EP2933415A1 - Door drive - Google Patents

Abstract

A door drive, in particular a swing door drive, comprises a housing (12), an output shaft (18) which can be coupled to a door leaf or a frame, a motor (20) for driving the output shaft (18) and a spring unit (22) during a respective opening movement the door leaf is tensioned and relaxes during a respective closing movement of the door leaf. In this case, the output shaft (18) via a rack (28) by the motor (20) can be driven, wherein the rack (28) via a front-bevel gear (30) can be acted upon, the an engine-side helical spur gear portion (32) Ratchet-side spur gear portion (34) and arranged therebetween, in particular provided with a Gleason toothing bevel gear portion (36).

Description

The present invention relates to a door drive, in particular swing door drive, with a housing, a coupling with a door leaf or a frame output shaft, a motor for driving the output shaft and a spring unit, which is tensioned during a respective opening movement of the door and during a respective closing movement of the Door leaf relaxed.

Such door drives are used to close the wing of a motorized door with spring force. This is particularly important in smoke and fire doors of importance, which must be closed quickly and reliably in case of alarm, especially after responding to a smoke detector or power failure. By opening the door leaf, the spring unit is tensioned at the same time. With the aid of the spring unit, the door drive can thus close the door leaf even in the event of a power failure, which is mandatory with fire doors.

The usual swing door drives of the type mentioned are relatively bulky and bulky and relatively expensive to manufacture.

The invention has for its object to provide a door drive, in particular revolving door drive, of the type mentioned above, which has a more compact structure and is cheaper to produce.

The object is achieved by a door drive with the features of claim 1. Preferred embodiments of the door drive according to the invention will become apparent from the dependent claims, the present description and the drawings.

The door drive according to the invention, in particular revolving door drive, comprises a housing, an output shaft which can be coupled to a door leaf or a frame, a motor for driving the output shaft and a spring unit which is tensioned during a respective opening movement of the door leaf and relaxes during a respective closing movement of the door leaf. In this case, the output shaft via a rack by the motor can be driven, which is acted upon by a front-bevel gear, which includes a motor side helical Stirnradgetriebeabschnitt, a rack-side straight spur gear and arranged therebetween, in particular provided with a Gleason toothing bevel gear section.

Due to this design results in a total of more compact and simpler construction of the door drive, which also significantly reduces the cost of production. The preferably provided Gleason toothing of the bevel gear section is characterized in that the edges of the tooth back form a spiral.

The motor-side helical spur gear section preferably comprises a helical gear pinion connected to a motor shaft and a helical spur gear meshing therewith.

In this case, there is the helical spur gear of the motor side helical Stirnradgetriebeabschnitts according to a preferred practical embodiment of the door drive according to the invention of a carbon fiber reinforced polyamide-containing material, whereby a corresponding noise reduction is achieved.

The bevel gear portion advantageously comprises a bevel gear meshing with a bevel gear, which is connected to the helical spur gear of the motor side helical Stirnradgetriebeabschnitts.

In this case, the helical spur gear of the motor side helical spur gear portion and the bevel pinion of the bevel gear portion are preferably arranged on a common shaft which is supported by an axially disposed between the helical spur gear and the bevel pinion ball bearing.

Here, the common shaft may be provided, for example, in the form of a bevel pinion bolt and the helical spur gear be fixed by means of a toggle plug on the bevel pinion bolt. The arranged between the helical gear and the bevel pinion ball bearing can thus absorb axial and radial forces, whereby the bevel pinion is positioned very accurately relative to the bevel gear.

The provided with the helical gear of the helical side helical gear portion and the bevel pinion of the bevel gear portion shaft can also be supported by a arranged on the side facing away from the bevel pinion of the helical spur gear ball bearing.

The bevel gear of the bevel gear portion and the spur gear of the straight spur gear portion are preferably designed as a one-piece sintered part, whereby the manufacturing cost of the door drive can be reduced and the most compact design is achieved.

The bevel gear and the spur gear spur gear in question can thus be made as one-piece sintered part with two teeth and a, for example, seven-toothed spur gear.

