WO2006108400A1 - Axe lineaire - Google Patents

Axe lineaire Download PDF

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Publication number
WO2006108400A1
WO2006108400A1 PCT/DE2006/000645 DE2006000645W WO2006108400A1 WO 2006108400 A1 WO2006108400 A1 WO 2006108400A1 DE 2006000645 W DE2006000645 W DE 2006000645W WO 2006108400 A1 WO2006108400 A1 WO 2006108400A1
Authority
WO
WIPO (PCT)
Prior art keywords
unit according
guide unit
linear guide
guide
linear
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.)
Ceased
Application number
PCT/DE2006/000645
Other languages
German (de)
English (en)
Inventor
Marco Jaekel
Stefan Niermann
Gerhard Baus
Frank Blase
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.)
Igus GmbH
Original Assignee
Igus GmbH
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 Igus GmbH filed Critical Igus GmbH
Priority to DE112006001562T priority Critical patent/DE112006001562A5/de
Publication of WO2006108400A1 publication Critical patent/WO2006108400A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C29/00—Bearings for parts moving only linearly
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/084—Characterised by the construction of the motor unit the motor being of the rodless piston type, e.g. with cable, belt or chain
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C29/00—Bearings for parts moving only linearly
    • F16C29/02—Sliding-contact bearings
    • 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
    • F16H19/00—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion
    • F16H19/02—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion for interconverting rotary or oscillating motion and reciprocating motion
    • F16H19/06—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion for interconverting rotary or oscillating motion and reciprocating motion comprising flexible members, e.g. an endless flexible member
    • 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
    • F16H19/00—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion
    • F16H19/02—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion for interconverting rotary or oscillating motion and reciprocating motion
    • F16H19/06—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion for interconverting rotary or oscillating motion and reciprocating motion comprising flexible members, e.g. an endless flexible member
    • F16H19/0672—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion for interconverting rotary or oscillating motion and reciprocating motion comprising flexible members, e.g. an endless flexible member characterised by means for tensioning the flexible member
    • 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
    • F16H19/00—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion
    • F16H19/02—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion for interconverting rotary or oscillating motion and reciprocating motion
    • F16H19/06—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion for interconverting rotary or oscillating motion and reciprocating motion comprising flexible members, e.g. an endless flexible member
    • F16H2019/0681—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion for interconverting rotary or oscillating motion and reciprocating motion comprising flexible members, e.g. an endless flexible member the flexible member forming a closed loop
    • F16H2019/0686—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion for interconverting rotary or oscillating motion and reciprocating motion comprising flexible members, e.g. an endless flexible member the flexible member forming a closed loop the flexible member being directly driven by a pulley or chain wheel

