EP1848900A2 - Entrainement lineaire par moteur electrique - Google Patents

Entrainement lineaire par moteur electrique

Info

Publication number
EP1848900A2
EP1848900A2 EP06708323A EP06708323A EP1848900A2 EP 1848900 A2 EP1848900 A2 EP 1848900A2 EP 06708323 A EP06708323 A EP 06708323A EP 06708323 A EP06708323 A EP 06708323A EP 1848900 A2 EP1848900 A2 EP 1848900A2
Authority
EP
European Patent Office
Prior art keywords
linear drive
drive according
electromotive linear
spindle
spindle nut
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP06708323A
Other languages
German (de)
English (en)
Inventor
Heinrich Dück
Christian Müller
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Dewertokin GmbH
Original Assignee
Dewert Antriebs und Systemtechnik GmbH and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Dewert Antriebs und Systemtechnik GmbH and Co KG filed Critical Dewert Antriebs und Systemtechnik GmbH and Co KG
Publication of EP1848900A2 publication Critical patent/EP1848900A2/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/10—Structural association with clutches, brakes, gears, pulleys or mechanical starters
    • H02K7/102—Structural association with clutches, brakes, gears, pulleys or mechanical starters with friction brakes
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65D—CONTAINERS FOR STORAGE OR TRANSPORT OF ARTICLES OR MATERIALS, e.g. BAGS, BARRELS, BOTTLES, BOXES, CANS, CARTONS, CRATES, DRUMS, JARS, TANKS, HOPPERS, FORWARDING CONTAINERS; ACCESSORIES, CLOSURES, OR FITTINGS THEREFOR; PACKAGING ELEMENTS; PACKAGES
    • B65D73/00—Packages comprising articles attached to cards, sheets or webs
    • B65D73/0078—Packages comprising articles attached to cards, sheets or webs the articles being retained or enclosed in a folded-over or doubled card
    • B65D73/0085—Packages comprising articles attached to cards, sheets or webs the articles being retained or enclosed in a folded-over or doubled card within a window, hole or cut-out portion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
    • F16H25/20—Screw mechanisms
    • F16H25/24—Elements essential to such mechanisms, e.g. screws, nuts
    • F16H25/2454—Brakes; Rotational locks
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/06—Means for converting reciprocating motion into rotary motion or vice versa
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
    • F16H25/20—Screw mechanisms
    • F16H25/24—Elements essential to such mechanisms, e.g. screws, nuts
    • F16H25/2454—Brakes; Rotational locks
    • F16H2025/2463—Brakes; Rotational locks using a wrap spring brake, i.e. a helical wind up spring for braking or locking
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/18—Mechanical movements
    • Y10T74/18568—Reciprocating or oscillating to or from alternating rotary
    • Y10T74/18576—Reciprocating or oscillating to or from alternating rotary including screw and nut
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/18—Mechanical movements
    • Y10T74/18568—Reciprocating or oscillating to or from alternating rotary
    • Y10T74/18576—Reciprocating or oscillating to or from alternating rotary including screw and nut
    • Y10T74/18704—Means to selectively lock or retard screw or nut

