EP1719860B1 - Household appliance door and household appliance - Google Patents

Abstract

Door comprises a protective device assigned to a control mechanism (38) which on operation of the door handle (17) prevents transfer of the pivoting movement of the door handle to the control mechanism. An independent claim is also included for a domestic appliance comprising the above door. Preferred Features: The protective device is a blocking element which can be adjusted into a blocking position to prevent the pivoting movement of the handle, a freewheel which uncouples the handle from the control mechanism, or a spring element which absorbs movement of the handle.

Description

The present invention relates to a household appliance and a household appliance door, which is pivotally mounted about a hinge axis, with a door handle which is pivotable about a parallel to the hinge axis Türgriffachse and connected to at least one control gear, the pivoting of the door in a first pivoting direction Door handle pivots in a direction opposite to the first pivoting direction of the second pivoting direction.

From the EP 0 659 960 a generic door is known, which corresponds to the preamble of claim 1. The door is pivotally mounted about a hinge axis and has a handle member. The handle element is pivotably mounted in the door about an axis extending parallel to the hinge axis of the door. The spatial orientation of the handle member is maintained substantially independent of the door position. Between the handle member and a stationary, the door bounding area a control gear is arranged for transmitting the pivotal movement of the door to the door handle.

From the GB 21 83 152 a door handle assembly with a door handle is known which is pivotable about an axis extending parallel to the hinge axis of the door. The door handle is pivotable between a first position in which the door is closed and a second position in which the door is opened. The door handle assembly includes biasing means in communication with the door handle for biasing the door handle to the first position.

The object of the present invention is to provide a household appliance or a household appliance door, which allows a reliable operation.

The object of the invention is achieved by a household appliance door with the features of claim 1 and by a household appliance according to claim 20. According to the characterizing part of claim 1, the control gear of the door is associated with a trained as a tension protection device. With the help of the protective device is a wrong operation of the door handle without pivoting the door prevents a transfer of the pivoting movement of the door handle on the control gear and thus damage the control gear and the resulting pivotal movement of the Door handle added by the tension spring. A pivoted movement exerted by an operator on the door handle is thereby not introduced into the control gear, whereby damage to the control gear is avoided.

In a preferred embodiment of the invention, the spring element exerts a first torque in a pivoting direction of the door handle. As a result, the door handle can be biased in this pivoting direction against an end stop.

The control gear can exert a second torque on the door handle according to another embodiment. This second torque counteracts the first torque. Characterized the pivot position of the door handle is determined depending on the size of the torque.

It is advantageous if the control gear for exerting the first torque has a tension element, which is provided between the tension spring and the door handle and spaced over a first lever arm length of the Türgriffachse engages the door handle. As a result, the tension spring can be arranged spatially separated from the door handle. Thus, on the one hand, the position of the tension spring is freely selectable; On the other hand, the size of the spring is independent of the geometric conditions on the door handle selectable.

It is also advantageous if, for exerting the second torque, a further, second tension element is used, which engages over a second lever arm length spaced from the door handle axis on the door handle. The door handle is advantageously pivoted only by means of attacking tensile forces; Thus, a low-cost pull rope can be used as a tension element that transmits only tensile forces and no shear forces.

In order to suitably adjust the size of the torques exerted on the door handle in accordance with the pivoting position of the door handle, the first and / or second lever arm length can advantageously change as a function of the pivoting position of the door handle. To avoid drive losses in the control gear - for example, due to an extension of tension elements - can be relatively large interpreted at the beginning of an opening movement of the door from the closed position, the Hebelarmlänge the first lever arm, while the lever arm length is smaller in a further pivoting movement.

Thus, the course of the first and second tension elements of the control gearbox is freely selectable, the control gear advantageously has at least one deflection roller. As a result, the position of the tension spring within the door interior is freely selectable.

In a particularly simple preferred embodiment of the invention, the first and second tension members are guided in the opposite direction via a common cam, which is associated with the door handle rotationally fixed. So that the first lever arm length of the first attacking tension element and the second lever arm length of the second attacking tension element are suitably dimensioned as a function of the pivot position of the door handle, the cam may be formed eccentrically.

In order to ensure a smooth and synchronous transmission of motion from the control gear to the door handle, it is advantageous to provide each of the two opposite narrow sides of the door each one of the control gear.

It is advantageous if the two second tension elements of the control gear is assigned a common spring element whose spring ends are in communication with the second tension elements. This ensures that the second torque of the two control gear is equal, causing a synchronous pivoting movement of the door handle is effected.

As a driving part of the control gear acts in a preferred embodiment of the invention, a hinge pin, which is associated with a conventional door hinge. Such a hinge is known to have a hinge part which is supported in the household appliance. In the hinge at least one spring is provided as a weight compensation means, which performs a lifting movement during the pivoting movement of the door. By means of the hinge plunger, the stroke movement of the spring is transmitted to the control gear.

In an alternative preferred embodiment, the drive part of the control gear is formed by a guide element of the door: The guide element is guided in the pivoting movement of the door in a gate path associated with the household appliance and cooperates with the control gear together to transmit a movement of the guide member to the control gear.

For the transmission of motion from the guide element to the control gear, the control gear can have a drive part with which the guide element cooperates. During the pivoting movement of the door, the guide element can rotate the drive part.

