EP0709515B1 - Driving device for domestic laundry drier - Google Patents

Driving device for domestic laundry drier Download PDF

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Publication number
EP0709515B1
EP0709515B1 EP95112317A EP95112317A EP0709515B1 EP 0709515 B1 EP0709515 B1 EP 0709515B1 EP 95112317 A EP95112317 A EP 95112317A EP 95112317 A EP95112317 A EP 95112317A EP 0709515 B1 EP0709515 B1 EP 0709515B1
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EP
European Patent Office
Prior art keywords
lever
spring
axis
drive device
relation
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EP95112317A
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German (de)
French (fr)
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EP0709515A1 (en
Inventor
Dieter Knopp
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BSH Hausgeraete GmbH
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BSH Bosch und Siemens Hausgeraete GmbH
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    • 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
    • D06F58/00—Domestic laundry dryers
    • D06F58/02—Domestic laundry dryers having dryer drums rotating about a horizontal axis
    • D06F58/04—Details 
    • D06F58/08—Driving arrangements

Definitions

  • the invention relates to a drive device for a household clothes dryer with an at least approximately horizontally rotatable laundry drum, by means of a drive belt from a countershaft sprocket in one Direction or reversible, with a large pulley non-rotatably connected and on a common, axially parallel movable Axle is mounted and in turn via a countershaft belt from the motor pinion an electric drive motor is driven, the common axis both in relation to the axis of the engine pinion and in relation to the drum axis is spring-loaded in the sense of increasing the distance.
  • Tensioning rollers are already used to avoid such length differences been (DE-OS 22 07 372) by means of one or more spring-loaded levers on the back of each belt. Apart from such an additional effort and the opposite deflection compared to the pinion enclosure Most of the resulting flexing work is not too complicated Tensioners are an undesirable feature: they cause the drive pinion to run up or the tension pulley on the incoming belt drum and reduce thereby the transferable forces.
  • the invention is based, with a drive device defined at the outset the task to avoid the above disadvantages and an adjustment-free construction to create the even after a longer life of the drive belt without Loss of the transferable forces does not have to be tightened and which the different requirements for the belt tension and the different ones Elasticity of the straps taken into account.
  • this object is achieved in that the drive belt is wrapped around the drum shell and that the spring load is related on the drum axis through a between a fixed housing part and the common axis clamped first spring and the spring load in relation to the axis of the engine pinion by one between the common Axle and the motor pinion clamped second spring is shown.
  • Such a design of the drive device equals tolerances in the system, as well as additional different length change tolerances of the Belt automatically for advanced use of the dryer out. An operation that is otherwise provided for during assembly can be omitted, through which the center distances for the drive belts are particularly adjusted ought to. Due to the insensitivity of the drive device according to the invention against long-term length tolerance tolerances of the belts, there is also no Number of service calls that are otherwise necessary to retighten the belts or the arrangement of an additional tension pulley.
  • the drive device counteracts one the prior art also known common spring for adjustment of the countershaft drive to the characteristics of the respective belt drive Considered.
  • this affects different requirements the belt tension and taking into account the different elasticity the strap.
  • the different belt tensions between the incoming and outgoing run of the straps on the two Use cases are only properly taken into account that for everyone Use case own spring is used to tension the belt. Thereby If the belt wear is too high due to excessive tension in the one strap as well as by too strong flexing in the other strap avoided.
  • the common axis near the free end of a single-armed lever. Merging mobility the common axis in both of these relationships the construction is simplified by a lever with one arm compared to known proposals and wins additionally Security in compliance with the transmission forces.
  • a further development of the invention is advantageous the fulcrum in the proper operating situation of the lever and the common axis together with the fulcrum the engine pinion at least approximately on a straight line lie.
  • a single additional component is used in further training of the invention thus designed, that the fulcrum for the big pulley and that Gear pinion on at least approximately in the direction on the axis of the motor pinion on the lever-guided slide is.
  • the carriage advantageously has a chamber with a spring support for the Compression spring, whose fixed counterpart on the lever is close to one slot in the guide for the slide for the penetration of the lever with the countershaft is located.
  • the base 2 of a floor assembly installed in the lower area of the housing 1 .
  • the drive motor rests in it 3 for the laundry drum 4, which in turn on one not shown, arranged away from the base 2 Housing component is rotatably mounted on the axis 5.
  • the Pivot 6 of the base part 2 also has a lever 7 with one arm stored in its operating position the axes of the Pivotal point 6 and the drive motor 3 with the common Axis 8 of the large pulley 9 and the countershaft sprocket 10 lie on a straight line 22.
  • the common axis is 8 doing near the free end 11 of the one-armed Lever 7 arranged.
  • the drum cross-sectional circular area 15 represents the area of the belt 14 wrapped, automatically in the same plane as the countershaft sprocket 10 lying drum disc.
  • the lever 7 is supported by a compression spring 16 which is double-walled Sleeve 17 is guided so that the large Pulley 9 their lay belt 18 between them and the motor pinion 19 stretches. This also keeps the lay belt 18 constantly tensioned without adjustment.
  • the tension of the belts 14 and 18 is partly due to the Geometry of the countershaft parts and essentially by the Tension forces of the springs 12 and 16 determined.
  • the feed area is to explain the force relationships from Fig. 1 in Fig. 2 shown enlarged.
  • the one for transmission necessary torque from the motor to the large pulley 9 and from the countershaft sprocket 10 to the jacket of the Drum 4 apply the required voltage for the Belts 18 and 14 tight.
  • the tension for the belt 18 will by the vector F18 and the tension for the belt 14 represented by the vector F14.
  • ⁇ is the angle between the belt tension F14 and the normal force F4 on the straight line 22.
  • the spring force F12 is broken down into the vector F2, which is the corresponding normal force on the straight line 22 at the point of application 20 of the point of intersection of the imaginary axis of the spring 12 with the straight line 22, and the vector F19, which ultimately results from the existing triangle of forces at the angle can be calculated.
  • F19 F12 ⁇ sin ⁇ .
  • Fig. 3 shows another embodiment for an inventive Drive device.
  • the one-armed man is not in it mounted lever 23 itself at its pivot 6 stored; the lever 23 is rigid in itself. But he has in the Near its lever end 11, a link guide 24, the central axis in the operating position of the lever 23 approximately on the Axis of the motor 3 shows.
  • the backdrop guide 24 takes one Carriage 25 on which the bearing for the large pulley 9 and is fixed for the countershaft sprocket 10. With this slide 25, the countershaft bearing can therefore in the direction the center axis of the link guide 24 back and forth become.
  • the carriage 25 has on its out of the lever 23rd projecting end 26 a counter bearing bridge 27 for a compression spring 28, which is supported on a bearing plate 29 of the lever 23.
  • the compression spring 28 therefore pulls the large pulley 9 on the countershaft bearing and the slide 25 in the Belt 18.

