EP4158218A1 - Dämpferanordnung und maschine für eine derartige dämpferanordnung - Google Patents
Dämpferanordnung und maschine für eine derartige dämpferanordnungInfo
- Publication number
- EP4158218A1 EP4158218A1 EP21728840.6A EP21728840A EP4158218A1 EP 4158218 A1 EP4158218 A1 EP 4158218A1 EP 21728840 A EP21728840 A EP 21728840A EP 4158218 A1 EP4158218 A1 EP 4158218A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- damper
- housing
- friction
- guide
- unit
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F7/00—Vibration-dampers; Shock-absorbers
- F16F7/08—Vibration-dampers; Shock-absorbers with friction surfaces rectilinearly movable along each other
- F16F7/082—Vibration-dampers; Shock-absorbers with friction surfaces rectilinearly movable along each other and characterised by damping force adjustment means
-
- D—TEXTILES; PAPER
- D06—TREATMENT OF TEXTILES OR THE LIKE; LAUNDERING; FLEXIBLE MATERIALS NOT OTHERWISE PROVIDED FOR
- D06F—LAUNDERING, DRYING, IRONING, PRESSING OR FOLDING TEXTILE ARTICLES
- D06F34/00—Details of control systems for washing machines, washer-dryers or laundry dryers
- D06F34/14—Arrangements for detecting or measuring specific parameters
- D06F34/16—Imbalance
-
- D—TEXTILES; PAPER
- D06—TREATMENT OF TEXTILES OR THE LIKE; LAUNDERING; FLEXIBLE MATERIALS NOT OTHERWISE PROVIDED FOR
- D06F—LAUNDERING, DRYING, IRONING, PRESSING OR FOLDING TEXTILE ARTICLES
- D06F34/00—Details of control systems for washing machines, washer-dryers or laundry dryers
- D06F34/14—Arrangements for detecting or measuring specific parameters
- D06F34/20—Parameters relating to constructional components, e.g. door sensors
-
- D—TEXTILES; PAPER
- D06—TREATMENT OF TEXTILES OR THE LIKE; LAUNDERING; FLEXIBLE MATERIALS NOT OTHERWISE PROVIDED FOR
- D06F—LAUNDERING, DRYING, IRONING, PRESSING OR FOLDING TEXTILE ARTICLES
- D06F37/00—Details specific to washing machines covered by groups D06F21/00 - D06F25/00
- D06F37/20—Mountings, e.g. resilient mountings, for the rotary receptacle, motor, tub or casing; Preventing or damping vibrations
- D06F37/22—Mountings, e.g. resilient mountings, for the rotary receptacle, motor, tub or casing; Preventing or damping vibrations in machines with a receptacle rotating or oscillating about a horizontal axis
-
- D—TEXTILES; PAPER
- D06—TREATMENT OF TEXTILES OR THE LIKE; LAUNDERING; FLEXIBLE MATERIALS NOT OTHERWISE PROVIDED FOR
- D06F—LAUNDERING, DRYING, IRONING, PRESSING OR FOLDING TEXTILE ARTICLES
- D06F37/00—Details specific to washing machines covered by groups D06F21/00 - D06F25/00
- D06F37/26—Casings; Tubs
- D06F37/267—Tubs specially adapted for mounting thereto components or devices not provided for in preceding subgroups
- D06F37/268—Tubs specially adapted for mounting thereto components or devices not provided for in preceding subgroups for suspension devices
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F7/00—Vibration-dampers; Shock-absorbers
- F16F7/08—Vibration-dampers; Shock-absorbers with friction surfaces rectilinearly movable along each other
- F16F7/09—Vibration-dampers; Shock-absorbers with friction surfaces rectilinearly movable along each other in dampers of the cylinder-and-piston type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/44—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction
- F16F9/46—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction allowing control from a distance, i.e. location of means for control input being remote from site of valves, e.g. on damper external wall
- F16F9/466—Throttling control, i.e. regulation of flow passage geometry
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/53—Means for adjusting damping characteristics by varying fluid viscosity, e.g. electromagnetically
- F16F9/535—Magnetorheological [MR] fluid dampers
-
- D—TEXTILES; PAPER
- D06—TREATMENT OF TEXTILES OR THE LIKE; LAUNDERING; FLEXIBLE MATERIALS NOT OTHERWISE PROVIDED FOR
- D06F—LAUNDERING, DRYING, IRONING, PRESSING OR FOLDING TEXTILE ARTICLES
- D06F2103/00—Parameters monitored or detected for the control of domestic laundry washing machines, washer-dryers or laundry dryers
- D06F2103/26—Unbalance; Noise level
-
- D—TEXTILES; PAPER
- D06—TREATMENT OF TEXTILES OR THE LIKE; LAUNDERING; FLEXIBLE MATERIALS NOT OTHERWISE PROVIDED FOR
- D06F—LAUNDERING, DRYING, IRONING, PRESSING OR FOLDING TEXTILE ARTICLES
- D06F2103/00—Parameters monitored or detected for the control of domestic laundry washing machines, washer-dryers or laundry dryers
- D06F2103/44—Current or voltage
- D06F2103/46—Current or voltage of the motor driving the drum
-
- D—TEXTILES; PAPER
- D06—TREATMENT OF TEXTILES OR THE LIKE; LAUNDERING; FLEXIBLE MATERIALS NOT OTHERWISE PROVIDED FOR
- D06F—LAUNDERING, DRYING, IRONING, PRESSING OR FOLDING TEXTILE ARTICLES
- D06F2105/00—Systems or parameters controlled or affected by the control systems of washing machines, washer-dryers or laundry dryers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F2230/00—Purpose; Design features
- F16F2230/08—Sensor arrangement
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F2230/00—Purpose; Design features
- F16F2230/18—Control arrangements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F2230/00—Purpose; Design features
- F16F2230/24—Detecting or preventing malfunction, e.g. fail safe
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/50—Special means providing automatic damping adjustment, i.e. self-adjustment of damping by particular sliding movements of a valve element, other than flexions or displacement of valve discs; Special means providing self-adjustment of spring characteristics
- F16F9/512—Means responsive to load action, i.e. static load on the damper or dynamic fluid pressure changes in the damper, e.g. due to changes in velocity
Definitions
- the invention relates to a damper arrangement and a machine, in particular a washing machine, with such a damper arrangement.
- Dampers can be used for this.
- the invention is based on the object of improving the damping of the relative movement of two mutually movable components in a machine and, in particular, of expanding the possibilities for influencing a damping effect.
- a damper arrangement has a control unit which is in signal connection with a damper.
- the damper which can be arranged between two mutually movable components, in particular components of a washing machine, and can each be connected to them, causes a damping effect.
- the control unit is used to regulate the damping effect of the damper.
- the control unit can be arranged externally to the damper or integrated in the damper.
- the damper arrangement comprises a determination unit, which is in signal connection with the control unit, for determining at least one input variable.
- the determination unit can be arranged externally to the damper or implemented integrated in the damper.
- the control unit is designed to transmit a control signal to the damper as a function of the at least one input variable.
- the damper is designed so that its damping effect can be variably determined as a function of the control signal.
- the variable definition of the damping effect takes place in particular actively.
- the damper is an active damper.
- the damping effect can be, for example, friction damping or hydraulic damping.
- An active damper is, for example, a friction damper with a freewheeling function that can be switched.
- Such a switchable damper has a switching unit which can be switched between a block arrangement and a freewheel arrangement.
- a Ver storage of the friction lining is blocked in the housing of the damper.
- Axial displacement of the friction lining in the housing is possible in the freewheel arrangement.
- Such a damper is known from DE 10 2016 207 809 A1, to which reference is hereby made.
- An active damper can be designed as a friction damper in which the frictional force, i.e. the damping effect, can be variably adjusted.
- At least one friction lining is attached to a friction lining carrier.
- the at least one friction lining can be adjustably arranged on the friction lining carrier and, in particular, can be pressed with a variable contact force against a corresponding friction partner, in particular the inner wall of a damper housing.
- the damping effect changes as a function of the contact pressure of the at least one friction lining.
- Such a damper is known from DE 10 2016225 036 A1, to which reference is hereby made.
- An active damper can also be a friction damper with a friction unit that generates a direction-dependent frictional force on an axially displaceable tappet.
- the plunger can be moved in the housing of the friction damper.
- the friction unit has at least one friction lining which rests against the plunger in a frictional manner.
- the frictional force can be variably set by means of a switching unit.
- the switching unit serves to block the tiltability of a friction lining, with frictional forces of different magnitude acting on the tappet in different tilting positions of the friction lining.
- Such a friction damper is known from DE 102020202348.4, which is hereby referred to.