Figur 1

in einer perspektivischen Ansicht ein Gargerät mit geöffneter Tür;

Figur 2

in einer vergrößerten Darstellung einen Ausschnitt eines Türgriffes mit zugeordnetem Lagergehäuse;

Figur 3

eine Schnittseitenansicht entlang der Linie A-A; und

Figur 4

eine Seitenschnittdarstellung der Tür entlang der Linie B-B aus der Figur 1;

Figur 5

eine vergrößerte Einzelheit aus der Figur 4;

Figur 6

in einer schematischen perspektivischen Darstellung ein Gargerät gemäß dem zweiten Ausführungsbeispiel;

Figur 7

in einer perspektivischen Darstellung ein Stauraummodul des Gargeräts aus der Figur 6;

Figur 8

eine vergrößerte Einzelheit aus der Figur 7 in perspektivischer Darstellung;

Figuren 9a - 9c

schematische Darstellungen, die einen Öffnungsvorgang der Tür zeigen;

Figur 10

eine Seitenschnittdarstellung eines oberen und unteren Abschnitts der Tür des Gargeräts aus der Figur 6;

Figur 11

eine Seitenschnittdarstellung entlang der Linie D-D aus der Figur 7;

Figur 12

eine Seitenschnittdarstellung entsprechend der Figur 11;

Figur 13

eine vergrößerte Schnittdarstellung entlang der Linie C-C aus der Figur 8;

Figuren 14a - 14c

in einer schematischen Ansicht verschiedene Zusammenbau-Varianten des erfindungsgemäßen Haushaltsgeräts;

Figur 15

in einer perspektivischen Darstellung einen unteren Ausschnitt der Tür;

Figur 16

ein Gargerät mit verschlossener Tür;

Figur 17

eine Schnittdarstellung entlang der Linie E-E aus der Figur 16;

Figur 18

eine vergrößerte Einzelheit aus der Figur 17;

Figur 19

eine vergrößerte Einzelheit entsprechend der Figur 18;

The invention is explained below with reference to four exemplary embodiments. Show it:

FIG. 1

in a perspective view of a cooking appliance with the door open;

FIG. 2

in an enlarged view a section of a door handle with associated bearing housing;

FIG. 3

a sectional side view along the line AA; and

FIG. 4

a side sectional view of the door along the line BB from the FIG. 1 ;

FIG. 5

an enlarged detail from the FIG. 4 ;

FIG. 6

in a schematic perspective view of a cooking appliance according to the second embodiment;

FIG. 7

in a perspective view of a storage module of the cooking appliance from the FIG. 6 ;

FIG. 8

an enlarged detail from the FIG. 7 in perspective view;

FIGS. 9a-9c

schematic diagrams showing an opening operation of the door;

FIG. 10

a side sectional view of an upper and lower portion of the door of the cooking appliance from the FIG. 6 ;

FIG. 11

a side sectional view along the line DD from the FIG. 7 ;

FIG. 12

a side sectional view according to the FIG. 11 ;

FIG. 13

an enlarged sectional view taken along the line CC from the FIG. 8 ;

FIGS. 14a-14c

in a schematic view different assembly variants of the household appliance according to the invention;

FIG. 15

in a perspective view of a lower section of the door;

FIG. 16

a cooking appliance with a locked door;

FIG. 17

a sectional view taken along the line EE from the FIG. 16 ;

FIG. 18

an enlarged detail from the FIG. 17 ;

FIG. 19

an enlarged detail corresponding to FIG. 18 ;

In the FIG. 1 is a cooking appliance 1 shown according to the first embodiment as a household appliance. The cooking appliance 1 has front-side operating and display elements 2 with an associated control unit. In the cooking appliance 1, a cooking chamber 3 is also provided. The cooking chamber 3 is bounded by a muffle 4 open at the front. The front opening of the muffle 4 is framed by a front muffle frame 8. The cooking chamber 3 can be closed by means of a door 5, which is mounted pivotably about a horizontal articulation axis 12. The door 5 has an inner door panel 7 and an outer Door glass 9 made of glass or glass ceramic. At an upper end face 6 of the door 5, a door handle 17 is provided which is pivotally mounted in a bearing housing 21.

In the FIG. 2 the arrangement consisting of the door handle 17 and the bearing housing 21 is shown enlarged in sections in a perspective view. For simplicity, the inner and outer door panels 7, 9 of the door are omitted. The door handle 17 has a handle bar 13 which is connected via bearing blocks 15 with a pivoting part 16. The pivoting part 16 forms the upper end face 6 of the door 5 and has pivot pins 19 on both sides in the longitudinal direction. These are rotatably mounted in the bearing housing 21. Both the bearing housing 21 and the pivot member 16 are preferably made as an injection molded part of a thermoset plastic. At both longitudinal sides of the bearing housing 21 stiffening elements 23 are formed. These dive into a door interior 41 and are releasably attached to lateral edge strips 25 of the door 5, for example screwed.

On the bearing housing 21 additional stiffening elements 27 are formed fronseitig. The stiffening elements 27 are according to the FIG. 3 in contact with the outer door window 9. The FIG. 3 shows a sectional view taken along the line AA from the FIG. 2 in which the door windows 7, 9 are indicated in dashed lines. Accordingly, the stiffening element 27 is in contact with the outer door pane 9, while the inner door pane 7 lies with the interposition of a seal 29 on a contact surface 22 of the bearing housing 21. From the FIG. 3 further shows that the bearing housing 21 has a support surface 31. The support surface 31 is disposed between the lateral pivot pins 19 and extends in the axial direction of the pivot member 16 over almost the entire length of the pivot member 1. In contact with the support surface 31 is a corresponding counter surface 33 of the pivot member 16. In the pivotal movement of the door handle 17 is thus the pivot member 16 is supported on the support surface 31. On the bearing housing 21 further two stops 35, 37 are formed, which limit a pivoting range of the door handle 17.

Like in the FIG. 2 is shown, the door handle 17 is associated with a tension spring 39 which biases the door handle 17 in a pivoting direction. The tension spring 39 is provided below the bearing housing 21 and extends in the longitudinal direction of the bearing housing 21 extends. The tension spring 39 is suspended in the between the door panes 7, 9th formed door interior 41 is arranged. Due to the free-hanging arrangement of the tension spring 39 within the door interior 41, a free expansion and thus a low-wear load of the tension spring 39 is achieved.

