EP2929196A2 - Dispositif de guidage linéaire pour machines-outils - Google Patents

Dispositif de guidage linéaire pour machines-outils

Info

Publication number
EP2929196A2
EP2929196A2 EP13796083.7A EP13796083A EP2929196A2 EP 2929196 A2 EP2929196 A2 EP 2929196A2 EP 13796083 A EP13796083 A EP 13796083A EP 2929196 A2 EP2929196 A2 EP 2929196A2
Authority
EP
European Patent Office
Prior art keywords
guide
sliding
linear guide
guide rail
carriage
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Withdrawn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
EP13796083.7A
Other languages
German (de)
English (en)
Inventor
Ulrich Baumann
Ernst-Ulrich Schmitz
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.)
Index Werke GmbH and Co KG Hahn and Tessky
Original Assignee
Index Werke GmbH and Co KG Hahn and Tessky
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 Index Werke GmbH and Co KG Hahn and Tessky filed Critical Index Werke GmbH and Co KG Hahn and Tessky
Publication of EP2929196A2 publication Critical patent/EP2929196A2/fr
Withdrawn legal-status Critical Current

Links

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
    • 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
    • B23Q1/38—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 using fluid bearings or fluid cushion supports
    • 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
    • F16C29/007—Hybrid linear bearings, i.e. including more than one bearing type, e.g. sliding contact bearings as well as rolling 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/12—Force, load, stress, pressure
    • F16C2240/18—Stress
    • 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
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/30—Angles, e.g. inclinations
    • 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
    • F16C2322/00—Apparatus used in shaping articles
    • F16C2322/39—General buildup of machine tools, e.g. spindles, slides, actuators
    • 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
    • F16C29/008—Systems with a plurality of bearings, e.g. four carriages supporting a slide on two parallel rails
    • 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
    • F16C29/025—Hydrostatic or aerostatic
    • 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
    • F16C29/04—Ball or roller bearings
    • F16C29/06—Ball or roller bearings in which the rolling bodies circulate partly without carrying load
    • F16C29/0633—Ball or roller bearings in which the rolling bodies circulate partly without carrying load with a bearing body defining a U-shaped carriage, i.e. surrounding a guide rail or track on three sides

