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EP1220961B1 - Damper - Google Patents

Damper Download PDF

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Publication number
EP1220961B1
EP1220961B1 EP00971282A EP00971282A EP1220961B1 EP 1220961 B1 EP1220961 B1 EP 1220961B1 EP 00971282 A EP00971282 A EP 00971282A EP 00971282 A EP00971282 A EP 00971282A EP 1220961 B1 EP1220961 B1 EP 1220961B1
Authority
EP
European Patent Office
Prior art keywords
housing
measuring element
damper
tappet
plunger
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.)
Expired - Lifetime
Application number
EP00971282A
Other languages
German (de)
French (fr)
Other versions
EP1220961A1 (en
Inventor
Thomas Peuker
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Suspa Compart GmbH
Original Assignee
Suspa Holding GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Suspa Holding GmbH filed Critical Suspa Holding GmbH
Priority to SI200030300T priority Critical patent/SI1220961T1/en
Publication of EP1220961A1 publication Critical patent/EP1220961A1/en
Application granted granted Critical
Publication of EP1220961B1 publication Critical patent/EP1220961B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • 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

Definitions

  • the invention relates to a damper, especially for washing machines with spin cycle.
  • EP 0 686 720 A1 describes a friction damper for washing machines known, the one in a damper housing slidably guided plunger having. At the inside of the plunger there is a Damping pistons are provided with an annular groove that runs in the longitudinal direction is limited by annular stops. On this ring groove section is a longitudinally displaceable between the two annular stops Damping ring provided with a friction lining. The friction lining lies rubbing against the inner wall of the damper housing. The damping ring is between stops provided on the damping piston slidable against spring elements.
  • a disadvantage of this configuration of a friction damper is that the plunger position cannot be determined can and the payload of the washing unit is not determinable, what about Vibration problems during a washing operation can lead.
  • a damper of a washing machine is known.
  • the damper has a housing with a slidably guided therein Pestle.
  • the damping strength of the damper is electrically adjustable.
  • DE 22 04 325 C2 discloses a drum washing machine with spring struts or friction dampers to dampen the vibrations of the washing unit known. These each have a housing with a slidable therein guided plunger. To determine the insertion depth of the The plunger is hollow with a permanent magnet. The housing The damper is arranged in the extension direction of the tappet provided the ring coil surrounding the plunger, which is able to position to detect the permanent magnet in the toroid.
  • a certain predetermined critical Determine insertion depth of the plunger and for example the Interrupt spin cycle due to particularly strong vibrations. The result is therefore only digital.
  • the disadvantage of this arrangement is that the position of the plunger cannot be determined continuously. In addition, the overall arrangement is achieved by the coil arranged upstream of the housing longer. Another disadvantage is that the determination of the payload the washing unit is not possible because of the large Stiction between the friction lining and the housing no depth The measure of the payload is.
  • the invention has for its object a damper with a housing and to provide a displaceably guided plunger, where the insertion depth of the plunger into the housing is as simple as possible can be determined and from this the insertion force acting on the plunger can be determined.
  • the object is solved by the features of claim 1.
  • the core the invention is that with the housing and the plunger each a measuring element is connected whose relative position to each other by electrical interaction is determined, the plunger over a Part of the insertion depth is an essentially idle stroke free of static friction having. This enables e.g. B. the weight of dry laundry and measure the water at rest and / or dynamic imbalance to be recorded during operation.
  • the drum washing machine shown in FIGS. 1 and 2 with horizontal Drum axis 1 has a vibratory washing unit 2 with a drive motor 3, which is not shown in detail Washing drum drives via a belt drive 4. More with the Washing unit 2 connected components, for example a gear, are not shown for the sake of simplicity.
  • the vibratory Washing unit 2 is over two struts described in more detail below 5 compared to a standing on the floor 6, a base frame forming machine frame 7 supported. A surrounding the washing unit 2 Washing machine housing 8 is opposite the machine frame 7 supported and connected to this.
  • the input and removal of laundry is carried out by an on an end face 9 of the washing unit 2 arranged flap 10.
  • Each strut 5 has a tubular housing 11 with a central longitudinal axis 12 in which a plunger 13 is displaceable coaxially is led.
  • a Stop 14 attached in the area of the free end of the plunger 13 in which a plunger 13 is displaceable coaxially is led.
  • a Stop 14 attached in the area of the free end of the plunger 13 .
  • One located outside the housing 11 Section of the plunger 13 surrounding, prestressed helical compression spring 15 is opposite the stop 14 on the one hand and the ram outlet side End of the housing 11 supported on the other hand, so that the plunger 13th can be inserted into the housing 11 against the force of the spring 15.
  • Outdoors An elastic link 16 is provided at the end of the plunger 13. This has a bearing 17 connected to the washing unit 2, which via elastic blocks 18 is clamped with the plunger 13. In the same way the free end of the housing 11 is articulated on the machine frame 7.
  • the drum washing machine according to FIGS. 3 and 4 differs from 1 and 2 in that the washing unit 2 on the machine housing 8 is suspended by means of helical tension springs 19.
  • the Tension springs 19 are attached to eyelets 20 on the one hand, in the upper area of the washing unit 2 are attached. On the other hand, they are on eyelets 21 suspended on the cover plate 22 of the washing machine housing 8 are trained.
  • At the bottom of the washing unit 2 are in the longitudinal direction in the middle two friction dampers described in more detail below 23 attached, which are connected to the machine frame 7.
  • everyone Friction damper 23 has a cylindrical housing 24 with a central longitudinal axis 25, in which a plunger 26 is guided coaxially. At the tappet exit end 27 of the housing 24 is in this Damping housing 28 is formed.
  • the pestle 26 has at its free end an articulated sleeve 30 as a link element by means of which the friction damper 23 on a bearing 36 on Washing unit 2 is mounted so that the friction damper 23 by one Pivot axis 32 is pivotable relative to the washing unit 2, which is parallel runs to drum axis 1.
  • an articulated sleeve 34 is also attached, the pivot axis 35 equally as the pivot axis 32, the central longitudinal axis 25 perpendicular cuts. With this joint sleeve 34, the friction damper 23 attached to a bearing 31 on the machine frame 7 so that the Pivot axis 35 also runs parallel to drum axis 1.
  • a damping piston 38 On the inside of the housing 37 of the housing 11 is the end of the plunger 13 a damping piston 38 is provided which has an annular groove 39 which in Longitudinal direction is limited by annular stops 40, 41, which are in one piece are formed with the damping piston 38.
  • a ring-cylindrical damping ring 42 In the ring groove 39 is a ring-cylindrical damping ring 42 is arranged, the has an annular groove 43 on the outer circumference, in which a friction-damping coating 44 is provided.
  • the damping ring 42 is in the Annular groove 39 approximately frictionless with respect to the damping piston 38 displaceable.
  • the friction-damping lining 44 is rubbing against the inside 45 of the housing 11.
  • the friction damping pad 44 can made of foamed, closed-cell impregnated with lubricant Polyurethane exist.
  • Housing 11 is a ring-cylindrical guide bushing 47 is provided, which is connected to the housing 11 via beads 48.
  • the plunger 13 is guided displaceably.
  • Guide tube formed in one piece with the guide bushing 47 50, which is surrounded by an annular cylindrical stop 51, compared to the helical compression spring 15 on in the insertion direction 49 located end is supported.
  • the strut 5 has a tappet position measuring device for detection the insertion depth T of the plunger 13 in the housing 11.
  • the measuring device has an annular-cylindrical sensor 52, which on the Insert direction 49 lying end of the damping piston 38 coaxially is attached to the central longitudinal axis 12.
  • the encoder 52 is made of metal, especially iron or another ferritic material.
  • the housing 11 consists of a magnetically permeable, in particular non-metallic Material.
  • the measuring device also has a coil unit 53 on, in the case shown in Fig. 5 of two connected in series Coils 54 and 55 exist.
  • the coils 54, 55 are via electrical connection lines 56 connected to an evaluation unit 57.
  • the coil unit 53 can in particular consist of one or two adjacent to one another Arranged coils surrounding the housing 11 exist.
  • the coil unit 53 extends in the longitudinal direction, in particular at least over the length of the encoder 52 at maximum insertion depth T of the plunger 13 is swept.
  • the coil unit 53 acts it is a so-called inductive in the measuring device Displacement transducer. This is by pushing the encoder 52 in the interior of the coil 54 changes its inductance.
  • the evaluation The inductance of the coil 54 takes place on one in general in electrical engineering known quarter bridge.
  • the advantage of this arrangement is that completely simple structure. The disadvantage is that only in a narrow area around the working point of a given insertion depth T changes the insertion depth T are proportional to the change in inductance.
  • the coil unit 53 two coils connected in series 54 and 55, as shown in Fig. 5, is the measuring device a so-called differential choke.
  • To the connecting lines 56 an electrical signal is applied or tapped by them.
  • By moving the encoder 52 in the interior of the coils 54, 55 their inductance is changed.
  • the evaluation of the insertion depth T via the change in inductance sets advance that the encoder 52 made of a ferromagnetic material, for example So made of iron / steel. If an evaluation of the insertion depth via an eddy current effect, then the encoder 52 should consist of a non-ferromagnetic but electrically conductive material, for example made of aluminum.
  • the washing unit 2 is first used Load laundry.
  • the plunger 13 sinks from that shown in FIG. 5 Starting position in the housing 11, so that the insertion depth T is enlarged.
  • the plunger 13 is inserted essentially free of static friction over a range ⁇ T until the damping ring 42 stops comes with the stop 41.
  • the plunger 13 thus has an idle stroke on.
  • the change ⁇ T of the insertion depth T im essentially proportional to the push-in force acting on the plunger 13, so that by measuring the change ⁇ T in the insertion depth T the Struts 5 of the washing machine the weight of the laundry can be measured.
  • the insertion force can be calculated.
  • the washing unit 2 vibrates, the The amplitude is so great that the damping ring 42 alternately stops comes with the stops 40 and 41, so that the movement of the Ram 13 is damped by the friction-damping coating 44.
  • the amplitude of the vibrations can be measured by measuring the insertion depth T can be determined at any time. Should the amplitudes of the Vibrations can become too large, based on signals from the evaluation unit 57 reduces the spin speed or the spin cycle be canceled. It is possible with the one described at the beginning Drum washing machine only one of the struts 5 with a plunger position measuring device to provide. The other strut 5 can be commercially available be trained.
  • the compression springs 58, 59 have the function described in the exemplary embodiment to the extent that when the plunger is slightly pushed in. 13 not only the helical compression spring 15, but also the compression spring 59 be upset what when determining the mass of the washing aggregate 2 from the insertion depth T through the evaluation unit 57 is considered.
  • the friction damper 23 will now be described with reference to FIG. 7 described in more detail according to a first embodiment.
  • a guide piston 61 located end of the plunger 26 is a guide piston 61 formed, the two longitudinally offset to one another, formed in one piece therewith has annular guide webs 62, 63, between which one Ring groove 64 is formed.
  • the guide webs 62, 63 are in a leading position the inner wall 65 of the housing 24.
  • an annular cylinder trained damping ring 66 provided along the outer circumference has a lining ring groove 67 in which the friction damping lining 29 is arranged, which rubs against the inner wall 65 is applied.
  • the friction-damping coating 29 consists of lubricant impregnated, foamed plastic or felt.
  • the guide piston 61 is essentially in the region of the longitudinal extent of the annular groove 64 Slidable relative to the damping ring 66.
  • the end of the housing 24 provided with a bead 68 so that the plunger 26 is not pulled out of it can be.
  • the plunger 26 and the guide piston 61 are made in one piece from plastic.
  • the housing 24 consists of a non-metallic material, in particular plastic, or from a magnetic permeable metal.
  • the plunger position measuring device has one in the direction of insertion 60 lying end of the plunger 26 arranged coaxially to the central longitudinal axis 25, ring-cylindrical encoder 69. Furthermore, a coil unit 70 with two arranged adjacent to each other, the housing 24 is cylindrical surrounding coils 71, 72 are provided, which via connecting lines 73 are electrically conductively connected to an evaluation unit 74. With regard to the structure of the encoder 69 and the coil unit 70 is on the description of the encoder 52 and the coil unit 53 of the shock absorber 5 according to the first embodiment.
  • the operational function of the friction damper 23 is referred to that of the strut 5.
  • the Plunger 26 As with the strut 5 is the Plunger 26 as long as a change ⁇ T representing an idle stroke Insertion depth T can be inserted essentially without static friction until the Web 63 comes into stop with the damping ring 66. Will the movement continued in the same direction, the frictional force is between to overcome the friction-damping coating 29 and the inner wall 65.
  • the friction damper 23 is thus the same as the strut 5 suitable for both the load of the washing unit 2 and, if necessary, to measure unbalance as well as the amplitude of the washing unit vibrations to determine in the spin cycle.
  • the evaluation unit 74 must be different from the strut 5 additionally by the Coil tension springs 19 exerted on the washing unit 2 opposing forces consider.
  • the damping ring 29 it is possible to mount the damping ring 29 with compression springs 58, 59 to support against the webs 62 and 63, whereby the same there described effects arise.
  • the friction damper 23 ' described according to a second embodiment.
  • Structurally different, but functionally similar parts get the same reference numbers with a prime.
  • the central difference from the first embodiment is that Structure of the ram position measuring device.
  • On in slot direction 60 located end of the housing 24 is a bottom 75 with a bead 76 provided connected to the housing 24.
  • At the bottom 75 is a coaxial to the central longitudinal axis 25, against the direction of insertion 60 protruding pin 77 arranged at the free end of the encoder 69 'is attached.
  • the pin 77 is made of a non-metallic material, such as B. plastic.
  • the encoder 69 ' is made of the material of the Pin 77, especially plastic, enclosed.
  • the guide piston 61 ' has a coaxial to the central longitudinal axis 25 in the insertion direction 60 located end open slot channel 78, which is formed is that the pin 77 with the encoder 69 'in this when inserted of the plunger 26 'can be inserted without contact.
  • the coil unit 70 ' has two adjacent coils 71 'and 72' on the Insert channel 78 surrounded by a ring cylinder and the adjacent to each other are arranged on the guide piston 61 '.
  • the connecting lines 73 ' are from the plunger 26' in the region of its free end out that they do not interfere with the insertion of the plunger 26 '.
  • the main difference consists in the encoder 69 'being stationary with the housing 24 is connected and the coil unit 70 'with the plunger 26 in the housing 24 can be inserted. This has the advantage that the housing 24 from one any material, such as B. steel, can be made because of the interaction between encoder 69 'and coil unit 70' completely within of the housing 24 takes place.
  • the friction damper 23 " according to a third embodiment. Obtain identical parts the same reference numerals as the friction damper 23 according to the first Embodiment, the description of which reference is hereby made. constructive different but functionally similar parts are given the same Reference number with two prime lines.
  • the damping ring 66 is slidably arranged Damping ring 66 "is on the outer circumference essentially free of static friction slidably on the inside of the receiving portion 81.
  • the damping ring 66 has the friction damping coating 29, which abuts the plunger 26 ′′.
  • the receiving section 81 is through a ring-cylindrical cover 85 with latching openings 86, into which the latching lugs 82 engage in a locking manner, locked.
  • stops 87 and 88 are provided on the inside of the Cover 85 and the inside pointing counter to the insertion direction 60 of the stop collar 80.
  • the Tappet 26 has a friction section made of metal, in particular steel 89, which is in contact with the covering 29.
  • the plunger 26 ′′ has one with the section 89 connected encoder support section 91, which consists of a non-metallic Material, especially plastic, is made.
  • the encoder 69 In the area of Insert direction 60 located end of section 91 is the encoder 69 ".
  • the housing 24" is made of a non-metallic material, especially made of plastic.
  • FIG. 10 differs from that of FIG. 9 only in that on the plunger 26 '' 'is not a separate encoder, but that as an encoder 69 '' 'serves the edge of the plunger 26' '', that is, in the interior of the housing 90 located end.
  • the structure is similar to the friction damper 23 'shown in FIG. 8 the description of which is hereby referred. Identical parts get the same Reference numerals as in the friction damper 23 'according to the second Embodiment. Structurally different, but functional Similar parts are given the same reference numerals with four superscripts Strokes.
  • the guide piston 61 '' '' essentially has the shape of an annular cylindrical sleeve, on the opposite of which Insert direction 60 end protruding radially outward Latches 94 are provided, which are in latched engagement with the Rest recesses 93 are located.
  • the end of the guide piston 61 '' '' is the one projecting radially outwards Guide web 62 is provided, the annular groove 64 through the guide webs 62 and 63 is limited in the axial direction.
  • the end of the guide piston 61 '' '' is a transmitter 69 '' '' cylindrical ring 97 arranged in a corresponding Annular groove 98 is fixed on the inside of the guide piston 61 '' ''.
  • the ring 97 is made of metal, in particular aluminum.
  • the one out Metal, especially iron, existing cylindrical pin 77 carries the Coil unit 70 '' '', which consists of a arranged on the surface of the pin 77 Coil 71 ', in particular made of copper wire.
  • the sink 71 ' is opposite the pin 77 by a thin plastic layer 102 isolated, with the individual windings of the coil 71 'against each other are isolated.
  • At the end opposite to the insertion direction 60 of the pin 77 is a radial opposite to the pin 77 and the coil unit 70 '' '' projecting spacer 99 is provided, which is a round Has cross section, between the spacer 99 and the Inner wall 100 of the guide piston 61 '' '' there is play.
  • the connecting line 73 "" is of that in the direction of insertion 60 lying end of the coil 71 'through the bottom 75 to one Plug 101 guided, from which a connection to the evaluation unit 74 can be produced.
  • the advantage of this arrangement is that the housing 24th selected without disadvantage on the plunger position measuring device made of metal can be.

