CH701926B1 - Swing Door Operator with cam. - Google Patents

Abstract

The invention relates to a swing door operator with cam for opening and closing a door, which has the following features: a motor drive unit (5); an output shaft (19) which drives via at least one receiving bush (36) at least indirectly via a linkage with lever and bearing block to a moving wing of a door; the drive unit (5) has a drive connection with the output shaft (19); at least one force accumulator (28), which presses a rotatably mounted roller (23) via a pressure member (25) connected to the force accumulator (28) and fixedly connected to the roller axle (24) on the peripheral surface of a cam disc (20), and the cam disc (20) is non-rotatably connected to the output shaft (19). The invention is characterized in that the swing door operator when changing from a pulling to a pushing rod mutually rotatable by 180 ° and has a bilateral Ankoppelungsmöglichkeit, where necessary, different ratios of the different types of linkage, namely slide rail or normal linkage, by shifting a start position (43 , 44) are formed on the same cam (20).

Description

The invention relates to a swing door operator with cam according to the preamble of claim 1.

The invention provides in this case a rotary vane drive with a cam and power storage before. This cam generates an uneven closing or opening torque in the opposite direction to the motor drive. This is to ensure that the door automatically closes or opens via a linkage coupled to the drive, even in the event of a power failure.

In the art, such cams with energy storage for a long time in door closers known (namely in door closers from Dorma). There are certainly door closers that have been converted into door drives (with motor supplements), especially Dorma.

In the document EP 1 505 242 A1 (Agtatec) two drainage surfaces are used to use without changing the device or the mounting situation pulling and pushing linkage for the door opening or to drive swing doors.

However, this is disadvantageous because due to the use of two drain surfaces to use an advantageous Absolutweggeber for detecting the door position for the motor operation twice as large travel angle, even if no swing door is driven.

In the inventive construction is provided that the swing door door drive when changing from a pulling to a pushing rod mutually rotatable by 180 ° and has a bilateral Ankoppelungsmöglichkeit, where necessary, different ratios of the different boom types (slide / normal linkage) by shifting a Start position are formed on the same cam.

In a preferred embodiment of the invention, the structure of the device is described as follows: There are 2 identical cams installed with spring-loaded rollers that work in parallel. This results in smaller and evenly distributed forces that can be set very fine, on the other hand, the biasing forces of the two springs can also be set independently. They are easily readable by the position of a bolt. The key point is that only a single, fixed curve shape is needed for the various common linkage types, i. H. The device can be manufactured in a single design and thus the requirements of the standards are met.

The output shaft is located in the center of the device and can be attacked on both sides, thereby the other direction of rotation is achieved by reverse assembly of the device, without the device's internal direction of rotation or visually changes something.

The desired effect of the cam generally is the achievement of a large clamping force with the lever with slide rail, as you can achieve with a normal rod and at the same time eliminate the effect that the highest spring force, which should ensure that the Door in the event of a power failure moved to the defined end position (normally the door closes), the engine is not so heavily loaded (critical for permanent opening). What is new about this device is the idea of using the different sections of the identical curve for the different linkages.

The invention deliberately takes into account that can not be driven with the given technical teaching swing doors, because this is required that different running surfaces are available on the cams. The invention dispenses with this in favor of a simpler production and a cost-effective Absolutweggebers and a cost-effective cam.

In the subject matter of EP 1 505 239, therefore, depending on the installation position of the drive, only one circumferential or run-off surface area or the other circumferential or run-off surface area must be effective in the adjustment of the rotary vane in the case of a wing to be opened only in one direction.

This is avoided in the present invention.

In the present invention, always only a single run-off area (run-off curve) of the cam is always run through, regardless of the installation position of the rotary vane drive.

To convert the rotary vane drive of a pulling drive (lever with slide) on a pressing drive (so-called normal linkage), it is provided that the entire drive housing is turned by 180 degrees attached to a mounting surface and that, moreover, the drive shaft of the rotary vane drive is led out axially on both sides of the housing to couple the respective linkage either on one side with the drive shaft or on the opposite side with the same drive shaft.

