CN102374237B - Retainer for roller and oscillating internally meshing gear device - Google Patents
Retainer for roller and oscillating internally meshing gear device Download PDFInfo
- Publication number
- CN102374237B CN102374237B CN201110196207.7A CN201110196207A CN102374237B CN 102374237 B CN102374237 B CN 102374237B CN 201110196207 A CN201110196207 A CN 201110196207A CN 102374237 B CN102374237 B CN 102374237B
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- Prior art keywords
- roller
- retainer
- recess
- union body
- radial direction
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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
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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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/46—Cages for rollers or needles
- F16C33/4617—Massive or moulded cages having cage pockets surrounding the rollers, e.g. machined window cages
- F16C33/4623—Massive or moulded cages having cage pockets surrounding the rollers, e.g. machined window cages formed as one-piece cages, i.e. monoblock cages
- F16C33/4635—Massive or moulded cages having cage pockets surrounding the rollers, e.g. machined window cages formed as one-piece cages, i.e. monoblock cages made from plastic, e.g. injection moulded window cages
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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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/66—Special parts or details in view of lubrication
- F16C33/6603—Special parts or details in view of lubrication with grease as lubricant
- F16C33/6629—Details of distribution or circulation inside the bearing, e.g. grooves on the cage or passages in the rolling elements
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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
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/042—Guidance of lubricant
- F16H57/0427—Guidance of lubricant on rotary parts, e.g. using baffles for collecting lubricant by centrifugal force
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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
- F16H2001/323—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 comprising eccentric crankshafts driving or driven by a gearing
Abstract
The present invention provides a retainer for maintaining high strength and further enhancing lubricating property of a roller, and an oscillating internally meshing gear device which is provided with the retainer and has high lubricating property. A plurality of rollers (60, 62) is maintained by the retainer (34, 35). The retainer comprises a pair of first and second ring bodies (34A, 34B), two end positions for positioning the rollers (60, 62), and a connector (34C) for connecting the first and second ring bodies (34A, 34B) and positioning circumferential positions of the rollers (60, 62). Recesses (34E, 34F) acting as channel of lubricant are formed on the axial middle part of the connector (34C), the radial size L6 of a base end part (34C1) of the connector (34C), which is adjacent with the first and second ring bodies (34A, 34B) is larger than the radial size L7 of the part of forming the recesses (34E, 34F).
Description
Technical field
The application advocates the preference of No. 2010-176571st, the Japanese patent application based on application on August 5th, 2010.The full content of its application is by referring to being applied in this specification.
The retainer that the present invention relates to a kind of roller and the oscillating internal engagement type gearing being assembled with this retainer.
Background technique
Oscillating internal engagement type gearing is disclosed in patent documentation 1.In this gearing, while external gear swings, internal messing is in internal gear.Multiple roller is configured with between external gear and the eccentric body making this external gear swing.Multiple roller is kept by retainer.Holder has: a pair ring body, specifies the plurality of roller end positions separately; And union body, connect this pair ring body and specify the circumferential locations of described multiple roller.
This oscillating internal engagement type gearing possesses multiple external gear, and is assembled with multiple roller (and retainer) respectively corresponding to each external gear.The adjacent ring body of each retainer contacts each other.In this patent documentation 1, about 2 retainers that this is adjacent, imagination sets the imaginary circle ring body specified by the union body of the 1st retainer and the imaginary circle ring body specified by the union body of the 2nd retainer, on this basis, the size of the union body of 2 retainers is set in the mode overlapping throughout the circumferential from these 2 imaginary circle ring bodies during end on observation.
In patent documentation 1, by this structure, even if when applying torque to gearing and the roller kept by the retainer of a side is about to, the union body also by its adjacent retainer bears and stops this torque to suppress the inclination of this roller.
Patent documentation 1: Japanese Patent Publication 2010-32000 publication (Fig. 3)
In the oscillating internal engagement type gearing possessing multiple external gear, gearing disclosed in patent documentation 1, is configured the axially locating of the roller between each eccentric body and external gear usually by the ring body contact each other of retainer.
But each roller and retainer (owing to being configured at the periphery of eccentric body) thereof, when the axle being provided with this eccentric body often rotates one time, the degree that the distance apart from the axle center of this axle changes only is equivalent to offset.Therefore, in order to the ring body continuous contact all the time each other that can make the retainer adjoined, the size (width) of the radial direction of ring body has to correspondingly become large., there is oiling agent and be difficult to enter from ring body gap each other and be difficult to the problem of the lubrication of carrying out roller swimmingly and so in its result.
