CA2033061A1 - Ball bearing transmission - Google Patents
Ball bearing transmissionInfo
- Publication number
- CA2033061A1 CA2033061A1 CA 2033061 CA2033061A CA2033061A1 CA 2033061 A1 CA2033061 A1 CA 2033061A1 CA 2033061 CA2033061 CA 2033061 CA 2033061 A CA2033061 A CA 2033061A CA 2033061 A1 CA2033061 A1 CA 2033061A1
- Authority
- CA
- Canada
- Prior art keywords
- balls
- transmission
- ball
- undulating
- ball 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.)
- Abandoned
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
- F16H—GEARING
- F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
- F16H25/04—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying rotary motion
- F16H25/06—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying rotary motion with intermediate members guided along tracks on both rotary members
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- 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
- F16H—GEARING
- F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
- F16H25/04—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying rotary motion
- F16H25/06—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying rotary motion with intermediate members guided along tracks on both rotary members
- F16H2025/063—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying rotary motion with intermediate members guided along tracks on both rotary members the intermediate members being balls engaging on opposite cam discs
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Transmission Devices (AREA)
- Friction Gearing (AREA)
- Retarders (AREA)
- Bearings For Parts Moving Linearly (AREA)
Abstract
2033061 9014532 PCTABS00002 Ball bearing transmission comprising an output part (3) lodged in a housing and an input part (1) on which is arranged a cam (1a) surrounded by a bearing (5) for the force-transmitting elements.
The balls (6) which transmit the force are maintained in non-positive contact with the bearing (5) by a freely rotating inertial race (7) and are also guided by guides located in the housing (2a) itself and in the output part (3). One of these guides consists of either radial guide grooves (10) or a continuous fluted groove and the other consists of a continuous fluted sliding channel (11); the number of flutes is different from the number of radial guide grooves (10) and from the number of flutes of the first flutes sliding channel, and the number of balls is equal to the number of radial grooves (10) and to the number of points of intersection of the two fluted sliding channels with the reference circle.
In a transmission in which the force-transmitting balls (6) are guided on one side in radial guide grooves (10), the ratio of the number of balls (6) and hence the number of radial guide grooves (10) to the number of flutes of the fluted sliding channel (11) is between n:(n-2) and n:(n+2), whereas in a transmission in which the force-transmitting balls (6) are guided on two sides in fluted sliding channels (11), the ratio of the number of balls (6) and hence the number of flutes in one fluted sliding channel to the number of flutes in the other fluted sliding channel (11) is at least equal to n:( +/- 2).
The balls (6) which transmit the force are maintained in non-positive contact with the bearing (5) by a freely rotating inertial race (7) and are also guided by guides located in the housing (2a) itself and in the output part (3). One of these guides consists of either radial guide grooves (10) or a continuous fluted groove and the other consists of a continuous fluted sliding channel (11); the number of flutes is different from the number of radial guide grooves (10) and from the number of flutes of the first flutes sliding channel, and the number of balls is equal to the number of radial grooves (10) and to the number of points of intersection of the two fluted sliding channels with the reference circle.
In a transmission in which the force-transmitting balls (6) are guided on one side in radial guide grooves (10), the ratio of the number of balls (6) and hence the number of radial guide grooves (10) to the number of flutes of the fluted sliding channel (11) is between n:(n-2) and n:(n+2), whereas in a transmission in which the force-transmitting balls (6) are guided on two sides in fluted sliding channels (11), the ratio of the number of balls (6) and hence the number of flutes in one fluted sliding channel to the number of flutes in the other fluted sliding channel (11) is at least equal to n:( +/- 2).
Description
i, 2033061 . . .
he present invention relates to a transmission of the type described in the preamble to patent claim 1.
In a known transmission of this kind (Cyclo Transmission) the eccentric is provided with a number of drivers, that work in conjunction with two rings that have peripheral teeth and which work in conjunction with a ring that has internal teeth in such way that the disks are constantly in engagement with the ring on one part of its circumference so that, because of the different number of teeth on the disks, on the onè hand, and on the ring, on the other, there will be a power or~path multiplication, respectively. ~lthough these known transmissions permit the transmission of great forces because their teeth resemble' undulations, they only permit a change of step-down or step-up ratios within relatively narrow limits, and for this reason are suitable mainly as reduction g~ars *or slowly-moving drive systems. In addition, they involve construction th~t is extramely costly, both from the point o~ view of design and with respect to material-technical c~sts, this being caused by the fact that in order to transmit force, the teeth have to be slid into en~agèment with each other. On tha one hand, this requires~
the use of extremely costly materials, and, on the other, requiras costly surface preparation for the worklng surfaces, in which connection it is impossible to avoid increased frictional losses because o~ this slidin~ function.
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apanese patent application 58-248324 describes a ball-bearing transmission in which the driving member, which is configured as a disk or a plate, is provided with an eccentric groove and the driven element, which is also configured as a disk or plate, incorporates an endless undulating groove in which the balls that transmit the force are guided Eas hemispheres--kalot~enartig--Tr.], a flange that is fixed to the housing being provided between the driving disk and the driven disk, said flange being provided with a number of radial slot guides~ In this type of transmission, regardless of its much simpler design configuration, essentially the same things apply as for the transmissions described heretofore, namely, because of the three-fold forced guidance of the balls in the two grooves and the slot guide, the balls are subjected to a high level of wear and the ball tracks wear very rapidly.
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, ' .', : Finally, EP-OS 207 206 describes a ball-bearing transmission with ::
a driving disk that is supported on an eccentric of the driving :
shaft by means oE a ball bearing, said driving disk being provided on both surfaces with guide grooves ~or balls which, in :
.
addition, roll in corresponding cou~ter guide grooves in the ~ ;
housing, on the one~:hand, and, on the other hand, in a driven : : disk.~ The functiona1 construction of this transmission corresponds to the Cyclo-transmission described in the :~ introduction hereto, the ball tracks of which, which work in~
~ conjunction with èach other, being:the epicycloids and the , . ~ j ~ . ~ . .
~ypocycloids of two (mathematical) ~inusoidal curves with different wave lengths (n:n-2~, the precise maintenance of which is d~cisive for the operation of the transmission. As in the case of the cyclo-transmission described in the introduction hereto, because of this close connection to the ~mathematical) cycloid shape of the ball tracks, the transmission is subjected to the same limitations as a gear~type transmission, in particular with regard to the dependence of the selectable reduction ratio condi~ions on one module--determined by the circumference of the cycloid pitch circle--with the result that selection of the reduction ratio is only possible in large, and in part broken, increments. ~ further disadvantage of the known transmission ~s caused by the cycloid form of the ball guide tracks which each cause the circulating balls to ~low down as they approach the tip of a cycloid and, having reached the tip of the cycloid, to accelerate once more into new curved parts that lie at an acute angle to the former dir~ction of movement. The irregularity of the path followed by the individual balls that is caused in this manner is smoothed out because of the effective of the other balls that are located in a constant curve area and for this reason is not perceptible at the output, but it exists regardless of this and aauses uneven running that confines the use of this transmission to slow-running drive systems.
