Choke point with valve body of varying diameter

Abstract

The present invention relates to a throttling point for a vibration damper, the vibration damper comprising a damper valve carrier having a circumferential annular groove, an annular valve body having a variable diameter arranged in the circumferential annular groove, the annular valve body forming the throttling point with a guide surface for allowing the flow of damping medium, the throttling cross section of the throttling point decreasing as the flow velocity of the damping medium within the throttling point increases, the circumferential annular groove forming a pressure chamber filled with the damping medium such that a radially outward actuating force acts on the valve body, wherein the pressure chamber is part of a hydraulic system having a connector connected to at least one working space of the vibration damper, and a hydraulic connection from the connector to the pressure chamber can be configured.

Description

Technical Field

[0001] This invention relates to a damper valve device. Background Technology

[0002] DE 10 2016 210 790A1 describes a damper valve device having an annular valve body within an annular groove of a valve carrier. Utilizing a flow guide surface, the valve body forms a throttling point that reduces the flow cross-section as the flow velocity of the damping medium increases within the throttling point.

[0003] The annular groove forms a pressure chamber for the valve body, which is filled with a damping medium and generates a radially outward widening actuating force on the valve body. Summary of the Invention

[0004] The object of the present invention is to easily adapt the damper valve device known in the prior art to a variety of applications.

[0005] This objective is achieved by the fact that at least one component of the hydraulic system can be configured.

[0006] The damper valve device can be adapted to various application requirements in a targeted manner through its installation capabilities, without modifying component dimensions.

[0007] One possibility is that the hydraulic system has a connector connected to at least one working space of the vibration damper, and the hydraulic connection from this connector to the pressure chamber can be configured. The operating speed, not only at the point of use but also at the throttling point, can be changed via this configuration.

[0008] In a further advantageous improvement, the hydraulic system can have a connecting channel between the two working spaces of the vibration damper, which is connected to the pressure chamber, and the cross-section of this connecting channel can be configured. Here, the inflow or outflow side of the connecting channel can selectively undergo a larger or smaller throttling effect.

[0009] Furthermore, there is a possibility of hydraulically connecting the bypass channel and the connecting channel in parallel. Both channels are connected to the pressure chamber, and the effective cross-section of the bypass channel can be configured. The advantage is that the bypass channel can be completely closed, and the connecting channel provides a minimal cross-section. Consequently, adjustments made when actively adjusting the bypass channel are simplified.

[0010] Alternatively, the connection channel can have a connector channel that connects to the pressure chamber, the cross-section of which can be configured. This variant offers the advantage that the pressure chamber can withstand radially incident flow and may have only a single connector opening. This particular feature provides the possibility that, through the blocked connector, the valve body's reset movement toward the starting diameter can be actuated independently of the flow velocity within the throttling point.

[0011] According to a preferred embodiment, the flow channel within the hollow piston rod can be connected to a hydraulic system. This flow channel is easily accessible from the outside and facilitates the use of an actuator, allowing the effective cross-section of the flow channel to be adjusted via the actuator.

[0012] Although the throttling point is adjustable, it can also be assigned to another passive damper valve in series hydraulically.

[0013] In one design variant, a bypass channel with an adjustable cross-section is connected in series, which hydraulically bridges the throttling point. Here, the volumetric flow rate through the throttling point and the volumetric flow rate entering the pressure chamber are set. The advantage of this solution is that the point of use of the throttling point changes uniformly.

[0014] Tests show that a series connection with a bypass channel that hydraulically bridges the throttling point and another damper valve is very suitable. Attached Figure Description

[0015] The present invention will be described in more detail below based on the accompanying drawings.

[0016] In the attached diagram:

[0017] Figure 1 The vibration damper is shown in cross-sectional view.

[0018] Figure 2 It shows Figure 1 Alternative illustrations,

[0019] Figure 3 and Figure 4 It shows Figure 2 Alternative variants,

[0020] Figure 5 The damping force characteristic curve is shown.

[0021] Figures 6 to 11 It shows Figure 3 and Figure 4 Alternative variants,

[0022] Figure 12 It shows Figure 13 Alternative illustrations, and

[0023] Figure 13 It shows according to Figure 12 Structural embodiments. Detailed Implementation

[0024] Figure 1 A damper valve assembly 1 is shown for a vibration damper 3 with any desired overall design (only details of the damper valve assembly are shown). This illustration serves as the basis for all further alternative illustrations and structural modifications. The damper valve assembly 1 includes a first damper valve 5 with a damper valve body configured as a piston 7 and fastened to a piston rod 9.

