WO2017157378A1 - Palier à roulement, entraînement à excentrique doté d'un tel palier à roulement et pompe à pistons radiaux et utilisation de celle-ci - Google Patents

Palier à roulement, entraînement à excentrique doté d'un tel palier à roulement et pompe à pistons radiaux et utilisation de celle-ci Download PDF

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Publication number
WO2017157378A1
WO2017157378A1 PCT/DE2017/100151 DE2017100151W WO2017157378A1 WO 2017157378 A1 WO2017157378 A1 WO 2017157378A1 DE 2017100151 W DE2017100151 W DE 2017100151W WO 2017157378 A1 WO2017157378 A1 WO 2017157378A1
Authority
WO
WIPO (PCT)
Prior art keywords
outer sleeve
rolling
radial
shaft
rolling bearing
Prior art date
Application number
PCT/DE2017/100151
Other languages
German (de)
English (en)
Inventor
Steffen BREHM
Jürgen Klonus
Marcus Gerngross
Thomas Kandler
Richard Frisch
Christopher HALUF
Jan KRÄMER
Markus Baier
Andreas Kohl
Original Assignee
Schaeffler Technologies AG & 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 & Co. KG filed Critical Schaeffler Technologies AG & Co. KG
Publication of WO2017157378A1 publication Critical patent/WO2017157378A1/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
    • 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
    • F16C19/44—Needle bearings
    • F16C19/46—Needle bearings with one row or needles
    • F16C19/466—Needle bearings with one row or needles comprising needle rollers and an outer ring, i.e. subunit without inner ring
    • 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
    • F16C21/00—Combinations of sliding-contact bearings with ball or roller bearings, for exclusively rotary movement
    • F16C21/005—Combinations of sliding-contact bearings with ball or roller bearings, for exclusively rotary movement the external zone of a bearing with rolling members, e.g. needles, being cup-shaped, with or without a separate thrust-bearing disc or ring, e.g. for universal joints
    • 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
    • F16C3/00—Shafts; Axles; Cranks; Eccentrics
    • F16C3/04—Crankshafts, eccentric-shafts; Cranks, eccentrics
    • F16C3/18—Eccentric-shafts
    • 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
    • F16C3/00—Shafts; Axles; Cranks; Eccentrics
    • F16C3/04—Crankshafts, eccentric-shafts; Cranks, eccentrics
    • F16C3/22—Cranks; Eccentrics
    • 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
    • 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
    • F16C33/588—Races of sheet metal
    • 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
    • F16C39/00—Relieving load on bearings
    • F16C39/02—Relieving load on bearings using mechanical means
    • 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
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • F16C2240/50—Crowning, e.g. crowning height or crowning radius

