Abstract:
A door for household appliances, in particular, a door for cooking appliances, are mounted to pivot about an articulation axis include a door handle that can be pivoted about a door-handle axis that runs parallel to the articulation axis and is connected to at least one control mechanism. When the door is pivoted in a first pivoting direction, the control mechanism pivots the door handle in a second pivoting direction that is opposite to the first. According to the invention, to obtain a reliable actuation of the door handle, a protective device is allocated to the control mechanism and prevents the pivoting motion of the door handle, during the actuation of the latter, from being transmitted to the control mechanism.

Description:
CROSS-REFERENCE TO RELATED APPLICATION 
   This application is a continuation, under 35 U.S.C. § 120, of copending international application No. PCT/EP03/01452, filed Feb. 13, 2003, which designated the United States; this application also claims the priority, under 35 U.S.C. § 119, of German patent application No. 102 08 494.7, filed Feb. 27, 2002; the prior applications are herewith incorporated by reference in their entirety. 

   BACKGROUND OF THE INVENTION 
   Field of the Invention 
   The present invention relates to a household appliance and to a household-appliance door that is mounted such that it can be pivoted about a hinge pin or articulation axis, having a door handle that can be pivoted about a door-handle axis running parallel to the articulation axis and connected to at least one control mechanism that, when the door is pivoted in a first pivoting direction, pivots the door handle in a second pivoting direction, counter to the first pivoting direction. 
   European Patent Application EP 0 659 960 discloses a generic door that is mounted pivotable about a hinge pin and has a handle element. The handle element is mounted in the door in a manner such that it can pivot about an axis running parallel to the hinge pin of the door. The spatial alignment or orientation of the handle element is retained substantially independently of the door position. A control mechanism is disposed between the handle element and a positionally fixed region delimiting the door, and is intended for transmitting the pivoting movement of the door to the door handle. 
   British Patent No. GB 21 83 152 discloses a door handle configuration having a door handle that can be pivoted about an axis running parallel to the hinge pin of the door. The door handle can be pivoted between a first position, in which the door is closed, and a second position, in which the door is open. The door handle configuration has a pre-stressing device that is connected to the door handle to pre-stress the door handle towards the first position. The door handle configuration has a housing that is fitted into the door structure. 
   SUMMARY OF THE INVENTION 
   It is accordingly an object of the invention to provide a household appliance and household appliance door that overcome the hereinafore-mentioned disadvantages of the heretofore-known devices of this general type and in which the door  handle can be actuated in an operationally reliable manner. With the foregoing and other objects in view, there is provided, in accordance with the invention, a household appliance door to be mounted pivotally about a hinge pin, the door including a door body configured to pivot about the hinge pin, the door body having a door handle pivotally disposed in the door body about a door handle axis disposed parallel to the hinge pin, at least one control mechanism operatively connected to the door handle to, during a pivoting of the door body in a first pivoting direction, pivot the door handle in a second pivoting direction opposite the first pivoting direction, and the at least one control mechanism having a safeguarding device preventing the pivoting movement of the door handle from being transmitted from the door handle to the at least one control mechanism during actuation of the door handle. 
   With the objects of the invention in view, there is also provided a household cooking appliance, including a housing having a hinge pin and a door according to the invention. 
   According to the invention, the control mechanism of the door has a safeguarding device. With the aid of the safeguarding device, during actuation of the door handle, the pivoting movement is prevented from being transmitted from the door handle to the control mechanism. A pivoting movement to which the door handle is subjected by a user is, thus, not introduced into the control mechanism, as a result of which, damage to the control mechanism is avoided. 
   In accordance with another feature of the invention, the safeguarding device is formed by a blocking element that can be adjusted into a blocking position. In the blocking position, the blocking element prevents the pivoting movement of the door handle. Such a blocking element can be used, in particular, during transportation of the household appliance. In the blocking position, the door handle is fixed and can be used to carry the household appliance without the control mechanism being damaged. Because, in an installed position of the household appliance, the door handle is no longer used as transporting measures, it is possible, in the installed position, for the blocking element to be adjusted into the release position. 
   In accordance with a further feature of the invention, the safeguarding device is formed by a freewheel coupling. The freewheel coupling uncouples the door handle from the control mechanism when the pivoting movement is transmitted from the door handle to the control mechanism. It is advantageous here that the control mechanism is safeguarded permanently against a pivoting movement emanating from the door handle without there being any need for additional handling steps, e.g., displacing a blocking element into the blocking position. 
   In accordance with an added feature of the invention, to prevent, in as straightforward a manner as possible, the pivoting movement from being transmitted from the door handle to the control mechanism, the safeguarding device, in a particularly advantageous configuration of the invention, is formed by a tension spring. The tension spring, when the pivoting movement is transmitted from the door handle to the control mechanism, absorbs the movement of the door handle. 
   In accordance with an additional feature of the invention, the spring element exerts a first torque in a pivoting direction of the door handle. The door handle can, thus, be pre-stressed against an end stop in this pivoting direction. 
   In accordance with yet another feature of the invention, the control mechanism can subject the door handle to a second torque. This second torque counteracts the first torque. The pivoting position of the door handle is, thus, defined in dependence on the magnitude of the torque. 
   In accordance with yet a further feature of the invention, it is advantageous if, for exerting the first torque, the control mechanism has a pulling element that is provided between the tension spring and the door handle and acts on the door handle such that it is spaced apart from the door-handle axis through a first lever-arm length. The tension spring may, thus, be disposed separately from the door handle. Consequently, on one hand, the position of the tension spring can be freely selected; on the other hand, it is also possible to select the size of the spring regardless of the geometrical conditions on the door handle. 
   In accordance with yet an added feature of the invention, it is also advantageous if, for exerting the second torque, use is made of a further, second pulling element that acts on the door handle such that it is spaced apart from the door-handle axis through a second lever-arm length. The door handle is, advantageously, pivoted merely by tensile forces acting on it; the pulling element used may, thus, be a cost-effective pulling cable that transmits only tensile forces and no shear forces. 
   In accordance with yet an additional feature of the invention, for the magnitude of the torques to which the door handle is subjected to be adjusted in a suitable manner in accordance with the pivoting position of the door handle, the first and/or second lever-arm length(s) may change in dependence on the pivoting position of the door handle. To avoid drive losses in the control mechanism—for example, on account of stretching of pulling elements—it is possible for the length of the first lever arm to be configured to be comparatively long at the beginning of an opening movement of the door from the closed position, while the lever-arm length becomes smaller during a further pivoting movement. 
