Damper assembly and machine for such damper assembly

Abstract

A damper assembly, particularly for use in a washing machine, comprises: at least one damper (14) generating a damping effect, particularly an active damper (14), which is capable of being arranged between two movable parts (2, 10) of the washing machine (1) and connected to the two parts respectively; an adjustment unit (25) communicating with the damper (14) and intended to adjust the damping effect of the damper (14); and at least one determining unit (26) communicating with the adjustment unit (25) to determine at least one input variable, wherein the adjustment unit (25) is designed to transmit an adjustment signal to the damper (14) according to the at least one input variable, and the damper (14) is designed to variably determine its damping effect according to the adjustment signal. In addition to at least one active damper, at least one passive damper can also be provided.

Description

[0001] This patent application claims priority to German patent application DE 102020206722.8, the contents of which are incorporated herein by reference. Technical Field

[0002] The present invention relates to a damper assembly and a machine having such a damper assembly, particularly a washing machine. Background Technology

[0003] In machines with components that can move relative to each other, it may be necessary to dampen the relative movement of the components. Dampers can be used for this purpose. Summary of the Invention

[0004] The objective of this invention is to improve the damping of the relative movement of two components in a machine that can move relative to each other, and in particular to expand the possibilities of influencing the damping effect.

[0005] This objective is achieved through the features of claims 1 and 10. The core of the invention lies in the damper assembly having an adjustment unit that communicates signals with the damper. This damper produces a damping effect and can be arranged between two components (parts of a washing machine) that can move relative to each other, and can be connected to both components respectively. The adjustment unit is used to adjust the damping effect of the damper. The adjustment unit can be arranged outside the damper or integrated into the damper.

[0006] Furthermore, the damper assembly includes a determining unit that communicates with the adjusting unit to determine at least one input variable. The determining unit can be located externally to the damper or integrated within it. The adjusting unit is designed to transmit an adjustment signal to the damper based on the at least one input variable. The damper is designed such that its damping effect can be variably defined according to the adjustment signal. This variable determination of the damping effect is particularly active. The damper is particularly an active damper. The damping effect can be, for example, frictional damping or hydraulic damping.

[0007] An active damper is, for example, a friction damper with switchable freewheeling capability. This switchable damper has a switching unit that allows switching between a locked configuration and a freewheeling configuration. In the locked configuration, displacement of the friction pads within the damper housing is blocked. In the freewheeling configuration, axial displacement of the friction pads within the housing is possible. Such a damper is known from DE 102016207809A1, which is referenced herein.

[0008] An active damper can be designed as a friction damper, wherein the frictional force, i.e., the damping effect, can be variably adjusted. At least one friction liner is attached to a friction liner carrier. By means of an adjusting member, at least one friction liner can be adjustably arranged at the friction liner carrier, and in particular, can be pressed against a corresponding friction mating member with a variable contact force, especially against the inner wall of the damper housing. The damping effect varies depending on the contact force of the at least one friction liner. Such a damper is known from DE102016225036A1, which is referenced herein.

[0009] Active dampers can also be friction dampers with friction units that generate directional friction on an axially movable plunger. The plunger is movable within the housing of the friction damper. The friction unit has at least one friction liner that frictionally rests against the plunger. The friction force can be variably determined by a switching unit. In particular, the switching unit is used to lock the tiltability of the friction liner carrier, wherein different amounts of friction force act on the plunger at different tilt positions of the friction liner carrier. This type of friction damper is known from DE 102020202348.4, which is referenced herein.

[0010] Because of the axial restriction that allows for variable adjustment of the mobility of the friction lining in the friction damper, an active damper can also be formed. This can be achieved, for example, by at least one axially movable inertial advance stop. This type of friction damper has a variable and adjustable inertial advance length. At least one inertial advance stop can be driven, for example, by a motor, particularly an electric motor, wherein the motor is arranged, for example, parallel to the longitudinal axis of the friction damper on the outside of the friction damper housing. The rotational motion of the motor is transmitted, particularly via a gear connection, to a rotating link having helical recesses and / or grooves along its outer circumference. An axially oriented adjusting rod is guided in these recesses and / or grooves and is connected to the inertial advance stop. The adjusting rod, and thus the at least one inertial advance stop, is axially adjusted by the rotational motion of the rotating link. This thus changes the inertial advance length of the friction damper.

[0011] Active dampers can also be provided by friction dampers, wherein the friction lining comprises foam plastic impregnated with magnetorheological fluid. The frictional characteristics, particularly the damping effect of such dampers, can be tuned in a targeted manner through the interaction of an electromagnetic field with the magnetorheological fluid. This type of damper is known from WO 99 / 22162A1, which is referenced herein.

[0012] Active dampers can also be hydraulic dampers, where the damping effect is achieved by the flow of damping fluid through an integrated throttling channel. The integrated throttling channel forms a fluid throttling connection. The throttling channel has a flow cross-sectional area and a throttling channel length that affect the damping effect. In active dampers, the length and / or cross-sectional area can be variably adjusted.

[0013] The adjustment unit is particularly independent of the machine's control system, especially the washing machine's control system.

[0014] The damping effect can be defined in multiple steps, that is, in discrete damping effect steps, and / or in a continuous damping effect process.

[0015] The damper assembly in a washing machine is particularly advantageous. However, the damper assembly according to the invention is also applicable to other machines, particularly those in the field of mechanical engineering, such as paint mixers in DIY shops, specialized paint dealers and / or paint shops, and / or for horizontal or vertical centrifuges and other rotating machines that may be unbalanced, such that the resonant frequency of the system can pass through during operation, in order to dampen the relative motion of two parts that can move relative to each other.

[0016] The damper design of the friction damper according to claim 2 ensures a robust damper assembly and effectively provides a damping effect. This damper assembly is particularly suitable for washing machines. Specifically, the friction damper has a friction unit for generating frictional force. The frictional force specifically resists relative movement between the housing and / or plunger of the friction damper.

[0017] The embodiment of the friction unit according to claim 3 achieves active, particularly direct, and variable adjustment of the frictional force. For this purpose, the friction unit can have an inertial forward function, which can be activated or deactivated and / or actively changed, i.e., actively adjusted. Regardless of whether the inertial forward function is activated, the damping effect of the damper assembly changes. Inertial forward means that for a fixed displacement path of the plunger, the so-called free-lift height, no frictional force or at most very small frictional force is generated by the friction damper relative to the housing of the friction damper. When the free-lift height is exceeded, the friction unit generates a higher frictional force. It is also conceivable that the amount of free-lift height can be set to be variable, staged, or continuous.

[0018] Alternatively or concurrently, the friction unit can be designed to variably adjust the frictional force, particularly the magnitude of the frictional force. This can be achieved, for example, by a friction unit having at least one friction liner, which is pressed against a movable component of the friction damper, i.e., at least one of the housing and / or plunger, by a variable and adjustable contact force. Therefore, the frictional force generated by the friction unit, particularly the friction liner, is adjustable.

[0019] As an embodiment of the hydraulic damper according to claim 4, the damping function can be directly changed, particularly by means of a variable and adjustable throttle valve. Specifically, the throttle valve can change its cross-sectional area and / or the length of the throttle passage.

[0020] Another conceivable approach is to design the damper as a piston-shell unit with a housing and a piston movable relative to it, wherein the piston may specifically have a carrier material with a magnetorheological fluid. The housing may have at least one electromagnetic coil, wherein the damping effect, i.e., the force resisting movement between the piston and the housing, can be variably adjusted by changing the electric field of the electromagnetic coil in the housing.

[0021] The damper assembly according to claim 5 achieves a simple design for the damper itself. The determination of at least one input variable can be independent of the damper. In particular, sensors already present in the machine (especially a washing machine) can be used. In particular, the damper assembly is capable of frequency-related adjustments, particularly by determining changes in the direction of components that can move relative to each other, particularly by means of an acceleration sensor, by means of a light-blocking plate, and / or by means of displacement measurement.

[0022] The embodiment of the determining unit according to claim 6 is possible without additional sensors. Characteristic parameters of the drive motor (particularly the electric motor driving the clothes drum of a washing machine) are used as input variables for the adjustment unit. In particular, motor performance, especially motor current and its variation over time, can be used as characteristic variables to identify imbalances in the clothes drum. Alternatively or additionally, the motor's rotational speed signal, particularly its variation over time, can be used for imbalance determination.

[0023] Alternatively or additionally, the determining unit according to claim 7 may include a sensor specifically integrated into the damper. This type of sensor may be a magnetic displacement sensor, an optical sensor, and / or, in the case of a hydraulic damper, a flow sensor. The sensor is specifically used to determine the movement of at least one damper component, particularly the housing, a plunger movable relative to the housing, and / or a friction unit.

[0024] The damper assembly according to claim 8 realizes a simplified embodiment of a machine, particularly a washing machine. Since the damper itself has a transport fixing device, particularly an integrated transport fixing device, the usual transport fixing device for washing machines is optional. The transport fixing device of the damper can be designed to fix a minimum damping effect (i.e., press fit), thereby reliably ensuring the exclusion of relative movement, particularly the relative movement of the washing machine tub within the washing machine housing. Alternatively or additionally, the transport fixing device of the damper can have a locking member to lock the movement of the damper, and thus the movement of the washing machine tub within the housing. In this case, the transport fixing device has a form-fit design. This locking is also possible by reducing the flow cross-sectional area of ​​the hydraulic damper to zero, i.e., closing it.

