RU2265764C2 - Driving gear - Google Patents

Abstract

FIELD: the invention refers to engineering industry, precisely to a driving gear which provides relative displacement of two details with possibility of their turning relatively to each other in a peripheral direction.

SUBSTANCE: a drive has at least one tool of linkage fixed relatively to the first detail which enters between at least two adjacent coils of a spiral ring placed on the second detail without any possibility of turning relatively to it of a spiral spring and at least one detail is installed with possibility to be set in motion relatively to another detail.

EFFECT: simplification of manufacturing of a driving gear and easing its control.

100 cl, 27 dwg

Description

The invention relates to a drive consisting of two parts located relative to each other, which are mounted with the possibility of rotation relative to each other in the peripheral direction using a rotary drive to provide relative movement of the parts.

Such drives are known as axial drives or axial gears, in particular as helical gears, in which, for example, a screw with an external thread is turned inside a sleeve with an internal thread, for example, by means of an electric motor or manually, and thereby provide axial movement of the screw relative to the sleeve . Such axial drives are used, for example, in screw presses. The maximum axial stroke is determined by the thread pitch and the number of revolutions of the screw. At the same time, the thread pitch determines the gear ratio of the drive, which can be defined as a stroke in one revolution. In addition, such drives are known for moving both parts in the radial direction as a collet for fixing parts.

Often the gear ratio, determined by the pitch of the thread, as well as the diameter of the screw, is too small, in particular, in conjunction with rapidly rotating and / or limited in power rotary drives, such as electric motors. In addition, such screw drives are difficult to manufacture and therefore are expensive. In addition, with insufficient care, the screw drive has a high coefficient of friction.

Therefore, the basis of the invention is the task of creating a simple to manufacture and not expensive drive with a large gear ratio, which, in addition, does not require complicated maintenance and is easy to manage.

The problem is solved, for example, by means of an actuator consisting of at least two parts that are rotatable in the peripheral direction relative to each other to provide axial relative movement, and at least one part is rotated relative to another part, and at least at least one fixed in axial direction relative to the first part of the means of engagement enters radially between two adjacent turns of a coil spring located without the possibility of rotation of the relative But the second detail. This ensures the following principle of operation: the first part is axially supported on the second part using at least one means of engagement, and when both parts are turned in the peripheral direction, the spring wire passes by the means of engagement, so that depending on the number of turns, a variable section arises a coil spring on which the engagement means can be supported, and thus both parts can be moved relative to each other. In this case, the parts are preferably arranged coaxially with respect to each other.

In addition, it is preferable that the coils of the coil spring are located, apart from the extension due to the gearing means, adjacent to each other, since due to this it is possible to realize very large gear ratios depending on the thickness of the wire of the coil spring and at the same time increase the transmitted force due to adjacent turns. On the other hand, if the coils are not adjacent to each other, then elastic transfer of forces along the axial path is possible depending on the stiffness of the coil spring and the distance between the coils at a given axial length of the engagement means.

According to the idea of the invention, the drive can be used in the traction and pushing direction, and in the traction direction with the axially movable part, an element to be axially moved can be engaged.

The coil spring is fixed on the second part without the possibility of rotation relative to it and is preferably fixedly connected at its ends to the second part, for example, inserted into the corresponding seats, riveted or welded. Thus, the second part with a twisted spring is equivalent to a screw with an external thread with the advantage that individual threads of the thread can abut each other, and due to this, there is a significant shortening of the "thread" with a corresponding increase in the gear ratio, and the extension of the adjoining turns spring occurs only in the place of radial engagement with the means of engagement, i.e. compared to a screw, only this part of the thread should be held with its actual size, while in other places the axial length of the part can be shortened. In particular, for reasons of reducing the cost of the hard springs, it is preferable to fix only one end of the spring on the second part without being able to rotate.

According to the idea of the invention, the engagement means, in particular, at large transmitted axial forces, can be supported in the traction or pushing axial direction by several turns, however, in the sense of optimizing the axial space, it is preferable that the engagement means rest on only one turn, i.e. preferably one perimeter or part of one perimeter, so in the figurative sense, "thread" has only one "thread". In this case, the coil spring is divided by the engagement means into two sections of the coil spring, and the engagement means, depending on the direction of transmission of the force — traction or pushing — rests axially on one of them.

The coil spring is located on the second part, preferably coaxially with the second part, wherein the engagement means in the engagement zone with the coil spring reproduces the axial travel of the coil spring. In another embodiment of the axial drive, an engaging means is provided which is approximately at right angles to the middle axis of the second part, in which case the middle axis of the coil spring is so rotated about the middle axis of the second part that the turns of the coil spring abut approximately flat to the means of engagement.

The shape of the coil spring wire may, according to the invention, deviate from the usual circular cross section and this may be a spring band with more or less pronounced edges. For example, a rectangular cross section of the spring band may be preferred, with the long side corresponding to the width of the band extending in the radial direction and the narrow side corresponding to the thickness of the band in the axial direction. Experiments and calculations have shown that the ratio of the width to the thickness of the tape is more than 1: 1, preferably 3: 1 to 60: 1.

In addition, the thickness of the tape, on the one hand, is crucial for the transmitted force and, on the other hand, for the gear ratio, the optimization of both values being the opposite. So, for example, it may be preferable in large drives to transmit axial forces to choose a thickness of the wire or tape up to 5 mm or in special cases even more, however, in most cases the thickness of the wire or tape is less than 2 mm, preferably about 1 mm, for example, if the drive is used as a shift lever for friction clutch in a car. In special applications, for example to provide very large gear ratios, the thickness of the spring wire or tape can be reduced even up to 0.1 mm. In this case, it is preferable to correlate the width, respectively, the diameter of the spring tape with the outer diameter, along with the choice of the material used, preferably spring steel, and in less critical cases other metals or plastics, to ensure spring properties and force transfer depending on the width of the tape. For commonly used tape widths, the ratio of the outer diameter of the coil spring to the radial width of the spring tape can range from 100: 1 to 1: 1, preferably from 30: 1 to 5: 1, with the ratio of the diameter of the coil spring to the tape thickness ranging from 700: 1 to 25: 1, preferably from 200: 1 to 40: 1.

The length of the drive is set depending on the application and is determined mainly by the number of turns and the thickness of the wire, respectively, of the tape, and the number of turns can be from 3 to 300, preferably from 5 to 50.

In special embodiments, it may be preferable that the drive has a different pitch along the axial path. A coil spring or a coil, for example, can have, for example, two different diameters on its axial length, with both diameters having a different pitch, so that the tape has different pitch values consistent with different diameters. In addition, it is possible to provide, for example, a trapezoidal cross-sectional spring tape, the beveled surface of which rolls along the convex means of engagement, for example, pins, and to perform a different step, you can change the thickness of the spring tape. In this regard, self-braking can be changed due to the gain of the axial displacement in the axial direction. So, for example, it is possible to compensate for the ratio of forces specified in the clutch by a Belleville spring, due to the different thickness of the spring tape to ensure uniform power characteristics.

In addition, a twisted tape, or twisted spring, can be used in conjunction with a sensor that measures movement, position, or the like. tape, as a device for determining the position of the drive. For this, the twisted tape may, for example, have a surface structure on the end surface, which can be evaluated using, for example, a path increment sensor. In this case, the surface structure can be such that recognition of the end position at least at one end of the tape, as well as the speed of the tape and the acceleration of the tape, is ensured. Evaluation methods, circuit solutions and errors are described in the special literature on track increment sensors, as well as sensors for anti-lock braking systems (ABS).

It may be preferable to arrange two or more twisted tapes in each other, for example radially in each other and / or relative to their surface of the tape, superimposed on each other, due to which, depending on the application, more favorable kinematics of sliding, reduction of surface compression, and .P.

It does not matter for the invention which of the parts is rotated: the first part with gearing means or the second part with a coil spring to achieve axial movement in the negative or positive direction. However, in particular, for reasons of a lower moment of inertia of the first part, it may be especially preferable to use the part with a coil spring in a stationary mode, and to set the part in motion with means of engagement.

In addition, it may be preferable to rotate both parts with a given speed of rotation and by creating a difference in rotation speeds, for example by braking or accelerating one of the parts, to provide axial movement of one part relative to the other, so that the rotary drive in this sense can be a brake , for example, an electromagnet or a hydraulic gripping cylinder, which accordingly brakes one part, for example, relative to a fixed housing, and the rotary movement necessary for the drive takes from the entire rotating system on which the drive can be mounted. It may be particularly preferable, in particular, for a shaft rotating in only one direction, depending on the desired axial movement, to brake, for example, the first part relative to the stationary body and the other part to be fixedly connected to the shaft. In this case, a change in the direction of axial movement can be achieved due to the fact that the other part is fixedly connected to the shaft, respectively, with a rotating element, and for example, the first part is braked relative to the fixed body. For a better understanding, you can imagine such a drive as a rotating screw with a nut screwed on it, while with the same direction of rotation, either the nut or the screw are braked against the fixed element, and in one case the nut is tightened, and in the other, loosened.

In a preferred embodiment, it is possible to use, for example, a combination of at least one freewheel and at least one brake actuating electromagnet or hydraulic pickup cylinder, and in one embodiment, both parts can be arranged, each of which is equipped with a mechanism freewheel on the shaft, and freewheel mechanisms are turned on oppositely with respect to their direction of action and equipped with an appropriate brake. hull housing.

When using the drive according to the invention in the push and pull directions, it may be preferable to provide various means of engagement for the pull and push directions, which however are included in the same intermediate space between the turns and can be axially spaced apart from each other.

The gearing means for the drive according to this invention is configured to provide the necessary axial support on the coil spring to absorb axial forces, and the radial gearing provides at least one slot along the perimeter for the passage of the coil spring or belt. In this case, it is preferable to implement the engagement means in the form of a threaded coil or an inclined section in order to guide the coil spring along the longest section of the perimeter and evenly distribute the forces arising between the engagement means and the spring. In this case, the engagement means can be fixed on the first part using conventional joining methods, such as welding, induction welding, riveting, crimping, etc. In addition, at least the first part can be manufactured using pressure treatment methods, such as pressing, deep drawing, lateral extrusion, etc., and the engagement means can be extruded onto them, so that the parts made using these methods are not at all require refinement or need only minor improvement.

Due to these devices, the axial displacement of the engagement means relative to its starting and ending points is ensured, when considering the travel of the guiding means in the peripheral direction, and the spring wire, respectively, the spring band passes between the start and end points, and it is assumed that the engaging means has the shape of a single thread stroke. The offset of the engagement means between which the spring wire extends is preferably equal to the thickness of the spring wire. In this case, the axial displacement is chosen so that the engagement means compensate for the coiling of the spring wire, that is, so that the area of the engagement means, which in the axial direction is directly surrounded by the passing spring wire and the decreasing portion of the coil spring, is axially displaced, preferably by the diameter of the spring wire in the direction of decreasing section of a twisted spring. It goes without saying that the concept of a twisted spring includes any other implementation, such as a spring band and vice versa.

According to the invention, the engagement means described above as a thread turn may have various preferred embodiments. Thus, for example, a plurality of perimeter-distributed, radially extending toward the coil spring, connected to the first pin part and acting as a thread turn can enter the intermediate space between the coils, and in this case it is preferable to arrange the pins in the axial direction along the imaginary thread winding. The number of pins, depending on the requirements, can be from two to twelve, preferably from three to five, and it is preferable that the pins extend as far as possible, for example, about the entire radial width of the spring wire. In addition, it is obvious that for traction and pushing directions, it is preferable to use separate sets of such pins.

In particular, to optimize the efficiency and minimize friction, it is preferable to install means of engagement with the possibility of rotation relative to the coil spring. Particularly preferred are, for example, embodiments in which the contact areas of the pins with the spring wire, which are radially inwardly directed, which in this case is preferably made as a spring band, are provided with rolling or sliding bearings. To further minimize the axial direction of the radial engagement of the pins, embodiments may be particularly preferred in which the pins in the axial direction are directly supported by a coil spring and placed in the first part with the possibility of rotation around their longitudinal axes using rolling or sliding bearings.

In another preferred embodiment, an arrangement of the engagement means can be provided in which they are located around the perimeter at approximately the same axial level, and they have different diameters or supports, for example, rolling or sliding bearings of different diameters, to display the axial stroke of the spring wire which relies the wire in the axial direction.

According to the invention, both parts can be radially inserted into each other, and it is particularly preferable to arrange the second part radially inside the first part. In such embodiments, in particular, it is preferable to arrange the coil spring radially outside the second part and thus radially between the two parts.

Another preferred exemplary embodiment has a first part with grooves made in a manner similar to a thread winding or thread winding segments, in which rolling bodies are inserted, which from the groove enter a twisted spring and thereby form an engaging means. It is preferable to have at least two rolling elements distributed around the perimeter, which can be inserted into already connected parts through an opening extending radially outward in the first part, the opening being then closed from the outside. In the same way, after assembly, pins distributed around the perimeter can also be mounted.

