EP3120034A2 - Arrangement de palier pour plateau circulaire - Google Patents

Arrangement de palier pour plateau circulaire

Info

Publication number
EP3120034A2
EP3120034A2 EP15715677.9A EP15715677A EP3120034A2 EP 3120034 A2 EP3120034 A2 EP 3120034A2 EP 15715677 A EP15715677 A EP 15715677A EP 3120034 A2 EP3120034 A2 EP 3120034A2
Authority
EP
European Patent Office
Prior art keywords
rotary table
ring
outer ring
table bearing
inner ring
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
EP15715677.9A
Other languages
German (de)
English (en)
Inventor
Jörg-Oliver Hestermann
Günter Schmid
Jürgen Hilbinger
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.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Schaeffler Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Publication of EP3120034A2 publication Critical patent/EP3120034A2/fr
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
    • F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
    • F16C27/04—Ball or roller bearings, e.g. with resilient rolling bodies
    • 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
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/38—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers
    • 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
    • B23Q1/40—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 ball, roller or wheel arrangements
    • 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
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/38—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers
    • F16C19/381—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with at least one row for radial load in combination with at least one row for axial load
    • 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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • 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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/583—Details of specific parts of races
    • F16C33/586—Details of specific parts of races outside the space between the races, e.g. end faces or bore of inner ring
    • 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
    • B23Q2220/00—Machine tool components
    • B23Q2220/004—Rotary tables
    • 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
    • F16C2300/00—Application independent of particular apparatuses
    • F16C2300/10—Application independent of particular apparatuses related to size
    • F16C2300/14—Large applications, e.g. bearings having an inner diameter exceeding 500 mm
    • 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 build up 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
    • F16C2322/00—Apparatus used in shaping articles
    • F16C2322/50—Hand tools, workshop equipment or manipulators

