Spring for a check valve, check valve having a spring of this kind, controllable vibration damper having such a check valve, and motor vehicle having a controllable vibration damper of this kind

Abstract

A spring for a check valve which can be used in particular in controllable vibration dampers, said spring comprising a flat main body with a first surface, a second surface and a centre point, and two or more spring arms, which cooperate resiliently with the main body and in the unloaded state protrude from the first surface or the second surface, the spring arms forming a free end and having a longitudinal axis that runs through the free end and tangentially to a circle about the centre point of the main body. The invention further relates to a check valve having a spring of this kind. In addition, the invention relates to a controllable vibration damper which comprises such a check valve, and to a motor vehicle having a controllable vibration damper of this kind.

Claims

1. A spring for a check valve, comprising: a laminar base body with a first surface, a second surface and a center point, two or more spring arms cooperating resiliently with the base body and which, in a relieved state, lift from the first surface or the second surface, wherein the spring arms form a free end and have a longitudinal axis that extends through the free end and tangentially to a circle about the center point of the base body, wherein the spring arms form in each instance a bending line with the base body, and the base body comprises grooves extending parallel to one another, wherein the bending lines do not extend parallel to the grooves.

2. The spring as in claim 1, wherein the spring arms are formed by the base body.

3. The spring as in claim 1, wherein the spring arms form in each instance a bending line with the base body, and wherein the bending line extends perpendicularly to the longitudinal axis.

4. The spring as in claim 1, wherein the spring arms comprise in each instance a contact region encompassing the free end, which is bent at an angle with respect to the remaining spring arm.

5. The spring as in claim 1, wherein the base body comprises abutment sections onto which abut adjacently disposed structural parts.

6. The spring as in claim 1, wherein the base body comprises a reception cutout.

7. The spring as in claim 6, wherein the reception cutout is at least in sections delimited by the spring arms.

8. The spring as in claim 1, wherein the base body comprises at least one anti-twist protection section to fix the spring in place so as to be braced against rotation relative to an adjacently disposed structural part.

9. A check valve, comprising: a check valve with a valve seat, a sealing washer, with which the check valve is closable or is closed, when the sealing washer is in contact on the valve seat, and a spring, comprising: a laminar base body with a first surface, a second surface and a center point, two or more spring arms cooperating resiliently with the base body and which, in a relieved state, lift from the first surface or the second surface, wherein the spring arms form a free end and have a longitudinal axis that extends through the free end and tangentially to a circle about the center point of the base body, wherein a spring of the spring arms presses the sealing washer into contact onto the valve seat, wherein the base body of the spring comprises a reception cutout, and wherein the check valve comprises a receiving body onto which the spring is axially movable slidable, wherein the receiving body penetrates the reception cutout, and an abutment body with which the movability of the spring with respect to the receiving body can be delimited.

10. The check valve as in claim 9, wherein the sealing washer comprises a reception opening and is slidably, axially movable onto the receiving body, wherein the receiving body penetrates the reception opening, and wherein movability of the sealing washer relative to the receiving body is delimitable with the abutment body.

11. The check valve as in claim 10, wherein the receiving body comprises at least one set-off against which the sealing washer abuts.

12. The check valve as in claim 9, further comprising: a base body that defines a longitudinal valve axis and at least one first channel extending at least substantially along the longitudinal axis and at least one second channel substantially extending perpendicularly to the longitudinal valve axis, wherein the second channel is opened on one side along the longitudinal valve axis, and a closure body closing off the at least one second channel along the longitudinal valve axis in an assembled state of the check valve, wherein the receiving body is disposed between the base body and the closure body.

13. The check valve as in claim 12, wherein between the receiving body and the abutment body at least one tolerance compensation body is fixedly disposed which, in the assembled state of the check valve, is in contact on the base body or on the closure body.

