WO2012010111A1

WO2012010111A1 - Damping unit for discontinuously damping a rotational motion

Info

Publication number: WO2012010111A1
Application number: PCT/DE2010/075065
Authority: WO
Inventors: Harald Eichner
Original assignee: Kaba Gallenschütz GmbH
Priority date: 2010-07-23
Filing date: 2010-07-23
Publication date: 2012-01-26
Also published as: HK1178953A1; SG186995A1; MX340800B; BR112013001683A2; MX2013000875A; DE112010005762A5; EP2596191A1; CN103025988A; EP2596191B1; RU2013108110A; CN103025988B; MY175162A; CN201933932U

Abstract

It is known how to damp the rotation of rotating doors and similar access barriers by means of a discontinuous gear train in that preferably noncircular gears first convert the continuous door rotation into a discontinuous rotation on the output side and said discontinuous rotation is damped by means of a damping element. Known arrangements use gears having identical rolling curves for this purpose, which leads to an overshoot of the rotation and to intermittent damping action. This should be improved by the invention. Said aim is achieved by a damping unit that uses two noncircular gears having different rolling curves, of which one is egg shaped and the other in contrast is shortened and at the same time widened relative to the first. This results in a modified damping profile that enables more uniform motion of the revolving door. This arrangement also enables a motor drive, which can be operated at a constant rotational speed because of the arising sine- or cosine-shaped inverse curve of the gear train and which enables a clean end-position motion of the driven access barrier.

Description

STEAMING UNIT DISCONTINUOUS

STEAMING OF A TURNING MOVEMENT

The present invention relates to a damping unit for discontinuous damping of a rotational movement of a rotatable about a drive axis around the drive wheel, in particular a drive wheel of access barrier, by means of a dis ^¬ continuous transmission, which is composed of two käm ^¬ menden, eccentrically mounted, non-circular gears and the drive wheel with an output shaft associated ^¬ assigned attenuator connects.

Such a damping unit is already known already from the interpreting ^¬ rule published patent application DE 36 38 353 AI. There, a continuous rotation of the end of a knee joint connected to a door closer is converted by means of a gear consisting of two identical non-circular gears into a discontinuous rotation, which is finally subjected to a damping.

In such door closers, but also in particular in access barriers used in Personenunterzelungseinrichtungen access to a protected area is usually made dependent on a condition, for example, from the pre ^¬ lying a valid ticket. Therefore, such an access lock to snap a Verrie ^¬ gelung after each passage of a person, so with a valid A ^¬ not admission ticket several people the protected area can be ^¬ come. By this locking a mechanical blockade of the access barrier is triggered, which prevents further rotation. If the access lock to move with undiminished Ge ^¬ speed to the end position, the would it snap ten of the locking mechanism on the one hand stress the material and on the other hand mean a noise pollution. Such noise in the range of access barriers is usually recom- found as a negative quality feature, so be ^¬ is also part of the manufacturer is a need to avoid this.

Basically, it is therefore desirable in such attenuations, be it in access barriers, door closers or other comparable facilities, to dampen the movement of the access barrier in the end position so that a gentle but zü ^¬ giger Endlagenlauf is achieved. A continuous rotation ^¬ movement could take place only equal ^¬ moderately with a direct damping, so that the door would be only sluggish by the damping, at best in the range of the extreme points of Dämpferkolbenauslenkung would run easier. Characterized in that the damping effect is dependent on the Drehgeschwin ^¬ speed, a large rotational speed, a high Dämp ^¬ Fung, a low rotational speed means a low attenuation, must be achieved for damping in the region of the end positions a to ^¬ participating rotational speed. This can be achieved by the use of a discontinuous gear ^¬ who, which is constructed so that an increasing Drehge ^¬ speed of the crank after the unstable position takes place until shortly before the end position.

