CN102667238B - Gearing - Google Patents
Gearing Download PDFInfo
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- CN102667238B CN102667238B CN201080051092.6A CN201080051092A CN102667238B CN 102667238 B CN102667238 B CN 102667238B CN 201080051092 A CN201080051092 A CN 201080051092A CN 102667238 B CN102667238 B CN 102667238B
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- Prior art keywords
- gear
- gearing
- recess
- external gear
- rolling element
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Classifications
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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
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
- F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
Abstract
The invention provides a kind of gearing, it reasonably takes into account the raising (increase of load capacity) of the durability utilized in the gear of rolling element and the embedded structure of spindle unit and the raising of miniaturization.Gearing of the present invention possesses: external gear (50,52), and it possesses the shaft insertion hole (50A, 52A) formed vertically; Eccentric shaft (44), it is as the spindle unit being embedded in described shaft insertion hole (50A, 52A); And multiple roller (rolling element) (46,48), be configured in a circumferential direction vertically between external gear (50,52) and eccentric shaft (44), and gearing of the present invention is along the circumferential direction formed with multiple recess (50C, 52C) holding multiple roller (46,48) respectively at the inner peripheral surface (or outer circumferential face of eccentric shaft (44)) of the shaft insertion hole (50A, 52A) of described external gear (50,52).
Description
Technical field
The present invention relates to a kind of gearing, particularly relate to a kind of consider gear and spindle unit chimeric form and take into account the gearing of the increase (raising of durability) of load capacity and the raising of miniaturization.
Background technique
Such as, eccentric swing internally meshed type gearing is disclosed in patent documentation 1.
As shown in Figure 12 and Fig. 6 (A), in this gearing Go, by the rotation of input shaft 12, eccentric shaft 14 is rotated, by the rotation of this eccentric shaft 14 while eccentric body 14A, 14B make external gear 16,17 eccentric swing internal messing in internal gear 18 (internal tooth namely in roller 18A).By this internal messing in external gear 16,17 and the relative rotation producing the number of teeth difference (in this example being 1) corresponding to this external gear 16,17 and internal gear 18 between internal gear 18, therefore limit the rotation of either side in internal gear 18 or external gear 16,17, export this from opposite side and relatively rotate composition.
In this gearing Go, consider durability and miniaturization, the following structure of extensive employing: the Internal and external cycle omitting the eccentric body bearing be configured between eccentric shaft 14 and external gear 16,17, and multiple roller 20,21 is directly configured between eccentric shaft 14 and external gear 16,17 as rolling element.
In addition, multiple roller 20,21 by retainer 22,23 vertically (with axle abreast) along the circumferential direction and axially locating.
Patent documentation
Patent documentation 1: Japanese Unexamined Patent Publication 2008-38941 publication (Fig. 1)
In this eccentric swing internally meshed type gearing, the life-span of the embedding part of external gear and eccentric shaft becomes the big factors determining speed reducer bulk life time.The load capacity of eccentric body bearing (roller) determines (such as primarily of the pitch diameter of the size (diameter and length) of roller, the quantity of roller and roller, in JIS B1518, the formula relevant according to these factor determination safe loads).
But actual conditions are that the size of external gear or internal gear is not only compressed to almost close to the limit in intensity, balance also cannot reduce further.In this case, the diameter of roller or the increase of pitch circle are directly connected to the increase of the radial direction size of gearing.In addition, the lengthening of roller length is directly connected to the increase of the axial extent of gearing, so have to sacrifice miniaturization.
The present invention completes to solve this problem in the past, and its problem is to provide a kind of gearing reasonably taking into account the increase (raising of durability) of the load capacity that make use of in the gear of roller and the embedded structure of spindle unit or the raising of miniaturization.
Summary of the invention
The present invention forms the above-mentioned problem of solution by following, namely provides a kind of gearing, comprising: gear, possess the shaft insertion hole formed vertically; Spindle unit, is embedded in described shaft insertion hole; Multiple rolling element, is configured between described gear and spindle unit, and this gearing is along the circumferential direction formed with the recess of the described multiple rolling element of multiple accommodation at the inner peripheral surface being formed with described shaft insertion hole of described gear or the outer circumferential face of described spindle unit.
The spindle unit of gear involved in the present invention and the shaft insertion hole that is embedded in this gear has the recess holding the part being configured at the rolling elements such as roller between this gear and spindle unit in the axial direction at its either side.Therefore, can to spindle unit and the factor of additional " sliding contact (face contact) " in the embedded structure of gear being set to " Structure deformation (linear contact lay or point cantact) " in the nature of things in the past, and can obtain to reduce slip resistance by the rotation of rolling element and increase 2 kinds of load capacity and so on by the increase internal face of recess and the area of contact of rolling element simultaneously and act on.