Definitions

  • the invention relates to a linear guide unit having a support profile, which has an open cross section, at least one guide rail on which at least one guide carriage is displaceable, a closed traction means for driving the guide carriage, and a respective deflection roller for the traction means at opposite ends of the support profile, wherein the Deflection rollers are arranged in flanged deflection housings.
  • a generic linear guide unit is known. This is provided with a supporting profile, which has a so-called open cross section, which is to be distinguished from a geunterenen cross-section.
  • An open cross section differs from a closed cross section, inter alia, by the course or by the distribution of the absorbable shear stresses.
  • shear stresses occur in a closed cross-section, like a liquid that circulates in an annular vessel.
  • an open profile for example a longitudinally slotted tube or a U-profile
  • the circulation of the shear stresses is interrupted.
  • the torsional stiffness of an open profile is thus significantly lower than the torsional rigidity of a closed profile.
  • a support profile with an open cross-section is sufficient for a linear guide unit when it is mounted on a sufficiently rigid substructure. Otherwise, namely without a sufficiently viable substructure, a rigid support profile must be provided which, for example, is a stable one having closed support profile. Support profiles with open cross-section must be connected over its entire length with a sufficiently warp-resistant substructure.
  • the open support profile according to EP 0 340 751 A2 forms a receptacle for an inner guide rail, which is mounted with a plurality of screws and an abutment rail with female threads.
  • the overall height of the open support profile is greater than its width.
  • the known support profile is provided with a deep upwardly open cavity, on the bottom of the guide rail is screwed.
  • the supporting profile is a complex component. For the production of the support profile many mechanical processing steps and for the assembly of the linear guide unit many assembly steps are necessary. The known linear guide unit is therefore expensive.
  • the invention has for its object to provide a linear guide unit, which is structurally simpler and cheaper to manufacture.
  • this object is achieved in that the support profile and the guide rail are integrated in a flat support profile guide, and that at least one mounting post is attached to an underside of the flat support profile guide facing away from the guide carriage.
  • the known support profile of EP 0 340 751 A2 has a height that corresponds to the height of the deflection housing.
  • a traction means always has a minimum radius of wrap. This wrap radius specifies the minimum diameter of the pulley.
  • the support profile according to EP 0 340 751 A2 is adapted to the overall height of the deflection housing.
  • the invention proposes the technical way to optimize the height of the deflection housing and the support profile in terms of cost-effective production.
  • the guide rail is formed integrally with the support profile.
  • the support profile guide obtained in this way has a particularly flat shape.
  • the invention provides to solve this problem, to wrap around the support profile guide with the traction means.
  • the arranged on an upper side of the support profile guide part of the traction means forms a Lasttrum.
  • the arranged on an underside of the support profile guide part of the traction means forms an empty strand.
  • the new construction of a linear guide unit with traction means and flat support profile guide requires further measures to produce over the length of the support profile guide a firm connection to a torsionally rigid substructure.
  • the invention provides at least one mounting post.
  • the mounting support creates a free space for the slack side. In addition, it bridges a distance between the underside of the support profile guide and the mounting surface of a substructure on which the linear guide unit is to be mounted.
  • the mounting bracket is an inexpensive component, for which neither a high material quality is required, nor a complicated mechanical processing.
  • the mounting post is located with its side facing away from the guide carriage free bearing side in the same plane as the side facing away from the guide carriage bottom of the deflector.
  • This design results in a common planar standing surface or bearing surface for the linear guide unit, composed of the undersides of the deflection housing and the free underside of the mounting bracket. In this way, the entire linear guide unit, namely both the deflection housing and the support profile guide can be fixed by means of the mounting post on a flat torsion-resistant substructure.
  • tensioning device for the traction means.
  • the tensioning device is simply arranged in a deflecting housing.
  • an arrangement of the clamping device on the guide carriage is possible. The latter is, however, considered kinematically disadvantageous because components of the clamping device must be accelerated or decelerated with each movement of the guide carriage. Any weight saving favors the dynamics of the carriage movement.
  • a clamping device on the guide carriage increases its mass to be moved inappropriate.
  • the clamping device may comprise at least one displacement element, with which the deflection roller is rotatably mounted.
  • the displacement element is displaceable within the deflection housing in the longitudinal direction of the linear guide unit.
  • the handling of the clamping device can be simplified if at least one adjusting element is provided for adjusting the position of the displacement element. As a simple adjustment is an adjustment into consideration, which cooperates with the displacement element. If the adjusting screw has a sufficiently low thread pitch, self-locking between the adjusting screw and an associated threaded bore results in the adjusted displacement position being maintained without further securing measures during operation of the linear guide unit.