The well-known from the above laid open patent cogs, which are identical, have in the implementation of the continuous in a discontinuous rotary motion, however, the disadvantage that due to the identi ^¬ 's design of the gears a significant deviation from the ideal damping curves must be accepted. Therefore, the prior art makes use of other possible answer ^¬ th the production of an ideal as possible Dämpfungsver ^¬ run. From the German patent DE 10 2007 010 385 B4 for this purpose, for example, a locking unit for a turnstile system is known. Such a turnstile is a possibility of an access barrier, in which a locking element is provided, which provides a spatial Untertei ^¬ lung. Through a stepping step of Sperrelemen- tes a passing through the access barrier in each case by one person is possible, whereby a person singling is reali ^¬ Siert. In the context of the disclosure of this German Pa ^¬ tentschrift an indexing of the locking element is realized by a motor which is controlled so that in the end region of the movement, ie in the region of the end position of the

Locking elements, a damping is provided. This damping is realized in that the motor is slowed down in the region of Endla ^¬ ge, so that it does not swing beyond the end position.

For various reasons, be it for reasons of Lärmreduk ^¬ tion, explosion protection or because the customer of a mechanical solution a longer service life verspre ^¬ chen than electronic components, there is also a demand for purely mechanical access barriers, which then, however, a high should have correspondingly good damping. Ideally incorporating a structurally possible liehst identical product variant is as desired in motorized case a rising damping are achieved until shortly before reaching the end ^¬ location, to a conversion or a leaner Pro ^¬ production - This should - as in the motorized version to enable. The present invention is therefore based on the object to provide a damping unit for continuously reinforcing Endla ^¬ gendämpfung a rotational movement, which allows a ^¬ most ideal damping course without overshooting and at the same time waives the use of an engine.

This object is achieved by the damping unit according to the features of claim 1. Further useful Ausgestal ^¬ tions of the damping unit can be found in the dependent claims.

Structurally, first a drive wheel is present, to which the access barrier attaches with its force. With the drive ^¬ wheel, which is rotatably mounted about a drive axis, the torque of the movement of the access barrier is transmitted to the damping unit. Instead of providing a motor for this, a black box was first provided here, which should unfold the same mode of action, as a motor in the control described above. It has proved to be an inventive solution to provide for the black box, a discontinuous transmission, which converts the generated by the rotation of the person passing continuous ^¬ ierliche rotation of the access barrier or the drive wheel of the access barrier in a non-continuous rotation. In effect, thereby a unkontinuierliche motion of an output shaft of the same discontinuous transmission is generated due to the continuous Dre ^¬ hung a drive axle of the discontinuous transmission used, wherein a speed-dependent damping of the output shaft N & N longer causes a strong attenuation at high speeds of the output shaft, while a small VELOCITY ^¬ Ability of the output shaft brings a low attenuation with it. The discontinuous gear used for this purpose comprises two non-circular gears, which have different Wälzkurven. It has been determined that arranged on the drive axle gear may have a substantially eiför ^¬-shaped rolling curve, preferably, while the other non-circular gear which sits on the output shaft, opposite the drive-side gear in the direction of the extremity shortened, is, however, widened in the direction transverse thereto , Such a distribution of the rolling curves generated in particular in comparison to the use of identical, for example, egg-shaped, rolling curves ^¬ a much more progressive Geschwindigkeitsver ^¬ running on the output shaft as a system response to the application of a continuous rotation of the drive axle. This results in a cleaner and a Endlagenlauf equal ^¬ more even attenuation behavior during rotation, resulting in independence of the rate of passage of results, wherein in each case a controlled Endlagenlauf instead ^¬ place.

A less preferred, especially in the end-of-run and in the unstable position worse configuration is caused by a reversal of the two gears, so arranging the widened and shortened gear on the An ^¬ drive axle. However, protection is explicitly sought for this.

Both non-circular gears are designed symmetrically with advantage, so that rotation of the access barrier can be done in both directions. Here, the zero Stel ^¬ le, and an unstable equilibrium in the central Drehpo ^¬ sition is in a position of the gears, which in their Symmet ^¬ rieachsen are congruent. Preferred dimensions, the Gears equal numbers of teeth to allow multiple passages in the same direction.

An advantage of the identical Wälzkurven according to the prior art is that only one tool must be made for the production of identi ^¬ rule gears. Due to the cost of such tools, this represents a decisive advantage, which makes a poorer rotational behavior quite acceptable. However, the invention uses MIM or CIM parts to minimize the cost of the tool. The cost of the tools required thereby are many times lower than the cost conventionally for such metallic Zahnrä ^¬ the required tools.

