Door closer

The invention relates to a door closer with a piston guided in a housing, at least one closer spring cooperating with the piston and a hydraulic damping device and with a closer shaft or closer axis connected to the piston via a gear, the gear having at least one pinion gear which is mounted eccentrically ( see FR-A-966 945).

On the door closer known from FR-A-966 945, which has a closer housing hinged to the door, the closer shaft is connected to an eccentrically mounted gearwheel which meshes with an oblique rack on the piston side. With this conventional transmission, a gear ratio adapted to the course of the closing force is obtained due to the differently long lever arms of the gear.

The same applies to the closer known from FR-A-15 10 056, whose housing is fixedly mounted on the door leaf or on the door frame and has a force-transmitting linkage between the door and frame. This known closer has a transmission with two elliptical gears.

In a pneumatic door closer known from US-A-13 59 144 with a crane-transmitting scissor linkage, the closer shaft is connected to a circular eccentrically mounted pinion which meshes with an odd toothed rack on the piston. The pinion used is a conventional circular pinion with regular toothing and a circular pitch curve.

The eccentric bearings make different lever arms effective.

In practice, great attention must be paid to the transmission ratio of the respective closer, i.e. the instantaneous ratio of the rotational angular velocity of the closer shaft to the rotational angular velocity of the door, especially when special demands are made of closers, be they overhead door closers or floor closers. This is the case, for example, with so-called slide arm closers, in which, due to the special translation characteristic of the slide arm, a special torque curve on the closer shaft is required in order to obtain the desired closing and opening moments on the door.

The object of the invention is to provide a door closer that delivers a favorable torque curve with a compact design.

The object is achieved in that it is provided in the door closer mentioned at the outset that the toothed pinion on its circumference and / or the complementary toothing associated with the toothed pinion on sections of the rolling curve has differently configured teeth, as claimed in claims 1, 3 and 5, respectively.

The eccentrically mounted pinion advantageously has a non-round, for example oval or elliptical, rolling curve, but can also be designed as a round eccentrically mounted pinion.

The toothing on the piston side can be formed on a toothed rack with a preferably S-shaped pitch curve.

Different designed teeth can be provided either on the toothed pinion-side toothing or on the associated complementary toothing or on both toothings. For example, profile shift, module and / or flank angle can be varied. This makes it possible to design the individual teeth so that an optimal course of the closing torque and the opening torque and a high efficiency with a compact design of the closer is achieved.

In order to optimize these closing parameters, it can be provided that the configuration of the teeth of the pinion and / or the complementary toothing is varied as a function of the door opening angles assigned to the rolling curve sections and / or as a function of the respectively effective lever arm.

In the embodiments in which the pinion-side toothing and / or the complementary toothing assigned to the pinion has a profile shift that varies over its pitch curve, it is advantageous if the profile shift in the pinion-side toothing is designed to be positive in a pitch curve section with an assigned large door opening angle. This means that the toothing on the pinion is displaced radially outwards. In the area of ​​large door opening angle in question, the radius of the pinion is relatively small. The positive profile shift makes it possible to use a closer shaft with a relatively large diameter to support the pinion, also considering the small radius.

The complementary toothing assigned to the pinion can have a corresponding but opposite profile shift as the toothing on the pinion side.

In a preferred further development it is provided that the profile shift of the toothing on the pinion side in a pitch curve section with an associated small door opening angle is designed to be negative. If the complementary piston cable toothing, which is preferably designed as a toothed rack, has corresponding but opposite profile displacement as the toothing on the pinion side, it follows that in the area of ​​small opening angles, the piston side toothing has positive profile displacement, with the result that the wall in this area is relatively little due to the toothing is reduced and therefore the piston can be made with a small diameter.

Preferably, the profile shift in the toothing on the pinion side increases continuously with increasing door opening angle in the direction of positive profile shift.

In the embodiments in which it is provided that the toothing on the pinion side and / or the complementary toothing associated with the toothed pinion has teeth with different modules via the pitch curve, teeth of different sizes are provided via the pitch curve sections. The strength of the toothing in the individual pitch curve sections can thus be set as desired. The module or the tooth size chosen is only so large that it is necessary for the strength.

In order to obtain approximately the same strength over the entire toothing, it is provided that the module is designed to be inversely proportional to the effective lever arm. The module preferably increases continuously with the assigned door opening angle.