It is thè task of the ~resent invention ~o create tra~smission ~hi~h, although of a simple design and which is subject to a very .. ... . . . . . ..
. . .
~ow level of wear, permiks the free selection of the step-down or step-up ratios within wide limits.
According to the present invention, this task has been solved by the ball baaring transmission described in claim 1.
In the ball bearing transmission according to the present invention, force is transmitted by means of balls, whereby, because of kh~ guidance of the balls in a freely rotatable ~earing ring (inertial ring), forced guidance in a direction which is transverse to the input and output side ball guide tracks, and which causes high frictional losses, is avoided. The transmission of force is thus effected ~nder frictlon which, for all practical purposes, is rolling friction, with only sli~ht oscillations about a centre plane and thus with only negligible friational losses. The ball bearing transmlssion according to the present invention can be manufactured so as to provide for any step-up or step-down ratios, and these can be selPcted freely and not as a function of a given modulus. Reductions smaller than 9:1 are possible, which cannot be achieved with the help of conventional gear-type transmissions. Commercially available balls can be used for transmission of the force and the guide tracks in the housing and in the output side can be produced ~y the most simple machining procedures. For this reason, pr~duc~ion cost.s are low~. ~Furthermor~, the.tran~mission makes it :
possible to tra~smit greater forces~becau e of the fact that all ~, ~ :: 5 : : ~
~` 2033061 ~ne balls that are used are simultaneously and constantly in power-transmitting engagement.
Additional embodiments and advantages are set out in the following description in which the present invention is explained in greater deta.il on the basis of the drawings appended hereto.
These drawings show the following:
Figure 1: a longitudinal ~ection through a ball bearing transmission according to the present invention;
Figure 2: a view of the transmission shown in figure 1, from the left;
Figure 3: a view of the interior of the input side housing wall o~ the transmission shown in figure 1;
Figure 4: a longitudinal section through the driving element of an embodiment of a multi-stage or multi-train transmission;
Figure 5: a view of the transmission ~hown in figure 4, from the right;
Figure 6: a longitudinal cross section through the driven element of the transmission shown in figures 4 and 5;
Figure 7: a longitudinal section through another embodiment of a ~ulti-stage or multi-train transmission;
Figure 8: a view from the `left into the transmission, which has been open by removal of the h~using top and the input drive sha ~t;
~: 6 :: : :
--Figure 9: a ball track groove combinati~Q ~ explanation of the associated calculations;
Fiqure 10 to figure 12: three additional examples of ball track groove combinations Figure 13: a cross section through a ball bearing transmi~sion with ball~supported force transmission balls;
Figure 14: a view of a section of the ball race in figure 8;
Figure 15: a cross section through a ball bearing transmission with an input and output force transmission balls that are separated and supported in a slide;
Figure 16: a partial croqs ~ection through a slide than can be . used in conjunction with the ball bearing ~ransmission as in figure 10~ this having individual ball-supported force transmission balls;
Figure 17: a cross section through a slide that can be used in ~onjunction with the ball bearing transmission as in figure 10, with the force transmi~sion balls being fiupported in pairs by ball bearings;
Figure 18: a view of a slide;
Figure 19: the ball race shown in figure 1~ as viewed from the side;
Figure 20: a view of another embodiment of a slide;
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igure 21: a view of the slide shown in figure 16, from the side;
Figure 22: a view of figure 16 from above;
Fi~ure 23: a view of a radial slot disk;
Figure ~4: a view of another embodiment of a ra~ial slot disk;
Figure 25: a cross section through a reduction gearing with ball bearings supported force transmission balls.
The single stage ball bearing transmission that is shown in figures 1 to 3 consists of a driven element 3 that is arranged in a housing 2a, 2b and a driving member 1 with an eccentric that is arranged on this and surrounded by a bearing 5 for the force-transmission elements. ~alls 6 that surround the bearing 5 in a ring are provided so as ~o transmit force, and these are held against the bearing 5 by a bearing ring 7 that is supported so as to be freely rotatable. In addition, the balls 6 are guided. on one side in ~ixed radial ball guide groove~ 10 that are formed in the housing 2 and, on the other side, in an undulating track lla, llb that is formed in the driven member 3. The number of balls, and correspondingly of radial guide grooves 10, being in the ratio between n:(n-2) and n:(n+2) to the number of undulations in the undulating track 11. The simplicity of the design of this transmission can be seen from the drawing, for commercially available parts can be used for the balls and ball bearings and the transmissio~ a a whol-e consi-sts- of simply shaped elements that do not require any 005tly machining. Thus, as is ~hown in ~. .
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_igure 3, the radial guide grooves can be produced in a suitably stepped cover element by simple milling or grinding, whereas the ball bearings 5 and the bearing ring 7, which are not involved in the transmission of force but are used to guide the balls 6, can be configured as simple flat rings, i.e., they do not re~uire a guide ~rack that con*orms to the curvature of the balls.
In a further development of the ball bearing transmission according to the present invention (see figures 4 to 6), several force transmission lines, each of which consists of a row of balls 6a, 6b and bearing ring 7a, 7b as well as corresponding radial ball guide grooves 10 and annular~ball guide tracks 11 that run annularly and are concentric to each other can be provided for special applications. For the case in which the concentric undulating ball guide tracks are arranged in a common driven element (not shown herein~, this involves a ~ingle-stage transmission that is suitable for transmitting correspondingly greaker forces, in which the individual force transmission lines are configured so as to be congruent, i.e., which must have the same number of undulations in the undulating ball guide tracks and an equal number of radial ball guide grooves in the two force transmission lines. Such a transmission can be used to transmit very great forces or can be used if structural requirements demand a particularly flat structure.
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r owever, in another embodiment of a transmission of this type, which incorporates ~everal force transmission lines, the concentric undulating ball guide tracks lla, llb (see figure 6) can be arranged in separate driven elements 3~, ~b, in which case the force transmission lines can also be configured differently, i.e., can have a different nu~ber o* undulations in the undulating ball guide tracks and a different number of radial ball guide grooves in the two force transmission lines for a correspondingly different number of balls. Such a transmission is a multi-stage transmission that can be configured as a transmission with fixed outputs or a~ a change-speed transmission, in which one output shaft ~an be connected by means of a clutch to one or the other driven member as desired, and the output drives that are not connected can idle.