   In accordance with again another feature of the invention, so that the course taken by the first and second pulling elements of the control mechanism can be freely selected, the control mechanism advantageously has at least one deflecting roller. The position of the tension spring within the door interior can, thus, be freely selected. 
   In accordance with again a further feature of the invention, the first and second pulling elements are guided in opposite directions over a common cam plate, which is associated in a rotationally fixed manner to the door handle. So that the first lever-arm length of the first pulling element and the second lever-arm length of the second pulling element are dimensioned in a suitable manner in dependence on the pivoting position of the door handle, the cam plate may be eccentric. 
   In accordance with again an added feature of the invention, the cam plate defines the first lever-arm distance and the second lever-arm distance and the first lever-arm distance is greater than the second lever-arm distance. 
   In accordance with again an additional feature of the invention, to ensure a smooth-running and synchronous transition of the movement from the control mechanism to the door handle, it is advantageous for in each case one of the control mechanisms to be provided on each of the two opposite narrow sides of the door. 
   In accordance with still another feature of the invention, at least one of the control mechanism, the first pulling element, and the second pulling element are connected to keep at least one of the first and second lever-arm lengths constant regardless of a pivoting position of the door handle. 
   In accordance with still a further feature of the invention, there is provided a drive part connected to the door handle and the control mechanism has a pulling element connected to the drive part and closed in a loop for transmitting rotary movement of the drive part to the door handle. 
   In accordance with still an added feature of the invention, the control mechanism has a tensioner for tensioning the pulling element. 
   In accordance with still an additional feature of the invention, it is advantageous, here, if the two second pulling elements of the control mechanisms are associated with a common spring element, of which the spring ends are connected to the second pulling elements. Such a configuration ensures that the second torques of the two control mechanisms are of equal magnitude, this resulting in a synchronous pivoting movement of the door handle. 
   In accordance with another feature of the invention, there is provided a hinge rod, which is associated with a conventional door hinge, acts as a drive part of the control mechanism. Such a hinge has, as is known, a hinge part secured in the household appliance. Provided in the hinge, as weight-balancing measures, is at least one spring that, during the pivoting movement of the door, executes a displacement movement. By the hinge rod, the displacement movement of the spring is transmitted to the control mechanism. 
   In accordance with a further feature of the invention, the spring element is a tension spring having a spring force between approximately five and ten times greater than a minimum value for a spring force corresponding approximately to frictional forces having to be overcome to restore the door handle. 
   In accordance with an added feature of the invention, in an alternative configuration, the drive part of the control mechanism is formed by a guide element of the door; the guide element, during the pivoting movement of the door, is guided in a sliding track associated with the household appliance, and interacts with the control mechanism to transmit a movement of the guide element to the control mechanism. 
   In accordance with a concomitant feature of the invention, to transmit movement from the guide element to the control mechanism, the control mechanism may have a drive part with which the guide element interacts. During the pivoting movement of the door, the guide element can rotate the drive part. 
   Other features that are considered as characteristic for the invention are set forth in the appended claims. 
   Although the invention is illustrated and described herein as embodied in a household appliance and household appliance door, it is, nevertheless, not intended to be limited to the details shown because various modifications and structural changes may be made therein without departing from the spirit of the invention and within the scope and range of equivalents of the claims. 
   The construction and method of operation of the invention, however, together with additional objects and advantages thereof, will be best understood from the following description of specific embodiments when read in connection with the accompanying drawings. 

   
     BRIEF DESCRIPTION OF THE DRAWINGS 
       FIG. 1  is a perspective front view of a first exemplary embodiment of a cooking appliance according to the invention with an opened door; 
       FIG. 2  is a fragmentary, enlarged perspective and partially hidden view of a cutout of a door handle according to the invention with an associated bearing housing; 
       FIG. 3  is a fragmentary, side cross-sectional view of the handle of  FIG. 2  along section line A—A; 
       FIG. 4  is a fragmentary, side cross-sectional view of the door handle of  FIG. 1  along section line B—B; 
       FIG. 5  is a diagrammatic, enlarged, cross-sectional view of a detail of the handle of  FIG. 4 ; 
       FIG. 6  is a fragmentary, perspective and partially hidden view of a second exemplary embodiment of a cooking appliance according to the invention; 
       FIG. 7  is a fragmentary, perspective and partially hidden view of a storage space module of the cooking appliance of  FIG. 6 ; 
       FIG. 8  is a fragmentary, enlarged, perspective view of a detail of the module of  FIG. 7 ; 
       FIG. 9A  is a fragmentary, side elevational and partially hidden view of a first part of an opening process of the mechanism of  FIG. 8 ; 
       FIG. 9B  is a fragmentary, side elevational and partially hidden view of a second part of an opening process of the mechanism of  FIG. 8 ; 
       FIG. 9C  is a fragmentary, side elevational and partially hidden view of a third part of an opening process of the mechanism of  FIG. 8 ; 
       FIG. 10  shows a side sectional illustration of an upper and lower section of the door of the cooking appliance from  FIG. 6 ; 
       FIG. 11  is a side elevational view of the mechanisms of  FIGS. 7 and 8  along line D—D in  FIG. 7  in a first position; and 
       FIG. 12  is a side elevational view of the mechanism of  FIG. 11  in a second position. 
       FIG. 13  is a fragmentary, enlarged, cross-sectional view of a portion of the module of  FIG. 8  along section line C—C; 
       FIG. 14A  is a diagrammatic front elevational view of a first embodiment of an assembly of the household appliance according to the invention; 
       FIG. 14B  is a diagrammatic front elevational view of a second embodiment of an assembly of the household appliance according to the invention; 
       FIG. 14C  is a diagrammatic front elevational view of a third embodiment of an assembly of the household appliance according to the invention; 
       FIG. 15  is a fragmentary, enlarged, perspective view a bottom part of an embodiment of door according to the invention; 
       FIG. 16  is a perspective view of a cooking appliance according to the invention with the door in a closed position; 
       FIG. 17  is a fragmentary, enlarged, cross-sectional view of a portion of the appliance of  FIG. 16  along section line E—E; 
       FIG. 18  is a fragmentary, enlarged, cross-sectional view of a first embodiment of a detail of the portion of  FIG. 17 ; 
       FIG. 19  a fragmentary, enlarged, cross-sectional view of a second embodiment of a detail of the portion of  FIG. 17 ; 
       FIG. 20  a fragmentary, side elevational view of a third embodiment of a top portion of the door according to the invention; and 
       FIG. 21  is a block circuit diagram illustrating a fourth exemplary embodiment of a control flow of the door according to the invention. 
