Hinge for a stove door

Abstract

The invention relates to a hinge for a stove door, comprising a housing (1) in which a plug-in part (2) is rotationally (10) mounted. In order to be able to easily influence the torque produced by the spring, a spring guide (3) which is loaded by a spring (6), preferably a pressure spring, is provided, said spring guide being fitted with roller (15) that is guided through a curved section (9) of the plug-in part (2).

Description

[0001] The invention relates to a hinge for a stove flap, which can also be referred to as a “stove hinge”, according to the preamble to claim 1.

[0002] Such stove hinges are already known in the art. They generally have a casing to which is pivoted a plug-in part. The casing is secured to the stove flap. The plug-in part is inserted into the stove or stove casing, e.g., a side wall, or otherwise fastened there. However, it is also possible to secure the casing to the stove and then plug-in part to the stove flap. The casing can essentially be shaped like a box. The pivot axis can be in a corner of the casing, e.g., in a lower outside corner, in particular at the location of the casing facing away from the segment of the plug-in part extending out of the casing.

[0003] Stove hinges of this kind often have a spring intended to offset the weight of the stove flap. The stove flap is normally pivoted to a horizontal axis on the front side of the stove, wherein the stove flap is situated vertically over the pivot axis in the closed position, and can be pivoted to the outside up to an angle of 90°. During this pivoting process, the opening torque of the stove flap increases in essentially a sinusoidal pattern. The spring of the stove hinge makes it possible to offset this opening torque (door torque) of the stove flap. In addition, the spring can also generate a certain locking force of the stove flap in its closed position.

[0004] The object of the invention is to propose a stove hinge with which torque generated by the spring can be easily influenced.

[0005] According to the invention, this object is achieved by the characterizing features of claim 1. The hinge encompasses a spring guide loaded by a spring. This spring is preferably a torsion or flat spiral spring. The spring guide is provided with a roll guided into a cam plate (pitch cam, guide track) of the plug-in part. However, it is here not absolutely necessary that the roll execute a rolling motion. Instead of an actual roll, use can also be made of another guide element that is rigid in design and can pivot while sliding along the cam plate or guide track. The roll or other guide element can be guided into the camp late or guide track. However, it can also traverse the cam plate or guide track in another manner.

[0006] The cam plate layout can influence the torque exerted by the hinge on the stove flap. This torque depends on the progression and inclination of the guide track, and the achieved rotational angle or opening angle. The initial stress of the spring is controlled over the progression of the guide track. Special settings, lock-in positions and/or closure moments can be achieved via the inclination of the guide track.

[0007] Advantageous further developments are described in the subclaims.

[0008] The spring is preferably designed as a compression spring. A compression spring, in particular a torsion spring, placed under pressure is less susceptible to vibration than a tensioned spring, so that less disturbing noises are generated. However, a tension spring can also be used.

[0009] Another advantageous further development is characterized in that the roll is provided on an outwardly facing bracket of the spring guide. The roll is preferably located outside the hinge casing. As a result, the distance, and hence the lever arm force, between the pivot axis of the hinge and roll can be increased, making it possible to better utilize the force of the spring. Accordingly, it is also possible to use smaller springs and make do with lower spring forces. Lowering the spring force enables weaker and smaller hinges, since the hinge components now just have to absorb lower forces.

[0010] In another advantageous further development, the cam plate has an inclination in the closed position of the hinge that generates the required closing force. Legal regulations stipulate that stove flaps must reach a specific closing force. This closing force can be easily generated via the corresponding inclination of the cam plate.

[0011] Another advantageous further development is characterized in that the cam plate has a neutral section at a certain open position of the hinge. In this case, the opening angle is preferably 200, forming the so-called “grill stop”. However, the angle can also lie between 10° and 30°, and even exceed this in specific instances. The neutral section of the cam plate triggers the “grill stop” of the stove flap at a predetermined opening angle.