The two ends of the tension spring 39 are each connected via a first pull cable 43 with the pivot member 16 to transmit a tension spring force on the pivot member 16. The first traction cables 43 are guided via pulleys 45, which are rotatably mounted on the stiffening elements 27, to cams 47. The cams 47 are rotatably connected on both sides with the longitudinal ends of the pivot member 16. Each of the first traction cables 43 is fixed to an attachment point 46 on the circumference of the cam 47. As a result, the tension spring 39 biases the door handle 17 against the first stop 35 and exerts a first torque M1 in a pivoting direction on the door handle 17 (FIG. FIG. 4 ). To protect against contamination, the cams 47 are arranged within lateral recesses of the pivoting part 16. The recesses are frontally covered by cover portions 18 of the pivot member 16.

At the periphery of each of the cams 47, a second pull cable 48 engages. The second pull cable 48 is guided opposite to the first pull cable 43 around the cam plate 47 and fixed to the attachment point 46 on the circumference of the cam plate 47. The first and second traction cables 43, 48 and the cam disks 47 form components of a control gear 38. The control gear 38 transmits a pivoting movement of the door 5 to the door handle 17, ie, when the door 5 is pivoted in a first pivoting direction, the control gear 38 pivots the door handle 17 in a direction opposite to the first pivoting direction of the second pivoting direction. The structure and operation of the control gear 38 are described below with reference to FIG. 4 explained.

In the FIG. 4 is an upper and lower section of the door 5 in a sectional view taken along the line BB of the FIG. 1 shown. The door 5 is arranged in a closed position. In the lower portion of the door 5, a conventional door hinge 49 is disposed in the door interior 41. The door hinge 49 protrudes with a hinge part 51 through the cooking chamber 3 facing the inside of the door; the hinge part 51 is inserted in a corresponding receptacle of the cooking appliance. As is known, the door hinge 49 has a counterbalancing mechanism, which is indicated by a weight compensating spring 56. The weight compensation mechanism exercises a pivoting movement of the door 5 a compensating force on the hinge part 51; the balancing force counteracts the weight of the door 5. During the pivotal movement of the door 5 results in a lifting movement of one of the spring ends of the counterbalance spring 56. This lifting movement of the spring end is tapped by means of a guided in a long groove 53 hinge pin 55. The hinge pin 55 is connected to the above-described pull cable 48 in connection, which acts on the circumference of the cam 47. Thus, the pull cable 48 converts the linear stroke of the hinge pin 55 in a rotational movement of the cam 47. The hinge pin 55 therefore acts as a driving part of the control gear 38. Is the door 5 from its in the FIG. 4 pivoted downwardly, the hinge pin 55 moves in the slot 53 in a rectilinear movement in the direction of the arrow shown downward. The rectilinear movement of the hinge pin 55 is transmitted to the cam 47 via the pull cable 48, whereby a second torque M2 directed counter to the first torque M1 is exerted on the door handle 17. This can be achieved that in the FIG. 4 shown horizontal orientation of the door handle 17 is maintained substantially independent of the pivotal position of the door 5.

When an operator an upward actuating force F - for example, during transport of the cooking appliance - on the in the FIG. 4 shown door handle 17 exerts, the resulting pivotal movement of the pivot member 16 of the door handle is received by the tension spring 39 in a clockwise direction. This prevents that the clockwise directed pivoting movement is transmitted from the door handle 17 to the control gear 38. The tension spring 39 thus acts as a protective device which prevents damage to the control gear 38.

For dimensioning the spring force of the tension spring 39 and the torque M1 exerted thereby is assumed by a minimum value for the spring force of the tension spring 39. This minimum value corresponds approximately to the frictional forces to be overcome for returning the door handle 17, after no more actuating force F is exerted on the door handle 17. The tension spring 39 is dimensioned such that the above minimum value is about 10-20% of the spring force of the tension spring 39. The spring force of the tension spring 39 is thus about five to ten times greater than this minimum value. In a faulty operation of the door handle 17, such as by exercising after above-directed actuating force F (see FIG. 4 ), therefore damage to the control gear 38 is prevented. At the same time allows the comparatively large spring force during a normal opening or closing operation of the door handle 17 by the operator an ergonomically favorable operating feeling.

To ensure that the movement of the hinge pin 55 is transmitted in a correct ratio to the door handle 17, the radius of the cam 47 is of great importance. The radius of the cam 47 determines on the one hand the length of the lever arm and thus the size of the torque with which the traction cables 43, 48 act on the cam 47. On the other hand, the gear ratio is determined by the cam radius, with which a drive movement of the control gear 38 is converted into a pivoting movement of the door handle 17. In the FIG. 5 the lever arm lengths r1, r2 of the cam disk 47 assigned to the first and the second pull cable 43, 48 are of different sizes. The FIG. 5 illustrates an enlarged view of the cam 47 of the FIG. 4 ,

In the FIG. 5 is the points of application of the traction cables 43 and 48 with the reference numerals A1 and A2 illustrated. The point A1 of the pull cable 43 moves counterclockwise during an opening operation of the door 5 by a rotation angle section of about 90 ° along the circumference of the cam 47. In this rotation angle section, the lever arm length r1 is substantially constant. The force exerted on the door handle 17 torque M1 is therefore constant during the pivotal movement of the door 5. At the same time, the engagement point A2 of the traction cable 48 moves counterclockwise about the rotational angle section of about 90 ° along the circumference of the cam plate 47. In this rotational angle section, the lever arm length r2 decreases with its pivoting movement of the door 5 from its closed position; that is, in the horizontal door position, the torque M2 applied to the door handle 17 is lowest. In the horizontal door position, the torque M2 counteracts a weight force of the door 5; the weight of the door 5 keeps the door 5 stable in its horizontal position. The reduced in the horizontal door position torque M2 is therefore not able to compensate for the weight of the door. The stable position of the door in its horizontal position is thus not affected by the torque M2. By an eccentrically shaped cam 47, the transmission ratio of the control gear 38 can be changed in dependence on the pivotal position of the door 5. Drive losses of the control gear 38, which arise, for example, at the beginning of a pivotal movement of the door by expanding the traction cables 43, 48 or by a game in the control gear 38, can thus be compensated.

