WO1990005617A1 - Systeme moteur permettant de produire un mouvement incrementiel entre deux corps et de mettre ceux-ci en position - Google Patents

Systeme moteur permettant de produire un mouvement incrementiel entre deux corps et de mettre ceux-ci en position Download PDF

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Publication number
WO1990005617A1
WO1990005617A1 PCT/DK1989/000269 DK8900269W WO9005617A1 WO 1990005617 A1 WO1990005617 A1 WO 1990005617A1 DK 8900269 W DK8900269 W DK 8900269W WO 9005617 A1 WO9005617 A1 WO 9005617A1
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WO
WIPO (PCT)
Prior art keywords
wedges
wedge
plate
bodies
tooth
Prior art date
Application number
PCT/DK1989/000269
Other languages
English (en)
Inventor
Hans MØLLER
Original Assignee
Moeller Hans
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
Priority claimed from DK634388A external-priority patent/DK634388A/da
Priority claimed from DK85689A external-priority patent/DK85689D0/da
Application filed by Moeller Hans filed Critical Moeller Hans
Publication of WO1990005617A1 publication Critical patent/WO1990005617A1/fr

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23Q—DETAILS, COMPONENTS, OR ACCESSORIES FOR MACHINE TOOLS, e.g. ARRANGEMENTS FOR COPYING OR CONTROLLING; MACHINE TOOLS IN GENERAL CHARACTERISED BY THE CONSTRUCTION OF PARTICULAR DETAILS OR COMPONENTS; COMBINATIONS OR ASSOCIATIONS OF METAL-WORKING MACHINES, NOT DIRECTED TO A PARTICULAR RESULT
    • B23Q16/00—Equipment for precise positioning of tool or work into particular locations not otherwise provided for
    • B23Q16/02—Indexing equipment
    • B23Q16/022—Indexing equipment in which only the indexing movement is of importance
    • B23Q16/023—Indexing equipment in which only the indexing movement is of importance by converting a reciprocating or oscillating movement into or linear indexing movement
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23Q—DETAILS, COMPONENTS, OR ACCESSORIES FOR MACHINE TOOLS, e.g. ARRANGEMENTS FOR COPYING OR CONTROLLING; MACHINE TOOLS IN GENERAL CHARACTERISED BY THE CONSTRUCTION OF PARTICULAR DETAILS OR COMPONENTS; COMBINATIONS OR ASSOCIATIONS OF METAL-WORKING MACHINES, NOT DIRECTED TO A PARTICULAR RESULT
    • B23Q1/00—Members which are comprised in the general build-up of a form of machine, particularly relatively large fixed members
    • B23Q1/25—Movable or adjustable work or tool supports
    • B23Q1/26—Movable or adjustable work or tool supports characterised by constructional features relating to the co-operation of relatively movable members; Means for preventing relative movement of such members
    • B23Q1/34—Relative movement obtained by use of deformable elements, e.g. piezoelectric, magnetostrictive, elastic or thermally-dilatable elements
    • B23Q1/36—Springs
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23Q—DETAILS, COMPONENTS, OR ACCESSORIES FOR MACHINE TOOLS, e.g. ARRANGEMENTS FOR COPYING OR CONTROLLING; MACHINE TOOLS IN GENERAL CHARACTERISED BY THE CONSTRUCTION OF PARTICULAR DETAILS OR COMPONENTS; COMBINATIONS OR ASSOCIATIONS OF METAL-WORKING MACHINES, NOT DIRECTED TO A PARTICULAR RESULT
    • B23Q16/00—Equipment for precise positioning of tool or work into particular locations not otherwise provided for
    • B23Q16/02—Indexing equipment
    • B23Q16/022—Indexing equipment in which only the indexing movement is of importance
    • B23Q16/026—Indexing equipment in which only the indexing movement is of importance by converting a reciprocating or oscillating movement into a rotary indexing movement
    • 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
    • F16H25/02—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms the movements of two or more independently moving members being combined into a single movement
    • 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
    • F16H49/00—Other gearings
    • F16H49/001—Wave gearings, e.g. harmonic drive transmissions
    • 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
    • F16H49/00—Other gearings
    • F16H2049/008—Linear wave gearings, i.e. harmonic type gearing imposing a strain wave to a straight flexible member engaging a second member with different pitch to generate linear motion thereof