A ~urther configuration o a ohange-speed transmission according to the present invention is shown in figure 7. In this transmission, the driven element 22 of the next~stage of the transmission is 6upported concentrically on the driven element 21 of the preceding stage of the transmission concentrically, such that its annular shoulder 24 that supports th~ undulating track 23 is opposite an annular shoulder 28 that i5 formed in ~he housing 25, 26, this annular shoulder 28 forming an annular gap 29 with the following driven element 22. The preceding driven~
12ment 21 is confi~ured as an e~centric 30 in the-~rea of the i annular ~ap 29 on which the bearing 3i for the balls 32 and the ; 2033061 `
nertial ring 33 which holds the ball 32 of thP followinglstage of the transmission which holds the ball 32 i~ arran~ed. Because of the resulting multiplication effect, this embodiment i5 particularly suited for manufacturing transmissions with very large step-up or ~tep-down ratios when, as a particular advantage, a power take-off is possible in each of the stages, as desired, so that the transmission can also be used as a change-speed transmission, in which connection, in order to produce a multi-stage or multi-train transmission in the manner described above additional driven elements can follow the last driven element in each instance.
Figure 7 also shows an additional, particularly advantageous embodiment of a transmission according to the present invention, such that in place of the radial ball guide grooves 27 that are used in the following force transmission line, an additional undulating track 37 is provided in the preceding force transmission line. For the first time, this creates a ball bearing transmission in which the balls are guided in two constant undulating tracks (i.e., which cause no sudden change in the direction of the balls and which are freely selectable, which is to say, independent o~ the ~mathematical) sinusoidal cycloid shape, In this way, the reduction xatio is freely selectable in whole and half steps, in which connection one can select a wave form that is flat~ i~P , is close to a ~ircular track, so that the balls run quieter or, which is advantageous for high-speed " ,- ~ .... ...
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" 2033061 rive ~ystems) the transmission of greater forces in slow-running transmissions, one can select a wave form with a greater amplitude. A further important advantage o~ the transmission according to the present invention, as compared to known ball bearing transmissions, in particular cyclo-transmissions, is the elimination of the guide flange, or the separate driving disk that i~s fixed in the housing, and thus a pair of curves, so that the transmission is also of a much simpler design.
In the case of such an embodiment with two interacting undulating tracks, it is advantageous ~see figure a) that the inertial rings 37 and 40 are provided with slot guides 38, 39 that enclose the balls and which hold the balls at a prescribed (mean~ distance ~rom each other without hindering the 61 ight oscillation of the ~alls about their working position (as is functionally caused), and which, in this manner, carry them in the desired and uniform direction of rotation.
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Single-stage transmissions can be provided with a radial groove guide or with double undulating groove guides, as desired. In the same way, multi-s~age or multi-train transmissions as shown in figures 4 or 7 can be provided with radial groove guides or with undulating groove guides in the housing in the individual stages, either unlformly or differently from ea~h other. I~f this em~odiment is used, in order to ensu~e trouble-free operation of the transmission all that has to ~e done is to maintain a ~ 12 ;~'' ' ~., ` ... '. ....
2033~61 ifference of at least (~/-) two undulations in the housing side undulating track compared to the drlven-side undulating track, whereas if the embodiment with radial groove guides is used it is preferred that a difference of one radial groove compared to the number of undulations in the dri~en side undulating track be provided, although a difference of two radial grooves compared to the ~umber of undulations in the undulating track can also be accommodated.
Figure 9 shows the interaction of the undulating tracXs and the computation of these, in which connection, in this embodiment, a ~ix-wave track interacts with a four-wave undulating track. In the drawing, the mean rolling circle is numbered 41, the six-wave undulating track is numbered 42, and the four-wave undulating track is numbered 43. When the six-wave undulating track ~2 is arranged in the housing and the four-wave undulating track 43 is arranged in the driven disk, this will result in a reduction of 1:~, and with the reverse arrangement, it will result in a reduction ratio of 1:3. The arrangement of the balls is effected at the points at which the two undulating tracks ~2, 43 and the rolling circle 41 ha~e a common point of intersection. In the ~quation that represents the basis for calculation of the fundamentals for computing the curve rx = the radial distance of a point on the undulating , I , :
track midline from the axis of xotation e = accentricity : , ' . . . . . . . ....
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Phix = the angle of curvature on the undulating track mldline Z1 - the number of waves in one undulating track Z2 = the ~mber o~ waves of the other undulating track or the number of radial grooves rs - the radial distance of the eccentric at the point set by rx Figures 10 to 12 show different examples for undulating track combinations based on using a seven-wave undulating track 44.
When this seven-wave undulating track is arranged on the driven side, this will result in a reduction of 1:3.5 regardIess of ~he number of waves on the housing side. In contrast to thisJ in the event that the seven-wave undulating track ls arranged in the housing in the ~ase of figure 10 (a five-wave track on the driven side) this will result in a reduction of 1:2.5; in the case of figure 11 (a four-wave track on the driven side) there will be a .
reduction ratio of 1:2; in the case of figure 12 (a three-wave track on the driven side) there will be a reduction of 1:1.5.~ ;
Thus this will result in a functional variability which will permit extensive standardization of the transmission elements `~ : :
~: : such that based on a few less standardized housings with varying numbers of waves it will be possible to produce a number of transmission types by using driven disks with undulating tracks having diff2.ent number~ of waves.
, . ~ ,, :
, ~ . : : , ~ 2033061 igures 13 to 25 show developments of the embodiment of a ball bearing transmission that is shown in figures 1 to 12, in which, unlike the transmissions used f~r transmitting force that have been described hereto~ore, separate sets of balls are used between the driving element and the fixed part (housing or radial slot disks) on the one hand, and between the driving element or the radial slot disk, respectively, and the driven element on the other, and which are supported on a ball race so as to be freely rotatable.
In thii~ sense, figures 13 and 14 show a transmisision that corresponds essentially to figure 1, in which the force is transmitted from the driving element 41 that is provided with the eccentric disk 61 through the fixed housing 44, to the driven element 51 by means of two sets of balls ~4, 65, which are supported so as to rotate freely on two rows of balls 66, 67 such that each of the balls 66, 67 that serve to transmit the force are supported on four balls of the two rows of balls 64, 65. In their turn, these supporting balls are each contained in an inertial ring 62, 63, of which, in parti.cular, the inner ring ~3 can be formed by a rolling bearing, in particular a needle roller bearing, instead of by a simple profile ring that has bearing tracks on both sides. This effQcti.vely eliminates any sliding fxiction between the force-transmitting elements of the transml~;siorl .
