WO2017183013A2 - Ensemble palier lisse de lubrifiant solide - Google Patents

Ensemble palier lisse de lubrifiant solide Download PDF

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Publication number
WO2017183013A2
WO2017183013A2 PCT/IB2017/053504 IB2017053504W WO2017183013A2 WO 2017183013 A2 WO2017183013 A2 WO 2017183013A2 IB 2017053504 W IB2017053504 W IB 2017053504W WO 2017183013 A2 WO2017183013 A2 WO 2017183013A2
Authority
WO
WIPO (PCT)
Prior art keywords
sliding
solid lubricant
partner
partners
bearing arrangement
Prior art date
Application number
PCT/IB2017/053504
Other languages
German (de)
English (en)
Other versions
WO2017183013A3 (fr
Inventor
Michael Döring
Original Assignee
Revobotik Gmbh
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Revobotik Gmbh filed Critical Revobotik Gmbh
Publication of WO2017183013A2 publication Critical patent/WO2017183013A2/fr
Publication of WO2017183013A3 publication Critical patent/WO2017183013A3/fr

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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/10—Construction relative to lubrication
    • F16C33/1095—Construction relative to lubrication with solids as lubricant, e.g. dry coatings, powder
    • 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
    • F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
    • F16C23/02—Sliding-contact bearings
    • F16C23/04—Sliding-contact bearings self-adjusting
    • F16C23/043—Sliding-contact bearings self-adjusting with spherical surfaces, e.g. spherical plain bearings
    • F16C23/045—Sliding-contact bearings self-adjusting with spherical surfaces, e.g. spherical plain bearings for radial load mainly, e.g. radial spherical plain 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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/043—Sliding surface consisting mainly of ceramics, cermets or hard carbon, e.g. diamond like carbon [DLC]
    • 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
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6696—Special parts or details in view of lubrication with solids as lubricant, e.g. dry coatings, powder
    • 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
    • F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
    • F16C23/02—Sliding-contact bearings
    • F16C23/04—Sliding-contact bearings self-adjusting
    • F16C23/043—Sliding-contact bearings self-adjusting with spherical surfaces, e.g. spherical plain bearings
    • F16C23/045—Sliding-contact bearings self-adjusting with spherical surfaces, e.g. spherical plain bearings for radial load mainly, e.g. radial spherical plain bearings
    • F16C23/046—Sliding-contact bearings self-adjusting with spherical surfaces, e.g. spherical plain bearings for radial load mainly, e.g. radial spherical plain bearings with split outer rings