[0025] The damper assembly with the emergency energy unit according to claim 9 ensures reliable and, in particular, risk-free operation of the machine with the damper assembly in emergency situations, i.e., especially when the machine and / or the damper assembly lose power, i.e., especially when standard energy is no longer available, and if applicable, only temporarily. The emergency energy unit specifically includes a drive mechanism capable of driving at least one of the components that can move relative to each other, the drive being particularly designed as an electric motor and capable of functioning as a generator in emergency situations. The emergency energy unit may also include a sensing unit for inducing current, particularly a coil and magnet attached to the damper component. The emergency energy unit may also include a battery or other type of battery cell and / or capacitor. Furthermore, the emergency energy unit may also have a mechanical energy storage unit, particularly a pre-tensioned spring member, particularly a pre-tensioned diaphragm spring or a pre-tensioned helical spring, and / or an independent, self-sufficient, usable fluid pressure, particularly in the form of a pressure vessel under fluid pressure, particularly filled with water, gas, and / or hydraulic media. Corresponding supply lines for water, gas, air, hydraulic media, or another fluid may also serve as a pressure source.

[0026] The machine according to claim 10, particularly a washing machine, has the advantage of a damper assembly, which is referred to herein. The machine has a first part and a second part movable relative to each other, wherein the second part is particularly rotatable about a rotational axis. In the machine, at least one damper is connected to, and particularly attached to, the first and second parts.

[0027] At least one damper is an active damper according to the patent application. Multiple active dampers can be provided for the machine. In addition to at least one active damper, at least one passive damper may also be provided, suitably attached to the component. In particular, multiple passive dampers may also be provided. Unlike active dampers, the damping effect cannot be variably determined for passive dampers. Passive dampers in the sense of this invention are themselves known standard, freewheel, spring piston, hydraulic and / or air shock absorber, and / or suspension strut.

[0028] The machine according to claim 11 enables an advantageous arrangement of at least one damper, particularly in a washing machine, because at least one damper supports a second component on its underside, the second component being suspended in a vibratory manner. The underside is understood as the region on the outer side of the second component, whose normal vector has a downward vertical component. The second component is particularly the washing tub in a washing machine.

[0029] Alternatively or additionally, in the machine according to claim 12, at least one damper may be hinged to the upper side of the second component. The upper side is understood as a region on the outer side of the second component whose normal vector has an upward vertical component. Specifically, the second component is hinged to at least one damper.

[0030] The machine according to claim 13 can reliably dampen vibrations (particularly those caused by imbalance of the clothes roller, i.e., in the radial direction relative to the axis of rotation of the clothes roller and / or in the axial direction of the axis of rotation).

[0031] The machine according to claim 14 ensures a sufficient number of dampers to reliably dampen the relative movement of the components.

[0032] The damper assembly in the machine according to claims 15 and 16 ensures reliable motion damping in all spatial directions.

[0033] The features pointed out in the patent claims and the features pointed out in the following embodiments of the damper device according to the invention are each suitable for further developing the subject matter according to the invention, individually or in combination with each other. The corresponding combinations of features do not imply any limitation on other embodiments of the subject matter of the invention, but are merely exemplary in nature. Attached Figure Description

[0034] Other features, advantages, and details of the invention will become apparent from the following description of embodiments based on the accompanying drawings, wherein:

[0035] Figure 1 A washing machine having a damper assembly according to the invention is shown in a schematic side view.

[0036] Figure 2 It shows according to Figure 1 Front view of the washing machine

[0037] Figure 3 A perspective view of a switchable damper according to a first embodiment is shown.

[0038] Figure 4 It shows according to Figure 3 The longitudinal section of section line IV-IV in the middle,

[0039] Figure 5 It shows Figure 3 A three-dimensional diagram of the damper setting components.

[0040] Figure 6 It shows according to Figure 3 A three-dimensional diagram of the piston of the damper.

[0041] Figure 7 A partial cross-sectional perspective view of the piston and setting member in a locked configuration is shown.

[0042] Figure 8 It shows according to Figure 3 A 3D diagram of the damper switching actuator.

[0043] Figure 9 The basis for the locked configuration is shown. Figure 3 A partial cross-sectional perspective view of the damper.

[0044] Figure 10 It shows the corresponding Figure 9 A diagram of a damper in an inertial forward configuration.

[0045] Figure 11 A perspective view of a friction damper including a friction device according to another embodiment is shown.

[0046] Figure 12 It shows the corresponding Figure 11 A partial diagram exposing the friction damper of the friction device.

[0047] Figure 13 It shows according to Figure 11 The longitudinal cross-sectional view along section line XIII-XIII is used to illustrate the friction device in the first adjustment position.

[0048] Figure 14 The diagram shows a second adjustment position that corresponds to a position different from the first adjustment position. Figure 13 The view,

[0049] Figure 15 It shows Figure 12An enlarged three-dimensional diagram of the friction liner carrier in the friction device.

[0050] Figure 16 It shows according to Figure 15 Side view of the adjustment component.

[0051] Figure 17 It shows according to Figure 16 The longitudinal section view of section lines XVII-XVII in the diagram.

[0052] Figure 18 It shows according to Figure 12 An enlarged 3D diagram of the adjusting components of the friction device.

[0053] Figure 19 It shows according to Figure 18 Side view of the adjustment component.

[0054] Figure 20 It shows according to Figure 19 The view with arrow XX in the middle,

[0055] Figure 21 It shows according to Figure 12 A three-dimensional magnified detail of the friction pads of the friction device.

[0056] Figure 22 A longitudinal cross-sectional view of a damper with magnetorheological fluid according to another embodiment is shown.

[0057] Figure 23 A longitudinal cross-sectional view of a damper in the form of a hydraulic damper with an extended piston rod, according to another embodiment, is shown.

[0058] Figure 24 It shows the corresponding Figure 23 An illustration of a piston rod being pushed in.

[0059] Figure 25 It shows Figure 23 Enlarged detailed view of the guide and sealing unit of the damper in the middle.

[0060] Figure 26 It shows according to Figure 25 A half-section perspective view of the guide and sealing unit.

[0061] Figure 27 A side view of a damper with an axially movable inertial forward stop element according to another embodiment is shown.

[0062] Figure 28 It shows the corresponding Figure 27 An illustration of a damper in a partially exposed form.

[0063] Figure 29It shows according to Figure 27 A side view of the damper's adjustment mechanism, wherein the inertial forward stop element is arranged in the extended position.

[0064] Figure 30 It shows according to Figure 29 The sectional view of section line XXX-XXX in the diagram.

[0065] Figure 31 It shows the corresponding Figure 29 The diagram shows the inertial forward stopping element positioned in the retracted position, and...

[0066] Figure 32 It shows according to Figure 31 The sectional view of section line XXXII-XXXII in the diagram. Detailed Implementation

[0067] Figure 1 and Figure 2 The drum washing machine 1 shown in the diagram has a vibrating washing unit 2, which has a drive motor 3 that drives a clothes drum 4 about a rotation axis 6 via a belt drive 5. The clothes drum 4 is arranged in a washing tub 7 and can be driven to rotate about the rotation axis 6. For simplicity, other components connected to the washing unit 2, such as the transmission mechanism, are not shown. The vibrating washing unit 2 is suspended from the washing machine housing 9 by two suspension members 8 designed as helical tension springs, which are supported and connected to the washing machine frame 10 erected on the ground. On one hand, the suspension members 8 are attached to a first hanging ring 11 arranged in the upper region of the washing unit 2. On the other hand, the suspension members 8 are suspended from a second hanging eye 12 formed on the washing machine housing 9. The washing machine housing 9 is covered by a cover plate 13.

[0068] On the lower side of the washing unit 2, two dampers 14 are centrally mounted in the washing machine housing 9 along the rotation axis 6 and connected to the washing machine frame 10. For example, the central longitudinal axis 16 of the dampers 14 is arranged in a common plane, which is, for example, perpendicular to the rotation axis 6. The dampers 14 may also be arranged in different planes. In particular, the different damper planes are oriented parallel to each other. These planes may also be oriented at an angle to each other. In particular, these planes are arranged at a certain distance from each other along the rotation axis 6.

[0069] As a supplement to or alternative to the damper 14, it is also possible to arrange the damper on the front face of the washing tub 7 facing the flap 24 and / or the rear face away from the flap 24. The damper arranged on the end face of the washing tub 7 can be fastened to the washing machine frame 10 and / or the washing machine housing 9, especially to the side wall of the washing machine housing 9.

[0070] Specifically, more than two dampers 14 may be provided. According to the illustrated embodiment, the dampers 14 have the same design, and in particular, each has the same damping effect, i.e., friction. It is conceivable that the dampers 14 may be designed differently, particularly having different damping effects, i.e., friction. Importantly, at least one of the dampers 14 is an active damper. The other dampers may be passive dampers.

[0071] Specifically, as a supplement to or alternative to the suspension component 8, the damper 14 can be provided on the upper side of the washing tub 7.