` : , :~ 15 , _n contrast to the embodiments shown in figures 1 to 14, in the embodiment shown in figures 15 to 25, in which corresponding parts bear the same reference numbers as in figures 13 and 14, the force is transmitted by means of an inertial ring 68 that acts axially through a ball bearing on the eccentric 61 in place of the radially acting inertial ring as in figure 14. For the remainder, the force is transmitted through~two sets of balls to the driven element 51, in which connection in ~his case of a transmission with an axially acting in~rtial ring the balls can each be arranged either i~dividually or by pairs in slides that are supported so as to be able to slide within radial slots of a guide disk that is ~ixed within the housing.
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In the case of ~igure 15, Which shows a simplified embodimen~ of the present invention, ~he balls 55,~56 which~tr~nsmits the force are supported directly and without ball supports in the slides s7 and the~lides within the radial slots 5~ of a disk 59 that is .
~fixed within the housing;~ variations of slides:with ball support systems are shown in:figures 16 to 22, and figures 23 and 24 show two :further embodiments of guide disks that are fixed withln the ~:
housing.
Thus:1 figure~l6 shows an embodiment of a slide 70, in:~which the ~
balls 71! 72 that transmit the force are~each supporjted by~a ~all race 73,:~4 that is ~pported in the baIl guidP~ ~rack:75i,~:w~e~eas~
in the~embodiment~6hown in;~figure~l7, the balls 76,~ 77 that~
.ransmits the force are supp~rted in pairs on a common ball race 78. In this, the ~upporting balls 78 are guided in a ball guide groove 79 tsee figures 18 and 19) of the slide 70 that is also provided with an external i~liding track 80 with which it overlaps the edges of the slot 58 of the disk 59 that is fixed in the housing (figure 15) in which it slides radially inwards or outwards, respectively, under the action of the force of the driving element 41, as a function of the eccentricity of the eccentric 61.
The slide 81 that is shown in figures 20 to 22 differs from that shown in figures 16 to 19 only in that here both the variants shown in ~igures 1~ and 17 have been combined into one slide.
Slides o~ this kind can be used to increase ~he transmission of force or to build multi-step transmissions as shown in figure 25.
Depending on the type of transmission, the slides can be used in conjunction with any guide disk, for example the guide disk 59 shown in figure lS, or also (see figure 23) the guide disk 85 that is provided with a total of eight radial slots 86 that extend from the outer edge in order to allow the slides to move and drillings 87 with which it is screwed to the housing. Figure 24 shows a corresponding view of an additional embodiment of a guide disk 88 with, in this case, ~our raidial slots 89 that ex~nd ~rom a cen~ral drillin~ and which are milled ~ simpli~y installation of the slides on the corners. However, i61ides can .~, : 17 : ' ... ... . ..
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lso be formed in two parts and the parts can then be screwed together after insertion into the radial slot.
Finally, figure 25 shows a ~ulti-step transmission that uses a dou~le isilide as shown in figures 20 to 22, in which connection the balls 91, 92, 93 that transmit the force are guided in the inertial ring 68, in the housing 44, and in the driven element 51 are each guided in grooves, whereas the balls 94 that circulate only on the surface of the inertial ring 68, i.e., not in the ball guide tracks, only have a supporting functio~. In this:
case, the guide disk 83 is supported ~y means of a ball bearing 84 so as to be rotatable, so that the guide disk 83 can follow th~ rotational motion that is governed by the balls 91, 9!2 that are guided in the undulating track.
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he present invention relates to a transmission of the type described in the preamble to patent claim 1.
In a known transmission of this kind (Cyclo Transmission) the eccentric is provided with a number of drivers, that work in conjunction with two rings that have peripheral teeth and which work in conjunction with a ring that has internal teeth in such way that the disks are constantly in engagement with the ring on one part of its circumference so that, because of the different number of teeth on the disks, on the onè hand, and on the ring, on the other, there will be a power or~path multiplication, respectively. ~lthough these known transmissions permit the transmission of great forces because their teeth resemble' undulations, they only permit a change of step-down or step-up ratios within relatively narrow limits, and for this reason are suitable mainly as reduction g~ars *or slowly-moving drive systems. In addition, they involve construction th~t is extramely costly, both from the point o~ view of design and with respect to material-technical c~sts, this being caused by the fact that in order to transmit force, the teeth have to be slid into en~agèment with each other. On tha one hand, this requires~
the use of extremely costly materials, and, on the other, requiras costly surface preparation for the worklng surfaces, in which connection it is impossible to avoid increased frictional losses because o~ this slidin~ function.
; ~ :
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:
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apanese patent application 58-248324 describes a ball-bearing transmission in which the driving member, which is configured as a disk or a plate, is provided with an eccentric groove and the driven element, which is also configured as a disk or plate, incorporates an endless undulating groove in which the balls that transmit the force are guided Eas hemispheres--kalot~enartig--Tr.], a flange that is fixed to the housing being provided between the driving disk and the driven disk, said flange being provided with a number of radial slot guides~ In this type of transmission, regardless of its much simpler design configuration, essentially the same things apply as for the transmissions described heretofore, namely, because of the three-fold forced guidance of the balls in the two grooves and the slot guide, the balls are subjected to a high level of wear and the ball tracks wear very rapidly.
.
, ' .', : Finally, EP-OS 207 206 describes a ball-bearing transmission with ::
a driving disk that is supported on an eccentric of the driving :
shaft by means oE a ball bearing, said driving disk being provided on both surfaces with guide grooves ~or balls which, in :
.
addition, roll in corresponding cou~ter guide grooves in the ~ ;
housing, on the one~:hand, and, on the other hand, in a driven : : disk.~ The functiona1 construction of this transmission corresponds to the Cyclo-transmission described in the :~ introduction hereto, the ball tracks of which, which work in~
~ conjunction with èach other, being:the epicycloids and the , . ~ j ~ . ~ . .
~ypocycloids of two (mathematical) ~inusoidal curves with different wave lengths (n:n-2~, the precise maintenance of which is d~cisive for the operation of the transmission. As in the case of the cyclo-transmission described in the introduction hereto, because of this close connection to the ~mathematical) cycloid shape of the ball tracks, the transmission is subjected to the same limitations as a gear~type transmission, in particular with regard to the dependence of the selectable reduction ratio condi~ions on one module--determined by the circumference of the cycloid pitch circle--with the result that selection of the reduction ratio is only possible in large, and in part broken, increments. ~ further disadvantage of the known transmission ~s caused by the cycloid form of the ball guide tracks which each cause the circulating balls to ~low down as they approach the tip of a cycloid and, having reached the tip of the cycloid, to accelerate once more into new curved parts that lie at an acute angle to the former dir~ction of movement. The irregularity of the path followed by the individual balls that is caused in this manner is smoothed out because of the effective of the other balls that are located in a constant curve area and for this reason is not perceptible at the output, but it exists regardless of this and aauses uneven running that confines the use of this transmission to slow-running drive systems.