Definitions

  • the invention relates to a slide bearing assembly for the storage of relatively moving components, which meets high demands on force load and rotational speed.
  • the solid lubricants used should be suitable for contact with food.
  • Ceramic bearing in combination with elastic material for damping of impacts and compensation of tolerances, ceramic bearing with embedded solid lubricant, bearing with ceramic coating.
  • spherical plain bearings are usually used in dry running. Usually, metallic balls are used which interact with a softer sliding partner, which usually consists of plastic. Spherical plain bearings are also known in robots which use ceramic balls, as it were in combination with plastics or other sliding partners having a significantly lower hardness (for example a material hardness of less than 900 HV).
  • the bearings used here have a low load capacity against forces and sliding speeds. But both are equally important for High-speed applications, as the joint loads increase with increasing robot speed, bearing forces generally square, sliding speeds usually linear. Also problematic in the prior art is the simultaneous fulfillment of requirements for suitability for contact and mixing with food. High load bearing materials are generally unsuitable for this purpose. Most plain bearings were designed for cylindrical operation. Again, mostly metallic waves and mostly softer sliding partners are used for dry running. This is especially true for the food contact applications. The plastic sliding bearings used have the disadvantage that the load capacity decreases with the sliding speed and thus can not be present at the same time high forces and high sliding speeds.
  • the sliding partner previously referred to as softer may consist of a combination of a solid state lubricant (e.g., PTFE) and an open cell material (e.g., metal, ceramic) or open-pore material (e.g., tissue).
  • a solid state lubricant e.g., PTFE
  • an open cell material e.g., metal, ceramic
  • open-pore material e.g., tissue
  • the object of the invention is to provide a sliding bearing assembly in which the above-mentioned disadvantages are at least partially eliminated.
  • a sliding bearing arrangement with at least two sliding partners, which are movable relative to one another having a solid lubricant element, wherein at least one of the sliding partners is movable relative to the solid lubricant element and wherein means are provided for the solid lubricant element against the at least one of the solid lubricant element to press movable sliding partner.
  • a solid lubrication is realized, in which a solid lubricant element is pressed onto the at least one moving sliding partner.
  • the sliding bearing arrangement can be carried out so maintenance-free, because it is permanently and evenly lubricated by the pressing of solid lubricant.
  • the sliding bearing assembly according to the invention can thus be operated in dry running, ie without lubrication with liquid or pasty substances.
  • the invention comprises the separate supply of a solid lubricant, which is supplied either directly to a sliding surface or in the interior of a sliding bearing assembly so that the sliding surface is wetted with the solid lubricant.
  • the solid lubricant element does not or does not contribute significantly to absorbing the operating load.
  • an external load acting on the slide bearing assembly is described that does not serve the internal function of the slide bearing assembly (the internal function is, for example, the cohesion of the bearing).
  • the material polytetrafluoroethylene (PTFE) is preferred because of its suitability for use in food processing and its good sliding properties.
  • Each sliding partner comprises a sliding surface which is designed to slide on a sliding surface of another sliding partner during operation.
  • the relative to each other and relative to the solid lubricant element movable sliding partner can be rotatably movable and / or be pivotally movable.
  • it may in particular be a rotary bearing arrangement or a pivot bearing arrangement.
  • a sliding partner may comprise a portion or a separate element that is not slidably configured. This may be, for example, a shaft or a shaft section on which the sliding surface is arranged.
  • the solid lubricant element is an element that provides lubricant in the form of abrasion caused by friction of the solid lubricant element on a surface.
  • the means may comprise: a feed device which is designed to receive the solid lubricant element, wherein the at least one sliding partner rotatable relative to the solid lubricant element is movable relative to the feed device.
  • the sliding partners can at least partially define a space in which the solid lubricant element is at least partially disposed and which is suitable for collecting solid lubricant abrasion.
  • the solid lubricant element can be arranged at least partially in one of the sliding partners and configured to deliver solid lubricant abrasion directly to a sliding surface of another sliding partner.
  • At least one of the sliding partners may be an outer sliding partner and be formed as an outer bearing ring.
  • the feed device can be rigidly connected to the outer sliding partner and / or to a bearing housing.
  • One of the sliding partners can be an inner sliding partner and have a spherical sliding element.
  • the inner sliding partner may have a shaft portion that is rotatable relative to the outer sliding partner.