[0012] The cam plate is preferably designed in such a way that the spring force generated by the cam plate progression essentially offsets the opening torque or door torque of the stove flap. If the cam plate has an inclination generating the required closing force in the closed position of the hinge, and/or if the cam plate has a neutral section at a certain open position of the hinge, the mentioned advantageous further development can be designed in such a way that the spring force generated by the cam plate progression essentially offsets the opening torque of the stove flap in those areas lying outside the closed position and/or specific open position.

[0013] The spring guide is preferably guided in the casing. This guiding mechanism is preferably achieved using a support, wherein the support preferably consists of plastic or some other suitable material.

[0014] Another advantageous further development is characterized in that the lever arm force of the roll can be varied relative to the pivot axis of the plug-in part. It is advantageous for the spring guide to have a guide pin that extends into another cam plate of the casing. However, it is also possible to provide the guide pin in the casing and the additional cam plate in the spring guide. Changing the length of the lever arm force between the roll and pivot axis that can be generated by moving the spring guide relative to the casing makes it possible to additionally influence the torque exerted by the hinge on the stove flap. The spring guide can be moved via the other cam plate (pitch cam, guide track), so that the lever arm of force of the acting spring force can be varied relative to the fulcrum of the plug-in part. The torque is controlled by superposing the effects of the cam plate of the plug-in part and additional camp plate. This makes it possible to expand the range of influence on the torque. Further, the physical size of the hinge can be reduced.

[0015] The initial stress of the springs can be variable. It is advantageous that a stop be adjustable for the springs. This stop can be designed as a nut, or encompass a nut, so that turning it can produce a change in the initial spring stress. The arrangement is preferably such that the nut or other component can be adjusted by hand to vary the initial spring stress. The hinge can be adjusted to various stove flaps by changing the initial spring stress.

[0016] Another advantageous further development is characterized in that a locking part is connected with the plug-in part. The locking part is preferably pivoted. It is advantageous for the pivot axis of the locking part to be shiftable. The locking part can have a wedge. The locking part preferably has an actuating projection.

[0017] In another advantageous further development, the locking part has a face that forms a stop surface. As a result, a reliable locking effect can be achieved even if the dimensions of the locking part and/or parts interacting with it deviate from the prescribed values due to manufacturing tolerances and/or wear.

[0018] It is advantageous if the distance between the face and pivot axis of the locking part widens as the locking part increasingly swivels out. In this way, the locking effect will be sufficient even when if distance between the pivot axis and the part interacting with the face of the locking part, e.g., a corner of the counter-bearing, should be greater than prescribed due to manufacturing tolerances, and or become greater over time due to instances of wear.

[0019] The face is preferably curved. In an advantageous further development, the face has a contour shaped like a circular arc, or at least essentially shaped like a circular arc, wherein the midpoint of the circular arc is spaced apart from the pivot axis of the locking part. As a result, the distance between the face and pivot axis of the locking part can widen as the locking part increasingly swivels out.

[0020] The invention also relates to a stove flap and/or a stove. In previously known stove flaps, it is often necessary to use two hinges. If the stove flap needs a counterweight, each of the hinges in previously known solutions must have a counterweight comprising a relatively strongly dimensioned spring.

[0021] Another object of the invention is to propose a simplified stove flap.

[0022] According to the invention, this object is achieved by a hinge according to the invention and a dummy flange with a casing to which a plug-in part is pivoted. The hinge according to the invention makes it possible to completely implement the counterweight. The arrangement can be such that the entire counterweight for the stove flap is achieved using a hinge according to the invention. A counterweight is then no longer required for the second hinge of the stove flap. Accordingly, the second hinge of the stove flap requires no hinge according to the invention, but rather only a simplified hinge, or a “dummy hinge”, which comprises a casing to which a plug-in part is pivoted. The second hinge, or dummy hinge, requires no spring-loaded spring guide provided with a roll guided through a cam plate of the plug-in part. This results in a simplification and cost savings.