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  • Engineering & Computer Science (AREA)
  • Textile Engineering (AREA)
  • Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)
  • Detail Structures Of Washing Machines And Dryers (AREA)

Description

Die Erfindung geht aus von einer Antriebseinrichtung für einen Haushalt-Wäschetrockner mit einer wenigstens annähernd horizontal drehbar gelagerten Wäschetrommel, die mittels eines Antriebsriemens von einem Vorgelege-Ritzel in einer Richtung oder reversierend antreibbar ist, das mit einer großen Riemenscheibe drehfest verbunden und auf einer gemeinsamen, achsparallel beweglich geführten Achse gelagert ist und seinerseits über einen Vorgelege-Riemen vom Motor-Ritzel eines elektrischen Antriebsmotors angetrieben wird, wobei die gemeinsame Achse sowohl in Beziehung auf die Achse des Motor-Ritzels wie auch in Beziehung auf die Trommelachse im Sinne einer Abstandsvergrößerung federbelastet ist.The invention relates to a drive device for a household clothes dryer with an at least approximately horizontally rotatable laundry drum, by means of a drive belt from a countershaft sprocket in one Direction or reversible, with a large pulley non-rotatably connected and on a common, axially parallel movable Axle is mounted and in turn via a countershaft belt from the motor pinion an electric drive motor is driven, the common axis both in relation to the axis of the engine pinion and in relation to the drum axis is spring-loaded in the sense of increasing the distance.

Aus dem US-A-3 382 587 ist eine Antriebseinrichtung bekannt, in der die Abstände zwischen den Achsen des Motor-Ritzels und des Vorgeleges sowie zwischen diesem und der Wäschetrommel fest eingestellt sind. Daher müssen bei der Montage der Antriebseinrichtung der Vorgelege-Riemen und der Trommel-Antriebsriemen mittels einer Justiereinrichtung gespannt werden; denn die Einbau-Abmessungen und die Längenabmessungen der Riemen sind toleranzbehaftet. Zum Zwecke der Einhaltung der für die erforderliche Kraftübertragung gewünschten Riemenspannungen müssen die Toleranzen durch Justage ausgeglichen werden. Außerdem unterliegen die Riemen über eine längere Lebensdauer einer bleibenden Längendehnung, die bei fest eingestellten Achsabständen zur Verminderung der Riemenspannungen und damit zur Herabsetzung der übertragbaren Kräfte sowie letztendlich zur Zerstörung der Riemen führt. Ferner muß auf die Eigenheiten des jeweiligen Riementriebs Rücksicht genommen werden. Dies betrifft zu allererst unterschiedliche Anforderungen an die Riemenspannung und Berücksichtigung der unterschiedlichen Elastizität der Riemen. Außerdem sind die Riemenspannungen zwischen dem zulaufenden und dem ablaufenden Trum der Riemen bei den beiden Einsatzfällen stark unterschiedlich. Eine Einzeljustage muß auch dies ausgleichen, damit entweder kein zu hoher Riemenverschleiß durch zu starke Spannung im einen Riemen oder kein zu starkes Walken im anderen Riemen vorzeitigen Verschleiß herbeiführt.From US-A-3 382 587 a drive device is known in which the distances between the axes of the engine pinion and the countershaft as well as between this and the laundry drum are fixed. Therefore, when assembling the drive device of the countershaft belt and the drum drive belt be tensioned by means of an adjusting device; because the installation dimensions and the length dimensions of the belts are subject to tolerance. To the Purposes of compliance with the desired for the required power transmission Belt tensions, the tolerances must be compensated by adjustment. In addition, the belts are subject to permanent wear over a longer service life Elongation, which with fixed center distances to reduce the belt tensions and thus to reduce the transferable forces as well ultimately leads to the destruction of the belt. Furthermore, the peculiarities of the respective belt drive. This affects first of all different requirements for belt tension and consideration the different elasticity of the straps. In addition, the belt tensions between the incoming and outgoing run of the belts in the two cases very different. A single adjustment must also compensate for this, so that either no excessive belt wear due to excessive Premature tension in one belt or no excessive flexing in the other belt Causes wear.