  • the solid lubricant element is advantageously a food-compatible element, so does not affect the quality and compatibility of food.
  • One of the sliding partners can be designed geometrically deformable in order to avoid a radial strain of the sliding bearing assembly - with minimal operating clearance and at the same time maximum contact of the sliding surfaces to each other.
  • the sliding bearing arrangement may further comprise provisions for sealing the Gleitla- geranix against leakage of solid lubricant.
  • the sliding bearing arrangement can be designed to be used in a robot, in particular in a parallel kinematic system, in particular in delta robots.
  • Such robots find particular application in food processing.
  • At least one of the sliding partners may have a sliding surface which is provided with a surface structure which promotes the wetting with solid lubricant.
  • a structure comprises in particular in the bearing gap leading grooves.
  • the slide bearing assembly may comprise two pairs of sliding partners, each pair each having a sliding partner having a spherical sliding member, and wherein the pairs of sliding bearings are braced against each other.
  • a further development of the invention comprises a slide bearing arrangement in which at least one sliding partner, preferably all sliding partners, consist of ceramic materials or of other materials with a surface hardness of> 900 HV and which is operated in dry operation.
  • one of the sliding partners is designed geometrically deformable in order to avoid a radial strain that could lead to failure of the bearing.
  • this sliding partner may be the annular outer sliding partner.
  • the opening of the annular element is proposed.
  • the solid lubricant element may be made of a different material than the at least two sliding partners on their contact surface.
  • At least one sliding partner may consist of ceramic materials with a surface hardness greater than 900HV.
  • the slide bearing assembly may be suitable for use in forearms of delta robots, with two forearms each with two spherical bearings are clamped with tools. It is particularly advantageous if materials are selected for the sliding partners and the solid lubricant of the sliding bearing arrangement which are approved for use in the food, animal feed or pharmaceutical industries, ie are compatible with foods, feedstuffs and / or pharmaceuticals. Then, wetting or mixing with the product or product surface to be processed during operation of the slide bearing assembly can be tolerated.
  • the solid lubricant element contributes only insignificantly to absorb the operating load. This results from the fact that the solid lubricant element does not form a running surface of one or more sliding partners.
  • a sliding bearing arrangement which enables low-pollution and low-maintenance operation in dry running, can be carried out with low backlash, has a low coefficient of friction and at the same time high loads due to bearing forces and high sliding speeds can endure.
  • FIG. 5 shows a detail of the embodiment of FIG. 4,
  • Fig. 15 is a radial feed of the solid lubricant in the contact surface between the sliding partners.
  • the sliding preferably both, made of ceramic material or at least of other materials with a surface hardness greater than 900 HV.
  • the sliding partners are operated in dry running.
  • a solid lubricant element 8 or solid lubricant in particular PTFE is used, which is also considered food compatible.
  • the solid lubricant element 8 is thus an element which provides lubricant due to abrasion.
  • Fig. 1 shows a sliding bearing assembly according to the first embodiment of the invention for a cylindrical bearing assembly.
  • sliding partners 1; 2, 3 present, in each case as an outer sliding an outer bearing ring 1, which is fixedly mounted on the bearing housing 6, and as an inner sliding partner in each case a portion of the shaft 2.
  • the inner sliding partner 2 also includes a Section that is not sliding with respect to the outer sliding partner 1.
  • the solid lubricant element 8 is pressed by means 4 against the inner sliding partner, so the shaft 2.
  • the space 7, in which the solid lubricant element 8 is located at least partially, is defined by the sliding partners and by the bearing housing 6, which surrounds at least the sliding partners.
  • the means 4 comprise a feed device, which is arranged centrally with respect to the two outer bearing rings 1 and is rigidly connected to the bearing housing 6.
  • the means 4 are designed to exert a force Fz on the solid lubricant element 8, so that the solid lubricant element 8 is permanently pressed against the shaft 2. Due to the friction during the rotation of the shaft 2, abrasion is produced on the solid lubricant element 8, which collects in the space 7, wets the sliding surfaces of the sliding partners and thus ensures their permanent lubrication.
  • the means 4 may have a spring element, which acts in a radial direction relative to the sliding partner 2, that is to say the shaft 2 or its axis of rotation.
  • FIG. 2 shows a cylindrical sliding bearing arrangement according to the second embodiment of the invention.
  • This sliding bearing arrangement comprises two pairs of sliding partners 1, 3.
  • the sliding bearing arrangement acts with respect to that of FIG. 1 angle-compensating and is thus less susceptible to tension within the sliding bearing assembly.