In addition, a plurality of rolling bodies can be introduced into an appropriately made, for example in the form of a peripheral thread or guiding groove or recess, the rolling bodies can be connected at their end and start points, so that the rolling bodies, due to their different spring the relative speed tape can run along the perimeter of the groove, moreover, in the transition zone of the rolling elements from the end of the turn to the beginning of the turn, the groove is preferably expanded in the radial direction and the spring tape in this it can pass in the axial direction through the thread round radially inside the rolling elements, preferably without contact with the rolling elements. In this regard, it is preferable to place the rolling bodies in a cage for the rolling bodies connected to the first part and to provide a radially widened sector of the groove only in the area in which the rolling bodies extend in the axial direction of the spring band. In particular, in order to better guide the rolling bodies and increase the surface of the spring band support on the rolling bodies, for example, to optimize contact pressure, the rolling bodies can be barrel-shaped and roll with their peripheral surfaces along the groove side and along the spring band.

According to the invention, both parts, for example, to reduce axial clearance or to provide special power characteristics, can be prestressed in the direction of action of the drive. For this, the coil spring itself can serve due to the use of a compression spring, which in the assembled state strains both parts in the axial direction, and / or due to the design of the coil spring, in which the coils in the assembled state are preferably in contact with each other or, if necessary, are located on a certain distance from each other. In this case, at least one bearing may be provided between the first part and the coil spring.

In addition, for pre-stressing both parts, an axially-acting energy accumulator such as a coil spring, gas cylinder or the like, which may be at least a coil compression spring resting axially on both parts, or consist of plane springs distributed around the perimeter, the corresponding ends of which are fixed on both parts, and which can simultaneously center both parts on top of each other. In addition, it may be preferable to axially strain at least one part, preferably a part mounted axially movable by means of a compensation spring, which compensation spring may also have a centering effect.

Another preferred possibility of centering both parts relative to each other and thereby relative to the coil spring, in particular in cases of application of an uncompensated, respectively, tension spring, is the ability to self-center the coil spring relative to its longitudinal axis. For this, a coil spring, in particular when making a spring wire in the form of a spring band, can have a cross section, for example, in the form of a V-shaped axial profile, in which one coil in the axial direction passes inside the other and is centered. In this case, it is particularly preferable to position the V-shaped profile with its tip against the direction of action of the coil spring, i.e. point the tip in the direction of travel of the axial drive. This embodiment of the coil spring may additionally have a different spring stiffness for supporting the spring coils against each other due to the effect of a Belleville spring, when the coils are already touching each other and then are loaded axially, so that one coil spring with two spring characteristics occurs, both of which the characteristics can be used in different ways, for example, as a compensation spring or as a damper for axial movement or the like.

According to the invention, the drive can be driven by the relative rotation of both parts with respect to each other. This is due to the differential angular velocity of both parts, that is, due to the fact that one of both parts can be in a state of rest or rotational motion, while the other part is rotated with a different rotation speed relative to the first part. To do this, one part can be rotated relative to another part using a rotary drive due to the fact that the rotary drive is supported on this part or on a part that is stationary relative to the housing. In this case, it may be preferable that the stationary, respectively, rotating during activation of the drive with constant angular velocity component moves axially so that it would be possible to provide, for example, also not rotating, respectively, rotating with the corresponding angular velocity element without a device for compensation for the difference in rotation speeds. For a given difference in rotational speeds between the part and the axially loaded element, for example, if the drive is designed so that the axially moving part rotates, it may be preferable to install both parts with the possibility of rotation relative to each other using, for example, a rolling bearing.

In order to prevent the engagement means from stopping in the spring attachment, it may be preferable to provide a stop before reaching the maximum spring rotation, which can act in the peripheral direction and / or in the axial direction and, due to its effect, act in a damping manner on the rotation movement, so that, for example, it can be prevented jamming both parts at the stop. In addition, the limitation of the rotary drive in at least one direction can be carried out as an alternative solution or in addition to the engagement means at the end of the spring. For this, it is possible, for example, to appropriately electrically limit the electric motor serving as a rotary drive by using a displacement sensor that monitors the maximum working stroke, for example, by measuring and evaluating the distance traveled and / or the number of rotor rotations, and at least one sensor may be a path increment sensor.

The rotary drive, according to the invention, can be any device with which it can rotate one part relative to another part. Most preferred are electric motors. Other rotary drives, in particular in cases of use without electric energy or when the use of electric energy can be dangerous, for example, in an explosive atmosphere, can be turbine drives, for example turbines driven by compressed air, which can also be used in cases where the use of compressed air as a drive medium can be more economical. The torque transmission from the rotary drive to the driven part can be carried out, for example, by means of a gear transmission, planetary gear, belt drive, or the like. with a decrease or increase in rotation speed.

The rotary drive preferably fits into the geometric dimensions of the drive without significantly increasing its volume. The rotary drive is preferably located at least inside the radial space of both parts, however, more preferably radially inside the second, respectively, outer part, or in a particularly preferred example, is performed radially inside the first, inner part when the parts are inserted into each other. In this case, both types of drive can have advantages, namely, a drive of a radially external as well as a radially internal part. It is particularly preferable to position the drive around a shaft that can rotate, with the radially inner part having an opening for passing the shaft, and install the drive rotatably on the shaft or together with the shaft or mount it on the housing to rotate relative to the rotating shaft. In this case, the installation of the drive on the shaft, respectively, fastening on a stationary part relative to the housing can be carried out on any of both parts. In this case, the rotary drive can also be located around the shaft, and it also has an opening the size of the diameter of the shaft. It is preferable to use an electric motor whose rotor has such an opening. In this case, the rotor can be mounted without the possibility of rotation relative to the shaft, for example, by means of gearing on the shaft, and the housing is respectively fixedly connected to one of both parts or can be supported on the shaft for rotation.

In addition, it may be preferable to install several, for example, two drives, radially in each other, so that in the axial direction there will be two drives with a minimum of usable space. In the form of such a design, it is possible, for example, to perform double clutch in the drive chain, in which the radially located inside the actuator actuates the cup spring of the first clutch, and the radially external drive - the cup spring of the second clutch. In this case, both drives can be driven, for example, in parallel or sequentially with the help of one electric motor, or both drives can be driven individually by a corresponding electric motor.

In particular, in order to minimize the structural space of the drive, it may be preferable to integrate the axially movable part directly into the rotating part of the rotary drive. Another part can also be integrated into the rotary drive housing. In a corresponding exemplary embodiment with one electric motor as a rotary drive, the electric motor rotor has a protrusion for axial load on an element which is formed by a coil spring, according to the invention, or which is fixed with the possibility of joint rotation with a coil spring, according to the invention, for example, due to the fact that it engages with the axial groove provided in the rotor. In this case, the axial protrusion can be displaced in the axial direction relative to the rotor, for example, the rotor can be made in the form of a sleeve, and the axial protrusion is displaced in the axial direction radially inside the sleeve, so that in the initial position without axial displacement, the protrusion is almost completely in the rotor. For this, a gearing means can be provided on the motor housing, which extends radially from the outside into a coil spring.

In some applications, it may be preferable to perform axial movement of the drive as self-braking. In other cases, it may be preferable to drive non-self-locking. The parameter influencing these properties may be the choice of the spring wire pitch, which for the manufacture of a self-braking embodiment can be very small, and in non-self-braking embodiments it can be correspondingly large.

In this sense, execution examples are also possible, which, after applying a large axial force, are tensed, and after removing this force, at least partially come back, i.e. they can be turned on. This partial problem can be solved using a drive in which the relative movement between the first and second parts is elastically damped, for example, using an energy accumulator. So, for example, in the area of the drive stop, an energy accumulator can be charged, which again gives off its energy in the form of a rotation pulse in the opposite direction, as soon as the rotational force of the rotary drive supported through the freewheel starts to decrease. In addition, an axially acting energy accumulator can be provided between the coil spring and the housing of the engagement means, against which the rotary drive works against the power component, so that with the weakening force of the rotary drive, the available self-braking of the drive in the opposite direction is removed and reversal can be achieved axial feed without actuating in the opposite direction of the rotary drive. In addition, changing the direction of the drive can be accomplished by resiliently suspending the entire drive in a peripheral direction with respect to a part of the housing or shaft. It may also be preferable to move the engagement means against the stop with the non-self-braking inclined portion when turning by means of a rotary drive, and after turning off the rotary drive, the engagement means are again turned back and thereby move in the opposite direction of the axial feed created by the rotary drive.

The drive may be part of a machine or machine element, in which two machine parts must move axially opposite to each other, for example, in manipulators, robots, grippers, presses, turning and milling machines, feed devices, etc. In addition, it is possible to axially load, for example, sets of drive pulleys with female means. In automatic transmissions, switching actuators can be used to shift gears and / or timing devices. Furthermore, with such a drive, linear drives such as glass lifters, ceiling sunroof drive devices and the like can preferably be realized. By eliminating the drive usually acting due to the ratio of the self-braking forces of the drive, it is preferable to reverse the direction of the drive. So, for example, the load of the proposed device in the axial direction can be converted into a rotary motion. At the very least, the clutch can be deactivated using a drive acting in one direction, and when self-braking is eliminated, it is automatically switched on again.

In addition, the drive with compressed clutch can be used to automatically compensate for wear. In this case, the clutch is compressed in the pushing mode, i.e. opposite to the axial tension of both pressure plates, the force of the energy accumulator, for example, a Belleville spring. Due to the release of the energy accumulator, the clutch is expanded and after moving the energy accumulator in the other direction in the traction mode, it is attracted from the equilibrium state to the stop. With the help of the well-known, regulating in the peripheral direction under the action of the spring of the stepped mechanism, you can compensate for the resulting axial clutch clearance.

In another exemplary embodiment, according to the invention, it is provided that the drive is used as a friction clutch release device for connecting and disconnecting two shafts, the clutch may, for example, consist of a clutch disc which is fixedly connected to the shaft and provided with friction linings, which is located between two the possibility of tension in the direction of each other with the help of the axially acting drive, fixedly connected to the second shaft of the pressure discs, which is under tension in the axial direction of the pressing disks creates frictional engagement between the two shafts through the friction pads and pressure plates. In this case, the drive can control the axial load of the axially acting energy accumulator, which can preferably be a disk spring, and thereby connect or disconnect the clutch.

Such friction clutch may be preferred for automobiles for connecting a drive shaft, for example, a crankshaft of a drive unit, such as an internal combustion engine, to a drive shaft, such as a gearbox input shaft. For these applications, it may also be preferable to position the drive around the input shaft of the gearbox.

In another exemplary embodiment, a self-braking drive is provided with a compressed clutch, which compresses the clutch and again expands against the self-braking force, and in the compressed state, the rotary drive does not have to operate continuously.

In this case, for the kinematics of the disconnecting device, it may be preferable to provide the disconnection path axially acting to support the disconnecting force by the force accumulator.

For example, the separation movement due to the rotary drive can be supported by an auxiliary spring, which is compressed with the clutch closed and thereby facilitates the disengagement process, and accordingly accelerates by reducing the disengagement forces. In this case, the spring characteristic can be linear, progressive or regressive and coordinated with the interaction of forces in the disengagement mechanism, at least depending on the disk spring, spring properties of the linings and the stiffness of the clutch parts, to ensure small disengagement forces with good clutch function. It goes without saying that the information obtained can be successfully applied accordingly for exhaust clutches. For this purpose, it is preferable to use a locking spring, which is first strained to the maximum on the trip path and then, after passing through the maximum, supports the rotary drive by creating an axial force, and it preferably supports, accordingly compensates, the disk spring characteristic.

An clutch release bearing may be further integrated into the drive, which may be coupled to the drive part and may further compensate for the radial difference between the drive shaft and the input shaft of the gearbox. In this case, you can use the coil spring of the drive as a tension component for fixing radial alignment.

In addition, the drive can preferably be used to disengage the double clutch, in particular for starter alternators and / or hybrid drives in which both clutches can be driven independently of one another, so that the internal combustion engine can be disconnected while the electric motor it drives or slows down the car and at the same time it supplies electrical energy through regeneration. It may be preferable to engage the drive in traction or pushing mode. The effect of such a double clutch is described in more detail in patent application DE 19925332.3, the full contents of which are included in this description. In addition, it may be preferable to perform several, for example, both clutches of such a double clutch in relation to the compression force of the Belleville springs for only part of the torque transmitted by the internal combustion engine. To transmit the maximum moment of the internal combustion engine, for example, in the full load range, the actuator can load the disk spring with traction in traction mode, so that a pressing force of the clutch loaded in this way, which corresponds to the full moment to be transmitted, is generated. It is understood that, for this purpose, the cup spring is so connected to the actuator that the tongues of the cup spring can be loaded in both axial directions. Such exemplary embodiments may be particularly preferred when using clutches that are provided for automatically compensating for wear (self-adjusting clutches), because, in particular, when using a force sensor to detect wear by increasing the disengagement force and to compensate for wear using the adjusting ring force released by this battery simple adjustment of the adjusting device is possible.

