movement is carried out by means of a solenoid-operated valve armature and by means of which a pump is actuated in order to expel gas inclusions from the valve housing.

Background

In particular, vibration dampers which do not have a strict separation between the hydraulic damping medium and the gaseous pressure medium are at risk of: the pressure medium dissolves in the damping medium and, for example, as a result of a pressure or temperature drop, again emerges as bubbles in the working chamber of the vibration damper or in the interior of the damping valve device in an accumulating manner.

One possible solution for solving the above-mentioned problem may consist in arranging a separating piston between the damping medium and the gaseous pressure medium or enclosing the pressure medium in an air bag, such as, for example, that disclosed by DE 19835222 a 1. Both solutions cause additional overhead or additional costs.

DE 102014215563 a1 discloses an adjustable damping valve device with a ventilation channel. In the installed position of the damping valve device, the ventilation channel connects the highest point of the interior of the valve housing, in particular the reciprocating chamber for the axially movable valve armature, to the adjacent working chamber. The diagram according to fig. 1 shows almost exactly what is achieved for mass production. In order to protect the coil body against the penetration of damping medium, several seals are required.

DE 102015204030B 3 describes a modification of the damping valve device according to DE 102014215563 a 1. A pump device is used to enable gaseous inclusions to be expelled from the reciprocating chamber of the valve armature. The gaseous inclusions are supplied to a damping medium flow which passes through a primary valve of the damping valve device. And discharging the gaseous inclusions from the damping valve device by using the damping medium flow. An advantage of this solution is that the vent channel according to DE 102014215563 a1 can be omitted.

It has now been shown, however, that the pump device no longer delivers reliably when a certain gas quantity is exceeded in the reciprocating chamber. As a result, a gas quantity remains in the reciprocating chamber and the valve armature experiences an undefined pressure which leads to a deviation of the damping force characteristic. Furthermore, due to the air bubbles in the reciprocating chamber, sufficient damping of the reciprocating movement of the valve armature is eliminated.

SUMMERY OF THE UTILITY MODEL

The object of the invention is to eliminate the problems known from the prior art with regard to gas inclusions in the damping valve device.

This object is achieved by: the valve housing has a discharge channel, the connection of which is arranged in the region of the valve housing filled with damping medium in the axial direction at least close to the sealing point for the coil, so that the connection is vertically higher than the deepest suction point of the pump device.

By combining the pump means with the discharge channel, the position of which the highest point in the reciprocating chamber is connected with the discharge channel can be selected significantly more advantageously than in the prior art. It is sufficient to fill the pump device with damping medium, so that gaseous inclusions can be discharged from the valve housing.

In general, each damping valve device has a pre-opening cross section which is permanently open for at least one flow direction, independently of the valve position of the movable valve body. The pre-opening cross section determines a damping force characteristic curve when the flow rate is gradually reduced, i.e. for example when the vibration damper begins to reciprocate. It is now possible for at least a part of the discharge channel to form a pre-opening cross section for the damping valve device. In this way, for example, the main stage valve can be designed as part of a damping valve arrangement without a pre-opening cross section.

For example, the following possibilities exist: the pre-opening cross section is formed by two surfaces facing each other inside the damping valve device. For example, a pole disk, which is usually produced relatively precisely, can be combined with the region of the valve housing in order to provide the pre-opening cross section.

In particular, it is possible for the pre-opening cross section to be formed by at least one throttle washer clamped by at least one housing section. It is not necessary to produce a highly precise surface for the pre-opening cross section on the housing section. The easy replacement of the throttle washer enables the use of standardized to detailed valve housings.

In a particularly simple embodiment, the outlet channel is formed by a radial bore in the valve housing. The advantage of this solution is that the wall of the valve housing is relatively thin and therefore the outlet channel has the properties of an orifice plate and thus practically no temperature dependency.

According to an advantageous embodiment, the valve housing has at least two axial housing sections, wherein a separating gap between the two housing sections forms part of the outlet channel. At least no longer is it necessary to produce the outlet channel with a complete cross section, but instead the separating seam can be used and thus also a bent joint shape can be achieved without additional effort.

It can even be provided that the separating slit is formed by a threaded portion and that the threaded portion forms part of the discharge channel. For this purpose, the thread portions have dimensional deviations, for example, by providing a thread clearance that is greater than is customary with standard thread portions, in order to thereby design the cross section of the joint to be larger.