[0025] The damper valve body 7 divides the cylinder body 11 of the vibration damper into a piston rod-side working space 13 and a working space 15 away from the piston rod. Both working spaces 13 and 15 are filled with damping medium. A passageway in one flow direction is provided for each condition. 17 and 19 are configured on different pitch circles in the damper valve body 7. The configuration of the passageway is considered by way of example only. The outlet side of the passageways 17 and 19 is at least partially covered by at least one valve plate 21 and 23.

[0026] The vibration damper may optionally have a tension stop 25 that contacts a cylinder-side stop surface, such as a piston rod guide 27, according to the defined extension movement of the piston rod 9.

[0027] The tension stop 25 includes a carrier disc 29, which is directly fixed to the piston rod 9 by a forced locking connection. For example, an annular elastomer element 31 is placed on the upper side of the carrier disc 29, and is held in place by a small radial prestress even when the piston rod 9 vibrates. Starting from the stop point on the stop surface, the elastomer element 31 acts as an additional support spring.

[0028] For example, the carrier disc 29 forms the damper valve carrier and, in this function, has a circumferential annular groove 33 in which a variable-diameter valve body 35 is guided. The damper valve carrier can also be spatially configured and arranged in a completely different spatial shape. The variability of the diameter can be achieved by using a flexible material or by a slotted design. A multi-piece design for the valve body 35 is also conceivable. The annular valve body 35 forms a throttling point 37 with the inner wall of the cylinder 11, and the inner wall 39 represents a flow guiding surface.

[0029] On the outer side, the valve body 35 carries a reset ring 41 (e.g., a reset ring in a fastening ring configuration). The reset ring 41 ensures a radial reset force on the valve body in the direction of the annular groove 33.

[0030] The annular groove 33, together with the valve body 35, defines the pressure chamber 43, which is maintained even with the annular valve body 35 having the smallest inner diameter. The pressure chamber 43 is part of the hydraulic system 45, which determines the pressure level within the pressure chamber directly or indirectly via wiring connections within the vibration damper, particularly within the damper valve assembly 1.

[0031] Figure 2 It shows Figure 1 An alternative illustration is provided. Starting from the working space 15, the damping medium flows through the passage 17, and the valve plate 21 is lifted from the piston 7. The damping medium flows into the annular space 47 between the piston 7 and the carrier disc 29. From the annular space 47, the flow path continues through the hydraulic system 45 into the working space 13, where the damping medium is divided into a throttling flow and a control flow within the control line 49 of the hydraulic system 45. The throttling flow determines the damping force of the damper valve assembly 1, and the control flow is used to generate pressure within the pressure chamber 45. The connection between the control line 49 and the throttling line is formed by the annular space 47 between the piston 7 and the carrier disc 29.

[0032] The connecting channel 53, as part of the control circuit 49, connects the piston rod-side working space 13 to the annular space 47. The pressure chamber 43, extending to the throttle point 37 (shown as a switchable throttle valve), functionally lies between two throttles 55, 57 within the connecting channel 53. The throttles can be formed, for example, by inflow and outflow openings into the connecting channel 53. The valve body 35 radially widens or contracts back to its initial position due to the radial reset force of the limiting ring 41, depending on the pressure level at the throttle point 37 and within the pressure chamber 43. Although the flow velocity within the throttle point 37 increases at high stroke speeds of the piston rod 9 relative to the cylinder 11, the pressure within the throttle point 37 decreases. Conversely, at relatively high stroke speeds, the pressure within the pressure chamber 43 at the throttle point 37 increases. These two effects cause the annular valve body 35 to radially widen in the direction of the inner wall 39 of the cylinder 11. As a result, the throttling cross section at throttling point 37 decreases, but the damping force increases.

[0033] Figure 3 and Figure 4A variant of the invention is shown in which the hydraulic system 45 has a connector (generated via a throttle 57) connected to the working space 13 of the vibration damper 3, and the hydraulic connection from the throttle 57 to the pressure chamber 43 can be arbitrarily configured. For this purpose, the hydraulic system 45 has a connecting channel 53 between the two working spaces 13, 15 of the vibration damper 3, which is connected to the pressure chamber 43, and the cross-section of the connecting channel 53 can be configured via the throttle 57. Essentially, the inflow or outflow of the damping medium into the pressure chamber can be configured.

[0034] According to Figure 3 In an exemplary embodiment of the alternative illustration, according to Figure 4 The carrier disc has a through-hole 59 that connects the pressure space 43 to a blind passage 61 within the piston rod 9. The through-hole 59 and the blind passage 61 form part of a connecting channel 53 in which an adjustable throttle 57 is also arranged. The blind passage is also connected by a radial passage 63 leading to the piston rod-side working space 13. An axially adjustable throttle rod 65 is provided within the blind passage, which can be actuated manually or by external power. In this illustration, the throttle is formed by a seat valve. A spool valve along with the through-hole 59 or radial passage 63 is also conceivable.