Definitions

  • the invention relates to an electromotive linear drive with one of a
  • the electromotive linear drive in question can be used for a variety of
  • Adjustment functions are used to adjust with the connection part of the lifting tube coupled components. This can be done directly, for example via a lever or a fitting.
  • the adjustment of the connected components is relatively low, since the speed of the spindle when the drive motor is also relatively low.
  • the opposite adjustment movements of a connected component are normally carried out with the drive motor, that is, the adjustment of a connected component depends on the direction of rotation of the spindle or whether the spindle nut is moved in the direction away from the drive unit or towards the drive unit.
  • linear drives are known in which, for example, by a coupling, the drive connection between the drive unit and the spindle is interrupted by a so-called uncoupling. In the industry, this process is called the disengagement of a drive. If the drive connection between the drive unit and the spindle is interrupted or disengaged and the threaded spindle is not self-locking, the connected component abruptly moves into a starting position due to its own weight.
  • linear drives in question are to be regarded as mass products, which are to be manufactured as simply as possible and consequently also as inexpensively as possible.
  • brake assemblies for controlling the speed of the spindle with the drive motor off not only the brake assemblies are necessary, but also the Entkuppelüen. Consequently, the design effort is relatively high, so that the cost of producing the linear drives are correspondingly high.
  • the invention has for its object to design a linear drive of the type described in more detail in a structurally simple manner and a minimum number of components so that in the case of a meaningful disengagement the displacement of a component connected to the linear drive component is increased with the drive motor from the normal speed and by the regulation of the linear velocity component of the lifting tube.
  • the spindle nut is in operative connection with the brake assembly, that in the adjustment of the lifting tube with the drive motor, the spindle nut frictionally with the spindle in a drive function and is non-rotatably arranged by housing parts of the linear drive, and at least when the drive motor is switched off, the force acting on the spindle nut by the brake unit can be reduced in a regulated manner, so that the spindle nut is capable of rotating, that the linear speed component of the lifting tube can be influenced by the braking force transmitted to the spindle nut by the brake assembly. Due to the operative connection between the brake assembly of the spindle nut according to the invention eliminates the hitherto necessary disengaging or uncoupling of the gear train.
  • the spindle nut In the normal case, that is, in both directions of rotation of the spindle when the drive motor is activated, the spindle nut is secured against rotation by the force acting on the spindle nut of the brake assembly, so that it moves depending on the direction of rotation of the spindle in the longitudinal direction.
  • a component connected to the linear drive can be adjusted with the speed component resulting from the rotational speed of the spindle, wherein the adjusting movement of the component can also be a pivoting movement.
  • the adjustment speed can be increased, the speed is not determined by the speed of the spindle, but by acting on the spindle nut, applied by the brake assembly force, since the spindle nut can rotate relative to the spindle.
  • the speed of the component connected to the linear drive is determined by the linear velocity component of the spindle nut.
  • the spindle nut can also be moved linearly with respect to the spindle during rotation of the spindle.
  • the particular advantage of the arrangement according to the invention lies in the fact that no decoupling or disengaging unit is necessary for adjusting a component with respect to the normal speed of increased speed.
  • the adjustment of a component is independent of the spindle no longer by the drive technology decoupling in the area between the drive unit and the spindle, but in the area between the spindle nut and the connecting part of the lifting tube.
  • This free movement of the component can, depending on the design of the linear drive in the region between the spindle nut and the housing or between the spindle nut, a housing part and the housing or between the spindle nut, a guide member and the housing or in the region between the spindle nut and the hub - Roehr lie.
  • the lifting tube is arranged non-rotatably, and that the spindle nut is rotatably supported by means of a bearing element firmly inserted into the lifting tube.
  • This bearing element acts schl formatmindernd and is in a preferred embodiment made of a sliding bearing material bearing bush, an axial sliding or rolling bearings.
  • a rolling bearing and in a preferred embodiment, a needle bearing.
  • connection of the lifting tube with the spindle nut can be done in various ways.
  • the lifting tube is fixedly connected to the spindle nut, and that the lifting tube is rotatably mounted with its free end portion in the connecting part. If then the adjustment speed of the connected component is to be increased by reducing the force applied by the braking and transmission means, the lifting tube can rotate synchronously with the spindle nut.
  • the braking and transmission means described above forward the forces to other components by friction.
  • a preferred embodiment is a
  • Braking and transmission means formed by at least one wrap the closer structure will be explained later.
  • Other braking and transmission means may be frictional clutches such as multi-plate clutches, cone clutches, disc brakes or shoe brakes. Also combinations of several similar or similar or different types of couplings and