Alternatively or additionally, the threaded portion can have an axial groove as part of the joint. In the alternative, a standard threaded portion can furthermore be present and thus standard tools can be used. Another advantage is that the axial grooves lead to significantly shorter joints.

In order to orient the functionally essential components of the damping valve device as perfectly as possible in the radial direction relative to one another, a centering bore is present between the two housing sections by the combination of the guide surfaces. One of the guide surfaces is separated from the fastening surface of the same housing section by a shoulder, wherein the discharge channel is formed outside the guide surface. This has the advantage that the seal for sealing the coil does not have to be pressed onto the outlet channel in order to reach its final assembly position. Thereby minimizing the intrinsic risk when the seal is installed.

Another alternative can be that the discharge channel cross section is formed by an angled connecting channel. The angled connecting channel has the following advantages, namely: the connecting channel can be manufactured from two sides without exit points, which have a poor deburring effect. Thus, for example, it is possible to combine an axial bore with a radial bore in order to position the outlet channel in the valve as advantageously as functionally possible.

In order to minimize machining costs, it can be provided that the angled connecting channel is connected to a connecting opening of the damping valve device.

Drawings

The invention is explained in detail below with the aid of the following description of the figures.

Fig. 1 shows a longitudinal section through a damping valve device;

FIGS. 2 and 3 illustrate an alternative embodiment of FIG. 1;

FIG. 4 shows a damper valve device with angled passages;

5-7 illustrate a damper valve device having a discharge passage between two surfaces facing each other;

8-10 show an alternative to FIG. 5;

FIG. 11 shows an alternative to FIG. 3;

FIG. 12 shows a damping valve device with a throttling gasket as part of the discharge passage;

fig. 13 shows an alternative to fig. 12.

Detailed Description

Fig. 1 shows a cut-out of a vibration damper 1 of any design. The problem to be solved is particularly apparent in the case of vibration dampers of double-tube design, but it is also possible in the case of vibration dampers of single-tube design, since, for example, during assembly, air is enclosed in the adjustable damping valve device 3.

The damper valve device 3 comprises a valve housing 5 which is fastened to an axially movable piston rod 7. The valve housing 5 comprises three sections. The first section forms a piston 9 with piston rings 11, which piston rings 11 divide a cylinder 13 filled with a hydraulic damping medium into working chambers 15, 17 close to the piston rod and remote from the piston rod. The piston 9 has conventional damping valves for both throughflow directions. The first damping channel group 19 forms a conventional first damping valve 23 with the valve disk assembly 21 on the upper side of the pot-shaped piston 9, and the second damping channel group 25 forms a conventional second damping valve 29 with the second valve disk assembly 27 on the lower side of the piston 9. These damping valves 23, 29 can optionally be used, since the invention functions independently thereof. If it is desired to dispense with the function of the damping valve 23, 29, the valve fittings 21, 27 are omitted.

The cup-shaped piston 9 is connected to the valve housing intermediate part 33 by a circumferential web 31. In this embodiment the connection is made by means of a threaded portion 35. Alternative embodiments, such as, for example, a crimped connection (Versicken) or welding, can of course also be used.

Between the pot-shaped piston 9 and the valve housing intermediate piece 33 there is a collection chamber 37, which is closed by a main stage valve 39. A valve disk 43, on which a main valve body 45 is supported in turn, is seated on the valve seat surface 41. The main stage valve body 45 has a stepped basic shape and is guided in an axially displaceable manner in a stepped opening 47 of the intermediate piece 33. For details of the main stage valve, reference is made to document DE 102012019321 a 1.

The valve disk 43 has a bypass flow opening 49 which opens into an annular chamber 51 of the main stage valve body 45. The annular chamber 51 is connected via a bypass channel 53 to a control chamber 55 located on the rear side with respect to the main stage valve body 45. The control chamber is defined by the intermediate piece 33, the back face of the main stage valve body 45 and the pole disk 57 of the valve armature 59.