Because the toothing has a relatively small module in sections of the rolling curve with an associated small door opening angle and a larger module in sections of the rolling curve with an associated large door opening angle, relatively small teeth are provided in the area of ​​the small opening angles and larger teeth in the area of ​​the large angles. This applies to the teeth of the toothed pinion in the same way as for the toothing on the piston side, which is preferably designed as a piston rod. The complementary toothing on the piston side can have varied modules such as the toothing on the pinion side.

In the embodiments in which it is provided that the pinion-side toothing and / or the complementary toothing associated with the pinion has at least one tooth with different flank angles, several such teeth are preferably provided, in particular in the area of ​​relatively large pressure angles, in order to reduce the wall friction . The pressure angle corresponds to the pitch angle of the rack and pinion curve, for example. This configuration of the teeth is advantageous in the so-called transition region of the toothed rack, ie, in the vicinity of the turning point of the S-curve-shaped rolling curve and in the complementary toothing on the pinion side. These are asymmetrical teeth, in which the flank on the pressure side has a more acute flank angle than a flank on the non-pressure side. This has the effect that the force component in the direction of the side wall and thus also the wall friction are kept relatively low.

The complementary toothing assigned to the pinion can have corresponding flank angles as the toothing on the pinion side.

It proves to be particularly advantageous if the configuration of the pinion-side and / or the complementary toothing assigned to the pinion is optimized by appropriate setting of profile shift, module and / or flank angle, in particular by computer-aided design. The characteristics of profile shift, module and flank angle can be optimized over sections of the rolling curve varied, in particular coordinated, selected, can also be set constant across the entire pitch curve.

In a special embodiment variant it is provided that the eccentrically mounted pinion interacts with a gear which corresponds to the gear of a conventional door closer. This makes it possible to use components of a conventional closer or to convert a conventional closer accordingly.

Particular cost advantages result from the production of a corresponding embodiment, in which it is provided that a conventional door closer with its housing and the mechanism therein, including the transmission, is used, and that two intermeshing eccentrically mounted pinions are arranged outside the housing, of which the one on the closer shaft of the conventional door closer and the other on another, shaft or axle mounted in the housing in order to transmit the closing torque to the door. That the eccentric gear is arranged outside the housing, the eccentrically mounted gears can be relatively large and can be designed as thinner disks. They can be manufactured as cheap stamped parts. The eccentrically mounted pinion advantageously has a non-circular, in particular oval or elliptical pitch curve, but can also be designed as a round eccentrically mounted pinion.

Further advantageous embodiments of the invention are specified in the subclaims.

The invention is explained in more detail below using exemplary embodiments in conjunction with the drawing; shows in the drawing;<ul id="ul0001" list-style="none" compact="compact"><li>1 is a schematic representation to explain the functional principle of a door closer working with an eccentric pinion,</li><li>2 shows a schematic illustration of an exemplary embodiment of an eccentrically mounted toothed pinion,</li><li>3 shows a schematic illustration of an exemplary embodiment of a toothing assigned to the pinion according to FIG. 2,</li><li>Fig. 4 is a schematic representation of an embodiment of a piston with internal teeth corresponding to FIG. 3 and an associated pinion acc. Fig. 2,</li><li>5 shows a schematic illustration to explain an embodiment variant with a high transmission ratio that is particularly suitable for floor door closers,</li><li>6 is a schematic partial sectional view of an embodiment of an overhead door closer,</li><li>7 is a schematic partial sectional view of a door closer for swing doors designed according to the invention,</li><li>8 is a schematic partial sectional view of a floor door closer for stop doors designed according to the invention,</li><li>9 shows a schematic top view of an embodiment variant which uses a conventional door closer and an additional eccentric gear, and</li><li>10 shows a schematic side view of the embodiment variant according to FIG. 9.</li></ul>

FIG. 1 shows in a schematic manner a toothed pinion 25 to be connected to a closer shaft, which meshes with toothing 27 that is fixed to the piston.

The piston, not shown, can cooperate in a conventional manner with a closer spring mounted in a housing. Versions as overhead door closers and floor closers are provided. In the case of an overhead door closer, the pinion 25 or the closer shaft carrying the pinion is connected to a linkage provided for power transmission between the door and the frame. The linkage can preferably be designed as a sliding arm.

The toothed pinion 25 has a pitch curve 26, which is composed of a first circular section with the radius R1, a circular section with the radius R2 continuously adjoining it, and a circular section with the radius R3, which is in turn continuously adjoining it. The central pitch curve section with the radius R2 has the smallest curvature, ie the radius R2 is significantly larger than the radials R1 and R3.

