CN104251260A - Eccentric ball bearing - Google Patents

Eccentric ball bearing Download PDF

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Publication number
CN104251260A
CN104251260A CN201410320312.0A CN201410320312A CN104251260A CN 104251260 A CN104251260 A CN 104251260A CN 201410320312 A CN201410320312 A CN 201410320312A CN 104251260 A CN104251260 A CN 104251260A
Authority
CN
China
Prior art keywords
inner ring
outer shroud
spheroid
diameter
bearing
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.)
Granted
Application number
CN201410320312.0A
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Chinese (zh)
Other versions
CN104251260B (en
Inventor
N·阿拉策
J·黑克尔
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch 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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of CN104251260A publication Critical patent/CN104251260A/en
Application granted granted Critical
Publication of CN104251260B publication Critical patent/CN104251260B/en
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
    • F16C23/10—Bearings, parts of which are eccentrically adjustable with respect to each other
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
    • F04B9/045—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms the means being 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
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/50—Other types of ball or roller 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
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/32—Balls
    • 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
    • F16C33/585—Details of specific parts of races of raceways, e.g. ribs to guide the rollers
    • 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
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
    • F16C19/163—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls with angular contact
    • F16C19/166—Four-point-contact ball 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
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • F16C2240/70—Diameters; Radii

Abstract

The invention relates to an eccentric ball bearing (1) used for an electro-hydraulic piston pump device of a vehicle brake system. The eccentric ball comprises an inner ring (2); an outer ring (3), which is eccentrically disposed on the inner ring (2) in an encircled manner; and ball bodies (5) having different orbit diameters, which are disposed between the inner ring (2) and the outer ring (3). The orbit of the inner ring (2) and/or the orbit of the outer ring (3) are/is provided with the ball bodies(5)having different orbit diameters, which are disposed between the inner ring (2) and the outer ring (3).