Definitions

  • the invention relates to a roller bearing, which has at least one outer sleeve with an outer lateral surface and a running surface facing away from the outer lateral surface, and with a number of received in the outer sleeve rolling elements, which are arranged in contact with the tread, wherein the outer sleeve has a first end and a second end.
  • the invention further relates to an eccentric drive, in particular for a radial piston pump, comprising a shaft rotatable about its longitudinal axis and a radial rolling bearing arranged on the shaft, the radial rolling bearing comprising at least one outer sleeve facing away from the shaft and a number of rolling elements accommodated in the outer sleeve, wherein the radial roller bearing is arranged either eccentrically to the longitudinal axis of the shaft on the shaft or is arranged on an eccentric ring which is rotatably connected to the shaft.
  • the invention relates to a radial piston pump comprising at least one pump piston and such an eccentric drive, as well as their use.
  • WO 2008/1 19596 A2 discloses a radial roller bearing with an outer sleeve in the form of a sleeve for an eccentric drive, which is used in particular in radial piston pumps.
  • the radial rolling bearing is arranged eccentrically to the longitudinal axis of a pump shaft on the pump shaft.
  • the object is with regard to the rolling bearing, which has at least one outer sleeve with an outer lateral surface and a running surface facing away from the outer lateral surface, and with a number of received in the outer sleeve rolling elements, which are arranged in contact with the tread, wherein the outer sleeve has a first end and has a second end, achieved in that the lateral surface of the outer sleeve is formed convex such that an outer diameter of the outer sleeve starting from the first end of the outer sleeve at least from the beginning of the tread steadily increases up to a maximum outer diameter and starting from the maximum outer diameter in the direction of the second end at least until the end of the tread steadily decreases.
  • a "start" and an “end” of the tread-seen in longitudinal section through the outer sleeve and the rolling elements- is understood to mean a limit of the tread assigned to the first end or the second end of the outer sleeve.
  • a sloping course i. a steady decrease of the outer diameter in the direction of the first end as well as the second end, present. It is essential, however, that the outer circumferential surface in the region of the first end and the second end, i. in areas which are arranged in the sectional view next to or offset from the tread, has no outer diameter which is greater than the maximum outer diameter D.
  • the inner circumferential surface of the outer sleeve may, in addition to the invention, for example, from the first end to the second end, at least in the region of the raceway of the rolling elements, constant inner diameter. If crowned rolling elements, in particular convex needles, are provided, then the inner circumferential surface, at least in the region of the raceway of the rolling elements, can likewise be adapted to the crowning of the needles or follow the profile of the convex shape of the outer lateral surface, so that the wall thickness is constant ,
  • the outer sleeve of the rolling bearing is formed in particular by pulling.
  • the convex or spherical shape of the outer surface of the outer sleeve is achieved by already known manufacturing technologies, here a deep drawing and crimping of the outer sleeve.
  • a stamp is inserted into the outer sleeve and this formed accordingly.
  • the outer sleeve of the rolling bearing can obtain its shape by a swaging process or by a cutting process.
  • the wall thickness differences are to be understood in the sectional view of the bearing as in the radial direction different distances of the inner and outer lateral surfaces (-Iinie) to the axis of rotation.
  • the lateral surface of the outer sleeve at least in the region of the running surface (9 " ), has a course which corresponds to a parabola of the formula
  • the maximum outer diameter of the outer sleeve extends in particular on a circumferential line of the outer sleeve, which is arranged concentrically to a virtual line which extends through the centers of gravity of the rolling elements.
  • a rolling bearing cage for receiving the rolling elements is also available. This can be designed as a plastic cage or metal cage. But full complement variants of the rolling bearing are possible.
  • the rolling elements of the rolling bearing are preferably formed like a needle, so that a needle bearing is formed.
  • other embodiments of the rolling bearing according to the invention comprising for example spherical, conical or cylindrical rolling elements instead of needle-shaped rolling elements are possible.
  • Variants of the rolling bearing having at least one inner ring which is arranged between the shaft or a shaft portion on the one hand and the rolling elements on the other hand or between the eccentric ring on the one hand and the rolling elements on the other hand, are considered to be inventive. It has proven useful if at the first end and / or the second end of the outer sleeve, a board is formed, which points in the direction of the rolling elements. For this purpose, the end of the outer sleeve is angled at approximately 90 ° and forms a leading edge for rolling elements or Wälz stressesmaschinefig. Such a board limits the path that the rolling elements, if appropriate also a cage, can travel between the first end and the second end of the outer sleeve.