It is thè task of the ~resent invention ~o create tra~smission ~hi~h, although of a simple design and which is subject to a very .. ... . . . . . ..
. . .
~ow level of wear, permiks the free selection of the step-down or step-up ratios within wide limits.
According to the present invention, this task has been solved by the ball baaring transmission described in claim 1.
In the ball bearing transmission according to the present invention, force is transmitted by means of balls, whereby, because of kh~ guidance of the balls in a freely rotatable ~earing ring (inertial ring), forced guidance in a direction which is transverse to the input and output side ball guide tracks, and which causes high frictional losses, is avoided. The transmission of force is thus effected ~nder frictlon which, for all practical purposes, is rolling friction, with only sli~ht oscillations about a centre plane and thus with only negligible friational losses. The ball bearing transmlssion according to the present invention can be manufactured so as to provide for any step-up or step-down ratios, and these can be selPcted freely and not as a function of a given modulus. Reductions smaller than 9:1 are possible, which cannot be achieved with the help of conventional gear-type transmissions. Commercially available balls can be used for transmission of the force and the guide tracks in the housing and in the output side can be produced ~y the most simple machining procedures. For this reason, pr~duc~ion cost.s are low~. ~Furthermor~, the.tran~mission makes it :
possible to tra~smit greater forces~becau e of the fact that all ~, ~ :: 5 : : ~
~` 2033061 ~ne balls that are used are simultaneously and constantly in power-transmitting engagement.
Additional embodiments and advantages are set out in the following description in which the present invention is explained in greater deta.il on the basis of the drawings appended hereto.
These drawings show the following:
Figure 1: a longitudinal ~ection through a ball bearing transmission according to the present invention;
Figure 2: a view of the transmission shown in figure 1, from the left;
Figure 3: a view of the interior of the input side housing wall o~ the transmission shown in figure 1;
Figure 4: a longitudinal section through the driving element of an embodiment of a multi-stage or multi-train transmission;
Figure 5: a view of the transmission ~hown in figure 4, from the right;
Figure 6: a longitudinal cross section through the driven element of the transmission shown in figures 4 and 5;
Figure 7: a longitudinal section through another embodiment of a ~ulti-stage or multi-train transmission;
Figure 8: a view from the `left into the transmission, which has been open by removal of the h~using top and the input drive sha ~t;
~: 6 :: : :
--Figure 9: a ball track groove combinati~Q ~ explanation of the associated calculations;
Fiqure 10 to figure 12: three additional examples of ball track groove combinations Figure 13: a cross section through a ball bearing transmi~sion with ball~supported force transmission balls;
Figure 14: a view of a section of the ball race in figure 8;
Figure 15: a cross section through a ball bearing transmission with an input and output force transmission balls that are separated and supported in a slide;
Figure 16: a partial croqs ~ection through a slide than can be . used in conjunction with the ball bearing ~ransmission as in figure 10~ this having individual ball-supported force transmission balls;
Figure 17: a cross section through a slide that can be used in ~onjunction with the ball bearing transmission as in figure 10, with the force transmi~sion balls being fiupported in pairs by ball bearings;
Figure 18: a view of a slide;
Figure 19: the ball race shown in figure 1~ as viewed from the side;
Figure 20: a view of another embodiment of a slide;
:
I ;`'l i i ~ ", I~
:
: 7 ' ' ~0~3061 - ~
igure 21: a view of the slide shown in figure 16, from the side;
Figure 22: a view of figure 16 from above;
Fi~ure 23: a view of a radial slot disk;
Figure ~4: a view of another embodiment of a ra~ial slot disk;
Figure 25: a cross section through a reduction gearing with ball bearings supported force transmission balls.
The single stage ball bearing transmission that is shown in figures 1 to 3 consists of a driven element 3 that is arranged in a housing 2a, 2b and a driving member 1 with an eccentric that is arranged on this and surrounded by a bearing 5 for the force-transmission elements. ~alls 6 that surround the bearing 5 in a ring are provided so as ~o transmit force, and these are held against the bearing 5 by a bearing ring 7 that is supported so as to be freely rotatable. In addition, the balls 6 are guided. on one side in ~ixed radial ball guide groove~ 10 that are formed in the housing 2 and, on the other side, in an undulating track lla, llb that is formed in the driven member 3. The number of balls, and correspondingly of radial guide grooves 10, being in the ratio between n:(n-2) and n:(n+2) to the number of undulations in the undulating track 11. The simplicity of the design of this transmission can be seen from the drawing, for commercially available parts can be used for the balls and ball bearings and the transmissio~ a a whol-e consi-sts- of simply shaped elements that do not require any 005tly machining. Thus, as is ~hown in ~. .
:
_igure 3, the radial guide grooves can be produced in a suitably stepped cover element by simple milling or grinding, whereas the ball bearings 5 and the bearing ring 7, which are not involved in the transmission of force but are used to guide the balls 6, can be configured as simple flat rings, i.e., they do not re~uire a guide ~rack that con*orms to the curvature of the balls.
In a further development of the ball bearing transmission according to the present invention (see figures 4 to 6), several force transmission lines, each of which consists of a row of balls 6a, 6b and bearing ring 7a, 7b as well as corresponding radial ball guide grooves 10 and annular~ball guide tracks 11 that run annularly and are concentric to each other can be provided for special applications. For the case in which the concentric undulating ball guide tracks are arranged in a common driven element (not shown herein~, this involves a ~ingle-stage transmission that is suitable for transmitting correspondingly greaker forces, in which the individual force transmission lines are configured so as to be congruent, i.e., which must have the same number of undulations in the undulating ball guide tracks and an equal number of radial ball guide grooves in the two force transmission lines. Such a transmission can be used to transmit very great forces or can be used if structural requirements demand a particularly flat structure.
.. , ............... . ~ . . . ;
~ .
r owever, in another embodiment of a transmission of this type, which incorporates ~everal force transmission lines, the concentric undulating ball guide tracks lla, llb (see figure 6) can be arranged in separate driven elements 3~, ~b, in which case the force transmission lines can also be configured differently, i.e., can have a different nu~ber o* undulations in the undulating ball guide tracks and a different number of radial ball guide grooves in the two force transmission lines for a correspondingly different number of balls. Such a transmission is a multi-stage transmission that can be configured as a transmission with fixed outputs or a~ a change-speed transmission, in which one output shaft ~an be connected by means of a clutch to one or the other driven member as desired, and the output drives that are not connected can idle.