In the FIG. 6 a cooking appliance according to a second embodiment is shown. The cooking appliance has a utility space module 83 indicated by a dot-dash line, in which the cooking appliance muffle 3 (not shown) is arranged. Below the utility room module 83, a storage module 79 is arranged. The storage module 79 has a storage space 61 in which a guide system 58 is provided for the door 5. With the guide system 58, the cooking appliance door 5 shown in dashed lines is displaceable in the storage module 79. The storage module 79 serves according to the FIG. 6 as a pedestal or foundation on which the utility module 83 is supported. The storage module 79 is formed as an upwardly open sheet metal housing. At the upper edge of the side walls 80 of the sheet metal housing 79 step-shaped abutment shoulders 85 are formed. On the abutment shoulders 85 is as in the FIG. 6 indicated in the correct position, the Nutzraummodul 83. In the Nutzraummodul 83 are in the FIG. 1 shown control and display elements 2 and an associated control unit provided. The control and display elements 2, together with the associated control unit independent of the storage module 79 are functional.

In contrast to the first embodiment, the drive movement for the control gear 38 is not by the in FIG. 4 shown conventional door hinge 49 produced. The control gear 38 of the second embodiment has rather than drive part a rotary shaft 57. The rotary shaft 57 is in operative connection with a guide element 59 of the guide system 58.

• Wie in der Figur 6 dargestellt ist, ist das Führungselement 59 Teil des Führungssystems 58, mit dessen Hilfe die Tür 5 während eines Öffnungsvorganges in den unterhalb des Garraums 3 vorgesehenen Stauraum 61 eingeschoben wird. Aus den Figuren 6 und 7 geht hervor, dass das Führungssystem 58 Kulissenbahnen 63 aufweist. Die Kulissenbahnen 63 sind in den beiden gegenüberliegenden Seitenwänden 80 des Stauraummoduls 79 ausgebildet. Die gegenüberliegenden Kulissenbahnen 63 führen Gleitstücke 60 des Führungselement 59. Die Gleitstücke 60 sind über eine Verbindungsstange 62 miteinander verschweißt. Das Führungselement 59 ist daher wie ein Führungsschlitten in den gegenüberliegenden Kulissenbahnen 63 geführt. Zwischen den beiden Gleitstücken 60 sind Stellhebel 67 an die Verbindungsstange 62 geschweißt. Wie in dem vergrößerten perspektivischen Ausschnitt der Figur 8 dargestellt ist, sind die Stellhebel 67 mit der Drehwelle 57 des Steuergetriebes 38 formschlüssig verbunden. Die Drehwelle 57 ist in den Figuren 6 und 7 in strichpunktierter Linie angedeutet.

The construction and operation of the guide system 58 for the door 5 and the generation of a drive movement for the control transmission 38 are explained below:

• Like in the FIG. 6 is shown, the guide member 59 is part of the guide system 58, by means of which the door 5 is inserted during an opening operation in the space provided below the cooking chamber 3 61. From the FIGS. 6 and 7 shows that the guide system 58 has slide tracks 63. The slide tracks 63 are formed in the two opposite side walls 80 of the storage module 79. The opposite slide tracks 63 guide sliders 60 of the guide member 59. The sliders 60 are welded together via a connecting rod 62. The guide element 59 is therefore guided like a guide slide in the opposite slide tracks 63. Between the two sliders 60 adjusting lever 67 are welded to the connecting rod 62. As in the enlarged perspective view of the FIG. 8 is shown, the adjusting lever 67 with the rotary shaft 57 of the control gear 38 are positively connected. The rotary shaft 57 is in the FIGS. 6 and 7 indicated in dotted line.

The above-mentioned positive connection between the control levers 67 of the guide carriage 59 and the rotary shaft 57 of the door 5 is in the FIG. 8 shown. In the FIG. 8 are the inner and outer door panel 7, 9 of the door 5 omitted. Accordingly, the rotary shaft 57 is rotatably mounted in the opposite edge strips 25 of the door 5. For positive connection, the adjusting lever 67 of the guide carriage 59 each have a rectangular recess 69 ( FIG. 8 ). In the recess 69, a corresponding rectangular shape portion 71 of the rotary shaft 57 is supported. The lateral edge strips 25 of the door 5 are provided to the outside each with a U-shaped groove which serves as a guide rail. In these guide rails 25 are each a bearing roller 65 slidably guided on both sides. The bearing rollers 65 are fixed to the side wall 80 of the storage module 79. The serving as a guide rail U-shaped groove is formed at its lower end side with an open end 26. Through the open end 26, the housing-fixed bearing roller 65 can be released from the associated guide rail 25 at a later-described door removal.

Each of the opposing slide tracks 63 has a start portion 90 and an insertion portion 91. According to the FIGS. 9a to 9c is a pitch angle of the starting portion 90 in about 45 °. The start portion 90 also occupies about 30% of the total length of the slide track 63, while the transition between the start portion 90 and the insertion portion 91 is arcuate. The insertion portion 91 extends substantially in a horizontal plane. The housing-fixed bearing rollers 65 are arranged approximately at the height of the insertion portion 91 of the slide track 63.