In addition, due to a part for rolling element can be held in recess, and circumferential locations and the axial position of multiple rolling element can be specified, therefore not need necessary retainer in the past.Therefore, it is possible to again set up in the space that retainer itself is shared in a circumferential direction or configure rolling element.In addition, such as, when rolling element is " roller ", can corresponding retainer this in the amount in the axially shared space of roller, the axial length of this roller is extended further.Therefore, if can ensure identical by the axial length of whole gearing, then correspondingly load capacity can be increased.Or, if can be identical load capacity, then the axial length of gearing can be shortened respective amount.
In addition, a part for corresponding rolling element is contained in the amount in recess, a part for this rolling element is assembled with the state embedded at gear or spindle unit side, if therefore the size of the radial direction of gearing is identical, then can increase load capacity by the rolling element configuring larger diameter, on the contrary, if the diameter of rolling element is maintained identical, then can reduce the size of the radial direction of gearing further.In addition, when forming recess in gear side, the pitch diameter of rolling element can also be increased.
According to the present invention, the increase (raising of durability) of the load capacity that make use of in the gear of rolling element and the embedded structure of spindle unit and the raising of miniaturization reasonably can be taken into account.
Accompanying drawing explanation
Fig. 1 is the sectional view of the gearing involved by an example representing embodiments of the present invention.
Fig. 2 is the sectional view of the arrow II-II line along Fig. 1.
Fig. 3 is the enlarged partial sectional figure near arrow III.
Fig. 4 is the plan view of the external gear monomer in said gear device.
Fig. 5 represents the sectional view of said gear device for the example of the beat driving purposes of wind generating unit.
Fig. 6 is by compared with the past for the effect of the miniaturization of said gear device and the figure illustrated, (A) be gearing (being equivalent to the sectional view of the arrow Va-Va of Figure 12) in the past, (B) gearing involved by above-mentioned mode of execution.
Fig. 7 is the sectional view that the gearing involved by an example of other mode of executions of the present invention is corresponding with Fig. 2.
Fig. 8 is the partial cross section figure representing the variation forming recess.
Fig. 9 is the sectional view of the gearing involved by an example representing another other mode of executions of the present invention.
Figure 10 is the sectional view of the arrow X-X line along Fig. 9.
Figure 11 is the partial cross section figure near the planetary pinion of the gearing involved by an example representing other mode of executions another of the present invention.
Figure 12 is the sectional view corresponding with Fig. 1 of an example of the gearing represented in the past.
Embodiment
Below, the gearing involved by an example of embodiments of the present invention is described in detail.
Gearing involved by this mode of execution rotates to substantially horizontal for making the generator unit (nacelle) of the topmost part of the cylinder pillar being configured at not shown wind-power generating system, and changes according to wind direction etc. the running shaft being rotatably installed on 3 air vanes (wing) of this nacelle.About the form being installed to wind-power generating system, will mention afterwards, at this, be described from the structure of gearing itself.
Fig. 1 is the sectional view of the gearing G1 involved by an example of embodiments of the present invention, and Fig. 2 is the sectional view of the arrow II-II line along Fig. 1, and Fig. 3 is the enlarged partial sectional figure near arrow III, Fig. 4 is the plan view of external gear monomer.
Referring to figs. 1 through Fig. 4, this gearing G1 is the input side reducing gear 40 of attached in series eccentric swing internally meshed type planetary gears and the device of outlet side reducing gear 42.This is because this gearing G1 functionally needs the high reduction speed ratio of 1/1000 ~ 1/3000.
Input side reducing gear 40 varies in size because handled torque is different with outlet side reducing gear 42, but in mechanics, have roughly the same structure.In present embodiment, in outlet side reducing gear 42, apply the present invention, therefore, for simplicity, outlet side reducing gear 42 is described in detail, omits the detailed description to input side reducing gear 40.
Outlet side reducing gear 42 possesses the input shaft 43 with output shaft one (dual-purpose) of input side reducing gear 40.Input shaft 43 is by self-aligning roller bearing 45 and roller bearing 47 dual-supporting.Input shaft 43 is assembled with the eccentric shaft 44 that can rotate integrally.Eccentric shaft 44 is configured at the radial direction central authorities of this gearing G1, and has 2 eccentric bodies 44A, 44B.Multiple roller 46,48 is configured with vertically respectively in the periphery of eccentric body 44A, 44B.External gear 50,52 is had by shaft insertion hole 50A, 52A are chimeric in the periphery of multiple roller 46,48.This external gear 50,52 internal messing is in internal gear 54.That is, in this mode of execution, external gear 50,52 is equivalent to " possessing the gear of the shaft insertion hole formed vertically ", and roller 46,48 is equivalent to " multiple rolling element ", and eccentric shaft 44 is equivalent to " being embedded in the spindle unit of shaft insertion hole ".About the embedded structure of eccentric shaft 44, roller 46,48 and external gear 50,52, will be described in detail later.