   

   DESCRIPTION OF THE PREFERRED EMBODIMENTS 
   Referring now to the figures of the drawings in detail and first, particularly to  FIG. 1  thereof, there is shown a cooking appliance  1  in a first exemplary embodiment of a household appliance according to the invention. The cooking appliance  1  has front-side operating and display elements  2  with an associated non-illustrated control unit. Furthermore, a cooking space  3  is provided in the cooking appliance  1 . The cooking space  3  is bounded by a muffle  4  that is open on the front side. A front-side muffle frame  8  frames the front-side opening of the muffle  4 . The cooking space  3  can be closed by a door  5  that is mounted pivotally about a horizontal hinge pin or articulation axis  12 . The door  5  has an inner door window  7  and an outer door window  9  of glass or glass ceramic. A door handle  17 , which is mounted pivotally in a bearing housing  21 , is provided on an upper end side  6  of the door  5 . 
     FIG. 2  shows the configuration including the door handle  17  and the bearing housing  21  in a perspective illustration enlarged in some sections. For simplification purposes, the inner and outer door windows  7 ,  9  of the door are omitted. The door handle  17  has a handle strip  13  that is connected to a pivoting part  16  through bearing blocks  15 . The pivoting part  16  forms the upper end side  6  of the door  5  and has pivot pins  19  on both sides in the longitudinal direction. The pivot pins  19  are mounted rotatably in the bearing housing  21 . Both the bearing housing  21  and the pivoting part  16  are, preferably, manufactured as an injection molded part from a duroplastic (thermosetting plastic material). Stiffening elements  23  are formed on both longitudinal sides of the bearing housing  21 . These stiffening elements  23  dip into an inner space  41  of the door and are fastened releasably, for example, screwed, to lateral edge strips  25  of the door  5 . 
   Additional stiffening elements  27  are formed on the front side of the bearing housing  21 . According to  FIG. 3 , the stiffening elements  27  are in contact with the outer door window  9 .  FIG. 3  shows a sectional illustration along the line A—A from  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 window  9  while the inner door window  7  rests, with the interposition of a seal  29 , against a contact surface  22  of the bearing housing  21 .  FIG. 3 , furthermore, reveals that the bearing housing  21  has a supporting surface  31 . The supporting surface  31  is disposed between the lateral pivot pins (journals)  19  and extends in the axial direction of the pivoting part  16  over virtually the entire length of the pivoting part  1 . A corresponding mating surface  33  of the pivoting part  16  is in contact with the supporting surface  31 . During the pivoting movement of the door handle  17 , the pivoting part  16  thereof is, therefore, supported on the supporting surface  31 . Furthermore, two stops  35 ,  37  that restrict and bound a pivoting region of the door handle  17  are formed on the bearing housing  21 . 
   As illustrated in  FIG. 2 , the door handle  17  is assigned a tension spring  39  that pre-stresses 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 . The tension spring  39  is suspended freely in the inner space  41  of the door that is formed between the door windows  7 ,  9 . The freely suspended configuration of the tension spring  39  within the inner space  41  of the door makes it possible to achieve a free expansion and, therefore, low-wear loading of the tension spring  39 . 
   The two ends of the tension spring  39  are connected in each case through a first tension cable  43  to the pivoting part  16  to transmit a tension spring force to the pivoting part  16 . The first tension cables  43  are guided through deflecting rollers  45 , which are mounted rotatably on the stiffening elements  27 , to radial cam plates  47 . The radial cams  47  are connected on both sides in a rotationally fixed manner to the longitudinal ends of the pivoting part  16 . Each of the first pulling cables  43  here is fixed on the circumference of the cam plate  47  at a fastening point  46 . As a result, the tension spring  39  pre-stresses the door handle  17  against the first stop  35  and subjects the door handle  17  to a first torque M 1  in a pivoting direction ( FIG. 4 ). To protect against contamination, the radial cams  47  are disposed within lateral cutouts of the pivoting part  16 . Covering sections  18  of the pivoting part  16  cover the cutouts on the end side. 
   A second tension cable  48  engages on the circumference of each of the radial cams  47 . The second tension cable  48  is guided around the cam plate  47  in the direction counter to the first pulling cable  43  and is fixed on the circumference of the cam plate  47  at the fastening point  46 . The first and second tension cables  43 ,  48  and the radial cams  47  form constituent parts of a control mechanism  38 . The control mechanism  38  transmits a pivoting movement of the door  5  to the door handle  17 , i.e., when the door  5  is pivoted in a first pivoting direction, the control mechanism  38  pivots the door handle  17  in a second pivoting direction, counter to the first pivoting direction. The construction and functioning of the control mechanism  38  are explained below with reference to  FIG. 4 . 
     FIG. 4  shows an upper and lower cutout of the door  5  in a sectional illustration along the line B—B from  FIG. 1 . The door  5  is disposed in a closed position. In the lower section of the door  5 , a conventional door hinge  49  is disposed in the interior space  41  of the door. The door hinge  49  has a hinge part  51  projecting through the inside of the door, which is directed toward the cooking space  3 ; the hinge part  51  is inserted in a corresponding socket in the cooking appliance. As is known, the door hinge  49  has a weight-balancing mechanism that is indicated by a weight-balancing spring  56 . During a pivoting of the door  5 , the weight-balancing mechanism exerts a balancing force on the hinge part  51 ; the balancing force counteracts the weight of the door  5 . A displacement movement of one of the ends of the weight-balancing spring  56  is achieved during the pivoting movement of the door  5 . This lifting movement of the spring end is picked off by a hinge rod or tappet  55  guided in a longitudinal groove  53 . The hinge rod  55  is connected to the abovedescribed pulling cable  48 , which acts on the circumference of the cam plate  47 . The tension cable  48 , therefore, converts the rectilinear lifting movement of the hinge rod  55  into a rotational movement of the radial cam  47 . The hinge rod  55 , therefore, acts as a driving part of the control mechanism  38 . If the door  5  is pivoted downward from its closed position, which is shown in  FIG. 4 , the hinge rod  55  moves in a rectilinear movement downward, in the direction of the arrow C that is shown, in the elongated hole or slot  53 . The rectilinear movement of the hinge rod  55  is transmitted through the tension cable  48  to the radial cam  47 . As a result, a second torque M 2  that is directed counter to the first torque M 1  is exerted on the door handle  17 . The effect that can be achieved as a result is that the horizontal orientation of the door handle  17  that is shown in  FIG. 4  is substantially retained regardless of the pivoting position of the door  5 . 