It is not necessary for the solution to lead out the output shaft permanently from the housing of the rotary vane drive. It is sufficient to provide a corresponding polygonal receptacle in the drive shaft, in which then a correspondingly adapted profiled stub shaft is used, which is coupled to the receiving socket on the rod for the door.

With the given technical teaching so there is the significant advantage that a very simple cam can be used and that this cam is only ever traversed in the same run-flat area, which is not the case in the prior art.

An ideal torque curve provides that at a door opening angle of about 0 degrees, a very large closing moment acts and with increasing door opening angle of this closing torque is smaller and runs essentially on a parabolic curve.

Important in the invention is now that this ideal torque curve is achieved with a single cam shape, regardless of whether a pulling or a pushing door drive is used.

In one embodiment of the invention, a so-called tandem arrangement is provided, which is claimed as essential to the invention, regardless of the former feature and also in combination therewith.

The so-called tandem arrangement according to the invention is that two absolutely symmetrical cams are arranged rotatably on the common drive shaft and that acts on each cam an associated role with an associated compression spring. This means that all parts are duplicated, namely the drive pulley, the roller and the associated thrust washer of the compression spring, so that it is a tandem arrangement.

The two rollers are rotatably mounted on a common roller axle, wherein on the outer circumference of the roller axle each having a different pressure piece acts, which receives one end of the respective compression spring, while the other, opposite end of the compression spring is accommodated in a spring plate, the each separately adjustable by an associated clamping screw.

In this way, each compression spring and thus also the pressure force of each compression spring can be set separately to the cam with the tandem arrangement shown. It can thus be made an absolutely symmetrical load case, so that at very high pressure forces (because of the use of two parallel compression springs) a relatively small travel is achieved with low insertion length at high pressure forces. Thus, very high closing or opening forces are achieved in a small space, as they were not possible in the prior art.

The state of the art (for example in the form of EP 1 505 239 A1) still uses an associated lever system for transmitting the spring force of the single compression spring, which makes the asymmetrical arrangement as a whole more prone to repair, more susceptible to wear and more complicated. These disadvantages are avoided by the invention and instead provide an absolutely symmetrical pressure system in the form of a tandem arrangement.

In the following the invention will be explained in more detail with reference to drawings showing only one embodiment. Here are from the drawings and their description further features essential to the invention and advantages of the invention.

In the drawings: <Tb> FIG. 1: <sep> Center longitudinal section through a rotary vane drive according to the invention; <Tb> FIG. 2: <sep> perspective view of the rotary vane drive of FIG. 1; <Tb> FIG. 3: <sep> horizontal section through the rotary vane drive of FIG. 1; <Tb> FIG. 4: <sep> section through the arrangement of Figure 3in height of the roller axis. <Tb> FIG. 5: <sep> Cross section through the arrangement in the amount of the motor shaft of the drive motor; <Tb> FIG. 6: <sep> section at the height of the output shaft; <Tb> FIG. 7: <sep> schematizes the representation of a lever linkage for a pulling door drive; <Tb> FIG. 8: <sep> the gear ratio for the pulling door drive without using the inventive rotary vane drive; <Tb> FIG. 9: <sep> schematizes the representation of a standard linkage for the pushing door drive; <Tb> FIG. 10: <sep> the gear ratio for the pushing door drive with respect to the door opening angle; <Tb> FIG. 11: <sep> the torque curve of the inventive rotary vane drive with pulling and pushing drive based on the angle at the output shaft; <Tb> FIG. 12: <sep> a spring moment curve resulting in the pulling door drive with the measures of the invention; <Tb> FIG. 13: <sep> the spring moment curve, which results in the oppressive door drive with the measures of the invention.

1 and 2 it is shown that the vane drive consists essentially of a U-shaped profiled carrier sheet 1, which carries a number of modules in itself.

In the rear region according to FIG. 2, the spring block 2 is arranged, to which a cam module 3 adjoins, wherein the control module 4 is also arranged in the housing of the carrier plate.

