DE29711278U1 - Gearbox for reversible rotary drives for driving a gate with different opening and closing speeds - Google Patents

Description

Gearbox for reversible rotary drives for driving a gate with different opening and closing positions.

Closing speed

The invention relates to an automatic transmission for reversible rotary drive elements, in particular for motors with a fixed speed in both directions of rotation, for driving a gate with different opening and closing speeds. Such a transmission consists of a transmission frame or housing for rotatably receiving the transmission parts, a drive member for directly or indirectly connecting the transmission to the rotary drive element in a rotationally fixed manner, an output member that follows each reversal of the direction of the drive member, a transmission connection consisting of transmission members acting between the drive member and the output member, and at least two transmission shafts for receiving (carrying) the transmission members.

When driving gates, but also when lifting and lowering loads in general, it is sometimes desirable to open or lift the load using another, in particular

D-40239 DÜSSELDORF MULVANYSTRASSE 2 TELEPHONE 49 / 211 / 96 145 - 0 ■ FAX 49 / 211 / 96 145 - 20

D-45133 ESSEN · FRÜHLINGSTRASSE 43 A ■ TELEPHONE 49 / 201 / 84 230 - 0 ■ FAX 49 / 201 / 84 230 - 20

POSTBANK COLOGNE (bank code 370 100 50) 115 211 - 504

at a higher speed than closing or lowering the load, in particular to save time when opening the gate and to ensure the greatest possible safety when closing the gate in the event of obstacles in the closing path.

Asynchronous three-phase motors are preferred as rotary drive elements for opening and closing gates. Due to the usual 50Hz frequency of an alternating current network, these have a very uniform fixed speed of e.g. 3000 revolutions per minute with two poles, 1500 revolutions per minute with four poles and 750 revolutions per minute with eight poles. It is possible to enable different clockwise and anti-clockwise speeds with such motors by changing the frequency and by using a pole switch. However, such additional devices are complex to manufacture and to connect and set up the drive to the gate to be driven - such work can only be carried out by specialists.

Based on this, the invention is based on the object of creating an automatic transmission of the type mentioned at the beginning, which, when the direction of rotation of the driving motor is reversed, moves the load in one direction of rotation at a different speed to operation in the opposite direction of rotation. Such a transmission should be as low-maintenance as possible and, in addition, enable the gate to be operated as safely as possible.

To solve this problem, an automatic transmission of the type mentioned at the beginning is proposed, in which the transmission connection consists of a first and a second transmission connection, in which the transmission shafts each accommodate both a transmission element of the first transmission connection and a transmission element of the second transmission connection, in which

Furthermore, two freewheel elements are provided which are selectively drivingly effective between the drive member and the output member and are arranged in such a way that one freewheel acts between the first gear connection and one of the gear shafts and the other freewheel acts between the second gear connection and one of the gear shafts.

The invention achieves, among other things, that the automatic transmission has a very compact design and is essentially maintenance-free and durable, since switching operations are completely eliminated. Both transmission connections are always set in rotation by the driving motor at the same time or, with an unbraked load, are kept in rotation by this motor, both when the motor is running clockwise and when it is running anti-clockwise at the time. However, at least after the target speed has been reached, only one freewheel between the drive element and the output element is effective for propulsion, i.e.

in the locking direction, while the other freewheel is then free-running, i.e. not propulsive. The same applies when the direction of rotation of the drive motor is reversed, whereby the other freewheel is now locked, i.e. effective for rotational drive, and the one freewheel is free-running, i.e. not effective for rotational drive.

A transmission according to the invention can be constructed and used in different ways. In particular, the drive member and the output member can be arranged coaxially to one another, but secondly they can also have axes that run parallel to one another and are laterally spaced apart, and thirdly the drive member and the output member can be connected to the drive and the load either on the same or on opposite sides of the transmission frame. In the first case, it is advantageously possible to have a direct drive between the drive and the output member.

drive side and output side, in which the drive element and the output element engage the same gear shaft and only one of the two freewheels, namely acting in the locking direction, is arranged between the two, so that both speeds are the same. The two gear connections then run along, but without being effective in this one direction of rotation. When the direction of the drive motor is reversed, both drive connections are effective in this design and, depending on the sub-Z gear ratios, allow a particularly large number of speeds to be specified for the output element.