Landscapes

  • Engineering & Computer Science (AREA)
  • Textile Engineering (AREA)
  • Fluid-Damping Devices (AREA)
  • Main Body Construction Of Washing Machines And Laundry Dryers (AREA)
  • Buildings Adapted To Withstand Abnormal External Influences (AREA)
  • Vibration Dampers (AREA)
  • Spinning Or Twisting Of Yarns (AREA)
  • A Measuring Device Byusing Mechanical Method (AREA)
  • Transmission And Conversion Of Sensor Element Output (AREA)

Abstract

The invention relates to a damper (5), especially for washing machines with a spin gear, comprising a push rod (13) which is moveably guided in a housing (11) and extends out from the end of said housing; and a push rod position measuring device for determining the depth (T) to which the push rod (13) is pushed into the housing (11). Said device has a first measuring element which is connected to the housing (11) and a second measuring element which is connected to the push rod (13), for electrically and/or magnetically interacting with the first measuring element. The first and second measuring elements can be pushed into each other. An evaluating unit (57) for giving electrical signals and for receiving and processing electrical signals for determining the depth (T) to which the push rod (13) is pushed into the housing (11) is provided and is electroconductively connected to the first measuring element or the second measuring element. A friction damping unit for producing a predetermined friction damping effect is also provided between the housing (11) and the push rod (13). The push rod (13) can be displaced almost stictionlessly in relation to the housing (11) within the range of a predetermined change in the depth (T) to which the push rod (13).

Description

Die Erfindung betrifft einen Dämpfer, insbesondere für Waschmaschinen mit Schleudergang.The invention relates to a damper, especially for washing machines with spin cycle.

Aus der EP 0 686 720 A1 ist ein Reibungsdämpfer für Waschmaschinen bekannt, der einen in einem Dämpfer-Gehäuse verschiebbar geführten Stößel aufweist. Am gehäuseinnenseitigen Ende des Stößels ist ein Dämpfungs-Kolben mit einer Ringnut vorgesehen, die in Längsrichtung durch ringförmige Anschläge begrenzt ist. Auf diesem Ringnut-Abschnitt ist zwischen den beiden ringförmigen Anschlägen ein längsverschiebbarer Dämpfungs-Ring mit einem Reibbelag vorgesehen. Der Reibbelag liegt reibend an der Innenwand des Dämpfer-Gehäuses an. Der Dämpfungs-Ring ist zwischen an dem Dämpfungs-Kolben vorgesehenen Anschlägen gegen Federelemente verschiebbar. Nachteilig bei dieser Ausgestaltung eines Reibungsdämpfers ist, dass die Stößelposition nicht ermittelt werden kann und die Zuladung des Wasch-Aggregats nicht bestimmbar ist, was zu Schwingungsproblemen während eines Waschbetriebs führen kann.EP 0 686 720 A1 describes a friction damper for washing machines known, the one in a damper housing slidably guided plunger having. At the inside of the plunger there is a Damping pistons are provided with an annular groove that runs in the longitudinal direction is limited by annular stops. On this ring groove section is a longitudinally displaceable between the two annular stops Damping ring provided with a friction lining. The friction lining lies rubbing against the inner wall of the damper housing. The damping ring is between stops provided on the damping piston slidable against spring elements. A disadvantage of this configuration of a friction damper is that the plunger position cannot be determined can and the payload of the washing unit is not determinable, what about Vibration problems during a washing operation can lead.

