DE102017118787B4 - Transmission arrangement for an actuator device for adjusting the height of a vehicle body - Google Patents

Abstract

Transmission arrangement (21) for an actuator device (20) for adjusting the height of a vehicle body, comprising a drive wheel (1) and a driven wheel (2), which are rotatably connected to one another via a respective toothing (3, 4) formed thereon, wherein on the driven wheel ( 2) a blocking element (5) is arranged to block a rotary movement, characterized in that the blocking element (5) has at least one guide track (6) with at least one blocking stop (7) integrated therein, the at least one guide track (6) having a is connected to a limited movable pin section (9), which is intended to be guided along the at least one guide track (6) when the driven wheel (2) rotates and to cause a rotary movement of the driven wheel ( 2) to lock, wherein the at least one guide track (6) has a first and second guide element (25a, 25b) with a respective guide surface (26a, 26b) to the foot guide of the pin section (9), the at least one locking stop (7) being arranged on a locking section (10) between the two guide elements (25a, 25b), the pin section (9) turning into a first direction of rotation (U1) can be guided along the first or second guide surface (26a, 26b), the pin section (9) during the rotary movement of the driven wheel (2) in a second direction of rotation (U2) via the first guide element (25a) in the blocking section (10) can be guided and can then be guided via the second guide element (25b) into a first guide track section (6a), and wherein a reversal of the direction of rotation of the driven wheel (2) in the blocking section (10) from the second direction of rotation (U2) to the first direction of rotation ( U1) can be carried out in order to guide the pin section (9) into the blocking stop (7) along the first guide surface (26a) in order to block the rotational movement of the driven wheel (2).

Description

The invention relates to a gear arrangement for an actuator device for adjusting the height of a vehicle body. The height adjustment of vehicle bodies serves to increase the ground clearance of motor vehicles and to lower them on level roads. For this purpose, for example, a device for adjusting the height of the vehicle body is provided in the spring struts of motor vehicles, which device comprises an actuator device, the device for adjusting the height of the vehicle body being driven by means of the actuator device.

For example, from the DE 10 2014 209 939 A1 an embodiment for a transmission arrangement or an actuator device with a blocking function. The transmission arrangement has a drive wheel which is arranged such that it can rotate about a drive axis and which has a drive toothed section in the direction of rotation. Furthermore, the gear arrangement has an output wheel, which is arranged rotatably about an output axis and which has an output toothing section in the direction of rotation, wherein the drive toothing section and the output toothing section can be brought into mesh with one another by rotating the drive wheel, so that the gear arrangement is in a driving state. The drive wheel has a drive blocking section and the driven wheel has a driven blocking section. The drive lock portion and the driven lock portion are engageable with each other by further rotation of the drive wheel from the drive state so that the gear assembly is in a locked state.

the DE 10 2017 109 145 B3 shows a gear arrangement for an actuator device for adjusting the height of a vehicle body, comprising a drive wheel and a driven wheel, which are rotatably connected to one another via a respective toothing formed thereon, a locking element for locking a rotary movement being arranged on the driven wheel, the locking element having at least one guide track has at least one locking stop integrated therein and at least one deflection position, wherein the at least one guideway is connected to a pin section that can move to a limited extent, which is intended to be guided along the at least one guideway when the driven wheel rotates and when the at least one guideway penetrates Blocking stop to block a rotational movement of the driven wheel, and by means of the at least one deflection position, the rotational position of the locking element during the guidance of the pin section through the at least one deflection position detektierb are.

the DE 10 2016 216 056 A1 shows an actuator device for adjusting the height of a vehicle body, comprising a rotatable drive pinion, which is at least indirectly connected to a rotatable output gear, the output gear being non-rotatably connected to a sun gear, and the drive pinion being at least indirectly connected to a locking unit, the locking unit having a rotatable Has locking arm which is intended to engage the sun gear to lock the output gear against rotation.

the DE 10 2014 206 142 A1 shows a device for adjusting the height of a vehicle body, containing a movement thread arranged between the vehicle body and a wheel carrier, which moves two components that can be displaced relative to one another between an upper and a lower adjustment position, the movement thread operatively engaging with two components that can be rotated relative to one another and are formed from a spindle and a spindle nut mutually standing threaded parts is provided, one threaded part being axially fixed and rotationally driven by a rotary drive on one component and the other transmission part being received on the other component in a rotationally fixed and axially displaceable manner.

the EP 1 333 201 A2 shows a shifting device of a transmission with a cam drive, which has a shifting element rotatably guided on an axis and provided with at least one grooved path, with at least one shifting means engaging in the grooved path, which can be moved axially when the shifting element is rotated due to the shape of the grooved path, and wherein the grooved path has an upshift path designed as an upshift groove for an upshift and a downshift path for a downshift, the downshift path being designed as a downshift groove which guides the shifting means during a downshift or a multiple downshift in an axial shift position equivalent to a neutral position (N).

the DE 10 2015 224 862 A1 shows a linear actuator, with a lifting device, the first lifting part and the second lifting part of which are arranged to be displaceable relative to one another along a lifting axis, and with a locking device which positively bridges the lifting device at several axial positions, the locking element of which has a link track and locking stops arranged in the axial positions, and with a stop element which is pivotable about the lifting axis and has at least one has cams that can be moved along the slideway for interacting with the locking stops, with an endless slideway and the locking stops being provided in these axial positions for each of these cams.