Definitions

  • a otory system for producing a relative, incremental movement and positioning between two bodies
  • the present invention relates to a motory system for pro ⁇ ducing a relative, incremental movement and positioning between two bodies and of the type specified in the intro ⁇ ductory clause of claim 1.
  • the motory system has been enriched with such qualities that it may occur as a commercial pro ⁇ duct, and in the same connection it is realized that such product will not be limited to show a flat tooth row, since it may operate with certain advantages with a round rack, while an essential further possibility is the use of a rack which is curved in its longitudinal direction, viz. as a toothed rim on a rotatable system; hereby it will be possible to operate e.g. spindle valves in a processing plant.
  • Such a motory system according to the invention may be embodied in a simple and cheap manner based on the possibilities as indicated in claims 2 and 3 of arranging the wedge carrying plate portions and the associated, outer pressure pistons, respectively, as the latter may be arranged in an uncomplicated manner in respective con ⁇ centric layers about the cylindrical or circular tooth rack. Furthermore, in connection with the invention, it has been realized that for the practical usability of the discussed system it is decisive that it is possible to check that the single wedges really reach their bottom positions by the successive movements and not least by the terminating movement of the last wedge during the adjust ⁇ ment sequence, and the matter claimed in claim 4, there ⁇ fore, is of high importance to the invention.
  • Fig. 1 is a schematic side view of a motory system according to the invention.
  • Fig. 2 is a corresponding, more detailed view.
  • Fig. 3 is a schematic top view of the system.
  • Fig. 4 is an exploded perspective view of the system
  • Fig. 5 is a further exploded perspective view of the system
  • Fig. 6 is a sectional view illustrating a single actuator means
  • Fig. 7 is an exploded perspective view illustrating various parts of a system for producing a rotary movement
  • Fig. 8 is a sectional view of the same system shown in its assembled condition
  • Fig. 9 is a perspective view of a modified part thereof.
  • Fig. 10 is an end view thereof.
  • Fig. 11 is a corresponding view of the same part, further modified/ and
  • Figs. 12-18 are various views of further embodiments.
  • the system shown in Fig. 1 comprises a stationary rack 2 with transverse tooth ribs 4 forming declivities 6 between them and a block body 8 surrounding the rack 2 with slide fit and provided with protruding working cylinders 10, which are hose connected with a driving station 12 as ⁇ sociated with a control unit 14.
  • each cylinder 10 Inside the block body 8, underneath each cylinder 10, is located respective wedge heads 16,18,20 mounted at one end of respective, horizontal leaf springs 22, the other ends of which are fixed to the block.
  • the wedge heads 16, 18,20 are individually depressable by means of respective piston rods 11 of the cylinders 10, while they will other ⁇ wise assume a free position lifted off from the teeth 4 by the action of the leaf springs 22.
  • this wedge By depressing one of the wedges, e.g. the wedge 18 in Fig. 2, this wedge is pressed to the bottom of the underlying declivity, 6 in the rack 2, and because the wedge is horizontally undisplaceable relative the block 8 due to the leaf spring 22 the block will hereby move a distance along the rack, if the wedge.did not initially assume a position exactly over-the middle of the declivity.
  • the system is not just a movement or motory system, but also a positioning system, provided the toothing 4,6 on the rack 2 be equidistant with a required accuracy, the control unit 14 in a simple manner being able to account for the number of wedge actu ⁇ ations between consecutive stops of the block member 8.
  • Fig. 3 where five individually operable wedges 16,17,18,19 and 20 are shown.
  • the added wedges 17 and 19 are located pitchwise halfway between the respective neighbouring wedges 16,18 and 18,20, whereby the possibi ⁇ lity of a terminating depressing of the wedges 17 and 19 will involve that the block 8 can be stopset in an in ⁇ creased number of accurate positions.
  • Each single wedge can be supplemented with more wedges located after each other in the longitudinal direc ⁇ tion of the rack 2 with a pitch exactly as the pitch of the teeth 4, such that the force of displacement by the pressing in of the wedge body is distributed over the flanks of more teeth 4, whereby the associated wear is reduced. This is illustrated in the following figures.
  • Fig. 4 is shown a practical example of the design of the block body 8. It consists of a bottom part 26 for guidingly receiving the rack 2, an intermediate part 28 that carries the working wedges, and a top part 30 holding the required means for actuating the wedges.