  • the spindle nut is rotatably guided by a housing part, wherein the housing part is rotatably mounted within the housing relative to the housing of the electromotive linear drive. If now the adjustment speed of the connected component to be changed, the housing part can rotate synchronously with the spindle nut relative to the housing by influencing the brake assembly.
  • the spindle nut is rotatably guided by a guide member, wherein the guide member is rotatably mounted relative to the housing of the electromotive linear drive.
  • the braking and transmission means of the brake assembly can be formed from at least one wrap spring, a multi-disc clutch, a cone brake, a disc brake, a jaw brake or the like. These are tried-and-tested components in the industry, which are simple in construction and reliable in operation.
  • the brake assembly consists of at least one rotatably mounted on the spindle nut bushing, at least one bush surrounding the brake and transmission means or a wrap spring and an externally operable handle, wherein an end portion or a central region of the brake - And transmission means or the wrap spring or the wrap springs with the handle is in operative connection or stand.
  • at least one wrap spring may consist of a helically bent section with a plurality of turns, which has at least one section in the end and / or in the middle region, which deviates from the shape of the helical section.
  • the wrap spring With a first end or a middle region, the wrap spring is non-rotatably connected via a component to the housing or to a housing part or to a guide part of the electromotive linear drive.
  • the other end of the wrap spring is pivotally movable relative to the first or relative to the central region of the wrap around the axis of rotation of the turns, so that the diameter of the wrap around the Drehach- se of the turns pivotally movable so that the diameter of the wrap spring is changeable ,
  • all sections of the brake and transmission means or all sections of the wrap spring can be actuated together or in succession, so as to regulate the braking effect together or in a specific order one after the other.
  • the braking and transmission means transmits the force necessary to Unverdus ashamed the spindle nut indirectly to the spindle nut.
  • the braking and transmission means is biased so that the necessary force for the unrotatability of the spindle nut is generated.
  • the Handle is designed so that as sensitive as possible, this force is reduced, since upon actuation of the handle, the wrap is widened, so that the force acting on the bushing force is reduced so that the adjustment speed of a connected component can be controlled.
  • the brake and transmission means or the wrap can be firmly connected to this handle, but it is provided in a preferred embodiment, that the handle has a shift rod whose central longitudinal axis is parallel and spaced from the central longitudinal axis of the spindle and the axis of rotation relative to the own Center longitudinal axis is offset. In a figurative sense, this creates an eccentric arrangement, so that upon actuation of the handle the brake and transmission means or the wrap spring is already actuated when it rests with one end on a nose and the shift rod acts against this end.
  • the handle still has a switching ring, which rotatably mounted on the mounted on the spindle nut, operatively connected to the wrap spring socket. Gert is and which is actuated by the shift rod, wherein an end portion of the
  • the shift rod is designed as a profile bar which has a circular arc-shaped outer contour on at least one longitudinal edge region and a central constriction on at least one side.
  • Design is an extremely simple storage of the shift rod possible, since it is rotatably mounted with its circular arc-shaped outer contour in a guide channel formed from guide webs of the housing or an attached to the housing flange tube guide channel.
  • the guide webs are adapted to the circular arc-shaped contour of the shift rod and encompass the area by more than 180 °.
  • the constriction at least on one side then allows the rotational movement of the shift rod.
  • the shift rod is provided on each side in the central region with a confiscation. As a result, a symmetrical cross-section is achieved, with respect to the center axis perpendicular to one another. sen.
  • the semicircular outer contour of the shift rod is facing away from the brake and transmission means or the wrap spring in this execution.
  • the shift rod extends substantially over the region of the spindle, so that in each position of the spindle nut on this by the brake and transmission medium or by the wrap spring force can be reduced.
  • the shift rod has an annular cross-section or an annular cross-sectional portion, the center of the circle extends along or parallel to the central longitudinal axis of the spindle.
  • the shift rod can be rotated about an axis of rotation or moved along an axis. A combination of a rotary and a sliding movement of the shift rod may be possible.
  • Another embodiment provides a shift linkage with more than one shift rod.
  • the shift rails can move relative to one another both about an axis and in an axis, so that, moreover, a movement relative to the housing of the electromotive linear drive can also take place at the same time.
  • Element may also be formed by a flexible strand which is flexible at least in one degree of freedom.
  • the spindle nut is guided securely in the process along the spindle, it is provided that it has a guide ring in the central region, that on both sides of this guide ring are provided smaller in diameter projections of the spindle nut, that on at least one approach a socket is rotatably mounted, that at least one bush is surrounded by the braking and transmission means or the wrap spring, and that the other bushing is mounted in the bearing element or that the lifting tube is mounted on the other shoulder.
  • the shift rod is arranged in the intermediate space between the movable lifting tube and the fixed flange tube or the housing, it is provided that the flange tube or the housing is equipped with corresponding guide webs for the spindle nut.