   If an operator exerts an upwardly directed actuating force F on the door handle  17  shown in FIG.  4 —for example, during transportation of the cooking appliance—the resultant pivoting movement of the pivoting part  16  of the door handle in the clockwise direction is absorbed by the tension spring  39 . This prevents the pivoting movement of the door handle  17 , which movement is directed in the clockwise direction of  FIG. 4 , from being transmitted to the control mechanism  38 . The tension spring  39 , accordingly, acts, as a safeguarding device that prevents damage to the control mechanism  38 . 
   The magnitude of the spring force of the tension spring  39  and/or the torque M 1  exerted thereby is based on a minimum value for the spring force of the tension spring  39 . This minimum value corresponds approximately to the frictional forces that have to be overcome to restore the door handle  17  after an actuating force F is no longer exerted on the door handle  17 . The tension spring  39  is dimensioned such that the abovementioned minimum value is approximately 10% to 20% of the spring force of the tension spring  39 . The spring force of the tension spring  39  is, therefore, approximately five to ten times larger than this minimum value. When the door handle  17  is actuated incorrectly, for example, as a result of the upwardly directed actuating force F being exerted (see  FIG. 4 ), damage to the control mechanism  38  is, thus, prevented. At the same time, the comparatively large spring force permits an ergonomically favorable operating feel during a normal opening or closing actuation of the door handle  17  by the operator. 
   The radius of the cam plate  47  is very important to ensure that the movement of the hinge rod  55  is transmitted to the door handle  17  in a correct transmission ratio. On one hand, the radius of the cam plate  47  determines the length of the lever arm and, thus, the magnitude of the torque by which the pulling cables  43 ,  48  act on the cam plate  47 . On the other hand, the cam-plate radius defines the transmission ratio by which a drive movement of the control mechanism  38  is converted into a pivoting movement of the door handle  17 . In  FIG. 5 , the lever-arm lengths r 1 , r 2  of the cam plate  47 , which lengths are associated with the first and the second tension cable  43 ,  48 , are configured such that they differ in magnitude.  FIG. 5  shows an enlarged illustration of the radial cam  47  from  FIG. 4 . 
   In  FIG. 5 , the points of action of the pulling cables  43  and  48  are designated A 1  and A 2 . During an operation for opening the door  5 , the point of action A 1  of the pulling cable  43  moves through an angle of rotation of approximately 90° in the counterclockwise direction along the circumference of the cam plate  47 . Over this angle of rotation, the lever arm length r 1  is substantially constant. The torque M 1  exerted on the door handle  17  is, therefore, constant during the pivoting movement of the door  5 . At the same time, the engagement point A 2  of the tension cable  48  moves through an angle of rotation section of approximately 90° in the counter-clockwise direction (with respect to  FIG. 5 ) along the circumference of the radial cam  47 . Over this angle of rotation, the lever arm length r 2  is reduced during a pivoting movement of the door  5  from its closed position; that is to say, in the horizontal door position, the torque M 2  exerted on the door handle  17  is the lowest possible. In the horizontal door position, the torque M 2  counteracts a weight of the door  5 ; the weight of the door  5  keeps the door  5  stably in its horizontal position. The torque M 2 , which is reduced in the horizontal door position, is, therefore, not capable of compensating for the weight of the door. The stable position of the door in its horizontal position is, therefore, not adversely affected by the torque M 2 . 
   A radial cam  47  that is formed eccentrically enables the transmission ratio of the control mechanism  38  to be changed as a function of the pivoting position of the door  5 . It is thus possible to compensate for drive losses of the control mechanism  38 , which are produced, for example, at the beginning of a pivoting movement of the door as a result of expansion of the pulling cables  43 ,  48  or of play in the control mechanism  38 . 
     FIG. 6  shows a cooking appliance according to a second exemplary embodiment of the present invention. The cooking appliance has a useful space module  83 , which is indicated by a chain-dotted line and in which the cooking appliance muffle  3  (not illustrated) is disposed. A storage space module  79  is disposed below the useful space module  83 . The storage space module  79  has a storage space  61  in which a guide system  58  for the door  5  is provided. The guide system  58  enables the cooking appliance door  5  (illustrated by dashed lines) to be displaced into the storage space module  79 . According to  FIG. 6 , the storage space module  79  serves as a base or foundation on which the useful space module  83  is mounted. The storage space module  79  is configured as an upwardly open sheet-metal housing. Step-shaped abutment shoulders  85  are formed on the upper edge of the side walls  80  of the sheet-metal housing  79 . The useful space module  83  rests on the contact shoulders  85  in a positionally correct manner, as indicated in  FIG. 6 . The operating and display elements  2 , which are shown in  FIG. 1 , and an associated control unit are provided in the useful space module  83 . The operating and display elements  2 , here, together with the associated control unit, can function independently of the stowage-space module  79 . 
   In contrast to the first exemplary embodiment, the driving movement for the control mechanism  38  is not produced by the conventional door hinge  49  that is shown in  FIG. 4 . On the contrary, the control mechanism  38  of the second exemplary embodiment has, as driving part, a rotary shaft  57 . The rotary shaft  57  is operatively connected to a guide element  59  of the guide system  58 . 