A radial connecting opening 61 is arranged in the intermediate piece 33 between the working chamber 15 close to the piston rod and the main stage valve 39. A control opening 63, which opens into an annular chamber 65 formed by a shoulder of the main stage valve body 45 and a shoulder of the intermediate piece 33, is located in the intermediate piece axially above the connecting opening 61. Connected to this annular chamber 65 is a radial channel 67 in the main stage valve body 45, which in turn merges into a control channel 67 leading to a preceding stage valve 71.

The intermediate piece 33 is in turn connected to the top end piece 73 of the valve housing 5, the piston rod 7 also being fixed to the top end piece 73. In the tip end piece 73, an electromagnetic coil 75 is arranged on a coil holder 77. Two annular seals 79, 81 separate the electromagnetic coil 75 from the space of the valve housing 5 filled with damping medium. A grounding body 83 is inserted into the coil carrier 77 and defines a reciprocating chamber 85 for the valve armature 59. Two oppositely acting spring assemblies 57, 89 hold the valve armature in a predetermined home position.

The valve armature 59 acts on the backing valve 71, which has a backing valve body 91 and a backing valve seat surface 93 formed by the back surface of the main valve body 45. A tubular valve seat is fixed inside the valve armature 59 and transmits the actuating force from the valve armature 59 to the upstream valve body 91. The closing force acting on the main stage valve can be set in the control chamber 55 by the pilot stage valve.

The valve armature and the reciprocating chamber 85 constitute a pump. For this purpose, the valve armature 59 has at least one axial channel 99 in its annular guide body 97, which connects the reciprocating chamber 85 in the region of the base 101 to the upper displacement chamber 103. The displacement chamber 103 is in turn connected to an outflow channel 105, the outflow channel 105 being formed by the tubular valve seat 95. A check valve 107 opening in the direction of the outflow channel 105 promotes the pumping action. The axial channel 99 can also be equipped with a check valve opening in the direction of the reciprocating chamber. The shuttle chamber 85 is connected to the control chamber 55 via the guide 109 of the valve seat 95 so that no negative pressure is generated in the shuttle chamber 85. Fig. 1 shows the damper valve arrangement in the currentless state. When the electromagnetic coil 75 is energized, the guide body 97 moves in the direction of the pole disk 57, thereby enlarging the displacement chamber 103. The volume increase is compensated by a bypass flow of damping medium from the shuttle chamber 85. When the current supply level is reduced or when the damping medium flows to the upstream valve 71, the guide body 97 moves in the direction of the piston rod 7, i.e. in the opposite direction, thereby compressing the displacement chamber 103 and displacing the damping medium and/or air through the open valve 107 into the outflow channel 105. For the precise function of the pump, reference is made to the disclosure of document DE 102011003924B 4. In the guide 109, for example, axially extending grooves can be formed for the flow connection between the shuttle chamber 85 and the control chamber 55. A stepped liquid-tight guide surface is present between the guide body 97 and the grounding body 83.

Furthermore, the control chamber 55 is connected to at least one axial groove 111 in the intermediate piece 33 of the valve housing 5. The axial groove 111 extends at least partially radially outside the cross section of the pole disk 57 into a further annular chamber 113, which is formed by an end face 115 of the intermediate part 33. The pole disk 57 and the coil carrier 77 are fixed in the tip end part 73 above the intermediate part 33 by this end face 115. The annular chamber 113 represents a region or basin which is permanently filled with damping medium. The basin 113 is defined in the axial direction by the sealed coil support 77. Almost below the outer annular seal 81 of the coil carrier 77, the valve housing 5, in this case the head piece 73, has an annular connection 117 which, in combination with a discharge channel 119 in the wall of the valve housing 5, connects the pot 113 to the working chamber 15 close to the piston rod. The discharge channel 119 is designed as a simple bore. The possible liquid level of the basin 113 is vertically above the bottom 101 of the reciprocating chamber 85. The air separated in the vibration damper therefore accumulates inside the damping valve device in the displacement chamber 103 or, if it is further contaminated, in the annular connection 117. The end face of the guide body 97 facing the reciprocating chamber 85 can be considered as the deepest suction point of the pump. The damping medium level should be contacted at the suction point.