  • the bushing surrounding the wrap spring faces the drive unit and the bushing of the drive unit mounted in the bearing element faces away from the drive unit.
  • the bushes can be made in a preferred manner of a metallic material, such as steel.
  • the spindle is also made of steel, while the spindle nut is made of a plastic.
  • one of the sockets preferably the bush surrounded by the braking and transmission means or the wrap spring, is equipped with a switching cam for actuating end switches which determine the end positions of the spindle nut.
  • This bushing with the switching cam has, in addition to the switching cam, further webs which, like the switching cam, extend in the longitudinal direction of the spindle and extend in longitudinal grooves of the housing, a housing section, a guide part or a flange tube.
  • a non-rotatable and longitudinally displaceable connection between the first end portion or central region of the braking and transmission means or the wrap spring and the housing is provided.
  • the brake and transmission means or the wrap spring is now connected to a housing section, a guide part or a flange tube in such a way that the adjustment speed of the connected component is changed when the force applied by the brake and transmission means or the wrap spring is reduced.
  • said housing section, the guide member or the flange tube is rotatably mounted relative to the housing of the linear drive.
  • the outer, surrounding the region of the spindle flange tube or the region of the housing is designed in its basic contour oval-shaped, wherein on the inner surface
  • the electromotive linear drive is designed as a furniture drive, preferably as a single drive, to adjust adjustable components of furniture, such as slatted frames, hospital and nursing beds and armchairs.
  • sealing elements are provided at least at the abutting edges of the housing parts, which prevent the penetration of liquids or solids into the housing.
  • parts of the outer skin of the linear drive can be made corrosion-resistant.
  • the electromotive linear drive has a housing section for receiving the spindle nut and essentially also the spindle.
  • This formed as a flange tube housing portion may be fixedly connected to the housing of the linear drive.
  • an element in the form of a flange or an adapter is arranged between the flange tube and the housing.
  • the flange tube may be fixedly connected to the flange while these
  • Flange flange tube assembly is detachably connected to the housing so that in different rotational angular positions, this unit can be fixed to the housing.
  • electromotive linear drive in which one end of the braking and transmission means or the wrap is firmly connected to another ring having a switching cam and in the longitudinal direction of the spindle extending webs, which are guided in longitudinal grooves of the flange tube , And that in the flange pipe limit switches for the end stop of the electric motor are installed in the respective end position, and that the limit switches are actuated by switching cam.
  • the electromotive linear drive is designed as a single drive, that is, it is equipped with a spindle and a spindle nut mounted thereon. tattet.
  • the linear drive is designed as a so-called double drive, which is equipped with two spindles and two spindle nuts, which are driven by two drive motors or by a drive motor. If a drive motor is used, the respective speed-reducing gearbox driving the spindle can be switchable via coupling elements.
  • the lifting tube in the connection region with the spindle nut has an internal thread, which is in engagement with an external thread of the spindle nut.
  • the internal thread is a fine thread, so that a very accurate setting of the internal thread
  • the spindle nut itself has an internally threaded bore, wherein the threads are formed as a movement thread, preferably as a trapezoidal thread.
  • Rolling springs can be applied, it is provided that a support sleeve is placed on the lifting tube in the spindle nut associated area, which has an inwardly directed annular projection, and that the spindle nut, the lifting tube and the support sleeve mutually aligned recesses, in the form-fitting connection of these components connecting elements, connecting portions, for example, engage or attack feather keys.
  • the lifting tube in the end region assigned to the spindle nut could also have a larger outer diameter than the rest of the region.
  • the support sleeve would be integrated into the lifting tube mutatis mutandis.
  • the bush with the lifting tube and / or the carrier sleeve could form a one-piece molded part.
  • the carrier sleeve and the lifting tube can be positively connected to one another, for example by means of threads or deformation sections.
  • the carrier sleeve can be attached to the lifting tube and / or have cross-sectional portions which may be web-like.
  • each inner diameter in the unmounted state is a little smaller than in the mounted state.
  • the inner circumferential surface of each wrap spring is frictionally engaged directly with the carrier sleeve.
  • the bushing is connected by connecting portions, for example by knurls or a tooth profile or connecting elements, for example by a plurality of feather keys with the support sleeve and / or with the lifting tube and / or with the spindle such that at least torques transmitted from the socket to the spindle nut are.
  • the support ring is also provided in this embodiment with a longitudinal slot and arranged loosely between stepped lugs or discs such that it transmits a frictional force of the associated wrap spring on the carrier sleeve, preferably transmits a torque frictionally from the associated wrap spring on the spindle nut.
  • a bearing ring is placed on the feather keys, which has an angular cross-section, wherein recesses are formed on the inner circumferential surface, which engage over the feather keys.
