EP1437476B1 - Drive for a wing, especially of a door or a window - Google Patents

Abstract

A closer spring (19) uses a driven shaft (8) to move a door leaf or window casement in a closing direction. While the closer spring is under pre-tension, the leaf/casement opens with a drive motor (2) and closes through the action of the closer spring. A flexible element on a spring plate (20) transfers force between the drive motor and the closer spring.

Description

The invention relates to a drive according to the preamble of patent claim 1.

From the DE 195 00 944 A1 , which is taken into account in the preamble of claim 1, is a drive for a wing, in particular a door or a window, with an electric drive motor, with which the wing is driven at least in the opening direction via an output shaft known. The drive has a closing spring, with which the wing can be driven in the closing direction via the output shaft. The opening of the wing takes place under the action of the drive motor. In this case, the closing spring is biased. The closing of the wing takes place under the action of the closing spring. A flexible power transmission element is used for power transmission between the drive motor and the closing spring. The closing spring is supported with its one end on a stop arranged in the housing and with its other end on a displaceably guided in the housing spring plate. The power transmission element is circumferentially arranged with its one end on a cam circumferentially and fixed with its other end to the spring plate. The power transmission element is designed as a Bowden cable or as a chain.

A disadvantage of using a Bowden cable is that it is subjected to a large bend in conjunction with a cam with a relatively small radius. This leads to a wear of the Bowden cable, through which this may tear under certain circumstances. If you want to avoid this disadvantage when using a Bowden cable, the use of a large diameter cam is required, resulting in a large depth of the drive housing. In strong tensile stress, however, the Bowden cable can also length, which, if necessary, complicated readjustments to maintain proper operation of the drive will be required.

Although a chain is more resistant to wear in comparison to the Bowden cable, it is bulky, so that it requires a relatively large installation space in the housing of the drive. The attachment of the chain to the cam and spring plate is complex, and when winding the chain on the cam results in several superimposed chain layers a large overall diameter of the cam and chain layers, which in turn makes a drive housing with great depth required.

The invention has for its object to provide a generic drive, the flexible power transmission element is low maintenance and wear, is suitable for cams with a small radius and also has a small footprint.

The object is solved by the features of patent claim 1.

The power transmission element is designed as a flat belt. With flat belts small bending radii can be realized, whereby they can also be used in conjunction with small diameter cams. This is essential for achieving compact dimensions of the drive, because the diameter of the cam is decisive for the depth of the drive housing. The fact that flat belts require no lubrication and can reach a very long service life under proper dimensioning, the drive is low maintenance. Another advantage of using a flat belt in the generic drive is that it barely elongates even under heavy tensile stress, in contrast to a Bowden cable. This also leads to a low-maintenance drive.

The outer material of the flat belt may be formed of polyurethane or rubber, but also the use of other suitable materials such as plastic, especially nylon is conceivable. It is essential that the material is flexible and low-wear.

To increase the stability of the flat belt can be embedded in the outer material ropes with high tensile strength, especially Stahlseil- or glass fiber strands.

The assembly of the drive is designed simply by the cam may have a receiving opening for receiving the one belt end of the flat belt, wherein the receiving opening may be formed as a rectangular cross-section, secant-like opening in the edge region of the cam and attachment of the flat belt to the cam so done can, that the belt end is guided into the receiving opening of the cam and is covered by at least one further layer of the flat belt. This results in a fixation of the flat belt to the cam by frictional engagement, wherein on further fasteners, e.g. Screws, can be dispensed with. In particular, caused by the closing spring tension increases this frictional engagement.

Alternatively, the flat belt on the cam can be fixed by an additional fastening device, such as a clamping screw.

The spring plate-side mounting of the flat belt is simple in that the spring plate may have a sleeve with an opening for receiving the other belt end of the flat belt, the attachment of the flat belt on the spring plate may be formed such that the flat belt by at least one jaw in the opening of the Sleeve is fixed.

A particularly secure spring-side assembly of the flat belt can be achieved in that the belt end is passed through the opening of the sleeve, the belt end is guided around a pin to form a loop and is guided in the opposite direction in the opening of the sleeve.

On additional fasteners for fixing the jaw in the opening of the sleeve may optionally be omitted by the cross section the opening of the sleeve is tapered, wherein the jaw is designed to be complementary.