[0023] It is advantageous if the dummy hinge comprises a spring, in particular a leg spring, which is mounted on the casing and on the plug-in part. This spring can be used to generate a closing torque. This is advantageous particularly when the dummy hinge has a locking device. In this case, the spring or leg spring can generate a small closing torque to maintain the function of the locking device.

[0024] It is advantageous if the dummy hinge has one or more features of the locking device. Accordingly, the plug-in part of the dummy hinge preferably has connected to it a locking part, preferably pivoting, wherein the pivot axis of the locking part is preferably shiftable. The locking part of the dummy hinge can have a wedge. It can also have an actuating projection. It is advantageous if the locking part of the dummy hinge has a face forming a stop surface, wherein the distance between the face and the pivot axis of the locking part preferably widens as the locking part increasingly swivels out. The face is preferably curved.

[0025] The face can have a contour shaped like a circular arc, or essentially shaped like a circular arc, wherein the midpoint of the circular arc is spaced apart from the pivot axis of the locking part.

[0026] Embodiments of the invention will be explained in detail below based on the attached drawing. The drawing shows:

[0027] FIG. 1 the hinge in the closed position, rear view,

[0028] FIG. 2 the hinge according to FIG. 1 in the closed position, side view,

[0029] FIG. 3 the hinge according to FIG. 1 and FIG. 2 in the open position, at an opening angle of about 45°, side view,

[0030] FIG. 4 the hinge according to FIGS. 1-3 in the open position, at an opening angle of essentially 90°, side view,

[0031] FIG. 5 the hinge according to FIGS. 1-4 in the closed position, top view,

[0032] FIG. 6 the progression of torque as a function of the opening angle of the hinge,

[0033] FIG. 7 a modification of the hinge with a locking part in the locked position,

[0034] FIG. 8 the hinge according to FIG. 7 in a partially open position,

[0035] FIG. 9 the hinge according to FIG. 7 and 8 in the locked position,

[0036] FIG. 10 a modification of the hinge shown on FIGS. 7 to 9 with a locking part, which has a face forming a stop surface, in a latched position with partially opened stove flap,

[0037] FIG. 11 the hinge according to FIG. 10 in a partially open position,

[0038] FIG. 12 the hinge according to FIGS. 10 and 11 in the locked position,

[0039] FIG. 13 a section from FIG. 10, magnified view,

[0040] FIG. 14 a dummy hinge in the closed position, rear view,

[0041] FIG. 15 the dummy hinge according to FIG. 14 in the open position, side view, and

[0042] FIG. 16 the dummy hinge according to FIGS. 14 and 15 in the closed position, side view.

[0043] The casing 1 of the hinge, which can also be referred to as the hinge body, can be built into the stove doors. However, a reverse arrangement could also be selected, in which the casing 1 of the hinge is built into the stove or otherwise attached to the stove (not shown in the drawings). A plug-in part 2 is secured to the casing 1 so that it can pivot around an axis 10. The connection to the stove is made via plug-in part 2, which is latched or otherwise secured to the stove. The pivot axis 10 is situated in the rear lower part of the casing 1, on the side of the casing 1 facing away from the plug-in part 2. The plug-in part 2 extends out of the casing 1.

[0044] A spring guide 3 is incorporated in the casing 1. The spring guide 3 encompasses a guide rod 11 that extends upwardly out of the casing 1, and has a stop 12 at its upped end. A compression spring 6 is tensioned between this stop 12 and a plastic support 5. The stop 12 can be designed as a nut (not shown in drawing), which can be turned on a thread provided at the upper end of the guide rod 11 (also not shown in drawing), thereby making it possible to change the pre-stress of the compression spring 6. In this case, the stop 12 designed as a nut can be adjusted using a tool, e.g., a screwdriver, a wrench or an Imbus wrench. The nut can also be designed as a wing nut or other hand-manipulated nut.