Description

Eccentric sphere bearing
Technical field
The present invention relates to a kind of eccentric sphere bearing with the feature of claim 1 preamble.Eccentric sphere bearing according to the present invention especially arranges the electro-hydraulic reciprocating pump equipment for hydraulic brake system of motor vehicle.This pumping unit is used to produce hydraulic brake pressure, for the braking maneuver in the braking system and/or outer force braking system of anti-sliding control.
Background technique
Patent application document DE 10 2,010 028 598 A1 disclose there is axle, the capacity eccentric bearing of roller in the bearer ring that surrounds axle prejudicially and the gap being positioned between axle and bearer ring.Bearer ring also can be described as outer shroud.Roller has different diameters according to the different gap width between axle and the bearer ring being eccentric in axle.If the axle of known capacity eccentric bearing be driven in rotation and bearer ring keep non-rotatable, then roller rolls on axle and in bearer ring and around rotate axle move.At this, bearer ring moves on circular track, because bearer ring and axial compression are opened by the roller with the around the movement of maximum diameter, and has the roller place bearer ring of minimum diameter near axle in relative side.
In reciprocating pump or reciprocating pump equipment, have one or more pump piston arranged relative to capacity eccentric bearing radial direction to abut on bearer ring outside with its end and driven by the bearer ring moved on circular track move reciprocatingly.Such as to be pressed onto from outside by pump piston with spring and to be close to bearer ring, this bearer ring is the outer shroud of capacity eccentric bearing.For in the electro-hydraulic reciprocating pump equipment of hydraulic brake system of motor vehicle, the rotary motion of capacity eccentric bearing transmission device on motor by the rotary motion of motor or Flange joint is converted to the to-and-fro motion for driven pump piston.
Summary of the invention
The eccentric sphere bearing with claim 1 feature according to the present invention has inner ring, surrounds the outer shroud of inner ring and the spheroid as rolling element prejudicially, and described spheroid is arranged in the gap between inner ring and outer shroud.Spheroid can homogeneously or heterogeneously be distributed in circumferentially.Because outer shroud is relative to the bias of inner ring, the change of the gap width in the gap between inner ring and outer shroud, this gap has the narrowest position and most width position, and it widens most width position from the narrowest position along two circumferencial directions always.Spheroid has different diameters according to the different gap width between inner ring and outer shroud.The diameter of spheroid with each spheroid circumferential location, the gap width in gap between inner ring and outer shroud is equally large.
Rotated relative to outer shroud if driven according to the inner ring of eccentric sphere bearing of the present invention, so spheroid rolls and moves, as known from ball bearing around inner ring in inner ring and in outer shroud.Eccentric sphere bearing according to the present invention is rolling bearing.When spheroid around the movement, outer shroud and inner ring press off by the spheroid with maximum diameter, and in the relative side that the spheroid with minimum diameter is positioned at, outer shroud is near inner ring.Can say, the gap width of change is around the inner ring motion be driven in rotation relative to outer shroud together with spheroid, that is, most broad gap width, other gap width of the smallest annular clearance width and each are moved around inner ring together with spheroid.Outer shroud moves around inner ring on a circular track.
According to the present invention, the inner ring of eccentric sphere bearing and/or outer shroud have the track of different race way diameter for having the spheroid of different-diameter.The spheroid with different-diameter rolls in inner ring and/or in outer shroud on the track with different race way diameter.Present invention achieves race way diameter to coordinate mutually with the different-diameter of the spheroid of eccentric sphere bearing.Make the skidding of spheroid in inner ring and in outer shroud namely slide thus to minimize.Skid superimposed with the rolling of spheroid in inner ring and in outer shroud, and be generally less desirable.It makes friction and wear increase.
Except the spheroid with different-diameter being provided with to the possibility of different race way diameter, another advantage being the design proposal of the ball bearing of the spheroid had as rolling element using eccentric sphere bearing construction according to the present invention be when track is flute profile in inner ring and in outer shroud to the axial lead of spheroid.Can be delivered to outer shroud from inner ring by axial force according to eccentric sphere bearing of the present invention, vice versa, and do not need axially locking inner ring and outer shroud.Track can be the groove with positive circular cross section, the circular cross-section of non-positive round, V-arrangement cross section or polygonal crosssection.The cross section of track also can have arc section or other segmental arc.This is enumerated is exemplary and nonexhaustive.
According to the structure that another advantage of eccentric sphere bearing of the present invention is the simple of it and low cost.The inner ring of commercial general ball bearing, outer shroud and ball, i.e. standard piece can be used.
Replace inner ring, eccentric sphere bearing according to the present invention can have axle, and axle also can be regarded as the inner ring in meaning of the present invention.
Eccentric sphere bearing according to the present invention especially arrange be applied in electro-hydraulic, for producing in the reciprocating pump equipment of braking force in hydraulic brake system of motor vehicle, the rotary motion of motor is converted to the to-and-fro motion for driven pump piston by it.But the present invention is not limited to this application, and is intended to eccentric sphere bearing itself.
In reciprocating pump or reciprocating pump equipment, cause the circular movement of its outer shroud according to the rotary motion of the inner ring of eccentric sphere bearing of the present invention, and be converted into the to-and-fro motion that one or more outside abuts in the pump piston of outer shroud outside.Under the hypothesis that outer shroud does not rotate together with inner ring, spheroid is with the half rotating speed around the movement of inner ring, and the speed that similarly outer shroud moves on circular track reduces by half.Eccentric sphere bearing according to the present invention has deceleration, and in the non-rotatable situation of outer shroud, the circular velocity of the bias of outer shroud reduces by half compared with the rotational speed of inner ring.The advantage had of slowing down is, rotating speed that can be higher drives, and this makes can use less and lighter motor when power is identical.