It is essential in the attachment of the flat belt to the cam and the spring plate, the frictional Festlegbarkeit the flat belt is only by frictional, i. without additional fasteners. The flat belt and the cam may have a high friction surface. The frictional determination comes about as soon as the flat belt is subjected to train. This is always the case with mounted drive, since the flat belt is acted upon by the closing spring.

Alternatively, the jaw in the opening of the sleeve in addition by an additional fastening means, such as a clamping screw, can be fixed.

The drive motor can be controlled directly or via an electronic control device. For this purpose, a transmission of the position and the rotational speed of the output shaft to the control device is required. This can be done by means of a rotation angle sensor.

The rotation angle sensor may have one or more switches and cooperate with a non-rotatably mounted on the output shaft contactor. Alternatively, the rotation angle sensor can be arranged at a different location of the drive, for example on the shaft of the drive motor or a transmission element. Here then the use of an incremental encoder or a potentiometer is suitable. Furthermore, the use of a Linearweggebers is conceivable, which measures the position of a linearly movable drive element, such as the spring plate.

In the control device can be stored in particular a wing position-dependent setpoint profile for the opening and closing speed of the wing connected to the drive. The signal of the rotation angle sensor is compared with the respective values of the setpoint profile and the drive motor is driven accordingly. The closing of the wing is under effect the closing spring. Here, the drive motor is operated as a generator and thus slows down the closing process. The braking can be done by direct connection of the drive motor to a constant braking resistor. Optionally, the braking can be canceled shortly before reaching the closed position of the door leaf to realize a so-called "final blow". This can be done via a switch which is operated shortly before reaching the closed position of the door leaf and interrupts the brake circuit. A "comfortable" braking can be done via the control device by the braking resistor can be varied depending on the sash position and speed.

The setpoint profile which can be stored in the control device can be determined during commissioning of the drive as part of a so-called "learning run". The drive motor can be operated with a predetermined power in the opening and closing direction for this purpose. Thus, the parameters required for the operation of the drive, such as opening width and weight (moment of inertia) of the wing can be determined. The set bias of the closer spring can be determined by means of this parameterization process and can be displayed via a suitable display device. Compared to the determined sash weight can then, for example, also by means of the display device, an indication of a reduction or increase in the bias of the closing spring, adjusted to the actual weight of the connected wing, issued.

The control device may be designed such that the operating states which have occurred during normal operation of the drive can be stored in the manner of a protocol. These operating logs can be retrieved, for example, when the drive is serviced by an authorized person.

One way to adjust the spring force is achieved in that the housing-fixed stop for the closing spring is designed as adjusting nut. For this purpose, the adjusting nut has an internal thread which cooperates with the external thread of a threaded sleeve. The threaded sleeve can be a tool intervention have, so that upon rotation of the threaded sleeve, the adjusting nut moves in the spring housing and thus causes a change in the bias of the closer spring.

Fig. 1

die Draufsicht auf die mechanischen Komponenten eines Antriebs (Darstellung ohne Gehäuse);

Fig. 2

eine Schnittdarstellung entlang Linie A - A des Antriebs in Fig. 1;

Fig. 3

eine vergrößerte Darstellung des Antriebs in Fig. 2 im Bereich der Kurvenscheibe;

Fig. 4

eine vergrößerte Darstellung des Antriebs in Fig. 2 im Bereich des Federgehäuses;

Fig. 5

eine gegenüber Fig. 4 abgewandelte Ausführung des Antriebs in vergrößerter Darstellung im Bereich des Federgehäuses;

Fig. 6

eine gegenüber Fig. 4 und 5 abgewandelte Ausführung des Antriebs in vergrößerter Darstellung im Bereich des Federtellers.

In the following, exemplary embodiments are explained in more detail in the drawing with reference to FIGS. Showing:

Fig. 1

the top view of the mechanical components of a drive (representation without housing);

Fig. 2

a sectional view taken along line A - A of the drive in Fig. 1 ;

Fig. 3

an enlarged view of the drive in Fig. 2 in the area of the cam;

Fig. 4

an enlarged view of the drive in Fig. 2 in the area of the spring housing;

Fig. 5

one opposite Fig. 4 modified version of the drive in an enlarged view in the region of the spring housing;

Fig. 6

one opposite Fig. 4 and 5 modified version of the drive in an enlarged view in the region of the spring plate.

