Door closer.

The invention relates to a door closer with a run in a housing piston, at least one co-operating with the piston closing spring and a hydraulic damper and a via a transmission connected to the piston closer shaft or closer axle.

NO contact of this kind is known from the DE-GBM 17 95 135th

This known closer is designed such that the attacking at the closer shaft torque is at its maximum in the zero position, decreases rapidly in the small aperture angle, then remains approximately the same, and finally gradually decreases to zero at an opening angle of 180 °. This is achieved in that the closing spring is guided on a fixed in the closer housing hollow cylinder and in slots at the ends thereof each one serving as an abutment slider in such a manner can be displaced, that the closer axis facing slide one by a roller on the closing shaft seated cam bears and the other slider is connected by a link with a crank which is mounted in the closing shaft of the opposite end of the housing and non-positively connected to the closing shaft by a chain drive.

This known device is both extremely expensive and on the other hand has only limited potential in terms of specifying a certain closing force curve.

The transmission ratio of the respective shutter, ie, the current ratio of the rotational angular velocity of the closing shaft to the rotational angular velocity of the door must, in practice, great attention should be paid, especially if to make contact, whether overhead door closer_'or floor springs, special requirements.

This is for example the case with so-called Gleitarmschließern in which the closing moments therefore are unfavorable, because with a small opening angle when the door has to be pushed into the lock, only a relatively low torque is available. Although Gleitarmschließern, which are characterized by an optically favorable appearance that Reibverhältnis at the moment of opening of the wing is low, as in small Aperture little friction arises, always relatively-long guide rails must be accepted in order to guarantee the required reliability.

The object of the invention is a both a top door closer and as _Bodentürschließer and in particular to provide as Gleitarmschließer usable door closers, which meets both the demands for compact design and economical production ability as well as the requirement concerning functional optimal closing and opening torques and accordingly the use of short, allows for GlelLarmschließern in dimensions about the closers dimensions corresponding guide rails.

The object is achieved in that in the door closer mentioned above, a transmission is provided with at least one toothed pinion, which is eccentrically mounted and / or has on its circumference differently configured teeth. In the case of the eccentric bearing, the pinion may have round or non-round rolling curves. When eccentric but also in the central storage of the pinion, the pinion toothing may have over the circumference of the pinion or on the rolling curve differently designed teeth, for example, profile modification, module and / or flank angle can be varied. In this case, the pinion engages in a complementary, the piston at least non-positively associated gearing.

The closing torque can be transmitted from the closer shaft itself or through an on the closing shaft rotatably mounted gear on the door. The same applies to the opening of the door from the door to the closer shaft and the bearing on the closing shaft gear to transfer the opening moment. Both by the eccentric mounting of the pinion and by the different configuration of the teeth, the possibility is created -a function of the closing angle to be adjusted changing translation function. It is also an optimal course of total closing torque and the opening moments and high efficiency in a compact design of the closer is adjustable.

The Wälzkurvenverlauf is selected accordingly. Preferably, the rolling curve of the eccentrically supported pinion is so constructed that it, starting from a range of minimum radius, merges continuously into a region of maximum radius; z. B., there is a rolling curve of a plurality of immediately merging into one another segments of a circle whose radii the centers of which are different and mutually offset. It can be provided that a second to a first, the large opening angles of the closer associated pitch curve section, a substantially larger radius (R₂) Comprising Direction, the first pitch curve continuously advancing translated second pitch curve follows, and that a third pitch curve connects continuously to this second pitch curve whose radius (R₃) Is smaller than the radius (R₁) Is associated with the first Wälzkurvenabschnitts and the region of small opening angle of the door closer. For the pinion associated complementary toothing results in a corresponding rolling curve, z. B. an elongated S-shaped rolling curve.

Specifically, in this embodiment it is advantageous if the pinion gear and / or the pinion associated with complementary teeth on sections of the pitch curve differently configured teeth has or have, the configuration of the teeth, in particular in dependence on the, the Wälzkurvenabschnitten associated door opening angles and / is varied, or in dependence on the respectively effective lever arm.

For example, the tooth pinion toothing and / or the pinion associated complementary teeth on its rolling curve varied profile shift exhibit. Advantageously, the profile shift in the pinion toothing is embodied in a positive pitch curve associated with a large door opening angle. This means that the tooth is moved to the pinion radially outward. In the area concerned is large door opening angle of the radius of the pinion is relatively small. The positive displacement profile creates the possibility of using a closer shaft with a relatively large diameter for mounting the pinion and in view of the semi-minor diameter.