   The construction and the functioning of the guide system  58  for the door  5  and the production of a drive movement for the control mechanism  38  is explained hereinbelow: 
   As illustrated in  FIG. 6 , the guide element  59  is part of the guide system  58 , with the aid of which the door  5  is pushed, during an opening process, into the storage space  61  provided below the cooking space  3 .  FIGS. 6 and 7  reveal that the guide system  58  has slotted-guide tracks  63 . The slotted-guide tracks  63  are formed in the two opposite side walls  80  of the storage space module  79 . The opposite slotted-guide tracks  63  guide sliders  60  of the guide element  59  therein. The sliders  60  are welded to each other through a connecting rod  62 . The guide element  59  is, therefore, guided in the opposite slotted-guide tracks  63  in the manner of a guide carriage. Between the two sliders  60 , adjusting levers  67  are welded to the connecting rod  62 . As illustrated in the enlarged perspective cutout of  FIG. 8 , the adjusting levers  67  are connected in a form-fitting manner to the rotary shaft  57  of the control mechanism  58 . The rotary shaft  57  is indicated in  FIGS. 6 and 7  by chain-dotted lines. 
   The above-mentioned form-fitting connection between the adjusting levers  67  of the guide carriage  59  and the rotary shaft  57  of the door  5  is illustrated in  FIG. 8 . The inner and outer door windows  7 ,  9  of the door  5  have been omitted from  FIG. 8 . Accordingly, the rotary shaft  57  is mounted rotatably in the opposite edge strips  25  of the door  5 . For the form-fitting connection, the adjusting levers  67  of the guide carriage  59  each have a rectangular cutout  69  ( FIG. 8 ). A corresponding, rectangular shape section  71  of the rotary shaft  57  is mounted in the cutout  69 . The lateral edge strips  25  of the door  5  are provided in the outward direction in each case with a U-shaped groove that serves as a guide rail. In these guide rails  25 , respective bearing rollers  65  are guided displaceably on both sides. The bearing rollers  65  are fastened to the side wall  80  of the storage space module  79 . The U-shaped groove, which serves as a guide rail, is constructed on its lower end side with an open end  26 . When the door is removed, as will be described at a later stage in the text, the housing-mounted bearing roller  65  can be released from the associated guide rail  25  by way of the open end  26 . 
   Each of the opposite slotted-guide tracks  63  has a starting section  90  and a slide-in section  91 . According to  FIGS. 9A and 9C , an angle of inclination of the starting section  90  is approximately 45°. The starting section  90 , furthermore, takes up approximately 30% of the entire length of the slotted-guide track  63  while the transition between the starting section  90  and the slide-in section  91  has a curved profile. The slide-in section  91  runs substantially in a horizontal plane. The bearing rollers  65 , which are fixed on the housing, are disposed approximately level with the slide-in section  91  of the slotted-guide track  63 . 
   The course of movement of the guide carriage  59  of the door  5  in the slotted-guide tracks  63  is described with reference to  FIGS. 9A to 9C .  FIG. 9A  shows the door  5  in its closed position. In the closed position, the sliders  60  of the guide carriage  59  are in the starting section  90  of the slotted-guide track  63 . During an opening movement of the door  5  from its closed position shown in  FIG. 10 , the sliders  60  of the guide carriage  59  are initially displaced upward. As a result, the adjusting levers  67  of the guide carriage  59  lift the door  5  upward. With this lifting movement of the door  5 , a lower end side  93  of the door  5 , which side pivots into the storage space  61 , is displaced, at the same time, upward away from a base  117  of the storage space module  79 , as is revealed in  FIG. 9B . As a result, a pivoting region S of the lower end side  93 , which region protrudes into the storage space  61  and is indicated by a chain-dotted line, is reduced. After the guide carriage  59  is moved from the starting section  90  into the horizontal slide-in section  91  ( FIG. 9C ), the door  5  is in a horizontal plane, in which it can be slid into the storage space  61 . During the pivoting movement of the door  5 , a pivoting angle between the door  5  and the guide block  59  changes. Because the rotary shaft  57  of the control mechanism  38  is mounted in a form-fitting manner in the adjusting levers  67  of the guide slide  59 , the change in the pivoting angle between the door  5  and the guide carriage  59  causes a rotation of the rotary shaft  57 . That is to say, during the pivoting movement of the door  5 , the rotary shaft  57  is inevitably rotated by the guide element  59 . 
   The manner in which the control mechanism  38  transmits the inevitable rotation of the rotary shaft  57  to the door handle  17  is explained with reference to  FIG. 10 .  FIG. 10  shows a side sectional view of the upper and lower section of the door  5  according to the second exemplary embodiment. This reveals that the adjusting lever  67  protrudes through an access opening  129  of the door  5  into the interior space  41  of the door and is connected in a form-fitting manner to the rotary shaft  57 . As can be gathered from  FIGS. 8 and 10 , the rotary shaft  57  is configured with a driving drum  54 , which is disposed in a rotationally fixed manner on the rotary shaft  57 . The driving drum  54  is in engagement circumferentially with the tension cable  48 . As in the first exemplary embodiment, the tension cable  48  is connected to the door handle  17 . 
   During the pivoting movement of the door  5 , a pivoting movement, therefore, arises between the guide carriage  59  and the door  5 . As a result, the rotary shaft  57  is rotated inevitably. The rotational movement of the rotary shaft  57  is transmitted through the driving drum  54  to the tension cable  48 . The tension cable  48  converts the rotational movement of the rotary shaft  57  into a rotational movement of the radial cam  47  and subjects the door handle to the second torque M 2  , which is directed counter to the first torque M 1 , on the door handle  17 . The door handle  17 , therefore, retains its horizontal alignment regardless of the pivoting position of the door  5 . 
   In contrast to  FIG. 4  of the first exemplary embodiment, in  FIG. 10 , the first tension cables  43 , which engage on both sides on the radial cams  47  of the pivoting part  16  of the door handle  17 , are not connected to a common tension spring. Rather, according to  FIG. 10 , each of the first tension cables  43  is associated with a dedicated tension spring  39 . The tension spring  39  is fastened at one end of the spring to the edge strip  25  of the door  5 . The other end of the tension spring  39  is coupled to the tension cable  43  through a retaining eyelet  75 . As a result, the door handle  17  is subjected to the first torque M 1  in the counterclockwise direction. 
   The control mechanism  38  shown in  FIG. 10  has a third tension cable  77 . The third tension cable  77  is, on one hand, in circumferential engagement with the driving drum  54  of the rotary shaft  57  and is guided about the driving drum  54  in the opposite direction to the second tension cable  48 . On the other hand, the third tension cable  77  is connected to the retaining eyelet  75  of the first tension cable  43 . The first, second, and third tension cables  43 ,  48 ,  77  of the control mechanism  38  form a closed cable control that envelops the radial cam  47  and the driving drum  54  to transmit the rotational movement to the door handle  17 . 