Aus der JP 04 250 197 A ist ein Dämpfer einer Waschmaschine bekannt. Der Dämpfer weist ein Gehäuse mit einem darin verschiebbar geführten Stößel auf. Die Dämpfungsstärke des Dämpfers ist elektrisch verstellbar.From JP 04 250 197 A a damper of a washing machine is known. The damper has a housing with a slidably guided therein Pestle. The damping strength of the damper is electrically adjustable.

Aus der DE 22 04 325 C2 ist eine Trommelwaschmaschine mit Federbeinen oder Reibungsdämpfern zur Dämpfung der Schwingungen des Wasch-Aggregats bekannt. Diese weisen jeweils ein Gehäuse mit einem darin verschiebbar geführten Stößel auf. Zur Bestimmung der Einschub-Tiefe des Stößels ist dieser hohl mit einem Permanentmagneten versehen. Dem Gehäuse des Dämpfers in Ausschub-Richtung des Stößels vorgeordnet ist eine den Stößel umgebende Ringspule vorgesehen, die in der Lage ist, die Position des Permanentmagneten in der Ringspule zu detektieren. Durch die bekannte Vorrichtung ist es möglich, eine bestimmte vorgegebene kritische Einschub-Tiefe des Stößels zu ermitteln, und bei dieser beispielsweise den Schleudergang aufgrund besonders starker Schwingungen zu unterbrechen. Das Ergebnis ist insofern nur digital. Nachteilig an dieser Anordnung ist, daß die Position des Stößels nicht kontinuierlich ermittelt werden kann. Darüber hinaus wird durch die dem Gehäuse vorgeordnete Spule die Gesamtanordnung länger. Nachteilig ist ferner, daß die Bestimmung der Zuladung des Wasch-Aggregats nicht möglich ist, da in Folge der großen Haftreibung zwischen Reibbelag und Gehäuse die Einschub-Tiefe kein Maß für die Zuladung ist.DE 22 04 325 C2 discloses a drum washing machine with spring struts or friction dampers to dampen the vibrations of the washing unit known. These each have a housing with a slidable therein guided plunger. To determine the insertion depth of the The plunger is hollow with a permanent magnet. The housing The damper is arranged in the extension direction of the tappet provided the ring coil surrounding the plunger, which is able to position to detect the permanent magnet in the toroid. Through the known device, it is possible to set a certain predetermined critical Determine insertion depth of the plunger, and for example the Interrupt spin cycle due to particularly strong vibrations. The result is therefore only digital. The disadvantage of this arrangement is that the position of the plunger cannot be determined continuously. In addition, the overall arrangement is achieved by the coil arranged upstream of the housing longer. Another disadvantage is that the determination of the payload the washing unit is not possible because of the large Stiction between the friction lining and the housing no depth The measure of the payload is.

Der Erfindung liegt die Aufgabe zugrunde, einen Dämpfer mit einem Gehäuse und einem verschiebbar in diesem geführten Stößel bereitzustellen, bei dem die Einschub-Tiefe des Stößels in das Gehäuse möglichst einfach ermittelt werden kann und aus dieser die auf den Stößel wirkende Einschubkraft ermittelbar ist.The invention has for its object a damper with a housing and to provide a displaceably guided plunger, where the insertion depth of the plunger into the housing is as simple as possible can be determined and from this the insertion force acting on the plunger can be determined.

Die Aufgabe wird durch die Merkmale des Anspruchs 1 gelöst. Der Kern der Erfindung besteht darin, daß mit dem Gehäuse und dem Stößel jeweils ein Meßelement verbunden ist, deren relative Position zueinander durch elektrische Wechselwirkung ermittelt wird, wobei der Stößel über einen Teil der Einschub-Tiefe einen im wesentlichen haftreibungsfreien Leerhub aufweist. Dies ermöglicht es, z. B. das Gewicht der trockenen Wäsche und des Wassers im Ruhezustand zu messen und/oder dynamische Unwuchten während des Betriebes zu erfassen.The object is solved by the features of claim 1. The core the invention is that with the housing and the plunger each a measuring element is connected whose relative position to each other by electrical interaction is determined, the plunger over a Part of the insertion depth is an essentially idle stroke free of static friction having. This enables e.g. B. the weight of dry laundry and measure the water at rest and / or dynamic imbalance to be recorded during operation.

Weitere vorteilhafte Ausgestaltungen der Erfindung ergeben sich aus den Unteransprüchen.Further advantageous embodiments of the invention result from the Dependent claims.

Zusätzliche Merkmale und Einzelheiten der Erfindung ergeben sich aus der Beschreibung von 7 Ausführungsbeispielen anhand der Zeichnung. Es zeigen:

Fig. 1
eine Trommelwaschmaschine in schematischer Darstellung in Seitenansicht mit Federbeinen,
Fig. 2
eine Trommelwaschmaschine gemäß Fig. 1 in Vorderansicht,
Fig. 3
eine Trommelwaschmaschine in schematischer Darstellung in Seitenansicht mit Reibungsdämpfern,
Fig. 4
eine Trommelwaschmaschine gemäß Fig. 3 in Vorderansicht,
Fig 5
einen Längsschnitt eines Federbeins gemäß einer ersten Ausführungsform,
Fig. 6
einen Längsschnitt eines Federbeins gemäß einer zweiten Ausführungsform,
Fig. 7
einen Längsschnitt eines Reibungsdämpfers gemäß einer ersten Ausführungsform,
Fig. 8
einen Längsschnitt eines Reibungsdämpfers gemäß einer zweiten Ausführungsform,
Fig. 9
einen Längsschnitt eines Reibungsdämpfers gemäß einer dritten Ausführungsform,
Fig. 10
einen Längsschnitt eines Reibungsdämpfers gemäß einer gegenüber Fig. 9 geringfügig geänderten vierten Ausführungsform,
Fig. 11
einen Längsschnitt eines Reibungsdämpfers gemäß einer gegenüber Fig. 8 geringfügig geänderten fünften Ausführungsform und
Fig. 12
eine Ausschnittvergrößerung des Reibungsdämpfers gegemäß Fig. 11.
Additional features and details of the invention result from the description of 7 exemplary embodiments with reference to the drawing. Show it:
Fig. 1
a drum washing machine in a schematic representation in side view with struts,
Fig. 2
1 in front view,
Fig. 3
a drum washing machine in a schematic representation in side view with friction dampers,
Fig. 4
3 in front view,
Fig. 5
2 shows a longitudinal section of a spring strut according to a first embodiment,
Fig. 6
2 shows a longitudinal section of a spring strut according to a second embodiment,
Fig. 7
2 shows a longitudinal section of a friction damper according to a first embodiment,
Fig. 8
2 shows a longitudinal section of a friction damper according to a second embodiment,
Fig. 9
2 shows a longitudinal section of a friction damper according to a third embodiment,
Fig. 10
6 shows a longitudinal section of a friction damper according to a fourth embodiment, which has been slightly modified compared to FIG. 9,
Fig. 11
a longitudinal section of a friction damper according to a slightly different from FIG. 8 fifth embodiment and
Fig. 12
an enlarged section of the friction damper according to FIG. 11.

Die in den Fig. 1 und 2 dargestellte Trommelwaschmaschine mit waagrechter Trommel-Achse 1 weist ein schwingungsfähiges Wasch-Aggregat 2 mit einem Antriebs-Motor 3 auf, der eine nicht im einzelnen dargestellte Wasch-Trommel über einen Riemen-Trieb 4 antreibt. Weitere mit dem Wasch-Aggregat 2 verbundenen Bestandteile, beispielsweise ein Getriebe, sind der Einfachheit halber nicht dargestellt. Das schwingungsfähige Wasch-Aggregat 2 ist über zwei nachfolgend genauer beschriebene Federbeine 5 gegenüber einem auf dem Boden 6 stehenden, einen Grundrahmen bildenden Maschinen-Gestell 7 abgestützt. Ein das Wasch-Aggregat 2 umgebendes Waschmaschinen-Gehäuse 8 ist gegenüber dem Maschinen-Gestell 7 abgestützt und mit diesem verbunden. Die Eingabe und Entnahme von Wäsche erfolgt durch eine an einer Stirnseite 9 des Wasch-Aggregats 2 angeordnete Klappe 10. Jedes Federbein 5 weist ein rohrförmiges Gehäuse 11 mit einer Mittel-Längs-Achse 12 auf, in dem koaxial ein Stößel 13 verschiebbar geführt ist. Im Bereich des freien Endes des Stößels 13 ist ein Anschlag 14 befestigt. Eine den außerhalb des Gehäuses 11 befindlichen Abschnitt des Stößels 13 umgebende, vorgespannte Schrauben-Druckfeder 15 ist gegenüber dem Anschlag 14 einerseits und dem stößelaustrittsseitigen Ende des Gehäuses 11 andererseits abgestützt, so daß der Stößel 13 gegen die Kraft der Feder 15 in das Gehäuse 11 einschiebbar ist. Am freien Ende des Stößels 13 ist eine elastische Anlenkung 16 vorgesehen. Diese weist ein mit dem Wasch-Aggregat 2 verbundenes Lager 17 auf, das über elastische Blöcke 18 mit dem Stößel 13 verspannt ist. In gleicher Weise ist das freie Ende des Gehäuses 11 an dem Maschinen-Gestell 7 angelenkt.The drum washing machine shown in FIGS. 1 and 2 with horizontal Drum axis 1 has a vibratory washing unit 2 with a drive motor 3, which is not shown in detail Washing drum drives via a belt drive 4. More with the Washing unit 2 connected components, for example a gear, are not shown for the sake of simplicity. The vibratory Washing unit 2 is over two struts described in more detail below 5 compared to a standing on the floor 6, a base frame forming machine frame 7 supported. A surrounding the washing unit 2 Washing machine housing 8 is opposite the machine frame 7 supported and connected to this. The input and removal of laundry is carried out by an on an end face 9 of the washing unit 2 arranged flap 10. Each strut 5 has a tubular housing 11 with a central longitudinal axis 12 in which a plunger 13 is displaceable coaxially is led. In the area of the free end of the plunger 13 is a Stop 14 attached. One located outside the housing 11 Section of the plunger 13 surrounding, prestressed helical compression spring 15 is opposite the stop 14 on the one hand and the ram outlet side End of the housing 11 supported on the other hand, so that the plunger 13th can be inserted into the housing 11 against the force of the spring 15. Outdoors An elastic link 16 is provided at the end of the plunger 13. This has a bearing 17 connected to the washing unit 2, which via elastic blocks 18 is clamped with the plunger 13. In the same way the free end of the housing 11 is articulated on the machine frame 7.