In addition, it may be preferable to damp the rotational vibrations of the internal combustion engine with the help of the drive due to the fact that at the corresponding amplitudes of the unevenness of rotation, the clutch is slightly unclenched and due to this, the clutch works with slippage at the corresponding maximum moment. In this case, the drive control is preferably carried out using a rotary drive, which receives the appropriate control value from the engine control system. So, for example, to control a rotary drive, you can use the ignition signal for a gasoline engine or the injection signal for a diesel engine. For this, additional values can be estimated for correlation with the magnitude of the expected amplitude, for example, rotation speed, throttle position, torque sensor signal, or the like.

In another exemplary embodiment, it is provided to install a split flywheel with a clutch release system using a drive according to the invention. Moreover, the divided flywheel has at least two rotating masses that are rotatably mounted relative to each other against the action of the at least one peripheral direction of the energy accumulator, the primary rotating mass being on the crankshaft of the internal combustion engine and the secondary rotating mass being mounted for engaging with the input shaft of the gearbox through the clutch mounted on the secondary flywheel is connected to the gearbox. As mentioned above, the clutch made in the form of a friction clutch can be connected and disconnected using the drive, for example, due to the fact that the clutch loading disk spring is actuated by the drive.

In addition, it is preferable for the invention to control the rotary drive by means of a control device connected to it, for example via a bus system. In this case, it may be preferable to evaluate at least one sensor signal and control the drive depending on at least this value. The sensors for creating the corresponding signal can be used individually or in combination with a speed sensor for measuring the speed of rotation of a rotary drive, a displacement sensor of a rotary drive, an acceleration sensor of a rotary drive, a force sensor or the like, as well as an individual or cumulative quantity measured derivative or calculated from the measurement values of these sensors.

In particular, when using a clutch in an automobile, the drive can be carried out automatically and at the same time use a control device that, alternatively or in addition to the above sensors, evaluates and calculates at least one signal of the following sensors for the preferred control of the clutch processes: wheel rotation speed at least at least one of the drive wheels and / or one of the non-drive wheels, throttle position, vehicle speed, gearbox rotation speed , rotation speed of the drive unit, vehicle acceleration, lateral acceleration, wheel lock signal, gear engaged, moment clutch, oil temperature in the gearbox, oil temperature in the drive unit, wheel steering angle.

In addition, it may be preferable to automatically engage the drive so that the clutch actuated by pressing or pulling is driven by a hydraulic gripping cylinder, which in turn is driven by a master cylinder through an intermediate hydraulic line. This master cylinder, according to the invention, can be driven by a drive, the master cylinder, drive, control device and / or, if necessary, compensation springs or the like. can be integrated into one module, which, among other things, has the advantage that it can be easily mounted, and that the number of mounted parts can be reduced during the final assembly of the car.

In addition, the basic principle of two parts rotated relative to each other with means of engagement in the spring can be implemented according to the invention, so that a coil spring is used as a spring and the engagement means enter the coil spring in the axial direction. If one part is held motionless and the other is rotated, then there is a radial movement of the engagement means relative to the coil spring and, if performed appropriately, for example, when the engagement means are distributed along the perimeter, this action can be used to create a collet for coaxially fixing parts around the axis of rotation of the axial drive , for example, in lathes. In addition, with appropriate execution of the engagement means in the axial direction, the belt can be placed on them and the drive can be rotated, so that with a relative rotation of both parts of the belt relative to each other, it is possible to control the change in the diameter of the working surface of the belt and thereby in combination with another belt pulley , which can be equipped with the same drive, which can be controlled in addition to the drive of the first pulley, you can create a belt drive with a variable adjustable gear ratio m It is clear that the choice of these possibilities for the use of a radial drive should not be considered as limiting and not as covering all possibilities. In this case, the idea of the present invention corresponds only to all those possibilities of implementation, which contain a radial movement of two parts, in particular one mounted with the possibility of rotation around the axis of the part, and at the same time distributed along the perimeter of the means of engagement, which are included in the axial direction in the coil spring, and the parts are preferably rotated relative to each other.

The following is a detailed description of the invention with reference to figures 1-26, which depict:

1-3 - sections of examples of the execution of the drive;

4 is a sectional view of an exemplary embodiment of a spring screw;

figure 5 - reeling shown in figure 4 of the screw from the spring;

6 is a sectional view of another exemplary embodiment of a spring screw;

Fig.7 is a section of a screw from the spring along the line aa in Fig.6;

Fig - section of a screw from a spring with a specially made coil spring;

Fig.9 is a detail of a screw from a spring with rolling bodies;

figure 10 - reeling shown in figure 9 details;

11 and 11A is a section of a means of engagement of the rolling elements;

Fig - detail of a screw from a spring with rolling bodies;

Fig.13-14 - preferred embodiments of the clutch with the drive as a disconnecting device;

Fig - divided flywheel with a drive as a disengaging clutch device;

Figs. 16-23 are other examples of actuators and their clutch assemblies;

24 and 25 show an example radial drive according to the invention, and

Fig.26 is an embodiment of a radial drive according to Fig.24 and 25.

Figure 1 shows an example of the execution of the actuator 1 with a spring screw 10 and a rotary actuator 20. The actuator is located around the shaft 2 and is mounted on a fixed relative to the housing part 3. The spring screw 10 consists essentially of the first, carrier means 27 for engaging the part 11 and the second part 13, on which a coiled spring 12 is mounted, which is rotatably fixed relative to it.

In the shown exemplary embodiment, the rotary drive 20 is made in the form of an electric motor, and the stator 21, using a sleeve-like part 22 radially outwardly extending inside the stator, which has a radially outwardly aligned housing receiving opening 3 of the housing 3 and a flange 22a enveloping it, is connected to the housing 3 without rotation regarding him. A rolling bearing 24 is provided on the sleeve-like part 22, for example, in the transition zone to the flange 22a, on which another sleeve-like part 25 is mounted radially outside for rotation, which is firmly connected to the rotor 26 on its inner perimeter. According to the invention, the rotor 26 is the first part drive 1 with means 27 gearing, which are mounted on the rotor without the possibility of rotation relative to it. Means 27 of engagement, as shown in this exemplary embodiment, can be made of fixedly connected to the rotor, for example, welded, having a T-shaped cross-sectional profile directed radially outwardly of flange 27a, on which contact points 28 are provided, which are in axial contact with corresponding contact points 30 twisted in the form of a twisted spring of the spring tape 29.

The contact points 28 for reducing friction are rolled along the spring belt 29 between the engagement means 27 and the spring belt 29 by means of a rolling bearing 31, which is fastened with a pin 32 in a corresponding recess in the flange 27a. In the shown embodiment, three rolling bearings 31 distributed along the circumference are provided as contact points 28 with the spring tape 29 in the pushing direction and a corresponding number of rolling bearings not shown in the traction direction, both the pins 32 of the pushing direction and the pins of the traction direction are axially displaced direction relative to each other to match the pitch of the thread-like stroke of the spring tape 29. The individual turns 30 of the coil spring 12 are divided by means of engagement 27 into two sections 1 2a, 12b of a coil spring, wherein the coils 30a, 30b of the individual sections or blocks 12a, 12b of the spring are adjacent to each other, or due to appropriate winding and choice of stiffness, the springs 12 can have at least a small gap, so that the engagement means 27 can rigidly or with damping, lean axially on the second part 13 through one of both blocks 12a, 12b.

When current is supplied to the rotary actuator 20 with polarity for driving the first part 11 in the direction of winding the coil spring 12, for example in the clockwise direction, and when the second part 13 is stationary, the radial engagement means 27 transfers the coils 30a of the spring section 12a to the spring section 12b due to the fact that it is against the action of an axial energy accumulator, for example, axially stressed between the housing 3 and the coil spring part 13, it relies on the spring portion 12b. Due to this, the part 13 is moved relative to the part 11 in the axial direction to minimize the distance between the two parts, i.e. part 13 moves in the direction of the housing 3, and the actuator 1 operates, therefore, in traction mode. When reversing the direction of rotation, for example, by changing the polarity of the electric motor 20, the engaging means 27 are supported by a spring package 12a facing from the housing 3, which increases relative to the number of turns 30a due to the rotation of both parts 11, 13 with respect to each other and thereby increases the axial distance between by both parts 11, 13, i.e. the drive operates in a pushing mode, with the part 13 using the annular protrusion 14 can axially move any element relative to the housing 3, while with relative rotation between the element to be moved and the protrusion 14, a rolling or sliding bearing can be located.

Made without the possibility of relative rotation and with the possibility of axial movement, the connection between the housing 3 and the part 13 is carried out in the shown embodiment using a coiled spring 35, which is mounted on the part 13 using the protrusions distributed around the circumference or the annular protrusion 36 and centers the part 13 on the part 11 The spring 35 is fixed without the possibility of relative rotation in the housing and in the part 13. Alternative or additional centering can be carried out using the outer perimeter of the tool 27 heating on the inner perimeter of the part 13, and in the contact zone 37 can be provided with a sliding support and / or a self-centering device known for rolling bearings, respectively, an axial displacement compensation device that can compensate for the axial displacement occurring under some circumstances between both parts 11, 13.

Similar to the first exemplary embodiment, the actuator 101 is shown in FIG. 2, with an alternative axially displaceable and without relative rotation of the connection of the part 113 with the housing 103 using preferably three plane springs 135 distributed along the perimeter, which are stationary at one end connected to the part 113, and at the other end are fixedly connected to the body, for example riveted, and due to the flat springs can also be centered both parts 111, 113.

Figure 4 shows in detail an example embodiment of the spring screw 10 according to the invention, and figure 5 shows the corresponding retraction when the axial arrangement is changed relative to figure 4. The first embodiment, according to FIG. 1, should not be construed as limiting the location and execution of the spring screw 10 as the main drive drive unit according to the invention.

The spring screw 10 consists essentially of a part 13 with a twisted spring 12 connected to it without relative rotation, and a part 11 with engagement means 27 radially entering the coil spring 12, which consist of a set 32a of distributed pins 32c and a set 32b of distributed around the perimeter of the pins 32d, the latter being axially offset relative to the set of pins 32a in the peripheral direction. The sets of pins 32a, 32b are in axial contact with the spring band 29 by means of a rolling bearing 31 which is disposed on the pins, the set of pins 32a being used for the pushing direction and the set 32b for the pushing direction of the drive. The sets of pins 32a, 32b can be arranged in the peripheral direction along the twisted line in accordance with the passage of the spring tape 29, so that the spring tape on each segment of the perimeter rests without a gap. The sets of pins 32a, 32b are axially displaced relative to each other, preferably by the width of the spring band, and are located at one longitudinal end in the part 11 and at the other end in the flange 27a, which is fixedly connected to the part 11 by means of jumpers (not shown).

In the illustrated embodiment, the part 11 is located radially inside the part 13. The sleeve-like part 13 has a radially inwardly directed protrusion 14 at one end, on which a coil spring 12 rests, and is closed at the other end by a cover 38, for example, by means of a thread, bayonet connection , a press fit or the like, the other end of the coil spring 12 resting on the cover 38. Moreover, in particular with a rotary connection, it may be preferable if there is a rotary connection between the cover 38 and the coil spring 12, example, using a rolling bearing 39.

The coil spring 12 is connected to the cover 38 and / or to the protrusion 14 without the possibility of relative rotation, for example, riveted, or, as shown, inserted into the slot 40 of the protrusion 14, and the end of the spring can be shifted into the slot.

To prevent hard impacts, at the ends of the turning area of the spring screw 10, thrust rings 41, 42 are preferably resilient to prevent sticking, into which the flange 27a abuts at the maximum rotation of both parts 11, 13.

6 shows a spring screw 210 in which the carrier means 227 of the engagement of the first part 211 is located radially outside of the second part 213, on which the coil spring 212 is located without the possibility of relative rotation. The means of engagement in this embodiment are also made of pins 232, which In this case, they enter radially into the coil spring 212 and are mounted rotatably in the cylindrical body 211, for example, by means of rolling bearings, so that the pins are rotated relative to the body 211 and rolled about the perimeter of the spring band 229.

7 shows a section along the line AA of the spring screw 210 shown in FIG. 6. A radially outer part 211 is shown, which carries engagement means 227 and the coil spring 212 carries part 213. The engagement means 227 consist of two sets distributed around the perimeter, in this example, three pins 232a, 232b, on which the spring band 229 is supported in the axial direction coil spring 212 in the traction, respectively, in the pushing direction. When both parts 211, 213 are rotated relative to each other, the spring band 229 extends axially between the two pins 232a, 232b, respectively, and by winding the spring band causes axial movement of the parts 211, 213 relative to each other by supporting the pins 232a, 232b in the axial direction to the changing sections of the coil spring, depending on the direction of rotation. Part 213, as shown, may have a central hole 213a for the passage of the shaft. In the end zones of the coil spring 212, persistent dampers may be provided, similarly to FIG. 6.

Figure 3 shows another exemplary embodiment of the actuator 301, which is located around the shaft 303 radially inside the rotary actuator, which in this case is formed by an electric motor 320 with a stator 321 and a rotor 326.