External gear 50,52 has the position inner pinhole 50B, 52B of running through vertically that are formed at and offset from center 01 (with reference to Fig. 4) respectively.In addition, in present embodiment, inner pinhole 50B, 52B are along the circumferential direction to be formed at equal intervals, but may not be at equal intervals.Domestic 60 (with interior roller 62 together) Spielpassung is in inner pinhole 50B, 52B.The eccentric phase of external gear 50,52 departs from 180 degree mutually, and internal messing is in internal gear 54 respectively.Internal gear 54 doubles as the local shell 56 of outlet side reducing gear 42.The internal tooth of internal gear 54 is made up of the export trade 58 of cylindrical shape.The quantity (quantity of export trade 58) of the internal tooth of internal gear 54 only more than the quantity of the external tooth of external gear 50,52 1.
Described domestic 60 press-ins export flange 64 or become to be integrated with it, export flange 64 and are integrated with output shaft 66 one-tenth.
In addition, the symbol 68 in figure be support in the lump multiple domestic 60 domestic supporting ring.In this mode of execution, by being formed this domestic supporting ring 68 with the parts with thickness and rotatably remaining on shell 70, this domestic supporting ring 68 can be made to have the function of " bearing ".Thus, with this domestic supporting ring 68 and output flange 64 dual-supporting domestic 60, and outer radial load (due to the load that blast oppositely inputs from air vane side) is blocked with this supporting portion of domestic 60.In present embodiment as described later, eccentric shaft 44, roller 46,48 and external gear 50,52 are assembled with gapless state by interference fit, to have auto-lock function, so the harmful effect that brings of the eccentric motion that can block this outer radial load external gear wheel 50,52 by this dual-supporting of domestic 60 and its effect is more remarkable.
As shown in Figure 5, gearing G1 and motor Mo links, and is fixed on the housing main body 74 of nacelle (being rotatably provided with the generator unit of air vane) by bolt 71 together with shell 70,56.By the way, be because the rigidity of the housing main body 74 of nacelle can be used as " hoop " like this compared with the wall thickness near bolt 71 in the shell 70,56 of unfertile land formative gear device G1.
The output shaft 66 of gearing G1 links and is fixed with the beat driving small gear (small gear for making nacelle rotate at horizontal plane) 75 of the not shown nacelle being arranged in wind-power generating system.Beat driving small gear 75 engages with (forming the inner ring of beat bearing 76) revolution internal gear 77.Revolution internal gear 77 is fixed on the not shown cylinder pillar side of wind-power generating system, and the outer frame 78 forming the outer ring of beat bearing 76 is fixed on housing main body 74 side of nacelle.In addition, the symbol 79 of Fig. 5 represents the brake unit be made up of braking propulsion device 79A, beat brake calipers 79B, brake disc 79C etc.
Then, utilize Fig. 2 to Fig. 4, to the eccentric shaft 44 in present embodiment, roller 46,48, the embedded structure of external gear 50,52 is described in detail.
Multiple recess 50C, 52C of holding a part for described multiple roller 46,48 is respectively formed vertically in a circumferential direction at the inner peripheral surface of shaft insertion hole 50A, 52A of external gear 50,52.The quantity being formed at (inserting domestic 60) inner pinhole 50B, 52B and domestic 60 of external gear 50,52 is in this example embodiment 12, therefore the quantity of roller 46,48 and recess 50C, 52C is set to 12 of equal number.Inner peripheral surface inside the radial direction making the recess 50C of external gear 50 be formed between inner pinhole 50B and inner pinhole 50B, in the same manner, the inner peripheral surface inside the radial direction making the recess 52C of external gear 52 be formed between inner pinhole 52B and inner pinhole 52B.At this, as shown in Figure 4, " inner peripheral surface inside the radial direction between inner pinhole 50B (52B) and inner pinhole 50B (52B) " refers to, the line Li1 linking the center O1 of external gear 50 (52) and the center O2 of inner pinhole 50B (52B) does not exist the center O3 of roller 46 (48).In the category of this connotation, be more preferably when pulling out tangent line from the center O1 of external gear 50 (52) to inner pinhole 50B (52B), between the tangent line of adjacent inner pinhole 50B (52B) (that is, between the tangent line Li2 of specific inner pinhole 50B (52B) and the tangent line Li3 of adjacent inner pinhole 50 (52B)) there is the center O3 of roller 46 (48).There is the center O3 of roller 46 (48) in the centre being more preferably adjacent tangent line Li2, Li3.For these structures, there is the size of the interval L1 (with reference to Fig. 2, Fig. 4) of this each inner pinhole 50B, 52B and recess 50C, 52C ensured while sufficient intensity, outside radial direction recess 50C, 52C being formed to as far as possible external gear 50,52, its result, this structure to guarantee significantly as far as possible the diameter of roller 46,48 or pitch circle comparatively effective.