Definitions

  • the invention relates to a linear guide for machine tools, comprising a guide rail extending in a longitudinal direction and having a constant cross-sectional shape in the longitudinal direction, and at least one guide carriage guided on the guide rail and encompassing the guide rail in partial regions of the cross-sectional shape.
  • the guide carriage is guided either exclusively by sliding guides on the guide rail or guided exclusively by WälzSystem exiten on the guide rail.
  • Slideways have the advantage that they have a high rigidity and high damping against self-building oscillations, but the disadvantage that they do not have a very high load capacity and high accuracy can be achieved only with great effort, however.
  • Rolling element guides have the advantage that they can be achieved with high accuracy with little effort and have a high load capacity, but the disadvantage that they have a certain elastic compliance and oppose vibrations or vibration only a low attenuation.
  • the invention is therefore an object of the invention to improve a linear guide of the type described above such that on the one hand ensure a precise guidance of the carriage relative to the guide rail and on the other hand have a high rigidity and a high damping against vibration.
  • This object is achieved according to the invention in a linear guide of the type described above in that the guide carriage is guided on the guide rail by at least one sliding guide which has at least one provided on the guide rail Gleitstütz phenomenon on which abuts a Gleitauflage Colour of the carriage, that the
  • Guide carriage on the guide rail is guided by at least one Wälz phenomena entry having at least one arranged on the guide rail rolling element track and provided on the carriage rolling element arrangement whose rolling elements are rolling along the Wälzterrorismlaufbahn the guide rail movable and that the at least one sliding guide and the at least one Wälz phenomena entry so are arranged and adapted to take on the carriage and perpendicular to the longitudinal direction of the guide rail acting, but differently oriented support forces.
  • the advantage of the solution according to the invention is thus to be seen in that it combines at least one sliding guide with at least one rolling element guide for guiding the guide carriage on the guide rail, wherein the sliding guide and the rolling element guide accommodate differently oriented supporting forces, that is to say that they are received by the sliding guide Supporting forces perpendicular to the longitudinal direction have a different orientation than the supporting forces received by the rolling body guide, so that either the sliding guide or the rolling element guide or both are acted upon by appropriate supporting forces depending on the load on the guide carriage.
  • the supporting forces acting on the sliding guide and the rolling body guide are in particular never rectified, but lie in a plane perpendicular to the longitudinal direction of the guide rail and have a different orientation in this plane.
  • Component of the force acting in the main load direction receives force.
  • the sliding guide is arranged so that it absorbs the force acting in the main load direction force, so that, for example, in the main load direction force is no or only a marginal load on the rolling element guide, so that the carriage when acting in the main load direction Force can be performed by the at least one slide with their advantageous properties.
  • the WälzSystem thus ensures that even when exposed transversely or opposite to the main load direction is always a reliable guidance of the carriage in the longitudinal direction with the participation of the slide and the rolling element or even with the involvement of Wälzschreibève Office.
  • a particularly advantageous solution provides, however, that the at least one rolling element guide and the at least one sliding guide are prestressed.
  • a bias of a sliding guide is not known from the prior art, since the preloaded design of a sliding guide is very expensive.
  • An essential component of the force is the largest of the two components in a component disassembly of the force.
  • the sliding guide and the rolling element guide could be biased separately.
  • the at least one rolling element guide and the at least one sliding guide are arranged relative to one another in such a way that the prestressing of the at least one sliding guide occurs simultaneously when the at least one rolling element guide is pretensioned.
  • Such a bias voltage makes it possible to achieve a high degree of precision even without the action of a load on the linear guide according to the invention, and in the case of transverse load forces acting on the main load direction, the guide precision and the guide rigidity and the good damping properties of the slide guide for the guiding properties of the linear guide allow. If, in particular, the load-related forces mentioned remain under the prestressing force, the sliding guide also outweighs the behavior of the linear guide with regard to the guiding properties of the linear guide, even in the case of load-related forces acting transversely or oppositely to the main load direction.