Definitions

  • the invention relates to a rotary table bearing arrangement, comprising a rotary table bearing with an inner ring, an outer ring and arranged in one or more rows rolling elements, which roll on the inner and outer ring, and in each case an arrangement component with a Aufspannabites, with which the outer ring and the inner ring are connected.
  • This machine usually comprises a rotary table, which is rotatably mounted on a corresponding rotary table bearing arrangement. While until now the rotary table bearing arrangement were designed only for pivoting tasks or slow continuous turning, it is necessary in view of the expansion of the scope of work, the bearing assembly designed so that even high speeds can be driven over a longer period.
  • the rotary table bearing is usually designed as a compact bearing, as a drive torque motor is used.
  • the rotary table bearing is designed as a rolling bearing, with different designs can be used, tailored to the stress of the bearing.
  • the performance of the bearing is determined by the effective preload in the rolling contact, which is a few micrometers depending on the bearing diameter. Depending on the friction in the rolling contact arise at high speeds Frictional losses in the form of heat, which is released on the inner and outer ring.
  • the torque motor used must have a limiting speed, which is usually achieved only via the field weakening operation, in order to still have sufficient torque for milling in the lower speed range.
  • a limiting speed which is usually achieved only via the field weakening operation, in order to still have sufficient torque for milling in the lower speed range.
  • At high speeds of the rotor and the current drive frequencies are high, which in turn leads to high Ummagnetleitersfrequenzen. This, in turn, leads to increased heat generation due to the re-magnetization losses in the rotor, and the rotor becomes hot.
  • An active cooling of the rotor is possible due to the risk of leakage only with increased effort.
  • the rotor is connected to the shaft, which is connected to the inner ring and is rotatably mounted on the inner ring, and which carries the table. This results in a heat transfer from the rotor to the rotary table bearing.
  • the invention is thus based on the object of specifying a rotary table bearing arrangement which, despite given locally different heating, makes possible the at least partial reduction of the prestressing which increases from this.
  • a rotary table bearing arrangement of the type mentioned that the Aufspannab- section of at least one arrangement component is radially elastically formed on the assembly component, and / or that the outer ring and / or the inner ring have a radially elastic connecting portion, via which respective ring is connected to the locating component.
  • the rotary table bearing arrangement has a specifically provided elasticity, which allows an immanent radially-symmetrical softness is given by which it is possible to give the diameter growth elastic with a corresponding spring stiffness can. This means that a radially-symmetrical elasticity compensates for any diameter growth, so that there is no or only a reduced increase in the bearing preload.
  • the elastic clamping section which carries the outer ring, can be embodied as a circumferential, elastically formed ring via a circumferential annular groove on the arrangement component.
  • the Anschraub configuration for the outer ring has a cylindrical ring shape, which is designed so that it can yield elastically, reversibly when expanding the An effetkomponente and the increase in pressure in the rolling contact moderately fails.
  • This elastic ring geometry metric is z. B. formed on a pierced, circumferential annular groove on the assembly component.
  • this annular elastic Aufspannabitess determines its elastic properties, it should be chosen so that the theoretically detectable, thermally induced diameter expansion, coming from the inner ring, can compensate for this. Should the required ring thickness be very thin, since the desired yield of the elastic clamping section to be achieved must be high, it is possible to make the cross section of the ring section for increasing the compliance, for example S-shaped, as well as possible segmentation of the ring is. Segmentation and S-shaped cross-sectional designs can also be provided together.
  • the design of the elastic Aufspannabitess as a ring shape over the circumferential annular groove leads to a radial elasticity.
  • the rotary table bearing which is usually screwed to the mounting section via the outer ring, has sufficient rigidity due to the ring shape of the mounting surface. This means that the radial-symmetrical stiffness is low, but in the tangential and axial direction, the rigidity is still high and meets the requirements.
  • the outer ring can be made substantially L-shaped in cross-section, wherein on the radially inwardly projecting towards the inner ring legs run the rolling elements and the vertically extending leg forms the connecting portion. About this vertical leg of the outer ring is fixed to the mounting portion, usually screwed. This, compared with the length of the horizontal leg significantly longer running mounting legs is sufficiently narrow to provide the desired elasticity.
  • the fixation respectively screwing of the outer ring can either quasi from above through the entire elastic leg in the Clamping section into it.
  • the Aufspannabêt from the bottom accessible openings for receiving the connecting portion on the mounting portion fixing screws, which are screwed into threaded bores on the front side of the elastic see thigh.
  • leg thickness also be too low in this embodiment to achieve the target elasticity, it is also possible here to segment this leg so that it can be made wider, but nevertheless due to the segmentation the radially symmetrical elasticity lies in the desired range.
  • the slots vertically seen to the level of the bottom of the annular groove or to the inwardly projecting leg of the outer ring to lead, so that consequently, seen vertically, result in relatively long slotted segments.
  • the concrete slot arrangement or the pitch and slot depth, consequently the number of segments and segment height, is ultimately to be interpreted on the basis of the given requirements in order to realize the desired target elasticity required by the requirements.
  • the first two embodiments are characterized in that the elasticity is provided in the region of the outer ring connection to the attachment.
  • the elastic clamping section which carries the inner ring, a hollow cylindrical cross-section of a bearing via the rotary table bearing shaft is against the inner ring, against which the inner ring is radially clamped.
  • the inner ring is radially penetrated by the shaft, which is to be stored on him, interspersed, he is firmly on the shaft having the corresponding Aufspannabrough pressed.
  • the hollow-cylindrical shaft section, on which the inner ring is clamped is configured elastically relative to the table flange by means of a corresponding geometric configuration, that is to say that a small radially symmetrical elasticity is provided in this region. If there is a thermally induced change in geometry in the bearing area, so it comes to an elastic deflection in the region of the hollow cylindrical shaft portion due to the support on the outer ring, for example, is not even elastically mounted.
  • a thermally induced otherwise adjusting bias increase is reduced by the radially inner elasticity.