  • a board is formed which faces in the direction of the rolling elements, and that the outer sleeve is formed as a sleeve, wherein the outer sleeve at its, the board opposite end a can bottom is closed.
  • Such variants allow a particularly good sealing of the rolling bearing against
  • the object is for the eccentric drive comprising a shaft rotatable about its longitudinal axis and a radial rolling bearing arranged on the shaft, the radial rolling bearing comprising at least one outer sleeve facing away from the shaft and a number of rolling elements received in the outer sleeve, the radial rolling bearing being either eccentric to the longitudinal axis the wave is arranged on the shaft or on an eccentric ring is arranged, which is rotatably connected to the shaft, achieved in that a rolling bearing according to the invention is provided as a radial rolling bearing.
  • the object is achieved for the radial piston pump characterized in that it comprises an eccentric drive according to the invention and at least one pump piston, wherein the at least one pump piston has a contact surface which is in point contact with the maximum outer diameter of the outer sleeve of the radial roller bearing.
  • the contact surface of the pump piston can be flat or spherical.
  • the radial piston pump according to the invention is improved in terms of their susceptibility to axial thrust. Along with this occurs a reduction in wear and an increase in the life. This is achieved essentially by the convex shape of the lateral surface of the outer sleeve of the radial roller bearing.
  • the eccentric drive transforms a rotational movement of the shaft into a radial lifting movement of the pump pistons which are in contact with the outer lateral surface of the outer sleeve of the roller bearing or radial roller bearing.
  • the point contact between pump piston and outer sleeve does not permit any resulting forces in the axial direction and therefore leads to a purely radial lifting movement of the pump pistons.
  • a load distribution on the rolling elements is ideally pronounced in a point contact according to the invention, while it comes in the previously occurring two-point contact in conjunction with axial thrust to an inhomogeneous load distribution, which leads to increased Axialverschl adopted and tilted barrel.
  • the outer sleeve is formed sufficiently dimensionally stable so that the outer circumferential surface is not deformed during operation of the radial piston pump and in turn leads to a deterioration of the wear behavior.
  • Case steel has proven to be the material for the outer sleeve.
  • the outer sleeve is dimensionally stable with a wall thickness in the range of at least 1 mm to about 2.5 mm.
  • FIGS. 1 to 7 are intended to explain the state of the art and the invention in detail. So shows:
  • FIG. 1 shows a radial piston pump with a rolling bearing according to the prior art in the sectional view
  • FIG. 2 shows the radial piston pump according to FIG. 1 with ideal viewing in half section
  • FIG. 3 shows the radial piston pump according to FIG. 1 when viewed in real-time in half section
  • 4 shows a radial piston pump according to the invention in half section;
  • FIG. 5 shows an eccentric drive according to the invention with a rolling bearing according to the invention in a sectional view
  • FIG 6 shows the radial piston pump according to FIG 4 in an enlarged view in half section
  • FIG. 7 shows a further inventive radial piston pump in a sectional view.
  • the rolling bearing 4 includes an outer sleeve 9 having an outer lateral surface 9 'and one of the outer lateral surface 9' facing away from the tread 9. "It also is a number of captured in the outer sleeve 9 rolling elements 5, which in contact with the tread 9" are arranged, available.
  • the rolling elements 5 are guided by a roller bearing cage 6.
  • the outer sleeve 9 has a first end 10 with a shelf 9a and a second end 1 1 with a further shelf 9b. Within the further shelf 9b is located to fix the position of the rolling bearing cage 6, a disc. 8 In contact with the outer circumferential surface 9 'of the outer sleeve 9 pump piston 12, 13 are arranged, which execute a lifting movement of the shaft 2 about the longitudinal axis 3. In this case, further pump pistons, which are not visible in this view, with the outer circumferential surface 9 'of the outer sleeve 9 are in contact.
  • the eccentric ring 7 rotating with the shaft 2 or the shaft section 2a transforms the rotational movement of the shaft 2 into a radial lifting movement of the contact surfaces 12a, 13a of the pump pistons 12, 13 which are in contact with the outer jacket surface 9 ' .
  • FIG. 2 shows the known radial piston pump 1 according to FIG 1 with ideal viewing in half section.
  • an ideal cylindrical shape of the outer sleeve 9 and the outer circumferential surface 9 ' is assumed.
  • the contact surfaces 12a, 13a of the pump piston 12, 13 are in contact with the outer jacket surface 9 'of the outer sleeve 9, a line contact being formed for this ideal case.
  • FIG. 3 now shows the radial piston pump 1 according to FIG. 1 when viewed in real-time in half section. It is not assumed here of an ideal cylindrical shape of the outer sleeve 9 and the outer circumferential surface 9 ' . Due to a production-related out-of-roundness, the outer sleeve 9 is generally not ideally cylindrical, but slightly incidental and concave. There arises in two places a contact between the respective pump piston 13 and the outer circumferential surface 9 'of the outer sleeve 9, which results in an axial positive guidance of the respective pump piston 12, 13 on the outer sleeve 9.
  • FIGS. 1 to 3 designate the same elements.
  • Tread the rolling bearing 4 ', the outer sleeve 9 with the outer lateral surface 9' and one of the outer lateral surface 9 'facing away 9 "on.