[0072] At its free end, plunger 17 has a first fastening member 18, by means of which damper 14 is attached to a first bearing 19 on washing unit 2 in a manner that allows it to pivot relative to washing unit 2 about a first pivot axis 20. A second fastening member 21 is attached to the free end of housing 15, by means of which damper 14 is attached to a second bearing 22 on washing machine frame 10 in a manner that allows it to pivot relative to washing machine frame 10 about a second pivot axis 23. Clothes are fed in and removed via flaps 24 arranged on washing unit 2.

[0073] The damper 14 communicates with the adjustment unit 25 to adjust the damping effect of the damper 14.

[0074] The signal connection between damper 14 and adjustment unit 25 can be wired or wireless. For illustrative purposes, in Figure 1 The signal connection is not shown in the diagram.

[0075] In addition, a determining unit 26 is provided. The determining unit 26 is used to determine at least one input variable. The determining unit communicates with the adjusting unit 25 via signal communication. This signal connection can be wireless or wired, and... Figure 1 Not shown in the diagram. The determining unit 26 may have one or more sensors (not shown) and / or communicate signals with them to determine the vibration behavior of components that can move relative to each other, i.e., the vibration behavior of the washing unit 2 relative to the machine frame 10.

[0076] Specifically, at least one damper-external sensor is provided, which is specifically designed as an acceleration sensor, light barrier, force sensor, frequency sensor, and / or displacement sensor. Alternatively, a sensor integrated into the damper 14 may be provided, which can be designed as a magnetic displacement sensor, optical sensor, force sensor, frequency sensor, and / or a flow sensor for the hydraulic damper.

[0077] Alternatively, the determining unit 26 may communicate with the drive motor 3 to determine the current characteristic variables of the drive motor 3, particularly its performance, especially the motor current and / or speed.

[0078] The adjustment unit 25 is designed to generate an adjustment signal based on at least one input variable and transmit it to at least one damper 14. The adjustment unit 25 is specifically designed to be independent of, i.e., autonomous to, the equipment control system of the drum washing machine 1. Optionally, the adjustment unit 25 and / or the determining unit 26 may be integrated into the washing machine control system. The damper 14 is designed to actively and variably limit the damping effect based on the received adjustment signal in a manner that improves the vibration behavior of the drum washing machine 1.

[0079] The damper 14, adjustment unit 25, and determining unit 26 form a damper assembly that improves the vibration behavior of the washing unit 2 in the drum washing machine 1. This damper assembly can also be used in other machines. In particular, this damper assembly can be used independently of the drum washing machine 1.

[0080] The function of the damper assembly in the drum washing machine 1 will be described in detail below. During the operation of the drum washing machine 1, the washing unit 2 is set to vibrate. The vibration of the washing unit 2 relative to the washing machine frame 10 is damped by the damper 14.

[0081] During the operation of the drum washing machine, the input variables are determined by the determining unit 26, and are continuously determined, and transmitted to the adjusting unit 25. The adjusting unit 25 generates adjusting signals from the input variables, and these adjusting signals are transmitted to at least one damper 14. In the case of the damper 14 or the damper 14 receiving the adjusting signals, the damping effect is actively and variably determined to ensure improved damping effect.

[0082] In the following text, refer to Figures 3 to 10 The first embodiment of the damper 14 is explained in more detail. The damper 14 is a switchable damper used in the drum washing machine 1 to dampen the imbalance of the clothes drum 4.

[0083] The damper 14 is designed as a friction damper. Each friction damper has a cylindrical housing 15 with a central longitudinal axis 16, in which a plunger 17 is guided for coaxial movement.

[0084] For a more detailed explanation of the structure and function of the damper 14 below, please refer to DE102016207809A1.

[0085] The damper 14 includes a generally cylindrical housing 15 having a central longitudinal axis 16. A generally cylindrical plunger 17 is arranged coaxially with the central longitudinal axis 16, and is displaceable relative to the housing 15 along the central longitudinal axis 16. The plunger 17 may also have a solid cross-section. The plunger 17 has a first end disposed within the housing 15 and a second end extending out of the housing 15. At the second end away from the housing 15, the plunger 17 has a first fastening member 18. The first fastening member 18 has a through sleeve 27 whose axis is oriented perpendicular to the central longitudinal axis 16.

[0086] At the end of the damper 14 opposite to the first fastening member 18, the housing includes a second fastening member 21, which is substantially the same in design as the first fastening member 18 and includes a through sleeve 27. The first fastening member 18 is fixedly connected to the plunger 17. The second fastening member 21 is fixedly connected to the housing 15. In particular, the second fastening member 21 is attached to the end face of the guide portion 28 of the housing 15.

[0087] With the help of fastening members 18 and 21, damper 14 is arranged in the washing machine, particularly between its frame and the washing drum, in order to dampen the movement of the washing drum relative to the frame, especially the movement caused by imbalance during rotation.

[0088] The housing 15 consists of several parts, and includes Figure 4 The switching housing component 29 and the friction damping housing component 30, detachably connected thereto, are shown on the right side. The switching housing component 29 and the friction damping housing component 30 are arranged one after the other along the central longitudinal axis 16. At the end face opposite to the second fastening member 21, the switching housing component 29 is connected to the friction damping housing component 30. This connection can be achieved by corresponding locking members 31.

[0089] At the end of housing 15 facing the first fastening member 18, the friction damping housing component 30 is closed by a guide cover 32. The guide cover 32 has a central guide opening 33 through which the plunger 17 is guided into the interior space of housing 4. The guide cover 32 has at least one locating web 34 extending along the central longitudinal axis 16, which engages in a recess 35 provided for this purpose on housing 15, particularly on the friction damping housing component 30. The locating web 34 definitively fixes the rotational position of the guide cover 32 relative to housing 15. The locating web 34 also serves to protect the guide cover 32 from rotation about the central longitudinal axis 16 relative to housing 15.

[0090] Four cover inertia-stopping elements 37 are integrally formed on the guide cover 32 on the inner side of the end face 36. The cover inertia-stopping elements 37 are oriented parallel to the central longitudinal axis 16 and arranged in an arc segment around the plunger 17 in a plane perpendicular to the central longitudinal axis 16. Specifically, the guide cover 32 is made of an elastic material, particularly plastic. More or fewer than four cover inertia-stopping elements 37 may be provided. The cover inertia-stopping elements 37 are spaced apart from each other, particularly equidistant, in the tangential direction relative to the central longitudinal axis 16. There is a certain distance between two adjacent cover inertia-stopping elements 37.

[0091] A housing bottom 38 is integrally formed on the end face of the friction damping housing component 30 opposite to the guide cover 32. The housing bottom 38 is oriented perpendicular to the central longitudinal axis 16. From the housing bottom 38, for example, four bottom inertia advance stops 39 extend in the direction of the guide cover 32. The bottom inertia advance stops 39 are oriented parallel to the central longitudinal axis 16 and are designed to correspond to the cover inertia advance stops 37. A guide portion 28 is integrally formed on the housing bottom 38 opposite to the bottom inertia advance stops 39. The guide portion 28 is used to guide the plunger 17 during axial displacement within the housing 15. The inner diameter of the guide portion 28 substantially corresponds to the outer geometry of the plunger 17. At the end opposite to the plunger 17, a second fastening member 21 is arranged on the guide portion 28. The guide portion 28 passes through the switching housing component 29 and the second fastening member 21 is as follows: Figure 3 and Figure 4 The right side of the middle section shows the protrusion at the rear end of the housing 15.

[0092] The friction unit, including piston 41, is arranged in the housing 15, particularly in the friction damping housing component 30. Piston 41 is a generally hollow cylinder. Piston 41 is movable within the housing 15 along the central longitudinal axis 16 and relative to the plunger 17. Piston 41 is arranged radially between the plunger 17 and the housing 15 along the central longitudinal axis 16.

[0093] The piston 41 has an inner annular groove in which a friction liner 42 is disposed. The friction liner 42 is part of the friction unit. The friction liner 42 is received in such a way that it is guided through the piston 41. Movement of the piston 41 along the central longitudinal axis 16 causes displacement of the friction liner 42. The friction liner 42 is specifically designed as a friction strip, the end face of which may be flat or uneven, such as serrated, corrugated, or other shapes. The annular friction liner 42 rests against the outer side of the plunger 17 with an inner cylindrical friction surface. The relative movement between the plunger 17 and the friction liner 42 results in a frictional force to resist the movement, i.e., frictional damping.

[0094] The inner groove of piston 41 is constrained on both sides in the axial direction by guide plates 43. The guide plates 43 are integrally formed with piston 41. In contrast to the inner groove, the guide plates 43 protrude radially inward relative to the central longitudinal axis 16. The guide plates 43 are designed as annular segments in a plane perpendicular to the central longitudinal axis 16. The inner contour defined by the guide plates 43 substantially corresponds to the outer contour of plunger 17, wherein the inner contour within the region of the guide plates 43 is larger than the outer contour of plunger 17 in order to prevent direct contact between piston 41 and plunger 17.