  • corresponding section segments by forming slots which, if appropriate, also extend only partially over the section length.
  • a radially inwardly extending annular collar may be provided on which in this case preferably also the rotor can be attached.
  • the rotary table bearing arrangement provides a defined introduced radially-symmetrical softness or elasticity, which can reduce thermally induced voltage peaks in the rolling contact.
  • the bearing can be nominally even more biased without significantly increasing the pressure, which maintains the backlash in the radial raceway system over a wider range of temperatures as the inner ring or outer ring heats up.
  • FIG. 1 is a schematic diagram of part of a rotary table machine with a rotary table bearing arrangement according to the invention
  • Figure 2 is an enlarged detail view of the rotary table bearing arrangement
  • FIG. 1 A first figure.
  • Figure 3 is a plan view of the elastic, designed as a cylindrical ring clamping section for the outer ring
  • Figure 4 shows an alternative embodiment of the Aufspannabitess with S-shaped cross-sectional profile
  • Figure 5 shows another embodiment of a rotary table bearing assembly according to the invention with L-shaped executed outer ring and optional elastic Aufspannabrough on the inner ring bearing assembly component in the form of a shaft.
  • FIG. 1 shows a section of a rotary table machine 1 according to the invention, comprising a table frame 2 with a frame component 3, which represents an arrangement component with a clamping section for an outer ring of a rotary table bearing, which will be described below. Furthermore, a shaft 4 is provided, which has a further arrangement component with a clamping section for the inner ring of the rotary table bearing, wherein this clamping section is realized via the hollow cylindrical section 5 of the shaft 4.
  • the shaft 4 has a table flange 6, on which not shown in detail the actual, is added to be rotated rotary table.
  • a torque motor 7 comprising a stator 8, which is fixed on the frame side, and a separate rotor 9 via an air gap, the extension of the hollow cylindrical portion 5 of Wave 4 is arranged.
  • Stator 8 and rotor 9 are separated in a known manner via an air gap, so that a free rotational mobility of the rotor 9 is given relative to the stator 8.
  • the structure and operation of such a torque motor is well known.
  • the rotary table bearing assembly further comprises the actual rotary table bearing 10, with an outer ring 1 1 and an inner ring 12.
  • the inner ring 12 is guided on the outer ring 1 1 over a total of three rows of rolling elements 13, 14, 15, wherein the Wälz redesignn 13 and 14 of the axial support and the row of rolling elements 15 serve the radial support.
  • the same physical effects also affect other types of bearings, such. B. double-row tapered roller bearings.
  • FIG. 2 shows an enlarged partial view of the area of the rotary table bearing 10.
  • a clamping section 16 is provided, which, as an example, has the plan view of FIG. 3, a plurality of threaded bores 17, into the corresponding one Fixing screws 18, which pass through the outer ring in corresponding openings 19 are screwed.
  • the clamping portion 16 is designed as a cylindrical ring which is defined by a circumferential annular groove 20. As a result of this over the annular groove 20 realized undercut the clamping section 16 is radially elastic, so it has a corresponding spring stiffness on speed, which allows him to respond to a possible thermally induced increase in diameter of the inner ring 12 yielding.
  • This radial-symmetrical softness or elastic compliance is at least partially compensated for an increase in the preload in the rolling contact, in particular in the region of the radial row of rolling elements 15, so that there is no undue stress increase which would result in an excessive bearing load.
  • the slots preferably extend over the entire height of the clamping section 16, that is, to the bottom of the annular groove 20. This reduces the tensile stress in the circumferential direction when the clamping section 16 expands and increases the respective elasticity, so that the clamping section 16 has a sufficient thickness can.
  • the rotary table bearing 10 can also be slightly biased slightly stronger, without significantly increasing the pressure. This ensures that at higher temperatures of the outer ring, which then also experiences a certain extent, the backlash in the radial track system is maintained over a wider temperature range.
  • FIG. 5 shows a further embodiment according to the invention of a rotary table bearing arrangement in which a corresponding rotary table bearing 10 is provided, comprising an outer ring 11, an inner ring 12 and the corresponding rows of rolling elements 13, 14, 15.
  • the outer ring 11 is in turn connected to a corresponding clamping section 16 of the arrangement component 3, that is, the table frame, screwed on corresponding fastening screws 18.
  • the outer ring 1 1 is designed for this purpose substantially L-shaped in cross section. It has a horizontal leg 24 on which the raceways for the rows of rolling elements 13, 14, 15 are formed. Furthermore, it has a vertical leg 25, which is significantly longer than the horizontal leg 24, so that the outer ring 1 1, compared with the embodiment according to Figures 2 and 4, seen vertically is significantly longer.
  • the vertical leg 25 is here completely penetrated by a corresponding opening 19 which is penetrated by the screw 18, which is screwed into a corresponding threaded bore 17 on the mounting section 16.
  • the cylindrical limb 25 is ultimately elastic due to its attachment section-side fixing, that is to say via which the corresponding resilience is compensated, which compensates for the compensation of any thermally induced diameter expansion in the region of the inner ring 12.
  • the radial-symmetrical elasticity is therefore also realized in this embodiment on the outer ring side, as well as in the embodiment described above. While in the previously described embodiment the elasticity is realized via the annular clamping section 16, in the embodiment according to FIG. 5 the elasticity is realized via the annular configuration of the leg 25 of the outer ring 11.
  • the leg 25 can also have corresponding slots to increase its elasticity, so that it can be used to increase its elasticity. segmented at least in sections. The function of both embodiments is ultimately the same.
  • FIG. 1 a design option for a radially inner elasticity is shown in FIG. While, see Figure 1, in a realization of the elasticity in the region of the outer ring of the hollow cylindrical portion 5 of the shaft 4 is designed very solid, in the embodiment of Figure 4, the hollow cylindrical portion 5 of the shaft 4 is made very narrow, so that the shaft 4th The hollow cylindrical section 5 of the shaft 4 forms the clamping section 28 onto which the inner ring 12 is pressed, thus providing a certain elasticity of the narrow hollow cylindrical section 5 relative to the table flange 6 due to the one-piece connection to the table flange 6 An optionally required stiffening can be achieved via a radially inwardly extending annular collar 27, on which the rotor 9 can also be fastened.
  • the section 5 can be provided with vertically extending slots in order, for example, to make it sufficiently elastic over its height for a given stiffening via the annular collar 27.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)
  • Support Of The Bearing (AREA)
  • Mounting Of Bearings Or Others (AREA)