Fig. 1 shows the mechanical components of a drive 1, wherein the housing of the drive 1, within which these components are arranged, for reasons of clarity, is not shown here. The drive 1 has a rotatable, designed as an output shaft 8 output member and is arranged in a known manner on or in a pivotally mounted wing or on or in a stationary frame, wherein a non-illustrated force-transmitting linkage rotatably connected to the output shaft 8 is connected.

On the motor shaft of the drive motor 2, a screw 3 is rotatably mounted, which meshes with a first, rotatably mounted on a shaft 5 mounted in the drive gear 4. On this shaft 5, a second gear 6 is rotatably disposed whose diameter is smaller than that of the first, meshing with the screw 3 gear 4. This smaller gear 6 meshes with a third, On the output shaft 8 of the drive 1 rotatably mounted gear 7, the diameter of which is larger than that of the second gear 6. Also rotatably on the output shaft 8, a cam 9 is arranged, on which a flat belt 10 is guided peripherally wraparound. The flat belt is inserted through an opening in a spring housing 11.

A cooperating with a rotational angle sensor 13 contactor 12 is rotatably mounted on the output shaft 8. The contactor 12 may be formed as a cam and the rotation angle sensor 13 as actuated by the cam, electrical switch, possibly also from a combination of several switches. Also, use of other types of suitable rotation angle sensors, e.g. Incremental encoder or potentiometer is conceivable, as is an arrangement elsewhere in the drive, e.g. on the shaft of the drive motor 2 or as a linear encoder in the spring housing. The output of the rotation angle sensor 13 is supplied to a controller of the drive. The contactor 12 may be adjustable relative to the output shaft 8 such that at a desired position of the movable blade connected to the drive 1, e.g. When the same is completely opened, an output signal of the rotation angle sensor 13 is generated and the drive motor 2 is then switched off via the control device.

The interior of the spring housing 11 is in Fig. 2 recognizable. On the side facing the drive motor 2 side of the elongate spring housing 11, a lid 17 is arranged. Through a central opening of the cover 17 therethrough, the adjusting device 15 of a threaded sleeve 16 extends out of the spring housing 11 to the outside. The threaded sleeve 16 has an annular collar, which is supported within the spring housing 11 on the lid 17. The area of the threaded sleeve 16 extending into the interior of the spring housing 11 has an external thread which cooperates with the internal thread of an adjusting nut 18. The adjusting nut 18 is displaceable parallel to the longitudinal axis of the spring housing 11, but secured by means of an anti-rotation device, not shown, against rotation relative to the spring housing 11. The adjusting 15 of the threaded sleeve 16 can be used as a hexagon for engagement be formed of a corresponding tool. A rotation of the threaded sleeve 16 thus causes a displacement of the adjusting nut 18 parallel to the longitudinal axis of the spring housing eleventh

On the adjusting nut 18, one end of a closing spring formed as a helical spring 19 is supported. The other end of the closing spring 19 is supported on a further, parallel to the longitudinal axis of the spring housing 11 displaceable spring plate 20. This spring plate 20 has a central opening for receiving and fixing the other belt end 29 of the flat belt 10. The flat belt 10 extends through an opening 14 of the threaded sleeve 16 into the spring housing 11 and extends toward the spring plate 20 concentrically within the turns of the closing spring 19. The closing spring 19 acts on the spring plate 20 in the drawing to the right, so that a tensile stress of Flat belt 10 results. The above-described adjustment 15 of the threaded sleeve 16 allows adjustment of the bias of the shutter spring 19th

If the drive motor 2 is energized in the opening direction, it causes a rotation of the output shaft 8 in the counterclockwise direction via the gear consisting of the worm 3 and the gears 4, 6, 7. About the power transmitting linkage, not shown, this rotational movement of the output shaft 8 is converted into an opening movement of the movable wing. The rotational movement of the output shaft 8 causes by the rotationally fixed coupling with the cam 9 a same direction rotational movement of the same. The flat belt 10 is thus pulled out of the spring housing 11 and wound on the cam 9. Simultaneously, the flat belt 10 pulls the spring plate 20 under compression of the shutter spring 19 in the drawing to the left.