  • the bottom part consists of a ⁇ -profiled base member 32 having at each end a cross block insertion 34, the lower edge of which is shaped in conformity with the upper cross secti ⁇ onal shape of the rack 2, while along the opposed insides of the upright side walls of the profile 32 there are mounted longitudinal guiding members 36 for the side edges of the rack 2.
  • the bottom part 26 will thus be ountable on the rack with slide fit about the rack.
  • the intermediate part 28 is a plate member which can be secured against the top side of the bottom part 26 and which carries at its underside a number of *wedge bodies for cooperation with the rack 2.
  • These wedge bodies are designated 40 and are each shaped with a number of single wedges 42 placed with exactly the same pitch as the teeth of the rack 2.
  • Each wedge body 40 is arranged on a longi ⁇ tudinally oriented plate strip member 44, which over a main portion is connected with a leaf spring 46 secured to the plate member 28 by a screw connection with a block member 48 depending from the plate member 28. It is indeed pos ⁇ sible that the block member 48 and optionally even the leaf spring 46 may be provided fully integrated with the plate member 28.
  • the wedge body is normally held in an upper position, in which the wedges 42 will be located entirely above the teeth of the rack 2.
  • the single wedge bodies 40 are mounted mutually slightly offset in the longitudinal direction with respect to their location relative the ' teeth of the rack 2, as ex ⁇ plained above.
  • the intermediate part 28 should carry an un ⁇ even number of wedge bodies 40, and it is an unqualified coincidence that in Fig. 4 only four such wedge bodies are shown.
  • the top part 30 is provided with the above mentioned actuators 10 for selective depression of the single wedge bodies 40, and these actuators, which are described in more detail below, are here powered by a pressure medium through laterally projecting stubs 50, which are connected with pressure hoses 52 leading to a non-illustrated pres ⁇ sure station corresponding to the unit 12 of fig. 1.
  • the base plate strips 44 of the wedge bodies 40 have extensions 54 with reduced width and extending beyond the wedge bodies 40.
  • these extensions 54 will be depressed, viz. down into the respective free spaces between the ⁇ -branches of the photosensors 38, such that through these it can be confirmed that each actuated wedge body is really pressed down into its bottom position, whereby such a detection may be used for * effecting an actuation order for the next wedge body.
  • the photo ⁇ sensors 38 are connected to a multiplug 56 on the*side of the bottom part 26.
  • the single wedge bodies 40 use is made of pressure pins which project downwardly from the top part 30 through holes in the intermediate plate member 28.
  • the top part consists of two double layer blocks 54 and 56 each consisting of two plate ele ⁇ ments 58 and 60 with an intermediate layer 62 of a rubber diaphragm material.
  • the lower plate element 58 is pro ⁇ vided some oblong holes 64, which accommodate respective, relatively thin plate members 66 that are just roughly fitting in the holes 64 and are each provided with a cen ⁇ tral, depending pin 68.
  • the diaphragm 62 extends flat over this or these areas, and in the underside of the upper plate element 60 there is provided a crosswise extending groove 70, see Fig.
  • each pin 68 projects down ⁇ wardly through a hole 72 in the plate member 28 of the intermediate part so as to step upon one of the underly ⁇ ing wedge bodies 40.
  • the working cylinders used are of a particularly sim ⁇ ple design, but normally the plate pistons 66 will occupy a relatively large area, such that ' the pins 68 cannot be arranged particularly close to each other.
  • a close juxtaposition is achievable with the use of the upper double layer block 56, which is designed principally equally, but with longer depending pins 68' placed offset relative the holes 64 in the bottom block 54.
  • This block is provided with extra throughlet holes 74 for the pins 68', whereby these may step upon further wedge bodies 40 through respective holes 72 in the intermediate plate member 28.
  • Fig. 4 it may be desirable that the wedge bodies be located in groups rather close to each other, and as they should ideally be centrally pressure loaded it may be difficult to arrange the pressure pins with corre ⁇ spondingly small mutual spacings. This problem, however, may be widely solved in that only some of the wedge bodies are actuated by centrally arranged pressure pins, while neighbouring wedge bodies are actuated not centrally, but 1 0
  • the pins may be arranged with generally increased spacing, e.g. such that two neighbouring piston plates 66 in one of the double layer blocks 54 or 56 operate a single wedge body in the said symmetrical manner, while a single piston plate in the other double layer block engages a neighbouring wedge body centrally.