Die Trommelwaschmaschine nach den Fig. 3 und 4 unterscheidet sich von der nach den Fig. 1 und 2 dadurch, daß das Wasch-Aggregat 2 an dem Maschinen-Gehäuse 8 mittels Schrauben-Zugfedern 19 aufgehängt ist. Die Zugfedern 19 sind einerseits an Ösen 20 angebracht, die im oberen Bereich des Wasch-Aggregats 2 angebracht sind. Andererseits sind sie an Ösen 21 aufgehängt, die an der Deckplatte 22 des Waschmaschinen-Gehäuses 8 ausgebildet sind. An der Unterseite des Wasch-Aggregats 2 sind in Längsrichtung mittig zwei nachfolgend genauer beschriebene Reibungsdämpfer 23 angebracht, die mit dem Maschinen-Gestell 7 verbunden sind. Jeder Reibungsdämpfer 23 weist ein zylindrisches Gehäuse 24 mit einer Mittel-Längs-Achse 25 auf, in dem koaxial ein Stößel 26 verschiebbar geführt ist. An dem stößelaustrittsseitigen Ende 27 des Gehäuses 24 ist in diesem ein Dämpfungs-Gehäuse 28 ausgebildet. Darin ist ein Reibungs-Dämpfungs-Belag 29 befestigt, der umfangsseitig gegen den Stößel 26 anliegt. Der Stößel 26 weist an seinem freien Ende eine Gelenk-Büchse 30 als Anlenkelement auf, mittels derer der Reibungsdämpfer 23 an einem Lager 36 am Wasch-Aggregat 2 so angebracht ist, daß der Reibungsdämpfer 23 um eine Schwenkachse 32 relativ zum Wasch-Aggregat 2 schwenkbar ist, die parallel zur Trommel-Achse 1 verläuft. Am äußeren Ende 33 des Gehäuses 24 ist ebenfalls eine Gelenk-Büchse 34 angebracht, deren Schwenkachse 35 gleichermaßen wie die Schwenkachse 32 die Mittel-Längs-Achse 25 senkrecht schneidet. Mit dieser Gelenk-Büchse 34 wird der Reibungsdämpfer 23 an einem Lager 31 am Maschinen-Gestell 7 so angebracht, daß die Schwenkachse 35 ebenfalls parallel zur Trommel-Achse 1 verläuft.The drum washing machine according to FIGS. 3 and 4 differs from 1 and 2 in that the washing unit 2 on the machine housing 8 is suspended by means of helical tension springs 19. The Tension springs 19 are attached to eyelets 20 on the one hand, in the upper area of the washing unit 2 are attached. On the other hand, they are on eyelets 21 suspended on the cover plate 22 of the washing machine housing 8 are trained. At the bottom of the washing unit 2 are in the longitudinal direction in the middle two friction dampers described in more detail below 23 attached, which are connected to the machine frame 7. Everyone Friction damper 23 has a cylindrical housing 24 with a central longitudinal axis 25, in which a plunger 26 is guided coaxially. At the tappet exit end 27 of the housing 24 is in this Damping housing 28 is formed. Inside is a friction-damping coating 29 attached, which abuts the plunger 26 on the circumferential side. The pestle 26 has at its free end an articulated sleeve 30 as a link element by means of which the friction damper 23 on a bearing 36 on Washing unit 2 is mounted so that the friction damper 23 by one Pivot axis 32 is pivotable relative to the washing unit 2, which is parallel runs to drum axis 1. At the outer end 33 of the housing 24 an articulated sleeve 34 is also attached, the pivot axis 35 equally as the pivot axis 32, the central longitudinal axis 25 perpendicular cuts. With this joint sleeve 34, the friction damper 23 attached to a bearing 31 on the machine frame 7 so that the Pivot axis 35 also runs parallel to drum axis 1.

Im folgenden wird unter Bezugnahme auf Fig. 5 der Aufbau des Federbeins 5 gemäß einer ersten Ausführungsform genauer beschrieben. Am im Gehäuse-Innenraum 37 des Gehäuses 11 befindlichen Ende des Stößels 13 ist ein Dämpfungs-Kolben 38 vorgesehen, der eine Ringnut 39 aufweist, die in Längsrichtung durch ringförmige Anschläge 40, 41 begrenzt wird, die einteilig mit dem Dämpfungs-Kolben 38 ausgebildet sind. In der Ringnut 39 ist ein ringzylindrisch ausgebildeter Dämpfungs-Ring 42 angeordnet, der außenumfangsseitig eine Ringnut 43 aufweist, in der ein Reibungs-Dämpfungs-Belag 44 vorgesehen ist. Der Dämpfungs-Ring 42 ist in der Ringnut 39 angenähert reibungsfrei gegenüber dem Dämpfungs-Kolben 38 verschiebbar. Der Reibungs-Dämpfungs-Belag 44 liegt reibend an der Innenseite 45 des Gehäuses 11 an. Der Reibungs-Dämpfungs-Belag 44 kann aus mit Schmiermittel imprägniertem, geschäumtem, geschlossenzelligem Polyurethan bestehen. Im Bereich des stößelaustrittsseitigen Endes 46 des Gehäuses 11 ist eine ringzylindrisch ausgebildete Führungs-Buchse 47 vorgesehen, die über Sicken 48 mit dem Gehäuse 11 verbunden ist. In der Führungs-Buchse 47 ist der Stößel 13 geführt verschiebbar. Zur Stabilisierung weist die Führungs-Buchse 47 ein entgegen der Einschub-Richtung 49 vorstehendes, einteilig mit der Führungs-Buchse 47 ausgebildetes FührungsRohr 50 auf, das von einem ringzylindrischen Anschlag 51 umgeben ist, gegenüber dem die Schrauben-Druckfeder 15 an ihrem in Einschub-Richtung 49 gelegenen Ende abgestützt ist.The structure of the shock absorber will now be described with reference to FIG 5 according to a first embodiment. On the inside of the housing 37 of the housing 11 is the end of the plunger 13 a damping piston 38 is provided which has an annular groove 39 which in Longitudinal direction is limited by annular stops 40, 41, which are in one piece are formed with the damping piston 38. In the ring groove 39 is a ring-cylindrical damping ring 42 is arranged, the has an annular groove 43 on the outer circumference, in which a friction-damping coating 44 is provided. The damping ring 42 is in the Annular groove 39 approximately frictionless with respect to the damping piston 38 displaceable. The friction-damping lining 44 is rubbing against the inside 45 of the housing 11. The friction damping pad 44 can made of foamed, closed-cell impregnated with lubricant Polyurethane exist. In the area of the tappet outlet end 46 Housing 11 is a ring-cylindrical guide bushing 47 is provided, which is connected to the housing 11 via beads 48. In the guide socket 47, the plunger 13 is guided displaceably. For stabilization has the guide bushing 47 protruding against the insertion direction 49, Guide tube formed in one piece with the guide bushing 47 50, which is surrounded by an annular cylindrical stop 51, compared to the helical compression spring 15 on in the insertion direction 49 located end is supported.

Das Federbein 5 weist eine Stößelpositions-Meßeinrichtung zur Erfassung der Einschub-Tiefe T des Stößels 13 in das Gehäuse 11 auf. Die Meßeinrichtung weist einen ringzylindrisch ausgebildeten Geber 52 auf, der am in Einschub-Richtung 49 liegenden Ende des Dämpfungs-Kolbens 38 koaxial zur Mittel-Längs-Achse 12 befestigt ist. Der Geber 52 besteht aus Metall, insbesondere Eisen oder einem anderen ferritischen Werkstoff. Das Gehäuse 11 besteht aus einem magnetisch permeablen, insbesondere nichtmetallischen Werkstoff. Die Meßeinrichtung weist ferner eine Spulen-Einheit 53 auf, die bei dem in Fig. 5 dargestellten Fall aus zwei in Reihe geschalteten Spulen 54 und 55 besteht. Die Spulen 54, 55 sind über elektrische Verbindungsleitungen 56 mit einer Auswerte-Einheit 57 verbunden. Die Spulen-Einheit 53 kann insbesondere aus einer oder zwei benachbart zueinander angeordneten, das Gehäuse 11 ringzylindrisch umgebenden Spulen bestehen. Die Spulen-Einheit 53 erstreckt sich in Längsrichtung, insbesondere mindestens über die Länge, die vom Geber 52 bei maximaler Einschub-Tiefe T des Stößels 13 überstrichen wird.The strut 5 has a tappet position measuring device for detection the insertion depth T of the plunger 13 in the housing 11. The measuring device has an annular-cylindrical sensor 52, which on the Insert direction 49 lying end of the damping piston 38 coaxially is attached to the central longitudinal axis 12. The encoder 52 is made of metal, especially iron or another ferritic material. The housing 11 consists of a magnetically permeable, in particular non-metallic Material. The measuring device also has a coil unit 53 on, in the case shown in Fig. 5 of two connected in series Coils 54 and 55 exist. The coils 54, 55 are via electrical connection lines 56 connected to an evaluation unit 57. The coil unit 53 can in particular consist of one or two adjacent to one another Arranged coils surrounding the housing 11 exist. The coil unit 53 extends in the longitudinal direction, in particular at least over the length of the encoder 52 at maximum insertion depth T of the plunger 13 is swept.

Für den Fall, daß die Spulen-Einheit 53 genau eine Spule 54 aufweist, handelt es sich bei der Meßeinrichtung um einen sogenannten induktiven Wegaufnehmer. Bei diesem wird durch das Einschieben des Gebers 52 in den Innenraum der Spule 54 deren Induktivität verändert. Die Auswertung der Induktivität der Spule 54 erfolgt an einer in der Elektrotechnik allgemein bekannten Viertelbrücke. Vorteilhaft an dieser Anordnung ist der gänzlich einfache Aufbau. Nachteilig ist, daß lediglich in einem engen Bereich um den Arbeitspunkt einer vorgegebenen Einschub-Tiefe T Änderungen der Einschub-Tiefe T proportional zur Induktivitätsänderung sind.In the event that the coil unit 53 has exactly one coil 54, acts it is a so-called inductive in the measuring device Displacement transducer. This is by pushing the encoder 52 in the interior of the coil 54 changes its inductance. The evaluation The inductance of the coil 54 takes place on one in general in electrical engineering known quarter bridge. The advantage of this arrangement is that completely simple structure. The disadvantage is that only in a narrow area around the working point of a given insertion depth T changes the insertion depth T are proportional to the change in inductance.