[0095] Four guide plates 43 are provided at each end face of the piston 41. The guide plates 43 are designed to extend tangentially to their central longitudinal axis 16, such that the guide plates 43 respectively adapt to the spaces between the cover inertial forward stop members 37 and the bottom inertial forward stop members 39. Figure 2 The diagram shows the damper, with piston 41 arranged adjacent to guide cap 32. Guide web 43 facing guide cap 32 accommodates the gap between adjacent cap inertia advance stops 37. This prevents accidental rotation of piston 41 relative to housing 15. Regarding their tangential position, the four cap inertia advance stops 37 are arranged rotated 45° relative to bottom inertia advance stops 39. Due to the space between the two guide webs 43, friction linings 42 are exposed in the piston 41 in the axial direction of the central longitudinal axis 16 in at least some areas. This exposed area of ​​friction lining 42 can be close to either the cap inertia advance stops 47 or the bottom inertia advance stops 39 on the end face. Friction lining 42 acts as a stop damper.

[0096] The damper 14 also has a switching unit 44 capable of switching between a locked configuration and an inertial forward configuration of the piston 41. The switching unit 44 includes a switching actuator 49 having a switching driver 45. According to the illustrated embodiment, the switching driver 45 is designed as a lifting solenoid that generates linear lifting motion triggered by an electrical switch.

[0097] The lifting solenoid is attached to the housing 15 of the damper 14 with its linear lifting axis 46 oriented parallel to the central longitudinal axis 16 of the damper. In the area of ​​the switching housing component 29 where the lifting solenoid is arranged, the housing 15 is non-circular, i.e., deviates from a cylindrical shape. The lifting solenoid is connected to the setting ring 48 via a force transmission member 47. The switching actuator 45, the force transmission member 47, and the setting ring 48, as switchable lifting solenoids, form a switching actuator 49, such as... Figure 8As shown. The force transmission member 47 is designed as a flexible wire, specifically guided along a rigid guide channel. The force transmission member is engaged, in particular, substantially radially, with the spring force movement overcome by means of an energy storage member in the form of a spring member 50. The set ring 48 has two openings 51 eccentrically arranged relative to the central longitudinal axis 16, in which a sleeve-shaped set member 52 with an end face engaging the web 53 engages. The set member 52 is a component of the switching unit 44. In particular, the switching unit 44, in the form of the set member 52, achieves a form-fit connection with the piston 41 in the locking configuration and release of the piston 41 in the inertial forward configuration. For this purpose, the set member 52 has a radial pin on the inner side of the inner cylinder liner surface, which serves as an outer profile member 54, engaging a meshing outer profile member 55 on the profile link. The meshing outer profile member 55 is integrally formed on the outer surface of the generally cylindrical piston 41. According to the illustrated embodiment, two outer profile connecting rods are disposed on the piston 41, wherein each outer profile connecting rod has two interlocking outer profile members 55. Each interlocking outer profile member 55 is substantially U-shaped, wherein the parallel legs of the U-shape extend circumferentially about the central longitudinal axis 16 in the mounted state of the piston 41. The outer profile connecting rods are arranged diametrically opposite to each other on the outside of the piston 41 relative to the central longitudinal axis 16. The respective openings of the U-shapes are oriented circumferentially about the central longitudinal axis 16.

[0098] The function of the friction damper 14 will be explained in more detail below. According to... Figure 9 The damper 14 is located in a locked configuration, as shown in the configuration of the setting member 52. In the locked configuration, the outer profile member 54 is located in one of the meshing outer profile members 55. The U-shaped parallel legs of the meshing outer profile member 55 form a notch in a direction parallel to the central longitudinal axis 16. The displacement of the piston 41 relative to the housing 15 and / or the plunger 17 is blocked. The relative displacement of the plunger 17 relative to the housing 15 is caused by friction due to the friction lining 42, which abuts against the plunger 17 radially and is blocked axially. In this configuration, the friction damping function of the damper 14 is switched to enabled, i.e., activated.

[0099] To switch the damper 14 to an inertial forward configuration, the switching unit 44 is activated by actuating the switching actuator 49. By switching the lifting solenoid 45, the force transmission member 47 engaging the lifting solenoid 45 is displaced along the lifting axis 46. The force transmission member 47 is radially supplied to the set ring 48 along a curved guide channel. The force transmission member 47 applies a torque about the central longitudinal axis 16 to the set ring 48, causing the set ring 48 to rotate about the central longitudinal axis 16. The set member 52, held in the opening 51 of the set ring 48 by the engaging web 53, rotates with the set ring 48. Due to the rotation of the set member 52, the outer profile member 54 rotates relative to the piston 41, plunger 17, and housing 15 about the central longitudinal axis 16. The outer profile member 54 is disengaged from the meshing outer profile member 55. Figure 10 The image shows the inertial forward configuration of the damper. In this configuration, the outer profile member 54 is spaced apart from the meshing outer profile member 55 in the circumferential direction, i.e., in the tangential direction, relative to the central longitudinal axis 16. The piston 41 is released by the setting member 52. In this configuration, the piston 41 is movable relative to the housing 15 and relative to the plunger 17 along the central longitudinal axis 16.

[0100] In order to switch the damper 14 back to the locked configuration, the lifting solenoid 45 is switched in the opposite direction, so the setting member 52 will rotate in the opposite direction around the central longitudinal axis 16.

[0101] The spring member 50 is part of a safety device that allows the switching unit 54 to switch again in the event of a power failure. For this purpose, a capacitor (not shown) is provided, which stores sufficient electrical energy to switch the lifting solenoid 45 in the event of a power outage. The movement of the lifting solenoid 45 is mechanically stored in the spring member 50.

[0102] The two meshing outer contour members 55 of the outer contour link are spaced apart from each other along the central longitudinal axis 16, which allows the piston 41 to be locked in multiple positions along the central longitudinal axis 16 by means of the setting member 52 and its outer contour member 54. In particular, an insertion chamfer may be provided on the meshing outer contour member 55 along the rotation direction of the setting member 52 to facilitate the insertion of the outer contour member 54 into the meshing outer contour member 55 even if the arrangement is not precise (i.e., if the outer contour member 54 is not precisely aligned with the meshing outer contour member 55).

[0103] Other embodiments of the outer contour member 54 and the meshing outer contour member 55 are also conceivable. According to an embodiment not shown, the outer contour member 54 may, for example, be wedge-shaped, which can engage in a locking manner with a wedge tip in one of a plurality of serrated recesses on the outer contour link, particularly the plurality of serrated recesses corresponding to the wedge tip. Specifically, at least five, particularly at least ten, particularly at least twenty corresponding recesses may be provided on the outer contour link to allow engagement of the wedge tip. This allows the outer contour member to be engaged in a meshing outer contour member substantially independently of the axial positioning of the piston 41.

[0104] Friction lining 42 can also be arranged on the outside of piston 41. In this case, meshing profile member 55 is implemented on the inside of piston 41. Then, profile member 54 will be arranged between plunger 17 and piston 41.

[0105] Other designs for the damper 14 are also possible, among which other designs for the switching actuator 49 are particularly conceivable. The switching actuator 49 may have a switchable rotating solenoid as a switching driver, also known as a plunger coil or voice coil. This rotating solenoid enables the active component to rotate relative to the static passive component. This type of damper has a particularly compact design.

[0106] In the following text, refer to Figures 11 to 21 Another embodiment of the invention is described below. Components that are structurally identical are given the same reference numerals as those in the first embodiment, and their description is incorporated herein by reference. Components that are structurally different but functionally similar are given the same reference numerals and the suffix "a".

[0107] exist Figures 11 to 14 The damper 14a shown has a housing 15 with a central longitudinal axis 16. For the structure and function of the damper 14a, see DE 102016225036 A1.

[0108] The housing 15 is formed of a first housing member, which is designed as an outer tube, and a first fastening member 18 is attached to the first housing member. The first fastening member 18 can be used to fasten the damper 14a to a component. At the end facing the first fastening member 18, the first housing member is closed. At the end opposite to the first fastening member 18, the first housing member is open. Through this opening, a second housing member, in the form of an inner tube, is inserted into the first housing member. The second housing member forms a plunger 17.

[0109] At the end opposite to the first housing member, the second housing member is closed. A second fastening member 21 is provided at the closed end of the second housing member, by which the damper 14a can be fastened to another component. The fastening members 18 and 21 are, for example, designed with fastening eyes for insert sleeves oriented transversely to the central longitudinal axis 16. The housing members can be displaced relative to each other along the central longitudinal axis 16. A guide member 58 is provided at the open end of the first housing member to guide the displacement of the second housing member.

[0110] According to the illustrated embodiment, the housing components are all designed as cylindrical tubes. In particular, it is also conceivable that the housing components have a non-circular profile in a plane perpendicular to the central longitudinal axis 16. For example, the housing components may be designed as square, rectangular, or elliptical tubes. In this design, shape fit prevents rotation of the housing components relative to the central longitudinal axis 16.

[0111] The damper 14a also includes a pull-out protection device that prevents the second housing member 6 from being unintentionally pulled far out of the first housing member. According to the illustrated embodiment, pull-out protection is ensured by the fact that a radially inwardly projecting profile member 59 is disposed on the first housing member and arranged along a circular line around the central longitudinal axis 16. The profile member 59 is joined within the first housing member behind a guide member 58. The guide member 58 is axially and radially fixed to the first housing member relative to the central longitudinal axis 16. The guide member 58 projects radially inward on the first housing member relative to the central longitudinal axis 16.

