WO2019007548A1 - Amortisseur comprenant un corps de frottement - Google Patents

Amortisseur comprenant un corps de frottement Download PDF

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Publication number
WO2019007548A1
WO2019007548A1 PCT/EP2018/000338 EP2018000338W WO2019007548A1 WO 2019007548 A1 WO2019007548 A1 WO 2019007548A1 EP 2018000338 W EP2018000338 W EP 2018000338W WO 2019007548 A1 WO2019007548 A1 WO 2019007548A1
Authority
WO
WIPO (PCT)
Prior art keywords
friction body
housing
friction
damping device
movement
Prior art date
Application number
PCT/EP2018/000338
Other languages
German (de)
English (en)
Inventor
Tobias GÖDDERTZ
Original Assignee
Stabilus 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 Stabilus Gmbh filed Critical Stabilus Gmbh
Publication of WO2019007548A1 publication Critical patent/WO2019007548A1/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
    • F16F7/00—Vibration-dampers; Shock-absorbers
    • F16F7/08—Vibration-dampers; Shock-absorbers with friction surfaces rectilinearly movable along each other
    • 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
    • F16F7/00—Vibration-dampers; Shock-absorbers
    • F16F7/08—Vibration-dampers; Shock-absorbers with friction surfaces rectilinearly movable along each other
    • F16F7/082—Vibration-dampers; Shock-absorbers with friction surfaces rectilinearly movable along each other and characterised by damping force adjustment means
    • F16F7/085—Vibration-dampers; Shock-absorbers with friction surfaces rectilinearly movable along each other and characterised by damping force adjustment means resulting in the damping effects being different according to direction of movement
    • 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
    • F16F7/00—Vibration-dampers; Shock-absorbers
    • F16F7/08—Vibration-dampers; Shock-absorbers with friction surfaces rectilinearly movable along each other
    • F16F7/09—Vibration-dampers; Shock-absorbers with friction surfaces rectilinearly movable along each other in dampers of the cylinder-and-piston type