The object of the present invention is to further develop a gear arrangement for an actuator device for adjusting the height of a vehicle body, the gear arrangement being intended to have a constant transmission ratio and a mechanical locking function, in contrast to the prior art mentioned above.

According to the invention, this object is achieved by the features of independent patent claim 1 . Advantageous configurations result from the respective dependent claims, the description and the drawings.

According to the invention, a gear arrangement for an actuator device for adjusting the height of a vehicle body comprises a drive wheel and a driven wheel, which are rotatably connected to one another via a respective toothing formed thereon, with a blocking element for blocking a rotary movement being arranged on the driven wheel, the blocking element having at least one guide track with at least has a locking stop integrated therein, wherein the at least one guide track is connected to a pin section that can move to a limited extent, which is intended to be guided along the at least one guide track when the driven wheel rotates and, when the at least one locking stop is penetrated, to cause a rotary movement of the driven wheel to lock, wherein the at least one guide track has a first and second guide element with a respective guide surface for guiding the pin portion, wherein the at least one locking stop on a locking portion is arranged between the two guide elements, wherein the pin section can be guided along the first or second guide surface during the rotary movement of the driven wheel in a first direction of rotation, wherein the pin section can be guided via the first guide element into the blocking section during the rotary movement of the driven wheel in a second direction of rotation and can then be guided into a first guideway section via the second guide element, and wherein the direction of rotation of the driven wheel can be reversed in the blocking section from the second direction of rotation to the first direction of rotation in order to guide the pin section to block the rotary movement of the driven wheel along the first guide surface into the blocking stop.

The two guide elements with the respective guide surface separate the blocking section on the at least one guide track from the adjacent guide track sections and also guide the pin section in the guide track. The guide elements are designed in such a way that the pin section can be guided unhindered in a defined second direction of rotation of the driven wheel. The first guide element is provided to guide the pin section along the first guide surface into the locking stop when the direction of rotation of the driven wheel is reversed in the first direction of rotation. In contrast, the second guide element is provided to prevent the pin section from being guided back into the blocking section when the direction of rotation of the driven wheel is reversed in the first direction of rotation. In other words, the second guide element separates the blocking section from the first guide track section in the first direction of rotation of the driven wheel.

The guide track is preferably designed in the form of a groove, with the pin section coming to rest essentially perpendicularly on the surface or normal plane of the guide track and also being guided by the groove walls delimiting the guide track. A guideway section is understood to mean a part of the guideway which is intended to guide the pin section of the lever arm along the blocking element and thereby at least partially deflect the lever arm. The at least one guideway preferably also has a second guideway section, the second guideway section comprising the blocking section and the blocking stop. The two guide sections can, for example, merge seamlessly into one another or be connected to one another by connecting sections in order to change the pin section between the two guide sections.

It is advantageous in such a configuration of the transmission arrangement that a rotational angle window of the locking element is enlarged, within which a rotational movement of the driven wheel can be stopped in order to position the pin section in the locking section in such a way that the pin section can rotate from the second direction of rotation to the first direction of rotation when the direction of rotation is reversed is in any case guided along the first guide surface of the first guide element into the locking stop.

The pin section is preferably designed to be axially displaceable on a lever arm, with the lever arm being pivotable about an axis of rotation, with the pin section engaging radially or axially in the at least one guide track and coming to rest essentially perpendicularly on the surface of the guide track by means of a spring prestressing force. In other words, the pin section comes into contact with the guide track at all times during a rotary movement of the output wheel due to the spring pretensioning force and is thus guided in the guide track. In this case, axial displacement paths of the pin section can be detected, for example, by means of a measuring device. In other words, the pin section is arranged on the lever arm via a guided sliding fit. In particular, the pin section is formed in two parts on the lever arm, the pin section being displaceable relative to the lever arm in the direction of the guide track. The lever arm can, for example, be accommodated at least indirectly on a housing. In particular, the lever arm is connected to a fastening element by fastening means. According to an alternative embodiment, it is possible to form the lever arm and the pin section in one piece and to connect the lever arm to the fastening means in parallel via a spring prestressing force. According to a further alternative embodiment, it is conceivable to form the lever arm and the pin section in one piece and to connect the lever arm to the fastening means in a tiltable manner by means of a spring prestressing force. A further alternative embodiment provides for the lever arm and the pin section to be designed in one piece and for the lever arm to be connected to the fastening means such that it can be tilted using the force of its own weight.