The entire carrier sheet 1 is fixed by means of associated wall fasteners 51 on a mounting surface, this mounting surface is e.g. a wall or a door.

In order to convert the entire rotary vane drive from a pulling into a pushing drive according to the invention, it is provided according to the invention that the entire carrier plate 1 is turned by 180 degrees in the direction of the arrow 52 and all parts remain the same. It is important that only the receiving socket 36 (see Figs. 7 and 9) is flanged for the attack of the transmission linkage either on one side of the output shaft 19 or on the opposite side of the same output shaft 19.

In the lower region of the support plate 1 in this case a motor 5 is arranged, which acts with its output shaft 19 on an encoder 6, which generates an electrical signal in dependence on the rotational speed of the motor. Thus, the motor 5 is commutated and further detects the relative position of the motor shaft 7 to the support plate 1.

Non-rotatably with the motor shaft 7, a ball screw 8 is fastened by the way, which passes through a spindle nut 10 which is fixedly connected to a rack 11. The rack 11 is in this case according to FIG. 6 formed as an approximately U-shaped part and runs on a preferably made of plastic rack guide 15th

The motor shaft 7 is rotatably mounted in front and rear fixed to the housing 9 bearings.

The teeth 12 of the rack 11 meshes positively with the teeth 22 of an output shaft 19 which is rotatably supported by means of two mutually opposite bearings 21 in the support plate 1.

The output shaft forms frontally profiled receptacles in which associated, profiled shaft stumps can be inserted, which form-fitting manner in the associated receiving sockets 36 of the linkage of FIG. 7bzw. 9eingreifen.

Thus, the respective free end of the associated linkage according to FIGS. 7 and 9 rotatably coupled to the output shaft 19 either on one side or the other.

The output shaft 19 is non-rotatably connected to a respective cam 20, so that a total of two spaced-apart cams 20 are provided which are formed exactly symmetrical to each other, so that a precisely centered pressure force is transmitted to the output shaft 19. This does not lead to tilting and the entry of bending moments, as they must be feared in the prior art.

The cams are - as stated - absolutely identical and form identical flow curves 47, on which roll off associated rollers 23 spring loaded.

It will be added that a displacement measuring system for the displacement of the rack 11 is provided. This displacement measuring system consists of a plunger 13 fixedly connected to the rack, which is in juxtaposition to an absolute displacement sensor 14 oriented in the axial displacement direction.

This Absolutweggeber 14 is formed for example as a sliding potentiometer and depending on the displacement of the rack thus an absolute displacement measurement for this shift is detected.

Thus, there are two associated path measuring systems, namely once the measuring system via the encoder 6 and the second of the Absolutweggeber 14th

These are therefore redundant path measuring systems, so that even if the other Wegmesssystem one of the failure of the one wayfinding system still works. This increases the reliability of the entire arrangement. The same redundancy advantage is also in the said tandem arrangement of acting as a force storage springs 28, because they are also present in absolutely parallel arrangement and are individually adjustable independently. In case of breakage or failure of a compression spring 28, consequently, the contact pressure of the other compression spring 28 is still sufficient to achieve an orderly closing or opening movement.

The arrangement of these two compression springs has the advantage that absolutely symmetrical forces on each separately arranged pressure piece 25 is entered.

Thus, there are two pressure pieces 25 provided with associated lugs 27, on each of which a spring end of the two compression springs 28 is attached.

Each pressure piece 25 is coupled via one or more pins 26 with the common roller axis 24, on which in turn the aforementioned rollers 23 are rotatably mounted.

Over the pins 26 is thus achieved a displacement assurance of the plungers 25 as a backup against axial displacement.

After a common roller axle 24 is used, this roller axle can adjust freely with the associated rollers 23 to the flow curves 47 on the respective cam 20.