[0045] The plastic support 5 lies on the upper sealing surface of the casing 1. It has a downwardly pointing part (not shown in drawing), which lies in a corresponding recess in the upper end surface 13 of the casing, and through which the guide rod 11 of the spring guide 3 is routed.

[0046] The lower end of the spring guide 3 has an outwardly pointing bracket 14, having secured to it a pin 7, around which a roll 15 is pivoted.

[0047] In addition, a guide pin 8 is incorporated, in particular pressed, into the spring guide 3, and guided in an additional cam plate 4 provided in the casing 1. It is advantageous if the pin 8 lies deeper, i.e., closer to the roll 15, than shown on the drawing, since the torque acting on the spring guide 3 then becomes smaller. The lever arm force h between the axis 10 and roll 15 takes place over the progression of the additional cam plate 4. The additional cam plate 4 is shaped like a longitudinal slit, which runs straight and parallel to the direction of movement of the spring guide 3 in the upper, longer area, and bends to the left, i.e., away from the roll 15, in the lower end area in the manner evident from FIGS. 2 to 4. As a result, the lever arm force h diminishes to the completely open position shown on FIG. 4.

[0048] The plug-in part 2 accommodates a cam plate 9 through which the roll 15 reaches, and in which this roll 15 is guided.

[0049] The beginning of the cam plate 9, i.e., the point where the roll 15 is located, has an initial section 16 with a certain inclination when the hinge assumes the closed position shown on FIG. 2, which generates a preset closing force.

[0050] This initial section 16 is followed by a convex section, which can be referred to as a cam 17. Provided on the side of the cam 17 facing away from the initial section 16 is a neutral section 18, which lies at a point on the cam plate 9 corresponding to an opening angle of about 20°. If the roll 15 lies in the area of the neutral section 18, the stove flap is in a stable position in which the opening torque (door torque) of the stove flap is essentially exactly as high as the counter-torque generated by the compression spring 6. In this position, the stove flap is in the so-called grill stop.

[0051] The ensuing area 19 of the cam plate 9 is designed in such a way that the spring force generated over this section 19 essentially offsets the opening torque of the stove flap.

[0052] This will be explained below based on FIG. 6. Recorded there on the horizontal axis is the opening angle of the hinge, starting with the opening angle 0° (closed position; FIG. 2) to the opening angle 90° (completely open position; FIG. 4). The torque is recorded in Nm on the vertical axis.

[0053] The bracket 20 represents the progression of the torque generated by a stove flap with a weight of about 10 kg. This torque increases in a sinusoidal pattern. It reaches its highest value at a full opening angle of 90°.

[0054] The cam plate 21 shows the progression of the torque generated by the hinge when opening the hinge. This torque has a maximum of somewhat more than 7.5 Nm at the outset of the opening process at an opening angle of about 5°. The very steep progression of the hinge torque up to this maximum is generated by the inclination of the initial section 16 of the cam plate 9.

[0055] In the ensuing area, the hinge torque drops of considerably. It reaches the cam plate 20 in the area of about 17°. If the stove flap is opened further, the torque of the hinge generated by the spring force presented in the cam plate 21 essentially corresponds to the opening torque of the stove flap presented in the cam plate 20. This can be achieved by appropriately shaping the section 19 of the cam plate 9.

[0056] When closing the stove flap, the torque generated by the hinge passes through the cam plate 22, which lies deeper than the cam plate 21 due to the hinge hysteresis. The cam plate 22 drops below the cam plate 20 at about 18°, decreases to approximately 0 Nm and again exceeds the cam plate 20 at about 13°. The 18° to 13° range corresponds to the grill stop, which assumes a stable position at the minimum of the curve 22 i.e., at about 17°.

[0057] As an option, changing the control cam plates 21, 22 also makes it possible to influence the stove flap in such a way that it drops softly after opened at a specific angle, e.g., 60°. In this case, the cam plate 21 intersects the cam plate 20 at this angle, e.g., 60°, and runs under the cam plate 20 at larger angles.