  • one or more additional double layer blocks can be used in the top part 30, such that the number of operative pins 68 may be still further increased.
  • the invention is not correspondingly limited, • as it will include both an 'inverted engagement 1 , i.e. whereby a moving body with a rigid, short rack member is moved along a beam provided with a longer row of actuatable wedge bodies, and a movement along curved paths.
  • the lat ⁇ ter possibility is particularly interesting, as it may refer to a rotation of a shaft having teeth extending in the longitudinal direction thereof, such that an exact rotational adjustment of the shaft can be effected.
  • the rack may be shaped with a round cross section for cooperation with wedge bodies 40 placed around the rack, and the toothing could then be provided in a thread- ing-like manner, which will facilitate the production of the rack.
  • the shaft may be connected with a wider pinion cooperating with sur ⁇ rounding wedge bodies 40, as examplified further below.
  • the resilient leaf strips 46 con ⁇ sist of separate strips secured to the lower block plate 28, but these strips could be provided in an integral man ⁇ ner as cut out tongues of or in a lower plate member of a spring material.
  • an actu ⁇ ator housing 80 cooperates with a pinion 82 on a shaft rotatably mounted in bearings 86 in the housing 80.
  • the pinion 82 is surrounded by a cylinder member 88 having tongue portions 90, which at their free ends are provided internally with wedge bodies 92 and externally with pres ⁇ sure pads 94.
  • a cylindrical block 96 is provided about the cylinder member 88 , which corresponds to the plate block 58 in Fig.
  • the periphally oriented tongue portions 90 can be replaced by cross oriented tongue por ⁇ tions 112 shaped with a rather broad tongue root, at which there is preferably provided a peripheral slot 114, whereby the tongue portions 112 are easy to bend despite the part- cylindrical shape of their root portions.
  • the tongues do not extend in the longitudinal direction of the force acting on .the pinion, but rather crosswise thereto, and for the same reason it is empha ⁇ sized that these tongue portions have root areas of such a width that already hereby they will be widely stabilized against their outer ends of engagement being displaced in the peripheral direction of the pinion.
  • each tongue 112 there is provided two wedges 92' with a mutual spacing of two teeth on the pinion, such that these wedges in a likeworthy manner will be depres- sable into declivities on either side of a central, non- used declivity, corresponding to the depression of a single wedge into just that declivity.
  • the two wedges will meet almost exactly the same resist ⁇ ance, and at least it will hold true that in their fully depressed positions they will be located fully centered, here stabilizing the tongue against being twisted about its longitudinal axis.
  • Fig. 11 shows a modified design of the spring cylinder 88, viz. entirely without specific tongue portions.
  • the wedges 92" are mounted on suitable base means, and it will be noted that by the depression of a set of wedges there "will only occur some deformation of the cylinder 88, and the cylinder is able to transfer quite considerable forces in the peripheral direction.
  • the invention is not limited to the embodiments shown, as e.g. for the driving of a pinion it will be possible to use wedge bodies provided on straightlined leaf springs extending tangentially to the pinion and being held by a rigid carrier structure.
  • FIG. 12-15 A first embodiment is shown in Figs. 12-15, which can be compared with Fig. 8, i.e. where a controlled rotary movement between the coacting parts is to be produced.
  • the pinion 82 is rigidly mounted on a shaft 120 constituting on main part of the system and e.g. being terminated in a pin ⁇ ion 122 for external transfer of movement.
  • this pinion is replaced by a wheel 124 hav ⁇ ing an inclined front cam surface, which cooperates with a complementary cam block 126 that is non-rotatably mounted i in such a manner that a rotation of the wheel will result in an axial displacement of the block 126, i.e. such that a rotation of the shaft 120 will be transformed into an axial displacement..
  • the other main part of this system is a rigidly mounted cylinder 88, see also Figs. 8 and 11 of the parent application, this cylinder in Fig. 13 being shown mounted in an apparatus housing 108.
  • the cylinder is provided with inner wedge bodies 92, which by local depressions of the resilient cylinder shell 88 may engage with the pinion 82 and produce the discussed relative movements between the two main parts.
  • iron members 128 mounted internally (or optionally even externally) on the cylinder 88 immediately in front of the associated wedge bodies, and coaxially with the pinion 82 a radially extending permanent magnet 130 is mounted so as to be rotatable for successive mag ⁇ netic attraction of the.iron members.