The rolling curve section with the smallest radius R3 is in the shown schematic representation in engagement with the toothing 27, wherein the position shown corresponds to the opening angle 0 of the closer, ie the assigned door is closed. If the door is opened, the spring force of the closer spring acting on the piston and thus on the toothed rack 27 carrying the teeth becomes effective via the lever arm A, ie a high closing force is available in the area of ​​small opening angles.

When the door is opened further or the opening angle is increased, the pinion 25 rotates counterclockwise and the piston-fixed toothing 27 is shifted to the right in the illustration in FIG. 1 against the spring force of the closer spring. The effective lever arm decreases in accordance with the selected course of the pitch curve, namely down to the value B, which corresponds to the radius R1 of the pitch curve 26 of the pinion 25. In the example shown in Fig. 1 the ratio of A to B is 2 to 1. This ratio corresponds to the translation achieved.

Through a suitable choice of the course of the rolling curve 26, which does not necessarily have to be composed of circular segments, a very flat course of the rolling curve 28 of the toothing 27 can be achieved, the flat course corresponding to a small pressure angle and thus minimizing the impact on the guide wall the toothing 27 impacting friction component is reached.

The maximum pressure angle in an embodiment according to FIG. 1 is designated by α.

FIGS. 2 and 3 show designs of a toothed pinion 25 or associated piston-side toothing 27. FIG. 4 shows an exemplary embodiment in which the pinion 25 engages in the toothing 27, the piston-side toothing 27 being designed as an internal toothing in a cavity 32 of the piston is. The pinion 25 is mounted on the closer shaft, which projects into the cavity 32.

The pinion 25 has only a portion of its circumference with which it meshes with the piston-side toothing 27. The toothing of the pinion 25 extends over a pitch curve section from 0 to 180 °.

In the illustration in FIGS. 2 and 3, the pitch curves 26, 27 are drawn into the toothings 25, 27 with a scale which indicates the respective angle of rotation of the pinion 25 or the associated door opening angle of the door for the various engagement positions.

In the exemplary embodiment in FIG. 4, the arrangement of the pinion 25 and the associated piston-side toothing 27 and their pitch curves 26, 28 correspond to the scheme according to FIG. Figure 1.

In the position shown in Figure 4, there is a rotational position of the pinion 25 of 0 °. The longer lever arm a. The door is closed. When the door is opened, the pinion 25 turns counterclockwise and, when the door is in the maximum opening position, it turns to 180 °. In this position the shorter lever arm b.

The toothing of the pinion 25 and the piston-fixed toothing 27 are designed as involute teeth. This has manufacturing advantages. However, other types of toothing are possible with other designs.

The toothing of the pinion 25 has a profile shift which is designed differently over the circumference of the pinion 25 between 0-180 °. It is negative in the area of ​​small angles, in particular around 0 °, and in the area of ​​large angles, specifically from about 30 ° and increasingly between 80 ° and 180 °. The profile shift increases continuously with the angle of rotation of the pinion 25 from the negative to the positive values.

The piston-side toothing 27 has a corresponding but opposite profile shift. Accordingly, positive values ​​are provided in the area associated with the small door opening angle and negative values ​​in the area with large opening angles.

The positive profile shift present in the toothing of the pinion 25 in the area of ​​large angles enables a closer shaft with a relatively large diameter to be used for mounting the pinion 25 despite the relatively short half-diameter b in this area. On the other hand, the positive profile shift present in the piston-fixed toothing 27 at the assigned small angles ensures that the wall thickness of the piston-side toothing 27 in this area is weakened only relatively little by the toothing, even with a large transmission ratio and steep pressure angle α, that is, the wall thickness does not become too thin even with the desired relatively narrow construction. This means that a relatively slim piston can be used even with a large gear ratio.

Furthermore, the toothing of the pinion 25 has different modules which vary between 0 and 180 ° over the pitch curve section. The same applies to the piston-fixed toothing 27.

The module increases continuously with the assigned door opening angle, in reverse proportion to the respective radius of the pinion 25 or to the respectively effective lever arm. This means that in the area of ​​small door opening angles (by 0 °) with a simultaneously large lever arm (by a) a relatively small module, ie small teeth, and in the area of ​​larger angles by a smaller lever arm (by b) a larger module, ie larger teeth are provided .

The associated complementary piston-fixed toothing 27 has a corresponding module variation, in which a relatively small module is provided in the area of ​​small opening angles and a larger module is provided in the area of ​​larger angles.