Zur Vermeidung solcher Längenunterschiede sind schon Spannrollen eingesetzt worden (DE-OS 22 07 372), die mittels eines oder mehrerer federbelasteter Hebel auf der jeweiligen Riemen-Rückseite lasten. Abgesehen von einem solchen Zusatz-Aufwand und der im Vergleich zur Ritzelumfassung gegenläufigen Umlenkung entstehenden Walkarbeit haben die meisten nicht bereits zu komplizierten Spannrollen eine unerwünschte Eigenschaft: Sie führen zum Auflaufen des Antriebsritzels bzw. der Spannrolle auf das zulaufende Riementrum und verringern dadurch die übertragbaren Kräfte.Tensioning rollers are already used to avoid such length differences been (DE-OS 22 07 372) by means of one or more spring-loaded levers on the back of each belt. Apart from such an additional effort and the opposite deflection compared to the pinion enclosure Most of the resulting flexing work is not too complicated Tensioners are an undesirable feature: they cause the drive pinion to run up or the tension pulley on the incoming belt drum and reduce thereby the transferable forces.

Antriebsvorrichtungen für Wäschetrockner der eingangs beschrieben Art sind durch US-A-2 506 516 und durch US-A-2 716 820 bekannt. Diese bekannten Vorrichtungen vermeiden bereits die Nachteile der Einzeljustage und der Spannrollenprobleme dadurch, daß die gemeinsame Achse des Vorgelege-Ritzels und der großen Riemenscheibe achsparallel beweglich geführt ist und sowohl in Beziehung auf die Achse des Motor-Ritzels wie auch in Beziehung auf die Trommelachse im Sinne einer Abstandsvergrößerung federbelastet ist. Damit hat man sich aber wieder einen neuen Nachteil eingehandelt, weil nämlich auf die Eigenheiten des jeweiligen Riementriebs nicht Rücksicht genommen werden kann. Dies betrifft ebenfalls zu allererst unterschiedliche Anforderungen an die Riemenspannung und Berücksichtigung der unterschiedlichen Elastizität der Riemen. Außerdem sind die Riemenspannungen zwischen dem zulaufenden und dem ablaufenden Trum der Riemen in beiden Einsatzfällen so unterschiedlich, daß bei Einsatz nur einer Feder zum Spannen beider Riemen gemäß Stand der Technik entweder ein zu hoher Riemenverschleiß durch zu starke Spannung im einen Riemen oder durch zu starkes Walken im anderen Riemen in Kauf genommen werden muß, wenn nicht wieder eine Spannrolle zum Einsatz kommen soll.Drive devices for tumble dryers of the type described are by US-A-2 506 516 and by US-A-2 716 820. These known devices already avoid the disadvantages of individual adjustment and tension roller problems in that the common axis of the countershaft sprocket and the large pulley is guided to move axially parallel and both in relation on the axis of the motor pinion as well as in relation to the drum axis is spring-loaded in the sense of increasing the distance. With that you have but again traded a new disadvantage because of the peculiarities of the respective belt drive cannot be taken into account. this concerns also first of all different demands on the belt tension and taking into account the different elasticity of the straps. Moreover are the belt tensions between the incoming and outgoing The belt runs so differently in both applications that when used only a spring for tensioning both belts according to the prior art either excessive belt wear due to excessive tension in one belt or must be accepted due to excessive flexing in the other belt, if a tension pulley is not to be used again.

Der Erfindung liegt die Aufgabe zugrunde, bei einer eingangs definierten Antriebseinrichtung die vorstehenden Nachteile zu vermeiden und eine justagefreie Konstruktion zu schaffen, die auch nach längerer Lebensdauer der Antriebsriemen ohne Verlust der übertragbaren Kräfte nicht nachgespannt werden muß und welche die unterschiedlichen Anforderungen an die Riemenspannung und an die unterschiedliche Elastizität der Riemen berücksichtigt. The invention is based, with a drive device defined at the outset the task to avoid the above disadvantages and an adjustment-free construction to create the even after a longer life of the drive belt without Loss of the transferable forces does not have to be tightened and which the different requirements for the belt tension and the different ones Elasticity of the straps taken into account.