- An active damper can also be formed in that, in the case of a friction damper, the axial limitation of the displaceability of a friction lining is variably adjustable. This can be done for example by means of at least one axially displaceable freewheel stop.
- a friction damper has a variably adjustable freewheel length.
- the at least one freewheel stop can, for example, be driven by a motor, in particular an electric motor, the electric motor, for example, parallel to the longitudinal axis of the friction damper is arranged on an outside of the housing of the friction damper.
- the rotary movement of the electric motor is transmitted in particular via a gear connection to a rotary link which has helical recesses and / or grooves along the outer circumference.
- axially oriented adjusting levers are guided, which are connected to the freewheel stop.
- the adjusting lever and thus the at least one freewheel stop are axially adjusted by a rotary movement of the rotary link. This changes the freewheeling length of the friction damper.
- An active damper can also be provided by a friction damper in which the friction lining has a foamed plastic which is soaked with a magneto-rheological fluid.
- the friction properties, in particular the damping effect of such a damper can be adjusted in a targeted manner by means of electromagnetic fields that interact with the magnetorheological fluid.
- a damper is known from WO 99/22162 A1, which is hereby referred to.
- An active damper can also be a hydraulic damper in which a damping effect is achieved in that a damping fluid flows through an integrated throttle channel.
- the integrated throttle channel forms a fluid throttle connection.
- the throttle channel has a flow cross-sectional area and a throttle channel length which influence the damping effect.
- the length and / or the cross-sectional area can be set variably.
- the control unit is in particular independent of a machine control of the machine, in particular of the washing machine.
- the damping effect can be defined in stages, that is to say in discrete damping effect stages, and / or continuously with a continuous course of damping effect.
- a damper arrangement in a washing machine is particularly advantageous.
- the damper arrangement according to the invention is also suitable for other machines, in particular in the field of mechanical engineering, such as, for example, for paint mixers in hardware stores, in paint shops and / or in paint shops, and / or for horizontal or vertical centrifuges and other rotating machines.
- the execution of the damper as a friction damper according to claim 2 ensures a ro bust damper arrangement and an efficient provision of the damping effect.
- This damper arrangement is particularly suitable in particular for washing machines.
- the friction damper has in particular a friction unit which is used to generate a frictional force.
- the frictional force counteracts, in particular, a relative movement between a housing and / or a tappet of the friction damper.
- the friction unit can have a freewheeling function that can be activated or deactivated and / or actively changed, that is to say can be actively adjusted.
- the damping effect of the damper arrangement is changed when the free-wheeling function is activated or not.
- Freewheel means that for a specified displacement path of the plunger, the so-called free stroke, with respect to the housing of the friction damper, no or at most a low frictional force is generated by the friction damper. When the free stroke is exceeded, the friction unit generates a higher frictional force. It is also conceivable that the amount of the free lift is variable, staggered or continuously fixable.
- the friction unit is designed to be able to variably set the friction force, in particular the amount of the friction force.
- This can be done, for example, in that the friction unit has at least one friction lining that rests on at least one of the movable components of the friction damper, i.e. the housing and / or the plunger, and is pressed with a variably adjustable contact force.
- the frictional force generated by the friction unit, in particular the friction lining can be adjusted.
- the execution of the damper as a hydraulic damper according to claim 4 enables a direct change of a throttle function, in particular by means of a variably adjustable Throttle valve.
- the throttle valve in particular enables a cross-sectional area and / or a length of a throttle channel of the throttle valve to be changed.
- the damper as a piston-housing unit with a housing and a piston that can be displaced for this purpose, wherein the piston can in particular have a carrier material with a magnetorheological fluid.
- the housing can have at least one electromagnetic coil, the damping effect, ie the force counteracting the movement between piston and housing, being variably adjustable by changing the electrical field of the electromagnetic coil in the housing.
- a damper arrangement according to claim 5 enables an uncomplicated design of the damper itself.
- the determination of the at least one input variable is possible independently of the damper.
- the damper arrangement enables in particular a frequency-dependent regulation, in particular by determining changes in direction of the mutually movable components, in particular by an acceleration sensor, by a light barrier and / or by a distance measurement.
- a parameter of a drive motor in particular an electric motor, which drives the laundry drum of the washing machine, serves as the input variable for the control unit.
- the current motor power in particular the current motor current, in particular the changes in the motor current over time, can be used as a parameter in order to identify an imbalance in the laundry drum.
- the speed signal, in particular the change in speed over time, of the electric motor can be used to detect imbalance.
- the determination unit can alswei sen a sensor which is integrated in particular in the damper.
- a sensor can be a magnetic displacement sensor, an optical sensor and / or a flow sensor in the case of a hydraulic damper.
- the sensor is used in particular to determine a movement of at least one damper component, in particular of the housing, of the plunger that can be displaced relative thereto and / or of the friction unit.
- a damper arrangement according to claim 8 enables a simplified execution of the Ma machine, in particular the washing machine.
- the transport lock of the damper can be carried out by defining a minimum damping effect, i.e. non-positive, so that it is reliably ensured that relative movements, in particular of the washing device tub in the housing of the washing machine, are excluded.
- the transport lock of the damper can have a locking element in order to lock the mobility of the damper and thus the mobility of the washing device tub in the housing. In this case, the transport lock is carried out positively. Such a locking would also be possible in that the flow cross-sectional area of a hydraulic damper is reduced to zero, that is to say closed.
- a damper arrangement with the emergency energy unit according to claim 9 ensures reliable and, in particular, risk-free operation of a machine with the damper arrangement in an emergency state, i.e. in particular when the machine and / or the damper arrangement are de-energized, i.e. in particular when standard energy is no longer available, possibly only temporarily.
- the emergency energy unit includes, in particular, a drive that can be driven at least one of the components that are movable relative to one another, which is designed in particular as an electric motor and can be used as a generator in an emergency state.
- the emergency energy unit can also have an induction unit for inducing electrical current, in particular a coil and a magnet, which are attached to damper components.
- the emergency energy unit can also have an accumulator or a battery unit of some other type and / or an electrical capacitor.
- the emergency energy unit can also be a mechanical energy store, in particular a pre-tensioned spring element, in particular a pre-tensioned disc spring or a pre-tensioned helical spring, and / or an independent, self-sufficient, available fluid pressure, in particular in the form of a pressure vessel under fluid pressure, in particular with Water, gas and / or hydraulic medium is filled, have.
- a corresponding pressure source can also be used de supply line for water, gas, air, a hydraulic medium or another fluid is used.
- a machine in particular a washing machine, according to claim 10 essentially has the advantages of the damper arrangement, to which reference is hereby made.
- the machine has a first and a second component which can be displaced relative to one another, the second component in particular being rotatable about an axis of rotation.
- the at least one damper is connected to the first component and to the second component, in particular special attached to it.
- the at least one damper is an active damper within the meaning of the patent application. There can be several active dampers on the machine. In addition to the at least one active damper, at least one passive damper can also be provided which is appropriately attached to the components. In particular, several passive dampers can also be seen easily. In contrast to the active dampers, a variable definition of the damping effect is not possible with the passive dampers. Passive dampers within the meaning of the inven tion are standard, free-wheeling, spring piston, hydraulic and / or air dampers and / or struts known per se.
- a machine according to claim 11 enables an advantageous arrangement of the at least one damper, in particular in a washing machine, in that the at least one damper supports the second component, which in particular is suspended in a swinging manner, on its underside.
- the underside is understood to be the area on an outside of the second component, the normal vector of which has a vertical component downwards.
- the second component is in particular the wash tub in the washing machine.
- the at least one damper can be articulated to an upper side of the second component.
- the upper side is understood to be the area on an outside of the second component, the normal vector of which has an upward vertical component.
- the second component is suspended from the min least one damper.
- a machine according to claim 13 enables reliable damping of vibrations, in particular due to imbalance of the laundry drum, that is to say in the radial direction in relation to the axis of rotation of the laundry drum and / or in the axial direction of the axis of rotation.
- a machine according to claim 14 ensures a sufficient number of dampers for reliable damping of the relative movement of the components.