According to a preferred embodiment, the respective guide element is designed as a ramp. The respective guide surface is formed essentially perpendicularly to the guide track. The respective ramp has the shape of an inclined plane and rises axially from a normal plane of the guideway in the direction of the second direction of rotation. At the front edge of the ramp, the respective guide surface is formed essentially perpendicularly to the guide track. In other words, the guide surface forms the connecting section between the front edge of the ramp and the normal plane and has a height difference. Alternatively, it is conceivable to design the respective guide elements as shoulders in the at least one guide track, so that the pin section on the respective guide elements is partially lowered during the rotational movement of the driven wheel in the second direction of rotation. Consequently, when the direction of rotation is reversed to the first direction of rotation, a rotary movement of the driven wheel is blocked or a return into the blocking section is prevented. It is also conceivable to design at least one of the guide elements, preferably the first guide element, as a depression through which the pin section is guided during the rotary movement of the driven wheel.

In particular, the pin section can be guided essentially along the first guideway section in the first direction of rotation of the output wheel, wherein the pin section can be guided essentially along the second guideway section in the second direction of rotation of the output wheel. When the driven wheel rotates in the second direction of rotation, the pin section in the guide track is guided out of the second guide track section over the ramp of the first guide element and jumps back onto the surface of the locking section when transferred over the ramp edge parallel to the first guide surface of the first guide element. Consequently, a reversal of the direction of rotation of the driven wheel in the first direction of rotation, while the pin section is present in the blocking section between the guide elements, results in the rotational movement of the driven wheel being blocked. The pin section comes into contact with the guide surface of the guide element and is then guided into the blocking stop to block the rotary movement. Only a further reversal of the direction of rotation into the second direction of rotation unlocks the rotary motion of the driven wheel.

To adjust the height of the vehicle body, the pin section is guided over the second guide element in a further step and jumps back onto the surface of the first guide track section when transferred over the front edge of the ramp parallel to the second guide surface of the second guide element. The pin section cannot be returned to the blocking section by again reversing the direction of rotation, so that the pin section comes into contact with the second guide surface and is guided along the first guide track section. The transfer of the pin section over the front edge of the ramp results in a relatively large change in the axial position of the pin section with at the same time little twisting of the driven wheel, whereby the guide elements can also be used to detect the rotational position of the blocking element. With each revolution of the driven wheel in the second direction of rotation, the guide elements thus form a reference point for the rotational position of the blocking element, which can be used to calculate how far and in which direction of rotation the blocking element must be rotated to initiate the blocking position. In addition, at least one deflection position can be provided at least on the first guide track section, which is used to detect the rotational position of the blocking element with each revolution of the driven wheel in the first direction of rotation. Alternatively, the guideway can also have three or more guide elements or also deflection positions, which essentially have different characteristic shapes or courses, as a result of which the distances between the measurements of the rotational position of the blocking element can be shortened. The leadership elements or the deflection positions can be arranged at the same distance from one another on the guide track. However, the guide elements or the deflection positions can also be arranged at different distances from one another on the guide track. Alternatively, the blocking element can also be arranged on the drive wheel, a device for adjusting the level of a vehicle body or another element of the transmission arrangement.

According to an alternative exemplary embodiment, the respective guide element is designed as a one-way flap. The respective guide surface is formed essentially perpendicularly to the guide track. The two one-way flaps are arranged pivotably in the guide track of the blocking element. The blocking of the rotational movement of the driven wheel by means of the respective one-way flap takes place analogously to the previously described design of the respective guide element as a ramp. The at least one guide track can be designed to be essentially planar and the pin section can be connected in one piece to the lever arm. The two one-way flaps are designed and arranged in such a way that the rotary movement of the driven wheel in the second direction of rotation is unhindered, with a reversal of the direction of rotation in the first direction of rotation depending on the position of the pin element preventing the previously described return of the pin section to the second guide track section or to the blocking section. If the pin section is positioned in the blocking section when the direction of rotation is reversed, the pin section is guided into the blocking stop along the first guide surface during the rotary movement of the driven wheel in the first direction of rotation. If the pin section is positioned in the first guide track section when the direction of rotation is reversed, the pin section is prevented from penetrating into the blocking section during the rotary movement of the driven wheel in the first direction of rotation.

The blocking element is preferably a blocking ring, with the guide track being formed on a cylindrical outer surface of the blocking element. The pin section engages in the guideway in the radial direction and is deflected in the axial direction toward the driven wheel. Consequently, the lever arm is designed to be pivotable essentially in the axial direction relative to the driven wheel, with the pin section moving up and down along a circular path. The blocking element is ring-shaped and is arranged on the end face of the driven wheel in a rotationally fixed manner. In particular, the blocking element is a separate ring which is connected to the driven wheel in a rotationally fixed manner. Furthermore, the blocking element can also be integrated in the output gear.

If the guideway is formed on a cylindrical lateral surface of the blocking element, the first guideway section is formed axially above the blocking stop and the second guideway section is formed axially below the blocking stop. In other words, the locking stop is arranged axially between the first and second guide track sections. The pin section is guided along the second or lower guide track section, in particular when the blocking element is rotated counterclockwise. If the blocking element is twisted clockwise, the pin section is guided essentially along the first or upper guide track section. Alternatively, the blocking element with the guide track can also be reversed on a cylindrical lateral surface of the blocking element, so that the pin section is guided along the second or lower guide track section, particularly when the blocking element rotates clockwise. If the blocking element rotates counterclockwise, the pin section is guided essentially along the first or upper guide track section.