Erfindungsgemäß wird diese Aufgabe dadurch gelöst, daß der Antriebsriemen um den Trommelmantel geschlungenen ist und daß die Federbelastung in Beziehung auf die Trommelachse durch eine zwischen einem festen Gehäuse-Teil und der gemeinsamen Achse eingespannte erste Feder und die Federbelastung in Beziehung auf die Achse des Motor-Ritzels durch eine zwischen der gemeinsamen Achse und dem Motor-Ritzel eingespannte zweite Feder dargestellt ist. Eine solche Ausbildung der Antriebseinrichtung gleicht im System steckende Toleranzen, wie auch zusätzliche unterschiedliche Längenänderungstoleranzen der Riemen beim fortgeschrittenen Gebrauch des Wäschetrockners automatisch aus. Dabei kann ein sonst bei der Montage vorgesehener Arbeitsgang entfallen, durch den die Achsabstände für die Antriebsriemen besonders justiert werden müßten. Durch die Unempfindlichkeit der erfindungsgemäßen Antriebseinrichtung gegen langfristige Längenänderungstoleranzen der Riemen entfällt auch die Zahl der sonst nötigen Kundendiensteinsätze zum Nachspannen der Riemen bzw. die Anordnung einer zusätzlichen Spannrolle.According to the invention, this object is achieved in that the drive belt is wrapped around the drum shell and that the spring load is related on the drum axis through a between a fixed housing part and the common axis clamped first spring and the spring load in relation to the axis of the engine pinion by one between the common Axle and the motor pinion clamped second spring is shown. Such a design of the drive device equals tolerances in the system, as well as additional different length change tolerances of the Belt automatically for advanced use of the dryer out. An operation that is otherwise provided for during assembly can be omitted, through which the center distances for the drive belts are particularly adjusted ought to. Due to the insensitivity of the drive device according to the invention against long-term length tolerance tolerances of the belts, there is also no Number of service calls that are otherwise necessary to retighten the belts or the arrangement of an additional tension pulley.

Ferner wird mit der erfindungsgemäßen Antriebseinrichtung entgegen einer aus dem Stand der Technik auch noch bekannten gemeinsamen Feder zur Justierung des Vorgelegeantriebs auf die Eigenheiten des jeweiligen Riementriebs Rücksicht genommen. Dies betrifft zu allererst unterschiedliche Anforderungen an die Riemenspannung und Berücksichtigung der unterschiedlichen Elastizität der Riemen. Außerdem können die unterschiedlichen Riemenspannungen zwischen dem zulaufenden und dem ablaufenden Trum der Riemen bei den beiden Einsatzfällen nur dadurch sachgerecht berücksichtigt werden, daß für jeden Einsatzfall eine eigene Feder zum Spannen der Riemen verwendet wird. Dadurch wird ein zu hoher Riemenverschleiß sowohl durch zu starke Spannung im einen Riemen als auch durch zu starkes Walken im anderen Riemen vermieden. Furthermore, the drive device according to the invention counteracts one the prior art also known common spring for adjustment of the countershaft drive to the characteristics of the respective belt drive Considered. First of all, this affects different requirements the belt tension and taking into account the different elasticity the strap. In addition, the different belt tensions between the incoming and outgoing run of the straps on the two Use cases are only properly taken into account that for everyone Use case own spring is used to tension the belt. Thereby If the belt wear is too high due to excessive tension in the one strap as well as by too strong flexing in the other strap avoided.

Gemäß einer vorteilhaften Ausbildung der Erfindung befindet sich die gemeinsame Achse in der Nähe des freien Endes eines einarmig gelagerten Hebels. Die Zusammenlegung der Beweglichkeit der gemeinsamen Achse in beiden genannten Beziehungen auf einen einarmig gelagerten Hebel vereinfacht die Konstruktion gegenüber bekannten Vorschlägen und gewinnt zusätzlich Sicherheit bei der Einhaltung der Übertragungskräfte.According to an advantageous embodiment of the invention the common axis near the free end of a single-armed lever. Merging mobility the common axis in both of these relationships the construction is simplified by a lever with one arm compared to known proposals and wins additionally Security in compliance with the transmission forces.

Für die Einhaltung einer definierten Spannkraft im Vorgelege-Riemen ist eine Weiterbildung der Erfindung vorteilhaft, bei der in ordnungsgemäßer Betriebssituation der Drehpunkt des Hebels und die gemeinsame Achse zusammen mit dem Drehpunkt des Motor-Ritzels zumindest angenähert auf einer Geraden liegen.For maintaining a defined tension in the countershaft belt a further development of the invention is advantageous the fulcrum in the proper operating situation of the lever and the common axis together with the fulcrum the engine pinion at least approximately on a straight line lie.

Die Einfachheit der Konstruktion mit der Anordnung auf einem einarmig gelagerten Hebel zeigt sich insbesondere darin, daß die Federbelastung in Beziehung auf die Trommelachse durch eine zwischen einem festen Gehäuse-Teil und dem äußersten freien Ende des Hebels eingespannte Zugfeder dargestellt ist.The simplicity of the construction with the arrangement on one single-armed lever is particularly evident in the fact that the spring load in relation to the drum axis one between a fixed housing part and the outermost one Free end of the lever clamped tension spring shown is.