A ~urther configuration o a ohange-speed transmission according to the present invention is shown in figure 7. In this transmission, the driven element 22 of the next~stage of the transmission is 6upported concentrically on the driven element 21 of the preceding stage of the transmission concentrically, such that its annular shoulder 24 that supports th~ undulating track 23 is opposite an annular shoulder 28 that i5 formed in ~he housing 25, 26, this annular shoulder 28 forming an annular gap 29 with the following driven element 22. The preceding driven~
12ment 21 is confi~ured as an e~centric 30 in the-~rea of the i annular ~ap 29 on which the bearing 3i for the balls 32 and the ; 2033061 `
nertial ring 33 which holds the ball 32 of thP followinglstage of the transmission which holds the ball 32 i~ arran~ed. Because of the resulting multiplication effect, this embodiment i5 particularly suited for manufacturing transmissions with very large step-up or ~tep-down ratios when, as a particular advantage, a power take-off is possible in each of the stages, as desired, so that the transmission can also be used as a change-speed transmission, in which connection, in order to produce a multi-stage or multi-train transmission in the manner described above additional driven elements can follow the last driven element in each instance.
Figure 7 also shows an additional, particularly advantageous embodiment of a transmission according to the present invention, such that in place of the radial ball guide grooves 27 that are used in the following force transmission line, an additional undulating track 37 is provided in the preceding force transmission line. For the first time, this creates a ball bearing transmission in which the balls are guided in two constant undulating tracks (i.e., which cause no sudden change in the direction of the balls and which are freely selectable, which is to say, independent o~ the ~mathematical) sinusoidal cycloid shape, In this way, the reduction xatio is freely selectable in whole and half steps, in which connection one can select a wave form that is flat~ i~P , is close to a ~ircular track, so that the balls run quieter or, which is advantageous for high-speed " ,- ~ .... ...
....
" 2033061 rive ~ystems) the transmission of greater forces in slow-running transmissions, one can select a wave form with a greater amplitude. A further important advantage o~ the transmission according to the present invention, as compared to known ball bearing transmissions, in particular cyclo-transmissions, is the elimination of the guide flange, or the separate driving disk that i~s fixed in the housing, and thus a pair of curves, so that the transmission is also of a much simpler design.
In the case of such an embodiment with two interacting undulating tracks, it is advantageous ~see figure a) that the inertial rings 37 and 40 are provided with slot guides 38, 39 that enclose the balls and which hold the balls at a prescribed (mean~ distance ~rom each other without hindering the 61 ight oscillation of the ~alls about their working position (as is functionally caused), and which, in this manner, carry them in the desired and uniform direction of rotation.
:
Single-stage transmissions can be provided with a radial groove guide or with double undulating groove guides, as desired. In the same way, multi-s~age or multi-train transmissions as shown in figures 4 or 7 can be provided with radial groove guides or with undulating groove guides in the housing in the individual stages, either unlformly or differently from ea~h other. I~f this em~odiment is used, in order to ensu~e trouble-free operation of the transmission all that has to ~e done is to maintain a ~ 12 ;~'' ' ~., ` ... '. ....
2033~61 ifference of at least (~/-) two undulations in the housing side undulating track compared to the drlven-side undulating track, whereas if the embodiment with radial groove guides is used it is preferred that a difference of one radial groove compared to the number of undulations in the dri~en side undulating track be provided, although a difference of two radial grooves compared to the ~umber of undulations in the undulating track can also be accommodated.
Figure 9 shows the interaction of the undulating tracXs and the computation of these, in which connection, in this embodiment, a ~ix-wave track interacts with a four-wave undulating track. In the drawing, the mean rolling circle is numbered 41, the six-wave undulating track is numbered 42, and the four-wave undulating track is numbered 43. When the six-wave undulating track ~2 is arranged in the housing and the four-wave undulating track 43 is arranged in the driven disk, this will result in a reduction of 1:~, and with the reverse arrangement, it will result in a reduction ratio of 1:3. The arrangement of the balls is effected at the points at which the two undulating tracks ~2, 43 and the rolling circle 41 ha~e a common point of intersection. In the ~quation that represents the basis for calculation of the fundamentals for computing the curve rx = the radial distance of a point on the undulating , I , :
track midline from the axis of xotation e = accentricity : , ' . . . . . . . ....
:;
.
Phix = the angle of curvature on the undulating track mldline Z1 - the number of waves in one undulating track Z2 = the ~mber o~ waves of the other undulating track or the number of radial grooves rs - the radial distance of the eccentric at the point set by rx Figures 10 to 12 show different examples for undulating track combinations based on using a seven-wave undulating track 44.
When this seven-wave undulating track is arranged on the driven side, this will result in a reduction of 1:3.5 regardIess of ~he number of waves on the housing side. In contrast to thisJ in the event that the seven-wave undulating track ls arranged in the housing in the ~ase of figure 10 (a five-wave track on the driven side) this will result in a reduction of 1:2.5; in the case of figure 11 (a four-wave track on the driven side) there will be a .
reduction ratio of 1:2; in the case of figure 12 (a three-wave track on the driven side) there will be a reduction of 1:1.5.~ ;
Thus this will result in a functional variability which will permit extensive standardization of the transmission elements `~ : :
~: : such that based on a few less standardized housings with varying numbers of waves it will be possible to produce a number of transmission types by using driven disks with undulating tracks having diff2.ent number~ of waves.
, . ~ ,, :
, ~ . : : , ~ 2033061 igures 13 to 25 show developments of the embodiment of a ball bearing transmission that is shown in figures 1 to 12, in which, unlike the transmissions used f~r transmitting force that have been described hereto~ore, separate sets of balls are used between the driving element and the fixed part (housing or radial slot disks) on the one hand, and between the driving element or the radial slot disk, respectively, and the driven element on the other, and which are supported on a ball race so as to be freely rotatable.
In thii~ sense, figures 13 and 14 show a transmisision that corresponds essentially to figure 1, in which the force is transmitted from the driving element 41 that is provided with the eccentric disk 61 through the fixed housing 44, to the driven element 51 by means of two sets of balls ~4, 65, which are supported so as to rotate freely on two rows of balls 66, 67 such that each of the balls 66, 67 that serve to transmit the force are supported on four balls of the two rows of balls 64, 65. In their turn, these supporting balls are each contained in an inertial ring 62, 63, of which, in parti.cular, the inner ring ~3 can be formed by a rolling bearing, in particular a needle roller bearing, instead of by a simple profile ring that has bearing tracks on both sides. This effQcti.vely eliminates any sliding fxiction between the force-transmitting elements of the transml~;siorl .