[0112] According to the illustrated embodiment, the friction unit is attached to the second housing member, i.e., to the inner tube. The friction unit includes a friction pad carrier 60, an adjustable friction pad 42a disposed on the friction pad carrier 60, and an adjustment member 61 for adjusting the friction pad 42a on the friction pad carrier 60. The friction unit is fixed to the second housing member along the axial direction of the central longitudinal axis 16 and with respect to rotation about the central longitudinal axis 16. According to the illustrated embodiment, the attachment of the friction unit to the second housing member is achieved through a notch 62 on the inner tube for clamping the friction pad carrier 60.

[0113] The friction unit protrudes radially from the central longitudinal axis 16 on the second housing member. The guide member 58 forms a removal stop for the second housing member because the radially protruding annular shoulder 65 of the guide member 58 prevents axial displacement of the friction unit, and in particular the friction carrier 60.

[0114] The following reference Figures 15 to 17The structure of the friction lining carrier 60 is explained in more detail. The friction lining carrier 60 is, for example, a single piece made of plastic. The friction lining carrier 60 employs a substantially hollow cylindrical design with a pin-shaped anchoring portion 63, by which the friction lining carrier 60 is inserted at its end face into the inner tube of the second housing member. The anchoring portion 63 has a circumferential inner groove 64, in which a notch 62 engages to hold the friction lining carrier 60 onto the second housing member. In the region of the anchoring portion 63, the friction lining carrier 60 has a first outer diameter D1, which substantially corresponds to the inner diameter of the inner tube of the second housing member.

[0115] The friction lining carrier 60 has a radially protruding annular shoulder 65 adjacent to the anchoring portion 63, through which the friction lining carrier 60 rests against the annular end face of the second housing member. The friction lining carrier 60 is axially supported on the inner tube of the second housing member via the annular shoulder 65.

[0116] The carrier portion 66 is axially adjacent to the annular shoulder 65. The carrier portion 66 has a second outer diameter D2 that is larger than the first outer diameter D1. The second outer diameter D2 substantially corresponds to the inner diameter of the outer tube of the first housing member. The carrier portion 66 has a plurality, particularly at least one, window-shaped radial recess 67 along its outer circumference, and according to the illustrated embodiment, exactly four such recesses 67. Two adjacent radial recesses 67 are spaced apart from each other by an axial web 68. On the end face, the friction liner carrier 60 has an annular web 80 in the region of the carrier portion 66.

[0117] The friction liner carrier 60 has a through hole 69 along the axial direction. In the region of the anchoring portion 63, the through hole 69 is designed with an adjusting slot 70 as a moving thread. In the transition region from the anchoring portion 63 to the carrier portion 66, the through hole 69 is designed as a truncated conical support portion 71.

[0118] The following reference Figures 18 to 20 The adjusting member 61 is explained in more detail. The adjusting member 61 has an adjusting pin 72. This adjusting pin 72 has an external thread corresponding to the internal thread of the adjusting slot 70. The adjusting member 61, together with the adjusting pin 72, is arranged on the adjusting slot 70 of the friction liner carrier 60 so that it can be adjusted along the adjusting direction 73. The adjusting direction 73 corresponds to the axial direction of the friction liner carrier 60.

[0119] The friction unit is arranged in the damper 14a with the adjustment direction 73 oriented toward the central longitudinal axis 16.

[0120] A pressing portion 74 is provided adjacent to the adjusting pin 72, which has a tapered, widened profile starting from the adjusting pin 72. At the outer end, the adjusting member 61 has a contact member 75, by means of which the adjusting member 61 can abut against the friction liner carrier 60 at the end to limit the adjustment.

[0121] An actuating part 76 is provided at the end face of the contact member 75, and the actuating part 76 is designed as an eccentrically arranged groove-shaped recess.

[0122] The following reference Figure 21 and Figure 22 The friction liner is explained in more detail. The friction liner 42a is a generally annular disc with a central circular opening 77 through which the adjusting member 61 can be guided. Along its outer circumference, a plurality of radially inwardly projecting recesses 78 are provided on the friction liner 42a, which allow the friction liner 42a to be secured to the axial web 68 of the friction liner carrier 60. This ensures that rotation of the friction liner 42a within the friction liner carrier 60 is prevented. Between each recess 78, the friction liner 42a has a radially projecting friction liner portion 79. The geometry of the friction liner portion 79 substantially corresponds to the size of the opening of the radial recess 67 on the friction liner carrier 60.

[0123] The friction liner 42a may also have multiple friction liner portions 79 that are separated from each other.

[0124] The friction lining 42a can be arranged in the friction lining carrier 60, particularly within the carrier portion 66, such that the friction lining portion 79 protrudes radially outward through the radial recess 67. The friction lining 42a is radially fixed in the direction of rotation about the central longitudinal axis 16 because the axial web 68 engages in the recess 78. The friction lining 42a is axially fixed to the friction lining carrier 60 by a circumferential annular web 80 joined at the rear end face by the friction lining portion 79.

[0125] The following reference Figure 13 The function of the friction damper will be explained in more detail. The friction unit is held in the inner tube by a friction liner carrier 60. The friction liner 42a is inserted into the carrier portion 66 of the friction liner carrier 60, such that the friction liner portion 79 is arranged in the radial recess 67. The adjusting member 61, together with the adjusting pin 72, passes through the opening 77 of the friction liner 42a and is screwed into the external thread on the adjusting slot 70 of the friction liner carrier 60.

[0126] According to the embodiment shown, the outer diameter of the adjusting pin 72 is smaller than the inner diameter of the opening 77. As long as the adjusting member 61 is screwed into the friction lining carrier 60 to a degree so small that the adjusting pin 72 is only arranged within the opening 77, the friction lining 42a will not expand radially.

[0127] By actuating the adjusting member 61 with the actuating member actuating it, torque can be transmitted from the actuating member to the adjusting member 61 when the actuating profile rests against the actuating member 76. The rotational movement of the adjusting member 61 causes axial displacement of the adjusting member 61 due to the adjusting slot 70. The axial displacement of the adjusting member 61 along the central longitudinal axis 16 causes the tapered widening pressing part 74 to gradually advance into the opening 77 of the friction liner 42a.

[0128] Once the outer diameter of the extrusion portion 74 is larger than the inner diameter of the opening 77 of the friction lining 42a, the friction lining 42a is subjected to a radially outward contact force. On one hand, the contact force causes compression of the material used to manufacture the friction lining 42a. Furthermore, the friction lining portion 79 is radially outwardly pressed through the radial recess 67 due to the contact force. The friction lining 42a presses directly against the inner side of the first housing member, i.e., the inner side of the outer tube. Based on the pressure exerted by the friction lining 42a against the inner side of the first housing member, a force is generated when the housing members shift relative to each other along the central longitudinal axis 16.

[0129] This configuration is like Figure 14 As shown, the adjusting member 61 is screwed into the friction liner carrier 60 to its maximum depth. The adjusting member 61 rests against the annular web 80 of the friction liner carrier 60 with its contact member 75 on its end face. This prevents further axial displacement of the adjusting member 61 along the central longitudinal axis 16. In this configuration, further axial displacement is also prevented by the adjusting member 61 resting against the support portion 71 by the pressing portion 74. The support of the adjusting member 61 on the friction liner carrier 60 is secure. The maximum screw-in depth is securely set.

[0130] exist Figure 14 In the configuration shown, the maximum contact force is transmitted from the compression section 74 to the friction liner 42a. In this configuration, the frictional effect of the damper 14a is maximized.

[0131] It is also conceivable to provide an assembly known as an expansion piston in the damper 14a, which includes an adjustment member 61, through which the friction lining 42a can be radially displaced relative to the central longitudinal axis 16.

[0132] According to another alternative embodiment, the component can be configured as a longitudinally slotted sleeve, wherein the sleeve body forms a friction liner carrier 60.

[0133] It is also conceivable to install a driver that drives the adjustment of the adjusting member 61 via a motor. This driver is specifically designed in the form of an electric motor and is specifically integrated into the second housing.

[0134] In the following text, refer to Figure 22The third embodiment of the invention is described below. Components that are structurally identical are given the same reference numerals as those in the first two embodiments, and are described herein with reference to those numerals. Parts that are structurally different but functionally similar are given the same reference numerals and the suffix "b".

[0135] A piston 41b is provided at the end of the plunger 17 located in the internal space 81 of the housing 15. The piston 41b is provided with annular recesses 82, and coils 125 wound around the piston 41b are arranged in each annular recess 82. A sleeve 126 of magnetically permeable material is provided on the inner surface of the housing 15 and serves as a pole shoe. The coils 125 that generate the electromagnetic field are connected to the controller via connecting wires 127.

[0136] Friction lining 42b is arranged on the outside of piston 41b, and is substantially cylindrical, and particularly annular-cylindrical.