Die Einfachheit der Konstruktion bei der Federbelastung des Vorgelege-Riemens zeigt sich in zwei Alternativen, bei denen die Federbelastung in Beziehung auf die Achse des Motor-Ritzels einmal durch eine zwischen dem Drehpunkt des Hebels und dem Hebelarm eingespannte Druckfeder und andererseits durch eine zwischen dem Drehpunkt der großen Riemenscheibe und einer am Hebelarm festen Gegenlage eingespannten Druckfeder dargestellt ist. Zwar erscheint hierdurch die Konstruktion des Hebelarms kompliziert. Da dieser aber aus einem Aluminium-Druckgußteil besteht, beschränkt sich die Kompliziertheit auf die einmalige Herstellung des Gußwerkzeugs.The simplicity of the design when loading the spring Countershaft belts are shown in two alternatives, among which the spring load in relation to the axis of the engine pinion once by one between the fulcrum of the lever and the lever arm clamped compression spring and on the other hand by one between the pivot point of the large pulley and one compression spring clamped on the lever arm fixed counterpart is shown. Thereby the construction appears the lever arm complicated. But since this is made of an aluminum die-cast part the complexity is limited on the one-off production of the casting tool.

Ein einziges zusätzliches Bauteil wird bei einer Weiterbildung der solchermaßen ausgestalteten Erfindung dadurch benötigt, daß der Drehpunkt für die große Riemenscheibe und das Vorgelege-Ritzel an einem mindestens annähernd in Richtung der Achse des Motor-Ritzels am Hebel geführten Schlitten angebracht ist.A single additional component is used in further training of the invention thus designed, that the fulcrum for the big pulley and that Gear pinion on at least approximately in the direction on the axis of the motor pinion on the lever-guided slide is.

Vorteilhafterweise weist der Schlitten eine Kammer mit einer entfernt vom Drehpunkt angebrachten Federstütze für die Druckfeder auf, deren feste Gegenlage am Hebel sich nahe einem in der Führung des Schlittens angebrachten Langloch für die Durchdringung des Hebels mit der Vorgelege-Welle befindet.The carriage advantageously has a chamber with a spring support for the Compression spring, whose fixed counterpart on the lever is close to one slot in the guide for the slide for the penetration of the lever with the countershaft is located.

Anhand zweier in der Zeichnung dargestellter Ausführungsbeispiele ist die Erfindung nachstehend erläutert. Es zeigen

Fig. 1
eine erfindungsgemäße Antriebseinrichtung mit einem einseitig gelagerten Hebel, der an seinem Lagerpunkt längsverschieblich unterbrochen ist und mit einer Druckfeder zum Spannen des Vorgelege-Riemens versehen ist,
Fig. 2
eine das Vorgelege gemäß Fig. 1 betreffende Einzelheit zur Erläuterung der Kraftverhältnisse an der gemeinsamen Achse und
Fig. 3
eine anders als in Fig. 1 und 2 ausgebildete Antriebseinrichtung, bei der die gemeinsame Achse auf einem im Hebel geführten und federbelasteten Schlitten angeordnet ist.
The invention is explained below using two exemplary embodiments shown in the drawing. Show it
Fig. 1
a drive device according to the invention with a lever mounted on one side, which is displaceably interrupted at its bearing point and is provided with a compression spring for tensioning the countershaft belt,
Fig. 2
a detail relating to the transmission according to FIG. 1 to explain the force relationships on the common axis and
Fig. 3
a differently than in Fig. 1 and 2 designed drive device, in which the common axis is arranged on a guided in the lever and spring-loaded carriage.

Im unteren Bereich des Gehäuses 1 eines Wäschetrockners ist der Sockel 2 einer Bodengruppe eingebaut. Darin ruht der Antriebsmotor 3 für die Wäschetrommel 4, die ihrerseits an einem nicht dargestellten, entfernt vom Sockel 2 angeordneten Gehäusebauteil auf der Achse 5 drehbar gelagert ist. Im Drehpunkt 6 des Sockelteils 2 ist außerdem ein Hebel 7 einarmig gelagert, in dessen Betriebsposition die Achsen des Drehpunkts 6 und des Antriebsmotors 3 mit der gemeinsamen Achse 8 der großen Riemenscheibe 9 und des Vorgelege-Ritzels 10 auf einer Geraden 22 liegen. Die gemeinsame Achse 8 ist dabei in der Nähe des freien Endes 11 des einarmig gelagerten Hebels 7 angeordnet. Am freien Ende 11 des Hebels 7 greift eine Zugfeder 12 an, deren anderes Ende in einen Haken 13 des Sockelteils 2 eingehängt ist. Durch diese Feder 12 wird das Vorgelege-Ritzel 10 in den Antriebsriemen 14 für die Wäschetrommel 4 gezogen. Dadurch bleibt der Riemen 14 ständig gespannt, ohne daß es irgendeiner Justage bedürfte. Die Trommelquerschnitts-Kreisfläche -Kreisfläche 15 stellt die vom Riemen 14 umschlungene, automatisch in derselben Ebene wie das Vorgelege-Ritzel 10 liegende Trommelscheibe dar.In the lower area of the housing 1 is a clothes dryer the base 2 of a floor assembly installed. The drive motor rests in it 3 for the laundry drum 4, which in turn on one not shown, arranged away from the base 2 Housing component is rotatably mounted on the axis 5. in the Pivot 6 of the base part 2 also has a lever 7 with one arm stored in its operating position the axes of the Pivotal point 6 and the drive motor 3 with the common Axis 8 of the large pulley 9 and the countershaft sprocket 10 lie on a straight line 22. The common axis is 8 doing near the free end 11 of the one-armed Lever 7 arranged. At the free end 11 of the lever 7 attacks a tension spring 12, the other end in a hook 13 of the base part 2 is suspended. By this spring 12, the countershaft sprocket 10 in the drive belt 14 for pulled the laundry drum 4. As a result, the belt 14 remains constantly excited, without the need for any adjustment. The drum cross-sectional circular area 15 represents the area of the belt 14 wrapped, automatically in the same plane as the countershaft sprocket 10 lying drum disc.