This is also the separate adjustability of each compression spring 28. It is provided that the rear end of each compression spring 28 is seated on a spring plate 30 and that each spring plate with an associated, separate clamping screw 31a, 31b is adjustable. In this way, possibly different compressive forces with differently dimensioned compression springs 28 are taken into account.

In order to observe a displacement of the compression springs 28 and to allow a precisely the same setting, it is provided that on each spring plate 30, a bolt 32 is arranged, which extends through an associated slot 33 in the rear part of the support plate 1 and from the outside is observable.

Thus, a displacement of the spring plate by means of the clamping screws 31a, 31b observed from the outside and be fine adjusted.

According to the invention also a stop limit for the displacement of the rack 11 is provided. The rack can thus strike in its foremost position against a stop 17 in the axial direction in a stop bracket 16 adjustable.

The stop 17 is in this case held by means of a thread 18 in the stop bracket 16 adjustable.

Different lever linkages will now be described with reference to FIGS. 7 and 9.

Fig. 7 shows a lever linkage with slide for a pulling door drive. Here, a slide rail 34 may be mounted either on the door or on a wall. If the slide rail 34 is mounted on a door, then a door bearing block 40 is slidably guided in the slide rail 34 and rotatably on the door bearing block 40 sets this one end of a lever 35, at its opposite free end a receiving socket 36 for the rotationally fixed coupling with the Output shaft 19 is arranged.

Conversely, it can of course also be provided that the slide rail 34 is mounted on a wall mounting surface.

In Fig. 9, a so-called normal linkage is shown. It can be seen that the door bearing block 40 is fixedly attached to a door leaf, and a lever 37 engages via a pivot bearing on the door bearing block 40.

The other end of the lever 37 is coupled via a further pivot bearing 39 with a lever 38, at its free front end, in turn, the receiving socket 36 is provided for coupling to the output shaft 19.

Based on the pulling drive a door results in a gear ratio according to FIG. 8. There it can be seen that a ratio of 0 to 2.5 is plotted on the ordinate. Here, the torque, which brings the drive, transmitted in a certain ratio to the door. The linkage shown in FIG. 7 serves this purpose.

Disadvantageously, Fig. 8nun shows that based on a door opening angle in the range of 0 to 100 degrees, a relatively constant gear ratio is given. This is considered to be disadvantageous because it is desirable to achieve a relatively high opening or closing moment when opening the door (near a door opening angle of 0 degrees) .This is not possible with such a pulling lever linkage.

This is where the invention, which generates novel torque ratios, as will be explained later with reference to FIG. 11.

First, however, reference is made to Fig. 10, where the gear ratio of a lever linkage for the pushing door drive is shown. This transmission ratio is preferred in and of itself and should be modeled with the measures of the invention according to FIG. 11.

Fig. 12 shows that when overflowing the flow curve 47 from a position 43, a torque curve of Fig. 12in arrow direction 45 is traversing, already at the start position 43, a relatively high torque is generated, which is desirable.

Fig. 13 shows the same ratio in a pushing door drive, where it can be seen that even a much higher torque at the start position 44 is achieved for a pushing door drive. This is also desirable in the sense of the invention.

11 now shows how it comes to the two desired torque curves of FIGS. 12 and 13.

It is important that there is a single torque curve 53 of FIG. 11, wherein for the pulling door drive a starting point at position 43 in the torque curve 53 is traversed, while for the oppressive drive only a later starting point, namely at position 44 is going through.

It follows that one and the same torque curve is used for both the pulling and the pushing operation and only the starting points 43 and 44 are shifted from each other for the respective operating modes. This is a significant advantage over the prior art, because it follows that always only one and the same flow curve 47 on the absolutely identical cam 20 (tandem cam) is traversed. Therefore, it will not go through different flow areas and differently shaped flow curves.

This makes the production of the two cams 20 particularly simple and enables a particularly wear-resistant operation.

From the comparison of FIGS. 8 and 12 it can be seen that the intrinsically disadvantageous position 46 is now raised by the measures according to the invention and instead a position 43 is reached, ie. an improvement of the torque curve at the door opening.