Definitions

  • the present invention relates to a damper or damper device, in particular a motion damper and / or industrial shock absorbers, in particular for use in struts.
  • the invention will be described with reference to struts in trains or automobiles, particularly road vehicles, but it should be understood that the present invention may be used in other damper devices.
  • gas springs can be used.
  • Damper devices are technically often less suitable due to strong temperature dependencies. Although conventional hydraulic damper devices have a lower temperature dependence, but are relatively expensive. In addition, both conventional dampers and gas springs high flow noise over their
  • Applicant's prior art discloses friction element dampers which cause frictional damping between a pipe and a friction body.
  • the present invention is therefore an object of the invention to provide a damping device available, which on the one hand no high temperature
  • a damping device in which a
  • a damper device is to be made available, which allows in comparison to the prior art cheaper Hubformen or shorter designs.
  • a damping device has a housing (in particular a tubular housing) and a rod element movable relative to this housing between at least two movement positions in a longitudinal direction of this housing and at least one friction body arranged inside the housing and a first at least temporarily on a surface of the rod element fitting
  • the friction body and in particular at least one surface of the friction body is at least temporarily on a peripheral surface of the
  • the mentioned direction of movement is in particular a straight-line direction of movement.
  • the rod element is movable relative to this friction body in the longitudinal direction of the housing and the friction body is designed such that a friction force occurring between the friction body and the rod element during movement of the rod element depends on a position of the rod element relative to the housing and / or in FIG Dependence of a direction of movement of the rod element changes.
  • frictional force is used, but it would additionally or alternatively also be conceivable, instead of the term frictional force, to use the term frictional coefficient or else that of a force between the respective frictional partners, in particular an outer surface the rod element and the friction body acts. In this case, preferably a friction coefficient and / or a force change, in particular between the surfaces rubbing against each other.
  • Rod element changes. In this way it is possible that, for example, when
  • Damping device comparatively low in the production.
  • a frictional force during withdrawal of the rod element from the housing is different from a frictional force when the rod element is pushed into the housing.
  • the simplification is always spoken of a rod element.
  • this rod element may preferably also be a tubular body or an internally hollow rod element.
  • a guide means for guiding the longitudinal movement of the rod member is provided. It is advantageous that this guide device is spaced in the direction of movement or in the longitudinal direction of the housing of the friction body. It would also be possible for two guide devices to be provided which guide the longitudinal movement of the rod element, and these two guide devices are preferably spaced apart from one another in the longitudinal direction of the housing.
  • Rod member occurs at least temporarily less than a frictional force which occurs between the friction body and the rod member.
  • a frictional force between the guide means and the rod member is at least temporarily less than 50% than the frictional force between the friction body and the rod member, preferably less than 40%, preferably less than 30% and more preferably less than 20% and most preferably less than 10 %.
  • the guide means comprises a plurality of projections which extend in the direction of the rod member (or pipe member). These projections extend in particular in a radial direction of the rod member. Particularly preferred are these projections (in particular in
  • Circumferential direction spaced from each other.
  • the at least one friction body is at one with respect to at least one
  • Rod member in the friction body the rod member has a first surface of the
  • the housing has a first
  • Attachment section in order to arrange this housing on another element, such as a support member in a vehicle.
  • the rod element preferably also has a fastening element in order to fasten the rod element to a further component of the vehicle.
  • These fastening devices may particularly preferably be threads.
  • Rod element in an end position creates a damping.
  • This is preferably achieved by a friction body with a very special geometry, which will be described in more detail below.
  • This friction body can preferably act as a linear freewheel brake and prevent movement of the rod member only in one direction considerably or
  • a direction change preferably take place in any position of the rod member relative to the housing.
  • the at least one friction body is arranged in a predetermined section of the housing.
  • the friction body is arranged in a portion of the housing which is opposite to an opening, via which the rod element is inserted into the housing.
  • the friction body is arranged in an end portion of the housing, particularly preferably in a lower third of the housing, preferably a lower quarter and particularly preferably a lower fifth of the housing.
  • the friction body has an opening through which the rod element can be guided.
  • the friction body has an annular structure.
  • the rod element is preferably pushed.
  • the opening is an opening with a circular cross-section.
  • the opening is preferably an opening with a variable cross section.
  • the opening has a smaller cross-section than a External cross section of the rod element.
  • the rod element has a circular cross-section.
  • a radially inner portion of the friction body is pivotable relative to a radially outer portion of the friction body. It is conceivable and preferred that a radially outer portion of the friction body is substantially stationary relative to the housing and in particular an inner wall of the housing and a radially inner portion of the friction body relative to the housing is movable, and in particular in the longitudinal direction of the housing is movable.