The module is selected so that the toothing 26, 27 is designed with approximately the same strength in the entire area. Furthermore, in the case of a small module, the rolling process runs particularly smoothly because of the lower flank friction in the case of a small module. The fact that in the area of ​​larger angles a relatively large module but at the same time a positive profile shift is also provided in the pinion 25, the disadvantageous undercut which otherwise occurs with a large module and a small radius is avoided.

The toothing of the pinion 25 and the piston-fixed toothing 27 also have specially set flank angles, as can be seen in FIGS. 2 to 4, the teeth in particular are designed asymmetrically in the region of the smaller door opening angles by the pressure-side flanks - those on the right in the drawing Flanks 20 of the pinion 25 or the left flanks 21 of the toothing on the piston side are steeper than the normal on the pitch curve in the region of the flanks.

This ensures that the force component in the direction of the piston wall is reduced and consequently the wall friction is kept low. This results in good efficiency.

In the exemplary embodiment in FIG. 4, the flanks 20, 21 of the teeth each represent the pressure side, both when opening and when closing. Due to their steeper design, the wall friction is reduced in both opening and closing.

The reduction in friction is particularly important when opening, because friction and spring force work in the same direction and counteract the opening movement; different when closing, there friction and spring force act in opposite directions. Thus, the opening torque to be applied is always greater than the closing torque.

The DIN regulations for door closers stipulate that the opening torque must not be more than 1.5 times the closing torque. This can easily be achieved with the configuration of the flank angle according to the invention.

5 shows an arrangement particularly suitable for floor door closers. In this case, an eccentric pinion 30 is connected to the closer axis, which meshes with a further, rotatably mounted, eccentric pinion 25, which in turn is in engagement with a toothing 27 which is fixedly connected to the piston, in particular in the form of a rack.

The pitch curve 31 of the eccentric pinion 30 extends with respect to the axis of rotation such that the lever arms effective with respect to the pinion 25 differ from the maximum value A₃ up to the minimum value B₃ change over the full opening angle of the closer.

The rolling curve 31 of the pinion 30 is assigned a rolling curve 29 on the pinion 25, which is indicated by dashed lines and extends approximately over half the circumference of the pinion 25. The other half of the circumference of the pinion 25 has a rolling curve 26 which interacts with the toothing 27 and which, in turn, is associated with the very flat rolling curve 28 of the toothing 27.

The minimum effective radius of pinion 25 is B2 and the maximum effective radius is A₂ featured.

The translations that become effective in the interaction of pinion 25 and toothing 27 are marked with A₁ and B₁ featured.

Using this version results in a particularly favorable k dimension of, for example, 20 mm, it being essential for the floor closer that, despite the very flat rolling curve 28 of the toothing 27, a very high transmission ratio can be achieved. The translation ratio is determined from the product of the individual translations, ie in the present case from the product<maths id="math0001"><math display="block"><mrow><mfrac><mrow><msub><mrow><mtext>A</mtext></mrow><mrow><mtext>3</mtext></mrow></msub></mrow><mrow><msub><mrow><mtext>B</mtext></mrow><mrow><mtext>3</mtext></mrow></msub></mrow></mfrac><mtext>×</mtext><mfrac><mrow><msub><mrow><mtext>A</mtext></mrow><mrow><mtext>2</mtext></mrow></msub></mrow><mrow><msub><mrow><mtext>B</mtext></mrow><mrow><mtext>2</mtext></mrow></msub></mrow></mfrac><mtext>×</mtext><mfrac><mrow><msub><mrow><mtext>A</mtext></mrow><mrow><mtext>1</mtext></mrow></msub></mrow><mrow><msub><mrow><mtext>B</mtext></mrow><mrow><mtext>1</mtext></mrow></msub></mrow></mfrac><mtext>.</mtext></mrow></math><img file="EP0243786B2_D0001.tif" /></maths> A ratio of, for example, 4.5 to 1 can be achieved without problems in practice.

It should also be mentioned that the engagement areas of the toothed pinion 25, ie the areas 26, 29 referred to above as pitch curves, can also overlap. The toothing in FIG. 5 can be designed in a corresponding manner as in FIGS. 2 to 4 with variation of the profile shift, the module and / or the flank angle.

Fig. 6 shows a partial sectional view of an overhead door closer designed according to the invention.