  • the inner sliding partners here have spherical sliding elements 3, which are arranged on the shaft 2 at a predetermined axial distance from each other.
  • the means 4 are configured similarly to the first embodiment, but they are each arranged in the outer bearing rings 1 and give the lubricant directly to the sliding surface of the sliding part 3 from.
  • Fig. 3 shows a third embodiment of the invention, a spherical Gleitla- geranssen in which the inner sliding partner 3 is spherical and the outer sliding partner is formed by two bearing rings 1.
  • the inner sliding partner 3 is seated on the shaft 2.
  • the space 7 is bounded by the two bearing rings 1, the spherical inner sliding partner 3 and the bearing housing 6.
  • the solid lubricant element 8 is fed into the space 7 between the two bearing rings 1, directly on the sliding surface of the inner sliding partner 3.
  • the forces Fv and Fz act as previously described.
  • Fig. 4 shows as a fourth embodiment schematically a e.g. Sliding bearing arrangement used in delta robots for the lower arms (without forearm bracing and sketch of the lower arms, which are connected to the outer bearing mountings of bearing ring 1).
  • the arrangement shown in Fig. 3 with double inner sliding element is carried out with separate supply of each of a solid lubricant element 8 for each pair of sliding partners.
  • the solid lubricant element 8 is fed directly to the sliding surface of the inner Gleit- partners 3 in the space 7 between the bearing ring 1 and the bearing housing 6.
  • the forces Fv and Fz act in turn as previously described.
  • the slide bearing arrangement according to FIG. 4 has as a particularly preferred field of application robots, in particular parallel robots and in particular delta robots. These robots achieve high travel speeds and have a performance-critical point, in particular at the spherical joints. Especially at high speeds and in the ratio of large moving masses or resulting high joint forces due to a low load capacity of the bearings, the maximum achievable speed can not be achieved or is associated with premature wear of the bearings.
  • FIG. 5 shows by way of example a possibility for allowing a deformability of the annular sliding partner 1. As a result, a radial tension of the slide bearing assembly can be avoided, which could lead to failure of the bearing.
  • the left-hand illustration shows in simplified form the bearing arrangement of FIG.
  • the right-hand illustration shows the sectional view AA.
  • the outer sliding partner so here the bearing ring 1, separated at a point 5, so that it can deform geometrically during operation.
  • This point 5 can at the same time include or form the feed device 4.
  • the bearing ring 1 is installed so that a securing element is used to prevent rotation.
  • All embodiments may include provisions for sealing the slide bearing against leakage of solid lubricant to the outside of the slide bearing assembly.
  • At least one of the sliding partners may have a sliding surface which is provided with a surface structure which promotes wetting with solid lubricant, in particular grooves leading into the bearing gap.
  • one of the hard sliding partners 1, 2, 3 are designed so that it can accommodate mainly disturbing thermal deformations. Since the sliding partners preferably, but not exclusively, run against each other without play, compensation should be made elsewhere. This can have the consequence that prevails between the outer sliding partner 1 and the bearing housing 6 game or a frictional connection. Since turning the outer sliding partner (bearing ring) 1 relative to the bearing housing 6 in operation is not desirable (this would lead to unwanted abrasion and failure of storage), a rotation can be provided. This rotation can be introduced at the point 5 or at any other location. The rotation should be as simple as possible, since the storage is often used per robot application and not interfere with the disassembly of the storage.
  • Another preferred embodiment is the introduction of the securing element 9 in axial alignment between the outer sliding partner (bearing ring) 1 and the bearing housing, see.
  • a significantly larger contact area can be achieved with the same cross-sectional area of the securing element, since the securing element can be executed over the entire width of the bearing.
  • this anti-twist device 9 is embodied by an additional form element on the outer sliding partner (bearing ring) 1, which overlaps the bearing housing 6 in such a form-fitting manner that no rotation can take place between the outer sliding partner (bearing ring) 1 and the bearing housing 6.
  • This feature has the advantage that no additional component must be provided, the bearing is removable and, as in FIG. 7, there is a large contact surface between the outer sliding partner (bearing ring) 1 and the bearing housing 6. If the shape of the outer sliding partner (bearing ring) 1 should be kept as simple as possible, which is particularly interesting in a realization of ceramic, the reverse expression using a shaped element of the bearing housing 6 can be provided as anti-rotation 9. This is shown in FIG. 9.
  • outer sliding partner (bearing ring) 1 should be interchangeable and the thermal expansion of the sliding is not included between outer sliding partner (bearing ring) 1 and inner sliding partner (bearing ball) 3 when heated, can, preferably between the outer sliding (bearing ring) 1 and the Bearing housing 6, a compensation of these deformations are added.