Für den Fall, daß die Spulen-Einheit 53 zwei in Reihe geschaltete Spulen 54 und 55, wie in Fig. 5 gezeigt, aufweist, handelt es sich bei der Meßeinrichtung um eine sogenannte Differentialdrossel. An die Verbindungsleitungen 56 wird ein elektrisches Signal angelegt bzw. von diesen abgegriffen. Durch ein Verschieben des Gebers 52 im Innenraum der Spulen 54, 55 wird deren Induktivität verändert. Über ungefähr 80 % der Länge der Spulen 54, 55 besteht im wesentlichen ein linearer Zusammenhang zwischen einer Änderung der Einschub-Tiefe T und der Induktivität.In the event that the coil unit 53 two coils connected in series 54 and 55, as shown in Fig. 5, is the measuring device a so-called differential choke. To the connecting lines 56 an electrical signal is applied or tapped by them. By moving the encoder 52 in the interior of the coils 54, 55 their inductance is changed. About 80% of the length of the coils 54, 55 there is essentially a linear relationship between a change in the insertion depth T and the inductance.

Die Auswertung der Einschub-Tiefe T über die Induktivitätsänderung setzt voraus, daß der Geber 52 aus einem ferromagnetischen Material, beispielsweise also aus Eisen/Stahl, besteht. Wenn eine Auswertung der Einschub-Tiefe über einen Wirbelstromeffekt erfolgt, dann sollte der Geber 52 aus einem nichtferromagnetischen, aber elektrisch leitendem Material bestehen, beispielsweise also aus Aluminium.The evaluation of the insertion depth T via the change in inductance sets advance that the encoder 52 made of a ferromagnetic material, for example So made of iron / steel. If an evaluation of the insertion depth via an eddy current effect, then the encoder 52 should consist of a non-ferromagnetic but electrically conductive material, for example made of aluminum.

Zum Betrieb der Waschmaschine wird das Wasch-Aggregat 2 zunächst mit Wäsche beladen. Hierdurch sinkt der Stößel 13 von der in Fig. 5 dargestellten Ausgangsposition in das Gehäuse 11, so daß die Einschub-Tiefe T vergrößert wird. Das Einschieben des Stößels 13 erfolgt im wesentlichen haftreibungsfrei über einen Bereich ΔT, bis der Dämpfungs-Ring 42 in Anschlag mit dem Anschlag 41 kommt. Der Stößel 13 weist somit einen Leerhub auf. In diesem Bereich ist die Änderung ΔT der Einschub-Tiefe T im wesentlichen proportional zur auf den Stößel 13 wirkenden Einschub-Kraft, so daß durch eine Messung der Änderung ΔT der Einschub-Tiefe T der Federbeine 5 der Waschmaschine das Gewicht der eingefüllten Wäsche gemessen werden kann. Über die Federkonstante der Feder 15 und die Änderung ΔT kann die Einschubkraft berechnet werden. Bei einem weiteren Einschieben des Stößels 13 in das Gehäuse 11 wird die Bewegung nun durch den Reibungs-Dämpfungs-Belag 44 gedämpft. Die Federkraft der Feder 15 ist derart eingestellt, daß während des Beladens der Dämpfungs-Ring 42 nicht in Anschlag mit dem Anschlag 41 kommt. Darüber hinaus ist es möglich, die Menge des zugeführten Wassers zu messen sowie eine durch ungleichmäßige Beladung entstehende Unwucht im Wasch-Aggregat 2 durch unterschiedliche Einschub-Tiefen T zwischen den verschiedenen Federbeinen 5 zu messen. Die Ermittlung der Zuladungs-Masse des Wasch-Aggregats 2 und einer ggf. vorliegenden Unwucht erfolgt durch die Auswerte-Einheit 57. Während des Betriebs und insbesondere während des Schleudervorgangs gerät das Wasch-Aggregat 2 in Schwingungen, deren Amplitude so groß ist, daß der Dämpfungs-Ring 42 abwechselnd in Anschlag mit den Anschlägen 40 und 41 kommt, so daß die Bewegung des Stößels 13 durch den Reibungs-Dämpfungs-Belag 44 gedämpft wird. Die Amplitude der Schwingungen kann durch die Messung der Einschub-Tiefe T zu jedem Zeitpunkt ermittelt werden. Sollten die Amplituden der Schwingungen zu groß werden, so kann basierend auf Signalen der Auswerte-Einheit 57 die Schleuderdrehzahl reduziert oder der Schleudervorgang abgebrochen werden. Es ist möglich, bei der eingangs beschriebenen Trommelwaschmaschine lediglich eines der Federbeine 5 mit einer Stößelpositions-Meßeinrichtung zu versehen. Das andere Federbein 5 kann handelsüblich ausgebildet sein.To operate the washing machine, the washing unit 2 is first used Load laundry. As a result, the plunger 13 sinks from that shown in FIG. 5 Starting position in the housing 11, so that the insertion depth T is enlarged. The plunger 13 is inserted essentially free of static friction over a range ΔT until the damping ring 42 stops comes with the stop 41. The plunger 13 thus has an idle stroke on. In this range the change ΔT of the insertion depth T im essentially proportional to the push-in force acting on the plunger 13, so that by measuring the change ΔT in the insertion depth T the Struts 5 of the washing machine the weight of the laundry can be measured. About the spring constant of the spring 15 and the change ΔT the insertion force can be calculated. Another one Pushing the plunger 13 into the housing 11, the movement is now damped by the friction-damping coating 44. The spring force of the Spring 15 is set such that the damping ring during loading 42 does not come into contact with the stop 41. Beyond that it is possible to measure the amount of water supplied as well as a unbalance in the washing unit caused by uneven loading 2 due to different insertion depths T between the different ones To measure struts 5. The determination of the load mass of the washing unit 2 and any imbalance that may be present is carried out by the evaluation unit 57. During operation and especially during Spin process, the washing unit 2 vibrates, the The amplitude is so great that the damping ring 42 alternately stops comes with the stops 40 and 41, so that the movement of the Ram 13 is damped by the friction-damping coating 44. The The amplitude of the vibrations can be measured by measuring the insertion depth T can be determined at any time. Should the amplitudes of the Vibrations can become too large, based on signals from the evaluation unit 57 reduces the spin speed or the spin cycle be canceled. It is possible with the one described at the beginning Drum washing machine only one of the struts 5 with a plunger position measuring device to provide. The other strut 5 can be commercially available be trained.

Im folgenden wird unter Bezugnahme auf Fig. 6 eine zweite Ausführungsform des Federbeins 5' beschrieben. Identische Teile erhalten dieselben Bezugszeichen wie bei dem Federbein 5 gemäß der ersten Ausführungsform, auf deren Beschreibung hiermit verwiesen wird. Konstruktiv unterschiedliche, jedoch funktionell gleichartige Teile erhalten dieselben Bezugszeichen mit einem hochgesetzten Strich. Der zentrale Unterschied gegenüber der ersten Ausführungsform besteht darin, daß der Dämpfungs-Ring 42' nicht wie bei der ersten Ausführungsform im wesentlichen kräftefrei relativ zum Dämpfungs-Kolben 38' verschiebbar ist. Zwischen dem Dämpfungs-Ring 42' und den Anschlägen 40' bzw. 41' sind koaxial zur Mittel-Längs-Achse 12 ringzylindrisch ausgebildete, vorgespannte Druckfedern 58 bzw. 59 vorgesehen. Diese stellen sicher, daß der Dämpfungs-Ring 42' regehnäßig in der in Fig. 6 dargestellten Ruhelage mittig zwischen den Anschlägen 40' und 41' angeordnet ist. Auf die im Rahmen des ersten Ausführungsbeispiels beschriebene Funktion haben die Druckfedern 58, 59 insofern Einfluß, als bei einem geringfügigen Einschieben des Stößels 13 nicht nur die Schrauben-Druckfeder 15, sondern auch die Druckfeder 59 gestaucht werden, was bei der Bestimmung der Masse des Wasch-Aggregats 2 aus der Einschub-Tiefe T durch die Auswerte-Einheit 57 zu berücksichtigen ist.A second embodiment will now be described with reference to FIG. 6 of the strut 5 'described. Identical parts get the same Reference numerals as in the strut 5 according to the first embodiment, to the description of which reference is hereby made. Constructively different, however, functionally similar parts are given the same reference numerals with a raised line. The key difference compared the first embodiment is that the damping ring 42 'is not essentially free of forces as in the first embodiment is displaceable relative to the damping piston 38 '. Between the Damping ring 42 'and the stops 40' and 41 'are coaxial to Center longitudinal axis 12 ring-cylindrical, preloaded compression springs 58 or 59 provided. These ensure that the damping ring 42 'rainily in the rest position shown in Fig. 6 in the middle between the stops 40 'and 41' is arranged. In the context of the first The compression springs 58, 59 have the function described in the exemplary embodiment to the extent that when the plunger is slightly pushed in. 13 not only the helical compression spring 15, but also the compression spring 59 be upset what when determining the mass of the washing aggregate 2 from the insertion depth T through the evaluation unit 57 is considered.