[0058] By appropriately dimensioning the hinge, cam plates 21 and 22 can be made to run at essentially the same distance on either side of the cam plate 20, as shown on FIG. 6. In a corresponding manner, divergent hinge dimensions make it possible to lower or lift cam plates 21 and 22, if needed.

[0059] Provided on the side of the plug-in part 2 in the lower part of the casing 1 is a recess 24, which is interspersed by the plug-in part 2 and the bracket 14 of the spring guide 3. As a result, the roll 15 provided on the bracket 14 is located outside the casing 1. This makes it possible to achieve a great distance, and hence high lever arm force h, between the axis 10 and the roll 15. As a result of this high lever arm force, the compression spring 6 can be dimensioned relatively weakly.

[0060] The force of the compression spring 6 is transmitted to the roll 15 via the spring guide 3. The roll 15 runs in the cam plate 9 of the plug-in part 2. The shape of the cam plate 9 enables an adjustment to the door torque in each open position. The neutral section 18 adjacent to the cam 17 permits an intermediate stop during the opening process or closing process (“grill stop”).

[0061] The hinge is also suitable for stoves with very heavy doors. In particular in stoves with a device for pyrolysis cleaning, the doors or flaps are relatively heavy. They reach a weight of up to 14 kg.

[0062] The invention provides a hinge that makes do with a low number of components. The hinge characteristics can be freely selected via the shape of the cam plate 9. The torque can be offset in any open position of the door or stove flap. In particular, the arrangement can be such that the torque generated by the spring is essentially exactly as high as the torque opening the door or flap. The hinge according to the invention has a small structure. Because a compression spring less susceptible to vibration than a tension spring is used, no disturbing noises are produced.

[0063] The support or plastic support 5 further dampens vibrations and noise.

[0064] The spring pre-stress can be variable. Since the spring force is relatively low, the spring pre-stress can be adjusted by hand. As a result, a hinge can be used for different stoves. The hinge is adaptable to various stoves, or adjustable for different stoves.

[0065] FIGS. 7 to 9 show a variation of the hinge, in which the additional cam plate 4′ lies deeper, i.e., closer to the roll 15, than in the form of execution according to FIGS. 1 to 5. In addition, the additional cam plate 4′ is curved throughout in such a way that the lever arm force h decreases as the hinge increasingly opens. The additional cam plate 4′ is curved in a way that the extent of the decrease in the lever arm force h becomes larger as the hinge increasingly opens.

[0066] For purposes of simplifying the drawing, FIGS. 7 and 9 do not show the spring guide 3. Parts corresponding to those in the form of execution according to FIGS. 1 to 5 are marked with the same reference numbers.

[0067] In the variation according to FIGS. 7 to 9, a locking part 25 is connected with the plug-in part 2. The locking part has a pivot axis 26 that is mounted in a guide 27 of the plug-in part 2 so that it can pivot and slide longitudinally. The locking part 25 can be pivoted around the pivot axis 26. The pivot axis 26 can be shifted in the guide 27. The guide 27 is essentially straight.

[0068] The end of the locking part 25 lying opposite the pivot axis 26 has a wedge 28, which is formed by the lower contour 29 essentially shaped like a circular arc and the upper contour 30 also shaped essentially like a circular arc, and which narrows proceeding away from the pivot axis 26. An upwardly pointing actuating projection 31 is also provided on the locking part 25 between the pivot axis 26 and the wedge 28.