The blocking element is preferably a blocking disk, with the guideway being formed on the face side. The pin section and thus also the lever arm are deflected in the radial direction towards the driven wheel. Consequently, the lever arm is designed to be pivotable in the radial direction relative to the driven wheel, with the pin section moving along a circular path. Depending on the application, this can be advantageous with regard to the installation space of the transmission arrangement. By the pin section penetrating into the at least one locking stop of the guideway, a positive locking of the output gear in one direction of rotation is realized.

On the lever arm, for example, a twisting angle can be determined by means of a measuring device, with the measuring device determining a twisting angle for each position of the pin section in the guideway, and with the measuring device determining a defined value of the twisting angle when guiding the pin section, for example by a deflection position of the guideway and thus detects the rotational position of the blocking element or the driven wheel. Alternatively, a course of the angle of rotation can be predefined, with which the rotational position of the blocking element can be detected.

If the guideway is formed on the end face of the blocking element, the first guideway section is formed radially on the outside and the second guideway section is formed radially on the inside of the blocking disk. In other words, the locking stop is radially between the first and second th track section arranged. The pin section is guided along the first or outer guideway section, in particular when the blocking element is rotated counterclockwise. If the blocking element rotates clockwise, the pin section is guided essentially along the second or inner guide track section. Alternatively, the blocking element with the guide track on the end face can be configured in reverse, so that the pin section is guided along the first or outer guide track section, particularly when the locking element rotates clockwise. If the blocking element rotates counterclockwise, the pin section is guided essentially along the second or inner guide track section.

According to a preferred exemplary embodiment, the lever arm has a press fit in relation to a stationary fixed component, with the guide track adjusting the position of the lever arm against a frictional force of the press fit. Consequently, the lever arm is only deflected if the course of the guideway specifies this for the pin section or the lever arm.

The invention includes the technical teaching that the pin section is arranged in an axially displaceable manner on a linear guide, with the linear guide being intended to guide the pin section along a linear axis, and with the pin section engaging radially or axially in the at least one guide track and by means of a spring biasing force comes to rest essentially perpendicularly on the surface of the guideway. “Axially displaceable” is to be understood as meaning that the pin section is pressed essentially perpendicularly onto the surface of the guideway, for example by means of a spring preload force, with the pin section coming into contact with and along the surface of the at least one guideway at all times during the rotational movement of the output wheel which is guided by at least one guideway.

The at least one guideway is preferably formed on a cylindrical lateral surface of the blocking element, with the pin section being deflected in the axial direction toward the driven wheel. The locking element is thus designed as a locking ring. Thus, the pin portion is moved up and down on the linear axis of the linear guide, with the linear guide being fixed stationary.

Alternatively, the at least one guide track can also be arranged on the front side of the blocking element, so that the pin section is deflected in the radial direction toward the driven wheel. The blocking element is thus designed as a blocking disk. Consequently, the pin section can be displaced within the linear guide in the radial direction to the driven wheel, the pin section being moved back and forth on the linear axis, the linear guide being fixed in a stationary manner. Depending on the application, this can be advantageous with regard to the installation space of the transmission arrangement. The linear guide is accommodated at least indirectly on a housing.

A linear adjustment path of the pin section within the linear guide can be determined, for example, by means of a measuring device, with the measuring device determining a defined value of the linear adjustment path when guiding the pin section via the guide elements of the guideway and thus detecting the rotational position of the locking element or the driven wheel. Alternatively, an adjustment path can be predefined, with which the rotational position of the blocking element can be detected.

The transmission arrangement according to the invention can be provided, for example, in an actuator device for adjusting the height of a vehicle body. The driven wheel is preferably connected at least indirectly to a rotatable component of the actuator device for adjusting the height of a vehicle body. In particular, the transmission arrangement according to the invention is part of this actuator device, with the actuator device being arranged either between the vehicle body and a chassis spring or between the chassis spring and a wheel carrier. In the first case, the actuator device can be arranged on the upper spring plate of the chassis spring. In the second case, the actuator device can be arranged on the lower spring plate of the chassis spring. The device for adjusting the height of the vehicle body is preferably formed by a threaded drive which has a threaded spindle which is arranged along a lifting axis and forms a first lifting part, and a spindle nut which forms a second lifting part. The screw drive is formed in particular by a ball screw drive, the balls of which roll on ball grooves of the spindle nut and the threaded spindle which are wound helically around the spindle axis. Reliable adjustment movements of the actuator device can be carried out with such ball screws.

