WO2021209282A1 - Amortisseur de vibrations - Google Patents

Amortisseur de vibrations Download PDF

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Publication number
WO2021209282A1
WO2021209282A1 PCT/EP2021/058896 EP2021058896W WO2021209282A1 WO 2021209282 A1 WO2021209282 A1 WO 2021209282A1 EP 2021058896 W EP2021058896 W EP 2021058896W WO 2021209282 A1 WO2021209282 A1 WO 2021209282A1
Authority
WO
WIPO (PCT)
Prior art keywords
cylinder
fluid
vibration damper
fluid chamber
seal
Prior art date
Application number
PCT/EP2021/058896
Other languages
German (de)
English (en)
Inventor
Stefan Hummel
Sven WECKWERTH
Michael STUPP
Original Assignee
Liebherr-Components Kirchdorf GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Liebherr-Components Kirchdorf GmbH filed Critical Liebherr-Components Kirchdorf GmbH
Priority to EP21717808.6A priority Critical patent/EP4136363A1/fr
Publication of WO2021209282A1 publication Critical patent/WO2021209282A1/fr

Links

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
    • F16F9/06—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using both gas and liquid
    • F16F9/061—Mono-tubular units
    • 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
    • F16F9/10—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using liquid only; using a fluid of which the nature is immaterial
    • F16F9/14—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect
    • F16F9/16—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts
    • F16F9/18—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts with a closed cylinder and a piston separating two or more working spaces therein
    • F16F9/20—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts with a closed cylinder and a piston separating two or more working spaces therein with the piston-rod extending through both ends of the cylinder, e.g. constant-volume dampers
    • 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
    • F16F9/3207—Constructional features
    • F16F9/3235—Constructional features of cylinders
    • 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
    • F16F9/36—Special sealings, including sealings or guides for piston-rods
    • F16F9/362—Combination of sealing and guide arrangements for piston rods
    • F16F9/363—Combination of sealing and guide arrangements for piston rods the guide being mounted between the piston and the sealing, enabling lubrication of the guide
    • 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
    • F16F9/36—Special sealings, including sealings or guides for piston-rods
    • F16F9/365—Special sealings, including sealings or guides for piston-rods the sealing arrangement having a pressurised chamber separated from the damping medium