An attenuation of the output shaft can be done according to the invention either by a turn provided there engine, wel ^¬ cher in a similar manner, as described above ben ^¬ controlled. As far as the discontinuous transmission knew sawn from the prior art is used with two identical Zahnrä ^¬ countries, so is the use of a motor for driving the transmission of the actual output side to an identical curve of the speed füh ^¬ reindeer, which means that a constant rotation of the motor has a rotation of the revolving door result, which is very fast in the region of the labile middle position. The motor may have to be controlled in ^¬ consuming so that its movement takes place according to the function at a constant rotation on the drive side. In addition, the engine would have to be much stronger than standard. The Ge ^¬ gear according to the invention, however, is so designed by its shape, that the inverse function is a sine or cosine, so that automatically con- standter speed of the motor of the high and Run realized, so a maximum speed is reached at the apex of the movement. The damping unit according to the invention is therefore suitable and designed both for the motor to ^¬ drive by a constant-speed motor as well as for manual operation, in the case of motor ^¬ operation, the functions of the drive and output axles are ver ^¬ exchanged. The motor thus acts on the output shaft and causes via the discontinuous gear rotation of the access barrier. The design according to the invention of Getrie ^¬ bes in this case ensures that the behavior of the transmission is in both operating directions exactly the same, so that in at ^¬ create a constant engine speed at the From ^¬ drive axle, the inverse function on the drive axle, a sine or cosine. Thus, due to also lower force required to accelerate and decelerate performance-based are used smaller engines, which ge ^¬ genüber powerful engines save costs.

The determination of an ideal Dämpfungsfunkton can be done using a gear linkage by the ideal Los ^¬ seminal moment in the stable position, so harrungsmoment the encryption so-called, is determined by varying the distance crank the wheels ^¬ coupling gear. From the integrated crank in the gear coupling can be read as an inverse sine or cosine function, which brings the above-mentioned advantages for motorized ^¬ th operation. He ^¬ mittelte function and the inverse function is now transferred to two non-circular gears, as the assembly of a wheel coupling transmission over the use of erfindungsge ^¬ MAESSEN discontinuous transmission we ^¬ is sentlich difficult with two gears and would therefore be more costly. Nevertheless, a use of a gear coupling is Of the transmission with two non-circular wheels of the invention expressly includes.

In a further embodiment is provided to assign a crank element of the output shaft, so that an eccentric Ver ^¬ binding of, for example, as a spring-damper member out guide ^¬ th attenuator is provided to the output shaft. Such an attenuator can for example be advantageously integrated into a gas spring which comprises a piston and a cylinder. In a linear movement of the

Piston in the cylinder or out of the cylinder, the movement in question is damped, so that by a compound of this piston in an eccentric manner with the output shaft, for example via said crank member, but optionally also directly with parts of the discontinuous transmission, the desired damping is provided ,

To further avoid overshooting in the end position, it is provided that the end position of the drive wheel is reached where the discontinuous transmission and the

Spring element in a stable equilibrium. This ^¬ be indicated that the discontinuous transmission is in the fastest movement of the output shaft, while the piston is in its floating position. It is provided, moreover, that the piston only attenuates in a rich ^¬ processing, in particular in the extension direction, so that in the reverse direction, that in particular during insertion, an undamped movement is possible. For this purpose, for example, the piston of the gas spring on a corresponding valve, via which oil flows over the valve opening of the piston and thus does not take place damping in the direction mentioned. However, it is also readily possible to turn the direction of effect ^¬ tion to the effect that the gas spring damps only in the slot, which should be expressly covered by the invention. Damping is also possible both in the a ^¬ ais and in the extension, although not the preferred variant.

A ausgestalte example in the form of a return spring ^¬ tes, additional return element can advertising used to the, the access barrier in an unstable position, for example when it is left after the start of rotation again in the opposite Rich ^¬ tung, back into an end position to verbrin ^¬ gen . to this end, a provision is always spent in the next lie ^¬ de end position to cause no unwanted completion of the rotation when the rotation started is canceled.

In order to obtain the ^greatest possible freedom in the use of ^{such a ¬} damping damping unit, it is provided to provide instead of a simple crank on the output shaft of the dis ^¬ continuous transmission, which only allows an eccentric connection with the attenuator to use a crank disc, which Distributed over its circumference fastening means for the attenuator provides, which have different eccentricities. If a toothed shaft is used as the drive axle and / or driven axle, the fastening means are distributed in the same number around the pivot point as teeth are provided on the toothed shaft. As a result, the crank disk can be assigned to each position of the fastening means in a suitable manner. This makes it possible to adjust the degree of attenuation again adapt to the different sizes at ^¬ special access barriers with various ^¬ the large mass the degree of attenuation in detail sen. In addition to the possibility of a fine adjustment here ^¬ also given a way to make an adjustment to ver ^¬ different products, such as Drehkreu ^¬ ze, revolving doors with different pitches, etc.