Based on FIGS. 9a to 9c the course of movement of the guide carriage 59 of the door 5 in the slide tracks 63 will be described. In the FIG. 9a the door 5 is shown in its closed position. In the closed position, the sliders 60 of the guide carriage 59 are in the starting portion 90 of the slide track 63. At an opening movement of the door 5 from their in the FIG. 9a shown closed position, the sliders 60 of the guide carriage 59 first move upward. The adjusting lever 67 of the guide carriage 59 thereby lift the door 5 upwards. With this lifting movement of the door 5, at the same time, a lower end face 93 of the door 5, which pivots into the storage space 61, moves away from a floor 117 of the storage space module 79, as can be seen from FIG FIG. 9b evident. A projecting into the storage space 61, indicated by dash-dotted line swivel range S of this lower end face 93 is thereby reduced. After the guide carriage 59 is moved from the starting portion 90 into the horizontal insertion portion 91 ( FIG. 9c ), the door 5 is in a horizontal plane in which it can be inserted into the storage space 61. During the pivoting movement of the door 5, a pivoting angle between the door 5 and the guide carriage 59 changes. Since the rotation shaft 57 of the control gear 38 is positively held in the adjusting levers 67 of the guide carriage 59, the change in the swivel angle between the door 5 and the guide carriage 59 causes a rotation of the rotary shaft 57. That is, the rotary shaft 57 is forcibly rotated during the pivotal movement of the door 5 by the guide member 59.

Based on FIG. 10 is explained in which way the control gear 38 transmits the forced rotation of the rotary shaft 57 on the door handle 17. In the FIG. 10 Fig. 3 is a side sectional view of the upper and lower portions of the door 5 according to the second embodiment. It follows that the adjusting lever 67 projects through an access opening 129 of the door 5 in the door interior 41 and is positively connected to the rotary shaft 57. Again FIG. 8 and the FIG. 10 can be seen, the rotary shaft 57 is formed with a drive drum 54 which is rotatably mounted on the rotary shaft 57. The drive drum 54 is circumferentially with the pull cable 48 into engagement. The pull cable 48 is, as in the first embodiment, with the door handle 17 in connection.

During the pivoting movement of the door 5 therefore results in a pivoting movement between the guide carriage 59 and the door 5, whereby the rotary shaft 57 is forced rotated. The Rotary movement of the rotary shaft 57 is transmitted to the pull cable 48 via the drive drum 54. The traction cable 48 converts the rotational movement of the rotary shaft 57 into a rotational movement of the cam 47 and exerts the second torque M2 on the door handle 17, which is directed against the first torque M1. The door handle 17 thus retains its horizontal orientation regardless of the pivotal position of the door 5.

In contrast to FIG. 4 of the first embodiment are in the FIG. 10 the first traction cables 43 acting on both sides of the cams 47 of the pivoting part 16 of the door handle 17 are not connected to a common tension spring. Rather, according to the FIG. 10 each of the first traction cables 43 assigned its own tension spring 39. The tension spring 39 is fixed with a spring end on the edge bar 25 of the door 5. The other spring end of the tension spring 39 is coupled via a holding eye 75 with the traction cable 43, whereby the first torque M1 is exerted on the door handle 17 in the counterclockwise direction.

That in the FIG. 10 shown control gear 38 has a third pull cable 77. The third pull cable 77 is guided on the one hand in circumferential engagement with the drive drum 54 of the rotary shaft 57 and in the opposite direction to the second pull cable 48 around the drive drum 54. On the other hand, the third pull cable 77 in conjunction with the retaining lug 75 of the first pull cable 43. The first, second and third pull cable 43, 48, 77 of the control gear 38 form a closed cable, for transmitting the rotational movement of the door handle 17, the cam 47 and the drive drum 54 wrapped.

For tightening the closed cable 43, 48, 77 a tightening spring 81 is integrated in the third pull cable 77. The tightening spring 81 is used to tighten the closed cable 43, 48, 77. In addition, the tightening spring 81 increases the torque M1, which is exerted by the tension spring 39 on the door handle 17. For exerting the torque M1, therefore, both the tightening spring 81 and the tension spring 39 are present. Advantageously, two relatively small-sized springs can thus be used, which consume little space in the limited door interior 41.

When the operator, for example, during a transport of the cooking appliance 1, the an upward actuating force F in the in the FIG. 4 shown door handle 17 exerts, the resulting pivotal movement of the pivot member 16 of the door handle is received clockwise by the tension spring 39 and the tightening spring 81. The resulting pivotal movement of the pivoting member 16 is thus not transmitted from the door handle 17 to the control gear 38. Damage to the control gear 38 is prevented.

The dimensioning of the spring force of the tension springs 39, 81 depends on the in connection with the FIG. 4 specified minimum value for the spring force.

Further, the traction cables 43, 48, 77 can be provided with adjusting elements for adjusting a tensile stress. By means of the adjusting elements, the tension cables provided on both sides of the door sides can be subjected to the same tension. As a result, a synchronous operation of the two control gear 38 is achieved.

The following is based on the FIGS. 7 . 11 and 12 a weight balance assembly 94 for the door 5 of the second embodiment described. The weight balance assembly 94 exerts during a movement of the door 5 acting against the weight of the door 5 compensating force on the door 5 from. The weight of the door 5 is therefore not absorbed by the operator during a door movement, but by the weight compensation arrangement 94.

In the FIG. 7 is shown in a perspective view of the storage compartment module 79, of which a space divider 111 described later is shown separately. The counterweight assembly 94 has a pivot lever 95 on each of the opposed side walls 80. The pivot lever 95 is pivotally mounted on the opposite side walls 80 via a lever axis 97. In the FIG. 11 is one of the side walls 80 in an enlarged side sectional view along the line DD of the FIG. 7 shown. Accordingly, the pivot lever 95 projects into the starting portion 90 of the slide track 63 and is engaged with the slider 60 of the guide carriage 59. A pivoting range of the pivot lever 95 is designed such that the pivot lever 95 is only in the region of the start portion 90 with the slider 60 of the guide carriage 59 in engagement. In contrast, the Swing lever 95 in the horizontal portion 91 out of engagement with the slider 60 of the guide carriage 59. The pivot lever 95 is connected to a tension spring 103 in connection. The tension spring 103 is attached to the side wall 80. In the FIG. 11 the tension spring 103 biases the pivot lever 95 in the counterclockwise direction.