Definitions

  • the present invention relates to an especially hydraulic vibration damper according to the preamble of claim 1.
  • Vibration dampers especially hydraulic vibration dampers that are filled with an oil, are used in a variety of applications to dampen mechanical vibrations by converting the vibration energy into heat. Vibration dampers of this type are used, for example, as shock absorbers on vehicles or to protect buildings from damaging vibrations such as those caused by people, machines, wind or earthquakes.
  • Typical vibration dampers known from the prior art are based on a cylinder which has a fluid chamber filled with fluid in which a piston is displaceably mounted.
  • the fluid in the cylinder is displaced by one or more damping elements that oppose the displaced fluid with a resistance.
  • the damping elements for example in the form of damping valves, are arranged in the piston so that the displaced fluid is forced from the pressure side through the piston to the low-pressure side.
  • a fluid channel can be provided in which one or more damping elements are arranged, which connects the fluid chamber on both sides of the piston with one another.
  • Seals are used to seal off the fluid chamber of the cylinder from the environment.
  • elastomer seals are often used, which are designed as liquid-tight Wel lendichtung and are arranged on the guide of the piston rod in or on the cylinder housing.
  • the object of the present invention is to provide a vibration damper which, compared to known devices, requires less maintenance.
  • the vibration damper in particular a special hydraulic vibration damper, with the features of claim 1.
  • the vibration damper according to the invention comprises a cylinder, which has a fluid chamber axially delimited by two cylinder covers and filled with a fluid inside, a piston displaceably mounted within the fluid chamber of the cylinder, which separates the fluid chamber into a first and a second chamber, and a with the piston connected to the piston rod, which extends through at least one of the cylinder covers and in this is slidably mounted.
  • the at least one cylinder cover in which the piston rod is mounted has a seal which seals the fluid chamber from the outside, ie from the environment, in a liquid- and / or gas-tight manner. If the fluid is a liquid, for example oil, the seal is liquid-tight. If the fluid is a gas, it is gas-tight.
  • a floating and contactless seal is additionally arranged between the fluid chamber and the seal.
  • non-contact seal is to be interpreted broadly and is to be regarded as a means (pressure reducing means or damping element) which is designed to generate a pressure difference between the fluid chamber and the side facing the seal, i.e. to reduce the pressure.
  • a pressure reducing valve can therefore also be viewed as a contactless seal in this sense. This enables a pressure reduction to the outside.
  • the additional integrated non-contact seal reduces the pressure applied to the (outer) seal, which leads to less friction and thus a longer service life of the seal. Due to the reduced wear of the seal, it has to be replaced less frequently, which considerably reduces the maintenance effort of the vibration damper according to the invention and extends the maintenance intervals required by changing the seal.
  • the vibration damper according to the invention can be, for example, a shock absorber for a vehicle, e.g. a car, excavator, mobile crane, etc., or a vibration damper to protect buildings from earthquakes, environmental influences or vibrations caused by people or machines.
  • a fluid channel which connects the first and second chambers to one another.
  • This can be, for example, a hose, a channel formed within the cylinder or a combination of such sections.
  • the fluid channel can comprise one or more connections or connecting elements.
  • the fluid channel preferably runs partially outside the cylinder, for example in the form of a hose which is connected to channels formed in the cylinder via connections.
  • the fluid channel runs within the cylinder tube.
  • the damper also works without oil compensation of the fluid, taking into account the use. In this case, the two oil connections are closed.
  • the fluid displaced from the pressure chamber i.e. the chamber that is in front of the piston in the direction of movement of the piston and whose volume is thereby reduced
  • the pressure chamber i.e. the chamber that is in front of the piston in the direction of movement of the piston and whose volume is thereby reduced
  • the piston rod ie the chamber on the other side of the piston, the volume of which increases due to the piston movement
  • the fluid channel comprises an inlet channel which is connected to the side facing away from the fluid chamber (ie low pressure side) of the contactless seal and is designed to allow fluid passing through the contactless seal into the other side of the piston to conduct lying chamber (low pressure chamber).
  • the inlet channel is preferably formed in the cylinder, in particular within the cylinder cover, and is connected to a part of the fluid channel extending outside the cylinder.