Except as radial ball bearing, eccentric sphere bearing according to the present invention also can be designed to angular contact ball bearing.This is enumerated is exemplary and nonexhaustive.
The content of dependent claims is expedients scheme and the improvement project of the invention provided in claim 1.
Accompanying drawing explanation
Below with reference to the accompanying drawings shown in embodiment elaborate the present invention.In accompanying drawing:
Fig. 1 shows according to eccentric sphere bearing of the present invention with end elevation; And
Fig. 2 a to Fig. 2 c shows the ring viewgraph of cross-section of the different circumferential locations at Fig. 1 eccentric sphere bearing.
Embodiment
Eccentric sphere bearing 1 according to the present invention shown in accompanying drawing has the inner ring 2 in outer shroud 3, described outer shroud and inner ring 2 parallel to an axis and arrange prejudicially.Due to bias, the gap 4 between inner ring 2 and outer shroud 3 has the gap width circumferentially changed, and gap 4 spreads to the most width position at eccentric sphere bearing 1 opposite side from the narrowest position along two circumferential direction.Be provided with the spheroid 5 as rolling element in gap 4 between outer shroud 3 and inner ring 2, it has different diameters according to the gap width of change.The gap width of the circumferential location that the diameter of spheroid 5 is positioned at each spheroid 5 is equally large.
Inner ring 2 is pressed onto on the axle 6 of unshowned motor or the driving mechanism of Flange joint on motor, axle 6 can be made to rotate around its axis by described motor or driving mechanism, is also its spin axis while of its axis.
Eccentric sphere bearing 1 is rolling bearing, and under inner ring 2 is driven in rotation and outer shroud 3 is kept non-rotatable situation, spheroid 5 rolls and at this with the half rotating speed around the movement of inner ring 2 in inner ring 2 and in outer shroud 3.Maximal clearance width around the movement together with two spheroids 5 with maximum diameter in the gap 4 between outer shroud 3 and inner ring 2.Similarly, minimum gap width and the half rotating speed around the movement of spheroid 5 with inner ring 2 with minimum diameter in the gap 4 between outer shroud 3 and inner ring 2.In other words, outer shroud 3 moves around inner ring 2 when inner ring 2 is driven in rotation relative to the bias of inner ring 2, and wherein, if outer shroud 3 rotates not together, eccentric circular velocity is then that the half of the rotating speed of inner ring 2 is so large.Outer shroud 3 on circular track around the axis of inner ring 2, be simultaneously also its spin axis motion, wherein, the speed of the circular movement of outer shroud 3 is that the half of the rotating speed of inner ring 2 is so large, namely slows down.
As known from traditional ball bearing, eccentric sphere bearing 1 has the ball bearing retainer 7 keeping spheroid 5 in their distances each other.
The inner ring 2 of eccentric sphere bearing 1 and outer shroud 3 have the track 8 spheroid 5 with different-diameter to different race way diameter d1, d2, d3, D1, D2, D3.This fact of case is illustrated by Fig. 2 a to Fig. 2 c, it illustrates the cross section of inner ring 2 and outer shroud 3 and each spheroid 5 at the different circumferential location of eccentric sphere bearing 1.Can see a spheroid 5 between inner ring 2 and outer shroud 3 respectively, wherein, spheroid 5 in fig. 2 a has minimum diameter, and spheroid 5 in figure 2 c has maximum diameter and spheroid 5 in figure 2b has diameter between minimum diameter and maximum diameter.Inner ring 2 have on its excircle around groove, and outer shroud 3 within it circumferentially have around groove, they form track 8.Have the cross section of arc-shaped at bottom place groove, it forms the track 8 of the spheroid 5 for having minimum diameter.In the cross section of groove laterally, respectively relative to eccentric sphere bearing 1 radial center face specular ground and then the section of two circular arcs be used for that there is the second large diameter spheroid 5.It continues until have the spheroid 5 of maximum diameter.By this cross section for each spheroid 5 with a diameter, groove has the track 8 of different race way diameter d1, d2, d3, D1, D2, D3.For the spheroid 5 with another diameter, groove has the track 8 of another race way diameter d1, d2, d3, D1, D2, D3.In the cross section of groove, be provided with the arc section forming track 8, make that there is larger-diameter spheroid 5 and roll on larger race way diameter d1, d2, d3 in inner ring 2 and roll on less race way diameter D1, D2, D3 in outer shroud 3.The cross-section segments that the straight V-arrangement of groove is arranged also is feasible as track, and the spheroid 5 that described cross-section segments has different-diameter rolls (not shown) on different race way diameter.Inner ring 2 is coordinated with the spheroid 5 with different-diameter mutually with race way diameter d1, d2, d3, D1, D2, D3 of outer shroud 3.
By the track 8 of channel-shaped, inner ring 2 and outer shroud 3 are by axial force transmission on spheroid 5, and such eccentric sphere bearing 1 has the axial lead between inner ring 2 and outer shroud 3.
In outside, pump piston 10 abuts on outer shroud 3 with its end.Only illustrate that the pump piston 10 of its end is radially placed relative to eccentric sphere bearing 1 and pressed against outer shroud 3 from outside by unshowned piston spring in the accompanying drawings.Pump piston 10 can axially movably, namely can be accommodated in the pumping holes 11 of pump case 12 relative to eccentric sphere bearing 1 with moving radially.Eccentric sphere bearing 1 be arranged opposite to each other in the present embodiment, namely to fist formula arrange two pump pistons 10 between pump case 12 cylindrical eccentric room 13 in.By driving inner ring 2 to rotate, outer shroud 3 (not being rotates together with inner ring 2) with a half speed of the rotating speed of inner ring 2 on circular track around the axis of inner ring 2, while be also that its spin axis moves.The circular movement driven pump piston 10 of outer shroud 3 is reciprocating.Therefore the rotary motion of inner ring 2 is converted to the to-and-fro motion for driven pump piston 10 by eccentric sphere bearing 1.Pump case 12 is constituent elements of so-called hydraulic block, is also provided with other unshowned hydraulic structure element, as the solenoid valve of the anti-skidding control device for hydraulic brake system of motor vehicle except pump piston 10.This hydraulic block itself is known, is here no longer further explained.