  • the magnet 130 is mounted in a holder 132 protruding from a shaft bush 134, which is axially connected ' with a planetary gear 136 driven by a control motor 138.
  • the shaft bush 134 is freely rotatable on a projecting end of the pinion shaft 120, while it has a limited free rotata- bility of e.g. 45 with the connector shaft 140 to the planetary gear 136.
  • the magnet will thus still be freely rotatable, though it will of course be held magnet ⁇ ically by its attraction to the iron member 128, which could even - for increasing the attraction effect - be con ⁇ stituted by a counter polarized permanentmagnet.
  • the at ⁇ traction engagement may be very strong with the use of modern magnetic materials, however without a corresponding ⁇ ly strong holding force against a lateral retraction of the magnet 130 from the engagement, i.e. the magnet can be turned away by applying a relatively modest momentum from the shaft 140, which may thus be driven by a relatively weak motor 138 through the planetary transmission 136.
  • the attraction engagement with the iron or magnet member 128 will be released, whereby the cylin ⁇ der 88 at the relevant place will straighten resiliently so as to remove the wedge body from its engagement with the pinion 82.
  • the turning away of the magnet will be fol ⁇ lowed immediately by a turning in of the magnet underneath the neighbouring iron or magnet member 128, which will thereby be attracted for effecting the next step of the desired movement, confer the parent application.
  • the said partly free rotatability of the magnet relative its driving shaft 140 is of importance for securing that the magnet may be attracted by and pivot towards the next iron member 128 very rapidly after its driven retraction from the former holding engagement, such that the pinion 82 is not in the meantime entirely out of connection with either of the wedge bodies 92.
  • the motor 138 may be controlled as a step motor for stepwise rotation of the magnet 130 in one direction or the other, but it is possible to use a quite cheap and conventional, reversible motor, partly because the driving shaft 134,140 of the magnet may be driven through a low gear ratio and partly because in this shaft connection there is a certain inner rotatability which makes it acceptable that the motor does not stop quite abruptly.
  • cylinder 88 surrounds a cross toothed rod (not shown) and is designed with cut tongue portions 112 corresponding to the tongues 112 of the Fig. 9 of the parent application.
  • wedge bodies 92 At the interior sides of and the outer ends of these tongue portions is provided wedge bodies 92 for cooperation with the cross oriented teeth on a throughgoing rod.
  • the task will be to control the depression of the tongue ends in a sequentially con- 1 8
  • this is ob ⁇ tained by arranging on the outside of the tongue ends out ⁇ wardly projecting and angularly bent portions 144, while about this system there is provided a rotatable cylinder 148, which is spotwise provided with inwardly projecting carrier portions 150 at an innermost end an iron or magnet member 152, which by a rotation of the outer cylinder 148 can be turned into positions underneath the iron or magnet • members 146 on the holder portions 144, such that these will hereby be pulled inwardly for forcing the respective wedge bodies 92 against the cross toothing of the central rod, see also Fig. 17.
  • a rack 156 may cooperate with wedge bodies 158, which may be selectively forced against the rack in carrying magnet members 160 that can be depressed by the repelling force of an overlying permanent magnet 162, which is moved to and fro by means of a control cylinder 164, the magnet 162 being mounted in a holder 166, which by means of rollers 168 is supported against an outer rigid pressure surface 170.
  • the rack 156 may be moved forwardly or rearwardly all according to the magnet holder 166 being moved forwardly or rearwardly between the central or the left or the right hand repelling magnet 160, respec ⁇ tively.
  • cylinder ton ⁇ gues 112 are shown to be tapering in such a manner that when they project alternatingly to opposite sides it is possible to utilize a very large part of the area of the cylinder body 148.
  • the dimension of the actuator magnet in its own peripheral direction or its direction of movement should be big enough to avoid any slip in the successive actuation of the armature members 128,146, whereby it will also with the present system be achievable that the motory system will be self-locking against the occurrance of a free relative movement, as a wedge body will not be moved free of the toothing before the next wedge body has been brought into initial engagement therewith.
  • the wedge bodies may be pro ⁇ vided fully integrally with the material of the carrier cylinder, by die pressing and a following tempering there ⁇ of, such that the cylinder appears as a spring steel member.