In the second embodiment, one of the gear connections is driving and the other gear connection is not driving - and vice versa. In this embodiment, it is also possible to drive the output member at the same speed as the input member - but at the expense of somewhat less flexibility in selecting the speed in the opposite direction. In this second embodiment, however, it is possible to run the output member at a higher speed in one direction of rotation and at a lower speed in the other direction of rotation than the driving motor.

The arrangement of the freewheels can also be very different, so one freewheel can be assigned to the output side and the other freewheel to the drive side gear element, but also to the other gear element on the drive and output side. The freewheels can be assigned to one gear shaft each or both to the same gear shaft. In addition, you can choose between right- or left-locking freewheels depending on the application.

The operation of the gear can be adapted to the application requirements: When raising and lowering a roller door, it can be advantageous, for example, if the drive motor rotating in the closing direction does not transmit power to the winding shaft when closing, but rather the lowering movement is started and maintained by the weight of the roller door after a brake is released, whereby the gear and the motor prevent the maximum accepted speed from being exceeded, since the motor speed is limited, i.e. fixed. In these cases, the lowering load, i.e. the roller door, can be stopped in its closing movement by an obstacle in the closing path, even though the motor continues to run. In these cases, a closing edge safety device to stop the drive motor can therefore be omitted. The obstacle is then only subjected to the force of the effective weight of the door. This weight of the door can even be reduced using a known weight compensation device. If, for example, a roller door jams in a roller door driven in this way, the roller door can be moved in the opposite direction. B. if the gate is stuck in its guide, the lifting cable will also come to a standstill because the motor is no longer driving it forward. This prevents the lifting cable from becoming slack. This slackening carries the risk that the gate sags downwards suddenly when the jamming ground is removed and is only caught by the lifting cable tightening again; this kind of delayed catch of the sagging movement could come too late and cause accidents.

However, it is also possible to configure the gear according to the invention by appropriately selecting the directions of rotation and transmission or reduction ratios and the locking direction of the freewheels so that the output member is forced to drive by the drive member in both directions of rotation. This application is desirable when a gate is closed and opened horizontally.

Another free design option for gears according to the invention is that the size of the increase or decrease ratios of the two gear connections can be freely selected to adapt to the respective task. In particular, it is possible to simply exchange the gear elements while retaining the other components in order to adapt the increase or decrease ratio to the specific application.

When choosing the gear connection, there is also a wide range of options available from the state of the art, e.g. belt drives, gear transmissions with spur, bevel, internal and external toothing and other gears.

The arrangement of the two gear shafts relative to one another can also be coaxial, e.g. using hollow shafts, or parallel or at an angle to one another, as is possible with bevel gears, while retaining the concept of the invention.

The transmission elements can be held by the transmission shafts directly, e.g. by means of a rotationally fixed connection, but also indirectly, i.e. by using a coupling element. Such a coupling element can also be one of the freewheels, e.g. a so-called sleeve freewheel.

Of course, it is also possible to couple gears according to the invention with rotary drive elements with variable rotational speed.

Further advantageous features of the subject matter of the invention, which in particular ensure a simple and functionally reliable gear structure, emerge from the sub-

Sayings and the following description of examples.

The aforementioned components to be used according to the invention, as well as those claimed and described in the exemplary embodiments, are not subject to any special exceptional conditions with regard to their size, shape, choice of material and technical conception, so that the selection criteria known in the respective field of application can be applied without restriction.

Further details, features and advantages of the subject matter of the invention emerge from the following description of the accompanying drawing, in which preferred embodiments are shown by way of example. In the drawing show

Fig. 1 shows a first embodiment of a transmission according to the invention in axial section (section along the line I-I according to Fig. 2);

Fig. 2 shows the embodiment according to Fig. 1, a view from the left (view A);

Fig. 3 shows a second embodiment of a transmission in the manner shown in Fig. 1 and

Fig. 4 a matrix of schematically illustrated embodiments of a transmission with laterally spaced gears arranged parallel to one another

waves.

In the embodiments shown in Figs. 1 and 3, a gear, designated as a whole by 10, is encapsulated by housing halves 12 and 13. Fig. 2 shows holes 23 for receiving connecting screws. In all of the illustrated

The embodiments presented are representations of gears of the same basic design (see also Fig. 4), in which a first and a second gear shaft 16 and 17 are mounted parallel to one another with a lateral distance from one another by both housing halves with roller bearings 24, 25, 26, 27 and held in place. In the embodiment according to Fig. 1, the shaft 16 is unstepped and uninterrupted, while the shaft 17 is divided into three parts and consists of a drive receptacle 17A forming the drive member 14, a bearing pin 17B connected to 17A in a rotationally fixed manner, and an output receptacle 17C forming the output member 15.