- Fig. 1 shows a washing machine with a damper assembly according to the invention in a schematic representation in side view
- FIG. 2 shows the washing machine according to FIG. 1 in a front view
- FIG. 3 shows a perspective illustration of a switchable damper according to a first embodiment
- FIG. 4 shows a longitudinal section along the section line IV-IV in FIG. 3,
- FIG. 5 shows a perspective illustration of an actuating element of the damper in FIG. 3
- 6 shows a perspective illustration of a piston of the damper according to FIG. 3
- FIG. 7 shows a partially sectioned perspective illustration of the piston and the actuating element in a blocking arrangement
- FIG. 8 shows a perspective illustration of a switching actuator of the damper according to FIG. 3,
- FIG. 9 shows a partially cut-away perspective illustration of the damper according to FIG. 3 in the blocking arrangement
- FIG. 11 is a perspective view of a friction damper according to a further embodiment with a friction device
- FIG. 12 shows a partial illustration of the friction damper corresponding to FIG. 11 with an exposed friction device
- Fig. 13 is a longitudinal section along the section line XIII-XIII in Fig. 11 to illustrate the Rei environment s device in a first adjustment position
- FIG. 14 shows a representation corresponding to FIG. 13 in a second adjustment position that is different from the first adjustment position
- FIG. 15 is an enlarged perspective illustration of a friction lining carrier of the friction device in FIG. 12,
- FIG. 16 shows a side view of the adjusting element according to FIG. 15,
- FIG. 17 shows a longitudinal section along the section line XVII-XVII in FIG. 16
- Fig. 18 is an enlarged perspective view of an adjusting element of the Reibungsvorrich device according to FIG. 12,
- FIG. 19 shows a side view of the adjusting element according to FIG. 18,
- FIG. 20 shows a view according to arrow XX in FIG. 19,
- FIG. 21 is a perspective enlarged detailed view of a friction lining of the Reibungsvor direction according to FIG. 12,
- FIG. 23 shows a longitudinal section of a damper in the form of a hydraulic damper according to a further embodiment with an extended piston rod
- FIG. 24 shows a representation corresponding to FIG. 23 with the piston rod pushed in
- FIG. 25 shows an enlarged detailed view of a guide and sealing unit of the damper in FIG. 23,
- Fig. 26 is a half-sectioned, perspective view of the guide and sealing unit according to FIG. 25,
- FIG. 27 shows a side view of a damper with axially displaceable freewheel stops according to a further embodiment
- FIG. 29 shows a side view of an adjusting mechanism of the damper according to FIG. 27, the freewheel stops being arranged in an extended position
- FIG. 30 shows a sectional view according to section line XXX-XXX in FIG. 29,
- FIG. 32 shows a sectional illustration along the section line XXXII-XXXII in FIG. 31.
- a drum washing machine 1 shown in FIGS. 1 and 2 has a vibratory washing unit 2 with a drive motor 3 which drives a laundry drum 4 via a belt 5 about an axis of rotation 6.
- the laundry drum 4 is net angeord in the washing tub 7 and can be driven to rotate about the axis of rotation 6.
- Other components connected to the washing unit 2, such as a transmission, are not shown for the sake of simplicity.
- the vibratory washing unit 2 is suspended from a washing machine housing 9 by means of two suspension elements 8 designed as helical tension springs.
- the suspension elements 8 are attached, on the one hand, to first suspension eyelets 11, which are arranged in the upper region of the washing unit 2. On the other hand, they are suspended from second suspension eyelets 12 formed on the washing machine housing 9.
- the washing machine housing 9 is covered with a cover plate 13.
- dampers 14 are attached along the axis of rotation 6 in the center of the washing machine housing 9 and are connected to the washing machine frame 10.
- the central longitudinal axes 16 of the dampers 14 are arranged in a common plane which, for example, is oriented perpendicular to the axis of rotation 6.
- the damper 14 can also be arranged in different levels ver.
- the various damper levels are in particular oriented paral lel to one another.
- the planes can also be oriented inclined to one another.
- the planes are arranged at a distance from one another, in particular along the axis of rotation 6.
- dampers 14 it is also conceivable, in addition or as an alternative to the dampers 14, to arrange dampers on the front end face facing the flap 24 and / or the rear end face of the wash tub 7 facing away from the flap 24.
- dampers Arranged on the front side of the wash tub 7 Damper can be attached to the washing machine frame 10 and / or the washing machine housing 9, in particular special on the side walls of the washing machine housing 9.
- dampers 14 are of identical design and in particular each have an identical damping effect, that is to say a frictional force. It is conceivable that the dampers 14 are designed differently, in particular have a different damping effect, that is to say frictional force. It is essential that at least one of the dampers 14 is an active damper. The other damper can be a passive damper.
- dampers 14 can be provided on the top of the wash tub 7.
- the plunger 17 has a first fastening element 18 at its free end, by means of which the damper 14 is attached to a first bearing 19 on the washing unit 2 in such a way that the damper 14 can be pivoted about a first pivot axis 20 relative to the washing unit 2.
- a second fastening element 21 is attached to the free end of the housing 15, by means of which the damper 14 is attached to a second bearing 22 on the washing machine frame 10 in such a way that the damper 14 can be pivoted about a second pivot axis 23 relative to the washing machine frame 10 .
- the input and removal of laundry takes place through a flap 24 arranged on the washing unit 2.
- the dampers 14 are in signal connection with a control unit 25 in order to control a damping effect of the damper 14.
- the signal connection of the dampers 14 to the control unit 25 can be wired or wireless. For reasons of illustration, the signal connection is not shown in FIG. 1.
- a determination unit 26 is also provided.
- the determination unit 26 is used to determine at least one input variable.
- the determination unit is in signal connection with the control unit 25.
- the signal connection can be wireless or wired and is not shown in FIG. 1.
- the determination unit 26 can have one or more, not shown Have sensors and / or are in signal connection therewith in order to determine the vibration behavior of the mutually movable components, that is to say of the washing unit 2 with respect to the machine frame 10.
- At least one damper-external sensor is provided, which is designed in particular as an acceleration sensor, light barrier, force sensor, frequency sensor and / or as a displacement sensor.
- a sensor integrated in the damper 14 can be provided, which can be designed as a magnetic displacement sensor, as an optical sensor as a force sensor, as a frequency sensor and / or as a flow sensor in a hydraulic damper.
- the determination unit 26 can have a signal connection with the drive motor 3 in order to determine a current parameter of the drive motor 3, in particular its performance, in particular the motor current and / or the speed.
- the control unit 25 is designed to generate a control signal as a function of the at least one input variable and to transmit it to at least one of the dampers 14.
- the control unit 25 is designed in particular to be independent, that is to say self-sufficient, from the device control of the drum washing machine 1.
- the control unit 25 and / or the determination unit 26 can be integrated in the washing device control.
- the dampers 14 are designed to actively define the damping effect as a function of the received control signal in such a way that the vibration behavior of the drum washing machine 1 is improved.
- the dampers 14, the control unit 25 and the determination unit 26 form a Dämpan arrangement, which enable an improved vibration behavior of the washing unit 2 in the drum washing machine 1.
- the damper assembly can also be used in other machines. In particular, the damper arrangement can be used independently of the drum washing machine 1.
- input variables are determined, in particular continuously, with the determination unit 26 and transmitted to the control unit 25.
- the control unit 25 generates control signals from the input variables, which are transmitted to at least one of the dampers 14.
- the damping effect is actively, variably set in order to ensure an improved damping effect.
- the damper 14 is a switchable damper which is used in the drum washing machine 1 in order to dampen the balance of the laundry drum 4.
- the dampers 14 are designed as friction dampers.
- Each friction damper has a tubular housing 15 with a central longitudinal axis 16, in which a plunger 17 is guided coaxially ver slidably.
- the damper 14 comprises a substantially cylindrical housing 15 with a central longitudinal axis 16.
- a substantially tubular plunger 17 is arranged concentrically to the central longitudinal axis 16 and which moves along the central longitudinal axis 16 relative to the housing 15 is relocatable.
- the plunger 17 can also have a full cross-section.
- the tappet 17 is arranged with a first end inside the housing 15 and led out of the housing 15 with a second end. At the second end facing away from the housing 15, the plunger 17 has a first fastening element 18.
- the first fastening element 18 has a through sleeve 27, the sleeve axis of which is oriented perpendicular to the central longitudinal axis 16.
- the housing has a second fastening element 21 which is essentially identical to the The first fastening element 18 is designed and has a through sleeve 27.
- the first fastening element 18 is firmly connected to the plunger 17.
- the second fastening element 21 is firmly connected to the housing 15.
- the second fastening element 21 is fastened in particular to a front end of a guide section 28 of the housing 15.
- the housing 15 is constructed in several parts and comprises a switching housing part 29 shown on the right in FIG. 4 and a friction damping housing part 30 that is detachably connected to it.
- a switching housing part 29 shown on the right in FIG. 4
- a friction damping housing part 30 that is detachably connected to it.
- the switching housing part 29 and the friction damping housing part 30 arranged one behind the other.
- the switch housing part 29 is connected to the friction damping housing part 30.
- the connection can be followed by corresponding locking elements 31.
- the friction damping housing part 30 is closed by means of a guide cap 32.
- the guide cap 32 has a central guide opening 33 through which the plunger 17 is guided into an interior of the housing 4.