The rack-side straight-toothed spur gear portion may in particular comprise a spur gear meshing with the rack and a spur gear connected to this spur pinion meshing with a spur pinion connected to the bevel gear of the bevel gear portion.

It is particularly advantageous if the spur gear and the straight-toothed spur gear of the rack-side spur gear portion are designed as one-piece sintered part, whereby the manufacturing cost of the door drive are further reduced and the door drive is kept relatively compact in construction. The spring unit preferably comprises a pushed onto the rack compression spring, which in particular again in terms of a compact construction of the door drive is advantageous.

According to a further preferred practical embodiment of the door drive according to the invention, the spring unit is arranged between an axially adjustable sleeve pushed onto the rack and a thrust bearing supported on a contact disk or the like. In this case, the sleeve can be axially adjustable in particular via a worm gear.

About the pinion of the third stage of the front-cone transmission, the rack can be retracted with a module toothing on the one hand motor in the transmission, on the other hand pushed out by the spring unit from the transmission. The rack may extend through the sleeve, the spring unit and the thrust bearing thrust washer. About the sleeve, the spring force and thus the closing force can be adjusted in the currentless operation.

The toothed rack preferably comprises a toothed section meshing with the spur-toothed pinion of the toothed-rack-side spur gear section and, in the region of its opposite end, a toothed section arranged in particular on the same side and meshing with a toothing of the output shaft. The toothed portions of the rack may thus be provided on the same side of the rack, i. pointing in the same direction.

In order to ensure the most reliable meshing, the rack is in the range of the sprocket-toothed straight spur gear and meshing with the teeth of the output shaft meshing toothed sections preferably in each case at least one on the side facing away from the respective toothed portion of the rack particular roller bearing roller, cylinder pin or supported.

The toothed rack preferably comprises a wave-shaped toothed section, which meshes with a non-circular toothing of the output shaft.

With such a design of the cooperating teeth of the output shaft and the rack, the resulting closing and opening torque can be influenced in the desired manner. Thus, a respective desired course of the closing and opening torque can be specified in particular by an appropriate choice of the waveform of the toothed portion of the rack and a corresponding choice of the shape of the non-circular toothing of the output shaft.

Preferably, the door drive has at least one pinion, which has a number of teeth between three and eight teeth. Thus, with a very small number of teeth as small as possible to realize stable gears.

The door drive can be arranged on a door leaf or a frame. The output shaft of the door drive can be connected via a lever or linkage with the frame or the door in conjunction.

The output shaft may comprise, for example, a bore with serration and, for example, thirty-one teeth for torque transmission to the lever or the linkage.

It may, for example, a gear housing, a gear cover and a tension profile and a bearing plate may be provided, in which the tension profile and the bearing plate comprehensive storable assembly, the preloaded spring unit, the rack and the output shaft can be inserted. The pull profile can be closed on one side over the sleeve, while it is closed on the other side with a lid. In between, the spring unit can be clamped. The rack can protrude from the sleeve. The example screwed bearing plate can form together with the tension profile bearing points for the output shaft.

The motor can be attached to a bearing plate, which is screwed to the gear housing and gear cover.

The helical motor pinion can be pressed for example on the motor shaft.

In order to obtain the smallest possible, stable gears, the pinions can each have a very small number of teeth, for example, between three and eight teeth. Thus, the motor pinion depending on the desired translation, for example, four to seven teeth and the bevel pinion, for example, five teeth, the spur gear spur in conjunction with the bevel gear, for example, seven teeth and the meshing with the rack spur pinion, for example, seven teeth. For a profile overlap of the teeth of more than 1, this is almost the smallest possible number of teeth. A profile coverage greater than 1 assures a smooth running of the gear stages, i. before the first tooth is disengaged, the second tooth is already engaged. The small pinion gear numbers lead on the one hand to small gear dimensions and to stable teeth with large ratios per gear stage. On the other hand, this creates the prerequisite for being able to sinter the gears without the risk of tooth breakage, since the sintered material has a lower strength than the steel commonly used. With sintered gears, the manufacturing costs can be reduced by a factor of 5 to 10 compared to steel gears that have to be machined.