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

Abstract

On peut obtenir un mouvement précis entre deux corps et les placer correctement (2 et 26, 28, 30) par l'abaissement progressif d'éléments réciproques à dents en quinconce (40, 42) se trouvant sur l'un des corps et qui s'engagent avec une rangée rectiligne de dents (4, 6) située sur l'autre corps (2). Le problème de l'usure des guides de ces éléments à dents, qu'entraîne la nécessité de transférer de grandes forces de déplacement, est ici résolu par le biais d'éléments à dents (40, 42) fixés sur des ressorts à lames, qui permettent aux éléments d'effectuer les mouvements d'entraînement requis tout en transférant sans friction au corps porteur pertinent (28) les forces transversales associées. On décrit également un dispositif avantageux d'entraînement (66, 68) pour actionner les éléments à dents, de même que l'application possible dudit principe de mouvement et positionnement pour produire des mouvements rotatifs.
PCT/DK1989/000269 1988-11-14 1989-11-14 Systeme moteur permettant de produire un mouvement incrementiel entre deux corps et de mettre ceux-ci en position WO1990005617A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DK6343/88 1988-11-14
DK634388A DK634388A (da) 1988-11-14 1988-11-14 Bevaegeindretning til relativ inkrementalbevaegelse og positionering mellem to legemer
DK85689A DK85689D0 (da) 1989-02-23 1989-02-23 Bevaegeindretning til relativ inkrementalbevaegelse og positionering mellem to legemer
DK856/89 1989-02-23

Publications (1)

Publication Number Publication Date
WO1990005617A1 true WO1990005617A1 (fr) 1990-05-31