- the guide cap 32 has at least one positioning web 34 which extends along the central longitudinal axis 16 and which engages in a recess 35 provided for this purpose on the housing 15, in particular the friction damping housing part 30.
- the rotary position of the guide cap 32 with respect to the housing 15 is clearly defined by the positioning web 34.
- the positioning web 34 also serves as a protection against rotation for the guide cap 32 with respect to the housing 15 about the central longitudinal axis 16.
- cap freewheel stops 37 are integrally formed on the guide cap 32.
- the cap freewheel stops 37 are oriented parallel to the central longitudinal axis 16 and arranged in a plane perpendicular to the central longitudinal axis 16 in the shape of a segment of a circle around the plunger 17.
- the guide cap 32 is in particular made of an elastic material, in particular plastic. It can also be more or less than four cap freewheel stops 37 may be provided.
- the cap freewheel stops 37 are spaced apart, in particular equally spaced, from one another in a tangential direction with respect to the central longitudinal axis 16. A free space is provided between two adjacent cap freewheel stops 37.
- a housing base 38 is integrally formed on the end face of the friction damping housing part 30 opposite the guide cap 32.
- the housing base 38 is oriented perpendicular to the central longitudinal axis 16.
- four base freewheel stops 39 extend in the direction of the guide cap 32, for example.
- the guide section 28 is formed in one piece.
- the guide section 28 is used to guide the plunger 17 during axial displacement within the housing 15.
- the inner diameter of the guide section 28 essentially corresponds to the outer geometry of the plunger 17.
- the second fastening element 21 is arranged on the guide section 28 .
- the guide section 28 is passed through the switch housing part 29 and the second fastening element 21 protrudes from the rear end of the housing 15 shown on the right in FIGS. 3 and 4.
- a friction unit which comprises a piston 41.
- the piston 41 is designed to be essentially hollow and cylindrical.
- the piston 41 can be displaced along the central longitudinal axis 16 in the housing 15 and relative to the tappet 17.
- the piston 41 is arranged in the radial direction of the central longitudinal axis 16 between the plunger 17 and the housing 15.
- the piston 41 has an inner annular groove in which a friction lining 42 is arranged.
- the friction lining 42 is part of the friction unit.
- the friction lining 42 is designed in particular as a rub strip, the end faces of which can be flat or uneven, for example jagged or corrugated or with a different profile.
- the annular friction lining 42 rests with an inner cylindrical friction surface on an outer side of the tappet 17.
- the inner groove of the piston 41 is delimited on both sides in the axial direction by guide webs 43.
- the guide webs 43 are made in one piece with the piston 41. Compared to the inner groove, the guide webs 43 protrude radially inward with respect to the central longitudinal axis 16.
- the guide webs 43 are each designed in a plane perpendicular to the central longitudinal axis 16 like a ring segment.
- the inner contour defined by the guide webs 43 essentially corresponds to the outer contour of the plunger 17, the inner contour in the area of the guide webs 43 being so larger than the outer contour of the plunger 17 that direct contact with the plunger 17 by the piston 41 is excluded.
- the guide webs 43 are designed in such a way that they can engage in the spaces between the cap freewheel stops 37 or in the spaces between the bottom freewheel stops 39.
- the piston 41 is arranged adjacent to the guide cap 32.
- the guide webs 43 which face the guide cap 32, grip into the spaces between adjacent cap freewheel stops 37. This prevents unintentional rotation of the piston 41 with respect to the housing 15.
- the four cap freewheel stops 37 are arranged rotated by 45 ° with respect to the bottom freewheel stops 39.
- the friction lining 42 in the piston 41 is exposed at least in some areas in the axial direction of the central longitudinal axis 16. This exposed area of the friction lining 42 can strike the end face against the cap freewheel stops 47 or bottom freewheel stops 39.
- the friction lining 42 serves as a stop buffer.
- the damper 14 also has a switching unit 44 which enables switching between a block arrangement and a freewheel arrangement of the piston 41.
- the switching unit 44 comprises a switching actuator 49 with a switching drive 45.
- the switching drive 45 is designed as a lifting magnet, which causes a linear lifting movement triggered by electrical switching.
- the lifting magnet is attached to the housing 15 of the damper 14 in such a way that the linear Hubach se 46 is oriented parallel to the central longitudinal axis 16 of the damper.
- the housing 15 In the area of the switching housing part 29 in which the lifting magnet is arranged, the housing 15 is out of round, that is to say deviating from a cylindrical shape.
- the lifting magnet is via a power transmission element
- the switching drive 45 as a switchable lifting magnet
- the force transmission element 47 and the adjusting ring 48 form the switching actuator 49, which is shown in FIG. 8.
- the force transmission element 47 is designed as a flexible wire, which in particular is guided along a rigid guide channel.
- the force transmission element acts essentially radially on the adjusting ring 48 and can be displaced there against a spring force by means of an energy storage element in the form of a spring element 50.
- the adjusting element 52 has a radial pin as a shaped element 54 on an inside of the inner cylinder jacket surface, which can engage in a counter-shaped element 55 on a shaped link.
- the counter-shape elements 55 are integrally formed on an outer side of the essentially cylindrical piston 41.
- each shaped link having two counter-shaped elements 55.
- the counter-shaped elements 55 are each essentially U-shaped, the parallel legs of the U extending in the circumferential direction around the central longitudinal axis 16 when the piston 41 is installed.
- the shaped links are arranged diametrically opposite one another on the outside of the piston 41 with respect to the central longitudinal axis 16. The respective opening of the U is oriented in the circumferential direction around the central longitudinal axis 16.
- the damper 14 is in the Blockadeanord voltage.
- the form element 54 lies in one of the counter-form elements 55.
- the parallel legs of the U of the counter-form elements 55 form an undercut in a direction parallel to the central-longitudinal axis 16.
- a displacement of the piston 41 relative to the joint housing 15 and / or the plunger 17 is blocked.
- a relative displacement of the plunger 17 with respect to the housing 15 causes a frictional force through the friction lining 42 resting radially on the plunger 17 and axially blocked.
- the friction damping function of the damper 14 is switched on, ie activated.
- the switching unit 44 is activated by actuating the switching actuator 49.
- the force transmission element 47 which engages the lifting magnet 45, is displaced along the lifting axis 46.
- the force transmission element 47 is fed radially to the adjusting ring 48 along the curved guide channel.
- the force transmission element 47 exerts a torque on the adjusting ring 48 around the central longitudinal axis 16 and causes a rotation of the adjusting ring 48 around the central longitudinal axis 16.
- the adjusting element 52 is rotated, which with the engaging webs 53 is held in the openings 51 of the adjusting ring 48.
- the form element 54 By rotating the adjusting element 52, the form element 54 is rotated about the central longitudinal axis 16 relative to the piston 41, the plunger 17 and the housing 15. The form element 54 is displaced from the counter-form element 55 out.
- the freewheel arrangement of the damper is shown in FIG.
- the shaped element 54 is in the freewheel arrangement of the counter-shaped element 55 in the circumferential direction, that is in the tangential direction, with respect to the central longitudinal axis 16 spaced angeord net.
- the piston 41 is released from the actuating element 52. In the freewheel arrangement, the piston 41 can be displaced along the central longitudinal axis 16 relative to the housing 15 and relative to the tappet 17.
- the lifting magnet 45 is switched in the correspondingly opposite direction and thus the actuating element 52 is rotated about the central longitudinal axis 16 in the opposite direction.
- the spring element 50 is part of a safety device which enables the switching unit 54 to be switched again in the event of a power failure.
- a capacitor not shown, is provided, which can store electrical energy that is sufficient to switch the solenoid 45 in the event of a power supply interruption.
- the movement of the lifting magnet 45 is mechanically stored in the spring element 50.
- the two counter-shaped elements 55 of a shaped link are arranged at a distance from one another along the central longitudinal axis 16. This makes it possible for the piston 41 to be blocked in various positions along the central longitudinal axis 16 by means of the adjusting element 52 and its shape element.
- insertion bevels can be provided on the counter-shaped element 55 along the direction of rotation of the adjusting element 52 in order to simplify the insertion of the shaped element 54 into the counter-shaped element 55 in the case of an imprecise arrangement, i.e. if the arrangement of the shaped element 54 is not exactly aligned with the counter-shaped element 55.
- the shaped element 54 can be wedge-shaped, for example, which can interlock with a wedge tip in one of several, in particular many, jagged recesses corresponding to the wedge tip on a shaped link.
- at least five, in particular at least 10 and in particular at least 20 corresponding recesses into which the wedge tip can engage can be provided on the shaped link. This makes it possible for the shaped element to be able to engage in one of the counter-shaped elements essentially independently of the axial positioning of the piston 41.