` : , :~ 15 , _n contrast to the embodiments shown in figures 1 to 14, in the embodiment shown in figures 15 to 25, in which corresponding parts bear the same reference numbers as in figures 13 and 14, the force is transmitted by means of an inertial ring 68 that acts axially through a ball bearing on the eccentric 61 in place of the radially acting inertial ring as in figure 14. For the remainder, the force is transmitted through~two sets of balls to the driven element 51, in which connection in ~his case of a transmission with an axially acting in~rtial ring the balls can each be arranged either i~dividually or by pairs in slides that are supported so as to be able to slide within radial slots of a guide disk that is ~ixed within the housing.
.
In the case of ~igure 15, Which shows a simplified embodimen~ of the present invention, ~he balls 55,~56 which~tr~nsmits the force are supported directly and without ball supports in the slides s7 and the~lides within the radial slots 5~ of a disk 59 that is .
~fixed within the housing;~ variations of slides:with ball support systems are shown in:figures 16 to 22, and figures 23 and 24 show two :further embodiments of guide disks that are fixed withln the ~:
housing.
Thus:1 figure~l6 shows an embodiment of a slide 70, in:~which the ~
balls 71! 72 that transmit the force are~each supporjted by~a ~all race 73,:~4 that is ~pported in the baIl guidP~ ~rack:75i,~:w~e~eas~
in the~embodiment~6hown in;~figure~l7, the balls 76,~ 77 that~
.ransmits the force are supp~rted in pairs on a common ball race 78. In this, the ~upporting balls 78 are guided in a ball guide groove 79 tsee figures 18 and 19) of the slide 70 that is also provided with an external i~liding track 80 with which it overlaps the edges of the slot 58 of the disk 59 that is fixed in the housing (figure 15) in which it slides radially inwards or outwards, respectively, under the action of the force of the driving element 41, as a function of the eccentricity of the eccentric 61.
The slide 81 that is shown in figures 20 to 22 differs from that shown in figures 16 to 19 only in that here both the variants shown in ~igures 1~ and 17 have been combined into one slide.
Slides o~ this kind can be used to increase ~he transmission of force or to build multi-step transmissions as shown in figure 25.
Depending on the type of transmission, the slides can be used in conjunction with any guide disk, for example the guide disk 59 shown in figure lS, or also (see figure 23) the guide disk 85 that is provided with a total of eight radial slots 86 that extend from the outer edge in order to allow the slides to move and drillings 87 with which it is screwed to the housing. Figure 24 shows a corresponding view of an additional embodiment of a guide disk 88 with, in this case, ~our raidial slots 89 that ex~nd ~rom a cen~ral drillin~ and which are milled ~ simpli~y installation of the slides on the corners. However, i61ides can .~, : 17 : ' ... ... . ..
. . ~ . : , . . . ...
: ~ .
lso be formed in two parts and the parts can then be screwed together after insertion into the radial slot.
Finally, figure 25 shows a ~ulti-step transmission that uses a dou~le isilide as shown in figures 20 to 22, in which connection the balls 91, 92, 93 that transmit the force are guided in the inertial ring 68, in the housing 44, and in the driven element 51 are each guided in grooves, whereas the balls 94 that circulate only on the surface of the inertial ring 68, i.e., not in the ball guide tracks, only have a supporting functio~. In this:
case, the guide disk 83 is supported ~y means of a ball bearing 84 so as to be rotatable, so that the guide disk 83 can follow th~ rotational motion that is governed by the balls 91, 9!2 that are guided in the undulating track.
.
:
.
:
, ~
Claims (20)
1. A ball bearing transmission, consisting of a driven member (3) that is supported in a housing and a driving element (1) with an eccentric (1a) that is mounted thereon and surrounded by a bearing (5) for the force transmission elements, characterized in that the balls (6) that serve to transfer the force are held in a force fit against the bearing (5) by means of an inertial ring (7, 37, 40) that is supported so as to be freely rotatable and are also guided in ball guides formed, on one side, directly in the housing (2) and, on the other side, in the driven element (3), of which one is formed either by radial ball guide grooves (10), a continuous eccentric groove (41) in conjunction with a ball guide formed by fixed radial slots (42) or a constant eccentric groove (41) in conjuction with a ball guide formed by fixed radial slots (42) or a continuous undulating groove (27), and the other being formed by a constant undulating track (11, 23) with a number of waves that differs from the number of radial guide grooves (10) or the number of waves in the first undulating track, respectively, and the number of balls corresponds to the number of radial ball guide grooves (10) or the number of intersection points of both undulating tracks with the pitch circle.
19 A ball bearing transmission as defined in claim 1, characterized in that the driven side ball-undulating guide track can be described by the equation wherein rx = the radial distance of a point on the undulating track midline from the axis of rotation e = eccentricity Phix = the angle of curvature on the undulating track midline Z1 = the number of waves in one undulating track Z2 = the number of waves in the other undulating track or the number of radial grooves rs = the radial distance of the eccentric at the point set by rx
3. A ball bearing transmission as defined in claim 1 or claim 2, characterized in that in a transmission with unilateral guidance of the force transmitting balls (6) in radial guide grooves (10) the number of balls (6) and correspondingly of radial guide grooves (10) is in proportion to the number of waves of the undulating track (11) in a ratio between n:(n-2) and n:(n+2).
4. A ball bearing transmission as defined in one of the claims 1 to 3, characterized in that in a transmission with bilateral guidance of the force transmitting balls (6) in undulating tracks (11, 36), the number of balls (6) and correspondingly of the waves in one undulating track (36) is in proportion to the number of waves of the other undulating track (11) in the ratio of at least n:(n+/-2).
5. A ball bearing transmission as defined in one of the claims 1 to 4, characterized in that the inertial ring (37, 40) is provided with slot guides (38, 39) that enclose the balls, and which hold the balls without hindering the slight oscillation about their working position (which is functionally determined) in a prescribed mutual (medium) distance from each other and carries them in this manner in the desired uniform direction of rotation.
6. A ball bearing transmission as defined in one of the claims 1 to 5, characterized in that several ball rings (6a, 6b) are provided separated radially from each other and each of the ball rings is held in contact with the bearing (5) or with the inertial ring (7a) that is located radially inwards by an inertial ring (7a, 7b).
7. A ball bearing transmission as defined in one of the claims 1 to 6, characterized in that in the individual hall rings there is in each instance an equal number of balls (6, 6a) and the associated undulating tracks have a correspondingly equal number of waves.
8. A ball bearing transmission as defined in claim 7, characterized in that the undulating tracks (11a, 11b) that guide the balls on the output side are arranged in a common driven disk (3).
9. A ball bearing transmission as defined in claim 6, characterized in that in order to form a change-speed transmission, a different number of balls (6, 6a) is contained in the individual ball rings, and the associated undulating tracks correspondingly contain a different number of waves.