[0069] The casing 1 of the hinge is connected with the stove flap. The plug-in part 2 is hung into a counter-bearing 32, which is secured to the stove. The counter-bearing 32 has brackets 33 into which an extension 34 of the plug-in part 2 engages. In addition, the counter-bearing 32 has a bracket 35, on which the rounded outer end 36 of the plug-in part 2 sits. As a result of the interaction between the brackets 33 with the extension 34 and bracket 35 with the end 36, the plug-in part 2 and hinge casing 1 connected thereto along with the stove flap connected thereto are reliably held in the position shown on FIG. 7 to 9 by the dead weight of the stove flap. However, it is possible to move the plug-in part 2 out of the brackets 33 and 35, namely by pivoting the plug-in part 2 relative to the counter-bearing 32 in the clockwise direction. During this movement, the extension 34 is moved out downwardly out of the area between the brackets 33, while the rounded outer end 36 moves by the bracket 35.

[0070] FIG. 7 shows the latched position of the hinge. The plug-in part 2 provides a recessed support surface 37, whose contour corresponds to the bottom surface 29 of the locking part 25. In the latched position, the lower surface 29 of the locking part 25 sits on the support surface 37. The upper surface 30 of the locking part 25 lies on the corner 38 of the counter-bearing 32. The wedge 28 of the locking part 25 formed by the surfaces 29, 30 is clamped between the support surface 37 and the corner 38. The pivot axis 26 of the locking part 25 lies in the central area of the guide 27, somewhat outside the middle in the direction away from the axis 10, as shown on FIG. 7. In this position, the wedge 28 of the locking part 25 prevents the stove flap from lifting out. To lift out the stove flap, the casing 1 of the hinge would have to be turned counterclockwise, which is prevented by the wedge 28 between the support surface 37 and the corner 38. The wedge 28 brings about an automatic interlock, which prevents the stove flap from lifting out. The wedge 28 cannot work itself loose. This precludes operator errors, which otherwise could result in the stove flap being inadvertently unhinged if lifted in a closed position.

[0071] However, it is possible to open the stove flap, i.e., pivot the casing 1 around the axis 10. After a slight pivot, the partially open position shown on FIG. 8 is reached. If the stove flap is to be unhinged, the stove flap is opened further until an opening angle somewhat larger than indicated on FIG. 9 is reached. In this open position, the locking part 25 is pivoted counterclockwise around the pivot axis 26 until it reaches the position shown on FIG. 9. In this position, the locking part 25 extends through the slit 24 into the casing 1 of the hinge. The latching lug 31 faces the axis 10. The stove flap is subsequently pivoted along with the casing 1 somewhat toward the closed position, until the locked position shown on FIG. 9 is reached. The outside end surface of the locking part 25 lies on the edge 39 bordering the slit 24 from above. This prevents a further closing of the hinge, i.e., a further pivot of the hinge clockwise around the axis 10. If the stove flap is lifted in this locked positions the plug-in part 2 is unhinged. The extension 34 of the plug-in part 2 slides downward out of the brackets 33, and the stove flap can be removed.

[0072] It can then be hung in again in a reverse movement. To release the locking mechanism of the locking part 25, the stove flap is opened a bit more by pivoting the casing 1 out of the locked position shown on FIG. 9 counterclockwise around the axis 10. In this position, the locking part 25 can be pivoted clockwise around the pivot axis 26. The locking mechanism is released as a result, and the stove flap can be closed, i.e., the casing 1 can be further pivoted clockwise around the axis 10. When closing the stove flap, the closed are 40 of the casing 1 lying over the upper edge 39 of the slit 24 engages. The actuating projection 31 abuts this closed area 40 above the edge 39, and is reliably brought by it into the latched position shown on FIG. 7 and kept there.

[0073] FIGS. 10 to 13 show a variation of the hinge depicted on FIGS. 7 to 9, in which the corresponding parts are provided with the same reference numbers. In the form of execution according to FIGS. 10 to 13, the locking part 25′ has a face 41 that forms a stop surface. The pivot axis 26′ of the locking part 25′ is not shiftable, but rather fixed. The cam plate 9 and additional cam plate 4 or 4′ are present in the form of execution according to FIGS. 10 to 13, but not shown in order to simplify the drawing, with the same holding true for brackets 33 and 35.

