Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
  • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
  • F16F9/32—Details
  • F16F9/50—Special means providing automatic damping adjustment, i.e. self-adjustment of damping by particular sliding movements of a valve element, other than flexions or displacement of valve discs; Special means providing self-adjustment of spring characteristics
  • F16F9/512—Means responsive to load action, i.e. static load on the damper or dynamic fluid pressure changes in the damper, e.g. due to changes in velocity
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
  • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
  • F16F9/32—Details
  • F16F9/34—Special valve constructions; Shape or construction of throttling passages
  • F16F9/348—Throttling passages in the form of annular discs or other plate-like elements which may or may not have a spring action, operating in opposite directions or singly, e.g. annular discs positioned on top of the valve or piston body
  • F16F9/3484—Throttling passages in the form of annular discs or other plate-like elements which may or may not have a spring action, operating in opposite directions or singly, e.g. annular discs positioned on top of the valve or piston body characterised by features of the annular discs per se, singularly or in combination

Definitions

• the invention relates to a damping valve device with a progressive damping force characteristic according to the preamble of patent claim 1.
• DE 102016210790 A1 describes a damping valve device for a vibration damper, which includes a first damping valve which, in a first operating range, transitions into an open operating position as the flow rate of a damping medium increases.
• the first damping valve is formed, for example, by a piston valve or a bottom valve of the vibration damper.
• a second operating range with a progressive damping force characteristic of the vibration damper is influenced by a throttle point in connection with a valve body, which can be converted from an open position to a throttle position independently of the stroke position of a piston rod of the vibration damper as a function of the flow velocity within the throttle position.
• the valve body moves in the closing direction with increasing flow rate of the damping medium. This generates an additional damping force that makes it unnecessary to use a conventional tension or compression stop, which is only effective in one end position of the piston rod.
• the throttling point and the damping valve are arranged hydraulically in series, with the valve body being designed as a ring element with variable diameter, which executes a radial closing movement in the direction of a flow control surface, in which a defined minimum passage cross section is maintained.
• DE 102019212966 A1 proposes that the ring element, which can be changed in diameter, is additionally supported by a compressive force within a pressure chamber formed by a ring groove.
• the function of the pressure chamber is particularly effective when the cross section of an inflow opening is larger than an outflow opening of the pressure chamber.
• the use of two throttle points then makes sense, one throttle point each for one working direction of the vibration damper. In terms of costs, however, it makes sense to limit the damping valve device to a throttle point that is optimally effective for both flow directions.
• the object of the present invention is to solve the problem known from the prior Tech technology.
• valve carrier in the annular groove has one valve element for each flow direction of the damping valve device and the annular groove is designed with two pressure chambers, each of which has at least one inflow opening and at least one outflow opening, with the effective inflow opening each having a larger cross section as the effective outflow opening
• the two pressure chambers are separated from one another by means of a partition.
• a design with two pressure chambers makes it possible to adjust the size of the pressure chamber and thus indirectly also to adjust the pressure forces that act on the valve element in the closing direction.
• the partition is formed by a disk connected to the valve support.
• the disc itself is a very simple component.
• the partition wall can be formed by the two valve elements, in that the two valve elements slide directly over one another.
• the partition has the outflow opening.
• valve elements can also be made for the valve elements to have the outflow opening, the valve element which is at rest when there is a flow against the damping valve device determining the outflow cross-section.
• the outflow opening in the valve elements can be designed as an axial channel. This results in a minimum flow length within the valve carrier.
• outflow openings are designed as radial channels. This design simplifies i.a. the shape of the partition.