The the pinion associated complementary teeth can have corresponding but opposite displacement profile as the tooth pinion toothing.

In a preferred development it is provided that the addendum of tooth sprocket-side gear is formed negative in a pitch curve associated with a small door opening angle. When preferably designed as a rack complementary piston side toothed appropriate ,. but having opposite profile shift as the pinion toothing, it follows that the range of small opening angle, the piston-side toothing positive profile displacement, with the result that the wall is reduced in this area by the toothing relatively little and therefore, the piston having a small diameter are executed can. Preferably, the profile displacement decreases in the tooth sprocket-side teeth with increasing opening angle continuously toward positive profile shift.

In further preferred embodiments it is provided that the toothed pinion toothing and / or the pinion associated with complementary teeth on the rolling curve having teeth with different modulus. This means that are provided on the Wälzkurvenabschnitte different sized teeth. Thus the strength of the teeth can be arbitrarily set in each Wälzkurvenabschnitten. Preferably, the module or the tooth size is chosen only as large as is needed for strength.

In order to obtain about the same strength throughout the toothing is provided, that the module is inversely proportional to the effective lever arm formed. Preferably, the module continues to rise with the associated door opening angle.

In particular embodiments it is provided that the toothing in portions of the pitch curve with an associated small angle of door opening relatively small modulus and in sections of the pitch curve with an associated large angle of door opening larger module. This relatively small teeth and in the area of ​​large angle bigger teeth so are provided in the region of small opening angle. This applies to the teeth of the pinion in the same manner as for the piston rod is preferably designed as piston-side toothing. Here, the complementary piston side teeth accordingly varied modules like the tooth pinion toothing aufwei; sen.

In particularly preferred embodiments it is provided that the pinion toothing and / or the pinion associated complementary toothing comprises at least one tooth with different flank angles.

Preferably, a plurality of such teeth, in particular in the range relatively large pressure angle, provided in order to reduce the wall friction. The pressure angle corresponds, for example, the lead angle of Zahnstangenwälzkurve. This configuration of the teeth is advantageous in so-called transition region of the rack, ie, in the vicinity of the inflection point of the S-curved rolling curve and in the complementary pinion toothing. It is asymmetrical teeth, in each of which the pressure-side edge has a more acute flank angle than a non-pressure-side flank. This causes the force component can be kept relatively small in the direction of the side wall and thus also the wall friction.

The the pinion associated complementary toothing can corresponding flank angle as the tooth pinion side dovetailing - exhibit opening.

Particularly advantageous turns out, if the design of the sprocket-side and / or the pinion associated complementary teeth on corresponding setting addendum modification, module and / or flank angle, is particularly optimized by Computer Aided Design. The characteristics profile shift, module and flank angle may vary over portions of the rolling curve, in particular coordinated, be selected, but may also be set to be constant over the entire pitch curve.

In one particular embodiment, it is provided that the eccentrically mounted pinion with a gear that corresponds to the transmission of a conventional door closer, cooperates. This creates the possibility of using components of a conventional shutter or convert a conventional normally accordingly.

Special cost benefits in the manufacture of a corresponding embodiment in which it is provided that a conventional door closer with its housing and its therein mechanism is used, including gear, and that two intermeshing eccentrically supported pinions are arranged outside the housing, of which the a is mounted on the closer shaft of the conventional door closer and the other on another, mounted in the housing shaft or axis in order to transfer the closing moment on the door. Since the eccentric gear outside the housing is arranged eccentrically mounted gears may be designed as a relatively large and thinner slices. They can be made as cheap stampings. Advantageously, the eccentrically mounted pinion on a non-round, in particular oval or elliptical pitch curve, but may also be designed as a round eccentrically supported pinion.

Further advantageous embodiments of the invention are specified in dependent claims.