- the friction lining 42 can also be arranged on an outside of the piston 41.
- the counter-shaped element 55 is embodied on an inside of the piston 41.
- the formula element 54 would then be arranged between the tappet 17 and the piston 41.
- the switching actuator 49 can have a switchable rotary magnet as a switching drive, which is also known as a plunger coil or voice coil.
- the rotary magnet enables an active component to rotate in relation to a static, passive component.
- Such a damper has a particularly compact design.
- FIGS. 11 to 21 A further embodiment of the invention is described below with reference to FIGS. 11 to 21.
- Structurally identical parts are given the same reference numerals as in the first embodiment, the description of which is hereby referred to.
- Constructively under- Different parts that are functionally identical have the same reference numerals with an a after them.
- a damper 14a shown in FIGS. 11 to 14 has a housing 15 with a central longitudinal axis 16. With regard to the structure and function of the damper 14a, reference is made to DE 102016225 036 A1.
- the housing 15 is formed by a first housing part which is designed as an outer tube and to which a first fastening element 18 is attached. With the first fastening element 18, the damper 14a can be fastened to a component. At the end facing the first fastening element 18, the first housing part is closed. The first housing part is open at the end opposite the first fastening element 18. A second housing part in the form of an inner tube is inserted into the first housing part through the opening. The second housing part forms the plunger 17.
- the second housing part is closed.
- a second fastening element 21 is provided, with which the damper 14a can be fastened to a further component.
- the fastening elements 18, 21 are each designed, for example, as fastening eyes with inserted sleeves which are oriented transversely to the central longitudinal axis 16.
- the housing parts can be displaced relative to one another along the central longitudinal axis 16.
- a guide element 58 is provided for the guided displacement of the second housing part.
- the housing parts are each designed as cylinder tubes.
- the housing parts have a non-circular contour in a plane perpendicular to the central longitudinal axis 16.
- the housing parts can be designed as square tubes, rectangular tubes or oval tubes. In such a Ausrete tion rotation of the housing parts with respect to the central longitudinal axis 16 is prevented by a positive connection.
- the damper 14a also has a pull-out protection which prevents the second housing part 6 from being unintentionally pulled far out of the first housing part.
- the pull-out protection is ensured in that molded elements 59, which project radially inwardly and are arranged along a circular line around the central longitudinal axis 16, are provided on the first housing.
- the shaped elements 59 engage behind the guide element 58 inside the first housing part.
- the guide element 58 is fixed axially and radially on the first housing part with respect to the central longitudinal axis 16.
- the guide element 58 protrudes inward in the radial direction with respect to the central longitudinal axis 16 on the first housing part.
- a friction unit is attached to the second housing part, that is to say to the inner tube.
- the friction unit comprises a friction lining carrier 60, an adjustable friction lining 42a arranged on the friction lining carrier 60 and an adjusting element 61 for the adjustable arrangement of the friction lining 42a on the friction lining carrier 60.
- the friction unit is along the axial direction of the central longitudinal axis 16 and with respect to a rotation fixed about the central longitudinal axis 16 on the second housing part.
- the friction unit is fastened to the second housing part by means of an indentation 62 on the inner tube for clamping the friction lining carrier 60.
- the friction unit protrudes in the radial direction with respect to the central longitudinal axis 16 on the second housing part.
- the guide element 58 forms a pull-out stop for the second housing part, in that the friction unit, in particular the friction carrier 60, is prevented from being axially displaced by the guide element 58 with a radially protruding annular shoulder 65.
- the structure of the friction lining 60 is explained in more detail below with reference to FIGS. 15 to 17.
- the friction lining carrier 60 is made in one piece, for example from plastic.
- the friction lining carrier 60 is designed essentially as a hollow cylinder with a pin-like anchoring section 63 with which the friction lining carrier 60 is inserted at the end into the inner tube of the second housing part.
- the anchoring section 63 has a circumferential inner groove 64 into which the indentation 62 engages in order to hold the friction lining carrier 60 on the second housing part.
- the friction lining carrier 60 has a first recess Outer diameter Di, which corresponds essentially to the inner diameter of the inner tube of the second housing part.
- the friction lining carrier 60 has the anchoring portion 63 adjoining, radially standing in front of the annular shoulder 65, with which the friction lining carrier 60 rests against an annular end face of the second housing part.
- the friction lining carrier 60 is axially supported with the annular shoulder 65 on the inner tube of the second housing part.
- the annular shoulder 65 is adjoined by a carrier section 66 in an axial direction.
- the carrier section 66 has a second outer diameter D2 which is larger than the first outer diameter Di.
- the second outer diameter D2 corresponds essentially to the inner diameter of the outer tube of the first housing part.
- the carrier section 66 has several, in particular at least one and, according to the exemplary embodiment shown, exactly four, window-like radial recesses 67 along the outer circumference. Two adjacent radial recesses 67 are each separated from one another by an axial web 68.
- the friction lining carrier 60 On the front side, the friction lining carrier 60 has an annular web 80 in the region of the carrier section 66.
- the friction lining carrier 60 has a through hole 69 along an axial direction.
- the through-hole 69 is designed in the area of the anchoring section 63 with an adjusting link 70 as a movement thread.
- the through hole 69 is designed as a frustoconical support section 71 from.
- the adjusting element 61 is explained in more detail below with reference to FIGS. 18 to 20.
- the adjusting element 61 has an adjusting pin 72.
- the adjusting pin 72 has an external thread which corresponds to the internal thread of the adjusting link 70.
- the adjustment element 61 can be arranged with the adjustment pin 72 on the adjustment link 70 of the friction lining carrier 60 in an adjustable manner along an adjustment direction 73.
- the adjustment direction 73 corresponds to an axial direction of the friction lining carrier 60.
- the friction unit is arranged in the damper 14a in such a way that the adjustment direction 73 is oriented to the central longitudinal axis 16.
- a pressing section 74 Adjacent to the adjusting pin 72, a pressing section 74 is provided which, starting from the adjusting pin 72, has a conically widening contour.
- the adjusting element 61 has a contact element 75 with which the adjusting element 61 can abut the friction lining carrier 60 at the end of the line to limit the adjustment.
- an actuating section 76 is provided, which is designed as an eccentrically arranged slot-like recess.
- the friction lining is explained in more detail below with reference to FIGS. 21 and 22.
- the friction lining 42a is designed essentially in the shape of an annular disk with a central, circular opening 77 through which the adjusting element 61 can be guided.
- a plurality of recesses 78 projecting radially inward are provided along the outer circumference of the friction lining 42a, with which the friction lining 42a can be fixed to the axial webs 68 of the friction lining carrier 60. This ensures anti-twist protection for the friction lining 42a in the friction lining carrier 60.
- the friction lining 42a has in each case radially protruding friction lining sections 79.
- the geometry of the friction lining sections 79 essentially corresponds to the size of the opening in the radial recesses 67 on the friction lining carrier 60.
- the friction lining 42a can also have a plurality of friction lining sections 79 designed separately from one another.
- the friction lining 42a can be arranged in the friction lining carrier 60, in particular within the carrier section 66, in such a way that the friction lining sections 79 protrude through the radial recesses 67 in the radial direction outward. Because of the axial webs 68 engaging in the recesses 78, the friction lining 42a is fixed radially in a direction of rotation about the central longitudinal axis 16. The friction lining 42a is fixed to the friction lining carrier 60 along the axial direction by the frontal, circumferential annular web 80, which is engaged from behind by the friction lining sections 79.
- the function of the friction damper is explained in more detail below with reference to FIG.
- the friction unit is held with the friction lining carrier 60 in the inner tube.
- the friction lining 42a is inserted in the carrier section 66 of the friction lining carrier 60, so that the friction lining sections 79 are arranged in the radial recesses 67.
- the adjustment element 61 is passed through the opening 77 of the friction lining 42a with the adjustment pin 72 and screwed into the adjustment link 70 of the friction lining carrier 60 with the external thread.
- the outer diameter of the adjusting pin 72 is smaller than the inner diameter of the opening 77. As long as the adjusting element 61 is screwed so slightly into the friction lining carrier 60 that only the adjusting pin 72 is located inside the opening 77, the friction lining 42a is radially expanded not held.
- a torque can be transmitted from the actuating element to the adjusting element 61.
- the rotary movement of the adjusting element 61 causes an axial displacement of the adjusting element 61 as a result of the adjusting link 70.
- the axial displacement of the adjusting element 61 along the central-longitudinal axis 16 causes the conically widening pressing section 74 to increasingly enter the opening 77 of the friction lining 42a pushes.
- the friction lining 42a is subjected to a pressing force acting radially outward.
- the pressing force causes compression of the material from which the friction lining 42a is made.