The door drive can also be provided with a transformer to reduce the voltage, for example, from 230 V to 24 V, and include control electronics. In addition, the door drive may be provided at the end with lids and include a cover.

The motor drives the gear rack via the motor pinion and the front-bevel gear and via this the output shaft, which is used to apply a lever or linkage to open the door leaf. When closing the door leaf, the previously tensioned spring unit drives the gearbox and the engine, whereby the output shaft with the lever or linkage in the other direction are rotated and adjusted. In this case, the engine can go into generator mode and control the closing speed and the end impact of the door leaf via the control electronics.

The closing of the door leaf also works without power, which is mandatory for fire protection swing door drives.

The non-circular toothing of the output shaft and the meshing with this wave-shaped toothed portion of the rack may in particular be designed so that the torque transmitted from the spring unit to the output shaft torque decreases with increasing opening angle of the door leaf. Here, the non-circular toothing of the output shaft and the meshing with this wave-shaped toothed portion of the rack are preferably designed so that the torque transmitted from the spring unit to the output shaft torque decreases from an opening angle of the door leaf in the range of 4 ° with increasing opening angle of the door leaf. By changing the pitch circle from big to small, a larger torque is generated at small door opening angles than at larger opening angles. Thus, the requirements for a large door closing torque at door opening angles in the range of 0 ° to 4 ° and a rapidly decreasing door closing torque are achieved with larger door opening angles with a smaller motor.

The door drive according to the invention has a lower height compared to the previous drives. When powering the door is less power required at an opening angle above 4 ° than before. With the sintered gears, the manufacturing costs are minimized. It is now possible to use smaller and correspondingly less expensive motors and transformers. In addition, with a smaller engine and more compact components also results in a lower total weight of the door drive.

Fig. 1

eine schematische Darstellung einer beispielhaften Ausführungsform eines beispielsweise als Obentürschließer vorgesehenen erfindungsgemäßen Türantriebs,

Fig. 2

eine schematische Schnittdarstellung des Türantriebs gemäß Fig. 1,

Fig. 3

eine vergrößerte schematische geschnittene Draufsicht des das Stirn-Kegel-Getriebe, die Zahnstange und die Abtriebsachse umfassenden Teils des Türantriebs gemäß Fig. 1,

Fig. 4

eine vergrößerte schematische geschnittene Seitenansicht des das Stirn-Kegel-Getriebe, die Zahnstange und die Abtriebsachse umfassenden Teils des Türantriebs gemäß Fig. 1,

Fig. 5

eine schematische Draufsicht des Stirn-Kegel-Getriebes, der Zahnstange und der Abtriebsachse des Türantriebs gemäß Fig. 1,

Fig. 6

eine schematische Seitenansicht des Stirn-Kegel-Getriebes, der Zahnstange und der Abtriebsachse des Türantriebs gemäß Fig. 1 und

Fig. 7

eine schematische perspektivische Ansicht des Stirn-Kegel-Getriebes, der Zahnstange und der Abtriebsachse des Türantriebs gemäß Fig. 1.

The invention will be explained in more detail below with reference to an embodiment with reference to the drawing; in this show:

Fig. 1

a schematic representation of an exemplary embodiment of an example provided as overhead door closer invention door drive according to the invention,

Fig. 2

a schematic sectional view of the door drive according to Fig. 1 .

Fig. 3

an enlarged schematic sectional plan view of the front-bevel gear, the rack and the output axis comprising part of the door drive according to Fig. 1 .

Fig. 4

an enlarged schematic sectional side view of the front-bevel gear, the rack and the output axis comprising part of the door drive according to Fig. 1 .

Fig. 5

a schematic plan view of the front-cone gear, the rack and the output shaft of the door drive according to Fig. 1 .

Fig. 6

a schematic side view of the front-cone gear, the rack and the output shaft of the door drive according to Fig. 1 and

Fig. 7

a schematic perspective view of the front-cone gear, the rack and the output shaft of the door drive according to Fig. 1 ,

The Fig. 1 to 7 show a schematic representation of an exemplary embodiment of a door drive 10 according to the invention, in the illustration according to Fig. 1 for example, is provided as a top door closer for a revolving door.