The stator 321 is connected motionlessly with the part stationary relative to the housing and forms the first part 311 with engagement means 327, which are formed by shaped parts 332. Distributed along the perimeter and radially inside the coil spring 312 and formed into the coil spring 312, the stator housing 321a and the shaped parts can be made as a whole, for example, using the technology of deformation of steel sheets, or consist of several parts. The axial support of the spring tape 329 on the shaped parts 332 can be due to sliding friction, and on the shaped parts 332 and / or on the spring tape 329 can be applied to reduce the coefficient of friction, for example, in the form of oil, fluoropolymers or the like. or at least contacting parts may be hardened or have an improved surface. For example, it may be preferable to apply a layer of tungsten carbide, which can be made particularly strong with intermediate layers, for example, copper, chromium, nickel, tantalum and / or the like.

The second part 313 is formed by a rotor 326, with which the coil spring 312 is connected without the possibility of relative rotation and with the possibility of movement in the axial direction, for example, by means of a radial extension 312a, which enters radially into the axially extending groove 326a of the rotor 326, and the pushing action the direction is ensured by the coils of the coil spring adhering to each other, and in the traction direction by the spring characteristic of the coil spring 312. In addition, the axial movement of the rotor 326 may be preferable. accordingly, the inner cup is made of two parts of the rotor, and axial movement without the possibility of rotation of the inner cup relative to the rotor can be achieved using rolling elements that extend in the axial grooves of both parts. Helical grooves can enhance the action of the drive with the same direction of rotation with the coil spring or weaken with the opposite direction of rotation, respectively, increase the voltage of the coil spring, respectively, weaken.

The coil spring 312 is centered on the shaft 303 and can be provided at its end loading the element to be moved, in particular, at different angular speeds of the coil spring and element, with a friction-reducing bearing, for example, a rolling bearing 312b. The entire drive is preferably closed by a casing, in particular, the space radially outside the stator 321 can be filled with grease, respectively, lubricated and sealed with seals 333, 334 between the rotor 326 and the stator 303, and the clutch release bearing 312b preferably provides a seal relative to the shaft 303 and compensates for axial displacement between the shaft 303 and the actuator 301, in particular by using self-centering in itself.

FIG. 8 shows a schematic sectional view of the structure of a spring screw 410 with a coil spring 412 having a V-shaped cross-sectional profile. Otherwise, the implementation of the spring screw 410 corresponds to or similarly to the implementation of the spring screw 10, 210 in the above-described examples, according to figures 4 and 6.

The V-shaped cross-sectional profile is particularly suitable for centering and / or stress of the coil spring 412, and the stress can be provided by the axial load of the spring turns 412a supported against each other, while the individual turns 412a act as plate-shaped or membrane springs. For this, the coils can already be adjacent to each other, so that a two-stage characteristic of the spring is created, which is based on the spring characteristic of the coil spring and on the spring characteristic of the cup spring. Such a spring 412, for example, to optimize the gear ratio of the drive, can be wound with the coils adjacent to each other or with prestress and act spring in the direction of action of the drive.

Fig. 9 shows a section through a spring screw 510, in particular for a drive with engaging means 527a, 527b operating in the traction, respectively, in the pushing direction, which are made in the form of rolling bodies shown in Fig. 11 in section along the line BB Fig.9, and located in the clip 550 for rolling elements, and along which the spring tape 529 of the coil spring is rolled. The clip 550 for rolling bodies is fixedly connected to the first part 511, which in this embodiment is a part driven by a rotary drive and forms a perimeter sector for the rolling bodies 527a, 527b and rests them in the radial direction and axially on the spring band 529, between the turns 529a, 529b of which is arranged with a radial clutch a holder 550 for bodies of revolution, the bodies 527a, 527b rolling in a peripheral direction and rolling along a spring band.

In a given sector of the perimeter, the bodies 527a, 527b are radially outwardly displaced into the housing 511, and the spring band 529 extends axially in this region past the rolling bodies 527a, 527b. At the same time, when the spring screw 510 is rewound, according to Fig. 9, as shown in Fig. 10, there are transition zones of the first and second row of rolling bodies 527a, 527b, which are located in the rolling body clip 550. In the peripheral zones 550a, 550b, which occupy the angular zone α, β, where 120 ° <α <160 °, 120 ° <β <160 ° C, where α, β are preferably 140 °, rolling bodies 527a, 527b are transferred to the housing while both rows of rolling bodies are offset relative to each other in the peripheral direction in accordance with the pitch of the spring band 529. The passage of the rolling bodies 527a, 527b in the cage 550 is such that the pitch of the spring band 529 is compensated around the perimeter, i.e. the beginning of the clip 550 is displaced in the axial direction relative to its end by the width of the spring band. This axial distance is compensated by the corresponding passage of the rolling bodies 527a, 527b in the housing 511. It will be appreciated that the housing 550 for the rolling bodies can be integral with the housing 511, for example, as a correspondingly deformed portion of a steel sheet.

Fig. 11a shows a section along the line CC in Fig. 9, in which the rolling body 527a is already partially located in the housing 511, and the rolling body 527b is still in the cage 550. The spring band 529 is driven by rotating in the direction of the arrow (see 10) by a housing 511 and is laid in layers on both sides of the rolling bodies 527a, 527b depending on the direction of rotation, so that the drive made with the spring screw 510 can be used in traction and pushing directions.

12 shows an embodiment of a spring screw 610, modified with respect to the spring screw 510, in which with respect to the outer casing 613 there is a radially inner part 611, which as a means of engagement has a yoke 650 provided with rolling bodies distributed around the perimeter, for example, needle rollers 627 driven by a rotary drive.

To prevent a segmented clip for rolling elements, at least a clip 650 and fixed to the housing 611 without being rotatable relative to it, the coil spring 612 is offset by their rotation axes relative to each other, so that the spring tape 629 in one sector of the perimeter of the clip 650 is axially supported on of the rolling body 627, and in the rest of the perimeter sector it extends radially outward in the axial direction past the rolling body clip 650 for shifting sections of the coil spring depending on the direction of rotation.

In order to optimize the passage and rolling conditions between the rolling bodies 627 and the spring band 629, the coil spring 612 is preferably located in the housing 613 so that the pitch of the coil spring 612 is compensated when the spring band adheres to the rolling bodies 627, i.e. so that the area of the spring band adjacent to the rolling bodies is approximately flat. For this, the axis of rotation or the middle axis of the coil spring 612 is rotated relative to the axis of rotation of the cage 550 for rolling elements, respectively, relative to the axis of rotation of the housing 613, to compensate for the spring pitch. It will be appreciated that when the spring 612 passes appropriately inside the spring and is driven radially outside from the raceway holder 650, a corresponding spring screw can be formed.

The drive described with reference to the preceding figures and manufactured using the shown spring screws is suitable, in particular, for connecting and disconnecting clutches connecting two shafts, for example friction clutches in an automobile. The drive according to the invention can be used instead of mechanical or hydraulic disconnection, moreover, it can be a manually driven or automatic clutch and this clutch can have an adjusting device, in particular an automatic self-regulating device. DE 19504847 describes, for example, friction clutch properties, in which a drive can also be advantageously used. The drive can, in particular, be used as a disconnector for traction and / or squeezed clutches or double clutches, and the clutch, in particular for dosing the torque to be transmitted, can work at least partially with slipping or with full coupling.

On Fig shows an example of the friction clutch 750 with the drive 701, according to the invention, which is located on a split flywheel 770 and has a self-adjusting device 790 wear compensation.

The divided flywheel 770 consists of a primary mass 770a in the form of an internal combustion engine (not shown) located on the crankshaft 703 without the possibility of rotation of the disk part 771 relative to it, the ignition marking 772 riveted with it and forming the chamber 771a of the disk part 773 with it radially outside, and located radially outside the starter gear rim 771c, and the secondary part 770b in the form of a clutch pressure plate 751 resting on the disk part 771 and fixedly connected radially inside from inside the flange chamber 771a part 751a, as well as those operating in the peripheral direction, at their ends loaded with primary and secondary load devices 771b, 751b of energy accumulators 774. The divided flywheel 770 during torsional vibrations of the internal combustion engine due to the relative rotation of both masses 770a, 770b acts against the action of the energy accumulators 774 as a torsion vibration damper, and additionally with the relative rotation of both parts 770a, 770b between both parts 770a, 770b it may itself be known how to operate the friction device 775 with or without a pivot clearance and, due to this, delayed friction caused by this if necessary.

On the clutch pressure plate 751, it is rotatably relative to it and axially displaceable with respect to it using flat springs 753, the pressure disk 754, between which the friction surfaces 752, 754a are clutchably engaged, the friction linings 755 of the clutch plate 755, which is connected to the input shaft 703 of the gearbox cannot be rotated relative to it, due to which the torque available on the crankshaft 703a is transmitted to the input shaft 703 of the gearbox.

The pressure disk 754 in the connected state is axially compressed with the axial-acting energy accumulator 757 and is compressed axially by the pressure disk and the disc spring tongues 757a are axially displaced and the clutch 750 is disconnected by the actuator 701 due to the inner part 713 being driven rotation by means of a rotary drive 720 and due to this, the outer part 711 moves in the clutch direction 750 against the action of the Belleville spring 757. To compensate for the difference in rotational speeds first spring 757 and the isolator 711 to the transfer of effort provided rolling bearing, for example, the bearing clutch 711a. The drive 701 is located around the input shaft 703 of the gearbox and is fixed by means of a rotary drive fixed to the housing 722, for example, an electric motor 720, or made integrally with the housing of the carrier part 722a on the transmission housing 703b, for example, by means of bolts 703d.

The rotatable inner part 713 with a coil spring 712, which is respectively strained axially between the stops 714, 742, is fixedly connected to the rotor 726, while the stator 721 is fixedly connected to the housing 722 of the electric motor 720. The outer part 711 using preferably three distributed along the perimeter of the flat springs 735 is connected without the possibility of relative rotation and with the possibility of axial movement with the fixed part of the housing, for example, as shown, with the bearing part 722a, so of actuator 701 is fully assembled to the housing 703b.

The principle of operation of the disconnecting device 750 using the actuator 701 is that when driving the axially motionless part 713 of the housing using the rotary actuator 720, the spring band 729 of the coil spring 712 thereby passes by the engagement means 727 and the coil spring section 712b at least partially shifted to the coil spring portion 712a on which the engaging means 727 rest, thereby axially moving the outer part 713 in the clutch direction 750 and the clutch disengages against the action of the disk spring 757. The clutch engages in principle with a different direction of rotation of the rotary actuator 720, and the disk spring 757 and the flat springs 735 contribute to this, and a spring bag 712 is formed on the clutch end of the coil spring 712, which can be supported in the axial direction of the tool 727 gears.

The clutch 750 has a known self-adjusting device 790 per se with axially tensioned between the clutch cover 792 and the disk spring 757 by the force sensor 791 and with an adjustment ring 793 pressed in the peripheral direction by the energy accumulators 791a to the clutch cover 792 and axially clamped between the disk a spring 757 and a clutch cover 792, which with an axial deviation of the force sensor 791 and thereby of the disk spring 757 with increased separation forces, for example, due to the oblique position of the disk th spring 757 due to, for example, wear of the friction linings 755, compensates for the axial clearance arising between the disk spring 757 and the clutch cover 792 by turning in the direction of action of the energy accumulators 791a until the axial clearance is selected by means of those provided on the adjustment the ring 793 distributed along the perimeter of the axially made inclined sections 793a.

FIG. 13 shows a friction clutch 850 with an actuator 801, in which a rotary actuator is inserted into the actuator by rotation of the clutch 850. For this, the actuator 801 is integrated into the clutch 850 and the actuator part, in this case the part 813 with a coil spring 812, through a connection with the friction closure or the safety friction clutch 813a is connected to the clutch cover 892 through the flange portion 813b or is integral with it, the clutch cover 892 and the cup spring 857 are shaped so that the actuator 801 is axially closed Ryshkov clutch 892, the clutch actuator 801 and 850 form a single unit with reduced axial space. The flange portion 813b may be axially tensioned relative to the housing 813 to form the friction contact of the friction clutch 813a. At the same time, the moment transmitted through the friction clutch 813a is greater than the friction moment of the actuator 801. Between the part 813 and the beam 822 fixedly mounted on the housing, a frictional closure can be created using the beam 822 mounted on the beam without the possibility of rotation relative to it and with the possibility of axial movement, when a current is displaced in the axial direction of the electromagnet 820a, at a preferably conical friction contact 875.

Part 811 with engagement means 827 forms, at an intermediate location of the friction disk 876, an axial load device for the disk spring 857 controlled by the friction moment through the disk spring tongues 857a. Part 811 is mounted to be able to engage with friction closure with housing 803a through a preferably tapered friction contact 877 with a second mounted axially displaceable and not rotatable on beam 822, for example by axial gearing (not shown), by an electromagnet 820b which, when current is applied, moves axially.

Clutch 850 is a compressed clutch, i.e. when the drive is displaced backward in the axial direction, as shown in FIG. 13, the clutch is disengaged, the friction linings 855 do not transmit the moment from the drive unit, which, using a crankshaft with a flywheel 870, which can also be a divided flywheel, made as a torsion vibration damper, through a clutch disc 856, mounted without the possibility of relative rotation on the input shaft 803 of the gearbox, as an alternative solution with or without torsional vibration damper 856a, to the input shaft 803 of the gearbox. When moving the part 811 in the direction of the flywheel 870, the tongues 857a of the disk spring 857 are loaded in the axial direction and the disk spring 857 moves axially mounted and connected without the possibility of relative rotation with the flywheel 870 and the clutch cover 892 by means of flat springs 853 of the pressure disk 854, due to which, between the pressure plate 854, the flywheel 870 and the friction linings 855 of the clutch plate 856 with the torsion vibration damper 856a, a frictional closure occurs that transmits the engine torque and the input shaft 803 of a transmission.