  • needle-shaped rolling elements 5 is provided in contact with the tread 9" are arranged and guided by a roller bearing cage 6.
  • the outer sleeve 9 has a first end 10 and a second end 1 1, wherein at the first end 10 and the second end 1 1 of the outer sleeve 9 each have a shelf 9 a, 9 b is formed, which points in the direction of the rolling elements 5.
  • the lateral surface 9 'of the outer sleeve 9 is convex such that an outer diameter of the outer sleeve 9, starting from the first end 10 of the outer sleeve 9 steadily increases up to a maximum outer diameter D and starting from the maximum outer diameter D in the direction of the second end 1 1 decreases steadily , Conversely, it is of course also possible that an outer diameter of the outer sleeve 9, starting from the second end 1 1 of the outer sleeve 9 steadily increases up to a maximum outer diameter D and starting from the maximum outer diameter D in the direction of the first end 10 decreases steadily.
  • the steady increase in the outer diameter of the outer sleeve 9 up to the maximum outer diameter D can be relationship as the steady decrease of the outer diameter of the outer sleeve 9 only be "from the maximum outer diameter D in the region of the tread. 9 important here, however, that the outer lateral surface 9 'in the area of the first end 10 and the second end 1 1, ie in the areas which are arranged in the sectional view next to or offset from the tread 9 "has no outer diameter which is greater than the maximum outer diameter D. This ensures the desired point contact between outer sleeve 9 and pump piston 12, 13.
  • the maximum outer diameter D of the outer sleeve 9 extends here on a circumferential line of the outer sleeve 9, which is arranged concentrically to a virtual line which extends through the centers of gravity of the needle-shaped rolling elements 5.
  • a punctiform contact is formed between the pump piston 12, 13 or the contact surfaces 12a, 1 3a (see FIG. 1) and the outer lateral surface 9 ' .
  • the point contact allows no resulting forces in the axial direction and therefore leads to a purely radial lifting movement of the pump piston 12, 13. It applies here: Fres- Frad Qualitatively also the load distribution on the rolling elements 5 was drawn, which is ideally designed for such a point contact ,
  • FIG. 5 shows an eccentric drive 14 according to the invention with a rolling bearing 4 ' according to the invention in a sectional view.
  • the rolling bearing 4 ' used here corresponds to that used in FIG.
  • the same reference numerals as in FIG. 4 or FIG. 1 designate the same elements.
  • the convex shape of the outer sleeve 9 can be seen, wherein the maximum outer diameter D of the outer sleeve 9 is noted. Starting from the circumferential line of the outer sleeve 9, which is located at the maximum outer diameter D, the outer diameter of the outer sleeve 9 in the direction of the first end 10 and the second end 1 1 decreases steadily.
  • FIG. 6 shows the radial piston pump 1 ' according to FIG. 4 in an enlarged view in half section.
  • the same reference numerals as in FIG. 4 or FIG. 5 designate the same elements.
  • the contact surface 13a of the pump piston 13 can be seen.
  • NEN which is in point contact with the outer sleeve 9.
  • the outer sleeve 9 must be formed sufficiently stable deformation, so that the outer surface 9 ' is not deformed during operation of the radial piston pump 1 ' and in turn leads to a deterioration of the wear behavior.
  • FIG 7 shows a further radial piston pump 1 " according to the invention in the cross-sectional view
  • the same reference numerals designate the same elements as in FIG 6 or FIG 1.
  • a roller bearing 4 " according to the invention which has an outer sleeve 9 with an outer jacket surface 9 ' and one of the outer jacket surface 9 'facing away running surface che 9 "has. at the first end 10 of the outer sleeve 9, a board 9a is formed, pointing towards the rolling bodies.
  • the outer sleeve 9 is formed here as a sleeve, wherein the outer sleeve 9 at its the board 9a
  • the bush bottom 9c is braced against the shaft 2 or the shaft section 2a via a lug 9d
  • the rolling bearing 4 " is here directly on the shaft section 2a, which is eccentric to the longitudinal axis 3 of the shaft 2 is arranged.
  • the on-board 9a encloses a disc 8 which acts also as a seal and the roller bearing 4 "protects against loss of lubricant.
  • the lateral surface 9 'of the outer sleeve 9 is convexly formed such that an outer diameter of the outer sleeve 9 starting from the first end 10 of the outer sleeve 9 steadily increases up to a maximum outer diameter D and steadily decreases starting from the maximum outer diameter D in the direction of the second end 1 1.
  • the outer sleeve 9 must be designed sufficiently stable in deformation, so that the outer circumferential surface 9 ' does not deformed during operation of the radial piston pump 1 " and in turn leads to a deterioration of the wear behavior.
  • rolling bearing according to the invention comprising, for example, spherical, conical or cylindrical rolling bodies instead of needle-shaped rolling bodies are possible.
  • Variants of the rolling bearing according to the invention which have at least one inner ring which is arranged between the shaft 2 or the shaft portion 2a on the one hand and the rolling elements 5 on the other hand or between the eccentric ring 7 on the one hand and the rolling elements 5 on the other hand, can be used within the meaning of the present invention.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Ocean & Marine Engineering (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)