The invention will now be described in conjunction with the drawings with reference to embodiments; in the drawings:<ul><li>_Fig. 1 is a schematic diagram for explaining the operating principle of a working eccentric pinion door closer,</li><li>_Fig. 2 is a schematic representation of an embodiment of an eccentrically mounted pinion,</li><li>_Fig. 3 is a schematic representation of an embodiment of a pinion according to the. 2 associated teeth,</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 gem. FIG. 2</li><li>Fig. 5 is a schematic diagram for explaining a suitable particularly for floor springs variant with a high transmission ratio,</li><li>Fig. 6 is a schematic partial sectional view of an embodiment of a Obentürschliessers,</li><li>is a schematic partial sectional view of a trained FIG. 7 according to the invention _Bo-door closer for swing doors,</li><li>Fig. 8 is a schematic partial sectional view of the invention formed by the bottom door closer for single action doors,</li><li>_Fig. 9 is a schematic plan view of a variant that uses a conven union door closer and an additional eccentric and,</li><li>_Fig. 10 gem is a schematic side view of the embodiment. Fig. 9.</li></ul>

1 shows in a way schematisiserter a slept serwelle to connecting pinion 25, dastmit a piston fixed gear 27, meshes.

The dargestelltaKolben unspecified can cooperate in a conventional manner with a mounted in a housing closing spring. There are provided as overhead door closers and floor springs versions. In case of an overhead door closer, the pinion 25 and the supporting the pinion closer shaft is connected to a provided for transmitting power between door and frame parts. The linkage may be preferably constructed as a sliding arm.

The pinion 25 has a pitch curve 26, which is composed of a first circular portion with the radius R1, a steadily to it subsequent circular section with the radius R2 and a turn steadily to it subsequent circular section with the radius R3. The mean pitch curve having the radius R2 has the least curvature, that is, the radius R 2 is substantially greater than the radii R1 and R3.

The pitch curve with the smallest radius R3 is in the shown schematic illustration in engagement with the toothing 27, wherein the position shown corresponds to the opening angle 0 of the shutter, that the associated door is closed. If the door is opened, it is on the piston and thus on the gear 27 carrying rack spring force of the closing spring on the lever arm_A effective, ie it is in the region of small opening angle in a high closing force.

In a further open the door or at a magnification of the opening angle of the pinion gear 25 rotates counterclockwise and the piston fixed gear 27 is moved against the spring force of the closing spring in the illustration in Figure 1 to the right. In this case, the effective lever arm decreases from according to the selected course of the rolling curve and that to the value B, which corresponds to the radius R1 of the rolling curve of the toothed pinion 26 25th In the example of FIG. 1 shown the ratio of A to B is equal to 2 is to 1. This ratio corresponds to the reached Translation.

By suitable choice of the course of the rolling curve 26, which need not necessarily be composed of circular segments, a very flat course of the rolling curve 28 of the teeth can be achieved 27, wherein the flat curve corresponds to a small pressure angle, thus minimizing in the guide wall the teeth 27 is achieved affecting ligand friction component.

The maximum pressure angle in an embodiment entsprchend Fig. 1 is indicated by α.

Figures 2 and 3 show embodiments of a pinion 25 and an associated piston-side gear 27. Figure 4 this is shown in an embodiment in which the pinion 25 engages the toothing 27, wherein the piston-side gear 27 is formed as internal toothing in a cavity 32 of the piston is. The pinion 25 is mounted on the closer shaft, which protrudes into the cavity 32nd

The pinion 25 carries only a portion of its periphery a toothing 27 with which it meshes with the piston-side toothing. The teeth of the pinion 25 extends across a pitch curve from 0 to 180 °.

In the illustration in Figs. 2 and 3 are in the toothings 25, 27, the rolling curves 26, 27 located 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 positions of engagement.

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

In the position shown in Figure 4 there is a rotational position of the pinion 25 of 0 °. It affects the longer lever arm a. The door is closed. Upon opening the door rotates the pinion 25 counterclockwise and is at maximum_Türöffnungsstellung in the rotational position of 180 °. In this position, the shorter lever arm acts b.

The teeth of the pinion 25 and the piston fixed teeth 27 are configured as involute. This has manufacturing advantages. However, other types of gear are quite possible in other embodiments.

The teeth of the pinion 25 has profile displacement, which over the periphery of the pinion 25 between 0 - 180 ° formed differently. It is at small angles, especially negative to 0 ° and in the large angle, namely starting at about 30 ° and increasingly formed positively from 80 ° to 180 °. The profile shift increases with the rotation angle of the pinion 25 continuously from the negative to the positive values ​​towards.

The piston-side gear 27 has corresponding but opposite _Profilverschiebung on. There are therefore in the small door opening angles region associated with positive and negative in the range of large aperture angle values ​​provided.