- the friction lining sections 79 are pressed radially outward through the radial recesses 67 as a result of the contact pressure.
- the friction lining 42a is pressed directly against an inside of the first housing part, ie the outer tube.
- a force results when the housing parts are displaced along the central longitudinal axis 16 relative to one another.
- FIG. 1 Such an arrangement is shown in FIG.
- the adjusting element 61 is screwed into the friction lining carrier 60 to a maximum depth.
- the adjustment element 61 rests with the contact element 75 on the end face on the annular web 80 of the friction lining carrier 60.
- a further axial displacement of the adjusting element 61 along the central longitudinal axis 16 is prevented.
- the support of the adjusting element 61 on the friction lining carrier 60 is robust.
- a maximum screw-in depth is robustly defined.
- the assembly can be designed as a longitudinally slotted sleeve with a sleeve body which forms the friction lining carrier 60.
- a drive which drives the adjustment of the adjusting element 61 by a motor.
- the drive is designed, in particular, in the form of an electric motor and, in particular, is designed to be integrated in the second housing part.
- a third embodiment of the invention is described below with reference to FIG. 22.
- Structurally identical parts are given the same reference numerals as in the first two embodiments, to the description of which reference is hereby made.
- Constructively under different, but functionally similar parts are given the same reference numerals with a subsequent b.
- a piston 41b is provided which is provided with annular recesses 82, in each of which a coil 125 is arranged, which is wound around the piston 41b.
- a sleeve 126 made of magnetically permeable material is provided on an inside of the housing 15 and serves as a pole piece.
- the coils 125 which generate the electromagnetic field, are connected to a controller via a connecting line 127.
- a friction pad 42b is arranged, which is in particular designed as an annular cylinder.
- the friction lining 42b consists of an open-cell foamed plastic, for example polyurethane or polyamide.
- the foamed plastic serves as a retention medium for a magneto-rheological fluid, as is known, for example, from US Pat. No. 5,382,373 or US Pat. No. 5,578,232.
- the basic structure of magneto-rheological friction damping when used in a friction damper is known from WO 99/22 162 A1, to the description of which reference is expressly made.
- the damper 14c is in the form of a hydraulic damper and has an essentially hollow-cylindrical inner housing 83 and an outer housing surrounding the inner housing 83, which forms the housing 15 of the damper 14c.
- the two housings 83 are according to the embodiment shown as pipe cuts out leads.
- the damper 14c is referred to as a two-pipe damper.
- the inner housing 83 is closed at a first housing end 85 shown on the left in FIG. 23 by a guide and sealing unit 86 for guiding and sealing a piston rod led out of the first housing end 85.
- the piston rod forms the plunger 17.
- the inner housing 83 is closed by an annular housing cover 89 with a bottom valve 90.
- the inner housing 83, the guide and sealing unit 86 and the housing cover 89 essentially enclose a working space 91 which is filled with a damping fluid 92.
- this displaceably guided piston 41c is arranged, which is attached to a first piston rod end 93.
- the piston 41c divides the working chamber 91 into a first partial working chamber 94 facing the first housing end 85 and a second partial working chamber 95 facing the second housing end 88 a first fastening element 18 is integrally formed in the form of a cylindri's through opening.
- the outer housing has a round cross section and surrounds the inner housing 83.
- a first housing end 85 is flanged to form a housing stop 97, a housing opening 98 being delimited through which the piston rod is guided.
- a second housing end 88 of the outer housing, which is opposite the first housing end 85, is closed by a housing base 99 formed in one piece with the outer housing.
- the Ge housing bottom 99 can also be connected to the outer housing as a separate and, in particular, multi-part component.
- the housing bottom 99 is provided on the side facing the inner housing 83 for receiving the bottom valve 90 with a housing-bottom recess 100, for example, in a stepped shape.
- a second fastening element 21 is formed or fastened on a side of the housing bottom 99 facing away from the inner housing 83, the second fastening element 21 being oriented essentially centrally to the central longitudinal axis 16.
- the inner housing 83 and the outer housing are arranged concentrically to the central longitudinal axis 16, so that a compensation space 101 is formed in the form of an annular gap.
- the compensation space 101 has a constant width along its circumference.
- the damper 14c comprises at least one housing with a non-circular, essentially oval cross-section, which is arranged offset to the other housing 83 in such a way that the compensation space 101 is formed in the form of an annular gap with an oval cross-section.
- the compensation space 101 can also stretch into the housing-bottom recess 100.
- the compensation chamber 101 can be under pressure and is partially filled with the damping fluid 92, for example oil, gas such as nitrogen.
- the guide and sealing unit 86 has a guide housing 102 and a guide cover 103.
- the guide cover 103 is arranged in a recess of the guide housing 102 provided for this purpose.
- the guide housing 102 is along the middle
- the tel longitudinal axis 16 is step-shaped and is arranged in a sealed manner in the inner housing 83 with an inner housing step.
- the guide housing 102 is circumferentially sealed with an outer housing step on the outer housing and is supported along the central longitudinal axis 16 via a disk 104 on the housing stop 97.
- the guide housing 102 On an end face facing the first housing end 85 of the outer housing, the guide housing 102 has a recess into which a sealing element 105 is inserted.
- the sealing element 105 serves to lead 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 element 105 arranged therein, so that a pressure chamber 106 is delimited by the guide and sealing unit 86, the sealing element 105 and the piston rod.
- valve ring prevents fluid flow from the working chamber 91 into the pressure chamber 106, in particular when the piston rod moves in an extension direction 107.
- a fluid flow from the working chamber 91 into the pressure chamber 106 can be tolerated.
- the guide housing 102 has a shoulder 124 on which the inner housing 83 extends in the axial direction, i. H. is supported along the central longitudinal axis 16.
- the inner housing 83 is fastened to the outer housing by the housing cover 89, which is annular and has a housing cover protruding over the inner housing 83 in the radial direction. Stop against the second housing end 88 rests.
- the housing cover 89 has a con centric to the central longitudinal axis 16 arranged housing cover bore, which merges into an annular housing cover recess. The bottom valve 90 enables a fluid flow from the compensation chamber 101 into the working chamber 91 and in particular into the second partial working chamber 95.
- the piston rod has a reduced diameter at its first piston rod end 93, as a result of which a piston rod stop 109 is formed.
- a first piston rod distance disc 110 On the first piston rod end 93, starting from the piston rod stop 109, a first piston rod distance disc 110, a first locking element 111 in the form of a disc spring, a piston disc 112, a second locking element 113 in the form of a disc spring, a second piston rod spacer 114 and a piston rod locking nut 115 are arranged.
- the piston rod locking nut 115 is screwed onto a piston rod thread and secures the piston 41c on the piston rod.
- the piston 41c is formed by the first closure element 111, the piston disk 112, the second closure element 113 and a piston seal 116.
- the piston seal 116 is annular and is arranged in a piston groove provided for this purpose in the piston disk 112.
- the piston groove is formed in an outer wall of the piston disk 112 facing the inner housing 83.
- the piston seal 116 seals the piston disk 112 from the inner housing 83.
- the first locking element 111 is effective when the piston rod moves in the insertion direction 108 and is referred to below as a compression plate spring.
- the second locking element 113 is effective in the pull-out direction 107 and is referred to below as a tension plate spring.
- the tension disk spring 113 interacts with a plurality of tension flow channels, not shown, and the compression disk spring 111 cooperates with a number of pressure flow channels, not shown.
- the throughflow channels each have a transverse channel running 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 throughflow channels are formed in the piston disk 112 and establish a connection between the first partial working space 94 and the second partial working space 95.
- the pressure flow-through channels can - viewed in the direction of insertion 108 - be built up from the longitudinal channel and the adjoining transverse channel.
- the train flow-through channels can be built up by the transverse channel and the adjoining longitudinal channel.
- the longitudinal channels of the tension through-flow channels can be arranged in the piston disk 112 in such a way that they can be closed by the elastically deformable tension disk spring 113.
- the longitudinal channels of the pressure flow channels can be arranged in the piston disk 112 in such a way that they can be closed by the elastically deformable pressure disk spring 111.
- the through-flow channels can each have an effective flow cross-sectional area which can be changed by closing one or more through-flow channels.
- damper 14c effective cross section of the flow channels wherein the cross section of the flow channels along these can be any.
- the effective flow cross-sectional area is thus to be understood as a resulting cross-section of the flow channels.
- the damper 14c has a preferred installation position such that the insertion direction 108 is identical to the direction of gravity.
- the damper 14c is attached to an element to be damped in such a way that the piston rod is fastened with the first fastening element 18 to the moving part to be damped. This means that the damper 14c is essentially aligned vertically with its central longitudinal axis 16, with the piston rod with the first fastening element 18 being arranged at the top in this installation position.