  • the friction body is a flexible element.
  • the friction body has a portion which can be arranged in at least two pivot positions.
  • a first pivot position of the friction body and a second pivot position of the friction body are distinguished by the fact that said opening has a different cross section in these respective pivot positions.
  • a smaller cross section of this opening is achieved when inserting the rod element into the friction body or into the housing, and a larger cross section of this opening when the rod element is pulled out. In this way, as explained in more detail below, allows the friction during insertion of the rod member in the friction body is greater than in a subsequent extraction.
  • the rod element has a
  • Insertion bevel and / or chamfer (generally a tapered portion) to be inserted into said opening of the friction body.
  • This insertion bevel may have a conical shape but also other shapes such as hemispherical shapes or schellipsoidförmige figures.
  • that region of the insertion bevel which has the smallest cross section also has a smaller cross section than the above-mentioned opening of the friction body.
  • Rod member an outer cross section of the rod member greater than a cross section of said opening of the friction body. In this way, a certain coefficient of friction is achieved.
  • the exact adjustments of these aspect ratios may be used to determine what friction is actually to occur between the rod member and the friction member.
  • the device has at least two, preferably at least three and particularly preferably a plurality of such friction bodies. Particularly preferably, these friction bodies are arranged directly adjacent to each other within the housing.
  • the friction bodies are arranged loosely and / or without additional guide elements within the housing. In this way, more uniform distribution of forces can be achieved and so the total wear can be reduced.
  • a damping fluid for example oil
  • the preferred is
  • these friction bodies are each configured identically.
  • a surface of a first friction body contacts a further surface of a further friction body and in particular a friction body adjacent in the longitudinal direction of the housing.
  • the friction between the individual friction bodies is kept low, which can be achieved recordable by a special coating of the respective mutually rubbing surfaces of the friction body.
  • a plurality of said friction bodies are pivotable and it is preferably a pivoting movement of the individual friction bodies coupled together.
  • the individual friction bodies are each pivoted together.
  • the friction body can be integrated into a separate unit. So it would be possible in the case of wear only this
  • the individual contiguous friction bodies and in particular their openings in at least one pivotal position of the friction body substantially form a hollow cylinder, through which the rod element can be guided.
  • the at least one friction body has a fourth surface resting against an inner wall of the housing. In this way, the friction body is clamped in a movement of the rod member between an outer surface of the rod member and an inner surface of the housing and in this way creates a certain frictional action.
  • the friction body has a section which can be pivoted relative to the housing. This is especially by this
  • the friction body may be in a first pivot position and in the subsequent withdrawal of the rod element out of the housing in a second pivot position.
  • the opening cross section of the friction body is changed in particular by this pivoting of the pivot portion of the friction body.
  • this pivoting portion is pivotable with respect to a circumferential direction of the friction body.
  • a sectional view of the respective pivot portion would be pivotable in a plane which is defined on the one hand by the direction of movement of the rod member and on the other hand by a radial direction of the respective cross-sectional view.
  • this friction body or an extension of the friction body in the longitudinal direction is changed by pivoting said pivot portion of the friction body.
  • the friction body pivots about a pivot axis which is always perpendicular to the longitudinal direction of the housing and / or to the direction of movement of the rod member.
  • pivot points of the pivoting sections lie on a circular line formed around the longitudinal direction.
  • a pivotal position of the pivotable portion changes in response to a direction of movement of the rod member. Upon withdrawal of the rod member or the piston rod is carried out in this way an automatic switching of the special friction body to a lower bias, whereby the friction force or operating force is significantly reduced.
  • This operating force has a direct influence on the forces of action or hand forces in the application, which are to be kept low in accordance with market requirements.
  • a change in the pivot position of the pivot portion of the friction body is caused by a movement of the rod member.
  • At least temporarily different surfaces of the friction body preferably contact this rod member.
  • said pivot portion is pivotable about a predetermined pivot angle.
  • the surfaces which contact the rod member are inclined at a preferred angle with respect to each other.
  • said pivoting angle, about which the pivoting portion is pivotable substantially coincide with that angle with respect to which the two surfaces of the friction body, which contact the rod element depending on the direction of movement.
  • the damping device has a limiting element which limits a pivoting movement of the at least one friction body.
  • This limiting element can be designed as a stop.
  • this limiting element has a conical surface, which in particular with respect to a radial direction of the housing by a predetermined angle, in particular to the maximum possible
  • Tilt angle is inclined.
  • the limiting element has a circumferential surface with respect to the longitudinal direction of the housing.
  • Embodiment is in at least one pivot position, a surface of a friction body on this limiting element and is preferably flat on this
  • this limiting element is arranged within the housing.