14. The check valve as in claim 12, further comprising: a working cylinder, a piston, movable back and forth in the working cylinder, that divides the working cylinder into a first working volume and a second working volume, wherein the first working volume and the second working volume are each connected across one pressurizing medium line with the check valve, wherein the check valve controls a vibration damper.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) Exemplary embodiments of the application will be discussed in detail with reference to the attached drawing. Therein depict:

(2) FIG. 1A a side view of a first embodiment of a spring in a not yet finished state,

(3) FIG. 1B a plan view onto the spring depicted in FIG. 1A,

(4) FIG. 1C a side view of the spring shown in FIGS. 1A and 1B in the installation state and in minimally loaded state,

(5) FIG. 1D a side view of the spring shown in FIGS. 1A and 1B in maximally loaded state,

(6) FIGS. 2A to 2D different views analogous to FIGS. 1A to 1D of a second embodiment of a spring,

(7) FIG. 3A a sectional representation of an embodiment of a check valve,

(8) FIG. 3B an enlarged representation of region X marked in FIG. 3A, and

(9) FIG. 4 a basic representation of a motor vehicle with a vibration damper comprising a check valve.

DETAILED DESCRIPTION

(10) In FIG. 1A is shown a first embodiment example of a spring 10 in conjunction with a side view and in FIG. 1B in conjunction with a plan view, wherein the spring is in a not yet finished assembly state. The spring 10 comprises a laminar, in this case disk-shaped, base body 12 with a center point M, which forms a first surface 16 and a second surface 18. In addition, the base body 12 forms three spring arms 20 which have an elongated form and each has a free end 22. The spring arms 20 are defined by appropriate cutouts in the base body 12. Each of the spring arms 20 defines a longitudinal axis L that extends through the free end 22. The spring arms 20 are developed and oriented such that their longitudinal axes L extend tangentially to a circle C about the center point M of the base body 12. The spring arms 20 are, in addition, distributed uniformly over the circumference of the circle C such that the longitudinal axes L form an angle of 120? with one another. Deviations, for example angles greater than 120?, are feasible within certain limits. Deviations from the strictly tangential orientation of the longitudinal axes [L] are also feasible within certain limits.

(11) In FIGS. 1C and 1D can be seen the spring axis X which extends through the center point M and is defined by base body 12. As discernable in FIGS. 1C and 1D, in the completed state of the spring 10 the spring arms 20 in this case lift from the first surface 16. For this purpose the spring arms 20 are bent about a bending line B at a certain bending angle which [bending line] is especially clearly visible in FIG. 1B. The bending line B extends perpendicularly to the longitudinal axis L of the particular spring arm 20.

(12) Furthermore is clearly evident in FIG. 1C that the spring arms 20 comprise a contact region 24 encompassing the free end 22, which contact region 24 is bent at an angle with respect to the remaining spring arm 20. The contact region 24 is also fabricated by bending. The contact region 24 is developed such that in the relieved state it extends substantially parallel to the first surface 16 or is slightly inclined toward the first surface 16.

(13) It is furthermore discernible in FIG. 1B that the base body 12, comprised for example of spring steel, comprises production-inherent grooves R on the first surface [16] and the second surface 18, of which in FIG. 1B only some are depicted by example. The grooves R extend parallel to one another. The bending lines B, about which the spring arms 20 are bent during the production of the spring 10, do not extend parallel to the grooves R, but rather form an angle with grooves R. The bending lines B of the two left, referred to FIG. 1B, spring arms 20 form an angle of approximately 60? and the bending line B of the right spring arm [20] forms an angle of approximately 90? with the grooves R.

(14) It is furthermore discernible in FIG. 1B that the base body 12 comprises overall three abutment sections 26, which are produced by deflecting about a bending edge at a bending angle of approximately 90?, which is evident in FIG. 1C. On the abutment sections 26 abut adjacently disposed structural parts such that the maximal spring travel by which the spring arms 20 can be bent, is delimited. Overloading of the spring arms 20 is hereby prevented.

(15) The base body 12 is moreover provided with a reception cutout 28 substantially having a circular cross section. At least in the assembled state, shown in FIGS. 1A and 1B, the reception cutout 28 is radially, at least in the assembled state, shown in FIGS. 1A and 1B, outwardly delimited by spring arms 20 and by three circular arc-shaped sections 30 that are formed by radially inwardly directed projections of base body 12. The spring 10 lies only with these circular arc-shaped sections 30 in contact on, for example, a mandril as will be explained in greater detail further down. Contact of the mandril on the spring arms 20 is therefore prevented and the transmission of frictional forces from the mandril onto the spring arms 20 and dragging is prevented.