   To tighten the closed cable control  43 ,  48 ,  77 , a tightening spring  79  is integrated in the third tension cable  77 . The tightening spring  79  serves to tighten the closed cable control  43 ,  48 ,  77 . In addition, the tightening spring  79  increases the torque M 1  that is exerted by the tension spring  39  on the door handle  17 . Therefore, both the tightening spring  79  and the tension spring  39  are present for exerting the torque M 1 . It is, therefore, advantageously possible for use to be made of two comparatively small springs that take up only a small amount of space in the limited inner space  41  of the door. 
   If the operator, for example, during transportation of the cooking appliance  1 , exerts an upwardly directed actuating force F on the door handle  17  shown in  FIG. 4 , the resultant pivoting movement of the pivoting part  16  of the door handle in the clockwise direction is absorbed by the tension spring  39  and by the tightening spring  79 . The resultant pivoting movement of the pivoting part  16  is, therefore, not transmitted from the door handle  17  to the control mechanism  38 . As a result, damage to the control mechanism  38  is prevented. 
   The dimensioning of the spring force of the tension springs  39 ,  79  depend on the minimum value for the spring force, which value is specified in conjunction with  FIG. 4 . 
   Furthermore, the tension cables  43 ,  48 ,  77  can be provided with adjusting elements for adjusting a tensile stressing. By the adjusting elements, the tension cables provided on both sides of the door sides can be acted upon with an identical tensile stress. As a result, a synchronous operation of the two control mechanisms  38  is achieved. 
   A weight-balancing configuration  94  for the door  5  of the second exemplary embodiment is described below with reference to  FIGS. 7 ,  11 , and  12 . During a movement of the door  5 , the weight-balancing configuration  94  exerts a balancing force on the door  5 , which force acts counter to the weight of the door  5 . The weight of the door  5  is, therefore, not absorbed by the operator during a door movement, but, rather, by the weight-balancing configuration  94 . 
     FIG. 7  shows, in a perspective view, the storage space module  79 , of which a space divider  111  (described later on) is illustrated separately. On each of the opposite side walls  80 , the weight-balancing configuration  94  has a pivoting lever  95 . The pivoting lever  95  is mounted pivotally on the opposite side walls  80  through a lever spindle  97 .  FIG. 11  shows one of the side walls  80  in an enlarged side elevational view along the line D—D from  FIG. 7 . Accordingly, the pivoting lever  95  protrudes into the starting section  90  of the slotted-guide track  63  and is in engagement with the slider  60  of the guide carriage  59 . A pivoting region of the pivoting lever  95  is configured such that the pivoting lever  95  is in engagement with the slider  60  of the guide carriage  59  only in the region of the starting section  90 . By contrast, in the horizontal section  91 , the pivoting lever  95  is disengaged from the slider  60  of the guide carriage  59 . The pivoting lever  95  is connected to a tension spring  103 . The tension spring  103  is fastened to the side wall  80 . In  FIG. 11 , the tension spring  103  pre-stresses the pivoting lever  95  in the counter-clockwise direction. 
   When the door  5 , which is illustrated by dashed lines in  FIG. 11 , is pivoted from its closed position downward into the horizontal position, the slider  60  runs from the starting section  90  into the horizontal section  91  of the slotted-guide track  63 . During this movement, the slider  60  of the guide slide  59  presses against the spring-pre-stressed pivoting lever  95 . The pivoting lever  95 , therefore, subjects the sliding component  60  to a balancing force. The balancing force acts counter to the weight of the door  5 . 
   As illustrated in  FIG. 11 , the pivoting lever  95  is pressed by the spring  103  against a first end stop  99 , which is formed by a rubber support. In the position shown in  FIG. 11 , the pivoting lever  95  permits an initial movement of the slider  60  of the guide carriage  59  out of the closed position of the door  5 . During this initial movement, the slider  60  does not engage with the pivoting lever  95 . According to  FIG. 11 , the slider  60  comes into contact with the pivoting lever  95  only at a pivoting angle of the door  5  of approximately 20°. This simplifies the initial movement of the door  5  out of its closed position for the operator. Moreover, the pre-stressed pivoting lever  95  according to  FIG. 11  acts as a stop against which the slider  60  of the guide carriage  59  strikes during the opening movement of the door  5 . A certain pivoting position of the door  5  is, thus, signaled to the user. In the present case, this pivoting position corresponds to a removal position (described later on), in which a simple removal of the door  5  from the guide system  58  is made possible. 
   Furthermore, the weight-compensating configuration  94  has a pivotally mounted retaining element  105  that is pre-stressed by a spring  106 . During the previously described initial movement of the door  5 , the spring-pre-stressed retaining element  105  presses the slider  60  of the guide carriage  59  in the direction of the pivoting lever  95 . As a result, the door  5  is retained stably in the removal position shown in  FIG. 11 . 
     FIG. 12  shows the door  5  mounted horizontally and slid into the storage space  61 . The slider  60  of the guide carriage  59  of the door  5  is in the horizontal slide-in section  91  of the slotted-guide track  63 . During the movement of the slider  60  in the region of the slide-in section  91  of the slotted-guide track  63 , the pivoting lever  95  is disengaged from the slider  60 . The pivoting lever  95 , therefore, does not exert any balancing force on the door  5 . While the slider  60  runs in the slide-in section  91  of the slotted-guide track  63 , the pivoting lever  95  is in the clockwise direction, by the spring  103 , against a second end stop  101 , which is, likewise, formed by a rubber support. 
   The pivoting lever  95  has a driver  107 . The driver  107  of the pivoting lever  95  protrudes, in  FIG. 12 , into the slotted-guide track  63 . According to  FIG. 12 , the slider  60  has been displaced from the starting section  90  into the slide-in section  91  of the slotted-guide track  63 . The adjusting lever  95  is pre-stressed against the second end stop  101  and is in a holding position. When the door  5  is displaced out of the storage space  61 , the slider  60  comes into engagement with the driver  107  of the pivoting lever  95 . As a result, the pivoting lever  95  is brought out of its holding position and comes, once again, into a pressure contact with the slider  60  of the guide carriage  59 . As a result, the pivoting lever  95  can, once again, exert the compensating force on the guide carriage  59  during a pivoting movement of the door  5 . 