  • the requirements can be as follows:
  • a clearance between the outer sliding partner (bearing ring) 1 and the bearing housing 6 is selected such that at a given heating no distortion of storage, ie between outer sliding (bearing ring) 1 and inner sliding (bearing ball) 3 may arise. Consequently, a game is provided, but this can be disturbing in robot operation and due to the changing load directions in robot operation can lead to micro-movements between outer sliding (bearing ring) 1 and bearing housing 6. This can adversely affect the fit between the outer sliding partner (bearing ring) 1 and bearing housing 6 by wear and even wear foreign abrasion in the storage, which can lead to failure of storage.
  • one or more elastic members 12 between outer sliding partner (bearing ring) 1 and bearing housing 6 are proposed to prevent this.
  • one or more rings made of a soft elastically deformable material are proposed (eg rubber, silicone, PTFE), the Insertion of the outer sliding partner (bearing ring) 1 are deformed and cause a tension of the game between outer sliding partner (bearing ring) 1 and bearing housing 6.
  • This can be done for example by an inserted in the bearing housing 6 circumferential groove 13, in which an O-ring is used.
  • this elastic ring could also be achieved by, for example, metallic materials (possibly also carbon) are used.
  • this ring can also consist of deformable partial elements which are positioned on the circumference.
  • harder materials eg metallic material, carbon materials
  • the shape must be adapted to the stiffness requirement.
  • Fig. 11 is exemplified for a spherical bearing means of a disc or annular element of solid lubricant 7, which has at least in its outer regions in contact with the inner or outer sliding and is fixed in the bearing housing 6, the lubrication produced. Since there is no relative movement between the outer sliding partner (bearing ring) 1 and the bearing housing 6, such will be present between the element 8 and the inner sliding partner and lead to abrasion of solid lubricant. This abrasion should be performed for the appropriate lubrication in the sliding contact between the two hard sliding partners 1 and 3.
  • a pivoting movement is present in such a way that particles of solid lubricant on the ball are taken along solely by this pivoting movement and are carried in the sliding contact between the outer sliding partner (bearing ring) 1 and the inner sliding partner (bearing ball) 3.
  • the feed is selected from a solid lubricant with very good lubricating properties.
  • a solid lubricant with very good lubricating properties for example, PTFE can be used or corresponding other solid lubricants.
  • a solid-state lubricant with a creeping, ie, material that is not significantly elastic over the exposure time of a load high lubricant entry into the contact surface between the outer sliding partner (bearing ring) 1 and the inner sliding partner (bearing ball) 3 can be realized even with small pivoting angles become.
  • the solid lubricant element 8 has an outer diameter, which is only slightly smaller than the smallest inner diameter of the inner sliding partner (bearing ring) 3, compared with the outer sliding partner 3.
  • a chamfer which causes an inner space 11 in which, on the one hand, lubricant collects, but is pressed in by the tapering gap and the established lubricant pressure.
  • the load due to lubricant pressure on the Sealing between the outer sliding partner (bearing ring) 1 and the solid lubricant element 8 is reduced, which improves the function of the seal.
  • a higher pressure can be built up following, which improves the function of the lubricant supply.
  • annular solid lubricant element 8 is laterally axially pressed against the outer sliding partner (bearing ring) 1 that a lubricant pressure in the contact surface of the sliding is achieved by the plastic deformation of the solid lubricant element 8 and the abrasion due to the relative movement to the inner sliding partner.
  • a molding element is provided which guides the deforming solid lubricant element and its abrasion into the contact zone.
  • FIG. 14 Another possibility of feeding solid lubricant into the contact surface between the sliding partners is shown in FIG. 14.
  • a mold element 14 At the outer sliding partner 1 is a mold element 14 in such a way that a portion of the contact surface of the sliding on the inner sliding partner 2 is accessible.
  • a solid lubricant element 8 is pressed by means of a feed device 4 on the surface of the inner sliding partner 2 axially to the outer sliding partner 1 (and inner sliding partner 2).
  • the relative movement between the inner sliding partner 2 and the outer sliding partner 1 and a relative movement between the solid lubricant element 8 and the inner sliding partner 2 produces abrasion on the solid lubricant element, which is carried directly into the contact surface of the sliding partners. This especially if there is a significant rotational movement of the storage.
  • FIG. Yet another possibility of feeding solid lubricant into the contact surface between the sliding partners is shown in FIG.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Ceramic Engineering (AREA)
  • Sliding-Contact Bearings (AREA)
  • Bearings For Parts Moving Linearly (AREA)
  • Rolling Contact Bearings (AREA)
  • Support Of The Bearing (AREA)
  • Lubricants (AREA)