The outlet channel 119 is designed as a precisely designed pre-opening cross section and therefore absolutely does not represent a leakage point for the damping valve device. During the inward movement of the piston 9 in the direction away from the piston rod's working chamber 17, the damping medium flows through the valve 23 in the piston 9 into the collection chamber 37. Without the need for energizing the solenoid, the flow path continues via valve disk 43 of main stage valve 39 and via annular chamber 51 of main stage valve body 45 into control chamber 55 and further via axial groove and cup 113 to joint 117 and to discharge passage 119. The air enclosed in this area is displaced into the working chamber 15 close to the piston rod. If gas inclusions are also present in the reciprocating chamber 85, the damping medium is also raised here and these gas inclusions are displaced through at least one axial channel 99 in the valve armature in the direction of the displacement chamber 103. Depending on the adjustment of the non-return valve 107, air is discharged from the displacement chamber 103 or compressed. In any case, the shuttle chamber 85 is filled with damping medium, since the bottom 101 is lower than the joint 117 and is always loaded with air in the direction of the highest possible point. When the valve armature 59 is first energized, it executes a pumping movement, thereby reducing the displacement chamber 103 in the axial direction. Thereby displacing air from the displacement chamber 103 into the outflow channel 105 of the valve seat 95. The outflow channel 105 in the interior of the valve seat 95 is again connected to the bowl 113, for example via an opening 121 in the forevalve body 914. Thereafter, air is supplied to the connection 117 via the control chamber 55 and the basin 113 and further to the discharge channel 119.

The principle design of the damping valve device according to fig. 2 corresponds to the description in relation to fig. 1. Between the two housing sections of the valve housing 5, i.e. the intermediate piece 33 and the tip end piece 73, a centering bore is present through the combination of the guide surfaces 123, 125, wherein the guide surface 125 of the tip end piece 73 is separated from the fastening surface 127, i.e. the threaded portion, by a shoulder 129. The outlet channel 119 is formed outside the guide surface 125, i.e. in a hollow recess 131 between a thread groove (gewendeauslauf) and the shoulder 129. Thus, the annular seal 81 does not have to be wiped over the internal thread of the tip end piece 73 and over the radially inner opening of the discharge channel 119 during assembly.

In the embodiment according to fig. 3, which corresponds in the main configuration to fig. 1 as well, the outlet channel 119 is formed by the two housing sections, i.e. the separating gap 133 between the intermediate part 33 and the tip part 73, since the threaded part is used as the outlet channel 119. The threaded part can additionally have an axial groove 135 for enlarging the available cross section and/or for keeping the discharge channel as short as possible. For easy arrangement of the machining process, the axial groove is machined, for example milled or punched, into the external thread of the intermediate piece.

With the embodiment according to fig. 4, it is shown that the outlet channel 119 connecting the connection 117 to the working chamber 15 close to the piston rod can also be designed as an angled connecting channel in the intermediate piece 33. Here, the inflow opening 63 for the bypass flow from the working chamber 15 close to the piston rod in the direction of the upstream valve 71 is used.

A variant of the damping valve device 3 is explained in the longitudinal views of fig. 5 to 7, in which the pre-opening cross section is formed not directly by the outlet channel 119, but by two surfaces facing each other in the interior of the damping valve device 3. In this case, the bottom region 135 of the pot-shaped region 113 in the intermediate part 33 and of the lower side of the pole disk pointing in the direction of the control chamber 55 is used. In fig. 6, the intermediate part 33 is shown enlarged as a separate part in section, and the pre-opening section 139 is clearly visible as a groove in the plan view of the intermediate part according to fig. 7. With this configuration, the cross-sectional dimension of the outlet channel 119 no longer functions as a pre-opening cross-section and can therefore be designed more freely.

The set of fig. 8-10 conforms to the same structural principle as shown in fig. 5-7. The difference is that a groove for the pre-opening cross section 139 is machined into the underside of the pole disk 57, as is shown in fig. 10, which shows the pole disk in the installed position on an enlarged scale in fig. 10.

Fig. 11 shows a combination of the variants according to fig. 3 and fig. 8 to 10. A window 140 is formed in the pole disk 57, which window connects the reciprocating chamber 85 to the pot 113 and to a bypass of the guide 109. A larger connection cross section is thereby available. The discharge channel 119 then has the radial dimension of the pre-opening cross section.

In fig. 12, the pre-opening cross section 139 is formed by at least one throttle washer 141 clamped by the housing sections 33, 73, which can have a star-shaped contour, for example, in order to connect the control chamber 55 with the annular chamber 113. In particular, the throttle washer 141 is arranged between the intermediate piece 33 and the pole disk 57.