(16) The base body 12, furthermore, forms overall three anti-twist protection sections 32 which, in the embodiment example shown in FIGS. 1A to 1D, comprise each a straight edge 34 which is disposed radially outward on the base body 12. With these edges 34 the spring 10 can be in contact on an appropriately formed adjacently disposed structural part. The anti-twist protection sections 32 comprise, furthermore, in each instance a bore 36 which can also be slid onto correspondingly disposed pins of an adjacently disposed structural part. Utilizing both measures can prevent the uncontrolled twisting of the spring 10 during operation.

(17) In FIGS. 2A to 2D is depicted a second embodiment example of the spring 10 in the same manner as the first embodiment example. The maximal diameter of the base body 12 of spring 10 according to the second embodiment example is less than that according to the first embodiment example. Accordingly, the length of the spring arms 20 is less than in the first embodiment example.

(18) The anti-twist protection section 32, furthermore, is developed differently and comprises three radially outwardly directing expansions 38 which can engage into corresponding recesses of an adjacently disposed structural part. The base body 12 according to the second embodiment example does not comprise abutment sections 26.

(19) The structure of the spring 10 according to the second embodiment example for the remainder is substantially equal to that of the first embodiment example. The grooves R in FIG. 2B are not drawn in FIG. 2B for purposes of presentation.

(20) In FIG. 3A is shown an embodiment example of a check valve 40 in the assembled state in conjunction with a sectional representation. In FIG. 3B is shown an enlargement of the detail marked X in FIG. 3A. The check valve 40 comprises a base body 42 and a closure body 44. The base body 42 defines a longitudinal valve axis A as well as a first channel 46 and a number of second channels 48. The first channel 46 extends along the longitudinal valve axis A, while the second channels 48 extend perpendicularly thereto. The second channels 48 are partially opened along the longitudinal valve axis A, referred to the presentation of FIG. 3A toward the right. The second channels 48 are consequently only completely closed after the closure body 44 has been set into the base body 42. It is therefore necessary for the closure body 44 to be set into the base body 42 under sealing, which can take place, for example, using not shown O-rings or by means of a press fit.

(21) Between the base body 42 and the closure body 44 a receiving body 50 is disposed. The receiving body 50 fulfills the function of a mandril such that the spring 10 can be slid onto the receiving body 50, wherein the receiving body 50 penetrates the reception cutout 28 of spring 10 with a reception section 52. The position of the spring 10 is consequently radially sufficiently fixed in place. The receiving body 50 furthermore forms a set-off 54 onto which the sealing washer 56 can abut, whereby the maximal spring travel of the spring arms 20 is delimited and consequently too strong a deflection of the spring arms 20 is prevented.

(22) As is especially evident in FIG. 3B, onto the receiving body 50 a sealing washer 56 is slid additionally, for which purpose the sealing washer 56 comprises a reception opening 60. To prevent the sealing washer 56 and the spring 10 to detach axially from the receiving body 50, an abutment body 58 is connected with the receiving body 50, for example by joining them under pressure or by a threaded connection. The abutment body 58 projects radially outwardly beyond the reception section 52. The spring arms 20 are in contact on the sealing washer 56 and press it against the abutment body 58 which delimits the axial movability of the sealing washer 56.

(23) In FIG. 3B is discernible that the diameter of the reception opening 60 is slightly larger than the diameter of the reception section 52. It is hereby prevented that an uneven loading of the sealing washer 56, which entails a rotation of the sealing washer 56 about a rotational axis extending perpendicularly to the longitudinal valve axis A, engenders the jamming of the sealing washer 56 on the reception section 52.

(24) As is also evident in FIG. 3B, a disk-shaped tolerance compensation body 62 is provided which is secured under clamping between the receiving body 50 and the abutment body 56 on these two bodies. Radially outward the tolerance compensation body 62 is in contact on the base body 42. The sealing washer 56 is pressed by the spring 10 against the tolerance compensation body 62. The thickness of the tolerance compensation body 62 and of the sealing washer 56 can be varied in order to compensate tolerances, for example, of the spring 10 and to set its reset force.