Im folgenden wird unter Bezugnahme auf Fig. 7 der Reibungs-Dämpfer 23 gemäß einer ersten Ausführungsform genauer beschrieben. Am in Einschub-Richtung 60 gelegenen Ende des Stößels 26 ist ein Führungs-Kolben 61 ausgebildet, der zwei längs zueinander versetzte, einteilig damit ausgebildete ringförmige Führungs-Stege 62, 63 aufweist, zwischen denen eine Ringnut 64 ausgebildet ist. Die Führungs-Stege 62, 63 liegen führend an der Innenwand 65 des Gehäuses 24 an. In der Ringnut 64 ist ein ringzylindrisch ausgebildeter Dämpfungs-Ring 66 vorgesehen, der entlang des Außenumfangs eine Belags-Ringnut 67 aufweist, in der der Reibungs-Dämpfungs-Belag 29 angeordnet ist, welcher reibend an der Innenwand 65 anliegt. Der Reibungs-Dämpfungs-Belag 29 besteht aus mit Schmiermittel imprägniertem, geschäumten Kunststoff oder Filz. Der Führungs-Kolben 61 ist im Bereich der Längserstreckung der Ringnut 64 im wesentlichen haftreibungsfrei gegenüber dem Dämpfungs-Ring 66 verschiebbar. Am entgegen der Einschub-Richtung 60 liegende Ende des Gehäuses 24 ist dieses mit einer Sicke 68 versehen, so daß der Stößel 26 aus diesem nicht herausgezogen werden kann. Der Stößel 26 und der Führungs-Kolben 61 sind einteilig aus Kunststoff hergestellt. Das Gehäuse 24 besteht aus einem nichtmetallischen Werkstoff, insbesondere Kunststoff, oder aus einem magnetisch permeablen Metall.The friction damper 23 will now be described with reference to FIG. 7 described in more detail according to a first embodiment. On in the direction of insertion 60 located end of the plunger 26 is a guide piston 61 formed, the two longitudinally offset to one another, formed in one piece therewith has annular guide webs 62, 63, between which one Ring groove 64 is formed. The guide webs 62, 63 are in a leading position the inner wall 65 of the housing 24. In the annular groove 64 is an annular cylinder trained damping ring 66 provided along the outer circumference has a lining ring groove 67 in which the friction damping lining 29 is arranged, which rubs against the inner wall 65 is applied. The friction-damping coating 29 consists of lubricant impregnated, foamed plastic or felt. The guide piston 61 is essentially in the region of the longitudinal extent of the annular groove 64 Slidable relative to the damping ring 66. At the opposite to the insertion direction 60 is the end of the housing 24 provided with a bead 68 so that the plunger 26 is not pulled out of it can be. The plunger 26 and the guide piston 61 are made in one piece from plastic. The housing 24 consists of a non-metallic material, in particular plastic, or from a magnetic permeable metal.

Die Stößelpositions-Meßeinrichtung weist einen am in Einschub-Richtung 60 liegenden Ende des Stößels 26 koaxial zur Mittel-Längs-Achse 25 angeordneten, ringzylindrischen Geber 69 auf. Ferner ist eine Spulen-Einheit 70 mit zwei benachbart zueinander angeordneten, das Gehäuse 24 ringzylindrisch umgebenden Spulen 71, 72 vorgesehen, die über Verbindungsleitungen 73 mit einer Auswerte-Einheit 74 elektrisch leitend verbunden sind. Bezüglich des Aufbaus des Gebers 69 und der Spulen-Einheit 70 wird auf die Beschreibung des Gebers 52 und der Spulen-Einheit 53 des Federbeins 5 gemäß der ersten Ausführungsform verwiesen.The plunger position measuring device has one in the direction of insertion 60 lying end of the plunger 26 arranged coaxially to the central longitudinal axis 25, ring-cylindrical encoder 69. Furthermore, a coil unit 70 with two arranged adjacent to each other, the housing 24 is cylindrical surrounding coils 71, 72 are provided, which via connecting lines 73 are electrically conductively connected to an evaluation unit 74. With regard to the structure of the encoder 69 and the coil unit 70 is on the description of the encoder 52 and the coil unit 53 of the shock absorber 5 according to the first embodiment.

Hinsichtlich der Beschreibung der Betriebsfunktion des Reibungsdämpfers 23 wird auf die des Federbeins 5 verwiesen. Wie beim Federbein 5 ist der Stößel 26 solange über eine einen Leerhub darstellende Änderung ΔT der Einschub-Tiefe T im wesentlichen haftreibungsfrei einschiebbar, bis der Steg 63 mit dem Dämpfungs-Ring 66 in Anschlag kommt. Wird die Bewegung in die gleiche Richtung fortgesetzt, so ist die Reibungs-Kraft zwischen dem Reibungs-Dämpfungs-Belag 29 und der Innenwand 65 zu überwinden. Der Reibungs-Dämpfer 23 ist somit gleichermaßen wie das Federbein 5 dazu geeignet, sowohl die Zuladungsmenge des Wasch-Aggregats 2 und ggf. Unwuchten zu messen als auch die Amplitude der Wasch-Aggregats-Schwingungen im Schleudergang zu ermitteln. Die Auswerte-Einheit 74 muß anders als beim Federbein 5 zusätzlich die durch die Schrauben-Zugfedern 19 auf das Wasch-Aggregat 2 ausgeübten Gegenkräfte berücksichtigen. Wie bei dem Federbein 5' gemäß der zweiten Ausführungsform ist es möglich, den Dämpfungs-Ring 29 mit Druckfedern 58, 59 gegenüber den Stegen 62 bzw. 63 abzustützen, wodurch dieselben dort beschriebenen Wirkungen entstehen.Regarding the description of the operational function of the friction damper 23 is referred to that of the strut 5. As with the strut 5 is the Plunger 26 as long as a change ΔT representing an idle stroke Insertion depth T can be inserted essentially without static friction until the Web 63 comes into stop with the damping ring 66. Will the movement continued in the same direction, the frictional force is between to overcome the friction-damping coating 29 and the inner wall 65. The friction damper 23 is thus the same as the strut 5 suitable for both the load of the washing unit 2 and, if necessary, to measure unbalance as well as the amplitude of the washing unit vibrations to determine in the spin cycle. The evaluation unit 74 must be different from the strut 5 additionally by the Coil tension springs 19 exerted on the washing unit 2 opposing forces consider. As with the strut 5 'according to the second embodiment it is possible to mount the damping ring 29 with compression springs 58, 59 to support against the webs 62 and 63, whereby the same there described effects arise.

Im folgenden wird unter Bezugnahme auf Fig. 8 der Reibungsdämpfer 23' gemäß einer zweiten Ausführungsform beschrieben. Identische Teile erhalten dieselben Bezugszeichen wie bei dem Reibungsdämpfer 23 gemäß der ersten Ausführungsform, auf deren Beschreibung hiermit verwiesen wird. Konstruktiv unterschiedliche, jedoch funktionell gleichartige Teile erhalten dieselben Bezugszeichen mit einem hochgesetzten Strich. Der zentrale Unterschied gegenüber der ersten Ausführungsform besteht in dem Aufbau der Stößelpositions-Meßeinrichtung. Am in Einschub-Richtung 60 gelegenen Ende des Gehäuses 24 ist ein Boden 75 über eine Sicke 76 mit dem Gehäuse 24 verbunden vorgesehen. An dem Boden 75 ist ein koaxial zur Mittel-Längs-Achse 25 angeordneter, entgegen der Einschub-Richtung 60 vorstehenden Zapfen 77 angeordnet, an dessen freiem Ende der Geber 69' befestigt ist. Der Zapfen 77 ist aus einem nichtmetallischen Werkstoff, wie z. B. Kunststoff, gefertigt. Der Geber 69' ist von dem Material des Zapfens 77, insbesondere Kunststoff, umschlossen. Der Führungs-Kolben 61' weist koaxial zur Mittel-Längs-Achse 25 einen am in Einschub-Richtung 60 gelegenen Ende offenen Einschub-Kanal 78 auf, der so ausgebildet ist, daß der Zapfen 77 mit dem Geber 69' in diesen beim Einschieben des Stößels 26' kontaktfrei einschiebbar ist. Die Spulen-Einheit 70' weist zwei benachbart zueinander angeordnete Spulen 71' und 72' auf, die den Einschub-Kanal 78 ringzylindrisch umgeben und die benachbart zueinander an dem Führungs-Kolben 61' angeordnet sind. Die Verbinduhgsleitungen 73' sind aus dem Stößel 26' im Bereich von dessen freiem Ende derart herausgeführt, daß sie ein Einschieben des Stößels 26' nicht beeinträchtigen. Hinsichtlich des weiteren Aufbaus und der Funktionsweise der Stößelpositions-Meßeinrichtung wird auf die Beschreibung des ersten Ausführungsbeispiels des Reibungsdämpfers 23 verwiesen. Der wesentliche Unterschied besteht darin, daß der Geber 69' ortsfest mit dem Gehäuse 24 verbunden ist und die Spulen-Einheit 70' mit dem Stößel 26 in das Gehäuse 24 einschiebbar ist. Dies hat den Vorteil, daß das Gehäuse 24 aus einem beliebigen Material, wie z. B. Stahl, gefertigt werden kann, da die Zusammenwirkung zwischen Geber 69' und Spulen-Einheit 70' vollständig innerhalb des Gehäuses 24 stattfindet.In the following, with reference to FIG. 8, the friction damper 23 ' described according to a second embodiment. Obtain identical parts the same reference numerals as in the friction damper 23 according to the first embodiment, to the description of which reference is hereby made becomes. Structurally different, but functionally similar parts get the same reference numbers with a prime. The The central difference from the first embodiment is that Structure of the ram position measuring device. On in slot direction 60 located end of the housing 24 is a bottom 75 with a bead 76 provided connected to the housing 24. At the bottom 75 is a coaxial to the central longitudinal axis 25, against the direction of insertion 60 protruding pin 77 arranged at the free end of the encoder 69 'is attached. The pin 77 is made of a non-metallic material, such as B. plastic. The encoder 69 'is made of the material of the Pin 77, especially plastic, enclosed. The guide piston 61 'has a coaxial to the central longitudinal axis 25 in the insertion direction 60 located end open slot channel 78, which is formed is that the pin 77 with the encoder 69 'in this when inserted of the plunger 26 'can be inserted without contact. The coil unit 70 'has two adjacent coils 71 'and 72' on the Insert channel 78 surrounded by a ring cylinder and the adjacent to each other are arranged on the guide piston 61 '. The connecting lines 73 'are from the plunger 26' in the region of its free end out that they do not interfere with the insertion of the plunger 26 '. With regard to the further construction and the functioning of the plunger position measuring device will refer to the description of the first embodiment of the friction damper 23 referenced. The main difference consists in the encoder 69 'being stationary with the housing 24 is connected and the coil unit 70 'with the plunger 26 in the housing 24 can be inserted. This has the advantage that the housing 24 from one any material, such as B. steel, can be made because of the interaction between encoder 69 'and coil unit 70' completely within of the housing 24 takes place.