  • the contactless seal is thus arranged between the fluid chamber and the inlet channel, the inlet channel being arranged between the outer seal and the contactless seal. This arrangement allows the Fluid forced from the pressure chamber by the contactless seal can escape via the fluid channel into the low-pressure chamber. The pressure at the outer seal is therefore only lower than that at the pressure chamber.
  • At least one non-return valve is provided in the fluid channel, which allows a flow of the fluid from the fluid channel into the fluid chamber, but vice versa blocks it. This ensures that fluid can only escape from the pressure chamber into the low-pressure chamber.
  • the fluid channel comprises an outlet channel which opens into the fluid chamber and in which the non-return valve is arranged.
  • the outlet channel does not end on the low-pressure side of the contactless seal, but directly in the fluid chamber.
  • the inlet and / or outlet channels are at least partially formed in the cylinder cover.
  • the channels are preferably connected to one another and connected to a part of the fluid channel extending outside the cylinder via a connection or a connecting element. It is also conceivable that some of the channels inside the cylinder jacket or the cylinder shell extends.
  • the inlet and / or outlet channels are located in particular in the cylinder cover through which the piston rod runs, or in the case of a piston rod running through both cylinder covers in both cylinder covers.
  • at least one inlet channel is provided for each pair of outer and non-contact seals so that the leakage fluid from each of the non-contact seals can flow off via the fluid channel into the respective other (low-pressure) chamber.
  • each cylinder cover has an (outer) seal which seals the fluid chamber from the outside in a liquid and / or gas-tight manner. Accordingly, two non-contact seals are provided, one of these non-contact seals being arranged between the fluid chamber and one of the (outer) seals.
  • each of the chambers separated by the piston can function as a pressure and a low-pressure chamber, depending on the direction of force.
  • a pressure reduced by one of the non-contact seals is applied to each of the seals.
  • the above-described fluid channel comprises an inlet channel and / or an outlet channel with an integrated check valve at each end.
  • the outer seals, the contactless seals and the inlet and outlet channels together with the check valves are designed to be identical (or mirrored). As a result, the vibration damper according to the invention works equally in both directions.
  • the cylinder and piston form a synchronous cylinder, i.e. both piston surfaces are the same size.
  • the (outer) seal is an elastomer seal and in particular a shaft seal contacting the piston rod.
  • the piston separates the first and second chambers from one another in a liquid-tight and / or gas-tight manner (depending on whether the fluid is a liquid or a gas). Ie there are no damping elements such as damping valves are provided in the piston or the piston rod. Instead, the damping effect is achieved by displacing the fluid from the pressure chamber via the contactless seal and finally via the fluid channel into the low-pressure chamber. This enables a simultaneous pressure reduction on the outer seal, which increases its service life.
  • the contactless device is a gap seal.
  • another type of non-contact seal such as a labyrinth seal can be used, which also reduces the pressure applied to the outer seal.
  • a valve e.g. a pressure reducing valve, would also be conceivable here.
  • At least one of the cylinder covers on the side opposite the fluid chamber borders a further closed fluid chamber which is designed to interact with the piston rod in such a way that the volume of the further fluid chamber varies with the movement of the piston rod.
  • the further fluid chamber is preferably filled with a compressible fluid.
  • the volume variation of the further fluid chamber as a function of the position of the piston rod can be realized in that the piston rod protrudes through the cylinder cover into the further fluid chamber or in that another piston or separating piston is provided at one end of the piston rod which faces away from the fluid chamber Page limits the further fluid chamber.
  • the further fluid chamber can be filled with a gas and serve as a gas cushion or gas damper for the vibration damper according to the invention.
  • the vibration damper according to the invention can be a single-tube damper.
  • the gas-filled further fluid chamber or gas chamber is used for volume and temperature compensation.
  • the fluid that is in the fluid chamber is in particular oil.
  • the fluid can be a gas.
  • FIG. 1 an exemplary embodiment of the vibration damper 10 according to the invention is shown in a cross-sectional view along the longitudinal axis of the vibration damper 10.
  • This exemplary embodiment is a hydraulic vibration damper 10.
  • the hydraulic vibration damper 10 comprises a cylinder 12, which has an oil-filled fluid chamber 18 in its interior, which is delimited at the axial ends of the cylinder 12 by two cylinder covers 14, 16 and radially by a cylinder shell 13.
  • a piston 20 is slidably mounted ver, which separates the fluid chamber 18 into two chambers 24, 26 liquid-tight.
  • the piston 20 can have one or more seals.