Claims (3)

1. for rotary motion being converted to reciprocating eccentric sphere bearing, there is inner ring (2), spheroid (5) in there is the outer shroud (3) that surrounds described inner ring (2) prejudicially and there is the gap (4) that is arranged between described inner ring (2) and described outer shroud (3), described spheroid has different-diameter according to the different gap width in the gap (4) between described inner ring (2) and described outer shroud (3), and above and in described outer shroud (3) roll and around the movement in described inner ring (2) when described inner ring (2) relatively rotates relative to described outer shroud (3), it is characterized in that, described inner ring (2) and/or described outer shroud (3) have different race way diameter (d1, d2, d3, D1, D2, D3) track (8) is for having the spheroid (5) of different-diameter.
2. eccentric sphere bearing as claimed in claim 1, it is characterized in that, the force component of axis is delivered on spheroid (5) by described track (8).
3. eccentric sphere bearing as claimed in claim 1, is characterized in that, described eccentric sphere bearing (1) has the ball bearing retainer (7) keeping described spheroid (5) in their distances each other.
CN201410320312.0A 2013-06-25 2014-06-23 Eccentric ball bearing Expired - Fee Related CN104251260B (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013212043.5A DE102013212043B4 (en) 2013-06-25 2013-06-25 Eccentric ball bearings
DE102013212043.5 2013-06-25

Publications (2)

Publication Number Publication Date
CN104251260A true CN104251260A (en) 2014-12-31
CN104251260B CN104251260B (en) 2017-04-12

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Family Applications (1)

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CN201410320312.0A Expired - Fee Related CN104251260B (en) 2013-06-25 2014-06-23 Eccentric ball bearing

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DE (1) DE102013212043B4 (en)

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5111712A (en) * 1988-10-06 1992-05-12 Carrier Corporation Rolling element radial compliancy mechanism
JP2003322149A (en) * 2002-05-08 2003-11-14 Koyo Seiko Co Ltd Eccentric thrust bearing
DE102010028598A1 (en) * 2010-05-05 2011-11-10 Robert Bosch Gmbh eccentric

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010067586A1 (en) * 2008-12-09 2010-06-17 Ntn株式会社 Bearing device for wheel

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5111712A (en) * 1988-10-06 1992-05-12 Carrier Corporation Rolling element radial compliancy mechanism
JP2003322149A (en) * 2002-05-08 2003-11-14 Koyo Seiko Co Ltd Eccentric thrust bearing
DE102010028598A1 (en) * 2010-05-05 2011-11-10 Robert Bosch Gmbh eccentric

Also Published As

Publication number Publication date
CN104251260B (en) 2017-04-12
DE102013212043B4 (en) 2021-01-28
DE102013212043A1 (en) 2015-01-08

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Granted publication date: 20170412

Termination date: 20210623