• 1 eine schematische, teilweise durchsichtige Perspektivdarstellung einer Aktuatorvorrichtung zur Höhenverstellung mit einer erfindungsgemäßen Getriebeanordnung gemäß einem ersten Ausführungsbeispiel,
• 2 eine schematische Draufsicht eines Sperrelements der erfindungsgemä-ßen Getriebeanordnung mit Hebelarm gemäß dem ersten Ausführungsbeispiel,
• 3 eine schematische Draufsicht eines Sperrelements der erfindungsgemä-ßen Getriebeanordnung mit Linearführung gemäß einem zweiten Ausführungsbeispiel,
• 4 eine schematische Perspektivdarstellung einer erfindungsgemäßen Getriebeanordnung gemäß einem dritten Ausführungsbeispiel,
• 5 eine schematische Seitenansicht eines Sperrelements der erfindungsgemäßen Getriebeanordnung mit Hebelarm gemäß dem dritten Ausführungsbeispiel,
• 6 eine schematische Seitenansicht eines Sperrelements der erfindungsgemäßen Getriebeanordnung mit Linearführung gemäß einem vierten Ausführungsbeispiel, und
• 7 eine stark vereinfachte Schnittdarstellung einer Führungsbahn des Sperrelements gemäß den 2 und 3 zur Veranschaulichung von an der Führungsbahn ausgebildeten Führungselementen.

Exemplary embodiments of the invention are explained in more detail below with reference to the drawings. Here shows

• 1 a schematic, partially transparent perspective view of an actuator device for height adjustment with a gear arrangement according to the invention according to a first embodiment,
• 2 a schematic top view of a blocking element of the inventive gear assembly with lever arm according to the first embodiment,
• 3 a schematic plan view of a blocking element of the inventive gear assembly with linear guide according to a second embodiment,
• 4 a schematic perspective view of a transmission arrangement according to the invention according to a third embodiment,
• 5 a schematic side view of a locking element of the transmission arrangement according to the invention with a lever arm according to the third embodiment,
• 6 a schematic side view of a blocking element of the transmission arrangement according to the invention with a linear guide according to a fourth exemplary embodiment, and
• 7 a greatly simplified sectional view of a guideway of the locking element according to the 2 and 3 to illustrate guide elements formed on the guide track.

According to 1 includes a transmission arrangement 21 according to the invention for an actuator device 20 for height adjustment of a - vehicle body - not shown here - a drive wheel 1 and a driven wheel 2, which are rotatably connected to each other via a respective toothing 3, 4 formed thereon. The actuator device 20 drives a gear 11 of a device 23 for adjusting the height of the vehicle body--shown here only in part--whereby a toothing 12 formed on the gearwheel 11 meshes with the toothing 4 of the driven wheel 2. The gear wheel 11 can be designed as a spindle nut in order to carry out a height adjustment of the vehicle body when rotated by means of a screw drive 24 . A blocking element 5 is also arranged on the output gear 2 , the blocking element 5 being arranged on the end face of the output wheel 2 in a rotationally fixed manner. The blocking element 5 is designed as a blocking disk and has a guide track 6 formed on the end face thereof. Alternatively, the blocking element 5 can also be integrated in the output wheel 2 on the end face or be designed in one piece.

The actuator device 20 can be driven by means of a drive motor--not shown here--which is connected to the drive wheel 1 in a rotationally fixed manner. The transmission arrangement 21 also includes a fastening element 13 on which a lever arm 8a is accommodated so that it can move horizontally to a limited extent. The fastening element 13 can be fastened to a housing 22 of the actuator device 20, for example. A pin section 9 is arranged at the distal end of the lever arm 8a and engages in the guide track 6 of the blocking element 5 axially with respect to the driven wheel 2 .

the 2 and 3 show the first and second embodiment of the blocking element 5. The driven wheel 2 is rotated during a height adjustment of a vehicle body with the blocking element 5 either in a first or second direction of rotation U1, U2 - not shown here. During the rotational movement of the driven wheel 2 in the first direction of rotation U1, the pin section 9 is guided exclusively along the first guide track section 6a. In the second direction of rotation U2, the pin section 9 is guided partly along the first guideway section 6a and partly along the second guideway section 6b. In other words, the pin section 9 is guided into the second guideway section 6b only during the rotational movement in the second direction of rotation U2. So that the pin section 9 can enter the second guideway section 6b after a reversal of the direction of rotation from the first direction of rotation U1 to the second direction of rotation U2, the guideway 6 has an alignment section 29 for aligning the direction of movement of the pin section 9 . The alignment section 29 is designed in such a way that the pin section 9 is always guided in the first guideway section 6a during the rotary movement of the locking element 5 in the first direction of rotation U1 and always from the first guideway section 6a into the second guideway section during the rotary movement of the locking element 5 in the second direction of rotation U2 6b and then back into the first guideway section 6a. The pin section is also guided into a blocking section 10 via a first guide element 25a formed in the second guide track section 6b and having a first guide surface 26a. The pin section 9 can then be guided into the first guide track section 6a via a second guide element 25b with a first guide surface 26a. In the present case, the two guide elements 25a, 25b are designed as ramps 27a, 27b. A detailed representation of the ramps 27a, 27b formed on the guide track 6 is shown in FIG 7 refer to.