Especially, gearing disclosed in patent documentation 1, when retainer for being formed in the mode preventing ring body from tilting by the stiffening effect of union body, adjacent ring body surface of contact each other maintains all the time by the state closely pressed.Therefore there is oiling agent to be difficult to enter roller side further and the worry that reduces further of lubricity.
Summary of the invention
The present invention completes to solve this problem in the past, its problem be to provide a kind of maintain the stable retention performance of roller and high strength while can improve the retainer of the lubricity of roller further and be assembled with the oscillating internal engagement type gearing of high lubricating property of this retainer.
The present invention solves above-mentioned problem by being set to following structure, a kind of retainer keeping multiple roller, and it possesses: a pair ring body, locates described multiple roller end positions separately; And union body, link this pair ring body and locate the circumferential locations of described multiple roller, wherein, described union body axially intermediate portion is formed with the recess of the passage becoming oiling agent, and the radial dimension being adjacent to the base end part of described ring body of described union body is greater than the radial dimension of the part being formed with described recess.
If reduce the size (length) of the ring body of retainer or the radial direction of union body, then there is the tendency that the stability that the lubricity of roller uprises further, roller keeps declines further.Retainer involved in the present invention is formed with the recess of the passage becoming oiling agent at axial intermediate portion.Its result, (because the size of the radial direction of union body entirety can maintain suitable size) can keep roller with stable state, and because oiling agent can be passed through recess, so can guarantee high-lubricity.
Further, in the present invention, the radial dimension being adjacent to the base end part of ring body of union body must be formed as the radial dimension being greater than the part being formed with this recess.Accordingly, can relax stress and concentrate on the described base end part of the union body that intensity aspect is strict with, (although being formed with recess) also can prevent the intensity of retainer entirety from declining.
In addition, as this recess forming position described in " axial intermediate portion " necessarily do not mean axial middle position, also can from central position deviation.Further, the formation number of recess is not limited to 1 yet.And then recess can be formed at the radial direction outer circumferential side of union body, also can be formed at inner circumferential side, the radial direction both sides of union body can also be formed at.
When the present invention is applied to the maintenance of the roller between eccentric body and external gear being configured in oscillating internal engagement type gearing, especially can play its original function.
Invention effect
According to the present invention, the retainer that can improve the lubricity of roller while maintaining the stable retention performance of roller and high strength further can be obtained, and be assembled with the oscillating internal engagement type gearing of high lubricating property of this retainer.
Accompanying drawing explanation
Fig. 1 is the overall synoptic diagram of the oscillating internal engagement type gearing of the retainer involved by an example being assembled with embodiments of the present invention.
Fig. 2 is the major component enlarged view near the retainer of Fig. 1.
Fig. 3 represents that this retainer keeps the stereogram of the state of roller.
Fig. 4 represents that this retainer keeps the sectional view amplified near the union body of the state of roller.
Fig. 5 is the magnified partial view that the union body of this retainer exists the square with the axis cross section of the part of claw.
Fig. 6 is the stereogram of the external gear of this gearing.
Fig. 7 is the disrumpent feelings plan view (A) in the local of the retainer involved by an example of other mode of execution of the present invention and side view (B).
Fig. 8 is the sectional view that the major component of Fig. 7 is amplified.
Fig. 9 is the magnified partial view of the retainer observing Fig. 7 inside radial direction.
Figure 10 is the overall synoptic diagram of other gearing of the retainer being assembled with Fig. 7.
In figure: 10-gearing, 12,14-eccentric body, 16,18-external gear, 20-internal gear, 22-input shaft, 34,35-retainer, 34A, 34B, 35A, 35B-the 1st, the 2nd ring body, 34C-union body, 34C1-base end part, 34E, 34F-recess, 34G, 34H-claw, 36-shell, 42,44-the 1st, the 2nd flange, 60,62-roller.
Embodiment
Below, an example of embodiments of the present invention is described with reference to the accompanying drawings in detail.
Fig. 1 is the overall synoptic diagram of the oscillating internal engagement type gearing of the retainer involved by an example being assembled with embodiments of the present invention.First, the brief configuration of this gearing of simple declaration.
This gearing 10 is in the gearing being called as oscillating internal engagement type of internal gear 20 by external gear 16,18 internal messing of eccentric body 12,14 swing rotary.