  • the area of the smaller diameter of the bearing ring faces the drive motor or the speed reduction gear.
  • On this side adjacent to the bearing ring a disc is attached, so that an open annular groove is formed. In this annular groove engages an approach of the guide flange, so that it is rotatable in the annular groove, but secured against axial displacement.
  • a lifting tube which has a large wall thickness, at least in one end region, so that the lifting tube forms a one-piece molded part at least with the carrier sleeve and / or the bushing.
  • the spindle nut could also have a section which is designed at least as a carrier sleeve and / or as a lifting tube.
  • the pitch direction of the threads of both the spindle, the spindle nut, and an additional nut are advantageously in a first direction preferably designed as a right-hand thread.
  • the electromotive linear drive is designed so as to generate adjusting forces, preferably in a first direction of movement.
  • the threads are formed in a second pitch direction, which is opposite to the first pitch direction, so that the linear drive generates an adjusting force in a second direction of movement.
  • a further embodiment provides that the carrier sleeve is associated with a guide device, whereby the guidance of the brake assembly is favored in the flange tube.
  • a guide device for this purpose, grooves or lugs may be formed on the carrier sleeve, which correspond with the guide device.
  • the guide device itself may be formed as a ring or as a ring portion, but is rotatably mounted with the support sleeve rotatable lengthwise and guided with the outer surface in the flange tube.
  • each wrap spring is angled and engages in a corresponding recess of the guide flange, wherein the second end of each wrap is in operative connection with a switching ring.
  • Each switching ring is rotatably mounted relative to the guide flange such that upon rotation of the switching ring, the diameter of the associated wrap spring is variable. Furthermore, it is provided that the angled end of the wrap spring is associated with an element having a higher strength than the guide flange.
  • the outer contour of the carrier sleeve is stepped. It is then possible that on each shoulder of the switching ring, the support ring, the
  • Support disc and the sleeve in the axial direction, so that at least these components are secured against displacement in one direction.
  • a retaining ring can engage in a groove of the carrier sleeve, so that at least the socket and / or a
  • Switching ring is secured against axial displacement. It may then be advantageous if the retaining ring is assigned to another disc. It is also advantageous if the carrier sleeve is formed from a metallic or non-metallic material, are placed on the metallic sleeves or sockets, for example made of a hardened steel. It is also advantageous if a control cam is still formed on the guide flange, so that a limit switch can be actuated in order to switch the current flow of the electromotive drive in an end position range. For exact guidance of the arrangement is still provided that webs are integrally formed on the guide flange, which engage slidably in correspondingly shaped longitudinal grooves of the flange tube.
  • annular projection of the support sleeve forms a spacer element, and that on the side facing away from the spindle nut an additional nut is mounted in the support sleeve.
  • this additional nut could be inserted into the lifting tube or coupled with the spindle nut.
  • the additional nut has a circumferential groove into which a holding element, for example an O-ring is inserted, so that the additional nut is connected to the carrier sleeve.
  • the retaining element is expediently elastic.
  • connection parts for connection of the electromotive linear drive are rotatably mounted on adjustable relative to other components components at the free ends of the lifting tubes. It is particularly advantageous if each connection part is designed as a clevis with a central slot and a transverse bore. However, other embodiments of each connecting part are possible, for example, flanges or pins, which have longitudinal and / or transverse bores or steps and threaded heads.
  • the rotatably mounted connection part is designed in a preferred embodiment as a structural unit, so that it can be used or attached in or at least partially in or on the free end of the lifting tube.
  • This assembly consists essentially of a first component, which is firmly connected to the lifting tube, for example by means of threads or deformations. A second part is then mounted to this first component so that it is rotatable.
  • the rotatable component is equipped with at least one bearing element, which is designed as a rolling bearing and / or as a sliding bearing and / or as a combination thereof, so that Forces are received in both the radial and in the axial direction between the first component and the second component, wherein at least the axial forces can be introduced into the lifting tube.
  • At least one sealing element is still provided, which protects the storage from the outside against the ingress of dust and moisture.
  • Another embodiment also provides a connecting element, which connects the first and the second component with each other and supports each other.
  • the connecting element is formed by a screw which is passed through the first and second component and is screwed into the second or in the first component.
  • the connecting element may also be a pin or a bolt, which is formed as a one-piece molded part with the first or with the second component.
  • Figure 1 shows an electromotive linear drive according to the invention in a partial view, the spindle associated area
  • Figure 2 shows the area shown in Figure 1 in a sectional view
  • FIG. 3 shows an enlarged view of the area marked in FIG. 2, containing the spindle nut
  • FIG. 4 is a perspective view of the region according to FIG. 1;
  • Figure 5 shows the area according to the figure 2 in perspective and in section