  • the adjusting element is designed as a pressure-loaded adjusting screw.
  • the screw head of the adjusting screw is simply supported on an inner wall of the deflecting housing.
  • the adjusting screw is protected in the deflection housing.
  • an opening is provided in the deflection housing, so that the screw head is accessible for a screwing tool. A reduction in the depth of engagement of the adjusting screw increases the tension of the traction device in this construction.
  • the traction means on ends which are mounted with at least one connection lock on the guide carriage.
  • the use of a shortened to the appropriate length traction simplifies the assembly of the linear guide unit.
  • the ends of the shortened traction means must be connected or connected to the guide carriage, so that there is a closed traction means. Tensile forces in the closed loop of traction means and guide slide around.
  • the guide carriage can with at least one
  • Linear bearings should be mounted on the guide rail.
  • the linear sliding bearing is a ⁇
  • Plain bearing plastic provided. Such a linear plain bearing can conveniently be operated dry and is insensitive to dirt.
  • the guide carriage has a plurality of linear plain bearings, which are displaceable on a guide rail, each with a sliding shoe with the interposition of a plain bearing sleeve. In this way, as required a guide carriage can be created in any size.
  • the sliding blocks can be coupled to each other with a carriage plate.
  • the support profile guide can be designed as a double support profile guide with two parallel guide rails, if an increased load capacity and rigidity is required.
  • At least one of the deflection rollers has a slide bearing. This can also be operated dry and is insensitive to dirt.
  • the sliding bearing of the deflection roller on a radial sliding bearing Since the traction means has a certain tension, it exerts in the sliding bearing radial bearing forces, which are absorbed by the radial sliding bearing.
  • the sliding bearing of the deflection roller may have an axial sliding bearing if.
  • Carrier element for transmitting a drive torque.
  • Deflection pulley for example, a drive shaft is provided, on which the drive roller is arranged with the interposition of a feather key. Furthermore, over one end of the shaft a drive movement are initiated.
  • a motor is provided to direct a drive torque in the pulley.
  • the traction means is preferably a toothed belt. This is useful because a timing belt can be operated without lubrication and requires little maintenance.
  • the support profile guide is made of metal, such as preferably aluminum.
  • the support profile guide or at least the guide rail made of a fiber composite material, such as a carbon fiber reinforced material.
  • 1 is a side view of a linear guide unit
  • Fig. 2 is a plan view of the linear guide unit according to
  • FIG. 3 is a sectional view according to III-III in Fig. 2,
  • FIG. 8 is a sectional view according to VIII-VIII in Fig. 2,
  • FIG. 9 is an enlarged sectional view according to IX-IX in Fig. 2.
  • the linear guide unit 1 on a flat support profile guide 2 with two integrated guide rails 2a and 2b. It is an open cross-section with a relatively low torsional rigidity.
  • a guide carriage 3 On the support profile guide 2, a guide carriage 3 is linearly mounted. The guide carriage 3 is driven by a traction means, namely a toothed belt 4.
  • the support profile guide 2 At the two front ends of the support profile guide 2 is ever a deflecting 5 or 6 provided therein with deflection rollers 7 and 8 respectively.
  • the support profile guide 2 i'st provided with mounting holes 9 to be connected to a substructure.
  • a mounting post 10 is attached on a side facing away from the guide carriage 3 underside of the support profile guide 2.
  • a mounting post 10 is attached on a side facing away from the guide carriage 3 underside of the support profile guide 2.
  • the guide carriage 3 has a carriage plate 11 and four linear bearings 12.
  • the arrangement of the linear sliding bearing 12 is best seen in the plan view of FIG. 2.
  • Each linear sliding bearing 12 is provided with a sliding block 13.
  • the sliding blocks 13 are mounted with the interposition of a plain bearing sleeve 14 on the guide rail 2a and 2b.
  • a shaft journal 15a of a shaft 15 is provided, via which a drive torque for driving the toothed belt 4 can be introduced.
  • FIG. 3 shows the arrangement and attachment of the toothed belt 4.
  • the toothed belt 4 wraps around the Support profile guide 2. It is guided at the ends of the support profile guide 2 on the pulleys 7 and 8 and forms two strands.
  • a strand is coupled to the guide carriage 3 and forms a load strand 4a.
  • the arranged on the other side of the support profile guide 2 strand forms a return strand 4b.
  • clamping pieces 16a which, like the toothed belt 4, have a tooth profile.
  • a clamping piece 16a engages the tooth profile of the toothed belt 4 and clamped by screws 16b against the carriage plate 11 of the guide carriage 3.
  • the connection with the clamping pieces 16a is provided on one of the support profile guide 2 facing bottom IIa of the carriage plate 11. The top of the carriage plate 11 thereby forms a free mounting surface IIb for a variety of devices.
  • the deflection housing 5 and 6 have a low overall height. Their size depends essentially on the size of the
  • Pulleys 7 and 8 which are housed in the deflecting 5 and. Because it is pulleys with low numbers of teeth, this allows a compact
  • the support profile guide 2 protrudes by a piece in the deflection housing 5, so that a positionally accurate and fixed
  • Guide rails 2a and 2b has.
  • the support profile guide 2 is surrounded by a toothed belt 4.
  • the toothed belt 4 wraps around a deflection roller 7. It forms a load strand 4a and a return strand 4b.
  • the load strand 4a is the guide rails 2a and 2b facing. Facing away from the guide rails 2a and 2b, the mounting post 10 is attached to the support profile guide 2.