  • the piston 20 is connected to a piston rod 22 which extends on both sides of the piston 20, has the same diameter on both sides (synchronous cylinder), extends through each of the two cylinder covers 14, 16 and is slidably mounted therein.
  • the piston rod 22 protrudes from the cylinder 12 and has a fastening means 42 at the outer end, via which the vibration damper 10 can be connected to another component or structure of a vehicle, building or other device.
  • the other end of the piston rod 22 likewise protrudes from the corresponding cylinder cover 16, but ends in a further fluid chamber 40 adjoining the cylinder cover 16.
  • elastomer seals 28 are arranged in each cylinder cover 14, 16, which are designed as a shaft seal and are arranged around the piston rod 22.
  • additional gap seals 30 are provided adjacent to the fluid chamber 18, ie between the fluid chamber 18 and the elastomer seals 28.
  • the gap seals 30, as a non-contact shaft seal, allow oil to pass from the fluid chamber 18 to the side facing the elastomer seal 28 (low-pressure side).
  • the vibration damper 10 further comprises a fluid channel 32 which connects the two chambers 24, 26 separated by the piston 20 to one another.
  • a force is exerted on the piston rod 22, so that the piston 20 moves in the direction of the further fluid chamber 40.
  • This increases the pressure on the chamber 26, which is located between the piston 20 and the further fluid chamber 40.
  • the other chamber 24 has a lower pressure.
  • the term “pressure chamber” is used for that chamber 26, 24 in which, due to the force acting on the piston rod 22, there is a greater pressure than in the other chamber 24, 26, hereinafter referred to as “low pressure chamber” the vibration damper 10 is constructed (essentially) symmetrically and functions in both directions (in relation to the longitudinal axis of the piston rod 22), one or the other chamber 24, 26 can represent the “pressure chamber” depending on the direction of the force.
  • the fluid channel 32 comprises a part running outside of the cylinder 12, which in this exemplary embodiment is designed as a hose 33 and runs essentially parallel to the piston rod 22 between the two cylinder covers 14, 16.
  • an inlet channel 34 is formed, which extends from the gap between the piston rod 22 and the cylinder cover 14, 16 or from the The pressure side of each gap seal 30 runs to a connection means 39, which connects the inlet channels 34 to the hose 33.
  • the connection means 39 are hydraulic connections angled at 90 °. From the inlet channels 34 in each of the cylinder covers 14, 16 an outlet channel 36 also runs directly to the fluid chamber 18.
  • each of the outlet channels 36 there is a non-return valve 38, which allows oil to flow from the outlet channel 36 into the fluid chamber 18, but not the other way around.
  • the inlet channels 34 are thus connected to the fluid chamber 18 via the gap seals 30 and the outlet channels 36 via the check valves 38.
  • the inlet and outlet channels 34, 36 as well as the check valves 38 and the connection means 39 are identical and mirrored to one another (on a plane running perpendicular to the longitudinal axis of the piston rod 22).
  • the inlet channels 34 run vertically and the outlet channels 36 run parallel to the piston rod 22.
  • a channel formed in the cylinder shell 13 is provided instead of the hose 33 extending outside the cylinder 12.
  • several fluid channels 32 can be connected in parallel, possibly each with a separate pair of inlet and outlet channels 34, 36 etc.
  • the gap seals 30 thus fulfill a double function. On the one hand, they represent a resistance to the oil displaced by the force and thus ensure the damping effect of the vibration damper 10 according to the invention. On the other hand, they reduce the pressure on the side facing the elastomer seal 28 so that it is less stressed or less friction is generated and these are thus spared. This reduces the wear and tear on the Elastomer seals 28 considerably, which increases the service life until the next maintenance interval.
  • the further fluid chamber 40 can be filled with a gas and thereby act as a gas damper or cushion, which ensures volume and temperature compensation when the vibration damper 10 is stressed.
  • the vibration damper 10 according to the invention is a hydraulic single-tube damper.
  • One of the ends of the piston rod 22 protrudes into the further fluid chamber 40 and ensures that when the piston 20 moves, the volume of the further fluid chamber 40 also changes.
  • the further fluid chamber 40 is closed.
  • a further fastening means 42 is attached to its axial end spaced apart from the piston 20.
  • a pneumatic vibration damper 10 could in principle also be used, the fluid chamber 18 being filled with gas instead of oil and the above-mentioned “liquid-tight” seals being designed to be gas-tight.
  • a gap seal 30 is used, which leads to a reduction in the gas pressure at the outer seals 28.
  • the gap seal 30 is only one possible example of a pressure reducing means which can be used in the vibration damper 10 according to the invention in order to reduce the pressure applied to the elastomer seal 28.
  • a valve could also be provided which fulfills the same function, i.e. generates a pressure difference and opposes the displaced oil with a resistance in order to generate a damping effect.
  • the pressure reducing means can thus also be viewed as a damping element.