In the present case, the pin section 9 can be displaced axially in the direction of the guide track 6 . Consequently, the pin section 9 comes into contact with the surface of the guide track 6 at all times during guidance along the guide track 6, the pin section 9 pressing essentially perpendicularly on the surface of the guide track 6, for example by means of a spring preload force. The pin section 9 is thus guided via the respective guide element 25a, 25b and jumps back into the normal plane of the guide track 6 at the respective guide surface 26a, 26b. In addition, the axially displaceable pin Section 9 can be used to detect the rotational position of the blocking element 5. With each revolution of the output wheel 2 in the second direction of rotation U2, the guide elements 25a, 25b form a respective reference point for the rotational position of the blocking element, which means that a measuring device - not shown here - can be used to calculate how far and in which direction of rotation U1, U2 the Locking element 5 must be rotated to initiate the locked position. Furthermore, one or more deflection positions can be provided at least on the first guide track section 6a in order to be able to detect a rotational position of the blocking element 5 during a rotational movement of the driven wheel 2 in the first direction of rotation U1. A twisting angle 14 of the lever arm 8a ( 2 ) or a linear adjustment path 15 of a linear guide 8b ( 3 ) are measured.

To initiate a blocking position, the direction of rotation of the in 1 shown output gear 2 or the blocking element 5 in the blocking section 10 instead, wherein the direction of rotation is reversed from the second direction of rotation U2 in the first direction of rotation U1. The pin section 9 comes into contact with the first guide surface 26a of the first guide element 25a and blocks the rotational movement of the driven wheel 2 , the pin section 9 being guided along the respective first guide surface 26a and coming into contact with the blocking stop 7 . Consequently, the pin section 9 penetrates into the blocking stop 7 for blocking the rotational movement of the driven wheel 2 .

In 2 according to the first exemplary embodiment, the guide track 6 of the blocking element 5 is connected to the lever arm 8a in such a way that the lever arm 8a is guided along the guide track 6 in a horizontal plane when the driven wheel 2 rotates. The lever arm 8a is thus designed to be pivotable about an axis of rotation 16 at an angle of rotation 14 . According to this embodiment, the lever arm 8a has a press fit. The position of the lever arm 8a is set by the guide track 6 of the blocking element 5. The pin section 9 engages axially in the guide track 6 and is arranged on the lever arm 8a in an axially displaceable manner. When the blocking element 5 rotates, the pin section 9 moves back and forth in the radial direction relative to the blocking element 5 along a circular path 17 , the guideway 6 on the blocking element 5 adjusting the position of the pin section 9 .

3 shows a second embodiment of the gear assembly 21, wherein the pin section 9 is arranged to be axially displaceable on a linear guide 8b, which is designed to be fixed in position. The linear guide 8b is intended to guide the pin section 9 along a radial axis 18 . The pin section 9 engages axially in the guide track 6 on the blocking element 5 . When the blocking element 5 rotates, the pin section 9 moves back and forth in the radial direction relative to the blocking element 5 along the radial axis 18 , the guideway 6 on the blocking element 5 adjusting the position of the pin section 9 .

According to the 4 the blocking element 5 is ring-shaped according to a third exemplary embodiment and is arranged on the end face of a driven wheel 2, which is not shown here, in a rotationally fixed manner. The guideway 6 is formed circumferentially on the blocking element 5 and has two guideway sections 6a, 6b on one section of the blocking element 5. A locking stop 7 is formed axially between the upper and lower guide track sections 6a, 6b. The blocking stop 7 is connected to the upper and lower guide section 6a, 6b via a blocking section 10 and can only be initiated by changing the direction of rotation of the driven wheel 2. In the guideway 6 there is an in 5 and 6 illustrated pin section 9 can be guided, the pin section 9 for example on a lever arm 8a ( 5 ) or on a linear guide 8b ( 6 ) is arranged.

after the 5 and 6 will this be in 1 driven wheel 2 shown in a height adjustment of a - twisted vehicle body with the locking element 5 either in a first or second direction of rotation U1, U2 - not shown here. The pin section 9 is guided along the first guideway section 6a during the rotational movement of the driven wheel 2 in the first direction of rotation U1. In the second direction of rotation U2, the pin section 9 is guided partly along the first guideway section 6a and partly along the second guideway section 6b, with the pin section 9 also being guided via a first guide element 25a with a first guide surface 26a into a blocking section 10. The pin section 9 can then be guided into the first guide track section 6a via a second guide element 25b with a first guide surface 26a. In the present case, the two guide elements 25a, 25b are designed as one-way flaps 28a, 28b, with the respective guide surfaces 26a, 26b being designed essentially perpendicular to the guide track 6.

In the present case, the pin section 9 can be displaced axially in the direction of the guide track 6 . Consequently, the pin section 9 always rests on the surface of the guide track 6 during guidance along the guide track 6, with the pin section 9 coming to rest essentially perpendicularly on the surface of the guide track 6, for example by means of a spring prestressing force. Thus, the pin section 9 is guided over the respective guide element 25a, 25b. The guide elements 25a, 25b are rotatably arranged on the blocking element 5 and are pressed against the blocking element 5 in the guide track 6 by means of a spring pretensioning force for blocking the rotational movement of the output wheel 2 . When the driven wheel 2 rotates in the second direction of rotation U2, the respective guide element 25a, 25b is displaced by the pin section 9. In other words, the pin section displaces the first guide element 25a and penetrates into the locking section 10 . After the pin section 9 has passed the first guide element 25a, the first guide element 25a, which is designed as a one-way flap 28a, pivots back and comes into contact with the blocking element 5 again. When the direction of rotation of the output wheel 2 is reversed while the pin section 9 is positioned in the locking section 10, the pin section 9 is guided along the first guide surface 26a into the locking stop 7. However, if the rotational movement of the output wheel is continued in the second direction of rotation U2 or if, after the output wheel 2 has been blocked, the direction of rotation changes again to the second direction of rotation U2, the pin section 9 displaces the second guide element 25b, which is designed as a one-way flap 28b, and penetrates the first guide track section 6a a. After the pin section 9 has passed the second guide element 25b, the second guide element 25b, which is designed as a one-way flap 28b, pivots back and comes into contact with the blocking element 5 again. When the direction of rotation of the driven wheel 2 is then reversed while the pin section 9 is positioned in the first guideway section 6a, the second guide surface 26b prevents the pin section 9 from penetrating back into the blocking section 10.