The variant according to fig. 13 is based on fig. 12. The pre-opening cross section is in turn embodied differently in the outlet channel 119, and instead of the throttle washer 141 a spacer washer 143 with radial perforations 145 is used. The perforations are adapted to connect the control chamber 55 to the basin 113 without throttling. In this case, gas inclusions can accumulate on the radial spring-back due to the perforations extending over the entire radial width of the spacer ring without the latter. The spacer washer 143 can have a C-shaped design, for example.

List of reference numerals:

1 vibration damper

3 damping valve device

5 valve housing

7 piston rod

9 piston

11 piston ring

13 jar

15 working chamber near piston rod

17 working chamber remote from the piston rod

19 first damping channel group

21 valve disc equipment

23 conventional first damping valve

25 second damping channel group

27 second valve disk assembly

29 conventional second damping valve

31 connecting piece

33 valve housing intermediate piece

35 screw part

37 collecting chamber

39 primary valve

41 seat surface

43 valve disc

45 main stage valve body

47 step opening

49 side-stream opening

51 annular Chamber

53 side-stream opening

55 control chamber

57 pole plate

59 valve armature

61 connecting opening

63 control opening

65 annular Chamber

67 radial channel

69 control channel

71 backing valve

73 tip piece

75 electromagnetic coil

77 coil support

79 annular seal

81 annular seal

83 grounding body

85 reciprocating chamber

87 spring assembly

89 spring assembly

91 preceding stage valve body

93 front stage valve seat surface

95 valve seat

97 guide body

98 end face

99 axial channel

101 bottom

103 displacement chamber

105 outflow channel

107 check valve

109 guide member

111 axial groove

113 annular chamber

115 end face

117 joint

119 discharge channel

121 opening

123 guide surface

125 guide surface

127 fixed surface

129 shoulder

131 hollow recess

133 dividing slit

135 axial groove

137 bottom region

139 pre-opening cross section

141 throttling gasket

143 space washer

145 perforation

Claims (11)

1. A damping valve device (3) comprising a valve housing (5) in which a valve armature (59) driven by means of a solenoid coil (73) executes an axial reciprocating movement and by means of this reciprocating movement a pump device (103, 105, 85, 107) is actuated in order to expel gas inclusions from the valve housing (5), characterized in that the valve housing (5) has an outlet channel (119), the connection (117) of which is arranged in the region (113) of the valve housing (5) filled with a damping medium in the axial direction at least close to a sealing point (81) for the solenoid coil (73), so that the connection (117) is vertically higher than the deepest suction point (85) of the pump device (103, 105, 85, 107).

2. The damper valve device according to claim 1, characterized in that at least a part of the discharge channel (119) forms a pre-opening cross section for the damper valve device (3).

3. Damping valve device according to claim 1, characterized in that the pre-opening cross section (139) is formed by two surfaces (57, 137) facing each other inside the damping valve device (3).

4. The damper valve device as claimed in claim 1, characterized in that the pre-opening cross section (139) is formed by at least one throttle washer (141) clamped by means of at least one housing section (33).

5. The damper valve device according to claim 1, characterized in that the connection (117) is connected to a discharge channel (119) formed by a radial bore in the valve housing (5).

6. The damper valve device according to claim 5, characterized in that the valve housing (5) has at least two axial housing sections (73, 33), wherein a separating gap (133) between the two housing sections (33, 73) forms part of the outlet channel (119).

7. The damper valve assembly according to claim 6, wherein the dividing slit is formed by a threaded portion.

8. The damper valve assembly according to claim 7, wherein the threaded portion has an axial groove (135) as part of the discharge passage (119).

9. The damper valve device according to claim 6, characterized in that between the two housing sections (33, 73) there is a centering bore which is produced by a combination of guide surfaces (123, 125), wherein one of the guide surfaces (125) is separated from a fastening surface (127) of the same housing section by a shoulder (129), wherein the discharge channel (119) is formed outside the guide surface (125).

10. The damper valve device according to claim 1, wherein the discharge passage (119) is formed by an angled connecting passage.

11. The damper valve device according to claim 10, characterized in that the angled connecting channel is connected to a connecting opening (61) of the damper valve device (3).

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