  • FIG. 6 is a perspective view of the region according to FIG. 3;
  • Figure 7 is an end view in the direction of the arrow VII in Figure 6;
  • Figure 8 shows a possible embodiment of a wrap spring
  • Figure 9 shows a further embodiment of the linear drive according to the invention in sectional view
  • FIG. 10 shows the embodiment according to FIG. 9 in a view.
  • FIGS. 1 to 6 For the sake of simplified illustration, only the part of the linear drive 10 affected by the invention is shown in FIGS. 1 to 6. As the figures show, this area includes a spindle 11 which is driven in rotation by a drive unit, not shown.
  • the drive unit consists of a drive motor in the form of a DC motor and a Drehierereduziergetriebe, which consists of a worm drive in a preferred embodiment, since such
  • the spindle 11 extends within an outer, fixed to a housing, not shown, flange 12, which may also be integrally formed with the housing.
  • the free, the drive unit remote from the end of the Flanschrohres 12 is closed by an end cap 33.
  • spindle nut 13 On the spindle 11 a explained in more detail with reference to FIG 3 spindle nut 13 is placed, which is in operative connection with a still further explained brake assembly 14.
  • the spindle nut 13 is connected to a lifting tube 15 such that the lifting tube 15 with respect to the flange tube 12 depending on the direction of rotation of the spindle 11 and retractable.
  • the braking device 14 consists essentially of a non-rotatably mounted on the spindle nut 13 bushing 16, a bush 16 surrounding wrap spring 17 and a relative to the sleeve 16 rotatable switching ring 18, which can be seen in Figures 6 and 7. Since the inner diameter of the wrap spring 17 after manufacture is smaller than the outer diameter of the bushing 16, a bias is built up due to the elasticity, so that it rests non-positively on the outer circumferential surface of the bush 16. The associated end of the wrap spring 17 is fixedly connected to the switching ring 18. The opposite End of the wrap spring 17 is fixedly connected to a second ring having a switching cam 19 and webs not shown, which are guided in longitudinal grooves of the flange tube 12. In the flange 12 are still housed limit switch 20 for the end of the electric motor in the respective end position. These limit switches 20 are actuated by the switching cam 19.
  • the bushing 16 could also be surrounded by more than one wrap spring 17 or loop spring sections 17a, 17b.
  • the wrap springs 17 could form a spring assembly, wherein the individual wrap springs 17 could be coupled together with their facing Stirnend Schemeen. However, they can also have a winding-free section in a bending process and be interconnected continuously with a blank.
  • the spindle nut 13 is provided in the central region with a guide flange 21, which is guided on the inside of the flange tube 12. On both sides of this guide flange 21, the spindle nut 13 is provided with smaller projections 22, 23. On the neck 22 which is surrounded by the wrap 17 bushing 16 is firmly placed. The connection of this approach 22 takes place positively by longitudinal webs which engage in corresponding grooves of the counterpart. On the neck 23, a bush 24 is fixedly mounted, which is mounted in a plain bearing bush 25 which is firmly inserted in the lifting tube 15. As the figure 3 shows, are the
  • Sockets 16 and 24 designed angular in cross-section.
  • the brake assembly 14 is facing the drive unit, not shown.
  • Figures 4 and 5 show the part of the linear drive 10 in a perspective view. These figures show that a connection element in the form of a clevis 26 is fixedly mounted on the free end of the lifting tube 15 facing away from the drive unit. Figures 4 and 5 show particularly clearly that the basic contour of the Flanschrohres 12 is oval-shaped, and that the spindle 11 is in an offset to the central longitudinal axis. In particular, Figure 4 shows that on the inside of the flange 12 webs are formed to support a handle 27 for actuating the switching ring 18 and to guide the spindle nut 13. As shown in particular Figures 6 and 7, the handle 27 consists of a switching rod 28 in the form of a profile bar.
  • the shift rod 28 contacts a nose of the shift ring 18, so that it is rotatable relative to the spindle nut 13 to widen the wrap spring 17.
  • the shift rod 28 extends substantially over the region of the spindle 11, so that the switching ring 18 can be rotated in any position of the spindle nut 13.
  • the shift rod 28 is located in a free space between the lift tube 15 and the flange tube 12.
  • the shift rod 28 is parallel and spaced from the spindle 11.
  • the shift rod 28 is parallel and spaced from the spindle 11.
  • Rotary axis of the shift rod 28 in offset from the central longitudinal axis, so that mutatis mutandis the effect of an eccentric is achieved, whereby the rotation of the switching ring 18 is effected.
  • FIG. 7 shows that the switching rod 28 consists of two round rods connected to one another via a web or the region facing away from the spindle 11 is circular arc-shaped, at least semicircular, and lies within a channel which is formed from two correspondingly shaped webs 29, 30 ,
  • the shift rod 28 embrace the webs 29, 30, the shift rod 28 by an angle which is greater than 180 °, so that the shift rod 28 is rotatable in the channel formed from the webs 29, 30 rotatable.
  • the shift rod 28 is provided in the middle region on both sides with recoveries.
  • the region facing the spindle 11 contacts a web 18a of the switching ring 18, since the web 18a is directed outwards.
  • the shift rod 28 can be by a lever attached to the outside of the housing or a
  • the housing of the linear drive 10 or the flange tube 12 is provided with a corresponding opening.
  • a retaining rail is inserted into the flange tube 12, which may, however, also be formed from integrally formed webs.