A piston 33 is arranged in the housing 1 and is biased in the usual way into the closed position by means of compression springs 34. In its area facing away from the springs 34, the piston 33 has a recess or a cavity 32 in which an eccentric pinion 25, which is connected in a rotationally fixed manner to the closer shaft, is arranged. This pinion 25 is in engagement with a toothing 27 which is adapted in terms of its rolling curve to the corresponding rolling curve of the pinion 25. A check valve 43 belonging to the damping device is provided in the area of ​​the piston recess 32 on the spring side.

The position of the piston 33 drawn with solid lines corresponds to the closed position. In this position, the largest lever arm A is effective between the eccentric pinion 35 and the toothing 27.

If the wing assigned to the closer is pivoted in the opening direction, then the piston 33 moves due to the interaction of pinion 25 and toothing 27 into the position shown in broken lines, the lever arm becoming smaller and smaller and finally in the position marked with 25 'and 27' Pinion and toothing reached the smallest value B.

In this embodiment, the flat course of the toothing 27 must be observed, which ensures that the friction component between the piston 33 and the housing 1 remains minimal.

Fig. 7 shows an embodiment of the invention in the form of a floor door closer for swing doors. The eccentric pinion 25 is arranged in a corner region of the housing 1 to achieve the most compact possible construction and is in engagement with a center-symmetrical tooth segment 35. This tooth segment 35 is articulated in the center and is connected to the piston 33 via a lever 36. The lever 36 is pivotally hinged at both ends.

The piston 33 is provided with a rod 38 which carries an axially adjustable support and guide disk 39 in the region of its end. Between this support and guide plate 39 and a stop sleeve 37 directly adjacent to the piston 33 in the middle position, a compression spring 34 is arranged, which is acted upon depending on the direction of the pivoting movement of the associated swing door, on the one hand via the support and guide plate 39 when supported on the stop sleeve 37 and secondly by the stop sleeve 37 when supported on the support and guide disk 39, which is attached to an adjustable sleeve 40 which on the one hand slidably receives the piston rod 38 and on the other hand can be adjusted in the axial direction from outside the housing.

By specifically specifying the rolling curves of eccentric pinion 25 and toothed segment 35, the course of the closing force can in turn be predefined optimally.

8 shows an embodiment of the invention in the form of a floor door closer for single-action doors.

In this embodiment, the eccentric pinion 35 is in turn preferably arranged in a corner region of the housing and interacts with an eccentric segment 41 which is pivotally mounted and is coupled to the piston 33 via a connecting rod 36. The cup-shaped piston 33 is biased by a spring 34 towards the bottom of the housing 1 and is movable between this bottom and a housing stop 42.

The eccentricities or rolling curves of pinion 25 and toothed segment 21 can in turn be selected in accordance with the desired closing force profile.

The embodiment shown in FIGS. 9 and 10 represents a modification of a conventional door opener according to the invention. A conventional overhead door closer is preferably used. It has a housing 45, with a closer shaft 46 mounted therein and a pinion (not shown), which is mounted centrally within the housing 45 on the closer shaft 46 and which meshes with a piston-fixed toothing in the housing 45, also not shown.

The normally open contact in this respect is equipped with an additional oval gear transmission 47, which in the exemplary embodiment is designed as an elliptical transmission, in that an eccentrically mounted gear 48 is placed on an end of the closer shaft 46 protruding from the housing 45, with another gear, likewise on the housing meshes on an additional axis 49 mounted gear 50. The gear wheel 50 is connected to the linkage, which in the present case is designed as a sliding arm 51. Alternatively, the axis 49 can also be designed as a shaft connected to the sliding arm 51, which then represents the closer shaft of the door closer according to the invention.

The gears 48, 50 are designed as elliptical gears. Depending on requirements, they can be dimensioned as relatively thin disks with relatively large half-knives; because they are arranged outside the housing 45 and are therefore not limited by the dimensions of the interior. The gears 48, 50 can therefore be manufactured as cheap stamped parts.

The gear 47 formed with the gears 48, 50 brings the desired ratio and ensures a favorable torque curve even when using a sliding arm. Furthermore, the desired construction of the conventional closer is maintained. In principle, the eccentrically mounted pinion can have a rolling curve profile, as in FIGS. 1 to 5, and the entire additional gear transmission can also be designed in accordance with the explanations in FIGS. 1 to 5.

All embodiments of the invention have in common that there is a technically simple and economically feasible construction, the eccentric elements also being inexpensive to produce, since a corresponding broaching tool or shape has to be produced only once for each special element.

The compactness of the respective closer, which can always be achieved, is paired with an optimal course of the total closing torque in all embodiments, which can be adapted as best as possible to the respective application.