  • the free side of the mounting bracket 10 is in the same plane as the adjacent bottom 5a of the Umlenkgeophuses 5 and the adjacent bottom 6a of the Umlenkgekoruses 6. In this way, over the entire length of the linear guide unit 1 results in a flat standing or supporting surface, with the Linear guide unit can be placed and fixed on a substructure.
  • the deflection housing 5 four adjusting screws 17 are arranged, which belong to a clamping device S for the traction means, the toothed belt 4.
  • the mounting bracket 10 of FIG. 4 is designed as a U-shaped profile 18. Between legs 18a of the U-shaped profile, a channel 19 is provided with space for the empty strand 4b. The empty strand 4b is encapsulated in the channel 19. The mounting bracket 10 bridges a height difference H between the support profile guide 2 and the bottom 5a of the deflection 5.
  • two mounting posts 10a and 10b are provided. These are particularly simple components which bridge the height difference H between the support profile guide 2 and the underside 5 a of the deflection housing 5. Between the mounting supports 10a and 10b results in a space for the slack side 4b. If the linear guide unit 1 is mounted on a substructure, an encapsulation of the sliver strand 4b also results in this construction field.
  • FIG. 10 Another alternative for a mounting post 10 is shown in FIG. It is a mounting bracket 10, which supports the support profile guide 2 partially.
  • the mounting bracket 10 has gaps 10c. These can serve, for example, to prevent accumulation of dirt that does not escape from a closed channel could.
  • the alternative shown in Fig. 7 provides for a modified support profile guide 2.
  • the support profile guide 2 has for this purpose support extensions 2c and 2d, which extend to both sides of the slack side 4b. Again, a mounting post 10 is provided. It is a simple mounting plate, which is attached to the free ends of the support extensions 2c and 2d. In the present case, the height difference H to be bridged between the support profile guide 2 and the underside 5a of the deflection housing 5 is less than in the exemplary embodiments of FIGS. 4 to 6.
  • Deflection housing 6 is with an already mentioned
  • Rotation axis of the guide roller 8 can be moved.
  • the deflection roller 8 is arranged on a shaft 15.
  • the shaft 15 is mounted on both sides of the guide roller 8 in the deflection housing 6.
  • the clamping device S is symmetrical. On both sides of the guide roller 8 block-like displacement elements 21 are provided. In the displacement elements 21, the shaft bearings for the shaft 15 of the guide roller 8 are arranged. For the purpose of tension of the toothed belt 4, the displacement elements 21 in
  • the deflection housing 6 is for this purpose on both sides of
  • Deflection pulley 8 provided with sliding pockets 22, the one
  • the clamping force for the toothed belt 4 is generated with adjusting screws 23.
  • the adjusting screws 23 cooperate Tapped holes 24 in the displacement elements 21 together.
  • the threaded bores 24 are arranged parallel to the direction of displacement of the displacement elements 21.
  • the adjusting screws 23 are screwed into the threaded holes 24.
  • the screw heads 23a of the adjusting screws 23 abut against the inside of the deflection housing 6.
  • a reinforcement of the clamping force of the toothed belt 4 is achieved by the adjusting screws 23 are rotated back in the threaded holes 24 of the sliding element 21. That is, the depth of engagement of the adjusting screw 23 is reduced.
  • the thread pairing adjustment screw / threaded bore acts as a movement thread.
  • the change in the screwing depth is converted into a movement of the displacement element 21.
  • Increasing the screwing depth produces a decreasing toothed belt tension.
  • a reduction in the depth of engagement causes an increase in the toothed belt tension.
  • an opening 25 is provided in the deflection housing 6, through which the screw head 23a is accessible for a screwing tool.
  • the adjusting screw 23 has a low thread pitch. The thread has a self-locking effect.
  • Fig. 8 further shows that the second deflection housing 5 no Clamping device for the toothed belt 4 has. Nevertheless, in the second deflection housing 5, the same displacement elements 21 are provided to support the deflection roller 7. Also sliding pockets 22 are provided. Because adjusting screws are missing, the displacement elements 21 are supported by the clamping force of the toothed belt 4 against the inner wall of the deflection housing 5, which serves as an abutment in the case.
  • Fig. 9 is a partial sectional view through the deflection housing 6 and through the driven shaft 15 is shown.
  • the illustrated shaft end 15 b is mounted in a displacement element 21.
  • the displacement element 21 is in turn received in a sliding pocket 22 of the deflection housing 6.
  • the illustrated shaft bearing has two separate plain bearings. It is a plain bearing sleeve 26 which sits in a bore of the displacement element 21 and about a slide bearing plate 27, which faces the deflection roller 6, laterally applied to the displacement element 21.
  • the plain bearing sleeve 26 serves to receive radial forces. With the slide bearing plate 27 axial forces are absorbed, which forwards the shaft 15 via a retaining ring 29 received in an annular groove 28. Between the plain bearing washer 27 and the retaining ring 29, an additional support plate 30 is provided. The support disk 30 prevents an axial force transmitted through the securing ring 29 not only acting against the edge of the sliding bearing sleeve 26, but also being received by the displacement element 21.
  • Fig. 9 shows a shaft-hub connection for the purpose of transmitting a drive torque from the shaft 15 in the guide roller 8.
  • the shaft-hub connection has a feather key 31.
  • the feather key 31 is mounted in a keyway 32 of the shaft 15.
  • the bore of the guide roller 8 also has a keyway 33, so that the positive shaft-hub connection shown can be mounted.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Bearings For Parts Moving Linearly (AREA)