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Application Number Title Priority Date Filing Date
PCT/DK1989/000269 WO1990005617A1 (fr) 1988-11-14 1989-11-14 Systeme moteur permettant de produire un mouvement incrementiel entre deux corps et de mettre ceux-ci en position

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AU (1) AU4623589A (fr)
WO (1) WO1990005617A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0524588A1 (fr) * 1991-07-22 1993-01-27 Charles Richiger Ag Moteur pas-à-pas, en particulier comme un actuateur pour des composants de machine
WO2003072979A1 (fr) * 2002-02-27 2003-09-04 Dr. Johannes Heidenhain Gmbh Engrenage et transducteur rotatif equipe de cet engrenage
NL1040681C2 (nl) * 2014-02-21 2015-08-25 Petrus Johannes Odems Inrichting voor het op een onderlinge afstand a uitvoeren van bewerkingen op een bewerkingsvlak van één of meer werkstukken.
WO2018038608A1 (fr) * 2016-08-23 2018-03-01 Universiteit Twente Moteur pas-à-pas pneumatique et dispositif comprenant au moins un tel moteur pas-à-pas pneumatique

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1172037A (en) * 1966-10-17 1969-11-26 Straumann Inst Ag Mechanism Comprising a Rachet Wheel Driven by at least one Vibratory Member
CH490628A (de) * 1968-07-30 1970-05-15 Fritz Hartmann Schrittschaltwerk
GB1194092A (en) * 1968-01-13 1970-06-10 Ferranti Ltd Improvements relating to Means for Producing Relative Movement Between Two Bodies
GB1472118A (en) * 1973-05-23 1977-05-04 Kennecott Corpper Corp Molybdenum and ferromolybdenum production

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1172037A (en) * 1966-10-17 1969-11-26 Straumann Inst Ag Mechanism Comprising a Rachet Wheel Driven by at least one Vibratory Member
GB1194092A (en) * 1968-01-13 1970-06-10 Ferranti Ltd Improvements relating to Means for Producing Relative Movement Between Two Bodies
CH490628A (de) * 1968-07-30 1970-05-15 Fritz Hartmann Schrittschaltwerk
GB1472118A (en) * 1973-05-23 1977-05-04 Kennecott Corpper Corp Molybdenum and ferromolybdenum production

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
DERWENT'S ABSTRACT NO. 85-241 763/39; & SU,A,1144849, publ. week 8539 (MINSK CAR IND.). *
DERWENT'S ABSTRACT NO. 88-27 351/04; & SU,A,1316793, publ. week 8804 (KAUN POLY). *

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0524588A1 (fr) * 1991-07-22 1993-01-27 Charles Richiger Ag Moteur pas-à-pas, en particulier comme un actuateur pour des composants de machine
WO2003072979A1 (fr) * 2002-02-27 2003-09-04 Dr. Johannes Heidenhain Gmbh Engrenage et transducteur rotatif equipe de cet engrenage
CN100351547C (zh) * 2002-02-27 2007-11-28 约翰尼斯海登海恩博士股份有限公司 传动机构及配有这种传动机构的自动同步发送机
US7694596B2 (en) 2002-02-27 2010-04-13 Dr. Johannes Heidenhain Gmbh Gear system and rotary transducer equipped with this gear system
NL1040681C2 (nl) * 2014-02-21 2015-08-25 Petrus Johannes Odems Inrichting voor het op een onderlinge afstand a uitvoeren van bewerkingen op een bewerkingsvlak van één of meer werkstukken.
WO2018038608A1 (fr) * 2016-08-23 2018-03-01 Universiteit Twente Moteur pas-à-pas pneumatique et dispositif comprenant au moins un tel moteur pas-à-pas pneumatique
US11898581B2 (en) 2016-08-23 2024-02-13 Machnet Medical Robotics B.V. Pneumatic stepper motor and device comprising at least one such pneumatic stepper motor

Also Published As

Publication number Publication date
AU4623589A (en) 1990-06-12

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