The shaft section of internal face 50C1,52C1 of recess 50C, 52C is set to " circular arc ", the diameter d 1 of this circular arc consistent with the diameter (d1) of roller 46,48 (with reference to Fig. 2).That is, the entirety of internal face 50C1,52C1 of recess 50C, 52C contacts with roller 46,48 respectively.In addition, the protuberance 50D (the protuberance 52D between recess 52C and the 52C of external gear 52) between recess 50C and the 50C of external gear 50 plays the locating function of the circumferencial direction of roller 46,48 respectively.
In addition, recess 50C, 52C about external gear 50,52 utilize broaching tool carry out stretch process together with shaft insertion hole 50A, 52A and heat-treat, and grind recess 50C, 52C afterwards.Insert eccentric shaft 44 by the rear inner side to this roller 46,48 configuring roller 46,48 at recess 50C, 52C of external gear 50,52 to assemble.
Now, external gear 50,52 with between eccentric shaft 44 by this recess 50C, 52C and roller 46,48 inserted into each other chimeric in an interference fit.Thus, the self-locking performance of the wind-power generating system being assembled with this gearing G1 can also be had.Namely, even if when having external force due to strong wind etc. from the effect of output pinion 75 side, also can play gearing G1 can not because of this external force the auto-lock function of reverse direction actuation and so on, therefore, it is possible to be used in this external force of antagonism, be such as configured at not shown braking device miniaturization in motor Mo.In addition, usage frequency or the load of this braking device can be reduced, therefore, it is possible to keep the life-span of this braking device longlyer.This auto-lock function is such as especially effective when the angular adjustment gearing (gearing that so-called pitch drives) etc. of the more air vane of the usage frequency (or service time) applying the present invention to braking device.In addition, referring in this said " interference fit " under the condition that temperature between the parts be in for mutually assembling is identical cannot the size relationship of direct-assembling.In order to assemble under the state of " interference fit ", specifically, by being set to the shrink fit of high temperature by being positioned at more outward parts, the parts be positioned at more in the inner part being set to the shrink-fit of low temperature, or assemble by methods such as the chimeric press-ins of powerful pressing-in force press-in.In this embodiment, only by eccentric shaft 44, roller 46,48 and external gear 50,52 interference fit, if but further assembling internal gear 54 by interference fit through export trade 58 and external gear 50,52 by interference fit assembles, then more powerful self-locking performance can be had.
In addition, symbol 59 is liners of the axially locating for carrying out roller 46,48, and 61 is pads.
Then, the effect of this gearing G1 is described.
In this embodiment, by the rotation of motor Mo, first in input side reducing gear 40, carry out the 1st grade with the effect identical with the effect of the following outlet side reducing gear 42 described and slow down.
In outlet side reducing gear 42, carry out the 2nd grade of deceleration as follows.That is, in this embodiment, internal gear 54 is integrated with 56 one-tenth, shell and is fixed, if so the input shaft 43 of outlet side reducing gear 42 rotates 1 time, then external gear 50,52 swings 1 time by eccentric body 44A, 44B of eccentric shaft 44.Its result, 1 tooth (number of teeth residual quantity) is only departed from the engaging position of external gear 50,52 and internal gear 54.Its result, external gear 50,52 only rotates relative to this internal gear 54 angle that (the direction rotation to contrary with the rotation of eccentric shaft 44) be equivalent to this number of teeth difference relatively.External gear 50,52 is rotated (rotation) relative to this internal gear 54 relative and is taken out from exporting flange 64 by the movable fit of described inner pinhole 50B, 52B and domestic 60 (and interior rollers 62).The rotation exporting male flange 64 is passed to the output shaft 66 be integrated with this output flange 64 one-tenth.
As shown in Figure 5, output shaft 66 link and be fixed with the beat driving small gear 75 of wind-power generating system.Beat driving small gear 75 engages with (forming the inner ring of beat bearing 76) revolution internal gear 77.Therefore, by motor Mo, the output shaft 66 of gearing G1 is rotated, thus with engaging of internal gear 77 of revolution, whole nacelle can be turned round in horizontal plane by beat driving small gear 75.Its result, by nacelle towards desired direction (such as direction) windward, and can bear blast effectively.
At this, be described in detail with reference to the effect of Fig. 6 to the telescoping part of the eccentric shaft 44 in this gearing G1, roller 46,48 and external gear 50,52.
Fig. 6 (A) represents the cross section of the gearing Go in the past shown in Figure 12, and Fig. 6 (B) (in the same manner as Fig. 2) represents the cross section of the gearing G1 of this mode of execution.For the ease of understanding, and for convenience's sake, roller 46,48 (20,21) is set to all identical with the parts beyond external gear 50,52 (16,17).
In gearing G1 involved by this mode of execution, be formed with multiple recess 50C, 52C of holding a part for multiple roller 46,48 respectively vertically in a circumferential direction at the inner peripheral surface of shaft insertion hole 50A, 52A of external gear 50,52.Therefore, it is possible to the Qian He to the eccentric shaft 14 with external gear 16,17 that are set to " Structure deformation (linear contact lay) " based on roller 20,21 in the past, the factor of additional " sliding contact (face contact) ".Because roller 46,48 rotates, so more slip resistance can be reduced than simple sliding bearing, and the area of contact of internal face 50C1,52C1 of this roller 46,48 and recess 50C, 52C can be increased than ever more significantly, load capacity can be increased to measuring (under the size GL1 (GLo) of the radial direction by gearing G1 (Go) is maintained in identical state).