Abstract

Ensemble palier lisse comprenant au moins deux pièces complémentaires de glissement qui sont mutuellement mobiles, présentant un élément lubrifiant solide, au moins un des homologues complémentaires étant mobile par rapport à l'élément lubrifiant solide et des moyens étant prévus pour appuyer l'élément lubrifiant solide contre l'au moins un des homologues complémentaire de glissement mobiles par rapport à l'élément lubrifiant solide.
PCT/IB2017/053504 2016-04-22 2017-06-13 Ensemble palier lisse de lubrifiant solide WO2017183013A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016107542.6A DE102016107542A1 (de) 2016-04-22 2016-04-22 Gleitlageranordnung mit Festkörperschmierstoff
DE102016107542.6 2016-04-22

Publications (2)

Publication Number Publication Date
WO2017183013A2 true WO2017183013A2 (fr) 2017-10-26
WO2017183013A3 WO2017183013A3 (fr) 2017-12-14

Family

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Application Number Title Priority Date Filing Date
PCT/IB2017/053504 WO2017183013A2 (fr) 2016-04-22 2017-06-13 Ensemble palier lisse de lubrifiant solide

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DE (1) DE102016107542A1 (fr)
WO (1) WO2017183013A2 (fr)

Cited By (1)

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Publication number Priority date Publication date Assignee Title
CN112963445A (zh) * 2021-01-21 2021-06-15 南京工程学院 一种新型直线轴承

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FR3112712B1 (fr) * 2020-07-23 2022-08-05 Coron Jean Paul Articulation instrumentée pour bras robotisé

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GB759954A (en) * 1953-04-27 1956-10-24 British Oxygen Co Ltd Lubricating device
US3578828A (en) * 1969-02-18 1971-05-18 Kaman Aerospace Corp Split-race bearing construction
DE2701672C3 (de) * 1977-01-17 1980-08-14 Glacier Gmbh Deva Werke, 3570 Stadtallendorf Dichtanordnung für ein Gleitlager zum Tragen schwerer Lasten
JPS62136658U (fr) * 1986-02-21 1987-08-28
JPH053640U (ja) * 1991-07-03 1993-01-19 光洋精工株式会社 セラミツクス製球面すべり軸受
DE10032250A1 (de) * 2000-07-03 2002-01-24 Elringklinger Gmbh Lagerelement zum Abstützen eines Körpers
CN106870349A (zh) * 2012-03-27 2017-06-20 Ntn株式会社 复合滑动轴承、托架引导件、可变容量型轴向活塞泵

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112963445A (zh) * 2021-01-21 2021-06-15 南京工程学院 一种新型直线轴承
CN112963445B (zh) * 2021-01-21 2023-10-27 南京工程学院 一种直线轴承

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DE102016107542A1 (de) 2017-10-26
WO2017183013A3 (fr) 2017-12-14

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