When panning in the FIG. 11 Dashed door 5 shown from its closed position down to the horizontal position, the slider 60 extends from the start portion 90 in the horizontal portion 91 of the link path 63. During this movement, the slider 60 of the guide carriage 59 presses against the spring-biased pivot lever 95. The pivot lever 95 thus exercises a balancing force on the slider 60 from. The compensating force counteracts the weight of the door. 5

Like in the FIG. 11 is shown, the pivot lever 95 is pressed by the spring 103 against a first end stop 99 which is formed by a rubber pad. In the in the FIG. 11 shown position, the pivot lever 95 allows an initial movement of the slider 60 of the guide carriage 59 from the closed position of the door 5. During this initial movement of the pivot lever 95 is disengaged from the pivot lever 95. The slider 60 passes according to the FIG. 11 only at a pivot angle of the door 5 of about 20 ° into contact with the pivot lever 95. This simplifies the operator for the initial movement of the door 5 from its closed position. Moreover, the acts according to the FIG. 11 prestressed pivot lever 95 as a stop against which the slider 60 of the guide carriage 59 abuts during the opening movement of the door 5. The operator is thus signaled a certain pivot position of the door 5. In the present case corresponds to this pivotal position of a removal position described later, in which a simple removal of the door 5 is made possible from the guide system 58.

Furthermore, the counterweight assembly 94 has a pivotally mounted retaining element 105, which is biased by a spring 106. The spring-biased holding member 105 presses during the above-described initial movement of the door 5, the slider 60 of the guide carriage 59 in the direction of the pivot lever 95. As a result, the door 5 is stable in the in the FIG. 11 shown removal position held.

In the FIG. 12 the door 5 is mounted horizontally and inserted into the storage space 61. The slider 60 of the guide carriage 59 of the door 5 is located in the horizontal insertion portion 91 of the link path 63. During the movement of the slider 60 in the region of the insertion portion 91 of the slide track 63 of the pivot lever 95 is disengaged from the slider 60. The pivot lever 95 therefore exercises no Balancing force on the door 5. While the slider 60 extends in the insertion portion 91 of the slide track 63, the pivot lever 95 is by means of the spring 103 in a clockwise direction against a second end stop 101, which is also formed by a rubber pad.

The pivot lever 95 has a driver 107. The driver 107 of the pivot lever 95 protrudes in the FIG. 12 in the slide track 63. According to the FIG. 12 the slider 60 has been moved from the start portion 90 in the insertion portion 91 of the slide track 63. The adjusting lever 95 is biased against the second end stop 101 and is in a holding position. When moving the door 5 from the storage space 61, the slider 60 comes into engagement with the driver 107 of the pivot lever 95. As a result, the pivot lever 95 is brought out of its arresting position and comes again in a printing system with the slider 60 of the guide carriage 59. Thus, the Swivel lever 95 again exert the compensating force on the guide carriage 59 during a pivoting movement of the door 5.

Hereinafter, the releasable mounting of the door 5 on the guide system 58 based on FIG. 8 explained. Due to the detachable mounting of the door 5 in the guide system 58, the door 5 is easily removed for cleaning: As already with reference to the FIG. 8 is described, the adjusting lever 67 on a rectangular recess 69. In the rectangular recess 69, the corresponding rectangular shape portion 71 of the rotary shaft 57 is supported. As a result, a positive connection between the guide carriage 59 and the rotary shaft 57 is produced. In the following, a locking element 73 is explained, which according to the FIGS. 8 and 13 is mounted on the rotary shaft 57. The locking element 73 is displaceable between a locking position and a release position. In the release position, the locking element 73 is the holder of the rotary shaft 57 in the Lever 67 free. In a locking position of the locking element 73, the rotary shaft 57 is permanently connected to the adjusting lever 67.

According to the FIG. 8 the locking element 73 has a bearing sleeve, which is displaceably mounted in the axial direction of the rotary shaft 57. On a front side of the bearing sleeve, a projection 76 is formed. The projection 76 protrudes in the FIG. 8 in the direction of a recess provided in the lever 67 recess 78. In the FIG. 8 The release position shown, the projection 76 of the locking member 73 is out of engagement with the recess 78 of the actuating lever 67. By raising the door 5 in an arrow Z, therefore, the rotary shaft 57 can be solved by the guide carriage 59 ..

The bearing sleeve of the locking element 73 has according to the FIG. 13 a guide pin 82. The guide pin 82 is guided in a corresponding longitudinal groove 84 of the rotary shaft 57 between the locking and the release position. This ensures that the projection 76 of the locking element 73 can be pushed into the recess 78 of the adjusting lever 67 in a positionally accurate manner. In addition, the bearing sleeve is formed with a latching projection 86. The latching projection 86 engages in both the release and the locking position in corresponding recesses of the rotary shaft 57 a. The locking element 73 is therefore fixed in the locking and release position. A random displacement of the locking element 73 is thereby prevented.

As already on the basis of FIG. 11 is described, the door 5 is held stable in the removal position in a pivoting angle of about 20 ° after its closed position between the holding member 105 and the adjusting lever 95. In this removal position, the rectangular recess 69 of the control lever 67 is open vertically upwards. The door 5 can therefore be raised vertically for removal in an ergonomically favorable manner, without the mold section 71 of the rotary shaft 57 tilted with the rectangular recess 69 of the control lever 67. At the same time, the housing-fixed bearing rollers 65 are readily feasible in the door removal by the open ends 26 of the lateral guide rails 25 of the door 5.