When the gearing that the beat for wind-power electricity generation drives, due to arrange or change time be in overhead very high position and the nacelle only guaranteeing to have narrow space need be carried to, therefore gearing miniaturization, Lightness be key factor.On the other hand in the nature of things, want raising also strong relative to the requirement of the durability of (unforeseeable size) load of natural objects.In present embodiment, have (outlet side reducing gear 42) eccentric shaft 44 by the situation of significantly slow down (but the lower torque of rotating speed is larger) and so in input side reducing gear 40, therefore by approaching face contact this technology and can maintaining miniaturization, Lightness while to increase the advantage of permissible load capacity and so on very big.In addition, in the present embodiment, in input side reducing gear 40, do not use structure of the present invention, in outlet side reducing gear 42, only use the structure of the present application.This is because, in a structure of the in-vention, due to the sliding contact of roller 46,48 and recess 50C, 52C, therefore preferably to use in the part of low speed.Such as, in the present embodiment, the rotating speed of motor is 1200rpm, the reduction speed ratio of input side reducing gear 40 is 30, and therefore the rotating speed of eccentric shaft 44 becomes 40rpm.In addition, the reduction speed ratio of the outlet side reducing gear 42 in present embodiment is that 43 (number of teeth of external gear 50,52 is 43, be 1 with the number of teeth difference of internal gear 54), so the speed of autorotation of external gear 50,52 (rotating speed of output shaft 66) goes out 1rpm slowly.That is, the relative rotation speed of external gear 50,52 and eccentric shaft (spindle unit) 44 is about 42rpm.In the present invention, according to upper type, the relative rotation speed being used in gear and spindle unit is less than the position of 100rpm, then can more effectively play its true value.
In addition, in recess 50C, 52C, accommodating a part for roller 46,48, therefore not needing the necessary retainer 22,23 of circumferential locations and axial position in the past in order to specify multiple roller 46,48.Further, can the part amount be contained in recess 50C, 52C of corresponding roller 46,48 part for roller 46,48 be assembled with the state entering external gear 50,52.Therefore, the size GL1 (GLo) of the radial direction of gearing G1 (Go) can be maintained identical while, the space that retainer 22,23 itself is shared is in a circumferential direction used for " increase (d0 → d1) of diameter " of roller 46,48, in this, also can reliably increase load capacity (if, can be identical load capacity, then the size of the radial direction of gearing G1 can be made to be less than gearing Go).Further, in the present embodiment, because external gear 50,52 side is formed with recess 50C, 52C, so the pitch circle d4 (d3 → d4) of large roller 46,48 also can be added.
In addition, from Figure 12 and Fig. 1 (or Fig. 3) relatively known, retainer 22,23 in the past can be used in the axially shared amount of space of roller 20,21 " increase of axial length " of roller 46,48, also can reliably increase in this load capacity (if, can be identical load capacity, then the axial length of gearing G1 (GL1) can be shortened respective amount than the axial length GLo of gearing Go.
In addition, in this mode of execution, the quantity of the quantity of domestic 60 and recess 50C, 52C is set to equal number, and multiple recess 50C, 52C are formed at the inner peripheral surface of the inner pin-and-hole 50B of external gear 50,52 each other, inside 52B radial direction each other respectively, even if (easily becoming limited in the intensity of external gear 50,52) recess 50C, 52C and the distance L1 between inner pinhole 50B, 52B so add diameter and the pitch circle d4 of large roller 46,48, also can be guaranteed significantly.
In addition, in this mode of execution, the quantity of the quantity of domestic 60 and recess 50C, 52C is set to equal number (being 12), and between whole each inner pinhole 50B, between 52B, configure roller 46,48 respectively accordingly, but according to purposes, the quantity that the quantity of roller 46,48 is less than domestic 60 also can be made.But, now, not by the forming position of recess 50C, 52C merely equivalent arrangements in a circumferential direction, but the inner peripheral surface of the inner pinhole 50B being formed at external gear 50,52 all the time each other, inside 52B radial direction each other.In addition, on the contrary, the quantity of inner pinhole also can be less than the quantity of roller.Now, the recess of more than 2 is formed at the inner peripheral surface inside inner pinhole radial direction each other.
Below, other changes of the present invention are described.
In the above-described embodiment, gear side forms recess outside, but in the present invention, also can form recess in spindle unit side.
The example of one shown in Fig. 7.In mode of execution shown in Fig. 7, recess 144C is formed at eccentric shaft (spindle unit) 144.In this mode of execution, the protuberance 144D between recess 144C plays the locating function of roller 146 (148).In addition, recess is not formed with in external gear 150 (152) in this embodiment.By this structure, also the action effect roughly the same with above-mentioned action effect can be obtained.