The in the teeth of the pinion 25 present in the large-angle positive profile shift permits despite in this area relatively short half diameter b a closer shaft can be used with a relatively large diameter for supporting the pinion 25th On the other hand ensures the piston fixed to the teeth 27 in the associated small angles present positive profile shift, that the wall thickness of the piston side teeth 27 is relatively little weak in this area, even with large translation and steep pressure angle α through the teeth, that is, that the wall thickness also at the desired relatively narrow construction is not too thin. This means that even at a high transmission ratio, a relatively slim piston may be used.

Furthermore, the teeth of the pinion 25 about the pitch curve between 0 to 180 ° varied, different module. The same applies to the piston fixed gear 27th

The modulus increases with the associated door opening angle continuously, and inversely proportional to the respective radius of the pinion 25 or to the respectively effective lever arm. This means that the range of small opening angle (0 °) at the same time a large lever arm (at a) relatively small module, ie, small teeth, and in the range larger angle at the same time a smaller lever arm greater (at b) module, ie larger teeth are provided ,

The associated piston-complementary tooth system fixed to the corresponding module 27 has variation, is provided in the smaller opening angle in the range of relatively small modulus and in the range larger angle larger module.

The modulus is chosen so that the teeth 25, 27 arranged in the entire area of ​​approximately equal strength. Furthermore, results in low modulus, a particularly liquid end of the rolling process due to the lower edge of friction at low modulus. Characterized that in the area of ​​larger angles, although relatively large module but at the same time is provided in the pinion 25 also positive profile displacement is avoided which might otherwise occur at the high modulus and a small radius piece according to undercut.

The teeth of the pinion 25 and the piston-fixed teeth 27 also have specifically set flank angle, as shown in Figures 2 to 4 it can be seen, in particular the teeth in the region of the smaller door opening angle are designed asymmetrically in that the pressure side flanks - the right in the drawing edges 20 of the pinion 25 and the left flanks 21 of the piston-side teeth 27 - steeper relative to the formal äuf the pitch curve, in Bereich'der flanks.

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

In the embodiment in Figure 4 each the _FOpen lanlen 20, 21 of the teeth, the pressure side is, both during and upon closing. Their steeper training is therefore open at as well when closing each reduces the wall friction.

The reduction of friction in particular when opening important because this friction and spring force acting in the same direction and that the opening movement counter; otherwise on closing, there act friction and spring force opposite. Thus, so the applied torque opening is respectively greater than the closing torque.

In the DIN standards for door closer is required that the opening moment may not be more than 1.5 times the closing moment. This can be achieved with the inventive design of the flank angle readily.

The basic schematic representation of FIG. 5 shows a suitable especially for BodentürschlieBer arrangement. Here mit.der closing shaft is an eccentric toothed pinion 30 which meshes with a further, rotatably mounted eccentric pinion 25, which in turn is engaged fixedly connected to the piston with, in particular as a rack gear formed 27th

The _Wälzkurve 31 of the eccentric toothed pinion 30 extends about the rotational axis such that the relative to the pinion 25 effective lever arms A of the maximum value₃ to the minimum value B₃ change over the entire opening angle of the shutter.

Of the _Wälzkurve 31 of the pinion 30 is the pinion 25 associated with a rolling curve 29, which is indicated by dashed lines and extends approximately over half the circumference of the pinion 25th The other half of the circumference of the pinion gear 25 has a cooperating with the teeth 27 rolling curve 26, which in turn very flat extending rolling curve 28 of the teeth is assigned to the 27th

The minimally effective expectant radius of the pinion 25 is connected to B₂and the maximum becomes effective radius with A₂ in.

The interacting of pinion 25 and gear 27 becomes effective translations are with A₁ and B₁ in ..

When using this embodiment, a particularly effective k-degree of for example 20 mm, which is the floor spring is essential that despite the very flat running rolling curve 28 of the teeth 27 a very high transmission ratio can be achieved. The transmission ratio is determined aus.dem product of individual translations, which in this case from the product A₃ A₂ A₁ , A Verhältnis'von example 4.5_' to 1 can be reached without problems in practice

We should also mention yet that the engaging portions of the _Zahnritzels 25, ie, designated above as pitch curves section 26, 29, may overlap. The teeth in Fig '. 5 may be designed in a corresponding manner as in Figs. 2 to 4 with variation of the profile offset, modulus and / or flank angle.