- the guide and sealing unit 86 is arranged in the housings 83, 84 of the damper 14c in such a way 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 arranged with an end-face, protruding ring elevation 118 and a groove in the guide housing 102 provided for this purpose.
- the guide cover 103 and the guide housing 102 are positioned relative to each other and in particular special with respect to the central longitudinal axis 16 are arranged concentrically.
- an outer groove is provided which extends ent long the central longitudinal axis 16 as a helix, that is, in the form of a helix.
- the guide cover 103 rests with the outer cylinder jacket surface 119 only in sections on an inner cylinder jacket surface 121 of the guide housing 102.
- the outer groove 120 enables a fluid flow along a helical line on an outer circumference of the guide cover 103 to a distributor channel 122.
- the distributor channel 122 is essentially step-shaped integrated into the guide housing 102 and connects the outer Groove 120 with shoulder 124, the distributor channel 122 extending as far as an outer jacket surface 123 of the outer housing section of the guide housing 102. This ensures that the damping fluid 92 can flow from the working chamber 91 along the outer groove 120 via the distributor channel 122 into the compensation chamber 101 arranged between the inner housing 83 and the outer housing. Because the distributor channel 122 is recessed opposite the shoulder on which the inner housing 83 is supported, said fluid flow is guaranteed. 1 iced.
- the outer groove 120 is also referred to as a throttle channel and, according to the first exemplary embodiment, has a semicircular flow cross-sectional area with a clear width d and a length.
- the clear width d is the diameter of the semicircle.
- the throttle channel 120 is guided on the outer cylinder jacket surface 119 of the guide cover 103 as a full helical line on the circumference, ie with an opening angle of 360 °.
- the helical throttle channel 120 can also have an opening angle different from 360 °. An opening angle of less than 360 ° as well as greater than 360 ° is possible.
- the pitch of the helix can be different from the width of the guide cover 103.
- the length 1 of the Drosselka channel 120 is greater than the clear width d of the throttle channel. It is also possible to select other cross-sectional shapes for the throttle channel 120, such as, for example, a circular shape or a rectangular shape.
- the throttle channel 120 can also be designed in a meandering shape or in another arrangement around the central longitudinal axis 16. It is possible to provide at least one one-way flow control valve in the throttle channel 120 in order to prevent a fluid flow from the compensation chamber 101 into the working chamber 91.
- the piston 41c has throughflow channels which can be closed by plate springs 111, 113.
- the plate springs 111, 113 are on the piston, ie the flow channels are closed ver.
- the fluid pressure on the disc springs 111, 113 rises with increasing insertion or extraction speed, in particular until a switching pressure is reached in one of the partial working spaces 94, 95.
- the corresponding disc spring 111, 113 lifts from the piston.
- the fluid flow between the two partial working spaces 94, 95 is possible without hindrance along the flow channels of the piston 41c.
- damper 14c has a non-progressive damping behavior.
- the damping force-speed characteristic is given by the effective flow cross-sectional area of the flow channels. It is also possible to design the damper 14c as a so-called progressive damper, the functioning of which is explained below. 23 and 24 show the rest state of the damper 14c.
- the plate springs 111, 113 do not rest against the associated contact surfaces and the throughflow channels are not closed.
- the piston 41c When the piston 41c moves in the pull-out direction 107 or in the push-in direction 108 at low speed, the piston 41c, in particular the disc springs 111, 113, remains essentially in the rest state shown in FIGS. 23, 24.
- the damping fluid 92 can flow through the flow channels when the piston 41c moves.
- the disc springs 111, 113 leave a sufficient gap between them and the associated contact surfaces so that the damping fluid 92 can get into the respective other partial working space 94, 95.
- the mode of operation of the disc springs 111, 113 is reversed with respect to the non-progressive damper 14c, ie the disc spring 111 acts as a tension disc spring and the disc spring 113 acts as a compression disc spring.
- the damping force-speed characteristic is given at low speed by the effective flow cross-sectional area of the flow channels.
- the function of the progressive damper 14c during a movement of the piston 41c in the insertion direction 108 is described, the insertion speed being substantially higher than the movement of the piston 41c described above.
- the damping fluid 92 located in the second partial working chamber 95 exerts a force on the compression plate spring 113.
- the compression plate spring 113 is increasingly elastically deformed and pressed against the associated contact surfaces of the throughflow channels, the effective flow cross-sectional area being increasingly reduced. If the force is sufficient, the compression plate spring 113 rests completely against the contact surfaces, so that the throughflow channels are completely closed.
- the damping fluid 92 can flow from the second partial working space 95 into the first partial working space 94 only through the flow channels.
- the tension plate spring 111 is pushed away from the associated contact surfaces, so that the fluid flow mentioned from the second partial working space 95 into the first partial working space 94 is made possible.
- the volume of the damping fluid 92 displaced by the piston rod flows via the throttle channel 120 and the distributor channel 122 into the compensation chamber 101 Damping fluid 92 throttled along the throttle channel 120.
- the throttle channel 120 is therefore essentially independent of the manufacturing tolerances of the piston rod and a guide bore through which the piston rod is guided in the guide and sealing unit 86.
- the guide and damping unit 86 enables a flow through the annular gap between the piston rod and the guide bore not to impair the damping effect of the damper 14c .
- a change in the throttle output and thus the damping effect of the damper 14c can be achieved directly and easily by changing the length of the throttle channel 120, for example by changing the width of the guide cover 103, ie its extension along the central longitudinal axis 16 .
- a valve ring (not shown) can be provided to prevent the damping fluid 92 from reaching the pressure chamber 106 unthrottled and from there with fluid pressure p f on the sealing element 105 works. As a result, the service life of the sealing member 105 can be increased.
- a venting opening (not shown) can be provided in the pressure chamber 106, which enables venting of the pressure chamber 106 at a minimum venting pressure p e. The vent pressure p e is greater than the fluid pressure pf.
- the damping fluid 92 When the piston rod is actuated starting from the arrangement in FIG. 24 along the extension direction 107, the damping fluid 92 is displaced from the first partial working space 94 by the piston 41c and flows at the first housing end 85 via the throttle channel 120 and the distributor Channel 122 into the compensation space 101. This means that even in the event of an operation When the damper 14c is moved in the pull-out direction 107, the damping fluid 92 passes through the throttle channel 120. At the second housing end 88, the damping fluid 92 is sucked into the second partial working space 95 via the bottom valve 90 of the inner housing 83. In addition, it is possible for a direct fluid flow from the first partial working space 94 into the second partial working space 95 to take place through the through openings in the piston disk 112.
- the throttle channel 120 is part of a throttle valve, which can be adjusted in particular variably.
- the length and / or the cross-sectional area of the throttle channel 120 are variably adjustable.
- the throttle channel 120 can be designed as an inner groove on the inner cylinder jacket surface 121 of the guide housing 102.
- the outer cylinder jacket surface 119 of the guide cover 103 can be designed without a groove. It is also conceivable that both cylinder jacket surfaces 119, 121 are designed with a groove.
- the throttle channel 120 can be embodied as an outer groove in an integrated manner on an outer cylinder jacket surface 119 of the guide housing 102. Accordingly, the inner housing section of the guide housing 102 cannot have a recess for a guide cover 103.
- the throttle channel 120 can be arranged in a spiral shape on an end face of the guide cover 103 facing the guide housing 102 and / or on an end face of the guide housing 102.
- FIGS. 27 to 32 A fifth embodiment of the invention will now be described with reference to FIGS. 27 to 32. Structurally identical parts are given the same reference numerals as in the previous embodiments, the description of which is hereby referred to. Parts that are structurally different but functionally identical are given the same reference numerals with a d added after them.
- the active damper 14d differs from the previous embodiments in that at least one stop element 128 for the axial displaceability of the friction lining is provided, which is displaceable along the longitudinal axis 16 of the damper 14d.
- the stop element 128 is also referred to as a freewheel stop. Due to the axial displaceability of the at least one stop element 128, the damper 14d has a variably adjustable freewheel length.
- the friction lining is accommodated in a piston 41 which is axially displaceable in the housing 15d. So that the friction unit with the friction lining can strike axially against the stop elements 128, the Reibungsbe lay exposed in the axial direction at least in areas. This means that the friction lining is not covered by the piston 41 in this area.
- the at least one stop element 128 can contact the friction lining directly, that is to say directly, when the piston 41 is displaced accordingly.
- the friction lining rests against the outside of the tappet 17 in a frictional manner.
- the damper 14d has four stop elements 128 which are held along a ring 129 and arranged along its circumferential line.
- the stop elements 128 are equally spaced in the circumferential direction, that is to say are arranged with a 90 ° rotational angle offset with respect to the longitudinal axis 16 to one another. It is also possible for fewer or more than four stop elements 128 to be arranged.