  • the support of the rolling element guide for biasing the same with the rolling element biasing force causes a sliding guide biasing force to simultaneously act on and bias the sliding guide due to the support of the rolling element biasing force via the sliding guide, thereby providing the at least one sliding guide with high precision Guide the guide carriage on the guide rail, in particular combined with high rigidity and high precision, can be operated.
  • the at least one Wälzterrorism entry is formed so that the bias of the at least one Wälzterrorism entry is effected by an elastic deformation of the rolling elements.
  • Such an elastic deformation of the rolling elements can be achieved in that they can be elastically deformed due to the Hertzian pressure, so that their shape deviates under prestress from an exact spherical shape or an exact cylindrical shape.
  • Such deviation from the exact spherical or cylindrical shape is on the order of a few microns, for example in the range between 6pm and 20pm, around which in Hertzian pressure the distance between the sphere center or cylinder axis and the deformed region is the exact radius of the sphere or the cylinder deviates.
  • an advantageous solution provides that the at least one sliding support surface and the at least one sliding contact surface of the sliding guide run transversely to the main load direction.
  • the at least one sliding support surface and the at least one sliding support surface of the sliding guide extend at an angle in the range of 40 ° to 90 ° to the main load direction.
  • an advantageous solution provides that the sliding guide is designed for a surface load of 50 N / mm 2 or less, in which case special sliding pairings are used.
  • the sliding guide is designed for a surface load of 15 N / mm 2 or less, more preferably 5 N / mm 2 or less.
  • the sliding bearing as a sliding pair has a combination of steel with gray cast iron or steel with bronze or steel with plastic or gray cast iron with gray cast iron or cast iron with bronze or gray cast iron with plastic or ceramic with steel.
  • an advantageous solution provides that a sum of all Gleitst Reifen vom the linear guide and a sum of all the Gleitauflage inhabit the linear guide an extension transverse to the longitudinal direction of the guide rail and in particular transverse to the main load direction, which is at least 1.5 times a width of the guide rail.
  • the linear guide according to the invention comprises two sliding guides.
  • sliding guides In the case of two sliding guides it is provided that these are arranged on both sides of a guide plane of symmetry, wherein the guide plane of symmetry lies in particular centrally between the two sliding guides.
  • the Gleitstütz vom and the Gleitauflage lake the sliding guides are both transverse to the guide plane of symmetry, preferably arranged at an acute angle to the guide plane of symmetry.
  • an advantageous solution provides that a Gleit Resultssstützkraft each of the sliding guides has a parallel and a force acting transversely to the guide plane of symmetry force component.
  • the two sliding guides are arranged so that the forces acting transversely to the plane of symmetry of the force cancel each other.
  • a Gleit Resultssstützkraft include a sliding guide and Gleit Resultssst Reifenkraft the other slide an angle in the range of 30 ° to 150 ° or from 210 ° to 330 ° with each other.
  • an advantageous embodiment of the solution according to the invention provides that the sliding support surface and the Gleitauflagemachining a sliding guide and the Gleitstütz requirements and the Gleitauflage simulation the other slide include an angle in the range of 30 ° to 150 ° or 210 ° to 330 ° with each other.
  • the linear guide comprises two rolling element guides.
  • the two rolling element guides are arranged on both sides of a guide plane of symmetry.
  • An expedient arrangement of such two sliding guides provides that a rolling guide supporting force of each of the rolling element guides has a force component acting in parallel and transversely to the plane of the guide symmetry.
  • the rolling element guides are arranged such that the force components acting transversely to the plane of symmetry cancel each other out.
  • a Wälz operationsstützkraft of a WälzERA entry and a Wälz operationsstützkraft the other WälzERA entry include an angle in the range of 30 ° to 50 ° or from 210 ° to 330 ° with each other.
  • linear guide according to the invention capable of running dry.
  • a particularly favorable solution provides that a lubricating film is arranged between the sliding support surface and the sliding support surface of the at least one sliding guide.
  • this lubricating film could be a hydrostatic lubricant film, which would require a complicated lubricant supply.
  • the lubricating film is a hydrodynamic lubricant film.
  • the thickness of the lubricating film in each position of the guide carriage over the extension of the guide rail in the longitudinal direction varies by less than 10%.
  • Such a slightly varying thickness of the lubricating film can be achieved, in particular, by pretensioning the at least one sliding guide and the at least one rolling element guide relative to one another.
  • the lubricating film has a thickness in the range of 2 pm to 6 pm.
  • Fig. 1 is a schematic representation of a machine tool according to the invention
  • FIG. 2 is an illustration of a first embodiment of a linear guide according to the invention
  • FIG. Fig. 3 is an enlarged view of a plan view in the direction of the arrow X in Fig. 2;