Each of these transmission shafts 16 and 17 carries one of the transmission elements of a first transmission connection 18 and a second transmission connection 19.

In the embodiment shown, the gear connections 18 and 19 are designed as toothed belt drives. The gear connection 18 consists of circumferentially grooved toothed belt wheels, which form the gear members 18A and 18B and are encircled by a closed toothed belt 18C. Front side wall disks 18D on the front ends of the smaller-circumferential gear member 18A serve to protect the belt when it is displaced sideways. The gear member 18A is connected in a rotationally fixed manner to the gear shaft 16. The gear member 18B is connected in a rotationally fixed manner to the output mount 17C of the bearing shaft 17 and thus in a rotationally fixed manner to the output member 15.

The second gear connection 19 is also designed as a toothed belt drive and is of the same design as the first gear connection 18. The toothed belt wheel forming one gear element 19B is connected in a rotationally fixed manner to the drive mount 17A of the gear shaft 17 and thus in a rotationally fixed manner to the drive element 14. The other, relatively larger in circumference and the gear

The toothed wheel forming the drive link 19A, however, is connected to the gear shaft 16 with the interposition of a freewheel element 22. The freewheel element 22 is designed as a well-known sleeve freewheel available on the market, which allows the pulley 19A to rotate freely around the gear shaft 16 in one direction of rotation, while the rolling elements automatically move into a clamping position in the opposite direction of rotation and the pulley is driven along by a rotation of the gear shaft 16 essentially without slippage. The same applies to the other freewheel element 21, also designed as a sleeve freewheel, which is inserted radially between the bearing pin 17B and the output mount 17C and is fitted in such a way that in one direction of rotation of the drive member 14 or the output member 15, mutual driving is possible and in the other direction of rotation freewheeling to the other part of the gear shaft 16 is possible. Spacers 28 prevent frictional contact between the gear members of the first and second gear connection.

The gear according to Fig. 1 works as follows: If, for example, a four-pole asynchronous three-phase motor 11 (not shown), which therefore generates a constant speed of 1500 rpm in clockwise and anti-clockwise rotation, is connected in a rotationally fixed manner to the drive element 14 and - viewed from the right in the figure - operated clockwise, the output element 15, which is, for example, connected in a rotationally fixed manner to the winding shaft of a roller door 20 (not shown), rotates in the same direction of rotation and at the same speed, because the sleeve freewheel 21 is installed in such a way that - viewed from the right - it works in the driving direction when rotating, i.e. the rolling elements are locked. Since the toothed belt wheel 19B is connected to the drive member 14 and the toothed belt wheel 18B is connected to the output mount 17C in a rotationally fixed manner, both belt transmission connections 18 and 19 are set in rotation and held in this clockwise rotation of the drive motor. The transmission shaft 16

rotates faster than the drive and driven member due to the selected gear ratio between the toothed belt wheels 18B and 18A (e.g. number of teeth 34 to 24). In contrast, the toothed belt wheel 19A rotates slower than the drive and driven member and considerably slower than the gear shaft 16 due to the selected gear ratio between the gear members 19B and 19A (e.g. number of teeth 24 to 34). All rotating parts then rotate clockwise when viewed from the right. Since the gear shaft 16 rotates faster than the toothed belt wheel 19A, the sleeve freewheel 22 must operate in freewheel mode in this situation.

If the roller door 20 connected to the gear 10 according to Fig. 1 and not shown in the drawing is to be closed again, the drive motor 11 (not shown) is operated in an anti-clockwise direction. At the same time or at a later time, a brake on the roller door (not shown) is released, so that the weight of the roller door then exerts a torque on the output member 15 in an anti-clockwise direction (viewed from the right). The drive motor, on the other hand, also exerts a torque on the drive member 14 in an anti-clockwise direction. However, this torque is not transmitted in a driving direction to the output member 15 and thus to the winding shaft of the roller door. The reason for this is, on the one hand, that the sleeve freewheel 21 is in freewheeling mode when the bearing pin 17B rotates. Consequently, the freewheel is only blocked when the rotation of the output member 15, generated by the gravitational lowering of the door, exceeds the speed of the drive motor, namely 1500 rpm. However, such a case cannot occur - except, for example, if one of the toothed belts 18C and/or 19C breaks. This is prevented by the other sleeve freewheel (freewheel element 22): If the output member 15C, which is driven in rotation by the gravitational lowering of the roller door in an anti-clockwise direction (viewed from the right), reaches