- the stop elements 128 can be arranged in the circumferential direction on the ring 129 equally or at different distances from one another.
- the stop elements 128 have different lengths h, h.
- the lengths h, h of the diametrically opposed stop elements 128 are identical. As a result, it is possible that not all stop elements 128 come into contact with or penetrate the friction lining when the friction lining hits the stop elements 128 at the same time, but with a time offset.
- the ring 129 is axially fixed on an adjusting element 132 via axial webs 130 and a radially outwardly extending annular collar 131.
- the stop elements 128, the ring 129, the axial webs 130 and the annular collar 131 form a stop unit 141.
- the adjusting element 132 has an inner groove 133 corresponding to the annular collar 131.
- the adjusting element 132 essentially has an outer ring 134 in which the groove 133 is arranged.
- At least one guide web 135 is integrally formed on the outer ring 134. According to the embodiment shown, four guide webs 135 are provided on the outer ring 134. More or fewer than four guide webs 135 can also be provided.
- the guide webs 135 extend parallel to the longitudinal axis 16 and are arranged in a plane perpendicular to the longitudinal axis 16 on a circular line, in particular equidistant from one another in the circumferential direction.
- the guide webs 135 extend, starting from the outer ring 134, in a direction opposite to the stop elements 128.
- the guide webs 135 In each case at their free end 136, which is arranged facing away from the outer ring 134, the guide webs 135 have a guide pin 137 directed radially inward.
- the damper 14d also has a displacement element 138.
- the displacement element 138 is designed essentially in the form of a sleeve.
- At least one guide track 139 is arranged on the outside of the displacement element 138.
- the guide track 139 is designed as an outer groove in the displacement element 138.
- the guide track 139 is designed helically along the outer periphery of the displacement element 138. According to the embodiment shown, four guide tracks 139 are provided.
- a guide pin 137 of a guide web 135 is arranged in each guide track 139 and is guided therein.
- the guide webs 135 encompass the displacement element 138 from the outside. Because the guide webs 135 with the guide pins 137 are arranged in the guide tracks 139, the adjustment element 132 is held axially on the displacement element 138.
- the Verlagerungsele element 138 has a force transmission element 140 which, according to the embodiment shown, is designed as an external toothing.
- the stop unit 141, the adjusting element 132 and the displacement element 138 form an adjusting mechanism 142.
- the adjusting mechanism 142 is used to axially adjust the Stop elements 128 along the longitudinal axis 16.
- the freewheel that is to say the idle stroke, of the friction lining in the friction damper 14d is variably set.
- a shift drive 45d which is coupled to a gear 143 and a further power transmission element 144, interacts with the displacement element 138.
- the further force transmission element 144 meshes with the force transmission element 140.
- the adjustment mechanism 142 is fixed to the housing on the damper 14d, that is, axially with respect to the longitudinal axis 16.
- the switching drive 45d which is designed in particular as an electric motor
- a rotary movement is transmitted from the further force transmission element 144 to the force transmission element 140.
- the guide pins 137 and thus the guide webs 135 are guided in the guide tracks 139.
- FIGS. 29 and 30 show the adjusting mechanism 142 in an extended position in which the damper 14d has a small, in particular a minimal, and in particular no freewheel.
- FIGS. 31 and 32 show a retracted position of the adjusting mechanism 132.
- the friction lining has a larger, in particular a maximum, freewheel.
- a damper arrangement according to the invention can in particular be implemented with one or more dampers 14, 14a, 14b, 14c of the exemplary embodiments explained above. It is ins- it is particularly conceivable that different types of dampers 14, 14a, 14b, 14c are combined in a damper arrangement and integrated in a washing machine 1.
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102020206722.8A DE102020206722A1 (de) | 2020-05-28 | 2020-05-28 | Dämpferanordnung und Maschine für eine derartige Dämpferanordnung |
PCT/EP2021/063402 WO2021239551A1 (de) | 2020-05-28 | 2021-05-20 | Dämpferanordnung und maschine für eine derartige dämpferanordnung |
Publications (1)
Publication Number | Publication Date |
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EP4158218A1 true EP4158218A1 (de) | 2023-04-05 |
Family
ID=76197414
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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EP21728840.6A Pending EP4158218A1 (de) | 2020-05-28 | 2021-05-20 | Dämpferanordnung und maschine für eine derartige dämpferanordnung |
Country Status (6)
Country | Link |
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US (1) | US20230193547A1 (de) |
EP (1) | EP4158218A1 (de) |
KR (1) | KR20230017242A (de) |
CN (1) | CN115667755A (de) |
DE (1) | DE102020206722A1 (de) |
WO (1) | WO2021239551A1 (de) |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
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CN116926884A (zh) * | 2022-04-06 | 2023-10-24 | 博西华电器(江苏)有限公司 | 衣物护理器具 |
DE102022110201B4 (de) | 2022-04-27 | 2024-02-08 | Karlsruher Institut für Technologie, Körperschaft des öffentlichen Rechts | Schwingungsdämpfer |
DE102022209864A1 (de) | 2022-09-20 | 2024-03-21 | Suspa Gmbh | Reibungsdämpfer |
Family Cites Families (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3016915A1 (de) * | 1980-05-02 | 1981-11-05 | Fritz Bauer + Söhne oHG, 8503 Altdorf | Schwingungsfaehige abstuetzung fuer waschmaschinen |
JPH04371194A (ja) * | 1991-06-18 | 1992-12-24 | Matsushita Electric Ind Co Ltd | ドラム式洗濯機 |
US5382373A (en) | 1992-10-30 | 1995-01-17 | Lord Corporation | Magnetorheological materials based on alloy particles |
US5578232A (en) | 1995-05-04 | 1996-11-26 | Hart & Cooley, Inc. | Open-coil heater assembly and insulator therefor |
US6394239B1 (en) | 1997-10-29 | 2002-05-28 | Lord Corporation | Controllable medium device and apparatus utilizing same |
DE102005032499B4 (de) | 2004-07-13 | 2009-10-22 | Lg Electronics Inc. | Dämpfer zur Vibrationsdämpfung und damit ausgerüstete Waschmaschine |
DE102004047999A1 (de) * | 2004-10-01 | 2006-04-06 | BSH Bosch und Siemens Hausgeräte GmbH | Reibungsdämpfereinrichtung für eine Waschmaschine |
CN101037840A (zh) | 2007-04-17 | 2007-09-19 | 海尔集团公司 | 具有磁流变主动减振器的滚筒洗衣机 |
US9022185B2 (en) * | 2010-05-11 | 2015-05-05 | Adil Kanioz | Electromechanical friction shock absorber |
DE102011080962A1 (de) | 2011-08-15 | 2013-02-21 | Suspa Gmbh | Dämpfer |
DE102012215044A1 (de) * | 2012-08-23 | 2014-02-27 | BSH Bosch und Siemens Hausgeräte GmbH | Einrichtung in einer Waschmaschine zur transportsicheren Festlegung des Trommelaggregats |
DE102016207809A1 (de) | 2016-05-04 | 2017-11-09 | Suspa Gmbh | Schaltbarer Dämpfer |
DE102016209826A1 (de) * | 2016-06-03 | 2017-12-07 | Suspa Gmbh | Dämpfer |
DE102016225036A1 (de) | 2016-12-14 | 2018-06-14 | Suspa Gmbh | Reibungsvorrichtung und Reibungsdämpfer mit einer derartigen Reibungsvorrichtung |
DE102018211769A1 (de) | 2018-07-16 | 2020-01-16 | BSH Hausgeräte GmbH | Schwingungsdämpfungssystem und Gerät zum Behandeln von Wäsche |
DE102020202348A1 (de) | 2020-02-24 | 2021-08-26 | Suspa Gmbh | Reibungsdämpfer |
-
2020
- 2020-05-28 DE DE102020206722.8A patent/DE102020206722A1/de active Pending
-
2021
- 2021-05-20 WO PCT/EP2021/063402 patent/WO2021239551A1/de unknown
- 2021-05-20 CN CN202180038676.8A patent/CN115667755A/zh active Pending
- 2021-05-20 EP EP21728840.6A patent/EP4158218A1/de active Pending
- 2021-05-20 US US17/924,175 patent/US20230193547A1/en active Pending
- 2021-05-20 KR KR1020227044736A patent/KR20230017242A/ko active Search and Examination
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US20230193547A1 (en) | 2023-06-22 |
WO2021239551A1 (de) | 2021-12-02 |
CN115667755A (zh) | 2023-01-31 |
KR20230017242A (ko) | 2023-02-03 |
DE102020206722A1 (de) | 2021-12-02 |
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