  • FIG. 4 is a further enlarged view of the plan view of FIG. 3 in the area of sliding guides and rolling element guides
  • FIG. 6 is a view similar to FIG. 3 of a second embodiment of a linear guide according to the invention.
  • FIG. 7 is a view similar to FIG. 3 of a third embodiment of a linear guide according to the invention.
  • FIG. 8 is a view similar to FIG. 3 of a fourth embodiment of a linear guide according to the invention.
  • FIG. 9 is a view similar to FIG. 3 of a fifth embodiment of a linear guide according to the invention.
  • FIG. 1 schematically illustrated embodiment of a designated as a whole with 10 machine tool includes a machine frame 12, on which on the one hand a workpiece carrier 14, for example in the form of a workpiece spindle unit is arranged, in which a designated as a whole 16 workpiece about a workpiece spindle axis 18 is rotatably mounted.
  • a workpiece carrier 14 for example in the form of a workpiece spindle unit is arranged, in which a designated as a whole 16 workpiece about a workpiece spindle axis 18 is rotatably mounted.
  • a tool carrier 22 designated as a whole which, for example, carries a tool turret 24 which is rotatable about a tool turret axis 26 relative to the tool turret housing 28 by one of tools 32 held on the tool turret 24 in a machining position relative to the workpiece 16 bring in which a machining of the workpiece 16 by means of the tool 32 by relative movement of the two to each other is possible.
  • the relative movement between the workpiece 16 and the tool 32 is possible in that either the workpiece carrier 14 or the tool carrier 22 or both are movable relative to the machine frame 12.
  • cross slide which has on the one hand a Z-slide 42 which is guided parallel to the Z-direction by two mutually parallel linear guides 44a, 44b on the machine frame 12 and on the other hand, a tool turret housing 28 carrying X-carriage 46 which by parallel to each other and parallel to the X-direction linear guides 48a, 48b is guided on the Z-slide 42.
  • Such linear guides 44a, 44b and 48a, 48b are formed in the known machine tools either as slideways or as rolling guides in general, slideways have the disadvantage that they must be built to achieve a good management precision consuming and are not suitable for large loads, however, a high rigidity and have good damping properties against vibrations, while Wälz Entryen have the advantage of high guiding precision and have the disadvantage that they have a low rigidity and low damping properties for possibly occurring during machining of the workpiece 16 vibrations.
  • FIG. 2 and 3 illustrated first embodiment of a linear guide 50 according to the invention for machine tools 10 comprises a extending in a longitudinal direction 52 guide rail 54 which has a constant over its entire longitudinal direction 52 cross-sectional shape 56.
  • the guide rail 54 according to FIG. 2 and 3, a foot region 60, with which the guide rail 54 can be mounted on a mounting surface 62, wherein the foot portion 60 rests with a réellestützamide 64 on the mounting surface 62, and wherein in the embodiment of FIG. 1, the mounting surface 62 is formed by a support side 66 of the machine frame 12 or the Z-slide 42.
  • the foot region 60 comprises foot support surfaces 68a, 68b running transversely to the foot support 64 and in the longitudinal direction 52 and lying laterally of the guide rail 54, wherein at least one of the foot contact surfaces 68a, 68b, in the example shown in FIG. 2, comprises the foot contact surface 68a on a step surface 72 of the support side 66 abuts, which in conjunction with the effetstützamide 64, the possibility of a precisely rectilinear alignment of the guide rail 54 on the support side 66, for example, the machine frame 12 or the Z-slide 42 allows.
  • this is the total guide rail 54 with these passing through screws 58, for example, perpendicular to the mounting surface 62 extending screws 58, to the support side 66auf usden part, so for example the machine frame 12 or the Z-slide 42, fixed.
  • the guide rail 54 has a guide area designated as a whole with 80, which for example on both sides to a longitudinal center plane 82 of the guide rail 54, wherein the longitudinal center plane 82 preferably transversely, in particular perpendicularly, extends to neurosciencestütz torque 64, arranged guide contours 84a, 84b, which between the predominantlystrom vom 68a, 68b and one of the foot support surface 64 opposite rail surface 86 are located, preferably the
  • Rail surface 86 parallel to the foot support surface 64 extends.
  • the guide contours 84a and 84b are formed by side depressions 92a and 92b extending from the foot abutment surfaces 68 in the direction of the longitudinal center plane 82 into the guide rail 54, which faces a side surface 94a, 94b facing the foot support surface 64 and the rail surface 86 have ordered side surfaces 96a, 96b and lying between the respective side surfaces 94a and 96a and 94b and 96b, preferably parallel to the longitudinal center plane 82 extending base surfaces 98a and 98b have.
  • the side surfaces 94a and 94b and 96a and 96b extend on the one hand in the longitudinal direction 52 and on the other hand at an acute angle and symmetrically to the longitudinal center plane 82, wherein the acute angle is in the range of 30 ° to 60 °.
  • the side surfaces 96a and 96b extend in each case from the corresponding base surface 98a or 98b to upper outer surfaces 102a and 102b of the guide rail 54 which are parallel to the predominantlystrom matters 68a and 68b, preferably in alignment therewith and thus transverse to the rail surface 86 ,