Abstract

L'invention concerne un amortisseur de vibrations, en particulier hydraulique, comprenant un cylindre comportant, à l'intérieur, une chambre de fluide délimitée axialement au moyen de deux couvercles de cylindre et remplie de fluide, un piston monté de sorte à pouvoir être déplacé à l'intérieur de la chambre de fluide du cylindre et divisant la chambre de fluide en une première et une seconde chambre, et une tige de piston reliée au piston, s'étendant à travers au moins un couvercle de cylindre, et montée mobile dans ce dernier. Le ou les couvercles de cylindre, dans lesquels la tige de piston est montée, comportent un joint d'étanchéité destiné à assurer l'étanchéité de la chambre de fluide par rapport à l'extérieur, de manière étanche aux liquides et/ou aux gaz. Selon l'invention, un joint d'étanchéité flottant et sans contact est disposé en outre entre la chambre de fluide et le joint d'étanchéité.
PCT/EP2021/058896 2020-04-15 2021-04-06 Amortisseur de vibrations WO2021209282A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP21717808.6A EP4136363A1 (fr) 2020-04-15 2021-04-06 Amortisseur de vibrations

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102020110325.5A DE102020110325A1 (de) 2020-04-15 2020-04-15 Schwingungsdämpfer
DE102020110325.5 2020-04-15

Publications (1)

Publication Number Publication Date
WO2021209282A1 true WO2021209282A1 (fr) 2021-10-21

Family

ID=75441895

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2021/058896 WO2021209282A1 (fr) 2020-04-15 2021-04-06 Amortisseur de vibrations

Country Status (3)

Country Link
EP (1) EP4136363A1 (fr)
DE (1) DE102020110325A1 (fr)
WO (1) WO2021209282A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2022234285A1 (fr) * 2021-05-06 2022-11-10 Domin Fluid Power Limited Système de suspension pour véhicule automobile

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN115009421B (zh) * 2022-06-06 2023-11-24 武汉理工大学 一种具有减震功能的回收舱

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2162540A1 (fr) * 1970-12-16 1972-07-13 Carpenter & Paterson Ltd
DE2730955A1 (de) * 1976-07-16 1978-01-19 Miller Fluid Power Corp Vorrichtung mit kolben und zylinder, insbesondere stossdaempfer
US4597322A (en) * 1984-01-09 1986-07-01 Moog Inc. Seal assemblies
US4957033A (en) * 1988-06-30 1990-09-18 Dominique Relange Device for sealing the mobile elements of an artillery recoil brake
DE10043050A1 (de) * 2000-09-01 2002-08-08 Zf Sachs Ag Führung einer Kolbenstange für ein Kolben-Zylinder-Aggregat
DE102017115801A1 (de) * 2017-07-13 2019-01-17 Liebherr-Components Kirchdorf GmbH Dichtung für einen Betonpumpenzylinder

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Publication number Priority date Publication date Assignee Title
US2500708A (en) 1946-08-26 1950-03-14 Gen Motors Corp Shock absorber
DE1684668U (de) 1952-06-14 1954-10-07 Fichtel & Sachs Ag Stossdaempfer, insbesondere fuer fahrzeuge.
GB1052680A (fr) 1964-09-21
US3972396A (en) 1975-06-05 1976-08-03 United Technologies Corporation Leakage detector with back pressure sensor
US4084668A (en) 1975-06-05 1978-04-18 United Technologies Corporation Redundant damper seals
US4280600A (en) 1979-07-02 1981-07-28 Otis Elevator Company Self-refilling hydraulic actuator

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2162540A1 (fr) * 1970-12-16 1972-07-13 Carpenter & Paterson Ltd
DE2730955A1 (de) * 1976-07-16 1978-01-19 Miller Fluid Power Corp Vorrichtung mit kolben und zylinder, insbesondere stossdaempfer
US4597322A (en) * 1984-01-09 1986-07-01 Moog Inc. Seal assemblies
US4957033A (en) * 1988-06-30 1990-09-18 Dominique Relange Device for sealing the mobile elements of an artillery recoil brake
DE10043050A1 (de) * 2000-09-01 2002-08-08 Zf Sachs Ag Führung einer Kolbenstange für ein Kolben-Zylinder-Aggregat
DE102017115801A1 (de) * 2017-07-13 2019-01-17 Liebherr-Components Kirchdorf GmbH Dichtung für einen Betonpumpenzylinder

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2022234285A1 (fr) * 2021-05-06 2022-11-10 Domin Fluid Power Limited Système de suspension pour véhicule automobile

Also Published As

Publication number Publication date
DE102020110325A1 (de) 2021-10-21
EP4136363A1 (fr) 2023-02-22

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