   The releasable mounting of the door  5  on the guide system  58  is explained below with reference to  FIG. 8 . Due to the releasable mounting of the door  5  in the guide system  58 , the door  5  can easily be removed for cleaning. As already described with reference to  FIG. 8 , the adjusting levers  67  have a rectangular cutout  69 . The corresponding rectangular shape section  71  of the rotary shaft  57  is mounted in the rectangular cutout  69 . This produces a form-fitting connection between the guide carriage  59  and the rotary shaft  57 . A locking element  73  that, according to  FIGS. 8 and 13 , is mounted on the rotary shaft  57  is explained below. The locking element  73  can be displaced between a locking position and a release position. In the release position, the locking element  73  releases the mounting of the rotary shaft  57  in the adjusting lever  67 . In a locking position of the locking element  73 , the rotary shaft  57  is connected non-releasably to the adjusting lever  67 . 
   According to  FIG. 8 , the catch element  73  has a bearing sleeve that is mounted such that it can be displaced in the axial direction of the rotary shaft  57 . A protrusion  76  is formed on one end side of the bearing sleeve. The protrusion  76  projects, in  FIG. 8 , in the direction of a cutout  78  provided in the actuating lever  67 . In the release position shown in  FIG. 8 , the protrusion  76  of the catch element  73  does not engage with the cutout  78  of the actuating lever  67 . Raising the door  5  in an arrow direction Z, thus allows the rotary shaft  57  to be released from the guide carriage  59 . 
   According to  FIG. 13 , the bearing sleeve of the catch element  73  has a guide pin  82 . The guide pin  82  is guided between the locking position and the release position in a corresponding longitudinal groove  84  of the rotary shaft  57 . The configuration ensures that the protrusion  76  of the catch element  73  can be pushed in a precisely positioned manner into the cutout  78  of the actuating lever  67 . In addition, the bearing sleeve is formed with a latching protrusion  86 . The latching protrusion  86  latches into corresponding cutouts of the rotary shaft  57  both in the release position and the locking position. The catch element  73  is, thus, secured in the locking position and release position. Accidental displacement of the catch element  73  is prevented in such a configuration. 
   As has already been described with reference to  FIG. 11 , the door  5  is kept stable in the removal position between the retaining element  105  and the actuating lever  95  over a pivoting angle of approximately 20° following its closed position. In this removal position, the rectangular cutout  69  of the actuating lever  67  is open in the vertically upward direction. The door  5  can, thus, be raised vertically upward in an ergonomically favorable manner for removal purposes without any skewing occurring between the shaped portion  71  of the rotary shaft  57  and the rectangular cutout  69  of the actuating lever  67 . At the same time, when the door  5  is removed, the housing-mounted bearing rollers  65  can readily be guided through the open ends  26  of the lateral guide rails  25  of the door  5 . 
   With the door  5  removed, the rotary shaft  57 , rather than being positively guided by the guide carriage  59 , can be rotated freely. On account of the freely rotatable rotary shaft  57 , the tension spring  79  shown in  FIG. 10  no longer has any effect on the magnitude of the torque M 1  by which the door  5  is pressed against the first stop  35 . With the door  5  removed, the magnitude of the torque M 1  is, thus, determined solely by the spring force to which the pulling cable  43  is subjected by the tension spring  39 . 
   The space divider  111  that is mentioned in conjunction with  FIG. 7  is explained in the following text. As emerges, in particular, from  FIG. 6 , the space divider  111  is disposed in the storage space module  79 . The space divider  111  divides the storage space  61  into a first storage space  61   a  and a second storage space  61   b . The space divider  111  has a horizontal intermediate base  113  and side walls  115 . The door  5  can be displaced into the first storage space  61   a . The space divider  111  also separates the guide system  58 , which is formed from the slotted-guide track  62  and guide carriage  59 , and the weight-balancing configuration  94  from the second storage space  61   b . Baking sheets or other accessories may be stored in the second storage space  61   b.    
   As emerges from  FIGS. 9A to 9C , the space divider  111  is disposed below the starting section  90  and the slide-in section  91  of the slotted-guide track  63 . The intermediate base  113  together with the side walls  115  and a housing base  117  form an access opening  119 . The latter is disposed spaced apart from the pivoting region S (indicated by a chain-dotted line) of the lower end side  93  of the door  5 . Display elements  121  ( FIGS. 7 and 8 ) are provided in the region of the access opening  119  of the second storage space  61   b . The display elements  121  are configured as cams or protuberances that are fastened to the base  117  of the storage space  61 . The display elements  121  indicate to the operator a maximum permissible length for objects that can be stored in the second storage space  61   b  without protruding into the pivoting region S of the lower end side  93  of the door  5 . Appliance front-side panels  123  are formed on the side walls  115  of the space divider  111  ( FIG. 7 ). The panels  123  serve for concealing the first storage space  61   a  from view. In addition, a collecting or drip channel  125  is provided in the housing base  117 , in the region of the appliance front-side access opening  119 , to keep the second storage space  61   b  free from contaminants, for example, dripping condensation water. 
     FIGS. 14A to 14C  illustrate schematic views of different variants of the household appliance according to the invention. 
     FIG. 14A  shows the working-space module  83  and the stowage-space module  79  separately from one another. The construction and the functioning of the two modules  79 ,  83  corresponds to that of the preceding figures. The stowage-space module  79  and the working-space module  83 , in the first instance, are produced independently of one another as separate structure units. The stowage-space module  79  and the working-space module  83  are, then, joined together in an assembly step to form the household appliance. According to  FIG. 14A , the stowage-space module  79  serves as a pedestal on which the working-space module  83  is positioned in the direction of the arrows in  FIG. 14A . 
   In contrast to  FIG. 14A , the stowage-space module  79  in  FIG. 14B  is disposed above the working-space module  83 . The door  5  can, thus, be displaced upward into the stowage space  61  of the stowage-space module  79 . In  FIG. 14C , the stowage-space module  79  is disposed on edge. The on-edge stowage-space module  79  is fastened, according to  FIG. 14C , on one side of the working-space module  83 . The door  5  can, thus, be displaced into the stowage space  79  disposed laterally on the working-space module  83 . 