[0137] Friction pad 42b is made of an open-cell foam material, such as polyurethane or polyamide. The foam material serves as the holding medium for the magnetorheological fluid, such as those known from US5,382,373 or US5,578,232. The basic structure of a magnetorheological friction damper used in a friction damper is known from WO 99 / 22162A1, and its description is explicitly cited.

[0138] In the following text, refer to Figures 23 to 26 The fourth embodiment of the present invention is described below. Components that are structurally identical are given the same reference numerals as those in the foregoing embodiments, and reference is made herein to the description of the foregoing embodiments. Parts that are structurally different but functionally similar are given the same reference numerals and the suffix "c".

[0139] In the following text, refer to Figures 23 to 26 This describes another embodiment of the invention. For the structure and function of the damper 14c, see DE 102011080962 A1. The damper 14c is in the form of a hydraulic damper and has a substantially hollow cylindrical inner shell 83 and an outer shell surrounding the inner shell 83, which forms the shell 15 of the damper 14c. According to the illustrated embodiment, the two shells 83 are formed as tubular portions. The damper 14c is referred to as a double-tube damper.

[0140] like Figure 23As shown on the left, the inner housing 83 is closed at the first housing end 85 by a guiding and sealing unit 86 to guide and seal the piston rod extending from the first housing end 85. The piston rod forms a plunger 17. At the second housing end 88, opposite to the first housing end 85, the inner housing 83 is closed by an annular housing cover 89 having a bottom valve 90. The inner housing 83, the guiding and sealing unit 86, and the housing cover 89 substantially surround a working space 91 filled with damping fluid 92. Coaxially with the central longitudinal axis 16, a piston 41c is arranged in the inner housing 83 and slidably guided along the central longitudinal axis, and the piston 41c is attached to the first piston rod end 93. The piston 41c divides the working space 91 into a first working space 94 facing the first housing end 85 and a second working space 95 facing the second housing end 88. A first fastening member 18 in the form of a cylindrical through-hole is integrally formed on the second piston rod end 96 arranged outside the damper 1.

[0141] The outer casing has a circular cross-section and surrounds the inner casing 83. A first casing end 85 is flanged to form a casing stop 97, which defines a casing opening 98 through which a piston rod is guided. A second casing end 88 opposite to the first casing end 85 is closed by a casing bottom 99 integrally formed with the outer casing. The casing bottom 99 can also be attached to the outer casing as a separate, particularly multi-part, component. On the side facing the inner casing 83, the casing bottom 99 is provided with, for example, a stepped casing bottom recess 100 for receiving a bottom valve 90. A second fastening member 21 is formed to or attached to the side of the casing bottom 99 away from the inner casing 83, wherein the second fastening member 21 is substantially centrally aligned with respect to the central longitudinal axis 16. The inner casing 83 and the outer casing are arranged coaxially with respect to the central longitudinal axis 16 such that the compensation space 101 is formed in the shape of an annular gap. The compensation space 101 has a constant width along its circumference. The damper 14c may also include at least one housing having a non-circular, generally elliptical cross-section, which is offset relative to another housing 83 such that the compensation space 101 is formed in the shape of an annular gap with an elliptical cross-section. The compensation space 101 may further extend into the recess 100 at the bottom of the housing. The compensation space 101 may be pressurized and partially filled with a damping fluid 92, such as oil, or a gas such as nitrogen.

[0142] To secure the inner housing 83 to the outer housing in the region of the first housing ends 85, 88, the guiding and sealing unit 86 has a guide housing 102 and a guide shield 103. The guide shield 103 is arranged in a recess in the guide housing 102 for this purpose. The guide housing 102 is stepped along the central longitudinal axis 16 and is arranged within the inner housing 83 with the inner housing step sealed. Using the outer housing step, the guide housing 102 is circumferentially sealed to the outer housing and supported along the central longitudinal axis 16 by a gasket 104 on the housing stop 97. At the end face of the first housing end 85 facing the outer housing, the guide housing 102 has a recess into which a sealing member 105 is inserted. The sealing member 105 is used to guide the piston rod out of the damper 14c in a sealed manner. The recess in the guide housing 102 is selected to be larger than the sealing member 105 arranged therein, such that the pressure chamber 106 is defined by the guiding and sealing unit 86, the sealing member 105, and the piston rod.

[0143] Additionally, a valve ring (not shown) may be provided between the guide housing 102 and the guide shield 103. The valve ring prevents fluid from flowing from the working space 91 into the pressure chamber 106, particularly when the piston rod moves in the pull-out direction 107. When the piston rod moves in the push-in direction 108, fluid can be allowed to flow from the working space 91 into the pressure chamber 106.

[0144] The guide housing 102 has a shoulder 124 on which the inner housing 83 is supported in the axial direction, i.e., along the central longitudinal axis 16. In the region of the second housing end 88, the inner housing 83 is fastened to the outer housing by a housing cover 89, which is annular and rests against the second housing end 88 such that a housing cover stop protrudes radially beyond the inner housing 83. To receive the bottom valve 90, the housing cover 89 has a housing cover hole arranged coaxially with the central longitudinal axis 16, which is incorporated into the annular housing cover recess. The bottom valve 90 allows fluid to flow from the compensation space 101 into the working space 91, and in particular, into the second part of the working space 95.

[0145] The piston rod has a reduced diameter at its first piston rod end 93, thereby forming a piston rod stop 109. Starting from the piston rod stop 109, a first piston rod washer 110, a first sealing member 111 in the form of a disc spring, a piston disc 112, a second sealing member 113 in the form of a disc spring, a second piston rod washer 114, and a piston rod locking nut 115 are arranged on the first piston rod end 93. The piston rod locking nut 115 is screwed onto the piston rod thread and secures the piston 41c to the piston rod. The piston 41c is formed by the first sealing member 111, the piston disc 112, the second sealing member 113, and a piston seal ring 116. The piston seal ring 116 is annular and is arranged in a piston groove provided for this purpose in the piston disc 112. The piston groove is formed in the outer wall of the piston disc 112 facing the inner housing 83. The piston seal ring 116 seals the piston disc 112 to the inner housing 83.

[0146] The first closing member 111 functions as the piston rod moves along the thrust direction 108 and is hereinafter referred to as a compression disc spring. The second closing member 113 functions in the pull-out direction 107 and is hereinafter referred to as a tension disc spring. The tension disc spring 113 cooperates with a plurality of pull flow channels (not shown), and the compression disc spring 111 cooperates with a plurality of pressure flow channels (not shown). Each flow channel includes a transverse channel extending transversely to the central longitudinal axis 16 and a longitudinal channel connected to the transverse channel and extending along the central longitudinal axis 16. The flow channels are formed in the piston disc 112 and provide a connection between a first working space 94 and a second working space 95. As seen along the thrust direction 108, the pull flow channel may consist of a longitudinal channel and an adjacent transverse channel. Conversely, the pull flow channel may consist of a transverse channel and an adjacent longitudinal channel. The longitudinal channels of the pull flow channels may be arranged in the piston disc 112 such that they can be closed by the elastically deformable tension disc spring 113. Accordingly, the longitudinal channels of the pressure flow passages can be arranged in the piston disc 112 such that they can be closed by elastically deformable compression disc springs 111. As the piston 41c moves in the pull-out direction 107 or the push-out direction 108, the flow passages can each have an effective flow cross-sectional area, which can be changed by closing one or more flow passages. The effective flow cross-sectional area is understood to refer to the cross-sectional area of ​​the flow passages that are effective for the damping force-velocity characteristics of the damper 14c, where the cross-sectional area of ​​the flow passages along them can be arbitrary. Therefore, the effective flow cross-sectional area should be understood as the final cross-sectional area of ​​the flow passages.

[0147] The damper 14c has a preferred mounting position such that the propulsion direction 108 is the same as the direction of gravity. The damper 14c is mounted on the element to be damped such that the piston rod is fastened to the moving part to be damped by the first fastening member 18. This means that the damper 14c is substantially perpendicularly aligned with its central longitudinal axis 16, wherein in this mounting position, the piston rod with the first fastening member 18 is arranged above.