A further additional damping can be achieved ^¬ who, that the discontinuous transmission is accommodated in a housing which is filled with gear oil. Here by a smoother running of the discontinuous gear bes is guaranteed bes, which is a damping ^¬ measure, which affects uniformly on the entire, continuous rotation of the drive wheel.

Em further integration step is effected by the fact that the drive axle, which is operatively connected to the drive wheel, as well as the output shaft, to which the damping engages ^¬ , each with the associated Unrundrad are provided in one piece. Together with the ball bearings used, wel che the non-circular wheels including axles stored in the space provided, two-shell housing, so that no more than eight parts are required for the completeness ^¬ ended non-circular gear. The assembly of such a non-circular gear turns out to be extremely simple and very inexpensive. As already shown above, such a Dämp ^¬ tion aggregate for a number of products can be used, especially for revolving doors and turnstiles of different pitch. In a 90 ° division of the turnstile, the drive wheel in the direction of the access barrier requires a 1: 4 translation, so that a quarter turn of the turnstile causes a single, complete revolution of the drive axle and the output shaft. The drive shaft carries out a complete rotation through so that due to the discontinuous transmission initially rapid movement and then an area dying slowly ^¬ mer movement, followed by another rapid movement to each other. Thus, there are two areas of rapid movement, it being noted that the attenuation of the attenuator is stronger during rapid movement, so that in a ^{herkömmli ¬} Chen damping cylinder actually these two areas would be greatly attenuated. Characterized in that the damping member, however, only works in one direction, takes place only in the last-mentioned rapid movement appreciable Dämp ^¬ Fung, whereby this area is located in the region of the end position of the turnstile. Due to the spring pressure of the Dämp ^¬ ment member here is a stable Endlagenlauf a. By another translation, the same unit can be used for a 120 ° division or 180 ° division, if then a 1: 3 or a 1: 2 translation is provided tion.

Since the discontinuous transmission will usually be enclosed in a housing and an alignment of the discontinuous transmission will be required to place the moment of greatest damping in the end region of the movement, it seems expedient to take measures to ensure the correct position of the discontinuous To ensure transmission in the housing. For this purpose, the drive axle or the

Output shaft at least in sections as a toothed shaft out ^¬ forms, so that directly on this toothed shaft in the case of the output shaft, the crank element and in the case of Antriebsach ^¬ se, the translation or the drive wheel can be placed. It is particularly useful if translation or drive gear have a multiple of the teeth, as provided in the toothed shaft. In this case, it is safe to provides that with each position of the translation wheel or the drive wheel, a correct setting is possible.

In addition, however, it is provided that a mark for the correct position of the discontinuous transmission is attached to the toothed shaft.

An alternative embodiment of the damping unit, according to which the drive wheel is designed as a toothed wheel, which engages in a rack or a toothed belt, leaves a

Use as a damping unit for a sliding door to when the rack bar or the toothed belt in the region of the wall is integrally arranged ^¬ and the gear rotates the drive wheel. The on ^¬ drive wheel may if necessary be geared down such that a complete sliding one complete revolution of the drive shaft corresponds to said ideally a not quite complete rotation is to target, so that the rest position is ideally achieved in an attenuation maximum, and thereby also in a maximum torque and the door safely closes. If you push the door slightly over the middle position to the open or closed position, it then moves automatically, pushed by the spring force of the spring-damper element, in the respective open or ge ^¬ closed position.

The same applies to the case of an insert of the damping unit in question for a swinging door, in which case a toothed rail is arranged in the opening direction of the door, which engages in the drive wheel or a gear associated therewith. If necessary, a translation can be a ^¬ set here. The invention described above is explained in more detail below with ^{reference ¬} an ^exemplary embodiment.