The door drive 10 includes a housing 12, a rotatably mounted in the housing 12 and coupled to a door leaf 14 or a frame 16 output shaft 18, a motor 20, in particular electric motor for driving the output shaft 18 and a spring unit 22, during a respective opening movement of the Door leaf 14 is tensioned and relaxes during a respective closing movement of the door leaf 14 to provide a closing moment.

In this case, the door drive 10 in the illustration according to Fig. 1 For example, provided as a top door closer for a revolving door. In the present case, the housing 12 is mounted with the output shaft 18 on the door leaf 14 and the output shaft 18 connected to a lever 24 which is provided with a sliding block or the like, which is guided in a slide rail 26 which is fixed to the frame 16.

Like that Fig. 2 to 7 can be seen, the output shaft 18 via a rack 28 by the motor 20 can be driven, which is acted upon by a front-bevel gear 30 having a motor side helical Stirnradgetriebeabschnitt 32, a rack-side spur gear 34, a straight spur gear portion 37 and an intermediate arranged, in particular provided with a Gleason toothing bevel gear section 36 includes.

In this case, the motor-side helical spur gear section 32 comprises a helical geared pinion 40 connected to a motor shaft 38 and a helical spur gear 42 meshing therewith.

The helical spur gear 42 of the motor-side helical spur gear section 32 may consist in particular of a carbon fiber reinforced polyamide-containing material.

The bevel gear section 36 comprises a bevel gear meshing with a bevel gear 44, which is connected to the helical spur gear 42 of the motor side helical spur gear section 32.

The helical spur gear 42 of the motor-side helical spur gear portion 32 and the bevel gear 46 of the bevel gear portion 36 are arranged on a common shaft 48 which is arranged by a ball bearing 50 (see, in particular, Figs Fig. 3 and 4 ) is supported. How, in particular, the Fig. 3 and 4 can be taken is the shaft 48, which is provided with the helical spur gear 42 of the motor-side helical spur gear section 32 and the bevel pinion 46 of the bevel gear section 36, is also supported by a ball bearing 52 arranged on the side of the helical spur gear 42 facing away from the bevel pinion 46.

The bevel gear 44 of the bevel gear section 36 and the spur gear 58 of the spur geared spur gear section 37 may in particular be designed as a one-piece sintered part.

The rack-side straight-toothed spur gear portion 34 includes a spur gear 54 meshing with the rack gear 28 and a spur gear 56 connected to this spur gear 54 meshing with a spur gear 58 connected to the bevel gear 44 of the bevel gear portion 36.

In this case, the spur gear 54 and the straight-toothed spur gear 56 of the rack-side spur gear portion 34 may be configured as a one-piece sintered part.

How in particular on the basis of the Fig. 3 and 4 can be seen, the spring unit 22 may comprise a pushed onto the rack 28 compression spring. In the present case, the spring unit 22 is arranged between an axially adjustable sleeve 60 pushed onto the rack 28 and a thrust bearing 62 supported on a contact disk 64 or the like. The sleeve 60 is, for example via a worm gear 66 (see Fig. 3 ) axially adjustable.

The toothed rack 28 comprises a toothed section 68, which meshes with the spur gear 54 of the toothed rack-side spur gear section 34, and a toothing section 70 which is arranged in particular on the same side and which meshes with a toothing 72 of the output shaft 18.

In this case, the rack 28 may in particular comprise a wave-shaped toothed portion 70 which meshes with a non-circular toothing 72 of the output shaft 18.

The provided with the helical spur gear 42 and the bevel pinion 46 shaft 48 may be provided, for example in the form of a bevel pin bolt on which the helical spur gear 42 is fixed by means of a Knebelkerbstift, which arranged between the helical gear and the bevel pinion 46 ball bearing 50 Axial - And radial forces can absorb and the bevel pinion 46 is positioned exactly relative to the bevel gear 44.

The rack 28 may in the region of their with the spur gear 54 of the rack-side spur gear 34 and meshing with the teeth 72 of the output shaft 18 toothing portions 68, 70 each have a on the side facing away from the respective toothed portion 68, 70 side of the rack 28 in particular roller bearing roller , Cylindrical pin 74 (see Fig. 5 and 7 ) or the like.