The input shaft 22 of gearing 10 is formed with small gear 24.Small gear 24 engages with 3 distribution gear 28A ~ 28C (only illustrating eccentric shaft 26A, distribution gear 28A respectively in Fig. 1) of 3 eccentric shaft 26A ~ 26C simultaneously.Each eccentric shaft 26A ~ 26C is formed with respectively described eccentric body 12,14.The periphery of each eccentric body 12,14 configures multiple roller 60,62, with chimeric state group, external gear 16,18 is housed in the periphery of the plurality of roller 60,62.Retainer 34,35 involved by embodiments of the present invention is applied to the multiple rollers 60,62 (aftermentioned) keeping being configured between this eccentric body 12,14 and external gear 16,18.
External gear 16,18 internal messing is in internal gear 20.The number of teeth of external gear 16,18 is only less than internal gear 20.Internal gear 20 is integrated with 36 one-tenth, shell.
Each eccentric shaft 26A ~ 26C is supported on the 1st, the 2nd flange 42,44 by roller bearing 38,40.1st flange 42 and the 2nd flange 44 pass through link from the outstanding wheel support body 44A of the 2nd flange 44 one and bolt 46 or become integrated.1st, the 2nd flange 42,44 of integration is supported on described shell 36 respectively by the 1st, the 2nd angular contact ball bearing 48,50.
In addition, be arranged in parallel with 2 external gears 16,18 in this example in the axial direction, the eccentric phase of each external gear 16,18 departs from 180 degree.As shown in Figure 1, Figure 2 and shown in Fig. 6, in 2 external gears 16,18, in order to ensure the space of the axial dimension amount of accommodation the 2nd ring body 34B of retainer 34 described later and the 1st ring body 35A of retainer 35, inside the radial direction of external tooth 16A, 18A, be formed with teat 16B, 18B.Thus, guarantee more greatly the facewidth L1 of the external tooth of external gear 16,18, and rationally held the part of the 2nd ring body 34B of holding part 34 and the 1st ring body 35A of retainer 35 in the space between the external gear 16,18 guaranteed in the existence because of this teat 16B, 18B.
In addition, the inner space of gearing 10 is airtight by oil sealing 54 etc., and is sealed with lubricating grease (oiling agent).
The effect of this gearing 10 of simple declaration.
If input shaft 22 rotates, then 3 eccentric shaft 26A ~ 26C are rotated to equidirectional with identical speed by small gear 24 and 3 distribution gear 28A ~ 28C.Thus, swing rotary limit, external gear 16, the 18 limit internal messing of each eccentric body 26A ~ 26C is embedded in internal gear 20.Because external gear 16,18 number of teeth is only less than internal gear 20, if so swing limit, external gear 16,18 limit internal messing is in internal gear 20, then each external gear 16,18 with produce slowly stable relative rotation between internal gear 20.
At this, if internal gear 20 (and shell 36) is fixed, now, eccentric shaft 26A ~ 26C and axle center O1 of around gearing 10 synchronous with the rotation composition of external gear 16,18 revolves round the sun.Export thereby, it is possible to take out to slow down from the 1st, the 2nd flange 42,44 rotated along with this revolution.On the contrary, if the rotation of external gear 16,18 (revolution of eccentric shaft 26A ~ 26C) is limited, now, due to internal gear 20 sideway swivel, rotate export therefore, it is possible to take out so-called frame from the shell 36 integrated with this internal gear 20 one-tenth.
Below the structure near described retainer 34,35 is described in detail.
Fig. 2 is the major component enlarged view near the retainer 34,35 of Fig. 1.Apparent from the description of Fig. 1, Fig. 2, in this mode of execution, 2 retainers 34,35 keep multiple roller 60,62 respectively and have identical shape.Therefore, in the following description as being not particularly limited, be then only be conceived to retainer 34 side be described.
In addition, Fig. 3 represents that retainer 34 keeps the stereogram of the state of roller 60.Fig. 4 represents that retainer 34 keeps the sectional view amplified near the union body of the state of roller 60.
Retainer 34 is formed by the resin comprising glass fibre, have a pair the 1st of the axial end positions specifying multiple roller 60, the 2nd ring body 34A, 34B and link these a pair the 1st, the union body 34C of the 2nd ring body 34A, 34B.The content of glass fibre is 35% in the present embodiment.In addition, as present embodiment, in the structure that retainer 34 (35) is rubbing against one another, especially in order to prevent the abrasion of the 2nd ring body 34B (35B) of this retainer 34 (35), the content of glass fibre is preferably 10 ~ 40%, is especially preferably 25 ~ 40%.Union body 34C is by specifying the circumferential locations of each roller 60 between the circumferencial direction that is positioned at (being kept by retainer 34) roller 60.