  • This support rail includes a linear potentiometer 31 with a slider 32 which is coupled to the spindle nut 13 and moves in synchronism with it in the longitudinal direction of the Flanschrohres 12 to determine the respective position of the spindle nut 13 with the drive motor off.
  • the spindle nut 13 and the housing consist essentially of a plastic.
  • the flange tube 12 may be made of a plastic or aluminum.
  • the shift rod 28 is rotated from the outside according to the counterclockwise a little, so that the wrap spring 17 widens, whereby the force exerted on the bush 16 and the resulting force Friction torque is reduced.
  • the wrap spring 17 can also be widened so far that no force is transmitted to the bushing 16, so that the connected component is lowered at an increased speed.
  • the wrap 17 retracts completely, so that the spindle nut 13 is completely braked and can not turn.
  • the spindle nut 13 is not positively secured against rotation in contrast to the previously known embodiments, but non-positively by the action of the wrap spring 17.
  • the Drehierereduziergetriebe can be designed so that it is self-locking, so that the force generated by the connected component with the drive motor off is held by the Drehierereduziergetriebe.
  • FIG. 8 shows a preferred embodiment of the wrap spring 17 used. Thereafter, this wrap spring 17 consists of two spaced sections 17a, 17b, which in the illustrated embodiment have the same number of turns and are spaced. The connection is made by a central web 36, which runs parallel and at a distance from the central longitudinal axis of the wrap spring 17, that is, it lies in the region of the turns of the sections 17a and 17b. Furthermore, FIG. 8 shows that the free end regions 34, 35 of the wrap spring 17 or of the sections 17a, 17b are angled outwards. They engage in the adjacent components, as already described.
  • FIG. 9 shows a longitudinal section of the electromotive linear drive 10.
  • the lifting tube 15 is on the spindle nut 13th associated end region provided with a thread, which is designated by the reference numeral 46.
  • the internal thread is a fine thread in a preferred embodiment and is in engagement with a corresponding external thread of the spindle nut 13.
  • the spindle nut 13 is screwed into the lifting tube 15 and connected via this thread 46 with the lifting tube.
  • the spindle nut 13 additionally has an internally threaded bore, which is equipped with flanks of a movement thread. In the illustrated embodiment, the movement thread is a trapezoidal thread.
  • a support sleeve 37 is placed in the associated end region, which has a stepped inner bore.
  • This carrier sleeve is made of plastic or a metal.
  • the spindle nut 13, the lifting tube 15 and the support sleeve 37 have mutually aligned recesses, in which a plurality of connecting elements in the form of feather keys 42 are used, so that the spindle nut 13, the lifting tube 15 and the support sleeve 37 are firmly connected.
  • the end region of the lifting tube 15 assigned to the spindle nut 13 could be correspondingly thick-walled, so that in this case the carrier sleeve is integrated in the lifting tube.
  • the support sleeve 37 and the lifting tube 15 could be positively connected to each other, for example by threads or deformation sections.
  • Socket 16 attached.
  • the right loop spring 17 in the illustration is placed on a support ring 44.
  • the bushing 16 by connecting elements, for example by a plurality of keys 42 with the support sleeve 37 and / or with the lifting tube and / or with the Spindelmut- ter 13 connected, so that at least torques from the sleeve 16 can be transmitted to the spindle nut 13.
  • the support ring 44 is provided in the illustrated preferred embodiment with a longitudinal slot and is loosely between staged approaches or discs 40 and transmits the frictional force of the associated wrap spring 17 on the support sleeve 37 and frictionally transmits a torque from the associated wrap 17 on the spindle nut 13th ,
  • FIG. 9 shows that a bearing ring 43, which has an angular cross-section, is placed on the region of the feather keys 42, wherein recesses are formed on the inner jacket surface, which engage over the feather keys 42.
  • a disc 40 is attached, so that an outwardly open annular groove is formed.
  • annular groove engages an approach of the guide flange 21, so that it is rotatably mounted in this annular groove, but secured against axial displacement.
  • One end of each wrap spring 17 is angled and engages in a corresponding recess of the guide flange 21 a.
  • the second end of each wrap spring 17 is in operative connection with a switching ring 18.
  • Each switching ring 18 is rotatably mounted relative to the guide flange 21 so that upon rotation of a
  • the carrier sleeve 37 has a stepped outer contour. On the surfaces of a stepped shoulder to the next step paragraph, the switching ring 18, the
  • securing elements for example in the form of a securing ring 41, engage in a groove of the carrier sleeve 37 and secure at least the bushing 16 and / or a switching ring 18 against axial displacement. It may be advantageous if the retaining ring 41 is still associated with a disc 40.
  • a switching cam 19 is further formed by a non-illustrated limit switch can be actuated to switch in a Endlagen Buffalo the current flow of an electric motor drive unit, not shown.
  • the carrier sleeve 37 is provided with an inwardly directed annular shoulder against which an additional nut 38 is supported on the outer side facing away from the spindle 11 or the spindle nut 13.
  • the additional nut 38 has a circumferential radial groove into which a holding element 39 is inserted.
  • This holding element connects the additional nut 38 with the carrier sleeve 37.
  • the holding element 39 is designed to be elastic. In the illustrated embodiment, it is formed by an O-ring.
  • FIG. 10 shows the position between the guide flange 21 and the switching ring 18 or the switching cam 19. As a result, a compact design and a convenient operation are achieved. In addition, the figure shows that the carrier sleeve 37 projects relative to the switching ring 18.