Abstract

L'invention concerne un arrangement de palier pour plateau circulaire, comprenant un palier pour plateau circulaire muni d'une bague intérieure, d'une bague extérieure ainsi que de corps de roulement, disposés en une ou deux rangées, qui roulent sur les bagues intérieure et extérieure, ainsi qu'à chaque fois un composant d'arrangement muni d'une portion de serrage qui relie la bague extérieure et la bague extérieure. Selon l'invention, la portion de serrage (16, 28) d'au moins un composant de l'arrangement (3, 4) est formée avec une élasticité radiale sur le composant d'arrangement (3, 4), et/ou la bague extérieure (11) et/ou la bague intérieure (12) possèdent une portion de liaison (25) à élasticité radiale par le biais de laquelle la bague (11, 12) correspondante est reliée au composant d'arrangement (3, 4).
EP15715677.9A 2014-03-19 2015-03-13 Arrangement de palier pour plateau circulaire Ceased EP3120034A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014205097.9A DE102014205097A1 (de) 2014-03-19 2014-03-19 Rundtischlageranordnung
PCT/DE2015/200159 WO2015139702A2 (fr) 2014-03-19 2015-03-13 Arrangement de palier pour plateau circulaire

Publications (1)

Publication Number Publication Date
EP3120034A2 true EP3120034A2 (fr) 2017-01-25

Family

ID=52823985

Family Applications (1)

Application Number Title Priority Date Filing Date
EP15715677.9A Ceased EP3120034A2 (fr) 2014-03-19 2015-03-13 Arrangement de palier pour plateau circulaire

Country Status (7)

Country Link
US (1) US10125812B2 (fr)
EP (1) EP3120034A2 (fr)
JP (1) JP6570538B2 (fr)
KR (1) KR102349994B1 (fr)
CN (1) CN106104028B (fr)
DE (1) DE102014205097A1 (fr)
WO (1) WO2015139702A2 (fr)

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CN106312592A (zh) * 2016-11-16 2017-01-11 大连三垒机器股份有限公司 中空式转台
DE102016124843A1 (de) * 2016-12-19 2018-06-21 Taktomat Kurvengesteuerte Antriebssysteme Gmbh Drehvorrichtung
CN107269683B (zh) * 2017-06-15 2022-12-02 浙江长盛塑料轴承技术有限公司 一种耐磨转盘轴承
DE102018000322A1 (de) * 2018-01-17 2019-07-18 Detlef Görgens 5 Achs - Fräskopf
US20210231098A1 (en) 2018-04-30 2021-07-29 Vestas Wind Systems A/S A rotor for a wind turbine with a pitch bearing unit
US11009063B2 (en) 2018-12-12 2021-05-18 Roller Bearing Company Of America, Inc. Spherical plain bearing for dampers
DE102022117968A1 (de) 2022-07-19 2024-01-25 Schaeffler Technologies AG & Co. KG Rundtischlageranordnung
DE102022117969A1 (de) 2022-07-19 2024-01-25 Schaeffler Technologies AG & Co. KG Rundtischlageranordnung
DE102022117967A1 (de) 2022-07-19 2024-01-25 Schaeffler Technologies AG & Co. KG Rundtischlageranordnung

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Also Published As

Publication number Publication date
KR20160133444A (ko) 2016-11-22
WO2015139702A2 (fr) 2015-09-24
US10125812B2 (en) 2018-11-13
US20170108037A1 (en) 2017-04-20
JP6570538B2 (ja) 2019-09-04
JP2017508931A (ja) 2017-03-30
DE102014205097A1 (de) 2015-09-24
WO2015139702A3 (fr) 2015-11-12
CN106104028B (zh) 2019-09-17
KR102349994B1 (ko) 2022-01-11
CN106104028A (zh) 2016-11-09

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