Der Hebel 7 wird durch eine Druckfeder 16, die in einer doppelwandigen Hülse 17 geführt ist, so gestreckt, daß die große Riemenscheibe 9 ihren Vorgelege-Riemen 18 zwischen sich und dem Motor-Ritzel 19 dehnt. Dadurch bleibt auch der Vorgelege-Riemen 18 ohne Justage ständig gespannt.The lever 7 is supported by a compression spring 16 which is double-walled Sleeve 17 is guided so that the large Pulley 9 their lay belt 18 between them and the motor pinion 19 stretches. This also keeps the lay belt 18 constantly tensioned without adjustment.

Die Spannung der Riemen 14 und 18 wird zum Teil durch die Geometrie der Vorgelege-Teile und im wesentlichen durch die Spannkräfte der Federn 12 und 16 bestimmt.The tension of the belts 14 and 18 is partly due to the Geometry of the countershaft parts and essentially by the Tension forces of the springs 12 and 16 determined.

Zur Erläuterung der Kraftverhältnisse ist der Vorlegebereich aus Fig. 1 in Fig. 2 vergrößert dargestellt. Die zur Übertragung notwendigen Drehkräfte vom Motor auf die große Riemenscheibe 9 und vom Vorgelege-Ritzel 10 auf den Mantel der Trommel 4 legen die jeweils erforderliche Spannung für die Riemen 18 und 14 fest. Die Spannung für den Riemen 18 wird durch den Vektor F18 und die Spannung für den Riemen 14 durch den Vektor F14 dargestellt. Aus diesen beiden bekannten Größen sowie aus dem Abstand LT vom Drehpunkt 6 des Hebels 7 zum fiktiven Angriffspunkt 20 der Kraft F12 der Zugfeder 12 an der Geraden 22 und dem Abstand LV vom Drehpunkt 6 zum Angriffspunkt der Spannung des Riemens 14 in der gemeinsamen Achse 8 des Vorgeleges lassen sich die notwendigen Federkräfte wie folgt errechnen:The feed area is to explain the force relationships from Fig. 1 in Fig. 2 shown enlarged. The one for transmission necessary torque from the motor to the large pulley 9 and from the countershaft sprocket 10 to the jacket of the Drum 4 apply the required voltage for the Belts 18 and 14 tight. The tension for the belt 18 will by the vector F18 and the tension for the belt 14 represented by the vector F14. From these two known ones Sizes as well as from the distance LT from the fulcrum 6 of the lever 7 to the fictitious point of application 20 of the force F12 of the tension spring 12 on the straight line 22 and the distance LV from the fulcrum 6 to the point of application of the tension of the belt 14 in the common Axis 8 of the countershaft can be the necessary Calculate spring forces as follows:

An der Achse 8 greift die Spannkraft F14 des Riemens 14 an, die genau auf der Verbindungslinie 21 zwischen der Achse 8 und der Achse 5 der Trommel 4 liegt. Zerlegt man diesen Kraftvektor F14 in die Normalkräfte F1 und F4, dann läßt sich ein weiterer in Richtung auf den Drehpunkt 6 des Vorgelege-Hebels zeigender Vektor F1 ermitteln. Dieser Vektor ergibt sich aus der nachstehenden Formel: F1 =F14 ×sinα. The tensioning force F14 of the belt 14 acts on the axis 8, which lies exactly on the connecting line 21 between the axis 8 and the axis 5 of the drum 4. If this force vector F14 is broken down into the normal forces F1 and F4, then another vector F1 pointing in the direction of the pivot point 6 of the countershaft lever can be determined. This vector results from the following formula: F 1 = F 14 × sinα.

Darin ist α der Winkel zwischen der Riemenspannung F14 und der Normalkraft F4 auf die Gerade 22. Therein, α is the angle between the belt tension F14 and the normal force F4 on the straight line 22.

Die Federkraft F12 zerlegt sich in den Vektor F2, das ist die entsprechende Normalkraft auf die Gerade 22 am Angriffspunkt 20 des Kreuzungspunktes der gedachten Achse der Feder 12 mit der Geraden 22, und den Vektor F19, der sich schließlich aus dem vorhandenen Kräftedreieck unter dem Winkel errechnen läßt. Darin ist F19 = F12 × sinβ. The spring force F12 is broken down into the vector F2, which is the corresponding normal force on the straight line 22 at the point of application 20 of the point of intersection of the imaginary axis of the spring 12 with the straight line 22, and the vector F19, which ultimately results from the existing triangle of forces at the angle can be calculated. In it F19 = F12 × sinβ.