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  • Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Devices (AREA)

Abstract

La présente invention concerne un entraînement linéaire par moteur électrique (10) qui comprend un moteur d'entraînement et un engrenage réducteur couplé à celui-ci, destiné à entraîner un axe (11) sur lequel est monté un écrou (13), l'entraînement linéaire (10) étant en outre équipé d'un système de frein (14) pour réguler la vitesse de rotation de l'axe (11). L'invention a pour objet la conception d'un tel entraînement linéaire qui est simple de réalisation et permet d'éviter d'avoir recours au découplage d'entraînement de l'unité d'entraînement formée par le moteur d'entraînement et l'engrenage réducteur, et de l'axe (11). Selon l'invention, un système de frein (14) à ressort enroulé (17) équipe l'écrou (13), la force transmise par le ressort enroulé (17) à une pièce (16) disposée dans celui-ci, pouvant être régulée pour faire varier la vitesse de rotation de l'axe (11) par rapport à la vitesse de rotation normale. L'entraînement linéaire (10) de l'invention convient en particulier pour déplacer des pièces mobiles d'un meuble.
EP06708323A 2005-02-17 2006-02-16 Entrainement lineaire par moteur electrique Withdrawn EP1848900A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200520002585 DE202005002585U1 (de) 2005-02-17 2005-02-17 Elektromotorischer Linearantrieb
PCT/EP2006/060031 WO2006087365A2 (fr) 2005-02-17 2006-02-16 Entrainement lineaire par moteur electrique

Publications (1)

Publication Number Publication Date
EP1848900A2 true EP1848900A2 (fr) 2007-10-31

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EP06708323A Withdrawn EP1848900A2 (fr) 2005-02-17 2006-02-16 Entrainement lineaire par moteur electrique

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US (1) US8281677B2 (fr)
EP (1) EP1848900A2 (fr)
JP (1) JP5114214B2 (fr)
AU (1) AU2006215577A1 (fr)
DE (1) DE202005002585U1 (fr)
WO (1) WO2006087365A2 (fr)

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Also Published As

Publication number Publication date
AU2006215577A1 (en) 2006-08-24
AU2006215577A2 (en) 2006-08-24
WO2006087365A3 (fr) 2006-12-21
JP5114214B2 (ja) 2013-01-09
US8281677B2 (en) 2012-10-09
DE202005002585U1 (de) 2005-05-19
JP2008530471A (ja) 2008-08-07
WO2006087365A2 (fr) 2006-08-24
US20090044646A1 (en) 2009-02-19

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