The size of the radial direction of the 1st, the 2nd ring body 34A, 34B of retainer 34 is L2, and the size of the radial direction of union body 34C is L3.This size L2, L3 are can with fully stable state location or the size keeping roller 60.
In union body 34C, axially intermediate portion is formed with totally 2 and become recess 34E, 34F of the passage of oiling agent.In this mode of execution, the radial direction outer circumferential side of union body 34C is configured with recess 34E, and inner circumferential side is configured with recess 34F.2 recesses 34E, 34F are formed at the position of axially mutually departing from.In this mode of execution, as shown in Figure 3, further by alternately assembling union body 34C turningly, recess 34E and 34E of the union body 34C adjoined and recess 34F and 34F also can be made to become the state axially departed from.
In recess 34E, 34F, the shape comprising the cross section of axle center O1 becomes truncated cone shape.It is to prevent the stress that transition occurs in the bight on the base of recess 34E, 34F from concentrating that the sectional shape of recess 34E, 34F becomes truncated cone shape.In order to avoid the decline of intensity, the degree of depth d1 of recess 34E, 34F all becomes the more shallow size of the pitch circle P1 not exceeding roller 60.Replace, axial formation length L4 ensures 2 ~ 3 of degree of depth d1 times and is designed to make oiling agent fully pass through.
But the shape of recess is not necessarily truncated cone shape, such as, can be that U-shaped also can for semicircle.Further, this example center dant 34E, 34F only form 1 at the outer circumferential side of union body 34C and inner circumferential side respectively, also can form more than 2.Forming position is also not limited to the position of this example.And then the degree of depth of recess 34E and 34F can be different, and the degree of depth of recess 34E (or 34F) also can corresponding each union body 34C and different.
In this retainer 34, the radial dimension L6 being adjacent to the base end part 34C1 of the 1st, the 2nd ring body 34A, 34B of union body 34C becomes the size of the radial dimension L7 being greater than the part being formed with recess 34E, 34F.This is the intensity near the base end part in order to fully guarantee easy concentrated stress.
Further, inside the radial direction of union body 34C and the end in outside be formed with claw 34G, 34H of preventing roller 60 from coming off respectively.This claw 34G, 34H in this embodiment not throughout union body 34C entire axial length and formed, and be formed in an axial part, specifically be formed in from the base end part 34C1 being adjacent to the 1st, the 2nd ring body 34A, 34B of union body 34C to axially a little away from position, the end inside the radial direction of union body 34C and the end outside radial direction form a pair claw 34G and 34H respectively.That is, the base end part 34C1 of union body 34C and axial central part 34C6 is not formed with claw.
The size (height of formation) of the claw 34G of the end inside radial direction is H1, and the size (height of formation) of the claw 34H of the end outside radial direction is for being a bit larger tham the H2 (H2 > H1) of H1.According to the setting of this size, inside the radial direction of retainer 34, (make claw 34G resiliently deformable) by applying some power and be pressed into each roller 60, thus this claw 34G can be crossed be assembled in retainer 34.
As shown in phantom in Figure 5, roller 60 moves to radial direction between claw 34G, 34H with the state kept by union body 34C, and this moving range Lm is set greater than the eccentric amount e (with reference to Fig. 2) (Lm > e) of described eccentric body 12,14.
In addition, as shown in Figure 2,2 retainers 34,35 contact with each other, and be sandwiched in described 1st, the 2nd flange 42,44 carry out axially locating by liner 64,66.In addition, retainer 34,35 does not directly nuzzle up each other, such as, also can make to clip plate between each retainer 34,35.
Secondly, the effect of the retainer 34 involved by this mode of execution is described.
Oscillating internal engagement type gearing 10 involved according to the present embodiment, multiple roller 60,62 is configured between eccentric body 12,14 and external gear 16,18, alleviates slip resistance when external gear 16,18 swings in the periphery of eccentric body 12,14.
Be conceived to retainer 34 side, multiple roller 60 specifies its axial position by the 1st, the 2nd ring body 34A, 34B of retainer 34, and specifies the position of circumferencial direction by union body 34C.In this mode of execution, the size of the radial direction of the 1st, the 2nd ring body 34A, 34B of retainer 34 is set as (larger) L2, and the size of the radial direction of union body 34C is also set as (larger) L3.Therefore, it is possible to fully stable state location or maintenance roller 60.And, even in the reduction speed ratio of gearing 10 lower and the eccentric amount e of eccentric body 12,14 is larger, 1st, the size L2 of the radial direction of the 2nd ring body 34A, 34B also can ensure corresponding size, so the 1st ring body 35A of the 2nd ring body 34B of adjacent retainer 34 and retainer 35 all the time with the contact of stable state continuance, and can suitably can carry out the axially locating of retainer 34,35.