Da F12 nicht bekannt ist, muß auch diese Kraft zunächst errechnet werden. Sie ergibt sich aus der Formel F12 = F2cosβ . Since F12 is not known, this force must also be calculated first. It results from the formula F12 = F 2 cosβ ,

Auch F2 ist nicht bekannt, aber durch folgende Formel errechenbar: F2 = F4 × LV LT ; denn da die am Ende des Hebels 7 angreifenden Kräfte im Gleichgewicht stehen müssen, muß das Drehmoment an der Achse 8 über den Hebelarm LV gleich sein mit dem Drehmoment am Angriffspunkt 20 über dem Hebelarm LT. Daraus und aus (2) bis (4) ergibt sich für die Kraft F19 folgende Formel F19 = LV LT ×F14×cosα ×sinβcosβ oder F19 = LV LT ×F14 ×cosα ×tanβ. F2 is also unknown, but can be calculated using the following formula: F2 = F4 × LV LT ; since the forces acting on the end of the lever 7 must be in balance, the torque on the axis 8 via the lever arm LV must be the same as the torque on the point of application 20 above the lever arm LT. From this and from (2) to (4), the following formula results for the force F19 F19 = LV LT × F 14 × cosα × are cosβ or F19 = LV LT × F 14 × cosα × tanβ.

Schließlich lassen sich die gegebene Riemenspannkraft F18 und die gefundenen Kraftkomponenten F1 und F19 gemäß (1) und (6) zu einer gemeinsamen Kraftkomponente addieren, der sich die durch die Druckfeder 16 des Hebels 7 aufzubringende Kraft F16 gleichgewichtig entgegenstellen muß: F16 = F18 + F1 + F19. Finally, the given belt tensioning force F18 and the found force components F1 and F19 according to (1) and (6) can be added to a common force component, which must be counterbalanced by the force F16 to be applied by the compression spring 16 of the lever 7: F16 = F18 + F1 + F19.

Fig. 3 zeigt ein anderes Ausführungsbeispiel für eine erfindungsgemäße Antriebseinrichtung. Darin ist nicht der einarmig gelagerte Hebel 23 an seinem Drehpunkt 6 selbst federnd gelagert; der Hebel 23 ist in sich starr. Er hat aber in der Nähe seines Hebelendes 11 eine Kulissenführung 24, dem Mittelachse in Betriebsstellung des Hebels 23 in etwa auf die Achse des Motors 3 zeigt. Die Kulissenführung 24 nimmt einen Schlitten 25 auf, an dem das Lager für die große Riemenscheibe 9 und für das Vorgelege-Ritzel 10 befestigt ist. Mit diesem Schlitten 25 kann das Vorgelege-Lager daher in Richtung der Mittelachse der Kulissenführung 24 hin- und herbewegt werden. Der Schlitten 25 hat an seinem aus dem Hebel 23 ragenden Ende 26 eine Gegenlagerbrücke 27 für eine Druckfeder 28, die sich an einer Lagerplatte 29 des Hebels 23 abstützt. Die Druckfeder 28 zieht daher die große Riemenscheibe 9 über das Vorgelege-Lager und den Schlitten 25 in den Riemen 18. Gleichzeitig wird durch die Zugfeder 12 am Ende 11 des Hebels 23 das Vorgelege-Ritzel 10 in den Riemen 14 gezogen.Fig. 3 shows another embodiment for an inventive Drive device. The one-armed man is not in it mounted lever 23 itself at its pivot 6 stored; the lever 23 is rigid in itself. But he has in the Near its lever end 11, a link guide 24, the central axis in the operating position of the lever 23 approximately on the Axis of the motor 3 shows. The backdrop guide 24 takes one Carriage 25 on which the bearing for the large pulley 9 and is fixed for the countershaft sprocket 10. With this slide 25, the countershaft bearing can therefore in the direction the center axis of the link guide 24 back and forth become. The carriage 25 has on its out of the lever 23rd projecting end 26 a counter bearing bridge 27 for a compression spring 28, which is supported on a bearing plate 29 of the lever 23. The compression spring 28 therefore pulls the large pulley 9 on the countershaft bearing and the slide 25 in the Belt 18. At the same time, the tension spring 12 at the end 11 of the lever 23, the countershaft sprocket 10 in the belt 14 drawn.

Durch völlig andersartige Abmessungen gegenüber dem Ausführungsbeispiel nach Fig. 1 und 2 ergeben sich bei dem in Fig. 3 dargestellten Ausführungsbeispiel andere Federspannungen. Der grundsätzliche Aufbau der erfindungsgemäßen Antriebseinrichtung und der Berechnungsgang für die Federkräfte sind aber gleichartig.Due to completely different dimensions compared to the embodiment 1 and 2 result in the in Fig. 3 illustrated embodiment other spring tensions. The basic structure of the drive device according to the invention and the calculation process for the spring forces but similar.