  • this limiting element is arranged on a sleeve which is also located in the interior of the housing. It is possible that this sleeve can be arranged in the longitudinal direction of the housing at different positions.
  • the number of friction bodies can be varied.
  • the damping device has a second friction body which is adjacent to the first friction body in the longitudinal direction is arranged.
  • a plurality of such friction bodies are preferably provided. Due to the configuration of a plurality of friction bodies arranged one behind the other, in particular also the surfaces which support the rod element in
  • the friction body is made of a material containing PE, POM or foam.
  • the friction body is made of a foam.
  • the friction body is made of a polyurethane foam. This is particularly preferably a closed-cell or closed-cell foam.
  • the foam is an abrasion-resistant foam. In this case, both an impregnated and a non-impregnated foam can be used. More preferably, a resilient foam is used.
  • the friction body has a first surface, which contacts the rod element during movement of the rod element in a first direction of movement, and particularly preferably a third surface which engages the rod element during movement of the rod element in a second direction of movement, that of the first direction of movement is opposite, contacted.
  • these two surfaces enclose a predetermined angle with one another, which particularly preferably corresponds to the pivoting angle of the pivoting section substantially and / or deviates from this angle by less than 10%.
  • the friction body (as viewed in a circumferential direction of the friction body) has a cross section which substantially
  • a surface of the rod member which contacts the friction members is machined. It is possible that this surface in terms of a
  • Friction optimization is edited. In this way, wear of the friction body can be reduced.
  • filter elements may also be provided in the interior of the housing, which prevent any abrasion of the friction body from reaching other areas of the spring device. Also could Filter elements may be provided, which prevent dirt particles from entering that region of the housing in which the friction body are arranged.
  • the present invention is further directed to a vehicle, and more particularly
  • this vehicle has a plurality of the above-mentioned damping devices. Particularly preferred are these
  • Damping devices arranged on struts of the vehicle.
  • a damper device and a spring device such as a coil spring, which can wind around an outer periphery of the damper means understood.
  • the present invention is further directed to a friction body, in particular for use in a damping device, wherein the friction body has an annular shape with a preferably circular opening.
  • the friction body has a first inner surface, and a second inner surface, wherein the second inner surface is angled relative to the first inner surface, and wherein the
  • Friction body has a foam material.
  • the inner surface is understood to mean a surface pointing in the direction of the inner opening.
  • the friction body has a circular cross-section.
  • the friction body also has a third, outer surface and a fourth outer surface, wherein the third outer surface is angled relative to the fourth outer surface.
  • At least one inner surface is parallel to an outer surface.
  • the further inner surface is parallel to the further outer surface.
  • the distance of the first mutually parallel inner and outer surfaces is greater than the distance of the second mutually parallel surfaces.
  • the inner and outer surfaces are flat surfaces.
  • the present invention is further based on a Reib redesign donation, in particular for
  • the Reibenia corpus comprises a plurality of annular friction bodies, each having a preferably circular opening and having a foam material, said annular friction body abut each other and wherein the Reibenia corpus further comprises a holding means which holds the individual friction body to each other ,
  • the individual friction body of Reib stresseses are designed in the above manner.
  • the holding means is particularly suitable and intended to be arranged within a damper device. It is possible that the holding means is made of a metal or a plastic.
  • the holding means may comprise a locking device such as an external thread so as to be screwed into a housing of a damper device can.
  • the holding means has a hollow cylindrical shape.
  • the friction body lie directly against each other, but it would also be conceivable that a separating material is provided between the individual friction bodies.
  • FIG. 1 a - 1 c Three schematic representations of an inventive
  • FIG. 2a, 2b Two representations of a force curve and a work history when
  • Fig. 3 is a representation of the friction body in different pivot positions
  • Fig. 5 is an external view of the damper device shown in Fig. 4.
  • FIG. 1 a shows a schematic representation of a damper device 1 according to the invention.
  • This damper device 1 has a rod element 6 which is movable from left to right here, that is to say in a longitudinal direction L of the damper device 1.
  • the reference numeral 12 denotes a guide device which serves to guide this longitudinal movement of the rod member 6.
  • a plurality of friction bodies 8 is arranged in a lower or right third of the housing 2. These friction bodies have a disc-shaped and / or ring-shaped design on. In the embodiment shown in FIG. 1a, a total of six such disk-shaped friction bodies are provided, which are accommodated in said housing section. These friction bodies 8 each have an opening 82 into which the rod element 6 can be inserted. For this purpose, the rod element also has an insertion bevel or chamfer in order to be able to be inserted more easily into the openings in this way.
  • the reference numeral 16 denotes a stop which serves as a travel limit for the
  • Bar element 6 is used.
  • the opening 82 is configured at least in the state shown in Figure 1 a such that it is slightly smaller than an outer cross section of the rod-shaped body 6. In this way, a frictional force between the rod member 6 and the friction bodies 8 is achieved. This frictional force dampens the movement of the rod member when inserted into the housing.