The pinion 54 of the rack-side straight-toothed spur gear portion 34 thus pulls the toothed rack 28 with module toothing into the front-bevel gear 30, which on the other hand is pushed out of the front-bevel gear 30 by the spring unit 22. The rack 28 penetrates the sleeve 60, the spring unit 22 and the thrust bearing 62 with the bearing plate 64. About the sleeve 60, the spring force and thus the closing force can be adjusted in the currentless operation. By rolling rollers or cylindrical pins 74 a reliable tooth engagement is guaranteed. The sleeve 60 can be moved axially via the worm drive 66, for example a worm with an Allen key. The output shaft 18 may be provided with a bore which has, for example, a serration with, for example, thirty-one teeth for torque transmission to the lever 24 driving the door leaf 14.

The door drive 10 may be provided with a transmission housing 76, a gear cover 77 (cf. Fig. 3 and 4 ), a tension profile and a bearing plate be provided. In the storable assembly train profile and bearing plate, the prestressed spring unit 22, the rack 28 and the output shaft 18 may be arranged. On the one hand, the tension profile is closed by the adjustable sleeve 60 and on the other side by the lid 78. In between, the spring unit 22 is clamped. The rack 28 extends through the sleeve 60 through to the outside. The bolted bearing plate together with the tension profile, the bearings for the output shaft 18th

During installation, the gear wheels and the assembly profile and bearing plate are inserted into the gearbox. The gear cover 77 closes the gear while holding the module train profile and bearing plate in position.

The motor 20 may be attached to a bearing plate 80 (see in particular the Fig. 2 and 3 ), which can be screwed to the transmission housing 76.

The helical motor pinion 40 may be pressed onto the motor shaft 38.

To obtain the smallest possible, stable gears, the pinions can have a very small number of teeth. For example, depending on the desired ratio, the motor pinion 40 may have four to seven teeth and the bevel pinion provided with a Gleason toothing may have five teeth, for example, while the straight toothed pinion 54 of the rack-side straight toothed spur gear portion 34 may have seven teeth. For a profile overlap of the teeth of more than 1, this is almost the smallest possible number of teeth. A profile coverage greater than 1 ensures a smooth running of the gear stages, i. before the first tooth is disengaged, the second is already engaged.

The door drive 10 may also include a transformer and control electronics.

The motor 20 drives the toothed rod 28 via the front-bevel gear 30 and via this the output shaft 18 in order to open the door leaf 14 via the lever 24. When closing the door leaf 14, the now-tensioned spring unit 22 drives the front-bevel gear 30 and the motor 20 and rotates the output shaft 18 with the lever 24 in the opposite direction. The engine now operates in generator mode and controls the closing speed and the end impact of the door leaf 14 via the control electronics.

The closing of the door leaf 14 also works normally, which is mandatory for fire door drives.

With the wave-shaped toothed portion 70 of the rack 28 and the non-circular toothed portion 72 of the output shaft 18, a larger torque is generated at smaller opening angles of the door leaf 14 than at larger opening angles, since the pitch circle is smaller. Thus, the required for opening angle of the door in the range between 0 ° and 4 ° high closing torque and required for larger opening angles fast falling door closing torque can be realized even with relatively smaller engines.

LIST OF REFERENCE NUMBERS

10

door drive

12

casing

14

door

16

frame

18

output shaft

20

engine

22

spring unit

24

lever

26

slide

28

rack

30

End-cone gear

32

Motor-side helical spur gear section

34

rack-side straight toothed spur gear section

36

Bevel gear section

37

straight toothed spur gear section

38

motor shaft

40

Helical motor pinion

42

Helical spur gear

44

bevel gear

46

bevel pinion

48

wave

50

ball-bearing

52

ball-bearing

54

straight toothed pinion

56

straight toothed spur gear

58

straight toothed pinion

60

shell

62

thrust

64

contact disc

66

worm gear

68

toothed section

70

wave-shaped toothing section

72

Out-of-round toothed section of the output shaft

74

roller bearing roller, cylinder pin

76

gearbox

77

transmission cover

78

further gear cover

80

end shield

Claims (16)