In addition, the pin section 9 can be used to detect the rotational position of the blocking element 5 . With each revolution of the output wheel 2 in the second direction of rotation U2, the guide elements 25a, 25b form a respective reference point for the rotational position of the blocking element, which means that a measuring device - not shown here - can be used to calculate how far and in which direction of rotation U1, U2 the Locking element 5 must be rotated to initiate the locked position. The rotation of the respective one-way flap 28a, 28b is detected with each revolution of the driven wheel 2, so that the rotational position of the blocking element 5 can be determined. Furthermore, deflection positions can be provided at least on the first guide track section 6a in order to be able to detect a rotational position of the blocking element 5 during a rotational movement of the driven wheel 2 in the first direction of rotation U1. A twisting angle 14 of the lever arm 8a ( 2 ) or a linear adjustment path 15 of a linear guide 8b ( 3 ) are measured. Furthermore, an axial displacement path of the pin section can be measured when passing through a correspondingly designed deflection position for detecting the rotational position of the blocking element 5 . In this case, the deflection position can be designed as a depression or as a bulge in the guide track 6 .

To initiate a blocking position, the direction of rotation of the in 1 shown output gear 2 or the blocking element 5 in the blocking section 10 instead, wherein the direction of rotation is reversed from the second direction of rotation U2 in the first direction of rotation U1. The pin section 9 comes into contact with the first guide surface 26a of the first guide element 25a and blocks the rotational movement of the driven wheel 2 , the pin section 9 being guided along the respective first guide surface 26a and coming into contact with the blocking stop 7 . Consequently, the pin section 9 penetrates into the blocking stop 7 for blocking the rotational movement of the driven wheel 2 .

According to 5 the pin section 9 is formed on a lever arm 8a, the lever arm 8a being pivotable about an axis of rotation 16, which leads perpendicularly into the plane of the drawing, through an angle of rotation 14, and the pin section 9 engaging radially in the guideway 6 on the blocking element 5. The guide track 6 is connected to the lever arm 8a in such a way that the lever arm 8a is guided up and down along the guide track 6 when the driven wheel 2 rotates in the vertical direction. The lever arm 8a can be fastened to a housing 22--not shown here--fastening elements 13--not shown here. When the blocking element 5 rotates, the pin section 9 moves up and down in the axial direction relative to the blocking element 5 along a circular path 17 , the guideway 6 on the blocking element 5 adjusting the position of the pin section 9 . The twisting angle 14 of the lever arm 8a can be used to detect the rotational position of the blocking element 5, the twisting angle 14 being measured, for example, with a measuring device—not shown here. When the blocking element 5 is rotated, a specific angle of rotation 14 can be determined for each position of the pin section 9 in the guide track 6 .

According to 6 a pin section 9 according to the fourth exemplary embodiment is arranged in the linear guide 8b, the linear guide 8b being designed to be fixed in position and intended to guide the pin section 9 along an axial axis 18. For example, to determine the rotational position of the blocking element 5 by means of a measuring device—not shown here—the linear displacement path 15 of the pin section 9 in the linear guide can be measured. The pin section 9 engages radially in the guide track 6 on the blocking element 5 . The guideway 6 is thus on an outside peripheral surface of the blocking element 5 is formed. When the blocking element 5 rotates, the pin section 9 moves up and down in the axial direction relative to the blocking element 5 along the axial axis 18 , the guide track 6 on the blocking element 5 adjusting the position of the pin section 9 .

According to 7 a section of the guide track 6 in the area of the blocking section 10 is shown. The guide elements 25a, 25b designed as ramps 27a, 27b rise linearly in the present case, with the respective guide surfaces 26a, 26b being designed essentially perpendicular to the guide track 6. The respective ramps 27a, 27b rise axially from a planar normal plane of the guideway 6 to a front edge of the respective ramp 27a, 27b and then fall again essentially vertically to the normal plane of the guideway 6 at the respective guide surface 26a, 26b. Alternatively, the ramps 27a, 27b can be designed to increase exponentially or in steps. It is also conceivable that the guide surfaces 26a, 26b are designed to be at least partially inclined. The configuration of the first guide surface 26a always prevents the above-mentioned pin section 9 from being able to be guided out of the blocking section 10 back into the second guideway section 6b when the direction of rotation reverses into the second direction of rotation U2. Furthermore, the configuration of the second guide surface 26b always prevents the pin section 9 from being able to be guided out of the first guideway section 6a back into the blocking section 10 when the direction of rotation is reversed into the second direction of rotation U2.