FIG. 13 shows that the start position for the normal linkage (position 44) of the ideal curve of FIG. 10 is approximated.

The cam 20 here rotates in the direction of arrow 48 (counterclockwise), wherein the position 43 indicates the starting position for the pulling drive, while the position 44 indicates the starting position for the oppressive drive.

The end position of the flow curve 47 then results at position 50. In this position, the door is then fully open, for example.

The curves shown in FIGS. 8, 10, 12 and 13 show the torque curves and gear ratios for the closing of the door under the action of the pressure springs 28 arranged in tandem. It is not crucial whether an engine is present or not. The above-mentioned curves, in particular in FIGS. 11 to 13, show the effect of the two tandem compression springs 28. The illustrated torque curves therefore show the door closing without a motor.

Under the action of the motor 5 and the rotary drive of the output shaft 19 so the door is opened and closed as a whole, but with the special torque characteristic, as explained with reference to FIGS. 11 to 13, additionally acts by the tandem compression springs 28.

In principle, the motor 5 opens the door, and he can of course also generate a closing moment when closing the door in special cases.

The ideal curve of Fig. 10 is desired when the entire system is de-energized. For this reason, the previously described tandem arrangement, consisting of two cams and two arranged in tandem compression springs 28 was selected.

drawing Legend

[0075] <Tb> 1 <sep> carrier plate <Tb> 2 <sep> spring block <Tb> 3 <sep> cam module <Tb> 4 <sep> control module <Tb> 5 <sep> Engine <Tb> 6 <sep> Encoder <Tb> 7 <sep> motor shaft <Tb> 8 <sep> ball screw <Tb> 9 <sep> Bearings <Tb> 10 <sep> spindle nut <Tb> 11 <sep> rack <Tb> 12 <sep> Gear <Tb> 13 <sep> ram <Tb> 14 <sep> absolute position <Tb> 15 <sep> rack guide <Tb> 16 <sep> Support holder <Tb> 17 <sep> stop <Tb> 18 <sep> Thread <Tb> 19 <sep> output shaft <Tb> 20 <sep> cam <Tb> 21 <sep> Storage <Tb> 22 <sep> Gear <Tb> 23 <sep> Role <Tb> 24 <sep> roller axis <Tb> 25 <sep> thrust piece <Tb> 26 <sep> Pin <Tb> 27 <sep> Approach <tb> 28 <sep> Pressure spring acting as energy storage <Tb> 29 <sep> - <Tb> 30 <sep> spring seat <tb> 31 <sep> Tightening screw a, b <Tb> 32 <sep> Bolts <Tb> 33 <sep> slot <Tb> 34 <sep> slide <Tb> 35 <sep> Lever <Tb> 36 <sep> receiving bush <Tb> 37 <sep> Lever <Tb> 38 <sep> Lever <Tb> 39 <sep> pivot <Tb> 40 <sep> pedestal <Tb> 41 <sep> - <Tb> 42 <sep> - <tb> 43 <sep> position (starting position sliding linkage) <tb> 44 <sep> position (start position normal linkage) <Tb> 45 <sep> arrow <Tb> 46 <sep> Position <Tb> 47 <sep> expiration curve <Tb> 48 <sep> arrow <Tb> 49 <sep> - <tb> 50 <sep> position (full open position) <Tb> 51 <sep> Wall mounting <Tb> 52 <sep> arrow <Tb> 53 <sep> torque curve

Claims (18)