[0035] Figure 5 The effect of the throttling point on the damping force characteristic curve of the damper valve device 1 is shown. Accordingly, a decreasing basic characteristic curve (shown as a solid line) exists for the damper valve 5, which allows the damping force to increase at a defined flow velocity S when using the throttling point 37 in conjunction with the throttle valve 57 at its maximum opening (shown as a dashed line). By using the throttle valve 57 at its minimum opening, the point of use of the throttling point 37 shifts in the direction of lower flow velocity, and the damping force achievable at the throttling point also increases due to the greater degree of closure of the throttling point.

[0036] according to Figure 6 and Figure 7 The embodiments are based on Figures 3 to 5 In addition to the connecting channel 53 and its throttles 55 and 57A, the damper valve device or hydraulic system 45 has a bypass channel 67, which is hydraulically connected in parallel with the connecting channel 53 between the pressure chamber 43 and the working space 13. The effective cross-section of the throttle 57B in the bypass channel 67 can be configured, such as in combination with... Figure 4As described. For this purpose, pressure chamber 43 has another connector or through-hole 59 that leads to a bypass passage 65 within the hollow piston rod 9. Under this principle, even in the event of a malfunction or incorrect setting of the throttle 57B within the bypass passage 67, a still comfortable damping force setting can be achieved without requiring additional emergency operating measures at the actuator to set the effective cross-section of the throttle 57B.

[0037] Figure 8 and Figure 9 As shown, in the case of damper valve device 3, connection channel 53 can also be connected to pressure chamber 43 via connector channel 69, and the cross-section of connector channel 69 is set by throttle 57C. Figure 9 Connector channel 69 extends radially from pressure chamber 43 into connection channel 53. Connection channel 53 functionally serves as a throttle 55, 57 via its flow resistance. Connector channel 69 abuts guide 71 for valve bolt 73, which extends from pressure chamber into hollow piston rod 9. Valve bolt is sealed in the area of ​​guide 71, preventing damping medium from entering the hollow piston rod.

[0038] Within the connector channel 69, the valve bolt 73 has a circumferential groove 75, which is defined on one side by the head 77 of the valve bolt 73. In the area where the groove 75 of the valve bolt intersects with the connection channel 53, the damping medium can flow around the valve bolt 73.

[0039] The head 77 of the valve bolt 73 has a larger diameter than the connector channel 69, allowing the valve bolt 73 to move only to a limited extent in the direction of the hollow piston rod 9. A guide channel 79 for the actuator rod 81 within the piston rod 9 intersects with the guide 71 of the valve bolt 73. In the overlapping area of ​​the valve bolt 73 and the guide channel 79, the valve bolt 73 has a through-hole 83 for the actuator rod 81, which forms a sliding connection with a cone 85 on the actuator rod 81. Axial movement of the actuator rod 81 causes radial movement of the valve bolt 73. A return spring 87 between the head 77 of the valve bolt 73 and the wall of the pressure chamber 43 ensures the valve bolt 73 returns to its maximum pass position.

[0040] If the actuator rod 81 is pushed deeper into the piston rod 9, the valve bolt 73 moves in the direction of the connecting passage 53 or in the direction of the wall of the pressure chamber 43. As a result, the supply of damping medium to the pressure chamber 43 is reduced or the pressure drop between the working space and the pressure chamber is increased. Consequently, the displacement of the throttling point 37 on the valve body 35 begins later than if the connector passage 69 were throttled to a less noticeable degree.

[0041] Figure 10 and Figure 11 Another embodiment of the damper valve device 1 is shown, in which a flow passage 89 within the hollow piston rod 9 is connected to the hydraulic system 45. This flow passage 89 forms a bypass to the connecting passage 53, but is hydraulically connected to the connecting passage via the annular space 47, as shown. Figure 11 As shown, the proportion of damping medium flowing through connecting channel 53 and thus into pressure chamber 43 is determined by the effective cross-section of throttle 91 or flow channel 89 (which can be adjusted via an actuator). As a result, the throttling point 37 can be set via throttle rod 65 based on this damping medium proportion. In this way, the flow paths through throttles 55 and 57 can be hydraulically bridged as a whole. Figure 10 In this case, the connection principle is implemented, and it is not necessary to configure a flow connection to the flow channel 89 on the valve carrier 29. The connection between the flow channel 89 and the connection channel 53 exists via radial channels 63, which lead to the connected working spaces 13, 47 on both sides of the carrier disk 29.

[0042] If already combined Figure 1 The described throttling point is hydraulically connected in series with another damper valve. However, the effective cross-sectional size of the bypass passage has no effect on the damping force characteristic curve of the second damper valve.