[0074] In the latched position according to FIG. 10, the face 41 of the locking part 25 abuts the stop edge 38 of the counter-bearing 32. This is shown on FIG. 13 on a magnified scale. The distance between the face 41 and the midpoint M of the pivot axis 26′ rises as the locking part 25 increasingly pivots clockwise, i.e., toward the latched position. This is achieved by having the midpoint of the bending radius r of the face 41 lie above, i.e., on the side of the midpoint M of the pivot axis 26′ of the locking part 25′ facing away from the axis 10. The midpoint m of the bending radius r is upwardly shifted by measure a relative to the midpoint M. As a result, the circular arc 42 formed by the radius r around the midpoint m, on which the face 41 lies, runs over the circular arc 44 in the area over the intersecting point 43 between this circular arc 42 and the circular arc 44 formed by the radius R around the midpoint M. The radius R corresponds to the distance between the corner 38 forming a stop edge and the midpoint M of the pivot axis 26′ of the locking part 25′.

[0075] The locking part 25′ drops down under its own dead weight while turning around the pivot axis 26′, until its curved face 41 stops against the upper outside horizontal edge of the counter-bearing window 45, i.e., against corner 38, thereby latching the connection between the plug-in part 2 and counter-bearing 32. Upwardly shifting the radius midpoint m of the face 41 from the rotational point M of the pivot axis 26′ of the locking part 25′ by measure a determines the permissible tolerance X in a horizontal direction and Y in a vertical direction. In this case, care must be taken not to exceed a value depending on the friction of the paired materials to uphold the principle of self-locking.

[0076] FIG. 12 shows the locked position, in which the face 41 abuts the edge 39. FIG. 11 shows the intermediate position.

[0077] FIGS. 14 to 16 show a dummy hinge 46 that can be used along with a hinge according to the invention, e.g., based on one of the forms of execution shown on FIGS. 1 to 13, for a stove flap. The hinge according to the invention is dimensioned in such a way that it can absorb the forces necessary for providing a counterweight. The invention makes this possible. The second hinge of the stove flap can then be formed by the dummy hinge shown on FIGS. 14 to 16, in which a counterweight is not provided. In particular, the dummy hinge according to FIGS. 14 to 16 lacks a spring-loaded spring guide provided with a roll guided through a cap plate of the plug-in part.

[0078] This gives the dummy hinge a considerably simpler design. Parts corresponding with those in the forms of execution on FIGS. 1 to 13 are provided with the same reference numbers. The dummy hinge 46 encompasses a casing 1, in which a plug-in part 2 is pivoted around an axis 10, and a leg spring 47, which generates a small closing torque to maintain the function of the lock formed by a locking part 25′ and the other components of the form of execution shown on FIGS. 10 to 13. The leg spring 47 is mounted on the casing 1 and plug-in part 2. It is mounted with one end in the-casing 2, winds round the bolt of the axis 10 several times, and then proceeds with its other end to a stop bolt 48 provided on the plug-in part 2, which it encompasses with its other end.

[0079] The dummy hinge 46 can be used in combination with a spring hinge according to the invention, e.g., according to one of the forms of execution on FIGS. 1 to 13, to save on costs. It functions as a rotational axis, and generates no torque during opening to counterbalance the door weight. The dummy hinge 46 requires neither a compression spring nor a mechanism for conveying the forces. This makes it less expensive to manufacture.

[0080] The invention and its advantageous further developments enable the provision of a hinge according to the principle of dual-acting, simple or overlapped control cam plates. The progression of the cam plate 9 brings about a stronger or weaker pre-stress on the spring 6, so that the hinge torque can be controlled over the progression of the opening angle. The cam plate 9 can further be dual-acting, in such a way that increasing the cam plate progression can generate a rising resistance or additional torque, thereby making it possible in particular to increase the closure moment during the closing process or create latching points. The additional cam plate 4 offers another way to influence the torque progression over the opening area of the stove flap by changing the lever arm force h of the attacking force relative to fulcrum 10. In particular, overlapping the two cam plate controllers 9 and 4 makes it possible to expand the range of torque influence, so that the size of the hinge can be considerably reduced. The interplay between the two cam plates 9 and 4 allows one to achieve nearly any desired hinge characteristics. In particular, the additional cam plate 4 permits a decrease in the effective lever arm force h shortly before the end stop. The arrangement can be such that the torque growing over the opening movement again tapers off. The stove flap can be made to open by itself starting at a desired opening angle.