_Fig. 6 shows a partial sectional view of a formed according to the invention, the overhead door closer. In the housing 1, a piston 33 is arranged, which in the usual way is biased by springs 34 to the closed position. The piston 33 has in its end facing away from the springs 34 area a recess or cavity 32, in which a with the closer shaft rotatably connected eccentric pinion 25 is located. This pinion 25 is in engagement with an adapted with regard to its rolling curve of the corresponding rolling curve of the pinion gear 25 to 27. A damping device belonging to check valve 43 is provided on the spring side of the piston recess in the region of the 32nd

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

If the normally associated wing pivots in the opening direction, then moves the piston 33 due to the interaction of the pinion 25 and toothing 27 in the dashed line position, the lever arm is constantly smaller and finally in the direction indicated by 25 'and 27' position pinion and gear reaches the minimum value B.

In this embodiment, the flatness of the teeth is to note 27, which ensures that the frictional component between piston 33 and housing 1 remains minimal.

_Fig. 7 shows an embodiment of the invention in the form of a_Bodentürschließers for swing doors. In this case, the eccentric gear 25 for achieving a highly compact structure-in arranged a corner region of the housing 1 and is engaged with a center symmetric toothed segment 35. This toothed segment 35 is pivoted centrally and is connected via a lever 36 to the piston 33 in combination. The lever 36 is hinged at both ends pivotally.

The piston 33 is provided with a rod 38, which carries an axially adjustable support and guide plate 39 in the region of its end. Between this support and guide plate 39 and an immediately adjacent in the center position of the piston 33 stop sleeve 37 a compression spring 34 is disposed, which is acted upon in dependence on the direction of pivotal movement of the associated swing door, namely on the one hand on the support and guide plate 39 adjusted for support on the stop sleeve 37 and on the other by the stop sleeve 37 with support on the support and guide plate 39, which is attached to an adjustable sleeve 40, on the one hand, the piston rod 38 slidably receives and on the other hand from outside the housing in the axial direction can.

Through selective default of Abwälzkurven of Exzenterritzel 25 and sector gear 35 can turn the clamping force course be optimally set.

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

In this embodiment, the eccentric toothed pinion 35 in turn is preferably arranged in a corner region of the housing and cooperates with an eccentric segment 41 which is pivotally supported and coupled by a connecting rod 36 with the piston 33rd The pot-shaped piston 33 is biased by a spring 34 toward the bottom of the housing 1 and movable between this floor and a housing stop 42nd

Dei eccentricities or Abwälzkurven of pinion 25 and gear segment 21 can be selected according to the desired clamping force course again.

The in Figures 9 and 10_gezeigte embodiment represents a modification of the invention a conventional door closer. Preferably, a conventional, overhead door closer is used. It comprises a housing 45, with mounted therein closer shaft 46 and a not shown, on the closing shaft 46 centrally mounted within the housing 45 the pinion that meshes with a fixed piston, also not shown teeth in the housing 45th

The extent conventional shutter is equipped with an additional oval gear mechanism 47, which is designed in the embodiment as elliptical gear by 46 an eccentrically mounted gear 48 is mounted on a projecting from the housing 45 end of the closer shaft, which with another, also on the case meshes on an additional axle 49 mounted gear 50th The gear 50 is connected to the linkage, which is formed in the present case as a slide arm 51st Alternatively it can be configured as connected to the sliding arm 51 shaft and the shaft 49, which then so is the closer shaft of the door closer according to the invention.

The gears 48, 50 are designed as elliptical gears. You can be sized as needed as a relatively thin disks with relatively large radii; because they are located outside the housing 45 and is therefore not limited by the dimensions of the interior. The gears 48, 50 can therefore be produced as cheap stampings.

The gear formed with the gears 48, 50 47 brings the desired transmission ratio and ensures a favorable torque curve even when using a sliding arm. Further, the desired construction of the conventional shutter is maintained. Basically, the eccentrically mounted pinion may have a Wälzkurvenverlauf, as shown in Figures 1 to 5, and also have the entire additional toothed gearing may be formed according to the embodiments in Figures 1 to fifth

All embodiments of the invention have in common that there is a technically simple and economically realizable construction, the eccentric members are also inexpensive to produce, since for each specific element only once an appropriate reamer or a corresponding shape to be manufactured.

The always achievable compactness of the respective shutter is in all embodiments paired with an optimal course of total closing torque, which can be optimally adapted to the respective application.