Claims (8)

  1. Drive device for a household laundry drier with at least one approximately horizontally rotatably mounted laundry drum drivable in one direction or reversibly by means of a drive belt (14) from an intermediate pinion (10), which is connected in rotationally fast manner with a large belt pulley (9) and mounted on a common axle (8) guided to be axially parallelly movable and which is in turn driven by an intermediate belt (18) from the motor pinion (19) of an electric drive motor (3), wherein the common axle (8) is spring-loaded in the sense of an increase in spacing not only in relation to the axis of the motor pinion (19), but also in relation to the drum axis (5), characterised in that the drive belt (14) is looped around the drum circumference and the spring loading in relation to the drum axis (5) is represented by a first spring (12) stressed between a fixed housing part (2, 13) and the common axle (8) and the spring loading in relation to the axis of the motor pinion (19) is represented by a second spring (16) stressed between the common axle (8) and the motor pinion (19).
  2. Drive device according to claim 1, characterised in that the common axle (8) is disposed in the proximity of the free end (11) of a lever (7, 23) mounted to be single armed.
  3. Drive device according to claim 2, characterised in that in the regular operational state the fulcrum (6) of the lever (7, 23) and the common axle (8) together with the fulcrum of the motor pinion (19) lie at least approximately on a straight line (22).
  4. Drive device according to claim 2 or 3, characterised in that the spring loading in relation to the drum axis (5) is represented by a tension spring (12) stressed between a fixed housing part (2, 13) and the outermost free end (11) of the lever (7, 23).
  5. Drive device according to one of claims 2 to 4, characterised in that the spring loading in relation to the axis of the motor pinion (19) is represented by a compression spring (16) stressed between the fulcrum (6) of the lever (7) and the lever arm (7, 17).
  6. Drive device according to one of claims 2 to 4, characterised in that the spring loading in relation to the axis of the motor pinion (19) is represented by a compression spring (28) stressed between the fulcrum (8) of the large belt pulley (9) and a mounting plate (29) fixed to the lever arm (23).
  7. Drive device according to claim 6, characterised in that the fulcrum (8) for the large belt pulley (9) and the intermediate pinion (10) is mounted at a slide (25) guided at the lever (23) at least approximately in the direction of the axis of the motor pinion (19).
  8. Drive device according to claim 7, characterised in that the slide (28) has a chamber-shaped end (26) with a counterbearing bridge (27), which is mounted remotely from the fulcrum (8), for the compression spring (28), the fixed mounting plate (29) of which is disposed at the lever (23) near an elongate hole (30), which is formed in the guide (24) of the slide (25), for the penetration of the lever (23) with the intermediate shaft.
EP95112317A 1994-10-27 1995-08-04 Driving device for domestic laundry drier Expired - Lifetime EP0709515B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4438425 1994-10-27
DE4438425A DE4438425B4 (en) 1994-10-27 1994-10-27 Drive device for a household tumble dryer

Publications (2)

Publication Number Publication Date
EP0709515A1 EP0709515A1 (en) 1996-05-01
EP0709515B1 true EP0709515B1 (en) 2001-05-23

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Application Number Title Priority Date Filing Date
EP95112317A Expired - Lifetime EP0709515B1 (en) 1994-10-27 1995-08-04 Driving device for domestic laundry drier

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US (1) US5694795A (en)
EP (1) EP0709515B1 (en)
DE (2) DE4438425B4 (en)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT1289377B1 (en) * 1996-05-22 1998-10-02 Electrolux Zanussi Elettrodome DEVICE FOR MOUNTING THE MOTOR IN A WASHING MACHINE
DE19728068B4 (en) * 1997-07-01 2006-08-17 BSH Bosch und Siemens Hausgeräte GmbH clothes dryer
US5976043A (en) * 1997-08-18 1999-11-02 Hise; Neil R. Apparatus for increasing wear life of machine members
IT237916Y1 (en) * 1997-09-18 2000-09-29 Candy Spa DRIVE BELT TRANSMISSION, IN PARTICULAR DRYER AND WASHING MACHINE
DE19944253B4 (en) * 1999-09-15 2008-10-16 Senkingwerk Gmbh drum drive
US7168274B2 (en) * 2003-05-05 2007-01-30 American Dryer Corporation Combination washer/dryer having common heat source
US7204774B2 (en) * 2004-05-17 2007-04-17 Emerson Electric Co. One-piece drive pulley and belt guide
DE102006061526A1 (en) * 2006-12-27 2008-07-03 BSH Bosch und Siemens Hausgeräte GmbH Drive unit of domestic spin dryer for drying laundry has drive motor fixed in dryer housing and transmission on turning arm with sprocket fixed to belt pulley
CN110594373B (en) * 2019-08-13 2024-02-13 上海海尔洗涤电器有限公司 Belt tensioning mechanism, clothes dryer and belt tensioning method of clothes dryer

Family Cites Families (7)

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Publication number Priority date Publication date Assignee Title
US2506516A (en) * 1945-09-19 1950-05-02 Hamilton Mfg Co Laundry drier
US2716820A (en) 1952-11-26 1955-09-06 Temco Inc Drying apparatus
US2814886A (en) * 1954-12-27 1957-12-03 Paul L Fowler Clothes dryer
US3066422A (en) * 1959-01-07 1962-12-04 Blackstone Corp Clothes driers
US2994216A (en) * 1959-09-02 1961-08-01 Westinghouse Electric Corp Laundry apparatus
US3382587A (en) * 1966-09-06 1968-05-14 Mc Graw Edison Co Clothes conditioning-drying machine
DE2207372A1 (en) * 1972-02-17 1973-08-23 Miele & Cie CLOTHING DRYER WITH CIRCULATING WASHING DRUM

Also Published As

Publication number Publication date
EP0709515A1 (en) 1996-05-01
US5694795A (en) 1997-12-09
DE4438425B4 (en) 2006-10-26
DE4438425A1 (en) 1996-05-02
DE59509281D1 (en) 2001-06-28

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