Claims

1. A hinge for a stove flap with a casing (1), to which is pivoted (10) a plug-in part (2),

characterized by

a spring guide (3) loaded by a spring (6) and provided with a roll (15), which is guided through a cam plate (9) of the plug-in part (2).

2. The hinge according to claim 1, characterized in that the spring (6) is a compression spring.

3. The hinge according to claim 1 or 2, characterized in that the roll (15) is provided on an outwardly pointing bracket (14) of the spring guide (3).

4. The hinge according to one of the preceding claims, characterized in that the cam plate (9) has the inclination (16) that generates the required closing force in the closed position of the hinge.

5. The hinge according to one of the preceding claims, characterized in that the cam plate (9) has a neutral section (18) with the hinge opened a specific distance, e.g., about 20°.

6. The hinge according to one of the preceding claims, characterized in that the cam plate (9) is designed in such a way that the spring force generated by the cam plate progression essentially offsets the opening torque of the stove flap.

7. The hinge according to one of the preceding claims, characterized in that the spring guide (3) is routed into the casing (1).

8. The hinge according to claim 7, characterized in that the spring guide is routed into the casing (1) via a support (5), preferably a plastic support.

9. The hinge according to one of the preceding claims, characterized in that the lever arm force (h) of the roll (15) can be varied relative to the pivot axis (10) of the plug-in part (2).

10. The hinge according to one of the preceding claims, characterized in that the spring guide (3) has a guide pin (8) routed in an additional cam plate (4) of the casing (1).

11. The hinge according to one of the preceding claims, characterized in that the pre-stress of the spring (6) can be varied.

12. The hinge according to one of the preceding claims, characterized in that a stop (12) for the spring (6) can be adjusted, preferably by means of a nut.

13. The hinge according to one of the preceding claims, characterized in that a locking part (25) is connected with the plug-in part (2).

14. The hinge according to claim 13, characterized in that the locking part (25) can be pivoted (26).

15. The hinge according to claim 14, characterized in that the pivot axis (26) of the locking part (25) is shiftable (27).

16. The hinge according to one of claims 13 to 15, characterized in that the locking part (25) has a wedge (28).

17. The hinge according to one of claims 13 to 16, characterized in that the locking part (25) has an actuating projection (31).

18. The hinge according to one of claims 13 to 17, characterized in that the locking part (25′) has a face (41) that forms a stop surface.

19. The hinge according to claim 18, characterized in that the distance between the face (41) and the pivot axis (26′) of the locking part (25′) becomes greater as the locking part (25′) increasingly pivots.

20. The hinge according to claim 18 or 19, characterized in that the face (41) is curved.

21. The hinge according to one of claims 18 to 20, characterized in that the face (41) has a circular arc contour, wherein the midpoint (m) of the circular arc (42) is spaced apart (a) from the midpoint (M) of the pivot axis (26′) of the locking part (25′).

22. A stove flap and/or stove,

characterized by

a hinge according to one of claims 1 to 21 and a dummy hinge (46) with a casing (1), to which a plug-in part (2) is pivoted (10).

23. The stove flap and/or stove according to claim 22, characterized in that the dummy hinge comprises a spring, in particular a leg spring (47), which is mounted to the casing (1) and to the plug-in part (2).

24. The stove flap and/or stove according to claim 22 or 23, characterized in that the dummy hinge (46) comprises the features of one or more of claims 13 to 21.