Abstract

Unité de guidage linéaire (1) qui comporte un profilé de support (2) présentant une section transversale ouverte, au moins un rail de guidage (2a, 2b) sur lequel peut coulisser au moins un chariot de guidage (3), un moyen de traction fermé (4) destiné à entraîner le chariot de guidage (3), et une poulie de renvoi (7, 8) pour le moyen de traction (4) située aux extrémités opposées du profilé de support (2), les poulies de renvoi (7, 8) étant situées dans des boîtiers de renvoi (5, 6) raccordés par une bride. L'objet de la présente invention est la mise au point d'une unité de guidage linéaire à structure plus simple et pouvant être fabriquée à moindre coût. A cet effet, le profilé de support (2) et le rail de guidage (2a, 2b) sont intégrés dans un ensemble de guidage plat (2) à profilé de support, et au moins un support de montage (10, 10a, 10b) est monté sur la face inférieure, opposée au chariot de guidage (3), de l'ensemble de guidage plat (2) à profilé de support.
PCT/DE2006/000645 2005-04-11 2006-04-11 Axe lineaire Ceased WO2006108400A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112006001562T DE112006001562A5 (de) 2005-04-11 2006-04-11 Linearachse

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200520005761 DE202005005761U1 (de) 2005-04-11 2005-04-11 Linearachse
DE202005005761.4 2005-04-11

Publications (1)

Publication Number Publication Date
WO2006108400A1 true WO2006108400A1 (fr) 2006-10-19

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2006/000645 Ceased WO2006108400A1 (fr) 2005-04-11 2006-04-11 Axe lineaire