If the energization of the drive motor 2 is canceled, the then relaxing closing spring 19 causes a movement of the spring plate 20 in the drawing to the right. The flat belt 10 fixed to the spring plate 20 is drawn into the spring housing 11 with a relaxing closing spring 19, wherein it unwinds from the cam 9 and a movement thereof clockwise. The rotatably coupled to the cam 9 output shaft 8 thus rotates in the same direction in a clockwise direction. About the power transmission linkage, not shown, this rotational movement of the output shaft 8 is converted into a closing movement of the movable wing. About the from the screw 3 and the gears 4, 6, 7 existing gear, the rotational movement of the output shaft 8 is converted into a rotational movement of the motor shaft of the drive motor 2. The drive motor 2 can act as a generator and thus slow down the closing process.

Out Fig. 3 the attachment of the flat belt 10 on the cam 9 can be seen. The cam 9 has a receiving opening 26, which is formed as located in the edge region of the cam 9, secant-like opening in the cam 9. The cross section of the receiving opening 26 is rectangular and slightly larger than the cross section of the flat belt 10. When mounting the drive, the belt end 24 of the flat belt 10 is inserted into the receiving opening 26 and fixed with a screw 25. On the screw 25 may possibly even be dispensed with, because after a complete rotation of the cam 9 in the counterclockwise direction additionally results in a fixation of the superposed layers of the flat belt 10 by frictional engagement, so that the belt end 24 of the flat belt 10 also hereby against slipping out of the receiving opening 26 of the cam 9 is secured.

Fig. 4 and Fig. 5 show in each case the area of the spring housing 11 of the drive in an enlarged view, namely two embodiments of the fixation of the flat belt 10 on the spring plate 20. The spring plate 20 each has a sleeve 27 with a central bore through which the flat belt 10 is guided. During assembly of the drive, the belt end 29 of the flat belt 10 is guided through this bore. Subsequently, the belt end 29 is guided around a pin 21 to form a loop 22 and again inserted into the bore of the sleeve 27, so that in the region of the bore of the sleeve 27 two layers of the flat belt 10 are superimposed.

In the execution according to Fig. 4 is the bore in the sleeve 27 of the spring plate 20 of constant diameter. The superimposed layers of the flat belt 10 are fixed by means of two clamping jaws 23, which are clamped by an adjustable in a threaded bore of the sleeve clamping screw 28 against the bore of the sleeve 27.

In the execution according to Fig. 5 can be dispensed with a clamping screw. The bore in the sleeve 27 tapers towards the interior of the spring housing 11, wherein the two jaws 23 are formed to be chamfered complementary to the taper of the bore. Characterized in that the spring plate 20 is acted upon by the closer spring 19 in the drawing to the right, the clamping jaws 23 are pressed with the intermediate layers of the flat belt 10 in the tapered inner surface of the bore of the sleeve 23. This results in a frictional connection and thus a fixation of the flat belt 10 on the spring plate 20th

In both embodiments, the sling 22 of the flat belt 10 with the pin 21 therein additionally prevents slipping out of the belt end 29 of the flat belt 10 from the spring plate 20.

Fig. 6 shows a further embodiment of the fixation of the flat belt 10 on the spring plate 20 in an enlarged view. The belt end 37 of the flat belt 10 is clamped between the clamping surfaces 32, 35 of two jaws 30, 33. The jaws 30, 33 are each formed in accordance with a half truncated cone, so that in the mounted state, ie at opposite clamping surfaces 32, 35 and intermediate belt end 37 a frusto-conical overall shape of the surfaces 31, 34 of the jaws 30, 33 results, the diameter of Truncated cone in the drawing slightly increases to the right. The spring plate 20 is annular, wherein its inner diameter is greater than the smallest diameter of the truncated cone formed by the clamping jaws 30, 33 and smaller than the largest diameter of this truncated cone. The clamping is thus achieved in that the acted upon by the closing spring 19 spring plate 20 is pressed in the drawing to the right, wherein he comes into contact with the surfaces 31, 34 of the jaws 30, 33 and compresses them, whereby the lying between the clamping surfaces 32, 35 belt end 37 of the flat belt is clamped. The clamping surfaces 32, 35 may have a friction-increasing configuration of their surface, for example a corrugation, or a coating with a high coefficient of friction. A subsequently mounted in the region of the smallest diameter of the truncated cone formed by the jaws 30, 33 ring 36 secures the clamp connection in addition.

In addition to the previously described truncated cone shape of the clamping jaws 30, 33, other shapes, for example a wedge shape, are also conceivable.