The invention is not limited to the preferred embodiments described above. Rather, modifications of this are also conceivable, which are included in the scope of protection of the following claims. It is also possible, for example, to design the blocking element 5 as a blocking disc and, contrary to the first and second embodiment described, to design the respective guide element 25a, 25b as a one-way flap 28a, 28b according to the third and fourth embodiment of the transmission arrangement according to the invention described above. In addition, it is possible, for example, to form the locking element 5 as a locking ring and, contrary to the third and fourth embodiment described, to form the respective guide element 25a, 25b as a ramp 27a, 27b according to the previously described first and second embodiment of the transmission arrangement according to the invention.

Reference List

1

drive wheel

2

output gear

3

Gearing on the drive wheel

4

Gearing on the driven wheel

5

blocking element

6

guideway

6a, 6b

track section

7

locking stop

8a

lever arm

8b

linear guide

9

pen section

10

lockdown section

11

gear

12

toothing on the gear wheel

13

fastener

14

twist angle

15

Linear adjustment range

16

axis of rotation

17

circular path

18

axis

20

actuator device

21

gear arrangement

22

Housing

23

contraption

24

screw drive

25a, 25b

guide element

26a, 26b

guide surface

27a, 27b

ramp

28a, 28b

one-way flap

29

alignment section

Claims (10)

Transmission arrangement (21) for an actuator device (20) for adjusting the height of a vehicle body, comprising a drive wheel (1) and a driven wheel (2) which are rotatably connected to one another via a respective toothing (3, 4) formed thereon, wherein on the driven wheel ( 2) a blocking element (5) is arranged for blocking a rotary movement, characterized in that the blocking element (5) has at least one guide track (6) with at least one blocking stop (7) integrated therein, the at least one guide track (6) with a limited movable pin portion (9) is connected, which is intended to be guided during rotation of the driven wheel (2) along the at least one guideway (6) and upon penetration of the at least a blocking stop (7) to block a rotational movement of the driven wheel (2), the at least one guide track (6) having a first and second guide element (25a, 25b) with a respective guide surface (26a, 26b) for guiding the pin section (9). , wherein the at least one locking stop (7) is arranged on a locking section (10) between the two guide elements (25a, 25b), the pin section (9) turning in a first direction of rotation (U1) along the first or second guide surface (26a, 26b), wherein the pin section (9) can be guided via the first guide element (25a) into the blocking section (10) during the rotary movement of the driven wheel (2) in a second direction of rotation (U2) and then can be guided via the second guide element (25b) into a first guide track section (6a), and wherein a reversal of the direction of rotation of the driven wheel (2) in the blocking section (10) from the second direction of rotation (U2) to the first direction of rotation ng (U1) can be carried out in order to guide the pin section (9) for blocking the rotational movement of the driven wheel (2) along the first guide surface (26a) into the blocking stop (7). Transmission arrangement (21) after claim 1 , characterized in that the respective guide element (25a, 25b) is designed as a ramp (27a, 27b). Transmission arrangement (21) after claim 1 , characterized in that the respective guide element (25a, 25b) is designed as a one-way flap (28a, 28b). Transmission arrangement (21) according to one of the preceding claims, characterized in that the pin section (9) is designed to be axially displaceable on a lever arm (8a), the lever arm (8a) being pivotable about an axis of rotation (16), the pin section (9 ) engages radially or axially in the at least one guide track (6) and comes to rest essentially perpendicularly on the surface of the guide track (6) by means of a spring prestressing force. Transmission arrangement (21) after claim 4 , characterized in that the lever arm (8a) has a press fit relative to a stationary fixed component, wherein the guideway (6) adjusts the position of the lever arm (8a) against a frictional force of the press fit. Transmission arrangement (21) according to one of Claims 1 until 3 , characterized in that the pin section (9) is arranged in an axially displaceable manner on a linear guide (8b), the linear guide (8b) being provided for guiding the pin section (9) along a linear axis (18), and the pin section (9) engages radially or axially in the at least one guide track (6) and comes to rest essentially perpendicularly on the surface of the guide track (6) by means of a spring prestressing force. Transmission arrangement (21) according to one of the preceding claims, characterized in that the at least one guideway (6) also has a second guideway section (6b), the second guideway section (6b) comprising the locking section (10) and the locking stop (7). Transmission arrangement (21) according to one of the preceding claims, characterized in that the pin section (9) can be guided essentially along the first guide track section (6a) in the first direction of rotation (U1) of the output wheel (2), the pin section (9) being the second direction of rotation (U2) of the driven wheel (2) can be guided essentially along the second guideway section (6b). Transmission arrangement (21) according to one of the preceding claims, characterized in that the blocking element (5) is a blocking disk, the guide track (6) being formed on the front side. Transmission arrangement (21) according to one of Claims 1 until 8th , characterized in that the locking element (5) is a locking ring, wherein the guideway (6) is formed on the periphery of the locking ring.

Images