When the door 5 is removed, the rotary shaft 57 is no longer constrained by the guide carriage 59, but freely rotatable. Due to the freely rotatable rotary shaft 57 has in the FIG. 10 Tightening spring 79 no longer affects the size of the Torque M1, with the door 5 is pressed against the first stop 35. The size of the torque M1 is thus determined with the door 5 removed solely by the force exerted by the tension spring 39 on the pull cable 43 spring force.

The following is the one related to the FIG. 7 mentioned space divider 111 explained. As in particular from the FIG. 6 is apparent, the space divider 111 is disposed in the storage module 79. The room divider 111 divides the storage space 61 into a first storage space 61a and a second storage space 61b. The room divider 111 has a horizontal intermediate floor 113 and side walls 115. In the first storage space 61 a, the door 5 can be moved. The space divider 111 also separates the guide system 58 formed from link track 63 and guide carriage 59 and the counterweight assembly 94 from the second storage compartment 61b. In the second storage space 61 b baking trays or other accessories can be stored.

Like from the FIGS. 9a to 9c is apparent, the space divider 111 is disposed below the start portion 90 and the insertion portion 91 of the slide track 63. In this case, the intermediate bottom 113 together with the side walls 115 and a housing bottom 117 an access opening 119. This is spaced from the indicated by dotted line pivoting range S of the lower end face 93 of the door 5 is arranged. In the area of the access opening 119 of the second storage space 61b, display elements 121 are provided ( FIGS. 7 and 8th ). The display elements 121 are formed as cams, which are fixed to the bottom 117 of the storage space 61. The display elements 121 indicate to the operator a maximum allowable length for objects that can be stored in the second storage space 61 b without protruding into the pivoting area S of the lower end face 93 of the door 5. On the side walls 115 of the room divider 111 device front side aperture 123 are formed ( FIG. 7 ). The panels 123 serve as a visual screen for the first storage space 61 a. In addition, a collecting channel 125 is provided in the housing bottom 117 in the region of the appliance front access opening 119 in order to keep the second storage space 61b free of contaminants, for example dripping condensate water.

In the FIGS. 14a) to 14c ) are shown in schematic view different variants of the household appliance according to the invention. According to the Figure 14a ), the utility module 83 and the storage module 79 are shown separated from each other. The structure and the operation of both modules 79, 83 corresponds to that of the preceding figures. The storage space module 79 and the utility space module 83 are first manufactured independently of each other as separate units. Subsequently, in an assembly step, the storage space module 79 and the utility space module 83 are joined together to form the household appliance. According to the Figure 14a the storage space module 79 serves as a pedestal on which the utility space module 83 is set in the direction of the arrow.

In contrast to Figure 14a is in the FIG. 14b the storage module 79 is disposed above the utility room module 83. The door 5 is therefore displaced upward into the storage space 61 of the storage module 79. In the FIG. 14c is the storage module 79 arranged edgewise. The edgewise arranged storage module 79 is according to the FIG. 14c attached to one side of the utility module 83. The door 5 is therefore displaceable in the storage space 79 arranged laterally on the utility space module 83.

In the FIG. 15 is a section of a bottom of the door 5 is shown in a perspective view. Accordingly, a sheet metal element 127 is glued to the inner door glass 7 by means of an adhesive connection. A part of the cooking chamber 3 facing inside of the door 5 is therefore formed by the sheet metal element 127. The sheet metal element 127 has an extension section which extends the inner door pane 7 to the lower end face 93 of the door 5. In addition, the sheet metal element 127 is bent at right angles to the formation of the lower end face 93 of the door 5. At the end of the bent portion of the sheet metal element 127 a bearing surface 134 is formed. By means of the contact surface 134, the distance between the outer door panel 9 and the inner door panel 7 is fixed.

Further, in the extension portion of the plate member 127, a through hole 129 is formed. Through the through hole 129 of the adjusting lever 67 of the guide carriage 59 projects, which is arranged in the door interior 41 with the rotary shaft 57 in engagement ( FIG. 8 ). Alternatively, through the passage opening 129 in the FIG. 4 shown hinge part 51 of the door hinge 49 of the first embodiment protrude. The passage opening 129 extends not only in the plane of the door inner side, but also in the plane of the lower end face 93 of the door fifth

In the sheet metal element 127 further mounting or operating openings can be provided. For example, according to the FIG. 15 on the lower end face 93 of the door 5, an operating opening 131 is provided. The operating opening 131 gives the operator access to the locking element 73, which is arranged adjustably on the rotary shaft 57. The locking element 73 is thus adjustable in a simple manner between the locking and the release position. In the sheet metal element 127, a collecting channel 133 is further embossed for collecting dripping condensate liquid. If the door 5 is therefore arranged horizontally in the storage space 61, condensate accumulates on the inside of the door in the collecting channel 133. In addition, the sheet metal element 127 has angle brackets 135 which serve to fasten the inner door pane 7 to the edge strips 25 of the door. About the angle bracket 135, the inner door panel 7 can be fastened in a simple manner to the edge strips 25 of the door, for example by means of a screw connection.

In the following spacers 139 are described, by means of which the door 5 can be arranged in the correct position in its closed position. In the FIG. 16 the cooking appliance 1 is shown, the door 5 is arranged in its closed position. On both sides of the door 5 edge strips 137 of the cooking appliance are arranged. The edge strips 137 are spaced from the door 5 via a gap 138. In the FIG. 17 is a sectional view taken along the line EE of the FIG. 16 shown. It follows that spacers 139 are provided between the lateral edges of the inner door panel 7 and the respective opposite edge strips 137. The spacers 139 are molded from plastic and fixed to the skirting 137 on the housing side. In the closed position of the door 5, the spacers 139 define a gap width b between the door 5 and the skirt 137. For optical reasons, it is preferred that the spacers 139 keep the door 5 centered between the skirting boards 137.