  • Figure 1 a shows a state in which the rod element is not yet inserted into the friction body.
  • the friction body 8 are formed self-switching and form in the rest position or in the installation position extending in the longitudinal direction L hollow cylinder 80 from.
  • the rod element is first inserted over a certain adjustment range, with only frictional forces on the rod guide 12 are opposed to the movement.
  • the reference character L denotes the longitudinal direction of the housing 2
  • FIG. 1b shows a situation in which the rod element has already been inserted further into the friction body 8 (arrow P1). Upon arrival of the rod member in the Dämpf Geb this enters the friction body and spreads them by an oversize between the
  • Rod element of 8cm and an inner diameter of the friction body of 7cm are provided.
  • Rod element 6 and the friction bodies It can be seen that in the situation shown in Figure b, the rod element only with a certain surface area of the friction body in Touch comes. If the kinetic energy is reduced, the rod element is clamped by the friction bodies, so that a certain holding force F is available for securing an end position. If the rod element is pulled out by overcoming this force (arrow P2), the friction body switch by design or change their pivot position, as shown in Figure 1 c. Due to this pivoting process creates a larger inner diameter of the friction body and in this way a much lower frictional force between the rod member on the one hand and the friction bodies on the other hand compared to the direction of movement of the insertion. In this state, other surfaces of the friction bodies preferably also come into contact with the outer circumference of the rod element 6, in particular the surface 8c.
  • the plastic construction offers the advantage that no painting is required.
  • the favorable stroke conditions and the short design also offer a variety of uses.
  • the Dämpf characterizing by different diameter ratios linear, progressive or degressive is adjustable.
  • Plastic construction can also be realized a very low weight.
  • a laser signature of the plastic surface would be possible.
  • Figures 2a and 2b show force relationships during insertion and withdrawal of the rod member in the housing or the damping device. It can be seen that when the rod element is pushed in, the thrust force increases relatively sharply above a certain position at a stroke of 20 mm. The areas below zero indicate how to retract the bar element. It will be appreciated that the forces required to pull the rod member are substantially less than the forces needed to insert the rod member. It can also be seen that, overall, the work W expended for inserting the rod element, which results as an integral of the force, is substantially greater than the comparatively work required to remove the rod
  • Rod element must be expended. Before the rod element with the friction body in Contact occurs, the required power is very low and is essentially only through the
  • FIG. 3 shows a representation of a friction body 8 in two different pivot positions. In the situation shown in the left pivot position, the rod member is pulled out of the friction body.
  • the rod member is pulled out of the friction body.
  • the reference numeral 8b denotes a surface of the friction body 8 which rests against the inner wall of the housing 2 during operation.
  • the reference numeral 84 denotes the pivoting portion of the friction body, which pivots as shown in the two subfigures.
  • the right-hand illustration shows the friction body in a second pivoting position, in that in which the rod element is inserted into it.
  • the cross-section d m 'of the opening 82 which is noticeably smaller than the cross-section d m . Therefore, the frictional forces between the rod member (not shown) and the friction body 8 are larger than those shown in the left subfigure.
  • the reference numeral 8c denotes a surface of the friction body, which at least temporarily abuts against the outer surface of the rod member 6 (not shown) during operation.
  • a particular geometry of the friction body 8 is preferably present in order to achieve the stated functionality. It can be seen that the cross-section Q of the friction body in the circumferential direction, viewed in the circumferential direction, is substantially rectangular, but with two cut-off corner regions.
  • d m denotes the diameter of the rod element or the diameter required to achieve a certain force during the return stroke.
  • d denotes the outer diameter of the friction element (in an unloaded state) and thus also the inner diameter of the housing or pressure tube.
  • t denotes the material thickness.
  • ⁇ denotes the setting or chamfer angle between the inside and
  • This external cross section is preferably at most 20% larger, preferably at most 10%, preferably at most 5% and particularly preferably at most 3%. Is preferred the outer cross section of the friction body by at least 0.2% greater than the inner cross section of the housing 2, preferably by at least 0.4% and more preferably by at least 1, 0%.
  • the reference numeral 8a indicates the surface which is in the insertion of the
  • the reference character h finally indicates the calculated height in a loaded state, for example, a state in which the rod member is retracted.
  • the calculation of the angle of attack ⁇ and the height may be, for example
  • FIG. 4 shows a further illustration of a damper device 1 according to the invention.
  • two fastening devices 32 and 34 are provided, which serve to fasten the damper device to a further object such as, in particular, a vehicle.
  • These fastening devices are preferably designed as external threads.
  • a second guide means 24 can be seen, which serves to guide the rod member 6 in its longitudinal movement.
  • the reference numeral 26 denotes a limiting element, which limits a pivoting movement of the individual friction bodies 8. In a pivoting state, a surface of the outermost friction body lays against a
  • FIG. 5 shows an external view of the damper device shown in FIG. 4. It can be seen that the housing has clamping points 28 on its outer circumference, which ensure a stable seating of the limiting element in the interior of the housing.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Vibration Prevention Devices (AREA)
  • Vibration Dampers (AREA)