[0043] according to Figure 12 Alternative illustrations and their basis Figure 10 The embodiments are very similar. Offset, the series circuit consisting of throttle point 37 and another damper valve 5 has a bypass channel or flow channel 89 for connecting channel 53, which hydraulically bridges throttle point 37 and the other damper valve 5. In this way, when the flow channel or throttle 91 is open, the damping force of the entire damper valve assembly 1 tends to shift towards a softer characteristic. This damping characteristic is particularly advantageous for motorcycles. Figure 13 It shows according to Figure 12 An alternative illustration of a possible structural embodiment of a throttling point and damper valve.

[0044] List of reference numerals

[0045] 1. Damper valve assembly

[0046] 3 Vibration dampers

[0047] 5. Damper valve

[0048] 7 Pistons

[0049] 9 Piston rod

[0050] 11 Cylinder Block

[0051] 13 Piston rod side working space

[0052] 15. Working space away from the piston rod

[0053] 17 Through the passage

[0054] 19 Through the passage

[0055] 21 Valve Plate

[0056] 23 Valve Plate

[0057] 25 Tension stop

[0058] 27 Piston rod guide

[0059] 29 Carrier disk

[0060] 31 Elastomer Components

[0061] 33 Annular groove

[0062] 35 Valve body

[0063] 37 Throttling Points

[0064] 39 Inner wall

[0065] 41 Reset Ring

[0066] 43 Pressure chamber

[0067] 45 Hydraulic System

[0068] 47. Circular Space

[0069] 49 Control circuit

[0070] 51 Throttling circuit

[0071] 53 Connection Channel

[0072] 55 Throttling device

[0073] 57 Throttling device

[0074] 57B Throttling Device

[0075] 57C throttle

[0076] 59 Through Hole

[0077] 61 Blind Hole Channel

[0078] 63 Radial Channel

[0079] 65 Throttle bar

[0080] 67 Bypass

[0081] 69 Connector Channel

[0082] 71. Guide

[0083] 73 Valve Bolt

[0084] 75 circumferential groove

[0085] 77 Head

[0086] 79 Guiding Channel

[0087] 81 Actuator rod

[0088] 83 Through Hole

[0089] 85 cone

[0090] 87. Return spring

[0091] 89 Flow Channel

[0092] 91 Throttling device

Claims

1. A throttling point (37) for a vibration damper (3), the vibration damper comprising a damper valve carrier (29) having a circumferential annular groove (33), an annular valve body (35) having a variable diameter arranged in the circumferential annular groove, the annular valve body (35) forming the throttling point (37) with a flow guide surface (39) for allowing the damping medium to flow, the throttling cross section of the throttling point decreasing as the flow velocity of the damping medium within the throttling point (37) increases, the circumferential annular groove (33) forming a pressure chamber (43) filled with the damping medium, such that a radially outwardly pointing actuating force acts on the valve body, the pressure chamber (43) being a component of a hydraulic system (45) of a damper valve device (1) of the vibration damper (3), wherein, The hydraulic system (45) also includes: A first channel (55, 57, 57B, 67) connecting the pressure chamber (43) to at least one working space (13, 15, 47) of the vibration damper (3); and The second channel (53, 89) connects the two working spaces (13, 15, 47) of the vibration damper (3). The effective cross section of at least one of the first channel (55, 57, 57B, 67) and the second channel (53, 89) can be adjusted via an actuator (65, 81).

2. The throttling point as described in claim 1, wherein, The first channel (55, 57, 57B, 67) includes connectors (55, 57, 57B), the effective cross-section of which can be adjusted via the actuator (65).

3. The throttling point as described in claim 1, wherein, The second channel (53, 89) includes a connection channel (53) connected to the pressure chamber (43), and the effective cross-section of the connection channel (53) can be adjusted via the actuator (65).

4. The throttling point as described in claim 1, wherein, The first channel (55, 57, 57B, 67) includes a bypass channel (67), the second channel (53, 89) includes a connecting channel (53) connected to the pressure chamber (43), and the effective cross-section of the bypass channel (67) can be adjusted via the actuator (81).

5. The throttling point as described in claim 3 or 4, wherein, The connection channel (53) has a connector channel (69) connected to the pressure chamber (43), the effective cross-section of which can be adjusted via the actuator (81).

6. The throttling point as described in claim 1, wherein, The second channel (53, 89) includes a flow channel (89) arranged in the hollow piston rod (9) of the damper valve device (1), and the effective cross section of the flow channel (89) can be adjusted via the actuator (81).

7. The throttling point as described in claim 6, wherein, The throttling point (37) is assigned to be hydraulically connected in series with another damper valve (5).

8. The throttling point as described in claim 7, wherein, The flow channel (89) is hydraulically bridged to the throttling point (37).

9. The throttling point as described in claim 7, wherein, The flow channel (89) hydraulically bridges the throttling point (37) and the other damper valve (5).

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