Im folgenden wird unter Bezugnahme auf Fig. 9 der Reibungsdämpfer 23" gemäß einer dritten Ausführungsform beschrieben. Identische Teile erhalten dieselben Bezugszeichen wie der Reibungsdämpfer 23 gemäß der ersten Ausführungsform, auf deren Beschreibung hiermit verwiesen wird. Konstruktiv unterschiedliche, jedoch funktionell gleichartige Teile erhalten dieselben Bezugszeichen mit zwei hochgesetzten Strichen. Das Gehäuse 24", dessen in Einschub-Richtung 60 gelegenes Ende mit einem Boden 79 verschlossen ist, weist am entgegen der Einschub-Richtung 60 gelegenen Ende einen Anschlagbund 80 auf, an den sich ein ringzylindrischer Aufnahme-Abschnitt 81 mit Rastnasen 82 aufweisenden Rastarmen 83 anschließt. In dem zwischen dem Aufnahme-Abschnitt 81 und dem Stößel 26" gebildeten Ringraum 84 ist der Dämpfungs-Ring 66" verschiebbar angeordnet. Der Dämpfungs-Ring 66" liegt außenumfangsseitig im wesentlichen haftreibungsfrei verschiebbar an der Innenseite des Aufnahme-Abschnitts 81 an. Auf der Innenseite weist der Dämpfungs-Ring 66" den Reibungs-Dämpfungs-Belag 29 auf, der reibend an dem Stößel 26" anliegt. Der Aufnahme-Abschnitt 81 ist durch einen ringzylindrisch ausgebildeten Deckel 85 mit Rastöffnungen 86, in die die Rastnasen 82 arretierend eingreifen, verschlossen. Auf der in Einschub-Richtung 60 weisenden Innenseite des Deckels 85 und der entgegen der Einschub-Richtung 60 weisenden Innenseite des Anschlagbundes 80 sind Anschläge 87 bzw. 88 vorgesehen. Der Stößel 26" weist einen aus Metall, insbesondere aus Stahl, gefertigten Reibungs-Abschnitt 89 auf, der in Kontakt mit dem Belag 29 steht. Im Bereich des Gehäuse-Innenraums 90 weist der Stößel 26" einen mit dem Abschnitt 89 verbundenen Geber-Trag-Abschnitt 91 auf, der aus einem nichtmetallischen Werkstoff, insbesondere Kunststoff, gefertigt ist. Im Bereich des in Einschub-Richtung 60 gelegenen Endes des Abschnitts 91 ist der Geber 69" angeordnet. Das Gehäuse 24" ist aus einem nichtmetallischen Werkstoff, insbesondere aus Kunststoff, gefertigt. Hinsichtlich des Aufbaus und der Funktionsweise des Gebers 69" und der Spulen-Einrichtung 70 wird auf die Beschreibung des Reibungsdämpfers 23 gemäß dem ersten Ausführungsbeispiel verwiesen.In the following, with reference to FIG. 9, the friction damper 23 " according to a third embodiment. Obtain identical parts the same reference numerals as the friction damper 23 according to the first Embodiment, the description of which reference is hereby made. constructive different but functionally similar parts are given the same Reference number with two prime lines. The housing 24 ", its end in the direction of insertion 60 closed with a bottom 79 is at the end opposite to the insertion direction 60 a stop collar 80 on which there is an annular cylindrical receiving section 81 with locking arms 82 having locking arms 83 connects. In that formed between the receiving section 81 and the plunger 26 " Annular space 84, the damping ring 66 "is slidably arranged Damping ring 66 "is on the outer circumference essentially free of static friction slidably on the inside of the receiving portion 81. On the inside, the damping ring 66 "has the friction damping coating 29, which abuts the plunger 26 ″. The receiving section 81 is through a ring-cylindrical cover 85 with latching openings 86, into which the latching lugs 82 engage in a locking manner, locked. On the inside of the Cover 85 and the inside pointing counter to the insertion direction 60 of the stop collar 80, stops 87 and 88 are provided. The Tappet 26 "has a friction section made of metal, in particular steel 89, which is in contact with the covering 29. In the area of the housing interior 90, the plunger 26 ″ has one with the section 89 connected encoder support section 91, which consists of a non-metallic Material, especially plastic, is made. In the area of Insert direction 60 located end of section 91 is the encoder 69 ". The housing 24" is made of a non-metallic material, especially made of plastic. In terms of construction and the functioning of the encoder 69 "and the coil device 70 to the description of the friction damper 23 according to the first embodiment directed.

Hinsichtlich der Beschreibung der Betriebsfunktion des Reibungsdämpfers 23" wird ebenfalls auf die des Reibungsdämpfers 23 verwiesen. Der zentrale. Unterschied besteht darin, daß bei kleinen Einschüben des Stößels 26" der Dämpfungs-Ring 66 in dem Aufnahme-Abschnitt 81 im wesentlichen haftreibungsfrei unter Bildung eines Leerhubs verschoben wird, bis dieser in Anschlag mit dem Anschlag 88 kommt. Die Auswertung der Zuladung des Wasch-Aggregats 2, einer möglichen Unwucht sowie die Ermittlung und Schwingungsamplituden ist somit gleichermaßen möglich. Es ist möglich, den Dämpfungs-Ring 66" mit Druckfedern gegenüber den Anschlägen 87, 88 vorzuspannen, wie dies für das Federbein 5' gemäß Fig. 6 beschrieben ist.Regarding the description of the operational function of the friction damper 23 "is also referred to that of the friction damper 23. The central one. The difference is that when the plunger is inserted small 26 "of the damping ring 66 in the receiving section 81 essentially is shifted free of static friction with the formation of an empty stroke until this comes into contact with the stop 88. The evaluation of the payload of the washing unit 2, a possible imbalance and the determination and vibration amplitudes are equally possible. It is possible, the damping ring 66 "with compression springs opposite the stops 87, 88 to be preloaded, as is the case for the spring strut 5 ′ according to FIG. 6 is described.

Der Reibungsdämpfer 23''' nach Fig. 10 gemäß einer vierten Ausführungsform unterscheidet sich von dem nach Fig. 9 nur dadurch, daß am Stößel 26''' nicht ein gesonderter Geber angebracht ist, sondern daß als Geber 69''' die Kante des Stößels 26''' dient, also deren im Gehäuse-Innenraum 90 befindliches Ende.10 according to a fourth embodiment differs from that of FIG. 9 only in that on the plunger 26 '' 'is not a separate encoder, but that as an encoder 69 '' 'serves the edge of the plunger 26' '', that is, in the interior of the housing 90 located end.

Im folgenden wird unter Bezugnahme auf die Figuren 11 und 12 der Reibungsdämpfer 23'''' gemäß einer fünften Ausführungsform beschrieben. The friction damper will now be described with reference to FIGS 23 '' '' according to a fifth embodiment.

Der Aufbau ähnelt dem in Fig. 8 dargestellten Reibungsdämpfer 23', auf dessen Beschreibung hiermit verwiesen wird. Identische Teile erhalten dieselben Bezugszeichen wie bei dem Reibungsdämpfer 23' gemäß der zweiten Ausführungsform. Konstruktiv unterschiedliche, jedoch funktionell gleichartige Teile erhalten dieselben Bezugszeichen mit vier hochgesetzten Strichen. Der Stößel 26' weist im Bereich seines gehäuseinnenseitigen Endes eine ringzylindrische Wand 92 auf, in der radial nach außen verlaufende Rast-Ausnehmungen 93 vorgesehen sind. Am in Einschub-Richtung 60 gelegenen Ende der Wand 92 ist der radial vorstehende, ringförmige Führungs-Steg 63 vorgesehen. Der Führungs-Kolben 61'''' weist im wesentlichen die Form einer ringzylindrischen Hülse auf, an deren entgegen der Einschub-Richtung 60 gelegenen Ende radial nach außen vorspringende Rastnasen 94 vorgesehen sind, die sich in verrastetem Eingriff mit den Rast-Ausnehmun-gen 93 befinden. Am in Einschub-Richtung 60 gelegenen Ende des Führungs-Kolbens 61'''' ist der radial nach außen vorspringende Führungs-Steg 62 vorgesehen, wobei die Ringnut 64 durch die Führungs-Stege 62 und 63 in axialer Richtung begrenzt wird. Wie bei der Ausführungsform gemäß Fig. 6 sind zwischen dem Dämpfungs-Ring 66 und dem Führungs-Steg 63 einerseits und dem Dämpfungs-Ring 66 und dem Führungs-Steg 62 andererseits zwei Druckfedern 95 bzw. 96 angeordnet, die dafür sorgen, daß der Dämpfungs-Ring 66 ungefähr mittig zwischen den beiden Stegen 62 und 63 angeordnet ist. An dem in Einschub-Richtung 60 liegenden Ende des Führungs-Kolbens 61'''' ist ein als Geber 69'''' ausgebildeter zylindrischer Ring 97 angeordnet, der in einer entsprechenden Ringnut 98 an der Innenseite des Führungs-Kolbens 61'''' festgelegt ist. Der Ring 97 besteht aus Metall, insbesondere aus Aluminium. Der aus Metall, insbesondere Eisen, bestehende zylinderförmige Zapfen 77 trägt die Spulen-Einheit 70'''', die aus einer auf der Oberfläche des Zapfens 77 angeordneten Spule 71', insbesondere aus Kupferdraht, besteht. Die Spule 71' ist gegenüber dem Zapfen 77 durch eine dünne Kunststoff-Schicht 102 isoliert, wobei auch die einzelnen Wicklungen der Spule 71' gegeneinander isoliert sind. An dem entgegen der Einschub-Richtung 60 liegenden Ende des Zapfens 77 ist ein radial gegenüber dem Zapfen 77 und der Spulen-Einheit 70'''' vorspringender Abstandhalter 99 vorgesehen, der einen runden Querschnitt besitzt, wobei zwischen dem Abstandhalter 99 und der Innenwand 100 des Führungskolbens 61'''' ein Spiel besteht. Durch den Abstandhalter 99 wird sichergestellt, daß die Spule 71' nicht in Kontakt mit dem Geber 69'''' kommt. Dies ist vor allem von Bedeutung, wenn Querkräfte auf den Reibungsdämpfer 23"" wirken, oder sich der Zapfen 77 verzieht. Die Verbindungs-Leitung 73"" ist von dem in Einschub-Richtung 60 liegenden Ende der Spule 71' durch den Boden 75 zu einem Stecker 101 geführt, von dem eine Verbindung zur Auswerte-Einheit 74 herstellbar ist. Vorteilhaft an dieser Anordnung ist, daß das Gehäuse 24 ohne Nachteil auf die Stößelpositions-Meßeinrichtung aus Metall gewählt werden kann. Darüber hinaus befinden sich keine elektrischen Bauteile an dem bewegten Stößel 26', so daß die Stößelpositions-Meßeinrichtung möglichst robust ist. Durch die Rastverbindung des Führungs-Kolbens 61'''' kann zunächst der Ring 97 mit diesem verbunden werden, bevor der Führungs-Kolben 61"" mit dem Stößel 26' verbunden wird. Die Bestimmung der Einschubtiefe T erfolgt ansonsten wie bei der Ausführungsform gemäß Fig. 8:The structure is similar to the friction damper 23 'shown in FIG. 8 the description of which is hereby referred. Identical parts get the same Reference numerals as in the friction damper 23 'according to the second Embodiment. Structurally different, but functional Similar parts are given the same reference numerals with four superscripts Strokes. The plunger 26 'points in the region of its end on the inside of the housing an annular cylindrical wall 92, in the radially outwardly extending Locking recesses 93 are provided. On in slot direction 60 the end of the wall 92 is the radially projecting, annular guide web 63 provided. The guide piston 61 '' '' essentially has the shape of an annular cylindrical sleeve, on the opposite of which Insert direction 60 end protruding radially outward Latches 94 are provided, which are in latched engagement with the Rest recesses 93 are located. On the in the direction of insertion 60 The end of the guide piston 61 '' '' is the one projecting radially outwards Guide web 62 is provided, the annular groove 64 through the guide webs 62 and 63 is limited in the axial direction. As with the embodiment 6 are between the damping ring 66 and the Guide web 63 on the one hand and the damping ring 66 and the guide web 62 on the other hand, two compression springs 95 and 96 arranged, respectively ensure that the damping ring 66 approximately midway between the two webs 62 and 63 is arranged. At the direction of insertion 60 the end of the guide piston 61 '' '' is a transmitter 69 '' '' cylindrical ring 97 arranged in a corresponding Annular groove 98 is fixed on the inside of the guide piston 61 '' ''. The ring 97 is made of metal, in particular aluminum. The one out Metal, especially iron, existing cylindrical pin 77 carries the Coil unit 70 '' '', which consists of a arranged on the surface of the pin 77 Coil 71 ', in particular made of copper wire. The sink 71 'is opposite the pin 77 by a thin plastic layer 102 isolated, with the individual windings of the coil 71 'against each other are isolated. At the end opposite to the insertion direction 60 of the pin 77 is a radial opposite to the pin 77 and the coil unit 70 '' '' projecting spacer 99 is provided, which is a round Has cross section, between the spacer 99 and the Inner wall 100 of the guide piston 61 '' '' there is play. By the Spacer 99 ensures that the coil 71 'is not in contact with the encoder 69 '' '' comes. This is especially important when shear forces act on the friction damper 23 "", or the pin 77 disfiguration. The connecting line 73 "" is of that in the direction of insertion 60 lying end of the coil 71 'through the bottom 75 to one Plug 101 guided, from which a connection to the evaluation unit 74 can be produced. The advantage of this arrangement is that the housing 24th selected without disadvantage on the plunger position measuring device made of metal can be. In addition, there are no electrical components the moving plunger 26 'so that the plunger position measuring device is as robust as possible. Through the locking connection of the guide piston 61 '' '' can first be connected to the ring 97 before the Guide piston 61 "" is connected to the plunger 26 '. The determination the insertion depth T is otherwise the same as in the embodiment 8:

Claims (9)

  1. Damper, in particular for spin-type washing machines, comprising
    a) a tubular housing (11; 24) which has a central longitudinal axis (12, 25);
    b) a tappet (13; 26; 26') which is displaceable in the housing (11; 24) and extends out of an end thereof;
    c) fastening elements (18; 30, 34) which are respectively mounted on the free end of the housing (11; 24) and of the tappet (13; 26; 26');
    d) a frictional damper unit for producing given frictional damping action between the housing (11; 24) and the tappet (13; 26; 26'),
    i) the frictional damper unit, on the end of the tappet (13; 26; 26') inside the housing, comprising a piston (38; 61; 61'; 61'''') which has an annular groove (39; 64; 96), and
    ii) a damper ring (42; 42', 66) which is longitudinally displaceable in the annular groove,
    aa) the damper ring (42; 42'; 66) resting by friction on the inside wall (45; 65) of the housing (11; 24) and
    bb) being approximately frictionlessly displaceable relative to the piston (38; 61; 61'; 61''''),
    iii) with the piston (38; 61; 61'; 61""), in the range of a given modification ΔT of insertion depth T, being displaceable relative to the housing (11; 24) approximately free from stiction,
    characterized in that
    e) a tappet-position measuring device is provided, detecting the depth of insertion T of the tappet (13; 26; 26') into the housing (11; 24) and comprising
    i) a first measuring element which is connected to the housing ( 11; 24),
    ii) a second measuring element which is connected to the tappet (13; 26; 26') for electrical and/or magnetical interaction with the first measuring element, with the first measuring element and the second measuring element being insertable one into the other, and
    iii) an evaluation unit (57; 74), which is electrically conductively connected to the first measuring element or the second measuring element, emitting electric signals and receiving and processing electric signals for determination of the depth of insertion T.
  2. Damper according to claim 1, characterized in that the first measuring element or the second measuring element comprises a coil unit (53; 70; 70'; 70'''').
  3. Damper according to claim 2, characterized in that the coil unit (53; 70; 70'; 70'''') comprises one or two coils (54, 55; 71, 72; 71', 72').
  4. Damper according to claim 2, characterized in that the first measuring element or the second measuring element, which does not comprise a coil unit (53; 70; 70'; 70""), is a transmitter (52; 69; 69'; 69"") of metal.
  5. Damper according to claim 1, characterized in that the annular groove (64) has lengthways stops (40', 41') and in that pre-loaded compression springs (58, 59) are disposed between the stops (40', 41') and the damper ring (42').
  6. Damper according to claim 4, characterized in that the transmitter (52; 69) is disposed on the end, inside the housing, of the tappet (13; 26) and the coil unit (53; 70) is disposed to encompass the housing (11; 24) annularly cylindrically.
  7. Damper according to claim 4, characterized in that a guide piston (61'; 61"") is provided on the end, inside the housing, of the tappet (26'), having an insertion channel (78) which is coaxial of the central longitudinal axis (25).
  8. Damper according to claim 7, characterized in that the coil unit (70') is disposed on the guide piston (61'), encompassing the insertion channel (78) annularly cylindrically.
  9. Damper according to claim 8, characterized in that a pin (77) is provided in the vicinity of the free end of the housing (24) and disposed therein coaxially of the central longitudinal axis (25), the pin (77) supporting the transmitter (69') and being insertable into the insertion channel (78).
EP00971282A 1999-10-14 2000-09-22 Damper Expired - Lifetime EP1220961B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
SI200030300T SI1220961T1 (en) 1999-10-14 2000-09-22 Damper

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19949520 1999-10-14
DE19949520 1999-10-14
PCT/EP2000/009282 WO2001027375A1 (en) 1999-10-14 2000-09-22 Damper

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EP1220961A1 EP1220961A1 (en) 2002-07-10
EP1220961B1 true EP1220961B1 (en) 2004-02-25

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AT (1) ATE260355T1 (en)
DE (2) DE10046712A1 (en)
ES (1) ES2214325T3 (en)
TR (1) TR200200877T2 (en)
WO (1) WO2001027375A1 (en)

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EP1477604A3 (en) 2003-05-13 2006-09-13 Lg Electronics Inc. Damper for washing machine
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EP1584730B1 (en) * 2004-02-20 2010-09-08 SUSPA Holding GmbH Damper with elastic guide- / damping unit
KR100548309B1 (en) * 2004-07-13 2006-02-02 엘지전자 주식회사 Damper using magnetic force and washing machine with same
CN100552115C (en) * 2004-08-06 2009-10-21 乐金电子(天津)电器有限公司 Roller washing machine
DE102005038950B4 (en) * 2004-09-15 2016-08-11 Suspa Holding Gmbh damper
DE102006027295B3 (en) * 2006-06-13 2007-07-12 Suspa Holding Gmbh Weight of the washing load in a horizontal axis front loading domestic washing machine is established by determining the depression characteristics between the unloaded and loading conditions in the suspension springs and dampers
DE102006034190A1 (en) 2006-07-24 2008-01-31 BSH Bosch und Siemens Hausgeräte GmbH A method for determining a loading amount of a laundry treating appliance and a laundry treating appliance suitable therefor
BRPI0904790A2 (en) * 2009-11-11 2013-11-12 Whirlpool Sa DAMPING DEVICE FOR THE SUSPENSION SYSTEM OF A CLOTHING WASHER
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DE202014103664U1 (en) 2014-08-06 2015-08-07 Seuffer gmbH & Co. KG Device for damping vibrations of a body
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CN105422720B (en) * 2016-01-05 2017-10-20 江苏大学 A kind of energy isolation mounting
CN109594295A (en) * 2017-09-30 2019-04-09 无锡小天鹅股份有限公司 The damper of washing machine and washing machine with it
CN111118826A (en) * 2020-02-10 2020-05-08 海信（山东）冰箱有限公司 Washing machine
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USRE45461E1 (en) 2004-09-15 2015-04-14 Suspa Gmbh Damper
DE102005038953A1 (en) * 2005-08-16 2007-02-22 Suspa Holding Gmbh damper
US7971693B2 (en) 2005-08-16 2011-07-05 Suspa Holding Gmbh Damper
WO2008012651A3 (en) * 2006-07-27 2008-05-22 Indesit Co Spa Household appliance for treating soft goods with displacement sensor
EP2319972A1 (en) * 2006-07-27 2011-05-11 Indesit Company S.p.A. Household appliance for treating soft goods with displacement sensor
US8432160B2 (en) 2007-12-27 2013-04-30 Indesit Compnay S.p.A Method for estimating the weight of the contents of a household appliance
DE102008049907A1 (en) 2008-10-02 2010-04-08 Suspa Holding Gmbh Vibration absorber for washing machine, has electronic circuit detecting submersion depth of tappet and evaluating coil digitally by controlling coil with repetitive defined switching on and off signal with fixed frequency
DE102008049907B4 (en) * 2008-10-02 2016-08-04 Suspa Gmbh Damper with sensor
EP2372184A1 (en) 2010-03-31 2011-10-05 Electrolux Home Products Corporation N.V. Home appliance
WO2011120758A1 (en) 2010-03-31 2011-10-06 Electrolux Home Products Corporation N.V. Home appliance

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DE50005453D1 (en) 2004-04-01
ES2214325T3 (en) 2004-09-16
WO2001027375A1 (en) 2001-04-19
TR200200877T2 (en) 2002-06-21
DE10046712A1 (en) 2001-04-19
ATE260355T1 (en) 2004-03-15
EP1220961A1 (en) 2002-07-10

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