is a speed that causes the gear shaft 16 to rotate at a higher speed than 1059 rpm, i.e. a higher speed than that at which the toothed belt 19A constantly rotates in the anti-clockwise direction, the freewheel 22A locks and prevents the speed of the gear shaft 16 from increasing any further. Due to the gear ratio between the pulley 18B and 18A, the speed of the output member 15 is prevented from exceeding a speed of approximately 750 rpm. The door is therefore lowered at half the speed of the drive motor. The drive motor therefore works as a brake. If the gate now encounters an obstacle that prevents the gate from being lowered further, the drive motor does not exert any torque in the sense of a lowering movement on the drive member 15 because the gear shaft 16 then rotates more slowly than 1059 rpm, or no longer rotates at all, and the freewheel 22 then releases the rotary drive connection between the toothed belt wheel 19A and the gear shaft 16.

A gear according to the invention can therefore basically be used for a wide variety of drive tasks. However, when used to drive doors with a winding shaft, such as roller doors, a number of particularly desirable advantages are achieved, because in this application the weight of the door generally exerts a torque in one and the same direction on the drive, because the weight of the door acts in the direction of lowering the door. This means that when lowering the door, no forces are required from the drive motor, or only those required to overcome frictional forces.

The embodiment according to Fig. 3 has the following differences from the first embodiment: The drive member 14 is laterally offset from the output member 15 at the front end of the stepped but undivided gear shaft 16. The output member 15 is located at the opposite

set end of the also stepped but undivided gear shaft 17. The arrangement and locking direction of the freewheel elements 21 and 22 is the same as in the first embodiment. Here too, the drive-effective locking directions of the two freewheels are opposite. This is indicated in Fig. 2 for the first embodiment by the directional arrows B and C. In contrast to the first embodiment, in the second embodiment the freewheel element 21 is inserted between the outer circumference, the gear shaft 17 and the inner circumference of the gear member 18B. There is a further difference in terms of the direction of rotation and the speed: If the drive motor (not shown) runs clockwise (viewed from the right), this corresponds to the closing movement, while a motor running counterclockwise corresponds to the opening direction of a roller door (not shown). If the speed during the opening movement is to be the same as in the first embodiment, namely 1500 rpm, and in the closing direction approximately 750 rpm, the speed of the drive element may only be approximately 1059 rpm, i.e. must be between the two. One such example is shown in Fig. 3. In a modification of this example, it is also possible to drive the drive element at 1500 rpm (both clockwise and anti-clockwise) and at the same time achieve speeds of 1500 rpm for one direction of rotation and 750 rpm for the other direction of rotation of the output element 15. For this purpose, the transmission ratio of the second gear connection 19 would have to be 1:1 and the transmission ratio of the first gear connection 18 would have to be 1:2.

In Fig. 4, a transmission according to the invention with laterally spaced, parallel gear shafts is shown in various basic design options in matrix form. The basic elements of each matrix element are the same and have the same reference numerals.

as in the embodiments according to Figs. 1 and 3. The individual components are only shown schematically. The top left column shows the embodiment according to Fig. 3 in a schematic, generalized form. Specific gear ratios and types of gear connections 18 and 19 or specific locking directions of the freewheel elements 21 and 22 are not specified. This generalization applies to all matrix elements.

The middle embodiment of the left column corresponds to a generalized embodiment of the example according to Fig. 1. The bottom matrix element of the left column in Fig. 4 shows an embodiment very similar to the top matrix element of this column. In the bottom matrix element, only the output member 15 is arranged on the same side of the transmission as the motor 11.

The second matrix element of the top row in Fig. 4 shows a configuration comparable to the first matrix element of this row, with only the freewheel elements 21 and 22 being provided on the respective adjacent gear element, namely the gear elements 18A and 19B.

In the third matrix element of the first row, both freewheel elements 21 and 22 are provided on the same gear shaft, namely the output-side gear shaft 17. In the fourth matrix element of the first row, both freewheel elements 21 and 22 are again provided on one and the same gear shaft, but this time on the input-side gear shaft 16.

The remaining six matrix elements of the matrix according to Fig. 4 are only indicated by intersecting dotted lines, in order to increase the clarity of the figure. The crossing points mean that in a gear arrangement, as shown in the first position of the row,

the freewheel elements are arranged in an interchangeable manner as can be seen in the respective example at the top of the respective column.