10. A ball bearing transmission as defined in claim 7 or claim 9, characterized in that the undulating tracks (11a, 11b) that guide the balls on the output side are arranged in driven disks (3) that are separated from each other.
11. A ball bearing transmission as defined in one or more of the claims 1 to 10, characterized in that in order to form a change-speed transmission a different number of balls (6, 6a) is contained in the individual ball rings, and the associated undulating tracks correspondingly have an unequal number of waves.
12. A ball bearing transmission as defined in one of the claims 1 to 11, characterized in that in order to form a multi-stage transmission or a multi-train change-speed transmission, the driven element (22) of each subsequently incorporated transmission stage is supported concentrically on the driven element (21) of each following transmission stage such that together with an annular surface (24) that bears the undulating track (23) they are opposite an annular shoulder (28) that supports the radial guide grooves (27) so as to form an annular gap (29), the preceding driven element (21) being formed as an eccentric (30) in the area of the annular gap (29), on which the bearing (31) for the balls (32) and the freely rotatable baring ring (33) that holds the balls (32) of the next ball-bearing transmission stage are arranged.
13. A ball bearing transmission as defined in claim 12, characterized in that the eccentric is formed in the area of the annular gap within the housing (26).
14. A ball bearing transmission as defined in one of the claims 1 to 13, characterized in that in order to transmit force, between the driving element (41) and the fixed part--housing (44) or radial slot disks (59, 85, 86)--on the one side and between the driven element (41) or the radial slot disks (59, 85, 86) and the driven element (51) on the other side, there are separated ball sets (55, 56; 71, 72; 76, 77).
15. A ball bearing transmission as defined in claim 14, characterized in that the balls of the ball sets (71, 72;
76, 77) are supported on a ball race (64, 65; 73, 74; 78) so as to be freely rotatable.
76, 77) are supported on a ball race (64, 65; 73, 74; 78) so as to be freely rotatable.
16. A ball bearing transmission as defined in one of the claims 1 to 15, characterized in that the eccentric disk (61) is surrounded by two rows of balls (64, 65) of which each is held in a bearing race (62, 63), these rows of balls serving to support the balls (66, 67) that transmit the force in such a way that each of the balls (66, 67) that serve to transmit the force is supported by four balls of the two rows of balls (64, 65).
17. A ball bearing transmission as defined in claim 1, claim 14, and claim 15, characterized in that the balls (71, 72) that serve to transmit the force are supported in each instance by a separate ball race (73, 74).
18. A ball bearing transmission as defined in claim 1, claim 14, and claim 15, characterized in that the balls (76, 77) that serve to transmit the force are in each instance supported in pairs by a common ball race (78).
19. A ball bearing transmission as defined in one or more of the claims 1, 14 to 18, characterized in that the balls are arranged in slides (70, 81) that are supported 50 as to be able to slide in each instance in a radial slot (58, 86, 89) of a disk (59, 85, 88) that is secured to the housing between the inertial ring (68) of the drive (41, 61) and the housing (44) or the output (51), respectively.
20. A ball bearing transmission as defined in one or more of the claims 14 to 20, characterized in that the balls (76, 72) that serve to transmit the force are supported in a slide (70) by means of a bushing (82) or a roller bearing, preferably by a needle roller bearing.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DEP3916108.0 | 1989-05-18 | ||
| DE3916108 | 1989-05-18 | ||
| DE19893920317 DE3920317A1 (en) | 1989-05-18 | 1989-06-21 | SPHERICAL GEARBOX |
| DEP3920317.4 | 1989-06-21 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA2033061A1 true CA2033061A1 (en) | 1990-11-19 |
Family
ID=25880978
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA 2033061 Abandoned CA2033061A1 (en) | 1989-05-18 | 1990-05-18 | Ball bearing transmission |
Country Status (6)
| Country | Link |
|---|---|
| EP (1) | EP0425657A1 (en) |
| JP (1) | JPH04500714A (en) |
| AU (1) | AU5810790A (en) |
| CA (1) | CA2033061A1 (en) |
| DE (1) | DE3920317A1 (en) |
| WO (1) | WO1990014532A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109964057A (en) * | 2016-11-17 | 2019-07-02 | 恩普乐斯股份有限公司 | Ball speed reducer |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2966536B2 (en) * | 1990-12-27 | 1999-10-25 | 加茂精工株式会社 | Rolling ball type differential reduction gear |
| DE19757845B4 (en) * | 1997-12-24 | 2006-12-14 | Dieter Bollmann | Ball power transmission |
| DE102006006003A1 (en) | 2006-02-08 | 2007-08-09 | Auma Riester Gmbh & Co. Kg | Superposition gear |
| JP2018115715A (en) * | 2017-01-19 | 2018-07-26 | 株式会社エンプラス | Ball speed reducer |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1359655A (en) * | 1970-08-01 | 1974-07-10 | Leeson P G | Speed changing mechanisms |
| US4643047A (en) * | 1981-10-20 | 1987-02-17 | Advanced Energy Concepts '81 Ltd. | Speed reducing gearing mechanism employing trochoidally formed gear surfaces for rolling torque transmission |
| US4584904A (en) * | 1982-03-26 | 1986-04-29 | Advanced Energy Concepts '81, Limited | Epicyclic transmission having free rolling roller driving elements |
| GB2130334A (en) * | 1982-10-22 | 1984-05-31 | Quadrant Drive | Motion transmitting device |
| JPS60146954A (en) * | 1983-12-30 | 1985-08-02 | Sanwa Tekki Corp | Gearless speed changer |
| JPH0762495B2 (en) * | 1985-06-27 | 1995-07-05 | 加茂精工株式会社 | Rolling ball type differential reduction mechanism |
-
1989
- 1989-06-21 DE DE19893920317 patent/DE3920317A1/en not_active Withdrawn
-
1990
- 1990-05-18 AU AU58107/90A patent/AU5810790A/en not_active Abandoned
- 1990-05-18 EP EP19900908947 patent/EP0425657A1/en not_active Withdrawn
- 1990-05-18 JP JP50835590A patent/JPH04500714A/en active Pending
- 1990-05-18 CA CA 2033061 patent/CA2033061A1/en not_active Abandoned
- 1990-05-18 WO PCT/EP1990/000802 patent/WO1990014532A1/en not_active Application Discontinuation
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109964057A (en) * | 2016-11-17 | 2019-07-02 | 恩普乐斯股份有限公司 | Ball speed reducer |
Also Published As
| Publication number | Publication date |
|---|---|
| EP0425657A1 (en) | 1991-05-08 |
| JPH04500714A (en) | 1992-02-06 |
| DE3920317A1 (en) | 1990-11-22 |
| WO1990014532A1 (en) | 1990-11-29 |
| AU5810790A (en) | 1990-12-18 |
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