Abstract

L'invention concerne un dispositif amortisseur (1) comprenant un boîtier (2) et un élément formant tige (6) mobile par rapport audit boîtier (2) dans une direction longitudinale (L) dudit boîtier (2) entre au moins deux positions de déplacement et au moins un corps de frottement (8) qui est disposé à l'intérieur du boîtier (2) et qui comporte une première surface de frottement (8a) reposant par intermittence sur une surface de l'élément formant tige (6). Selon l'invention, l'élément formant tige (6) peut être déplacé par rapport au corps de frottement dans la direction longitudinale (L) du boîtier. Ledit corps de frottement (8) est configuré de telle manière qu'une force de frottement se formant entre le corps de frottement (8) et l'élément formant tige (6) dans le cas d'un déplacement de l'élément formant tige (6) varie en fonction d'une position de l'élément formant tige (6) par rapport au boîtier et/ou à une direction de déplacement de l'élément formant tige (6).
PCT/EP2018/000338 2017-07-06 2018-07-04 Amortisseur comprenant un corps de frottement WO2019007548A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017006374.5A DE102017006374A1 (de) 2017-07-06 2017-07-06 Dämpfer mit Reibkörper
DE102017006374.5 2017-07-06

Publications (1)

Publication Number Publication Date
WO2019007548A1 true WO2019007548A1 (fr) 2019-01-10

Family

ID=63113460

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Application Number Title Priority Date Filing Date
PCT/EP2018/000338 WO2019007548A1 (fr) 2017-07-06 2018-07-04 Amortisseur comprenant un corps de frottement

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DE (1) DE102017006374A1 (fr)
WO (1) WO2019007548A1 (fr)

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2753177A (en) * 1953-04-20 1956-07-03 William H A Boyd Friction spring shock absorber
DE1744287U (de) * 1957-02-28 1957-05-02 Hemscheidt Maschf Hermann Federdaempfungsaggregat, vorzugsweise fuer fahrersitze, kleinstfahrzeuge u. dgl.
FR70249E (fr) * 1956-06-07 1959-03-25 Amortisseur de frein de chocs

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1085725B (de) * 1958-08-28 1960-07-21 Peka Fahrzeugbau K G Reibungsstossdaempfer
DE9309885U1 (de) * 1993-07-02 1993-08-26 BT Bautechnik - Impex GmbH & Co KG, 85764 Oberschleißheim Dichtring für Betonschächte
AU2003289052A1 (en) * 2002-12-12 2004-06-30 Fukoku Co., Ltd. Damper
DE102005029938B3 (de) * 2005-06-28 2006-11-09 Zf Friedrichshafen Ag Zusatzfeder für ein Kolben-Zylinderaggregat
DE102013109196B4 (de) * 2013-08-26 2023-03-02 Miele & Cie. Kg Reibungsdämpfer, insbesondere für eine Trommelwaschmaschine

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2753177A (en) * 1953-04-20 1956-07-03 William H A Boyd Friction spring shock absorber
FR70249E (fr) * 1956-06-07 1959-03-25 Amortisseur de frein de chocs
DE1744287U (de) * 1957-02-28 1957-05-02 Hemscheidt Maschf Hermann Federdaempfungsaggregat, vorzugsweise fuer fahrersitze, kleinstfahrzeuge u. dgl.

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