The principle of operation of the actuator 801 for connecting and disconnecting the clutch is as follows: in the main position with the clutch open when the engine is running, both parts 811, 813 rotate at the same speed of rotation. To engage the clutch part 813 due to the supply of current to the electromagnet 820a is braked by frictional closure on the friction contact 875 relative to the housing 803a. Due to this, there is a difference in the rotational speeds between the two parts 811, 813 and due to this, the axial movement of the part 811, which leads to the loading of the disc spring tongues 857a and engagement of the clutch. When the clutch is fully engaged, using the magnitude of the current in the electromagnet 820a and / or using a sensor such as a clutch displacement sensor, a torque sensor and / or a rotational speed sensor, it is possible to adjust the axial position of the part 811, i.e. hold unchanged or coordinate with the necessary pressing force to transmit torque corresponding to the vehicle's driving mode. In this case, the clutch compression occurs with a force reduced in accordance with the gear ratio of the drive 801, for example, with a shut-off force of 1000 N in the range of 100 N.

To disengage the clutch, the electromagnet 820b is axially moved until a frictional closure is formed on the friction contact surface 877 of the part 811. This results in a difference in rotational speeds between the two parts 811, 813, which is opposite to the difference in rotational speeds during the engagement process, since the part 811 rotates faster than part 813, whereby part 811 moves axially backward and the clutch disengages.

In this case, it may be preferable to connect the plate spring tongues 857a immovably in the axial direction with the part 811. In particular, when using a self-adjusting device to compensate for the wear of the friction linings 855, the disk spring 857 can be axially moved back through the part 811 to the stop representing the working engagement point, for example, to the clutch cover 892, and the resulting gap between the pressure plate 857 and the disk spring 857, measured by a force and / or displacement sensor, compensate for in a natural way, for example, by means of a compensation ring with peripheral, axially ascending inclined sections. It is clear that such a sensor takes into account the axial movement of the pressure plate to the operating point and the spring characteristic of the plates and / or flat springs 853.

It is understood that the clutch can also be disconnected and connected using one axially displaceable electromagnet instead of electromagnets 820a, 820b, which at each end forms frictional contact with friction contact surfaces 875, 877. The use of two electromagnets has the advantage that the reverse movement of part 811 to deactivate clutch 850 can occur with path length control, i.e. both electromagnets 820a, 820b can be actuated purposefully simultaneously or alternately, which provides finer control of axial movement.

On Fig shows an example of the friction clutch 950, which is similar to the friction clutch, according to Fig, and there is only one electromagnet 920, made with the possibility of axial movement and connected to the housing 903a without the possibility of rotation relative to it, which is mounted with the possibility of connection with using frictional closure by means of friction contact surface 977 with part 911. The actuator may have a spring screw, according to the invention, shown in FIGS. 4, 6, 8, 9, 12, or shown in this uchae mechanism 901 with inclined portions which has at least two distributed along the perimeter, shtykoobraznyh inclined portion 912a with a radial and axial component of the path and configured complementary manner inclined portions 912b in the part 911, 927 between which the rolling bodies.

In the presence of the same friction ratios on the parts 911, 913, the clutch release mechanism 901 remains stationary. When the friction contact surface 975 is frictionally closed by means of an electromagnet 920, the part 913 is braked relative to the housing 903a and, through the rotary cover 992, transmits rotational motion to the mechanism with inclined sections, rotates the inclined sections 912a, 912b relative to each other with the help of guide bodies of revolution and moves axially due to the axial component of the inclined sections and thereby includes the clutch. The shutdown process is carried out due to the braking of the part 911 through the formation of a frictional closure with the friction contact surface 977.

On Fig shows a section of a flywheel 1070, which has a primary mass 1070a and a secondary mass 1070b, which are installed with the possibility of rotation relative to each other against the action of the damper containing the battery 1074 energy. The flywheel 1070 carries a friction clutch 1050, which is adapted to be actuated through a disconnecting device 1020. As follows from a comparison of FIG. there is no need for a detailed description of Fig.16.

Actuator 1020 includes an electric rotary actuator 1020a, which in this case is made in the form of a multi-pole electric motor with an external rotor.

The electric drive, respectively, the electric motor 1020a contains a stator 1002, which is without the possibility of relative rotation, respectively, through a press fit, is connected to a bearing flange 1001 having a sleeve-like protrusion 1001a. The bearing flange 1001 rests in this case on the gearbox housing, respectively, on the clutch cap 1035. The windings, respectively, the frontal parts 1003 of the windings are located under and / or outside the lined package 1002 with distribution along the perimeter. The windings, respectively, the frontal parts 1003 of the windings, can be made and arranged so that between them there is sufficient space to accommodate Hall sensors in them. Using these Hall sensors or other sensors, it is possible to determine the number of relative rotations, respectively, the angular positions, as well as the direction of rotation between the stator 1002 and the surrounding rotor 1004. The rotor 1004 preferably contains permanent magnets. These permanent magnets are preferably composed of rare earth magnets. Magnets should consist of a material that can withstand high temperatures and at the same time has a high energy density. In this case, the temperature resistance should be of the order of at least 200 ° C, preferably up to 350 ° C and above. The magnets may preferably consist of individual plates that are mounted directly on the rotor housing 1007. Such fastening can be carried out, for example, using adhesive bonding. However, it may be appropriate to use a cermet ring that is magnetized after being shaped.

The latter embodiment has the advantages of low manufacturing cost and easier installation.

The rotor 1004 is supported relative to the stator 1002 on a support 1005, which in this case is made in the form of a deep groove ball bearing. In the shown embodiment, the housing 1007 of the rotor 1004 serves directly for support. To ensure an accurate concentric position between the stator 1002 and the rotor 1004, a support place 1006 is provided, which is located in the axial direction at a distance from the support 1005, which in this case is made in the form of a sliding bearing. The bearing location 1006 may, however, also be a rolling bearing, such as, for example, a needle bearing or a ball bearing. By using both of the support sites 1005 and 1006, a predetermined radial clearance is established between the rotor 1004 and the stator 1002. In addition, by using the support sites 1005 and 1006, contaminants can be prevented from entering the area between the stator and the rotor. Preferably, the rolling bearing serving as the bearing seat 1005 has at least one axial seal which prevents contaminants from entering the bearing 1005, respectively, in the inner area of the stator 1002 and rotor 1004.

The spring band 1015 is housed in an annular recess, respectively, in a seat bounded respectively by both parts 1011 and 1012. The bottom of the recess in the axis direction preferably has an axial lift that corresponds to the pitch of the spring band 1015. Both parts 1011, 1012 may be resiliently or immovably at a distance from each other and / or with respect to the means 1004b with an intermediate arrangement of the engagement spring 1015, respectively, to have such a distance from each other in the axial direction that the tape 1015 is almost b the gap is between the two parts 1011, 1012, and the occurring wear of the tape 1015 or parts 1016, 1017, 1018 can preferably be compensated by the elastic stress of the parts 1011, 1012 in the axial direction, so that the rotary clearance of the drive used as the disconnecting device 1020 is eliminated, or at the very least, it is possible to counteract it. This may be particularly advantageous when the pivoting movement, respectively the axial movement of the disconnecting device 1020, is monitored, controlled and adjusted using sensors, for example track increment sensors. Other details of the disconnecting device 1020 are shown in FIGS. 17 and 18, with FIG. 18 showing a view along arrow XVIII in FIG. On Fig shows a section of the disconnecting device 1020, which is offset at an angle relative to the plane of the section in Fig.16 around the axis 1095 of rotation. In FIGS. 17 and 18, the same parts, respectively, the same zones, are denoted by the same reference numerals as in FIG.

The oblique run-outs 1012a and 1011a shown in FIG. 17 ensure that the ends of the spring band 1015 are caught during installation and during operation of the disconnecting device 1020 — always the correct position.

The spring band 1015 is tensioned by the force generated by the tensioning means in the form of countersunk head screws 1020a. This tension force provides axial stress of the parts 1011 and 1012 relative to each other. Thus, due to the indicated tension force, the tape 1015 is fixed in both parts 1011 and 1012.

Inclined run-outs 1011a and 1012a additionally serve to guide, respectively, the bearings of the needle bearings 1017, respectively, of the bearing shells 1018, when the disconnecting device, respectively, the drive operates in the area of the last turn of the tape 1015.

In the shown embodiment, the ring 1010 is connected to the rotor 1004 without the possibility of rotation relative to it. This connection can be made by hot pressing, or by embossing or welding. The outer axially expanded portion of the ring 1004a serves as an axial stop for parts 1011 and 1012. By stopping the corresponding areas of the parts 1011 and 1012 in the ring 1010, the axial direction of travel of the actuator 1020 is limited.

As shown in FIGS. 17 and 18, the parts 1011 and 1012 with respect to the bearing flange 1001 are secured with a guide means 1013 without the possibility of relative rotation, and also are sent in the axial direction. To this end, pins 1013 and sliding guides 1014 are provided in the illustrated embodiment. The pins 1013 extend parallel to the axis of rotation 1095 and are fixedly connected to the bearing flange 1001. Slide guides 1014 are located on at least one of the parts 1011, 1012.

The clutch release bearing 1009 shown in FIG. 16 is shown on part 1011 in the shown exemplary embodiment. The clutch release bearing 1009 can be mounted on part 1011, for example, using a safety ring. The bearing 1009 is preferably in the form of a so-called self-centering clutch release bearing.

In order to prevent the actuator 1020 from returning to its original position when the engine torque is removed or, correspondingly, it is absent, it may be advisable to provide the entire guide assembly (bearing flange 1001 with guides) with one more support, so that the bearing flange 1001 can rotate around axis 1095. B In this case, the rotational moment (reference moment) created by the engine for driving can be supported by an energy accumulator, for example, a coil spring, which is provided between existent flange 1001 and non-rotatably mounted part, such as a cap or clutch gearbox housing. Using the energy stored in the specified energy storage device, the actuator 1020 can be returned to its original position.

As for the other features and the principle of operation, as well as embodiments of the actuating device, according to Fig.16-18, then the embodiments described in relation to Fig.1-15 are valid.

The clutch assembly 1170 shown in FIG. 19 comprises two friction clutches 1170a and 1170b.

The friction clutch 1170a has, in the illustrated exemplary embodiment, a clutch disc 1155a which is mounted so as to be connected directly to the output shaft 1101a of the engine, in particular the internal combustion engine. Friction clutch 1170b has a clutch disc 1155 that is coupled to an input shaft 1103 of a gearbox not shown. In the illustrated embodiment, the clutch disc 1055 has, as shown in FIG. 19, a main damper and a so-called idle damper. Friction clutches 1170a and 1170b have corresponding actuating means, which in the shown embodiment are formed by radially inwardly directed tongues 1193 and 1194 of Belleville springs. The tab springs 1195, 1196 having tongues 1193 and 1194 are rotatably supported by the corresponding housing 1197, 1198 and load the corresponding pressure plate 1199, 1199a. The inertial mass-forming part 1180 carries, respectively, forms opposite pressure plates 1181, respectively, 1181a of the friction clutches 1170b, respectively, 1170a. The component 1180 is mounted with the support 1182 so that it can rotate relative to the shaft 1103a when the friction clutch 1170a is open. With the friction clutch 1170b open, the inertia part 1180 can rotate freely with respect to the shaft 1103. When both clutches 1170a and 1170b are open, the inertia part 1180 can rotate with respect to both shafts 1103a and 1103. The inertia part 1180 can preferably be an integral part of the so-called starter-generator motor and in this case it forms a rotor. In addition, the electric motor can be designed so that it can serve as an electric motor for driving or at least to support driving a car. If necessary, you can abandon the starter function and provide a separate starter. The use and more precise implementation of such electric motors is described in the following patents: DE 19838853 A1, DE 19801792 A1, DE 19745995 A1, DE 19718480 A1.

Friction clutches 1170a and 1170b are configured to connect and disconnect using actuator 1120. Actuator 1120 has two actuators 1120a, 1120b. Both actuators 1120a, 1120b in this case rely on the gearbox housing or clutch cap, namely, similarly to the actuator 1020 described with reference to Fig.16. A comparison of the actuator 1120b with the actuator 1020, according to Fig.16, shows that both actuators equipped with an electric drive, at least with respect to the design are almost identical. The actuator 1120a also has, at least in relation to the functional parts, a structure similar to that of the actuator 1120b, respectively, 1020.

As shown in FIG. 19, the actuator 1120b is located radially inside and in alignment with the actuator 1120a. In addition, in the shown exemplary embodiment, both actuators 1120a and 1120b are axially inserted into each other, namely as shown in the exemplary embodiment, so that they end on the gearbox side in almost the same plane. However, for some applications, it may also be appropriate if the actuators 1120a, 1120b are at least partially offset from one another in the axial direction.