Show it:

Fig. 1: a damping unit according to the prior

Technology in a perspective Dar ^¬ position obliquely from above, Fig. 2 shows a damping unit according to the invention in a perspective view obliquely from above,

FIG. 3 shows a graph of various Kolbenab- operating speeds according to the prior art, the invention and the Ideal ^¬ fall,

Fig. 4 is a diagram showing the according to the inverse function of the function shown in FIG. 3 He ^¬ invention,

5 shows a revolving door with a damping unit according to FIG. 2 in a perspective illustration, FIG.

Fig. 6: a swing door with a damping ^¬ aggregate according to Figure 1 in a Perspecti ^¬ vischen representation, and.

Fig. 7: a sliding door with a Dämpfungsaggre ^¬ gat of FIG. 1 in a perspektivi ^¬ 's representation. Figure 1 shows a damping unit 10 according to the prior art, which is particularly suitable for damping a rotational movement of an access barrier. The rotational movement of the access barrier in this case acts on a translation, not shown, wherein the rotational movement is transmitted to the drive wheel 13. The drive wheel 13 is mounted on a drive axle ^¬ At 15, which is connected to a diskontinuierli ^¬ chen gear wheels consisting of two identical non-circular teeth 11 and 12. FIG. Due to the egg-shaped Wälz ^¬ curve of the gears 11 and 12 is a continuous rotation ^¬ movement of the access barrier in a discontinuous Drehbe ^¬ movement on an output shaft 16, which is connected to a damping ^¬ element 17, 18, converted. Due to the identical tables rolling curve, it is not necessary to prepare a plurality of tool press ^¬ ge for the two gears 11, 12, so that the kept low for the production of the gears 11, 12 costs. However, the resulting Wälzkurve is not ideal because it favors intermediate damper and muffled in the range of the final position inaccurate. Also the area of the unstable situation is very pronounced.

Figure 2 shows the solution according to the invention, which is constructed in the same Wesent ^¬ handy, however, comprises two gears 11 and 12 having different pitch curves. Thus, the rolling curve ^¬ curve of a drive-side gear 11 is substantially egg-shaped, while the Wälzkurve the driven side Zahnra ^{¬ of} the 12 against the pitch curve of the drive-side gear 11 in the direction of eccentricity shortened, but is widened in the transverse direction. In this way, both gears 11, 12 to the same extent and allow idealized ^¬ th course of the rotational speed produced at the Ab ^¬ drive axle 16 and thus the damping. This is done via a force acting on the output shaft 16 piston 18 of a gas spring 17, which is connected via a Kurbelele ^¬ ment 14 with the output shaft 16. Thereby, the unkontinuierliche rotary motion to a linear motion is converted Be ^¬ which is attenuated by the gas spring 17th The gas spring 17 only attenuates in the extension of the piston 18, so that te in a full revolution of the drive shaft 16 ^¬ the gas spring 17 te only in the second half, so after a complete insertion of the piston 18 in the cylinder of the gas spring 17, with the Damping begins. Starting from the end position shown, therefore, a rotation of the access barrier connected to the drive wheel 13 will be undamped until the end of half a turn, then the damping will begin. However, the damping acting in depen ^¬ dependence of the extension speed of the piston 18, so that the attenuation due to the kinematic design of the discontinuous transmission effect due to the unkontinuierlichen movement from the second rotary half until almost the end of the rotation towards increasingly dominant in the overall system, so that in the end region a sufficiently strong damping ^{stattfin ¬} det to keep the access barrier from overshooting and to make them come to a standstill in the final position.

Figure 3 shows a diagram in which the courses of the Kol ^¬ bengeschwindigkeit is plotted against the rotation angle of the driven-side gear 12, in accordance with an ideal curve 51, a curve according to the solution of the prior art 50 and according to the invention 52. In view of the symmetry of both tooth ^¬ wheels 11, 12 are also in the curves 50, 51 and 52 are symmetrical curves whose symmetry is a Punktsymmet ^¬ rie to zero at the rotation by π. The ideal curve 51 shows in the area around the point of symmetry 53 a steep and substantially constant slope, which means a uniform damping in this area. In this point of symmetry 53, the system reaches a labile Equilibrium ^¬ weight, wherein the piston velocity has a turning point. Due to the high speed change is vermie ^¬ that the access lock can remain in their mid-position of green ^¬ friction. The same applies to the curve with gears according to the invention 52. Only the curve with the same gears 50, which reflects the prior art ^¬ , has too low a change in speed of the piston in the slope, which means interim Ver ^¬ slowdowns and accelerations due to the damping behavior of the piston 18 lead to intermediate dampers in the movement. Also, the high point of the damping or the piston speed in the case of the curve with ^fiction, according ^¬ gear wheels 52 further verscho ^¬ ben towards the end position than in the curve with the same gears 50, which leads to ei ^¬ nem cleaner end-of-run.