(25) The abutment body 58 and the base body 42 form a valve seat 64 against which the sealing washer 56 is pressed when the spring 10 is not under load. Hereby the check valve 40 is also closed. The check valve 40 comprises therefore an annular gap that can be closed by the sealing washer 56. It should be noted that the tolerance compensation body 62 in [not shown] plan view substantially comprises two concentric annuli that are connected with a number of radially extending webs. The section plane of FIGS. 3A and 3B extends through some of these webs such that the impression is generated of the check valve 40 being closed by the tolerance compensation body 62. However, this is only the case in the region of the webs. Since in this embodiment example the tolerance compensation body 62 rests on the receiving body 50 as well as also on the base body 42, and the sealing washer 56 is pressed against the tolerance compensation body 62, the valve seat 64 is also formed by the tolerance compensation body 62. Use of the tolerance compensation body 62, however, is not mandatory.

(26) The check valve 40 is exclusively fluid controlled. When a fluid flows along the direction marked by the arrows P of FIG. 3A through the first channel 46, the fluid exerts a fluid force onto the sealing washer 56 which, as a consequence, is moved along the longitudinal valve axis A away from the tolerance compensation body 62. Due to this movement, the spring arms 20 are bent whereby these apply a reset force onto the sealing washer 56 which counteracts the fluid force. The sealing washer 56 comes to a standstill where the fluid force and the reset force are of equal magnitude. Due to the movement of the sealing washer 56 away from the tolerance compensation body 62, the check valve 40 is opened and the fluid can leave the check valve 40 across the second channels 48. If the flow velocity decreases, if the flow stops or the direction of flow reverses, the fluid force decreases or the fluid force acts in the opposite direction onto the sealing washer 56. The sealing washer 56 is consequently again pressed against the tolerance compensation body 62 and closes the check valve 40.

(27) FIG. 4 shows a motor vehicle 66 in conjunction with a schematic diagram, which comprises a controllable vibration damper 68, developed in this case as a shock absorber. The vibration damper 68 comprises a working cylinder 70 in which a piston 71 is disposed such that it is movable back and forth. The piston 71 divides the working cylinder 70 into a first working volume 72 and into a second working volume 74. The first working volume 72 and the second working volume 74 are each connected with a valve device 78 across a pressurizing medium line 76. With this valve device 78 the first and the second working volume 72, 74 can be supplied with a pressurizing medium, for example with a hydraulic fluid or compressed air, in the desired manner whereby the vibration damper 68 becomes controllable. The hydraulic or pneumatic structural unit, disposed for this purpose in the valve device 78, are not shown separately, however the structure of the valve device 78 can be oriented, for example, toward the valve device 78 depicted in DE 38 03 888 A. The valve device 78 shown in FIG. 4 comprises at least one check valve 40, which is depicted in FIGS. 3A and 3B, wherein the check valve 40 comprises a spring 10 according to FIG. 1 or 2. In the example depicted in FIG. 4 the valve device 78 comprises two check valves 40 which are connected in parallel, however open and close in opposite directions. When using different springs 10, different pressure conditions in the first and the second working volume 72, 74 and controllable and direction-dependent damping properties of the vibration damper can be realized.

LIST OF REFERENCE SYMBOLS

(28) 10 Spring 12 Base body 16 First surface 18 Second surface 20 Spring arm 22 Free end 24 Contact region 26 Abutment section 28 Reception cutout 30 Circular arc-shaped section 32 Anti-twist protection section 34 Edge 36 Bore 38 Expansion 40 Check valve 42 Base body 44 Closure body 46 First channel 48 Second channel 50 Receiving body 52 Reception section 54 Set-off 56 Sealing washer 58 Abutment body 60 Reception opening 62 Tolerance compensation body 64 Valve seat 66 Motor vehicle 68 Vibration damper 70 Working cylinder 71 Piston 72 First working volume 74 Second working volume 76 Pressurizing medium line 78 Valve device A Longitudinal valve axis B Bending line C Circle L Longitudinal axis M Center point P Arrow R Groove X Spring axis