  • at least one guide carriage 110 is arranged on the guide rail 54, which surrounds the guide rail 54 in the region of its rail surface 86 and the guide contours 84a and 84b and on the guide contours 84a and 84b by means of guide sections 112a and 112b, respectively.
  • the guide surfaces 114a and 114b which extend over the longitudinal direction 52 of the guide rail 54 and thus also in the longitudinal direction of the guide carriage 110 on the guide portions 112a and 112b, lie flat on the side surfaces 94a and 94b of the guide contours 84a and 84b and thus form sliding guides 120a and 120b, wherein in the overlap region between the side surfaces 94a and 94b and the guide surfaces 114a and 114b, the side surfaces 94a and 94b of
  • Guide rail 54 form Gleitstütz vom 124a and 124b and the guide surfaces 114a and 114b form slide bearing surfaces 126a and 126b, respectively, which constitute the slide guides 120a and 120b, the slide bearing surfaces 126a and 126b respectively having a sliding guide supporting force GSa and GSb perpendicular to the sliding supporting surfaces 124a and 124b, respectively, and mirror-symmetrical to Longitudinal plane 82 extend, which also forms a guide plane of symmetry 128 (Fig. 4).
  • the sliding guide forces GSa and GSb can be decomposed into components GSap and GSbp running parallel to the guide symmetry plane 128 and components GSas and GSbs running perpendicular to the guide symmetry plane 128, whereby the components GSas and GSbs cancel each other out, so that the components GSap and GSbp become a total - add sliding guide support GGS parallel to the plane of symmetry of the guide as shown in Fig. 4 shown.
  • the Automatverleiterssstützkraft GGS defines a main load direction HLR, so that in this main load direction HLR acting on the carriage 10 with a force KL load in the form of Bacleitleitstützkraft GGS is taken up exclusively by the sliding guides 120a and 120b, and thus a guide of the carriage 110 according to the already above properties of a pure sliding causes.
  • the side surfaces 96a and 96b form rolling element raceways 132a and 132b, respectively, on which the rolling elements 116a and 116b roll with their lateral surfaces when moving the guide carriage 110 in the longitudinal direction 52 and thus also support it.
  • the rolling element guides 130a and 130b lie on a side of the guide guide plane 134 which is opposite to the slide guides 120a and 120b and is perpendicular to the main load direction HLR.
  • the rolling body guides 130a and 130b are only for receiving a load acting on the carriage 110 in the direction of the total gear guide supporting force GWS, and thus opposite to the main load direction HLR, so that all loads acting opposite to the main load direction HLR from the rolling element guides 130a , 130b are received alone and thus the guidance of the guide carriage 110 takes place on the guide rail 54 exclusively in accordance with the above-mentioned properties of the rolling body guides 130a and 130b.
  • the WälzShConsequentlyn 118a and 118b could be arranged with the rolling elements 116a and 116b and the Gleitstütz vom 124a and 124b to the guide portions 112a and 112b of the guide carriage 110 such that the Gleit Operationss vom 126a and 126b without bias on the Gleitstützbericht 124a and 124b slide and, accordingly, the rolling elements 116a and 116b roll off vortemposabi on the WälzConsequentlymaschinennenbahnen 132a and 132b.
  • the advantage of the inventive combination of sliding guides 120a, 120b and rolling element guides 130a, 130b for guiding the guide carriage 110 along the guide rail 54 is that the rolling element guides 130a or 130b, as shown in FIG. 5, open the possibility of the rolling elements 116 due to the Hertzian pressure in the overlay on the corresponding rolling element raceway 132 to deform elastically, so that there is the possibility of elastically biasing the WälzSystem entryen 130 a and 130 b in a direction parallel to the respective Wälz Operationssstützkraft WSa, WSb direction perpendicular to the Wälzoasalaufbahnen 132 , so that even without load application of the guide carriage 110, the WälzConsequently entryen 130 with a WälzEffspannkraft WV, which runs parallel to the Wälz stressesstützkraft WS, are acted upon.
  • the guide sections 112a and 112b of the guide carriage 110 In order to apply the rolling body preload forces WVa and WVb, the guide sections 112a and 112b of the guide carriage 110 must in turn be supported on the sliding guides 120a and 120b, respectively, so that a sliding guide preload force GVa or GVb is applied to the rolling body preload force WVa or WVb as reaction force to the rolling body preloading force WVa and WVb Sliding guides 120 acts, this sliding guide biasing force GVa or GVb in the same direction as the respective Gleitstütz originally GSa and GSb act and arise from the WälzEffspann- forces WVa and WVb, when a force separation according to parallel and perpendicular to the guide plane of symmetry 128 components takes place and is taken into account that the perpendicular to the plane of symmetry plane 128 cancel components as in
  • the rolling body biasing forces WVa, WVb for example, a deformation of the rolling elements, 116a, 116b so that they differ in a range between 6 pm and more and 20 pm and less from the actual geometry of the rolling elements 116.