[0148] The guiding and sealing unit 86 is arranged in the housings 83, 84 of the damper 14c, such that the guide cover 103 faces the working space 91. The guide cover 103 is arranged in a recess 117 of the guide housing 102 provided for this purpose. The guide cover 103 is provided with an end face, a protruding annular ridge 118, and a groove of the guide housing 102 provided therefor. Thus, the guide cover 103 and the guide housing 102 are positioned relative to each other, and in particular, are arranged concentrically relative to the central longitudinal axis 16. The outer cylinder liner surface 119 of the guide cover 103 is provided with an outer groove extending in a spiral form along the central longitudinal axis 16. Thus, the outer cylinder liner surface 119 of the guide cover 103 only partially rests on the inner cylinder liner surface 121 of the guide housing 102. The outer groove 120 allows fluid to flow along a spiral line at the outer periphery of the guide cover 103 to the distribution channel 122. The distribution channel 122 is integrated into the guide housing 102 in a stepped manner, and the outer groove 120 connects to the shoulder 124, wherein the distribution channel 122 extends to the outer cylinder liner surface 123 of the outer housing portion of the guide housing 102. This ensures that the damping fluid 92 can flow from the working space 91 along the outer groove 120 via the distribution channel 122 into the compensation space 101 arranged between the inner housing 83 and the outer housing. The fluid flow is ensured by the fact that the distribution channel 122 is recessed relative to the shoulder supported by the inner housing 83. The outer groove 120 is also referred to as a throttling channel, and according to a first embodiment, it has a semi-circular flow cross-sectional area having a net width d and a length. In this embodiment, the net width d is the diameter of the semicircle. Figure 25 and Figure 26In the illustrated embodiment, the throttling channel 120 at the outer cylinder liner surface 119 of the guide cover 103 is designed as a full-circumferential spiral, i.e., with an opening angle of 360°. This means that the pitch of the spiral corresponds to the width of the guide cover 103. The spiral throttling channel 120 can also have an opening angle other than 360°. Opening angles less than 360° and greater than 360° are also possible. The pitch of the spiral can be different from the width of the guide cover 103. The length of the throttling channel 120 can also be adjusted by changing the width of the guide cover 103, i.e., by changing the dimension of the guide cover 103 along the central longitudinal axis 16. The length l of the throttling channel 120 is greater than the net width d of the throttling channel. Other cross-sectional shapes, such as circular or rectangular, can also be selected for the throttling channel 120. The throttling channel 120 can also have a meandering shape or other arrangements around the central longitudinal axis 16. At least one throttling check valve can be provided in the throttling channel 120 to prevent fluid from flowing from the compensation space 101 into the working space 91.

[0149] The function of damper 14c is described below. Piston 41c has flow passages that can be closed by disc springs 111, 113. When the damper is stationary, disc springs 111, 113 are in contact with the piston, i.e., the flow passages are closed. When the piston rod is actuated, the hydraulic pressure on disc springs 111, 113 increases as the insertion or withdrawal speed increases, particularly until a switching pressure is reached in one of the partial working spaces 94, 95. When this switching pressure is reached, the corresponding disc spring 111, 113 lifts the piston. Fluid flow between the two partial working spaces 94, 95 is unimpeded along the flow passages of piston 41c. This applies when piston 41c is actuated in the pull-out direction 107 and the push-in direction 108. This type of damper 14c has non-progressive damping behavior. The damping force-velocity characteristics are given by the effective flow cross-sectional area of ​​the flow passages.

[0150] The damper 14c can also be implemented as a so-called progressive damper, the working principle of which will be explained below. Figure 23 and Figure 24 The non-operating state of damper 14c is shown. Disc springs 111 and 113 are not against the relevant contact surfaces, and the flow passages are not closed. Specifically, when piston 41c moves at a low speed in the pull-out direction 107 or the push-out direction 108, disc springs 111 and 113 are essentially held in place. Figure 23 , Figure 24The non-operating state is shown. When piston 41c moves, damping fluid 92 can flow through the flow channel. Disc springs 111 and 113 have sufficient clearance between themselves and their respective contact surfaces to allow damping fluid 92 to enter the corresponding other working spaces 94 and 95. In the progressive damper 14c, the disc springs 111 and 113 function in the opposite manner to those in the non-progressive damper 14c; that is, disc spring 111 acts as a tension disc spring and disc spring 113 acts as a compression disc spring. The effective flow cross-sectional area through the flow channel gives the damping force-velocity characteristics at low speeds.

[0151] Below, based on Figure 23 This describes the function of the progressive damper 14c as the piston 41c moves in the thrust direction 108, with a much higher thrust velocity compared to the movement of the piston 41c described above. During the movement of the piston 41c, the damping fluid 92 located in the second working space 95 applies a force to the compression disc spring 113. As the force increases, the compression disc spring 113 gradually elastically deforms and presses against the relevant contact surface of the flow channel, thereby gradually reducing the effective flow cross-sectional area. When sufficient force is applied, the compression disc spring 113 is completely pressed against the contact surface, so that the flow channel is completely closed. In this case, the damping fluid 92 can only flow from the second working space 95 into the first working space 94 through the flow channel. This forces the tension disc spring 111 away from the associated contact surface, thereby allowing the fluid to flow from the second working space 95 into the first working space 94.

[0152] A certain volume of damping fluid 92 discharged from the piston rod flows into the compensation space 101 via the throttling channel 120 and the distribution channel 122. The damping fluid 92 is throttled along the throttling channel 120 because its flow cross-section is reduced compared to the annular cross-section in the first working space 94. Therefore, the throttling channel 120 is essentially independent of the manufacturing tolerances of the piston rod and the guide hole through which the piston rod is guided in the guiding and sealing unit 86. Furthermore, dimensional variations in the manufacturing of the throttling channel 120 are not significant to the damping effect of the damper 14c, as the damping function depends on the volumetric flow rate of the damping fluid 92 through the throttling channel 120. The damping effect is significantly affected by the length of the throttling channel 120, which is greater than the net width d of the throttling channel 120. In particular, the guiding and sealing unit 86 allows flow through the annular gap between the piston rod and the guide hole to not affect the damping effect of the damper 14c.

[0153] By changing the length of the throttling channel 120, for example by changing the width of the guide cover 103 (i.e., its extension along the central longitudinal axis 16), the throttling performance and damping effect of the damper 14c can be changed directly and directly.

[0154] Flow through the annular gap is also permissible. In this case, a small portion of the damping fluid 92 flows into the pressure chamber 106. For this purpose, a valve ring (not shown) can be provided to prevent the damping fluid 92 from entering the pressure chamber 106 without being throttled, where it flows at a fluid pressure p. f This acts on the sealing member 105. This increases the service life of the sealing member 105. A vent (not shown) can also be provided in the pressure chamber 106 to allow the pressure chamber 106 to discharge at a minimum pressure p. e Discharge. Discharge pressure p e Greater than fluid pressure p f .

[0155] When pulling out direction 107 from Figure 24 When the piston rod is actuated, the damping fluid 92 is displaced from the first working space 94 via the piston 41c and flows into the compensation space 101 at the first housing end 85 via the throttling channel 120 and the distribution channel 122. This means that when the damper 14c is actuated in the pull-out direction 107, the damping fluid 92 also passes through the throttling channel 120. At the second housing end 88, the damping fluid 92 is drawn into the second working space 95 via the bottom valve 90 of the inner housing 83. Furthermore, fluid can flow directly from the first working space 94 into the second working space 95 through the through-hole in the piston disc 112.

[0156] The throttling passage 120 is part of a throttling valve, and is particularly variable and adjustable. Specifically, the length and / or cross-sectional area of ​​the throttling passage 120 are variable and adjustable.

[0157] In another embodiment, the throttling channel 120 may be formed as an inner groove on the inner cylinder liner surface 121 of the guide housing 102. Conversely, the outer cylinder liner surface 119 of the guide cover 103 may be designed without grooves. It is also conceivable that both cylinder liner surfaces 119, 121 may be designed with grooves.

[0158] According to another embodiment, the throttling channel 120 can be integrally formed as an outer groove on the outer cylinder liner surface 119 of the guide housing 102. Therefore, the inner housing portion of the guide housing 102 may not include the recess for the guide cover 103.

[0159] According to another embodiment, the throttling channel 120 may be spirally arranged on the end face of the guide cover 103 facing the guide housing 102 and / or the end face of the guide housing 102.

[0160] In the following text, refer to Figures 27 to 32The fifth embodiment of the invention is described below. Components that are structurally identical are given the same reference numerals as those in the foregoing embodiments, and are described herein with reference to those numerals. Components that are structurally different but functionally similar are given the same reference numerals and the suffix "d".

[0161] The active damper 14d differs from the aforementioned embodiment in that it is provided with at least one stop member 128 for the axial mobility of the friction lining, the stop member 128 being movable along the longitudinal axis 16 of the damper 14d. The stop member 128 is also referred to as an inertial advance stop. Due to the axial mobility of at least one stop member 128, the damper 14d has a variable and adjustable inertial advance length.

[0162] As in the damper according to the first embodiment, the friction lining is housed in a piston 41 that is axially displaceable within the housing 15d. To enable the friction unit with the friction lining to axially impact the stop member 128, the friction lining is exposed in at least some areas in the axial direction. This means that in these areas, the friction lining is not covered by the piston 41. When the piston 41 is displaced accordingly, at least one stop member 128 can immediately, i.e., directly, contact the friction lining. The friction lining makes frictional contact with the outer surface of the plunger 17. Referring to the first embodiment, regarding the basic inertial forward movement function.

[0163] In the illustrated embodiment, the damper 14d has four stop members 128, which are held along the annulus 129 and arranged along its circumference. According to the illustrated embodiment, the stop members 128 are equidistant in the circumferential direction, i.e., offset by a 90° rotation angle relative to the longitudinal axis 16. Fewer or more than four stop members 128 may also be arranged. The stop members 128 may be arranged at equal or different distances from each other in the circumferential direction on the annulus 129.

[0164] According to the illustrated embodiment, the stop members 128 have different lengths l1 and l2. In particular, the lengths l1 and l2 of the stop members 128 arranged opposite each other along their diameter are the same. This results in a time lag when the friction lining impacts the stop members 128, not all stop members 128 simultaneously contacting or penetrating the friction lining.