Be not limited to this mode of execution, in the present invention, roller revolves round the sun centered by spindle unit by the speed identical with the either side (forming the side of recess) of spindle unit or gear.Therefore, the designing points that this roller becomes important is more effectively rotated.Form the change of recess at this spindle unit and have that the contact resistance (contact resistance relative to roller and gear side) of roller and spindle unit side is further becomes large and so on trend, therefore sometimes find out the designing points of spinning rollers effectively further according to the situation of the relative rotation speed of gear and spindle unit more like a cork.
Other structures of mode of execution involved by Fig. 7 are identical with mode of execution before, therefore only add the identical symbol of rear two digits to position that is identical in the drawings or that have an identical function, omit repeat specification.
Then, in the above-described embodiment, form recess 50C, 52C of diameter (d1) circular shape identical with the diameter d 1 of roller 46,48, the entirety of internal face 50C1,52C1 of recess 50C, 52C contacts with roller 46,48, but the formation shape of the recess in the present invention is not limited to this example, such as, a part for the internal face only having recess and the formation of roller contact can be also set to.This example is shown in Fig. 8.
Fig. 8 (A) is configured to the axial section shape of the recess C10 of gear G10 to be set to ellipse and the figure that contacts with roller R10 of 2 positions only near opening portion C11, C12.In this structure, the structure involved by the mode of execution of the Fig. 1 to Fig. 5 before the contact area rate of recess C10 and roller R10 reduces, and although there is a little foozle, the accommodation of roller R10 opposed recesses C10 is more stable.
Fig. 8 (B) is that recess C21, the C22 formed further in the recess C20 of gear G20 as multiple recess also intermittently reduces the figure with the contact segment of roller R20.The action effect of the centre of the structure involved by mode of execution of above-mentioned Fig. 1 to Fig. 5 and the structure of Fig. 8 (A) can be obtained.
Fig. 8 (C) is the figure of the diameter d 3 of the circular arc of the recess C30 of diameter d 4 bigger ground formative gear G30 than roller R30.This structure can reduce the area of contact of recess C30 and roller R30 further, and can obtain the self-aligning effect of spindle unit S10 opposed gear G30, therefore, it is possible to improve the rounding rotated further.In addition, the example of this Fig. 8 (C), compared with the example of (A), (B), the contact of recess C30 and roller R30 is closer to linear contact lay, in the recess that (but comprising the example of this Fig. 8 (C)) is involved in the present invention, the contact of recess and roller becomes " convex with recessed contact " from " convex with convex contact " on shaft section, so the damage (also than convex with convex contact in the past) of (even if supposing the state become close to linear contact lay) contacting part is little.In addition, the example of this Fig. 8 (C) also can obtain and easily find out the advantage in the design of the designing points that (easily adjusting) roller can rotate effectively and so on.
Like this, the formation shape of recess of the present invention can consider the material of the purposes of gearing, gear and spindle unit or relative rotation speed, the rounding etc. of durability that expectation obtains or rotation suitably determines.
In addition, in above-mentioned mode of execution, there is the eccentric swing internally meshed type planetary gears that eccentric shaft is present in the radial direction central authorities of gearing, but be not limited to the gearing of this structure as application gearing of the present invention.Such as, as shown in FIG. 9 and 10, the present invention also can be applicable to the gearing G2 of the structure running through external gear (gear) as multiple eccentric shaft (spindle unit).
Because the basic structure of this planetary gears itself is well-known, so only simply illustrate.
If (outlet side reducing gear) input shaft 80 rotates, then 4 eccentric shafts 84 are rotated in deceleration by driving gear 82,83 simultaneously.Its result, the eccentric body 84A being integrally installed on each eccentric shaft 84 each other and 84B rotate with same phase each other, external gear 90,92 is by swing rotary while connecing in roller 86,88 and internal gear 94.Internal gear 94 is in and is integrated and the state of fixing with 96 one-tenth, shell, if so external gear 90,92 swing rotary, then produces the phenomenon of this external gear 90,92 and the engaging position movement successively as the pin 94P of the internal tooth of internal gear 94.
Now, the number of teeth of the gear ratio internal gear 94 of external gear 90,92 is only a little, so by the movement of this engaging position, the internal gear 94 that the phase place of external gear 90,92 is in stationary state relatively only departs from the amount that (rotation) is equivalent to number of teeth difference.Therefore, eccentric shaft 84 revolves round the sun around the axle center of gearing G2 with the speed being equivalent to this rotation composition, support the 1st of this eccentric shaft 84 the, the 2nd wheel carrier 96,98 one-tenth be integrated and rotate with the speed being equivalent to this revolution speed.