  • the sliding support surfaces 124a, 124b are made of cast iron and the guide rail 54 is made of hardened steel, a surface pressure of up to 2.5 N / mm 2 can be realized.
  • this extent amounts to more than 20% of a width B of the foot support surface 64 of the guide rail 54.
  • the sliding support surfaces 124a, 124b likewise extend over the entire length of the guide carriage 110 in the longitudinal direction 52 of the guide rail 54.
  • the Gleitstütz vom 124a and 124b and the Gleitauflage crab 126a and 126b are guided relative to each other by a lubricating film 140a and 140b, said lubricating film 140a, 140b preferably as a hydrodynamic lubricating film, which is due to the movement of the guide carriage 110 relative to the guide rail 54 forms.
  • the lubricating film has a thickness in the range of 2 pm to 6 m.
  • inserts 142a and 142b are inserted into the guide portions 112a, 112b for forming the slide pads 126a and 126b, so that the material for forming the slide pads 126a, 126b is independent of the material of the carriage 110 and, in particular, irrespective of the material of the guide portions 112a , 112b can be chosen.
  • the sliding contact surfaces 126a and 126b can be realized by materials such as bronze, plastic or ceramic, so that with a suitable choice of the guide rail 54 even the most varied sliding mating for the sliding materials can be selected.
  • the second embodiment is formed in the same manner as the first embodiment, so that the description of the individual elements can be fully incorporated by reference to the comments on the first embodiment.
  • the guide contour 84a and the guide portion 112a are formed to form the slide guides 120'a and 120'b, with the side surfaces 94a and 96a having their respective portions forming the slide support surfaces 124a and 124b and the guide portion 112a in turn forms the sliding abutment surfaces 126'a and 126'b which slidably abut against the sliding support surfaces 124'a and 124'b.
  • the Gleitstütz vom 124'a and 124'b and the Gleitauflage crab 126'a and 126'b run symmetrically to the guide plane of symmetry 128 ', which does not coincide in this embodiment in the longitudinal center plane 82 of the guide rail 54, but perpendicular to this. Further, symmetrically to the guide plane of symmetry 128 'in the guide portion 112b, the rolling elements 116'a and 116'b are arranged in corresponding WälzSystem effectn 118'a and 118'b, which in turn on the side surfaces 94b and 96b to form the corresponding Wälzoasalaufbahnen 132a and 132b support.
  • the main load direction HLR ' is parallel to the guide plane of symmetry 128', and in the guide plane of symmetry 128 'is also the total slide support force GGS' resulting from the slide support forces GS'a and .gamma. Taken up by the slide guides 120'a and 120'b GS'b composed.
  • the WälzSystem enclosureen 130'a, 130b formed by the in the WälzArchitectingn 118'a, 118'b recorded rolling elements 116'a, 116'b to the WälzConsequentlybahnen 132'a, 132'b bias in the same way as described in connection with the first embodiment, so that a biasing force on the sliding guides 120'a and 120'b acts in the same manner, as described in connection with the first embodiment.
  • the guide contours 84" a, 84 "b of the guide rail 54" are formed as projections, wherein the guide contour 84 "a the V-shaped sliding support surfaces 124" a and 124 “b bears, these sliding support surfaces 124 "a and 124" b are symmetrical to the guide plane of symmetry 128 and thus with sliding guide surfaces 126 "a and 126" b of the guide section 112 "a slide guides 120" a and 120 “b formed symmetrically to the guide plane of symmetry 128" are arranged.
  • Wälz moments 116 "a and 116" b are effective, which also have, for example, balls as rolling elements 116 “a and 116" b, which in Wälz stressesn 118 "a and 118" b and roll on rolling element raceways 132 "a and 132" b formed by the guide contour 84 "b of the guide rail 54".
  • the main load direction HLR is in the guide symmetry plane 128 "and the resulting total slip support force GGS" is also in the guide symmetry plane 128, while a resulting total roll support force GWS "is also in the guide symmetry plane 128", but opposite to the resulting one
  • a single slide 120 "' is formed by a portion of the upper rail 86 and a portion of a lower slide surface 88 facing the upper rail surface 86.
  • the lower guide carriage surface forms the slide support surface 124 "and the upper rail surface 86 forms the slide support surface 126" 'of the slide guide 120 "'.
  • the upper rail surface 86 may extend over the entire width of the guide rail 54 in the same manner as the lower guide carriage surface 88, it is possible to provide the sliding guide 120 '' with a high load capacity. Since the sliding support surface 124 "'and the sliding support surface 126"' extend perpendicular to the main load direction, no forces acting transversely to the guide plane of symmetry 128 also occur when the sliding guide 120 "'is loaded in the main load direction HLR.
  • the rolling elements 116a and 116b are arranged in the same manner as in the first embodiment and form the rolling element guides 130a and 130b in the same manner as described in connection with, for example, the first embodiment, so that in this regard to the comments on the first embodiment can be fully incorporated by reference.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Bearings For Parts Moving Linearly (AREA)