The Indian FIG. 18 shown spacers 139 has a ramp 14 and a centering 143. The ramp be 141 leads the door 5 in a closing movement in the closed position in which the optically favorable gap width b is reached. The centering portion 143 follows in the closing direction of the door 5 after the run-on slope 141. In the closed position of the door 5, the centering 143 of the opposing spacers 139 each side stops for the opposite edges of the inner door glass 7. As in the enlarged Detail from the FIG. 18 is shown, the marginal edges of the inner door panel 7 between the centering portions 143 of the spacers 139 and the opposite peripheral edge of the inner door panel 7 are arranged with a slight play s of about 1mm.

In the FIG. 19 a modification of the above-described spacer 139 is shown. Accordingly, the run-up slope 141 is formed bulged and merges without transitional edges in the centering 143. The opposite edge of the inner door panel 7 is also rounded. During the closing movement of the door 5 in the direction of the arrow, therefore, a particularly smooth positioning of the door 5 between the centering sections 139 is achieved.

By means of the spacers 139, it is possible to support the guide carriage 59 with an axial clearance in the link tracks 63. The axial clearance ensures smooth sliding of the guide carriage 59 in the link tracks 63. On the other hand, it is ensured by the spacers 139 that the door 5 - despite the axial play - is positioned in the correct position in its closed position.

Claims (20)

1. Domestic appliance door, especially oven door, which is pivotably mounted about an articulated axis (12, 65), having a door handle (17), which can be pivoted about a door handle axis (19) running parallel to the pivot axis (12, 65) and is connected to at least one control gear (38), which pivots the door handle (17) in a second pivot direction opposing a first pivot direction when the door (5) is pivoted in a first direction, characterised in that a protective device (39) embodied as a tension spring is assigned to the control gear (38), by means of which, when the door handle (17) is operated incorrectly without pivoting the door (5), a transmission of the pivot movement from the door handle to the control gear (38) and thus damage to the control gear (38) is prevented and the tension spring (39) absorbs the pivot movement of the door handle (17) resulting therefrom.
2. Domestic appliance door according to claim 1, characterised in that the spring element (3 9) exerts a first torque (M1) in a pivot direction of the door handle (17).
3. Domestic appliance door according to claim 2, characterised in that the control gear (38) exerts a second torque (M2) on the door handle (17) acting in the opposite direction to the first torque (M1).
4. Domestic appliance door according to claim 2 or 3, characterised in that the control gear (3 8), in order to exert the first torque (M1), has a first tension element (43) which connects the spring element (39) to the door handle (17) and engages with the door handle (17) via a first lever arm length (r1) at a distance from the door handle axis (19).
5. Domestic appliance door according one of claims 3 to 4, characterised in that the control gear (38), in order to exert the second torque (M2), has a second tension element (48) which engages with the door handle (17) via a second lever arm length (r2) at a distance from the door handle axis (19).
6. Domestic appliance door according to one of claims 4 or 5, characterised in that the first and/or second lever arm lengths (r1, r2) change as a function of a pivot position of the door handle (17).
7. Domestic appliance door according to one of claims 4 or 5, characterised in that the first and/or second lever arm lengths (r1, r2) are constant, regardless of a pivot position of the door handle (17).
8. Domestic appliance door according to one of claims 4 to 7, characterised in that the control gear (38) has at least one guide pulley (45) which is mounted on the door (5) and which determines the course of the first and/or second tension element (43, 48).
9. Domestic appliance door according to one of claims 5 to 9, characterised in that the first and second tension elements (43, 48) are guided into the opposite direction via a common cam (47), which is assigned to the door handle (17).
10. Domestic appliance door according to claim 9, characterised in that the first lever arm length (r1) of the common cam (47) is greater than the second lever arm length (r2) of the common cam (47).
11. Domestic appliance door according to one of claims 9 or 10, characterised in that the control gear has a tension element (43, 48, 77) closed in a loop-like manner for transmission of the rotational movement from the drive part (57) to the door handle (17).
12. Domestic appliance door according to claim 11, characterised in that a tightening means (81) is provided in the control gear (38) for tightening the tension element (43, 48, 77) closed in a loop-like manner.
13. Domestic appliance door according to one of the preceding claims, characterised in that on each of the two opposing narrow faces (25) of the door (5) one of the control gears (38) is provided in each case.
14. Domestic appliance door according to claim 13, characterised in that a common spring element (39) is assigned to the two second tension elements (48) of the two control gears (38), the spring ends of said spring element (39) being connected to the two tension elements (48).
15. Domestic appliance door according to one of the preceding claims, characterised in that the control gear (38) is actively connected to a drive part (55, 59) which moves upon the pivot movement of the door (5).
16. Domestic appliance door according to one of the preceding claims, characterised in that the drive part is a guide element (59) assigned to the door (5), which is guided in a slide track (63) assigned to the domestic appliance upon the pivot movement of the door, and the guide element (59) interacts with the control gear to transmit a movement of the guide element (59) to the control gear.
17. Domestic appliance door according to claim 16, characterised in that the control gear (38) has a drive shaft (57) with which the guide element (59) interacts, and the guide element (59) rotates the drive shaft (57) upon the pivot movement of the door (5).
18. Domestic appliance door according to one of claims 1 to 10, which has a hinge (49) with a hinge part (51), which is retained in the domestic appliance, which hinge (49) has at least one spring (55) as counterbalance means, which carries out a lifting movement of a hinge plunger (55) upon the pivot movement of the door (5), characterised in that the drive part is formed by the hinge plunger (55).
19. Domestic appliance door according to one of the preceding claims, characterised in that the spring force of the tension spring (39) is five to ten times greater than a minimum value of a spring force, which approximately corresponds to the friction forces which should be overcome in order to reset the door handle (17).
20. Domestic appliance, especially oven, with a domestic appliance door according to one of the preceding claims.

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