List of reference characters

1

drive

2

drive motor

3

slug

4

gear

5

wave

6

gear

7

gear

8th

output shaft

9

cam

10

flat belts

11

spring housing

12

contactor

13

Rotation angle sensor

14

opening

15

adjustment

16

threaded sleeve

17

cover

18

adjusting nut

19

closer spring

20

spring plate

21

bolt

22

loop

23

jaw

24

strap end

25

screw

26

receiving opening

27

shell

28

clamping screw

29

strap end

30

jaw

31

surface

32

clamping surface

33

jaw

34

surface

35

clamping surface

36

ring

37

strap end

Claims (15)

1. Drive (1) for a leaf, in particular of a door or of a window,
   having an electric drive motor (2) with which the leaf can be driven in the opening direction by means of an output shaft (8),
   having a closing spring (19), which is arranged in a housing (11), with which the leaf can be driven in the closing direction by means of the output shaft (8), with the leaf being opened under the action of the drive motor (2) and in the process the closing spring (19) being prestressed, and with the leaf being closed under the action of the closing spring (19), and having a flexible force-transmitting element for transmitting force between the drive motor (2) and the closing spring (19),
   with the closing spring (19) being supported by way of one of its ends against a stop which is arranged in the housing (11) and by way of its other end against a spring plate (20) which is displaceably guided in the housing (11), and
   with the force-transmitting element being arranged by way of one of its ends such that it wraps around the circumference of a cam disc (9) which is arranged in a rotationally fixed manner on the output shaft (8), and being fixed by way of its other end to the spring plate (20),
   characterized
   in that the force-transmitting element is in the form of a flat belt (10).
2. Drive according to Claim 1,
   characterized in that the cam disc (9) has an accommodation opening (26) for accommodating one end (24) of the flat belt (10).
3. Drive according to Claim 2,
   characterized in that the flat belt (10) is fastened to the cam disc (9) in such a way that the belt end (24) is inserted into the accommodation opening (26) in the cam disc (9) and the accommodation opening (26) is covered by at least one further layer of the flat belt (10).
4. Drive according to Claim 1,
   characterized in that the spring plate (20) has a sleeve (27) with an opening for accommodating the other end (29) of the flat belt (10).
5. Drive according to Claim 4,
   characterized in that the flat belt (10) is fastened to the spring plate (20) in such a way that the flat belt (10) can be fixed by at least one clamping jaw (23) in the opening in the sleeve (27).
6. Drive according to Claim 4,
   characterized in that the flat belt (10) is fastened to the spring plate (20) in such a way that the belt end (29) is guided through the opening in the sleeve (27), the belt end (29) is guided around a pin (21) so as to form a loop (22) and is inserted into the opening in the sleeve (27) in the opposite direction.
7. Drive according to Claim 6,
   characterized in that the cross section of the opening in the sleeve (27) is of tapering design, with the clamping jaw (23) being formed in a complementary manner.
8. Drive according to Claim 6,
   characterized in that the clamping jaw (23) can be fixed in the opening in the sleeve (27) by a clamping screw (28).
9. Drive according to Claim 1,
   characterized in that the spring plate (20) has an opening for accommodating clamping jaws (30, 33).
10. Drive according to Claim 9,
    characterized in that the clamping jaws (30, 33) have facing clamping faces (32, 35) between which one end (37) of the flat belt (10) can be clamped.
11. Drive according to Claim 9,
    characterized in that the clamping jaws (30, 33) have outer faces (31, 34) in the form of a truncated cone.
12. Drive according to Claim 11,
    characterized in that the spring plate (20) is annular, with the inside diameter of the spring plate (20) being greater than the smallest diameter of the truncated cone which is formed by the clamping jaws (30, 33) and is smaller than the largest diameter of the truncated cone which is formed by the clamping jaws (30, 33), so that the spring plate (20) rests on the outer faces of the clamping jaws (30, 33) and the end (37) of the flat belt (10) is clamped between the clamping jaws (30, 33).
13. Drive according to Claim 9,
    characterized in that the clamping jaws (30, 33) have wedge-shaped outer faces (31, 34).
14. Drive according to Claim 1,
    characterized in that the stop, which is arranged in the housing, for the closing spring (19) is adjustable.
15. Drive according to Claim 14,
    characterized in that the stop, which is arranged in the housing, for the closing spring (19) is in the form of an adjusting nut (18) which can be adjusted by means of a threaded sleeve (16).

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