If the person passing the access barrier does not drive the transmission but a motor mounted on the output side, then the transmission according to the invention provides an inverse curve 54 according to FIG. 4, which results in a sine or cosine curve on the drive side or on the side of the access barrier. The design thus allows the use of the same transmission for manual operation and motorized operation, in the latter case the motor does not have to be subjected to a complex Steuerver ^¬ drive, but can be driven at a constant rotation ^¬ number to a suitable movement of the access barrier, ie a clean up and down run, to ensure. The arrangement according to Figure 5 shows a damping unit 10, the drive shaft 13 is connected via a translation 21 with a turnstile 20. Such a turnstile 20 can be used with the same damping unit 10 as a revolving door or a similar system. It is single ^¬ Lich necessary in this case to provide or another crank member 14 to choose another Exzentrizi ^¬ ty when using a crank disk to accommodate the greater mass of a revolving door in damping. Due to the division in 120 ° shown here, a 1: 3 ratio is to be selected. If a hub 20 about with only 2 or 4 locking rake ver ^¬ turns to be, so the translation is merely adapt thereto, ie a 1: 2 gear ratio, in case of Zweitei ^¬ development, a 1: 4 gear ratio, in Case of a four-fold use. In the case of selected 1: 3 gear ratio, is at a complete rotation of the turnstile 20, from ^¬ drive axle 16 rotate three times, so three times a Dämpfungsma ^¬ ximum, namely at each passage through the turnstile 20, be overcome.

As shown in Figure 6, a use of the invention for a swing door 30 is also provided. There is provided in the area of the Be ^¬ wall above the swing door 30 has a toothed rail 31 which directly engages with the drive wheel 13 and therefore offset in this rotation. The size of the drive wheel 13 is to be selected in this case so that a complete swing corresponds to a complete revolution of the drive wheel 13. The swinging door 30 is thus initially can swing on ^¬, wherein the driving wheel 13 continuously rotates once full. Also in the opposite direction will be a damping in the range of the end position. It should be noted here that in order to achieve an ideal damping, no complete rotation is carried out, so that a Dreier- quasi effect of damping maximum to maximum attenuation is effected. This appears to be practicable in each case with a reciprocating movement, in a bidirectionally used turnstile 20 this is not the case. This also no need Schließmecha- mechanism be overcome by force, but only in final position automatically run by eg a ratchet lock to read ^¬ sen.

Finally, another embodiment is shown in FIG. 7, in which a sliding door 40 is realized. In accordance with the above, a toothed strip 41, which is mounted parallel to the wall, engages in a translation associated with the drive wheel 13, so that damping is also effected by the damping unit 10 when the sliding door 40 is pushed completely open. Here, too, he ^¬ therefore such a damping follows that the sliding door reaches its end position under dampening.

Described above thus a damping unit for damping a rotational movement unkontinuierlichen insertable into ^¬ particular in the area of access barriers. By implementing a continuous rotation into an uncon ^¬ continuous rotation, which is particularly suitable for damping, such a damping in selected areas of the rotational movement take place, so that in particular a damping rising to the range of the end position can be realized. An ideal damping curve is achieved by the use of toothed ^¬ wheels with uneven Wälzkurve, wherein the output-side gear is shortened in the direction of its eccentricity relative to the drive-side gear and widened in the transverse direction thereto. LIST OF REFERENCE NUMBERS