In addition, as shown in FIG. 19, in the actuator 1120b, the mechanical components necessary for the drive, such as the components forming the rotor 1104 and the stator 1102, are located radially inside the mechanical actuator, which in this case has a tape 1115. In the actuator 1120, this the radial arrangement is the opposite, since in it the rotor 1104a and the stator 1102a surrounding it are located radially outside the spring band. However, for some applications, it may be appropriate if, in the radial direction, the actuator 1120b has the same design as the actuator 1120a. However, the actuator 1120a may have in the radial direction the same principle construction as the actuator 1120b. In addition, it may be preferable if the actuator 1120 is configured so that between the mechanical axial drives having tapes 1115 and 1115a for the clutch disengaging bearings 1109 and 1019a, there are stator and rotor elements necessary for the corresponding electric drive. For example, the tapes 1115 and 1115a can have such a difference in diameters that the annular space formed between the two tapes 1115, 1115a is sufficient to accommodate a common stator, in which case a corresponding ring rotor is located radially inside and radially outside this stator. Due to the corresponding current supply, only one or both rotors can optionally be driven into rotation. If necessary, brakes can also be provided, with which you can selectively brake, respectively stop, the rotors. Such brakes may preferably be in the form of electromagnetically activated brakes, respectively, in the form of electromagnetic brakes.

The clutch assembly 1270 shown in FIG. 20 is in the form of a so-called double clutch, which can be used, for example, in conjunction with a gearbox switched under load, or with a gearbox with a power supply and / or power take-off. The clutch assembly 1270 has two independently engaged clutches 1270a, 1270b having a corresponding clutch disc 1255a, 1255b. The clutch disks 1255a, 1255b are connected through the hubs to a corresponding shaft 1203, 1203a. The shaft 1203b is made in the form of a hollow shaft that surrounds the shaft 1203, respectively, in which the shaft 1203 is located. The clutch assembly 1270 is connected to the output shaft 1203 of the engine. As shown in FIG. 20, both friction clutches 1270a and 1270b have a corresponding energy accumulator in the form of a Belleville spring 1295, 1296, which are rotatably supported by a corresponding housing 1297, 1298. Belleville springs 1295, 1296 have a main body serving as the energy accumulator. 1295a, 1296a, from which the tongues 1293, 1294 directed radially inwardly extend. Belleville springs 1295, 1296 load the corresponding pressure plate 1299, 1299a, which belong to the friction clutches 1270a, 1270b. Friction clutches 1270a, 1270b share a common opposed pressure plate 1281, which is a component of the inertial body 1280. The inertial body 1280 is located on the carrier disk 1282, which is connected by a drive to the output shaft 1203a. As shown in FIG. 20, the clutch device 1270 is configured so that the friction clutches 1270a and 1270b are axially located on both sides of the opposed pressure plate 1281.

The friction clutch 1270b is driven by an actuator 1220, namely, an actuator similar to that described with respect to FIG. 16, an actuator 1020, as well as with other figures.

Friction clutch 1270a, which is provided in the axial direction adjacent to the engine, is driven by an actuator, or actuator 1220a, respectively. The actuator 1220a relative to its constituent components, respectively parts and the principle of operation, is similar to that described with respect to other figures, actuators, respectively, actuators, in particular those described in relation to figures 16-19. This already follows from a comparison of the shown components of the actuator 1220a with the components of other actuators. You can see, for example, a spring band 1215, a stator 1202, a rotor 1204, a support 1205 provided between the rotor and the stator, and a clutch release bearing 1209. The disconnecting device 1220a is located around the sleeve-like gasket 1283, which is provided between the carrier plate 1282 and the output shaft 1203a of the engine. The rotor 1204 is located radially inside the stator 1202, which means that the actuator 1220a has an electric motor with an internal rotor.

The direction of the axially movable parts surrounding the clutch release bearing 1209 is provided by the tube-shaped zone 1201a, which is provided on the carrier part 1201b.

The friction clutch 1270b has a force compensation that optimizes the change in force to actuate the friction clutch 1270b, so that the maximum actuating force that the actuator 1220 must create can be relatively small. In the illustrated exemplary embodiment, force compensation is realized by means of a compensation spring 1286. Such compensation springs are described, for example, in DE 19510905 A1.

In addition, both friction clutches 1270a and 1270b are provided with a corresponding adjustment device 1287, 1287a, which compensates for at least the friction linings of the clutch discs 1255a, 1255b.

FIG. 21 shows a portion of a clutch assembly 1370 with a disconnecting device 1301 that is integrated into the clutch cover 1392 and axially loads a single-arm lever or energy accumulator 1357, such as a belleville spring, which in turn axially loads a push a disk 1354, which with the help of unimaged connecting means, for example, flat springs, is axially movable and centered with the cover 1392 or with another part rotating in natural with a crankshaft. The design shown can be used, for example, as a change to the clutch assembly 770, according to FIG. 15, whereby the corresponding parts 754, 792, 757, 720 are basically replaced. It is understood that such a design may be preferable for clutch with a rigid or elastic flywheel and / or with a two-mass flywheel.

The lever 1357 can be made rigid or elastic in the axial direction, for example, in the form of a disk spring, and rely with its radially outer end 1357a on the thrust ring 1392a inserted into the clutch cover. Radially inside the lever 1357, the pressure disk 1354 abuts by means of a thrust ring or by means of cams 1354a distributed around the perimeter, so that by means of a single-arm lever action, the pressure disk 1354 is axially moved by the pressure ring 1376 of the disconnecting device 1301, which presses against the radially inner the area 1357b of the lever 1357, and in conjunction with unimaged clutch parts, such as a pressure plate and a clutch disk rigidly connected to the input shaft of the gearbox, creates a friction closure tion between the crankshaft and the input shaft of the transmission. Using other embodiments of the linkage devices, other preferred forms of push or release clutches can be realized, in which case the push ring must be configured accordingly so that it can perform traction and / or pushing functions. In this example, we are talking about the pressure clutch, which in each axial position of the disconnecting device 1320 between the functional end zones, respectively, in any axial position of the pressure ring 1376 can be installed in a self-retaining manner due to the self-braking function of the axial drive 1310.

In the embodiment shown in FIG. 21, in particular, for reasons of economy of structural space, the axial drive 1310 of the disconnecting device 1301 is spatial, i.e. in the axial direction, is separated from the rotary actuator 1320. This reduces the space required for the disconnecting device 1301. The housing 1311 of the actuator 1310 using a bearing, for example a rolling bearing 1309 is rotatably located on the inner perimeter of the clutch cover 1392 and secured in the axial direction with safety ring 1309a. The housing 1311 is supported axially by an axial stop 1311c on a rolling bearing 1309. Both halves 1311a, 1311b of the housing are connected radially externally by means of fixing means 1311d. The coil spring 1315, wound spirally in contact with the coils, is connected at its ends to the corresponding housing part 1311a, 1311b, and several, for example, three, distributed along the perimeter, radially directed engaging means, for example, pins 1332, which are rotatably mounted, for example, are placed using bearings 1327a, 1327b on beam 1327. Bearings 1327a, 1327b may be sliding or rolling bearings. The beam 1327 is located on the sleeve 1328, which carries the flange portion 1329, on which the pressure ring 1376 is placed. In the shown embodiment, the parts 1327, 1329, 1376 are fixedly connected to each other, for example, welded, riveted, coupled or the like. It is clear that these parts 1327, 1329, 1376 can also be made in the form of two or one part. Parts 1327, 1329, 1376 are centered relative to the clutch cover 1392 or relative to the housing 1311, for example, as shown, using centering cams distributed around the perimeter or shoulder 1311e.

The rotary actuator 1320 is connected to the gearbox housing 1303a only partially shown with axial displacement and without the possibility of relative rotation, for example, using an axially acting energy accumulator, for example a coil spring 1335, which springs the axial rotary actuator housing 1321 relative to the housing 1303a gearboxes, moreover, in parts of the housings 1303a, 1321, in which the coil spring 1335 is placed, a receiving device (not shown) is provided which prevents turning it, for example recesses into which engages a coil spring 1335. Another possibility for fixing axially movable and centering both housings 1303a, 1321 with respect to each other may consist in the use of flat springs.

In the inner space of the housing 1321 of the rotary drive 1320, which in this case is made in the form of an electric motor and can also be a hydraulic or pneumatic turbine or the like, the stator 1336 is fixedly connected to the housing 1321. A rotor bearing 1338 is installed radially inside the stator 1336 using a rolling bearing 1337, which on the side of the end is in contact with the pins 1332.

The principle of operation is as follows: in the inactive state of the rotary drive 1320, the rotor 1337 in contact with the pins 1332 and the flange portion 1329 rotate with the speed of rotation of the clutch unit 1370. Due to the self-braking actuator 1310, the axial position of the lever 1376 is maintained until the actuator 1310 is activated by the rotary actuator 1320. When the rotary actuator 1320 is activated, the rotor 1337, which accelerates or decelerates to a higher or lower rotation speed than the speed of rotation of the clutch cover 1392, leads the pins 1332 are moved, the force of pressing the pins 1332 against the spring band 1315 is controlled by the spring 1335. To optimize the frictional contact between the pins 1332 and the rotor 1337, the contact surfaces between them can can be provided with a friction coating, for example the pins can be coated with a high friction plastic coating. In addition, a friction ring made of rubber or plastic can be arranged around the pins, and the surface of the pins can be made rough, for example, corrugated, knurled or the like, to increase the adhesion to the friction ring. 3a, by driving the pins 1332, the spring 1315 is shifted relative to the pins 1332, the ratio of the radius r _{1 of the} pins on the contact surfaces with the rotor 1337 to the radius r ₂ on the contact surface with the spring 1315 determines the first gear ratio. By shifting the spring 1315, which in the axial direction rests on the pins 1332, the lever 1376 moves in the axial direction, and the clutch against the action of the force of the Belleville spring 1357 is turned on from the off state shown in Fig. 21. When reversing the direction of rotation of the rotary actuator 1320, the spring 1315 is shifted in the opposite direction, while it rests on another set (not shown) of the pins, which are located with axial displacement relative to the pins 1332, which need not be driven, since the receiving part 1327 is already driven into motion by means of pins 1332, and the clutch disengages with the support of a poppet spring 1357.

On Fig shows an example implementation of the unit 1470 clutch, which, with the exception of the rotary actuator 1420 switchgear is identical to the unit 1370 clutch, according to Fig.21. In the shown embodiment, the rotary drive 1420 is coupled to another drive 1450, so that the electric motor 1420a with the rotor 1437 and the stator 1436 can be made with less power. Part 1421 of the housing of the rotary actuator 1420 is centered on part 1403a of the gearbox housing, and is also fixed without the possibility of relative rotation and axial movement. Radially inside the housing part 1421, it is located centrally without relative rotation and axial displacement of the spring housing 1452, in which the spring 1456 of the axial actuator 1450 is fixed at both ends. The spring housing 1452 is connected to a disconnecting ring 1433, which axially covers on both sides the pins 1432, through a detachable, excluding the possibility of relative rotation of the snap connection 1453, which in this case is formed from a radial, forming the rear pin of the protrusion 1453a, to which snaps into ring 1453b. Due to this, during installation, it is possible to separate the rotary drive 1420 from the clutch unit 1470. The disconnecting ring 1433, depending on the direction of rotation of the rotary actuator 1420, can be pulled or pushed, so that the connection or disconnection process can be actively performed and there is no need for additional spring elements. In this case, the pressing force of the pressure disk 1454 is determined by the pressing force of the rotary drive 1420, taking into account the gains of the axial drives 1410, 1420, and the self-braking of the axial drive 1420 helps to essentially maintain the pressing force after shifting the clutch to another state.

The principle of operation compared with the unit 1470, according to Fig.21, due to the introduction of a pre-amplifying drive 1450 is changed as follows: in the position shown in Fig.21, the clutch is turned off. By activating the electric motor 1420a, the rotor 1437 rotates relative to the stator 1436 and drives the pins 1455 in the peripheral direction, due to which the spring 1456 is shifted and due to this, the spring case 1452 with the separation ring 1433 is axially shifted to the pressure plate 1454. Due to this the pins 1432 are braked with an axially directed contact surface to the rotary actuator 1420 and thereby drive the actuator 1410 in a known manner. The latter engages the clutch by о he moves the axial disk 1454 in the axial direction. When the direction of rotation of the rotary actuator 1450 is reversed, the spring 1456 is shifted and due to its support on the pins 1455, the pins 1432 come into frictional contact with the contact surfaces 1433b facing the pressure disk 1454 and are braked, due to which the drive 1410 moves backward in the direction of the rotary actuator 1420. This movement can be supported by the action of the lever 1457 if it is designed as an axially acting energy accumulator. In the neutral position, i.e. when the clutch is not to be actuated, the rotary actuator 1450 moves the isolation ring to a position in which there is no frictional contact with the pins 1432. The energy for shifting the clutch comes essentially from the rotational energy of the internal combustion engine. By means of a disconnecting ring 1433, the permutation is only controlled, due to which the electric motor 1420a can have correspondingly lower power. It is understood that axial drives 1310, 1410, in conjunction with rotary drives, are exemplary embodiments that can be used in conjunction with other types of clutches, for example extendable, compressible, compressible and contractible by means of axial displacement of the clutches.