Abstract

L'invention concerne un palier à roulement (4', 4") qui comprend au moins une douille extérieure (9) dotée d'une surface d'enveloppe extérieure (9') et d'une surface de roulement (9'') opposée à la surface d'enveloppe extérieure (9'), et qui comprend un certain nombre de corps de roulement (5) logés dans la douille extérieure (9), lesquels sont disposés de manière à être en contact avec la surface de roulement (9''), la douille extérieure (9) comprenant une première extrémité (10) et une deuxième extrémité (11). La surface d'enveloppe extérieure (9') de la douille extérieure (9) est formée de manière convexe, de telle sorte qu'un diamètre extérieur de la douille extérieure (9) augmente de manière continue à partir de la première extrémité (10) de la douille extérieure (9) au moins à partir du début de la surface de roulement (9'') jusqu'à un diamètre extérieur maximal (D) et diminue de manière continue à partir du diamètre extérieur maximal (D) en direction de la deuxième extrémité (11) au moins jusqu'à l'extrémité de la surface de roulement (9'').
PCT/DE2017/100151 2016-03-17 2017-02-27 Palier à roulement, entraînement à excentrique doté d'un tel palier à roulement et pompe à pistons radiaux et utilisation de celle-ci WO2017157378A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016204458.3 2016-03-17
DE102016204458.3A DE102016204458B4 (de) 2016-03-17 2016-03-17 Wälzlager, Exzenterantrieb mit einem solchen Wälzlager sowie Radialkolbenpumpe und deren Verwendung

Publications (1)

Publication Number Publication Date
WO2017157378A1 true WO2017157378A1 (fr) 2017-09-21

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PCT/DE2017/100151 WO2017157378A1 (fr) 2016-03-17 2017-02-27 Palier à roulement, entraînement à excentrique doté d'un tel palier à roulement et pompe à pistons radiaux et utilisation de celle-ci

Country Status (2)

Country Link
DE (1) DE102016204458B4 (fr)
WO (1) WO2017157378A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018200063A1 (de) * 2018-01-04 2019-07-04 Robert Bosch Gmbh Vollrolliges Nadellager

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2263318A (en) * 1992-01-16 1993-07-21 Nsk Ltd Device for reciprocating a plunger or the like.
DE19839430A1 (de) 1998-08-29 2000-03-02 Schaeffler Waelzlager Ohg Radialkolbenpumpe
US20020110301A1 (en) 2001-02-09 2002-08-15 Ntn Corporation Shell type roller bearing assembly
WO2008119596A2 (fr) 2007-03-31 2008-10-09 Schaeffler Kg Palier à roulement radial pour commande à excentrique, commande à excentrique pour pompe à pistons radiaux, et système antiblocage présentant ladite commande à excentrique

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Publication number Priority date Publication date Assignee Title
DE1069434B (fr) 1900-01-01
US2659637A (en) 1950-06-14 1953-11-17 Roller Bearing Co Of America Roller bearing for compensating shaft misalignment
DE1675099U (de) 1954-03-03 1954-04-15 Karl Schauer Automat in faltschachtelform fuer schokoladetaefelchen.
DE1425932B2 (de) 1964-09-07 1972-10-12 Dürkoppwerke GmbH, 4800 Bielefeld Selbsteinstellendes waelzlager
GB1186221A (en) * 1967-01-31 1970-04-02 Torrington Co Improvements in and relating to Rolling Bearings.
DE4411979A1 (de) 1994-04-07 1995-10-12 Schaeffler Waelzlager Kg Stützrolle mit einer Stufenmantelfläche
JP4285157B2 (ja) * 2003-08-28 2009-06-24 株式会社ジェイテクト ステアリングコラム用軸受装置
DE102006015897A1 (de) 2005-12-10 2007-06-14 Continental Teves Ag & Co. Ohg Elektromotor-Pumpenaggregat mit verbessertem Getriebe
DE102007011051A1 (de) 2006-03-28 2007-10-04 Heidelberger Druckmaschinen Ag Anilox-Druckwerk
DE102006057483A1 (de) 2006-12-06 2008-06-12 Schaeffler Kg Oelgeschmierter Exzenterantrieb für eine Verdrängermaschine, insbesondere für eine Membranpumpe
JP5176438B2 (ja) * 2007-09-03 2013-04-03 日本精工株式会社 プランジャポンプ及びプランジャポンプ用ラジアルニードル軸受

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2263318A (en) * 1992-01-16 1993-07-21 Nsk Ltd Device for reciprocating a plunger or the like.
DE19839430A1 (de) 1998-08-29 2000-03-02 Schaeffler Waelzlager Ohg Radialkolbenpumpe
US20020110301A1 (en) 2001-02-09 2002-08-15 Ntn Corporation Shell type roller bearing assembly
WO2008119596A2 (fr) 2007-03-31 2008-10-09 Schaeffler Kg Palier à roulement radial pour commande à excentrique, commande à excentrique pour pompe à pistons radiaux, et système antiblocage présentant ladite commande à excentrique

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DE102016204458B4 (de) 2021-07-29

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