10 damping unit

11 drive side gear

12 driven side gear

13 drive wheel

14 crank element

15 drive axle

16 output shaft

17 gas spring

18 pistons

20 turnstile

21 translation

30 swinging door

31 tooth rail

40 sliding door

41 rack

42 translation

50 curve with the same gears

51 ideal curve

52 curve with gears according to the invention

53 point of symmetry

54 inverse curve

55 Motor speed curve

Claims

P A T E N T A N S P R E C H E

Damping unit for discontinuous attenuation of a rotary motion of a drive shaft (15) around ro ^¬-mountable drive wheel (13), in particular a drive ^¬ wheel (13) of an access barrier, by means of a diskonti ^¬ ous transmission which is mounted from two mutually FIGHTING ^¬ Menden, eccentrically , non-circular gears (11, 12) is constructed and the drive wheel (13) ver ^¬ binds with a ei ^¬ ner output shaft (16) associated attenuator,

characterized in that the transmission comprises two gears (11, 12) with unequal Wälzkurve, wherein a, preferably on the output shaft (16) mounted, tooth ^¬ wheel (12) relative to a second, preferably on the drive axle (15) mounted gear (11) is shortened in the direction of its eccentricity and widened transversely thereto.

Damping unit according to claim 1, characterized in ^¬ net that the antriebsseit strength gear (11) has an ovoid in ^¬ We sentlichen rolling curve.

Damping unit according to one of claims 1 or 2, characterized in that the attenuator has two Ex ^¬ tremstellungen, including an end position, where ^¬ in the gears (11, 12) are aligned in the same direction in these extreme positions of the attenuator and have a common axis of symmetry. Damping unit according to one of the preceding Ansprü ^¬ che, characterized in that the toothed wheels (11, 12) are produced by means of MIM or CIM technique.

Damping unit according to one of the preceding Ansprü ^¬ che, characterized in that the toothed wheels (11, 12) have the same numbers of teeth.

Damping unit for the discontinuous damping of a rotational movement of a drive axle (15) around ro ^¬ tierbaren drive wheel (13), in particular a drive wheel (13) of an access barrier, by means of a discontinuous transmission, which the drive wheel (13) with an output shaft (16 ) associated damping ^¬ member,

characterized in that the transmission is constructed as a gear coupling transmission.

Damping unit according to one of the preceding Ansprü ^¬ che, characterized in that the attenuator is a motor drive, which one, preferably posi tion-dependent, damping on the output shaft (16) Verur gently.

Damping unit according to one of claims 1 to 6, characterized ^{¬ in} that the attenuator is a Dämp ^¬ tion cylinder whose piston (18) with its free end of the output shaft (16) eccentrically, preferably un interposition of a crank member (14), anver ^{¬ is} bound.

9. damping unit according to claim 8, characterized in ^¬ net, that it is in the crank member (14) to a Kur- belscheibe is, distributed over its circumference buildin ^¬ actuating medium of different eccentricities for ex ^¬ centric mounting of the piston (18) are assigned. 10. damping unit according to one of claims 8 or 9,

characterized in that it is in the Dämpfungszy ^¬ relieving a gas pressure spring (17) which preferably attenuates before ^¬ only in the extraction of the piston (18). 11. Damping unit according to one of claims 8 to 10,

characterized in that the damping cylinder is assigned a restoring element which acts a restoring be ^¬ force in the direction of the nearest end position ^¬.

12. damping unit according to one of the preceding Ansprü ^¬ che, characterized in that the inverse function of the function of the rotational speed of the output shaft in dependence ^¬ dependent on the rotation angle of the drive axle at constant rotation of the same a cosine or sinusoidal

History has.

13. Damping unit according to one of the preceding Ansprü ^¬ che, characterized in that the discontinuous transmission in one, preferably two identical

Half-shell composite, housing is added, which is preferably filled with gear oil.

14. Damping unit according to one of the preceding claims, characterized in that the output side

Gear (12) integral with the output shaft (16) and the drive-side gear (11) integral with the drive shaft ^¬ (15) are made.

15. Damping unit according to one of the preceding Ansprü ^¬ che, characterized in that the drive wheel (13) via a translation, preferably a translation (21, 42) in the ratio 1: 4, 1: 3 or 1: 2, with the Access ^{SS ¬} is connected.

16. damping unit according to claim 15, characterized in ^¬ net, that the drive axle (15) and / or the drive axle (16) at least partially formed as a toothed shaft, wherein preferably the number of teeth of the drive wheel (13) an integer multiple of the At ^¬ number of teeth of the toothed shaft section is. 17. damping unit according to one of claims 15 or 16, characterized in that the drive wheel (13) or the translation (42) an additional gear is arranged coaxially to ^¬ and engages in a rack (41). 18. Damping unit according to one of claims 1 to 16, characterized in that the drive wheel (13) is designed as a gear in which a toothed rail (31) engages.