Abstract

L'invention concerne un dispositif de guidage linéaire destiné à des machines-outils, comprenant un rail de guidage qui s'étend dans une direction longitudinale et présente dans la direction longitudinale une forme de section transversale constante, ainsi qu'au moins un chariot de guidage qui est guidé contre le rail de guidage et englobe le rail de guidage dans des zones partielles de sa forme de section transversale. L'invention a pour objet d'apporter des améliorations à ce dispositif de guidage linéaire de sorte que celui-ci d'une part assure un guidage précis du chariot de guidage par rapport au rail de guidage et d'autre part présente une rigidité élevée et une atténuation élevée des vibrations. A cet effet : le chariot de guidage est guidé contre le rail de guidage par au moins une glissière qui présente au moins une surface d'appui coulissant en contact avec le rail de guidage, contre laquelle appuie une surface de contact coulissant du chariot de guidage ; le chariot de guidage est guidé contre le rail de guidage par au moins un élément de guidage à corps roulants qui présente au moins un chemin de roulement disposé contre le rail de guidage et un agencement de corps roulants, disposé contre le chariot de guidage, dont les corps roulants peuvent rouler le long du chemin de roulement du rail de guidage ; et la ou les glissières et le ou les éléments de guidage à corps roulants sont disposés et conçus de sorte qu'ils absorbent les forces d'appui qui agissent sur le chariot de guidage et perpendiculairement à la direction longitudinale du rail de guidage, tout en étant orientées différemment entre elles.
EP13796083.7A 2012-12-07 2013-11-28 Dispositif de guidage linéaire pour machines-outils Withdrawn EP2929196A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012111943.0A DE102012111943A1 (de) 2012-12-07 2012-12-07 Linearführung für Werkzeugmaschinen
PCT/EP2013/074949 WO2014086653A2 (fr) 2012-12-07 2013-11-28 Dispositif de guidage linéaire pour machines-outils

Publications (1)

Publication Number Publication Date
EP2929196A2 true EP2929196A2 (fr) 2015-10-14

Family

ID=49674317

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13796083.7A Withdrawn EP2929196A2 (fr) 2012-12-07 2013-11-28 Dispositif de guidage linéaire pour machines-outils

Country Status (3)

Country Link
EP (1) EP2929196A2 (fr)
DE (1) DE102012111943A1 (fr)
WO (1) WO2014086653A2 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014014789B4 (de) * 2014-10-10 2017-10-05 Eccon Gmbh Gleitwagen mit einem elastischen Element
GB2555141A (en) 2016-10-21 2018-04-25 Accuride Int Ltd A sliding support assembly
DE202018003002U1 (de) * 2018-06-27 2020-03-31 Schneeberger Holding Ag Linearbewegungsführung

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE7333605U (fr) * 1900-01-01 Wotan-Werke Gmbh, 4000 Duesseldorf
FR1142912A (fr) * 1954-01-07 1957-09-24 Vyzk Ustav Obrabecich Stroju Palier fluide pour guidages
DE3435593A1 (de) * 1984-09-28 1986-04-03 Joachim Dipl Ing Klement Maschinenelement, als komplette in sich geschlossene kombinierte waelz- und gleitfuehrung als geradfuehrung
DE3531813C1 (de) * 1985-09-06 1986-11-20 Honsberg Gmbh Geb Schlittenfuehrungssystem
JPH0251619A (ja) * 1988-08-16 1990-02-21 T Echi K Kk 直線摺動用ベアリング
JPH0560129A (ja) * 1991-08-23 1993-03-09 Nippon Thompson Co Ltd 防振性を有する直動案内摺動ユニツト
AU4585397A (en) * 1996-09-30 1998-04-24 Surface Technologies Ltd. Bearing having micropores, and design method thereof

Non-Patent Citations (1)

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Title
See references of WO2014086653A2 *

Also Published As

Publication number Publication date
WO2014086653A2 (fr) 2014-06-12
DE102012111943A1 (de) 2014-06-12
WO2014086653A3 (fr) 2014-07-31

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