• valve elements are preloaded with a cover side on the partition.
• Fig. 1 Detail from a vibration damper in the area of the damping valve device
• FIG. 1 shows a damping valve device 1 for a vibration damper 3 of any design, which is only partially shown.
• the vibration damper 3 includes a first damping valve 5 with a damping valve body designed as a piston 7 which is fastened to a piston rod 9 .
• the damping valve body 7 divides a cylinder 11 of the vibration damper into a working chamber 13 15 on the piston rod side and a working chamber 13 15 remote from the piston rod, both of which are filled with damping medium.
• In the damping valve body 7 are natural detergent channels 17; 19 are designed for one flow direction on different pitch circles.
• the design of the passage channels 17; 19 is only to be regarded as an example.
• An exit side of the passage channels 17; 19 is provided with at least one valve disk 21; 23 at least partially covered.
• the vibration damper has a cable stop 25, which comes into contact with a stop surface on the cylinder side, e.g. a piston rod guide 27, after a defined extension movement of the piston rod 9.
• the cable stop 25 includes a valve carrier 29 which is fixed directly to the piston rod by a positive connection.
• a valve carrier 29 which is fixed directly to the piston rod by a positive connection.
• an annular elastomer element 31 is placed, for example, which will keep ge over a ge ring radial prestress even with an oscillating movement of the piston rod 9.
• the elastomeric element 31 acts from the stop point on the stop surface as an additional support spring.
• the valve carrier 29 has a circumferential annular groove 33, in which two variable diam water valve element 35 A; 35B is guided.
• the basic construction of Ven tilelements such. B. an elastic ring member or a multi-member Ventilele element are subordinate to the consideration of the function of the invention.
• This valve element 35A; 35B are radially movable or radially elastic and each forms a valve body for a throttle point 37 as part of the damping valve device 1.
• the valve elements 35A; 35 form with an inner wall of the cylinder 11, the same throttle point 37, wherein the inner wall 39 is a flow guide is.
• the invention can also be embodied in a valve carrier 29 which is independent of the cable stop.
• each valve element 35A, 35B carries a separate return spring 41A;
• variable throttle cross section 45 which generates an additional damping force.
• the throttle point 37 is fully open.
• the damping force is then only from the passage channels 17; 19 in connection with the valve discs 21; 23 he begets.
• the valve disks 21; 23 lift the valve disks 21; 23 from its valve seat surface 47; 49 off.
• the lifting movement is carried out by a supporting disc 51; 53 limited.
• the valve element 35A; 35 B In a second operating range with a piston rod speed that is greater than the limit speed of the first operating range, i.e. greater than the 1m/s specified as an example, the valve element 35A; 35 B into a throttle position and executes a closing movement in the direction of the flow guide surface 39. Due to the high flow rate of the damping medium in the throttle point 37, which is shaped as an annular gap, a negative pressure forms, which leads to a radial widening of the respective active valve element 35A; 35B leads. However, so that the throttle point 37 cannot become blocked under any circumstances, the defined minimum through-flow cross-section is determined by the return spring 41 A; 41 B is complied with or a mechanical stop, e.g. B. on the valve carrier limits the expansion movement of the respective valve element and thus determines the minimum passage cross section. This operating behavior is independent of the inflow direction of the damping valve device 1.
• FIG. 2 shows an enlargement of the damping valve device 1 according to FIG. 1 with a different method of attachment to the piston rod 9.
• the enlargement shows that the annular groove 33 and thus the damping valve device 1 are designed for two flow directions.
• the valve carrier 29 in the annular groove 33 has a valve element 35A; 35 B per flow direction.
• valve carrier 29 has two pressure chambers 55A; 55B, each of which has at least one inflow opening 57A; 57B and at least one outflow opening 59A; 59B, the effective inflow opening being a larger one in each case Having cross-section than the effective outflow opening.
• the inflow openings 57A; 57B in the valve carrier 29 are connected to the working chamber 13.
• Each pressure space 55A; 55B is surrounded by an inner lateral surface 61A; 61 B of the valve elements 35A; 35B, ring groove side surfaces 63; 65 and a common annular groove base 67 of the valve carrier 29 is formed.
• the pressure chamber 55A; 55B causes the valve element 35A;
• the two pressure chambers 55A; 55 B are separated by a partition 69 from each other.
• the valve elements are 35A; 35 B sealingly on the annular groove base 65 over a large area.