1. swing door operator with cam for opening and closing a door, which has the following features: - A motor drive unit (5); - An output shaft (19) via at least one receiving socket (36) at least indirectly via a linkage (34-36, 40, 36-40) with levers (35, 37, 38) and bearing block (40) to be moved a wing Door drives; - The drive unit (5) has a drive connection with the output shaft (19); - At least one energy storage device (28) which a rotatably mounted roller (23) via a with the energy storage (28) connected and with the roller axle (24) fixedly connected pressure piece (25) on the peripheral surface of a cam (20) presses, and - The cam (20) is non-rotatably connected to the output shaft (19), characterized in that the swing door drive when changing from a pulling to a pushing linkage mutually rotatable by 180 ° and has a bilateral Ankoppelungsmöglichkeit, where necessary, different ratios of the various Linkage types, namely slide rail linkage (34-36, 40) or normal linkage (36-40), by means of displacement of a start position (43, 44) on the same cam (20) are formed. 2. swing door operator according to claim 1, characterized in that it is formed of a plurality of modules having a U-shaped support plate (1), a spring block (2), a cam module (3) and in the housing of the support plate (1). arranged control module (4). 3. swing door drive according to claim 1 and 2, characterized in that the rotary vane drive two identical and parallel cam plates (20) with spring-loaded rollers (23), wherein the biasing forces acting as a force storage compression springs (28) independently by means of a clamping screw (31 a , 31b) are formed adjustable. 4. swing door drive according to claims 1 to 3, characterized in that for the various types of linkage, the cam (20) has only a single, fixed embodiment. 5. swing door operator according to claims 1 to 4, characterized in that the output shaft (19) is formed on both sides coupled, whereby a different direction of rotation by means of reverse assembly of the swing door drive is formed. 6. swing door operator according to claims 3 to 5, characterized in that the motor (5) has a reduced load at maximum spring force of the compression spring (28). 7. swing door operator according to claims 1 to 6, characterized in that it automatically opens or closes a door in case of power failure. 8. swing door operator according to claims 1 to 7, characterized in that regardless of the mounting position of the rotary vane drive only a single flow curve (47) or drain area (47) of the cam (20) is traversed. 9. swing door drive according to claims 3 to 8, characterized in that the force of the compression spring (28) is centered on the cam (20) and forms stable flow conditions. 10. swing door operator according to claims 3 to 9, characterized in that the non-rotatable arrangement of two symmetrical, spaced cams (20) on a roller axle (24) with the corresponding two associated rollers (23) and with the two the compression springs (28 ) associated pressure pieces (25) form a tandem arrangement. 11. swing door operator according to claims 3 to 10, characterized in that two parallel compression springs (28) are provided which form a symmetrical load case, the pressure force of each compression spring (28) on the corresponding cam (20) is separately adjustable, and in case of failure of a spring (28) is sufficiently dimensioned. 12. swing door operator according to claims 1 to 11, characterized in that the torque curve (53) substantially forms a parabolic curve. 13. swing door operator according to claims 2 to 12, characterized in that the output shaft (19) of the motor (5) acts on an arranged encoder (6) which generates an electrical signal in dependence on the rotational speed of the motor (5) the motor (5) commutes and further detects the position of the motor shaft (7) to the support plate (1), wherein the motor shaft (7) rotatably connected to a ball screw (8), which passes through a spindle nut (10) and fixed with an approximately U-shaped rack (11) is connected and runs in a rack guide (15). 14. swing door drive according to claim 13, characterized in that the rack (11) has a toothing (12) which positively engages a on the output shaft (19) arranged toothing. 15. Swing door drive according to claims 13 to 14, characterized in that a displacement of the rack (11) is detected by means of a displacement measuring system, one with the rack (11) fixedly connected plunger (13) in juxtaposition to an aligned in the axial displacement direction Absolutweggeber (14) and forms a redundant position measuring system together with the measuring system via the encoder (6). 16. Swing door drive according to claims 3 to 15, characterized in that a displacement of the compression springs (28) by means of separately on the respective spring plate (30) arranged bolt (32) is detectable from the outside, wherein the bolt (32) has an associated slot (33) in the rear part of the support plate (1) protrude. 17. Swing door drive according to claims 1 to 16, characterized in that the pressure pieces (25) are secured by means of arranged pins (26) against axial displacement on the roller axis (24). 18 swing door operator according to claims 3 to 17, characterized in that the identically designed cams (20) for pulling and pushing linkage same flow curves (47) which by shifting the respective starting points (43, 44) against each other equal torque curves (53) run through.