     FIG. 15  gives a perspective illustration of part of an underside of the door  5 . Accordingly, a sheet-metal element  127  is adhesively bonded to the inner door panel  7 . Part of the inside of the door  5 , which is directed toward the cooking space  3 , is, thus, formed by the sheet-metal element  127 . The sheet-metal element  127  has an extension portion that extends the inner door panel  7  to the bottom end side  93  of the door  5 . Furthermore, the sheet-metal element  127  is bent at right angles to form the bottom end side  93  of the door  5 . An abutment surface  134  is formed at the end of the bent part of the sheet-metal element  127 . The distance between the outer door panel  9  and the inner door panel  7  is defined by the abutment surface  134 . 
   Furthermore, a through-passage opening  129  is formed in the extension portion of the sheet-metal element  127 . Projecting through the through-passage opening  129  is the actuating lever  67  of the guide carriage  59 , which engages with the rotary shaft  57  disposed in the door interior  41  ( FIG. 8 ). As an alternative, the hinge part  51  of the door hinge  49  of the first exemplary embodiment (illustrated in  FIG. 4 ) can project through the through-passage opening  129 . The through-passage opening  129 , in addition to extending in the plane of the inside of the door, also extends in the plane of the bottom end side  93  of the door  5 . 
   Further installation or operating openings may be provided in the sheet-metal element  127 . For example, according to  FIG. 15 , an operating opening  131  is provided on the bottom end side  93  of the door  5 . The operating opening  131  gives the user access to the catch element  73 , which is disposed in an adjustable manner on the rotary shaft  57 . The catch element  73  can, thus, easily be adjusted between the locking position and the release position. Furthermore, a collecting channel  133 , for collecting dripping condensation liquid, is stamped in the sheet-metal element  127 . If the door  5  is, thus, disposed horizontally in the stowage space  61 , condensation located on the inside of the door collects in the collecting channel  133 . The sheet-metal element  127  additionally has angled carriers  135  that serve for fastening the inner door panel  7  on the border strips  25  of the door. Through the angled carriers  135 , the inner door panel  7  can easily be fastened on the border strips  25  of the door, for example, by a screw connection. 
   Spacers  139  by which the door  5  can be disposed correctly its closed position are described hereinbelow.  FIG. 16  shows the cooking appliance  1  with its door  5  disposed in its closed position. Border strips  137  of the cooking appliance are disposed on both sides of the door  5 . The border strips  137  are spaced apart from the door  5  through a gap  138 .  FIG. 17  shows a view in section along line E—E from  FIG. 16 . It can be seen from this view that spacers  139  are provided between the lateral peripheral edges of the inner door panel  7  and the respectively opposite border strips  137 . The spacers  139  are formed from plastic and are fastened, on the housing side, on the border strips  137 . In the closed position of the door  5 , the spacers  139  define a gap width b between the door  5  and the border strip  137 . For visual reasons, it is preferred if the spacers  139  retain the door  5  in a centered manner between the border strips  137 . 
   The spacer  139  illustrated in  FIG. 18  has a run-on slope  141  and a centering portion  143 . The run-on slope  141  guides the door  5 , during a closing movement, into the closing position, in which the visually favorable gap width b is achieved. The centering portion  143  follows after the run-on slope  141  in the closing direction of the door  5 . In the closed position of the door  5 , the centering portions  143  of the opposite spacers  139  each form lateral stops for the opposite peripheral edges of the inner door panel  7 . As is shown in the enlarged detail from  FIG. 18 , the peripheral edges of the inner door panel  7  are disposed with a small amount of play s of approximately 1 mm between the centering portions  143  of the spacers  139  and the opposite peripheral edge of the inner door panel  7 . 
     FIG. 19  shows a modification of the above-described spacer  139 . Accordingly, the run-on slope  141  is of convexly curved formation and merges into the centering portion  143  without any transition edges. The opposite peripheral edge of the inner door panel  7  is, likewise, rounded. During the closing movement of the door  5  in the direction of the arrow in  FIG. 19 , the door  5  is, thus, positioned particularly smoothly between the centering portions  139 . 
   The spacers  139  make it possible to mount the guide carriage  59  with axial play in the sliding tracks  63 . The axial play ensures smooth-running displacement of the guide carriage  59  in the sliding tracks  63 . On the other hand, the spacers  139  ensure that the door  5 —despite the axial play—is positioned correctly in its closed position. 
   A top portion of the cooking appliance door  5  according to the third exemplary embodiment is indicated schematically in  FIG. 20 . The bearing housing  21  and the door handle  17  mounted therein are configured in accordance with  FIG. 2 . Additionally, a blocking element  151  is secured in the bearing housing  21 . The blocking element  151  can be displaced in the longitudinal direction of the bearing housing  21 .  FIG. 20  shows the blocking element  151  in its blocking position, in which it projects into a corresponding cutout  152  provided in the pivoting part  16  of the door handle  17 . In the blocking position, the blocking element  151  prevents the door handle  17  from pivoting in relation to its bearing housing  21 , that is say, the door handle  17  is rotationally fixed in relation to the bearing housing  21 . If the user, thus, subjects the door handle  17  to an upwardly directed force, for example, during transportation of the cooker, transmission of a pivoting movement from the door handle  17  to the control mechanism  38  and, thus, possible damage to the control mechanism  38  are, therefore, prevented. 
   A fourth exemplary embodiment of the invention is indicated in  FIG. 21  by way of schematic block diagram. Accordingly, the control mechanism  38  transmits a drive movement, in a first arrow direction I, to the cam plate  47  and, further, to the door handle  17 . A freewheel coupling  161  is connected between the cam plate  47  and the door handle  17 . The freewheel coupling  161  allows transmission of movement from the cam plate  47  to the door handle  17  in the first arrow direction I. 
   When the door handle  17  is actuated, the freewheel coupling  161  is subjected to a pivoting movement in a second arrow direction II, counter to the first arrow direction I. During a transmission of pivoting movement from the door handle  17  to the freewheel coupling  161  in the second arrow direction II, the freewheel coupling, nevertheless, allows freewheeling. Transmission of movement from the door handle  17  to the control mechanism  38  is, thus, prevented. Accordingly, the freewheel coupling acts as a safeguarding device for the control mechanism  38  and prevents forces from being introduced into the control mechanism  38  from the door handle  17 .