• the partition is alternately from the two valve elements 35A;
• the valve elements 35A; 35B have the effective outflow opening 59A; 59B, which e.g. B. together from a groove in the inner surface of the valve elements 35A; 35B and the annular groove base 65 is formed.
• the outflow openings 59A; 59B in the partition wall 69 between the two valve elements 35A; 35B out.
• the outflow openings 59A; 59 B designed as an axial channel in the valve elements.
• the cross section of the outflow openings 59A; 59B in the two valve elements does not necessarily have to be of the same size.
• valve elements 35A; 35 B a separate return spring 41 A; 41B.
• These return springs 41 A; 41 B do not necessarily have to be identical, i. H. they can have different restoring forces.
• valve elements 35A; 35B be dimensioned differently to different Liche pressure forces for the valve elements 35A; to generate 35B.
• the damping valve device is constructed symmetrically in relation to a transverse central axis of the valve carrier 29 .
• the damping medium flows for one flow direction via the opening 57A in the valve carrier 29 into the pressure chamber 55A of the valve element 35A and causes a pressure increase which causes the valve element 35A to expand.
• the inflow opening 57A in the valve carrier 29 is many times as large as the axial passage 59A in the valve element 35B. This axial channel in the resting valve element serves as an outflow opening 59A.
• valve element 35A When there is a flow against the damping valve device during a retraction movement of the piston rod 9, i.e. via the opening, a practically identical operating behavior occurs.
• the valve element 35A then remains in its illustrated maximum passage position and the axial channel 59B in the valve element 35A serves as an outflow opening for the pressure chamber 55B of the valve element 35B.
• the partition wall 69 is formed from a separate disc which is connected to the valve carrier 29 .
• the partition wall 69 is stationary between two shells 29A; 29B of the valve support 29 is arranged.
• valve elements 35A; 35B Due to the inner lateral surfaces inclined towards the base of the annular groove, the valve elements are prestressed with a cover side on the partition wall.
• the outflow opening 59 is executed here in the separate partition 69 and ver also binds the two pressure chambers 55A; 55B. Between the inner surfaces 61 A; 61B of valve elements 35A; 35B and the annular groove base 67 there is a radial distance, so that a free annular area of the disk is available for the arrangement of the outflow opening 59 . Nevertheless, one can provide that a valve element 35A; 35B overlaps the outflow opening 59 with its top side facing the partition 69 in order to control an outflow cross section depending on the direction.
• FIG. 4 again shows a modification of the damping valve device according to FIG. 35B executed.
• the radial channels are in the initial position of the valve elements 35A; 35 B in the direction of the flow guide surface 39 and in the direction of the working chamber 13 on the one hand from the valve elements 35A; 35B and due to the position of the valve elements on the disc or partition 69 is closed.
• the disc between the two valve elements 35A; 35 B is fixed as a closed annular disk, so that there is no hydraulic connection between the two pressure spaces 55A; 55B exists.
• damping medium flows into the pressure chamber 55B and into the radial channel 59B.
• Inside half of the throttle point 37 forms a negative pressure and thus an expansion force for the valve element 35B.
• the other valve element 35A is moved only by the force of the un-low pressure of the throttle point 37 in the direction of the flow guide surface 39 or the inner wall of the cylinder 11. Consequently, the expansion force on this valve element 35A is significantly lower.
• the damping force is always determined by the valve element that is subject to the greater expansion force.
• the damping medium 35B flows out of the pressure chamber via the radial channel 59B on the outside past the partition wall 69 and the outer lateral surface 43A of the valve element 35A.
• a mirrored performance of the valve elements 35A; 35B occurs when the damping valve device 1 is subjected to a flow via the inflow opening 57A.

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Physics & Mathematics (AREA)
• Fluid Mechanics (AREA)
• Fluid-Damping Devices (AREA)

Priority Applications (1)

Applications Claiming Priority (2)

Publications (1)

Family

ID=80446701

Family Applications (1)

Country Status (3)

Citations (4)

• 2021
  • 2021-02-16 DE DE102021201436.4A patent/DE102021201436B4/de active Active
• 2022
  • 2022-02-15 WO PCT/EP2022/053647 patent/WO2022175252A1/de active Application Filing
  • 2022-02-15 CN CN202280014898.0A patent/CN116848337A/zh active Pending

Patent Citations (4)

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