Door drive (10), in particular revolving door drive, with a housing (12), a drive shaft (18) which can be coupled to a door leaf (14) or a frame (16), a motor (20) for driving the output shaft (18) and a spring unit ( 22), which is tensioned during a respective opening movement of the door leaf (14) and relaxes during a respective closing movement of the door leaf (14), wherein the output shaft (18) via a rack (28) by the motor (20) is driven, the via a front-bevel gear (30) can be acted upon, comprising a motor-side helical spur gear portion (32), a rack-side spur gear spur gear portion (34) and an interposed, in particular provided with a Gleason gearing bevel gear portion (36). Door drive according to claim 1,
characterized in that the helical-toothed spur gear portion (32) on the motor side comprises a helical geared pinion (40) connected to a motor shaft (38) and a helical spur gear (42) meshing therewith. Door drive according to claim 2,
characterized in that the helical spur gear (42) of the motor-side helical spur gear portion (32) consists of a carbon fiber reinforced polyamide-containing material. Door drive according to at least one of the preceding claims,
characterized in that the bevel gear portion (36) comprises a bevel gear (44) meshing bevel pinion (46) which is connected to the helical spur gear (42) of the motor side helical Stirnradgetriebeabschnitts (32). Door drive according to claim 4,
characterized in that the helical spur gear (42) of the motor side helical spur gear portion (32) and the bevel pinion (46) of the bevel gear portion (36) are disposed on a common shaft (48) defined by an axially between the helical spur gear (42) and the bevel pinion (46) arranged ball bearing (50) is supported. Door drive according to claim 5,
characterized in that the with the helical gear (42) of the motor side helical Stirnradgetriebeabschnitts (32) and with the bevel pinion (46) of the bevel gear portion (36) provided by a shaft on the side facing away from the bevel pinion (46) side of the helically toothed Spur gear (42) arranged ball bearing (52) is supported. Door drive according to one of the preceding claims,
characterized in that the bevel gear (44) of the bevel gear portion (36) and the spur gear spur gear (58) of the straight spur gear portion (37) are designed as a one-piece sintered part. Door drive according to one of the preceding claims,
characterized in that the rack-side spur gear sprocket section (34) comprises a spur gear (54) meshing with the rack (28) and a spur gear (56) connected to this spur gear (54) connected to the spur gear (44). the spur gear portion (36) connected spur pinion (58) meshes. Door drive according to claim 8,
characterized in that the straight-toothed pinion (54) and the straight-toothed spur gear (56) of the rack-side straight-toothed spur gear portion (34) are designed as a one-piece sintered part. Door drive according to at least one of the preceding claims,
characterized in that the spring unit (22) comprises a pushed onto the rack (28) compression spring. Door drive according to claim 10,
characterized in that the spring unit (22) between an on the rack (28) pushed axially adjustable sleeve (60) and a thrust washer (64) or the like supported thrust bearing (62) is arranged. Door drive according to claim 11,
characterized in that the sleeve (60) via a worm gear (66) is axially adjustable. Door drive according to at least one of the preceding claims,
characterized in that the toothed rack (28) comprises a toothing section (68) meshing with the spur gear (54) of the rack-side spur gear section (34) and a toothing section (70) arranged in particular on the same side in the region of its opposite end Gearing (72) of the output shaft (18) meshes. Door drive according to claim 13,
characterized in that the toothed rack (28) in the region of their with the spur gear (54) of the rack-side spur gear (34) and the toothing (72) of the output shaft (18) meshing toothing sections (68, 70) respectively over at least one the particular toothed portion (68, 70) facing away from the rack (28) arranged in particular roller bearing roller, cylinder pin (74) or the like is supported. Door drive according to at least one of the preceding claims,
characterized in that the rack (28) comprises a wave-shaped toothed portion (70) which meshes with a non-circular toothing (72) of the output shaft (18). Door drive according to at least one of the preceding claims,
characterized in that at least one pinion has a number of teeth between three and eight teeth.

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