On Fig shows an example implementation of the permutation device 1480 in the idle state of the clutch unit 1470. With the clutch unit 1470 at rest, there is no relative movement between the release ring 1433 and the pins 1432, so that the axial drive cannot disconnect the clutch. To create such a relative movement, it is possible, for example, to detachably connect the housing part 1411, in which the spring 1415 of the axial drive 1410 is placed, to the rotor 1437 of the rotary drive 1420. For this, appropriate means can be provided, for example, an electromagnet 1481, which is fixedly connected to a part of the housing, for example, with the gearbox housing part 1403a, and when operating with the locking element 1482, connects the spring housing 1411 to the rotor 1437 without the possibility of relative rotation when the clutch is in the oops. The locking element 1482 may preferably be configured as a gear located on an electromagnet 1481 axially displaceable and rotatable, which is meshed with an external gear ring 1483 around the rotor 1437, and engages with the external gear ring 1484 when resting in gear at rest. the formation of the permutation device 1480 at rest. In addition, the means for fixing without the possibility of relative rotation of the rotor 1437 and the housing 1411 can be located directly on the rotor 1437 or on the housing 1411, so that there is no need to perform with the possibility of rotation of the locking means 1482. It may also be preferable to perform the permutation device 1480 at rest depending on the centrifugal force so that in the idle state of the clutch, both parts 1437, 1411 are connected to each other and separated from each other at the still existing speed of rotation of the clutch.

The permutation at rest is carried out in such a way that when the rotor 1437 is connected to the housing 1411, the rotary drive 1420 is activated, while the rotor 1437 moves the spring 1456 and drives the housing 1411, due to which the spring 1415 of the drive 1410 is also shifted in the same axial direction . In this case, the pins 1432 move without a functional load, i.e. they are not in frictional contact with the separation ring 1433. Due to this, the axial movement of the actuator 1410 and the clutch are released. The connection is carried out by reversing the direction of rotation of the rotary drive 1420. A prerequisite for the correct operation of the permutation at rest is approximately the same gear ratio of the drives 1410, 1450. Compensation of gear ratios that are different under certain circumstances is achieved, for example, by matching the ratio of the radii r ₁ , r _{2 of the} pins 1432. The power of the electric motor 1420a for rearrangement at rest can be chosen so that it temporarily works in excess of the nominal Flax power. The duration of the rest permutation process can be increased in comparison with the clutch permutation time in normal mode to less than 0.3 seconds, preferably less than 0.1 seconds.

On Fig shows a partial section of another preferred example of the use of the drive 1520 for the coupling coupling 1570 for connecting two located around the shaft 1550 with the rotary axis 1550a of the idle wheels 1551, 1552, for example, in a gearbox. The idle wheels 1551, 1552 are made as mounted on the shaft 1550 using bearings 1551b, 1552b, for example rolling bearings, gears that can rotate on their end surfaces facing each other and have a corresponding synchronizing ring 1551a, 1552a of the synchronizer and gear linkage 1554 , 1555. The fixed wheel 1556 is located on the shaft 1550 without the possibility of rotation relative to it, for example, using an unshaped key connection, and is made of parts 1556a, 1556b, and in the axial direction between they are provided mounted on the shaft 1550 with bearings 1557a, 1557b, for example rolling bearings, rotatably around its pivot axis and without being able to rotate in the direction of the axis of rotation 1550a, for example, three pivots 1532 distributed around the perimeter. Parts of the fixed wheel 1556 1556a, 1556b fixed in the axial direction with the help of a safety ring 1556c. On the external gearing 1559 of the fixed wheel 1556, there is an internal gear coupling 1560, which is axially movable and axially movable, and which has a free cutout 1561 in the axial direction of travel thereof. The movable coupling 1560 forms respectively two fixedly spaced apart from each other in the axial direction, the annular flange parts 1562, 1563, which, using bearings, for example, rolling bearings 1564, 1565, are mounted on a sliding sleeve 1560 and with by means of not depicted recesses, the spring 1515 is gripped with a geometric closure and without the possibility of relative rotation. The pins 1532 radially enter the spring 1515, the contact surfaces 1532a of the pins 1532 being installed with a voltage relative to the spring 1515 and only one side of the pins 1532 is in contact with the spring 1515. there are others, similarly mounted on the shaft 1550 and distributed around the perimeter of the pins (not shown), the radial size of which slightly extends beyond the spring 1515. Radially outside the pins 1532 are located with a gap in the hollow groove 1567 of the ring 1568, which is stationary relative to the housing, for example, using the shaft bearing bracket 1550, or on a part of the gearbox housing, and with the possibility of axial movement along the axis of rotation 1550. The axial movement is controlled by two coaxial axes of rotation 1550 of the electromagnets 1570, 1571, and when activated, one side of the pins 1532, which is in the adjacent contact, respectively the friction contact, with the friction ring 1572, which brakes the pins on the corresponding side, is braked.

In the main position shown in Fig. 23, none of the idle wheels 1551, 1552 are connected to the fixed wheel 1556, the movable sleeve 1560 is in the neutral position, no current flows in any of the electromagnets 1570, 1571. With a rotating shaft 1550, all parts rotate without relative rotation with the same rotation speed due to the self-braking of the drive 1520. If it is necessary to connect one of the idle wheels 1551, 1552 with a fixed wheel 1556 with power meshing, then the current is supplied to the corresponding electromagnet 1570, 1571 and thereby move the annular flange 1568 in the axial direction and bring the pins 1532 on one side into contact with the friction ring 1572. Due to this, the pins 1532 are braked by performing rotation around its axis 1558. This rotation leads to the fact that the pins drive the spring band 1515, due to which the movable sleeve 1560 is displaced in the axial direction and after synchronization due to the corresponding locking ring 1551a, 1552a synchronization occurs geometric closure between the movable sleeve 1560 and the corresponding gear gear 1554, 1555 The disconnection of the geometric circuit is achieved by disabling the activated and supplying current to the corresponding other electromagnet 1570, 1571.

On Fig shows an example of a radial drive in the form of a belt pulley 1601 for adjusting the variable diameter of the pulley with the removed part 1613 of the pulley (see Fig.25). On Fig shows a section along the line aa in Fig.24. The belt pulley 1601 is formed from a rotatably mounted shaft 1602, to which two flange parts 1603, 1604, axially spaced apart from each other, are fixedly connected, respectively welded, pressed or coupled. On the outside of the flange parts 1603, 1604, a corresponding disk part 1613, 1614 is rotatably mounted on the shaft 1602. To provide support, which can be carried out through a rolling bearing, a sliding bearing, or the like. the disk parts 1613, 1614 on their inner perimeter are provided with a protrusion 1615, which adjoins in the axial direction to the corresponding flange part 1603, respectively, 1604, and between them can be provided a means to reduce friction, and on the opposite side is fixed in the axial direction by a locking ring 1616 .

The corresponding coil springs 1617, 1618 are located in the disk parts 1613, 1614, in this case in the radially outer zone of the disk parts 1613, 1614 radially between the two axial protrusions 1619, 1620, the springs 1617, 1618 at least at one end fixedly connected to one of axial protrusions 1619, 1620, for example, are welded, riveted, clamped or coupled, and thereby rotate the disk parts 1613, 1614 when they rotate relative to the shaft 1602 and flange parts 1603, 1604. Both disk parts 1613, 1614 relative to the shaft 1602 are driven using op irradiating to a fixed part of the housing of the drive unit (not shown), which can rotate the disk parts relative to the shaft 1602 using located on the outer perimeter of the disk parts 1613, 1614 gearing 1621, schematically shown in Fig.24. The coil springs 1617, 1618 include a corresponding set of perimeter pins 1622, 1623 distributed as permeation means, which are fixed in the peripheral direction and mounted with the possibility of radial movement in the corresponding guide grooves 1624, 1625, and to reduce the friction of the pins 1623, 1624 in places bearings 1626 can be provided with contacts with spring turns 1617, 1618 and / or in places of contact with grooves 1624, 1625. On the first set of pins 1622, the springs 1617, 1618 are supported radially from the inside, and on the second set pins 1623 - radially outside, wherein sets of pins 1622, 1623 mounted at a distance from each other in the radial direction. In the transition zone 1627, the spring tapes 1617a, 1618a are transferred in the perimeter segment between the two pins 1622a, 1623a from the set of pins 1622 to the set of pins 1623, so that with such a relative rotation of the disk parts 1613, 1614 relative to the flange parts 1603, 1604 by rewinding the spring tapes 1617a, 1618a, depending on the direction of relative rotation, the sets of pins 1622, 1623 are radially moved. Both sets of pins 1622, 1623 are connected to each other at a distance by a spring ring 1628, so that the pins 1622, 1623 of the sets are radially they are pivoted in both directions on one side - on a spring band 1617, 1618, and on the other hand on a spring ring 1628.

A belt (not shown), worn on a belt pulley 1601 and transmitting torque to at least one other belt pulley, is connected to a power circuit with at least a set of pins 1623. Additionally, a part of the torque can be transmitted to the belt by a spring ring 1628. In this case, the contact points between the belt and the set of pins 1623, respectively, with the spring ring 1626 can be carried out by means of frictional closure, fine gearing, fine splined connection, or the like.

FIG. 26 shows a section through another exemplary embodiment of the belt pulley 1701, which, in contrast to the belt pulley shown in FIGS. 24 and 25, is not actively rearranged by a rotary drive, but uses the rotation energy of the belt pulley 1701 to rearrange the diameter of the belt pulley. the disk parts 1713, 1714 of the belt pulley 1701 can be brought into frictional contact with the friction surfaces 1732, 1733 of two electromagnets 1730, 1731, which are supported motionlessly on the housing, and only one disk is braked with a rotating shaft 1702 hand side of 1713, 1714 via respective electromagnet 1730, 1731, and executed for that appropriately sets of pins 1722, 1723 transmit the resulting slowdown in the unbraked disk portion. Each of the disk parts 1713, 1714 through a gearing 1734, 1735 is geometrically connected to one of the wheels 1736, 1737, which is rotatably mounted on the flange part 1703, 1704. In this case, the gearing 1734 is located radially inside relative to the shaft 1739, on which has gear 1737 and gear 1737 radially outwardly relative to shaft 1739, on which gear 1737 is located. This results in a rotational movement of the shaft 1702 of the disc part 1713 during braking with the electromagnet 17 30 depending on the direction of rotation of the shaft 1702 is ahead or behind it and due to the resulting relative rotation between the disk part 1713 and the driven sets of pins 1722, 1723 disk part 1714, on the one hand, and flange parts, on the other hand, there is a permutation in the radial direction of the pin sets 1722, 1723. When braking the disk part 1714 using an electromagnet 1731 due to the complementary arrangement of the gearing 1735 relative to the shaft 1739 with the same direction of rotation of the shaft 1702 occurs The radial direction of the belt pulley 1701 is opposite in comparison with the braking of the disk part 1713, so that the diameter of the belt with the rotating shaft 1702 can be increased and decreased due to braking of the disk parts 1713, 1714. It is clear that the radii of the gears 1736, 1737 are so coordinated with the other and with the thickness of the spring bands 1717a, 1718a that between the disk parts 1713, 1714 and the flange parts 1703, 1704 there is no gear ratio due to the gears, i.e. with the help of gears 1736, 1737 only the direction of rotation is reversed, and the relative rotation of the disk parts 1613, 1614 is set depending on the thickness of the spring bands 1717a, 1718a.

The claims filed with the application contain proposals for the formulation without prejudice to achieve far-reaching patent protection rights. The applicant reserves the right to claim protection of combinations of features disclosed only in the description and / or drawings.

The references indicated in the dependent claims indicate the further development of the subject matter of the main claim at the expense of the features of the corresponding dependent claim; they cannot be understood as a rejection of independent, substantive protection of a combination of features of the dependent claims.

Since the subjects of the dependent claims, taking into account the state of the art, on the priority day can form their own and independent invention, the applicant reserves the right to make from them the subject of independent claims or selected applications. In addition, they may also contain independent inventions that have a different implementation from the objects of the preceding dependent claims.

Examples of implementation should not be construed as limiting the invention. Numerous changes and modifications are possible within the scope of this disclosure, in particular such variations, elements and combinations and / or materials, which, for example, by combining or modifying the individual described in the general description and in relation to the embodiments, as well as in the claims and contained in the drawings of the features, respectively, of the elements or stages of the method may be obvious to a person skilled in the art, and who, due to the combined features, lead to a new subject or to new stages method, respectively, to the sequences of stages of the method, even if they relate to methods of manufacture, verification or to methods of operation.