15 List of reference symbols

10 transmission 11 engine 12 Housing half 13 Housing half 14 Drive link 15 Output link 16 Gear shaft 17 Gear shaft 17A Drive mount 17B Bearing journal 17C Output mount 18 first gear connection 18A Gear link 18B Gear link 18C Timing belt 18D Side wall panels 19 second gear connection 19A Gear link 19B Gear link 19C Timing belt 19D Side wall panels 21 Freewheel element 22 Freewheel element 23 Connecting screws 24 roller bearing 25 roller bearing 26 roller bearing 27 roller bearing 28 Spacers A Opinion B Direction arrow C Direction arrow

Claims (14)

PALGEN, SCHUMACHER & KLUIN DÜSSELDORF ESSEN PATENT ATTORNEYS OUR REGISTRATION: 97 213 SCH/jc E s s E N , 25 June 1997 Gesellschaft für Antriebstechnik Dr.-Ing. Günther Hammann & Co. Wiesenstraße 81 D - 40549 Düsseldorf Protection claims: 1. Gearbox for reversible rotary drive elements, in particular motors (11) with a fixed speed in both directions of rotation, for driving a gate with different opening and closing speeds, - with a gear frame or housing (12, 13) for the rotatable mounting of the gear parts, - with a drive member (14) for the direct or indirect rotationally fixed connection of the gear to the rotary drive element, - with an output member (15) following each reversal of the direction of the drive member, - with a gear connection consisting of gear elements acting between the drive element and the driven element and - with at least two gear shafts (16, 17) for receiving (carrying) the gear members,
characterized , that the gear connection consists of a first and a second gear connection (18; 19), D-40239 DÜSSELDORF ■ MULVANYSTRASSE 2 TELEPHONE 49 / 211 / 96 145 - 0 FAX 49 / 211 / 96 145 - 20 D-45133 ESSEN ■ FRÜHLINGSTRASSE 43 A ■ TELEPHONE 49 / 201 / 84 230 - 0 ■ FAX 49 /201/84 230 - 20 POSTBANK COLOGNE (bank code 370 100 50) 115 211 - 504 that the transmission shafts each accommodate both a transmission member (18A or 18B) of the first transmission connection (18) and a transmission member (19A or 19B) of the second transmission connection and that at least two freewheel elements (21, 22) are provided, which are arranged between the drive member and the output member in an optionally driving manner and in such a way that that one freewheel acts between the first gear connection and one of the gear shafts and the other freewheel acts between the second gear connection and one of the gear shafts. 2. Transmission according to claim 1, characterized in that the drive member and the output member are arranged coaxially to one another. 3. Transmission according to claim 1, characterized in that the drive member and the output member have axes that run parallel to one another and are laterally spaced apart from one another. 4. Transmission according to one of claims 1 to 3, characterized in that both freewheel elements (21, 22) are assigned to the same transmission shaft (16 or 17). 5. Transmission according to one of claims 1 to 3, characterized in that the freewheel elements (21, 22) are each assigned to one of the transmission shafts (16, 17). 6. Transmission according to one of claims 1 to 5, characterized in that in one direction of rotation of the drive member no torque is transmitted to the output member, so that, in particular, a motor coupled to the drive member prevents exceeding a maximum accepted speed. 7. Transmission according to one of claims 1 to 5, characterized in that the output member is positively driven in both directions of rotation by the drive member. 8. Transmission according to one of claims 1 to 7, characterized in that at least one of the transmission connections (18; 19) is a belt transmission or a gear transmission with spur, bevel or internal and external toothed gears.
10 9. Gearbox according to one of claims 1 to 8, characterized in that the gear shafts (16, 17) are arranged coaxially to one another, parallel to one another or in a winding arrangement with one another. 10. Transmission according to one of claims 1 to 9, characterized in that the transmission members (18A, 18B; 19A, 19B) are received directly or indirectly by the transmission shafts (16; 17). 11. Transmission according to one of claims 1 to 9, characterized in that a freewheel element (21, 22) is interposed between a transmission shaft (16, 17) and a transmission member (18A, 18B, 19A, 19B). 12. Transmission according to one of claims 1 to 11, characterized in that at least one of the freewheel elements (21, 22) is a sleeve freewheel. 13. Transmission according to one of claims 1 to 12, characterized in that for one direction of rotation of the drive member the speed of the output member is identical to the speed of the drive member. 14. Transmission according to claim 13, characterized in that a gear connection has a gear ratio of 1:1.