[0165] The annular member 129 is axially fixed to the adjusting member 132 via the axial web 130 and the radially outwardly protruding annular clamp 131. The stopping member 128, the annular member 129, the axial web 130, and the annular clamp 131 form the stopping unit 141.

[0166] For this purpose, the adjusting member 132 has an inner groove 133 corresponding to the annular clamp 131. The adjusting member 132 essentially has an outer ring 134 in which the inner groove 133 is disposed. At least one guide web 135 is integrally formed on the outer ring 134. According to the illustrated embodiment, four guide webs 135 are provided on the outer ring 134. More or fewer than four guide webs 135 may also be provided. The guide webs 135 extend parallel to the longitudinal axis 16 and are arranged on a circular line in a plane perpendicular to the longitudinal axis 16, particularly equidistant in the circumferential direction. The guide webs 135 extend from the outer ring 134 in a direction opposite to the stop member 128.

[0167] In different cases, the guide web 135 has a radially inwardly pointing guide pin 137 on the free end 136 of the guide web 135 arranged opposite to the external annulus 134.

[0168] The damper 14d also includes a displacement member 138. The displacement member 138 is substantially sleeve-shaped. At least one guide rail 139 is arranged on the outer side of the displacement member 138. According to the illustrated embodiment, the guide rail 139 is configured as an outer groove in the displacement member 138. The guide rail 139 is designed in a spiral shape along the outer periphery of the displacement member 138. According to the illustrated embodiment, four guide rails 139 are provided.

[0169] Guide pins 137 of the guide web 135 are arranged in and guided in each guide rail 139. The guide web 135 surrounds the displacement member 138 from the outside. Due to the fact that the guide web 135 is arranged together with the guide pins 137 in the guide rail 139, the adjusting member 132 is axially held on the displacement member 138.

[0170] At the free end opposite to the adjusting member 132, the displacement member 138 has a force transmission member 140, which, according to the illustrated embodiment, is designed as an external tooth.

[0171] The stop unit 141, the adjusting member 132, and the displacement member 138 form the adjusting mechanism 142. The adjusting mechanism 142 is used to axially adjust the stop member 128 along the longitudinal axis 16. The axial adjustment of the stop member 128 variably adjusts the inertial forward movement or idle travel of the friction lining in the friction damper 14d.

[0172] Interacting with the displacement member 138 is a switching drive 45d, which is connected to the transmission mechanism 143 and another force transmission member 144. This other force transmission member 144 engages with the force transmission member 140.

[0173] The following will refer to Figures 29 to 32The axial adjustability of the stop member 128 is explained in more detail. An adjustment mechanism 142 is arranged on a damper 14d, which is fixed to the housing, i.e., axially fixed relative to the longitudinal axis 16. When the switching drive 45d, specifically designed for an electric motor, is actuated, rotational motion is transmitted from another force transmission member 144 to the force transmission member 140. The rotational motion of the force transmission member 140, integrally arranged on the displacement member 138, guides the guide pin 137 and thereby guides the guide web 135 in the guide rail 139. Due to the helical design of the guide rail 139, axial displacement occurs in the displacement member 132 according to the direction of rotation, and thus axial displacement occurs in the stop unit 141. Therefore, depending on the direction of rotation of the force transmission member 140, this axial displacement either moves away from or towards the force transmission member 140. Thus, the axial position of the stop member 128 within the housing 15 of the friction damper 14d can be variably adjusted and specifically defined.

[0174] Figure 29 and Figure 30 The adjustment mechanism 142 in its extended position is shown, wherein the damper 14d has small, particularly minimum, inertial forward movement, and in particular, no inertial forward movement. Accordingly, Figure 31 and Figure 32 The retracted position of the adjusting mechanism 132 is shown. In this position, the friction pads have a large, particularly maximum, forward inertial force.

[0175] The damper assembly according to the invention can be implemented in particular by one or more dampers 14, 14a, 14b, 14c of the above embodiments. In particular, it is conceivable that different damper types 14, 14a, 14b, 14c are combined in the damper assembly and integrated into the washing machine 1.

Claims

1. A damper assembly for use in a washing machine, the damper assembly comprising: a. At least one damper (14; 14a; 14b; 14d) that produces a damping effect, said at least one damper (14; 14a; 14b; 14d) being able to be arranged between two movable parts (2, 10) of said washing machine (1) and being able to be connected to said two parts respectively. b. An adjustment unit (25) that communicates with the dampers (14; 14a; 14b; 14d) to adjust the damping effect of the dampers (14; 14a; 14b; 14d). c. At least one determining unit (26) that communicates with the adjusting unit (25) to determine at least one input variable. in d. The adjustment unit (25) is designed to transmit an adjustment signal to the damper (14; 14a; 14b; 14d) according to the at least one input variable. e. The dampers (14; 14a; 14b; 14d) are designed to variably determine their damping effect according to the adjustment signal. f. The damper (14; 14a; 14b; 14d) is designed as a friction damper, having friction units (41, 42) for generating frictional forces. Its features are, The axial restriction of the mobility of the friction pads (42) of the friction unit (41, 42) can be variably adjusted.

2. The damper assembly according to claim 1, characterized in that, The friction damper (14; 14a; 14b; 14d) has a housing (15) and a plunger (17) that can be displaced relative to the housing (15).

3. The damper assembly according to claim 2, characterized in that, The friction units (41, 42) are variable and adjustable, used to generate variable and adjustable frictional force.

4. The damper assembly according to claim 1, characterized in that, The at least one determining unit (26) has at least one damper-external sensor for determining the vibration characteristics of the components (2, 10) that can move relative to each other.

5. The damper assembly according to claim 1, characterized in that, The at least one determining unit (26) communicates with the drive motor (3), which can drive at least one of the components (2, 10) that can move relative to each other, for determining the characteristic variables of the drive motor (3).

6. The damper assembly according to claim 5, characterized in that, The characteristic variable is at least one of the performance, current and speed of the drive motor (3).

7. The damper assembly according to claim 1, characterized in that, The at least one determining unit (26) has at least one sensor for determining the motion and / or force of at least one damper component.

8. The damper assembly according to claim 7, characterized in that, The at least one sensor is integrated in the damper (14; 14a; 14b; 14d).

9. The damper assembly according to claim 7, characterized in that, The at least one damper component is at least one of the friction unit (41, 42), the housing (15), and the plunger (17) that can be displaced relative to the housing (15).

10. The damper assembly according to claim 1, characterized in that, The damper (14; 14a; 14b; 14d) has a transport fixing device.

11. The damper assembly according to claim 10, characterized in that, The transport fixing device is formed by fixing the minimum damping effect and / or has a locking element to lock the mobility of the damper.

12. The damper assembly according to claim 1, characterized in that, Emergency power units used to provide power in emergency conditions.

13. A machine that has a. First component (9, 10) b. Second component (2, 7) c. The damper assembly of claim 1, wherein the damper (14; 14a; 14b; 14d) is connected to the first component (9, 10) and the second component (2, 7).

14. The machine according to claim 13, characterized in that, The first component is a housing (9, 10), wherein the second component is an element mounted in the housing (9, 10) to vibrate, wherein the second component (2, 7) is displaceable relative to the first component (9, 10).

15. The machine according to claim 13, characterized in that, The machine is a washing machine, wherein the first component is a washing machine housing (9), and wherein the second component is a washing tub (7) installed in the washing machine housing (9, 10) to vibrate, wherein a clothes drum (4) is arranged in the washing tub (7) and the clothes drum (4) is mounted such that it can rotate about a rotation axis (6).

16. The machine according to claim 13, characterized in that, The at least one damper (14; 14a; 14b; 14d) is fastened at a first end to the bottom side of the bottom element (10) facing the first component (9, 10), and at a second end to the bottom element (10) and / or a side element adjacent to the bottom element (10).

17. The machine according to claim 13, characterized in that, The at least one damper (14; 14a; 14b; 14d) is fastened at a first end to the upper side of the cover element (13) facing the first component (9, 10), and at a second end to the cover element (13) and / or a side element adjacent to the cover element (13).

18. The machine according to claim 15, characterized in that, The at least one damper (14; 14a; 14b; 14d) is fastened at its first end to the outside of the washing tub (7) oriented parallel to the axis of rotation (6) of the clothes roller (4) or to the end face of the washing tub (7) oriented perpendicular to the axis of rotation (6) of the clothes roller (4).

19. The machine according to claim 15, characterized in that, The damper assembly has at least two dampers (14; 14a; 14b; 14d), wherein at least one damper is designed as an active damper.

20. The machine according to claim 19, characterized in that, The dampers (14; 14a; 14b; 14d) are arranged spaced apart from each other in a longitudinal direction oriented parallel to the axis of rotation (6) of the garment roller (4).

21. The machine according to claim 19, characterized in that, The dampers (14; 14a; 14b; 14d) are arranged circumferentially spaced from each other relative to the axis of rotation (6) of the garment roller (4).

22. The machine according to claim 13, characterized in that, The determining unit (26) of the at least one damper (14; 14a; 14b; 14d) communicates with a sensor arranged externally relative to the damper (14; 14a; 14b; 14d).

23. The machine according to claim 22, characterized in that, The sensor is designed as an acceleration sensor, a light barrier, a force sensor, a frequency sensor, and / or a displacement sensor.

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