Claims (100)

1. A drive for providing relative movement of two rotatably disposed relative to each other in the peripheral direction, characterized in that at least one means of engagement fixed relative to the first part is included between at least two adjacent turns located on the second part without the possibility of rotation relative to it of a coil spring, such as a coil spring, and at least one part is installed with the ability to be rotated relative to other parts ali. 2. The drive according to claim 1, characterized in that the coil of the spring are essentially adjacent to each other. 3. The drive according to claim 1, characterized in that the middle axis of the spring intersects the middle axis of the second part inside the second part. 4. The drive according to claim 1, characterized in that the spring and the second part are located coaxially relative to each other. 5. A radial drive for providing relative radial movement, consisting of at least two parts rotatably mounted relative to each other in the peripheral direction, characterized in that at least one gearing means fixed relative to the first part in the axial direction is included in the axial direction between at least two adjacent turns located on the second part without the possibility of rotation relative to it of a spiral spring, and at least one part of the mouth Credited with the possibility to be rotated relative to the other parts. 6. The drive according to claim 5, characterized in that the turns of the spring are essentially adjacent to each other. 7. The drive according to any one of claims 1 to 6, characterized in that the drive is provided for traction and / or pushing direction. 8. The drive according to claim 7, characterized in that both parts are located coaxially relative to each other. 9. The drive of claim 8, characterized in that the spring having two ends is fixed by at least one end on the second part without the possibility of rotation relative to it. 10. The drive according to claim 9, characterized in that at least one end of the spring is axially supported on the second part. 11. The drive of claim 10, characterized in that at least one end of the spring is radially supported on the second part. 12. The drive according to claim 11, characterized in that at least one means of engagement is based in the axial direction, respectively, in the radial direction, at least one turn. 13. The actuator according to claim 12, characterized in that the spring is divided by at least one engagement means into at least two sections (12a, 12b) of the coil spring. 14. The drive according to item 13, wherein the spring coils in the integrated position are divided by means of engagement into two sections in which the coils are adjacent to each other. 15. The drive according to 14, characterized in that the coil spring forming a twisted spring is a spring band. 16. The drive of claim 15, wherein the spring band is approximately rectangular in cross section. 17. The drive according to clause 16, wherein the ratio of the radial width to the thickness of the tape is more than 1: 1, preferably from 3: 1 to 60: 1. 18. The drive according to 17, characterized in that the thickness of the tape is less than 5 mm, preferably less than 2 mm 19. The drive according to p. 18, characterized in that the ratio of the outer diameter of the coil spring to the radial width of the spring band is from 100: 1 to 1: 1, preferably from 30: 1 to 5: 1. 20. The drive according to claim 19, characterized in that the ratio of the diameter of the coil spring to the thickness of the tape of the spring tape is from 700: 1 to 25: 1, preferably from 200: 1 to 40: 1. 21. The drive according to claim 20, characterized in that the spring band or spring wire is made of an elastic material, in particular spring steel or plastic. 22. The drive according to item 21, wherein the coil spring has from 3 to 300, preferably from 5 to 50 turns. 23. The drive according to claim 22, characterized in that both parts are axially spaced from each other depending on their relative rotation. 24. The drive according to item 23, wherein the first part on the second part is supported by at least one means of engagement on a section of a coil spring, which varies in axial size depending on the relative rotation of both parts relative to each other. 25. The drive according to paragraph 24, characterized in that for the traction and pushing directions there are various means of engagement. 26. The drive according A.25, characterized in that the spring band of the twisted spring passes in the axial direction between the two means of engagement. 27. The drive according to p. 26, characterized in that the means of engagement are located at different heights in the axial direction. 28. The drive according to claim 27, characterized in that at least the engagement means between which the spring band extends in the axial direction are offset relative to each other in the axial direction. 29. The drive according to p. 28, characterized in that the means of engagement, between which passes in the axial direction of the spring band, are displaced relative to each other in the axial direction by the thickness of the spring band. 30. The drive according to clause 29, wherein the two gear means, between which the spring band passes, are displaced relative to each other in the axial direction, and the gear means, surrounded by a passing spring band and a decreasing portion of the coil spring, are axially displaced to the side a decreasing portion of the coil spring by the thickness of the spring band. 31. The drive according to claim 30, characterized in that for each direction of the drive action a set of gearing means is used with gearing means displaced axially by the thickness of the spring band. 32. The drive according to p. 31, characterized in that at least one means of engagement consists of many directed radially in the direction of the coil spring, respectively, in the axial direction towards the coil spring, distributed around the perimeter connected to the first part of the pins. 33. The drive according to p, characterized in that the set is between 3 and 12. 34. The drive according to p. 33, characterized in that the pins enter the coil spring about the entire width of the spring band. 35. The drive according to claim 34, characterized in that a bearing is located on the pins, such as, for example, a rolling bearing (31) or a sliding bearing. 36. The drive according to p. 35, characterized in that the pins are connected to the first part with the possibility of rotation around its longitudinal axis. 37. The drive according to clause 36, wherein the pins are mounted on the first part using a bearing, preferably a rolling bearing or a sliding bearing. 38. The drive according to clause 37, wherein both parts are inserted into each other. 39. The drive according to § 38, characterized in that the second part is located radially inside the first part. 40. The drive according to § 39, wherein the coil spring is located radially between the first part and the second part. 41. The drive according to p, characterized in that at least one means of engagement is formed by at least one inclined portion made in the first part and extending in the peripheral direction. 42. The drive according to paragraph 41, wherein the at least one inclined portion in the peripheral direction has an axial slot for the passage of the spring band. 43. The drive according to § 42, wherein the at least one inclined portion in the perimeter zone has a lift height approximately equal to the thickness of the spring band. 44. The drive according to claim 43, characterized in that at least one recess having a shape of a segment or a recess extending along the perimeter in the form of a thread is provided in the first part, in which a plurality of rolling bodies are inserted, which form at least one means of engagement, moreover, at the end point of the thread turn of the rolling body are transferred to the starting point of the thread thread. 45. The drive according to item 44, wherein the rolling elements in the transition zone from the end point to the starting point pass along an extended radially outward relative to the radius of the coil spring trajectory. 46. The drive according to item 45, wherein the trajectories of the spring wire and the recesses for the rolling elements intersect. 47. The drive according to item 46, wherein the rolling elements are barrel-shaped. 48. The drive according to item 47, wherein the rolling elements with their perimeters roll along the recess, respectively, along the spring band. 49. The drive according to p, characterized in that the first part and the second part are tensioned in the direction of action of the drive. 50. The drive according to § 49, wherein the first part and the second part are axially tensioned relative to each other. 51. The drive according to item 50, wherein the first part and the second part are tensioned against the axial, respectively radial action of the energy accumulator. 52. The drive according to paragraph 51, wherein the energy accumulator is a coil spring, respectively, a coil spring. 53. The drive according to paragraph 52, wherein the coil spring is a coil compression spring that is tensioned between the first and second parts and whose coils in the integrated state form two coil coil sections separated by the engagement means, the coils of which are pressed against each other. 54. The drive according to item 53, wherein the energy accumulator consists of at least two plane springs distributed along the perimeter, fixed at one end on the first part and the other end on the second part. 55. The drive according to item 54, wherein the energy accumulator consists of at least one coil spring, axially strained between the first part and the second part. 56. The drive according to claim 55, wherein the coil spring is self-centering relative to its longitudinal axis. 57. The drive according to item 56, wherein the spring band has an axial profile relative to its cross section. 58. The drive according to clause 57, wherein the axial profile is approximately V-shaped. 59. The drive according to § 58, characterized in that the top of the V-shaped profile is located opposite the direction of action of the coil spring. 60. The drive according to § 59, characterized in that the drive is driven using the differential angular velocity of both parts. 61. The drive of claim 60, wherein one of the two parts is rotated relative to the other part. 62. The drive according to p. 61, characterized in that one of both parts is rotated relative to the other, stationary relative to the housing of the part. 63. The drive according to item 62, wherein one part is driven from a rotary drive. 64. The drive according to item 63, wherein the rotary drive is an electric motor. 65. The drive according to item 64, wherein the rotary drive is a turbine, such as, for example, a pneumatic turbine or the like. 66. The drive according to item 65, wherein the rotary drive has the maximum radial size of the part to be driven. 67. The drive according to p, characterized in that the rotary drive is located radially inside the radially outer part. 68. The drive according to item 67, wherein the rotary drive radially located inside the radially outer part actuates the radially outer or radially inner part. 69. The drive of claim 68, wherein at least one stop is provided in the direction of rotation until at least one end of the spring is reached. 70. The drive according to p, characterized in that the emphasis is made with the ability to act in a damping manner on the pivoting movement in the peripheral direction and / or in the axial direction. 71. The drive according to item 70, characterized in that in the rotary drive, at least in one axial direction, a limitation of the path of movement is provided. 72. The drive according to claim 71, characterized in that with the electric rotary drive (20), the limitation is carried out electrically. 73. The drive of claim 72, wherein the rotary drive has a path sensor for determining axial displacement. 74. The drive according to p, characterized in that the path sensor is a path increment sensor. 75. The drive according to item 74, wherein the path sensor is configured to control the maximum working path of the drive in the axial direction. 76. The drive according to item 75, wherein the radially inner part has a Central hole. 77. The drive according to p, characterized in that the rotary drive is located around the shaft passing through the hole, without the possibility of rotation relative to the shaft or with the possibility of rotation. 78. The drive according to p, characterized in that the drive is mounted on a rotating shaft without the possibility of rotation relative to it, and to bring it into action the first part is braked relative to the stationary housing. 79. The drive according to p, characterized in that at least one first part is installed with the possibility of connection with a power circuit with a rotating element, and at least one second part with a fixed body. 80. The drive according to p, characterized in that the shaft rotates in only one direction. 81. The drive as an axial drive according to claim 80, characterized in that for driving the drive in one axial direction, the first part is connected to the shaft without the possibility of rotation relative to it, and the second part is braked relative to the housing, and for actuating the drive the second axial direction, the second part is connected to the shaft without the possibility of rotation relative to it, and the first part is braked relative to the housing. 82. The drive according to p, characterized in that the connection to the shaft without the possibility of rotation relative to it and / or braking relative to the housing is carried out using at least one electromagnet and / or using a hydraulic or pneumatic gripping cylinder supplied from the source pressure. 83. The drive of claim 82, wherein the rotary drive has a central hole through which the shaft passes. 84. The drive according to p, characterized in that one of both parts is integrated into the rotating part of the rotary drive. 85. The drive of claim 84, wherein the other part is integrated into the rotary drive housing. 86. The drive of claim 85, wherein the rotary drive is mounted on the shaft with the possibility of rotation or without the possibility of rotation relative to it. 87. The drive of claim 86, wherein one part acts on an element to be axially moved with an angular velocity different with respect to it, and a rolling bearing is provided between the part and the element. 88. The drive p, characterized in that the rolling bearing is located on the part. 89. The drive according to p, characterized in that its rotary drive is controlled by a control device. 90. The drive according to p, characterized in that the movement of the drive is carried out using a control device with the assessment of at least one sensor signal. 91. The drive of claim 90, wherein the at least one sensor signal corresponds to a rotation speed of the rotary drive, a movement signal of the rotary drive, acceleration of the rotary drive, a force signal or other derivative thereof, a combined and / or calculated value. 92. The drive according to claim 91, characterized in that it is provided for in an automated vehicle clutch in combination with a control device, at least according to claims 89-91, and for its operation, signals of the following sensors are evaluated and / or used: rotation speeds at least drive wheels and / or non-drive wheels, throttle position, vehicle speed, gearbox rotation speed, drive unit rotation speed, vehicle acceleration, lateral acceleration, wheel lock signal, gear engaged, before Vai clutch torque, the clutch temperature, the oil temperature in the gearbox oil temperature of the drive unit, the rotation angle. 93. A machine element for continuously changing the distance between two machine parts, of which one part with the help of the drive, at least one of the preceding paragraphs is mixed relative to the other part in the radial direction. 94. Machine element with a collet for radially clamping parts using a drive according to any one of claims 1-92. 95. Belt drive with a variable gear ratio, containing two belt pulleys located on the corresponding shaft without the possibility of rotation relative to it, and at least one belt pulley has a drive according to any one of claims 1-92 for setting a variable diameter of the working surface of the belt and, if necessary, means are provided to compensate for the length of the belt. 96. Disconnecting device for friction clutch containing clamped with the help of an axially acting battery energy between at least two pressure plates mounted on the first shaft without the possibility of rotation relative to it, the clutch disk mounted on the second shaft without the possibility of rotation relative to it characterized in that the drive mounted on one of both shafts according to any one of claims 1-92 acts directly or indirectly on the axially acting battery e ergii. 97. Friction clutch for a car with a drive unit, for example, an internal combustion engine with a drive shaft and an output part, for example, a gearbox with an input shaft of a gearbox, and in the power flow between the drive shaft and the input shaft of the gearbox there is a friction clutch according to 96, equipped with a disconnecting system, driven by a drive according to any one of claims 1 to 92, provided as an axial drive. 98. Friction clutch according to p. 97, characterized in that the drive is located on the input shaft of the gearbox. 99. A divided flywheel with at least one primary one located on the drive shaft without the possibility of turning the flywheel therefrom relative to it and mounted with the possibility of rotation relative to the primary mass against the secondary mass acting in the peripheral direction of the battery, containing friction clutch according to claims 97 and / or 98. 100. Machine part containing features according to any one of the preceding paragraphs.

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