Country Status (2)

Country Link
DE (2) DE202005005761U1 (fr)
WO (1) WO2006108400A1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1975463A2 (fr) 2007-03-30 2008-10-01 Robert Bosch GmbH Unité linéaire
CN106481764A (zh) * 2016-11-22 2017-03-08 宁波舒普机电股份有限公司 一种直线传动模组
DE102016107396A1 (de) 2016-04-21 2017-10-26 Festo Ag & Co. Kg Schlitten zum Führen an einer Linearführungseinheit
CN109026991A (zh) * 2018-09-06 2018-12-18 上海超客机器人有限公司 一种上下引导式直角转向系统
CN111288133A (zh) * 2020-03-27 2020-06-16 北京众驰伟业科技发展有限公司 一种直线拖动机构及直线驱动设备
US20210021115A1 (en) * 2018-03-28 2021-01-21 Igus Gmbh Line guiding appartus

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202010015448U1 (de) 2010-11-12 2011-02-24 Perneder, Raimund Rotatorische Übertragungseinheit
DE102017113540A1 (de) * 2017-06-20 2018-12-20 Technische Universität Darmstadt Linearführung und ein Verfahren zu deren Herstellung

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0200694A2 (fr) * 1985-04-22 1986-11-05 Tollo System Ab Rail profilé avec à l'intérieur un ou des chariots entraînés par une courroie
EP0340751A2 (fr) * 1988-05-06 1989-11-08 Deutsche Star GmbH Unité de guidage rectiligne
DE9211223U1 (de) * 1992-08-21 1992-11-05 Giessler, Werner, 7615 Zell Lineareinheit in Portalausführung
WO1993009356A1 (fr) * 1991-10-28 1993-05-13 Leif Gullblom Agencement destine a l'orientation laterale d'un bloc coulissant
US5445045A (en) * 1991-08-01 1995-08-29 Smc Kabushiki Kaisha Actuator and actuator arrangement
US20050054468A1 (en) * 2003-09-09 2005-03-10 Smc Kabushiki Kaisha Actuator

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0200694A2 (fr) * 1985-04-22 1986-11-05 Tollo System Ab Rail profilé avec à l'intérieur un ou des chariots entraînés par une courroie
EP0340751A2 (fr) * 1988-05-06 1989-11-08 Deutsche Star GmbH Unité de guidage rectiligne
US5445045A (en) * 1991-08-01 1995-08-29 Smc Kabushiki Kaisha Actuator and actuator arrangement
WO1993009356A1 (fr) * 1991-10-28 1993-05-13 Leif Gullblom Agencement destine a l'orientation laterale d'un bloc coulissant
DE9211223U1 (de) * 1992-08-21 1992-11-05 Giessler, Werner, 7615 Zell Lineareinheit in Portalausführung
US20050054468A1 (en) * 2003-09-09 2005-03-10 Smc Kabushiki Kaisha Actuator

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1975463A2 (fr) 2007-03-30 2008-10-01 Robert Bosch GmbH Unité linéaire
EP1975463A3 (fr) * 2007-03-30 2011-09-21 Robert Bosch GmbH Unité linéaire
DE102016107396A1 (de) 2016-04-21 2017-10-26 Festo Ag & Co. Kg Schlitten zum Führen an einer Linearführungseinheit
CN106481764A (zh) * 2016-11-22 2017-03-08 宁波舒普机电股份有限公司 一种直线传动模组
US20210021115A1 (en) * 2018-03-28 2021-01-21 Igus Gmbh Line guiding appartus
US12088072B2 (en) * 2018-03-28 2024-09-10 Igus Gmbh Line guiding apparatus
CN109026991A (zh) * 2018-09-06 2018-12-18 上海超客机器人有限公司 一种上下引导式直角转向系统
CN111288133A (zh) * 2020-03-27 2020-06-16 北京众驰伟业科技发展有限公司 一种直线拖动机构及直线驱动设备

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DE112006001562A5 (de) 2008-03-20

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