In preferably involved gearing G2, about as gear external gear 90,92, the eccentric shaft 84 as spindle unit and the multiple rollers 86,88 configured in a circumferential direction vertically between eccentric body 84A, 84B at external gear 90,92 and eccentric shaft 84, by forming recess 90C, 92C at external gear 90,92 (above formed and be fitted together to and have the inner circumferential of the shaft insertion hole of described eccentric shaft 84), also can obtain structure identical with mode of execution before, and identical action effect can be obtained.
In addition, as shown in figure 11, the present invention possesses as the planetary pinion 100 of gear of the present invention, as being supported by this planetary pinion 100 as the wheel carrier pin 102 of rotatable spindle unit, multiple rollers 104 of configuring in a circumferential direction vertically between planetary pinion 100 and wheel carrier pin 102, and possess sun gear and internal gear (all omitting diagram) further, also can be applied to the gearing G3 being made up of simple planetary mechanism planetary pinion 100, sun gear and internal gear thus.In addition, because simple planetary mechanism itself is well-known, so detailed.
In addition, now, the recess 100A that also can be configured to planetary pinion 100 (above formed and be fitted together to have on the inner peripheral surface of the shaft insertion hole of described wheel carrier pin 102 and formed) is formed at inside the radial direction of the teeth portion 100B of this planetary pinion 100 respectively.As shown in figure 11, be more preferably, be formed at circumferencial direction middle position in teeth portion 100B (near) radial direction inside.Thereby, it is possible to guarantee the distance L2 of the tooth root 100C of recess 100A and planetary pinion 100 significantly, and the roller 104 being greater than respective amount (or being greater than pitch circle) can be assembled.
Like this, the present invention can be applicable to various gearing.Also can be the purposes that the pitch of wind-power generating system drives, not be limited to the purposes of the gearing of wind-power generating system in addition.
In addition, in mode of execution before, the example forming recess is illustrated, but the formation method of recess involved in the present invention is not limited thereto by carrying out stretch process with broaching tool.Such as, the hole (becoming the hole of a part for recess afterwards) of multiple circle along the circumferential direction can be formed near the central authorities of parts becoming gear, and grind this circular port, afterwards, the shaft insertion hole of a part for each circular port of the similar incision of diameter is formed in the central authorities of the parts becoming gear.Thus, the part that a part for circular port can be remained being cut by shaft insertion hole is used as recess.When for this formation method, the grinding of the internal face of the recess in the example before can realizing replacing based on the cutting edge reconditioning processing of circular port or the manufacture of polishing, (grinding than in example before) can improve surface roughness more.
And, in the recess of above-mentioned mode of execution, the pitch diameter (pitch diameter of roller) of recess (50C) is less than the diameter of protuberance (50D), but when being the method for shaft insertion hole forming said gear central authorities afterwards, also can manufacture the structure making the pitch diameter of recess (pitch diameter of roller) be greater than the diameter of protuberance.
In addition, rolling element of the present invention may not be " roller ", also can be rolling elements such as " balls ".
Industrial Availability
The structure of " gear " that the present invention can apply is not particularly limited, and can be applicable in oscillating internal engagement type external gear, in the involute gear of simple planetary mechanism, or can be applied to further in the gear of the gearing of other structures.For the oscillating internal engagement type gearing of internal gear oscillating-type, also can be applicable to internal gear.
Disclosure in the specification of No. 2009-274773, Japanese patent application of application on December 2nd, 2009, accompanying drawing and claim, its full content is by referring to being applied in this specification.
The explanation of symbol:
G1-gearing, 44-eccentric shaft (spindle unit), 44A, 44B-eccentric body, 46,48-roller (rolling element), 50,52-external gear, 50A, 52A-shaft insertion hole, 50B, 52B-inner pinhole, 50C, 52C-recess, 50C1,52C1-internal face, 50D, 52D-protuberance, 54-internal gear, 60-is domestic.
Claims (5)
1. a gearing, is characterized in that, possesses:
Gear, possesses the shaft insertion hole formed vertically;
Spindle unit, is embedded in described shaft insertion hole; And
Multiple rolling element, is configured between described gear and spindle unit, and
At the inner peripheral surface being formed with described shaft insertion hole of described gear, be along the circumferential direction formed with multiple recess for holding described multiple rolling element,
This gearing possesses: as described gear external gear, as possess eccentric body described spindle unit eccentric shaft, be configured at described external gear and described eccentric shaft eccentric body between multiple rolling element and the internal gear of described external gear institute internal messing, and form make described external gear eccentric swing by the eccentric body of described eccentric shaft, rolling element and recess while make the eccentric swing internally meshed type planetary gears of this external gear and described internal gear internal messing
This gearing possesses further and runs through the multiple domestic of described external gear, and described external gear possesses in the position of the off-centring from this external gear and makes the plurality of domestic multiple inner pinholes inserted respectively,
Described eccentric shaft is configured at the radial direction central authorities of this gearing, and described shaft insertion hole is formed at the radial direction central authorities of described external gear,
Described multiple recess is all formed at the inner peripheral surface inside the radial direction between the described inner pinhole of described shaft insertion hole and inner pinhole,
Further, between the tangent line being centrally located at adjacent inner pinhole making rolling element when described recess is formed as the center pull-out tangent line from the center of external gear to inner pinhole,
Described domestic quantity is identical with the quantity of described recess.
2. gearing as claimed in claim 1, is characterized in that,
Only a part for the internal face of described recess contacts with described rolling element.
3. gearing as claimed in claim 1, is characterized in that,
Protuberance between described recess and recess has the locating function of the circumferencial direction of described rolling element.
4. gearing as claimed in claim 1, is characterized in that,
Described gear carries out chimeric by described recess and rolling element with interference fit with described spindle unit.
5. gearing as claimed in claim 1, is characterized in that,
Form the described eccentric shaft of described swing inner engaging gear mechanism, external gear and internal gear, comprise the recess of described external gear and the contact segment of rolling element, carry out assembling and formative gear device with interference fit, this gearing is the gearing used in the drive portion of the recovering device of natural energy.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2009-274773 | 2009-12-02 | ||
| JP2009274773A JP5256181B2 (en) | 2009-12-02 | 2009-12-02 | Gear device |
| PCT/JP2010/071588 WO2011068160A1 (en) | 2009-12-02 | 2010-12-02 | Gear device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102667238A CN102667238A (en) | 2012-09-12 |
| CN102667238B true CN102667238B (en) | 2015-08-05 |
Family
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201080051092.6A Expired - Fee Related CN102667238B (en) | 2009-12-02 | 2010-12-02 | Gearing |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP5256181B2 (en) |
| CN (1) | CN102667238B (en) |
| WO (1) | WO2011068160A1 (en) |
Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2013096550A (en) * | 2011-11-04 | 2013-05-20 | Nabtesco Corp | Gear transmission device |
| JP6310764B2 (en) * | 2014-04-30 | 2018-04-11 | ナブテスコ株式会社 | Gear transmission |
| JP6378110B2 (en) * | 2015-02-19 | 2018-08-22 | 日本電産コパル株式会社 | Planetary gear transmission |
| CN106090186B (en) * | 2016-06-13 | 2018-10-02 | 中航工业哈尔滨轴承有限公司 | The design method of planetary gear and the planetary gear endoporus on end-face grinding machine |
| KR101955790B1 (en) * | 2017-03-27 | 2019-03-07 | 유경복 | Simplex Drive |
| JP7047301B2 (en) * | 2017-09-22 | 2022-04-05 | 日本電産株式会社 | transmission |
| JP6932068B2 (en) * | 2017-11-15 | 2021-09-08 | 住友重機械工業株式会社 | Eccentric swing type gear device |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2008038941A (en) * | 2006-08-02 | 2008-02-21 | Sumitomo Heavy Ind Ltd | Eccentric swing gear unit |
| WO2008096747A1 (en) * | 2007-02-05 | 2008-08-14 | Sumitomo Heavy Industries, Ltd. | Power transmission device and method of producing the same |
| WO2009025206A1 (en) * | 2007-08-20 | 2009-02-26 | Sumitomo Heavy Industries, Ltd. | Output gear-equipped reduction device and method of assembling the same |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0618724U (en) * | 1992-08-11 | 1994-03-11 | 株式会社鈴木鉄工所 | Bearing for molten metal bath |
| JPH0669495U (en) * | 1993-03-16 | 1994-09-30 | 帝人製機株式会社 | Eccentric differential reducer |
| JPH07317756A (en) * | 1994-05-23 | 1995-12-08 | Sando Iron Works Co Ltd | Submerged bearing |
| JP4888993B2 (en) * | 2005-07-12 | 2012-02-29 | 株式会社コエックス | Inscribed planetary gear mechanism (involute reduction mechanism) |
| JP2009144533A (en) * | 2007-12-11 | 2009-07-02 | Mitsubishi Heavy Ind Ltd | Wind turbine generator |
-
2009
- 2009-12-02 JP JP2009274773A patent/JP5256181B2/en active Active
-
2010
- 2010-12-02 CN CN201080051092.6A patent/CN102667238B/en not_active Expired - Fee Related
- 2010-12-02 WO PCT/JP2010/071588 patent/WO2011068160A1/en active Application Filing
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2008038941A (en) * | 2006-08-02 | 2008-02-21 | Sumitomo Heavy Ind Ltd | Eccentric swing gear unit |
| WO2008096747A1 (en) * | 2007-02-05 | 2008-08-14 | Sumitomo Heavy Industries, Ltd. | Power transmission device and method of producing the same |
| WO2009025206A1 (en) * | 2007-08-20 | 2009-02-26 | Sumitomo Heavy Industries, Ltd. | Output gear-equipped reduction device and method of assembling the same |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2011117521A (en) | 2011-06-16 |
| WO2011068160A1 (en) | 2011-06-09 |
| JP5256181B2 (en) | 2013-08-07 |
| CN102667238A (en) | 2012-09-12 |
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