At this, in union body 34C, the outer circumferential side of its axial intermediate portion and inner circumferential side are formed with recess 34E and recess 34F respectively.Therefore (even if the 1st of retainer 34 the, size L2, the L3 of the radial direction of the 2nd ring body 34A, 34B and union body 34C formed significantly), passed through at this recess 34E, 34F by oiling agent, combine with the rotation of roller 60 itself, oiling agent can spread all over the complete cycle of roller 60 well.Especially in this embodiment, these 2 recesses 34E, 34F are formed at the position of axially mutually departing from, further, by alternately assembling each union body 34C turningly, recess 34E and 34E and recess 34F and 34F of adjacent union body 34C also become the state axially departed from.Thus, oiling agent also easily to circumference or move axially, and can improve lubricity further.
Further, in this mode of execution, the radial dimension L6 being adjacent to the base end part 34C1 of the 1st, the 2nd ring body 34A, 34B of union body 34C becomes the size of the radial dimension L7 being greater than the part being formed with recess 34E, 34F.Therefore, it is possible to the intensity near the base end part 34C1 fully guaranteeing easy concentrated stress.
Further, in this mode of execution, claw 34G, 34H of union body 34C are not formed throughout the entire axial length of union body 34C, but are only formed at a part for the axis of union body 34C.In particular, claw is not formed with at the axial central part 34C6 place of the base end part 34C1 adjoined with the 1st, the 2nd ring body 34A, 34B and roller 60.Therefore, oiling agent can more freely move to the axis of roller 60 and the whole surface of circumferencial direction, and can improve lubricity further.But, such as, when more preferably considering intensity, claw can be formed throughout entire axial length.
In addition, the retainer 34 in present embodiment and retainer 35 are contacted with each other by the 2nd adjacent ring body 34B, 35B and carry out mutual axially locating.Easily there are the 2nd ring body 34B, 35B wearing and tearing each other in this position structure, but in this mode of execution, because forming retainer 34 (35) by the resin of the glass fibre comprising 35%, so durability can be guaranteed well.And, in particular, due to present embodiment be by the 2nd adjacent ring body 34B, 35B between contact carry out the structure of mutual axially locating, and it is identical with the conventional art described, in fact the structure of imaginary circle ring body in complete cycle overlap is, and lubricating condition is not good, so can be better by the effect of the well-formed ground lubrication roller 60 (62) of present embodiment.
And, in this mode of execution, claw 34G, 34H be formed at from the base end part 34C1 of the union body 34C adjoined with the 1st, the 2nd ring body 34A, 34B to axially a little away from position, i.e. this base end part 34C1 and between recess 34E, 34F, so this claw 34G, 34H play a role as reinforcement (reinforcement).That is, while this claw 34G, 34H enhancing durability aspect itself requires the base end part 34C1 of strict union body 34C, recess 34E, 34F upper stress can be stoped to concentrate the impact brought directly to be passed to base end part 34C1 side.
In addition, because of the existence of claw 34G, 34H, also can easily carry out the assembling of roller 60 to retainer 34.In this mode of execution, the size (height of formation) of the claw 34G inside radial direction is H1, and the size (height of formation) of the claw 34H outside radial direction is for being a bit larger tham the H2 (H2 > H1) of H1.According to the setting of this size, inside the radial direction of retainer 34, (make claw 34G resiliently deformable) be pressed into each roller 60 by applying power, thus this claw 34G can be crossed be assembled in retainer 34.Assembled roller 60 outside radial direction (because the claw 34H in outside is larger) also can not fly away from.Further, if the claw 34G crossing inner side is assembled in retainer 34 by disposable for roller 60, then this roller 60 (so long as not with strength and make it drop inside radial direction wittingly) can not come off from retainer 34.
Further, in this mode of execution, roller 60 is set greater than the eccentric amount e of eccentric body 12,14 to the range L m of radial direction movement with the state being held in union body 34C.Therefore, when so the retainer 34 (35) being assembled with roller 60 being assembled in the periphery of eccentric body 12,14 of gearing 10,2 retainers 34 (35) both sides can be assembled from axial phase the same side (make roller 60 or 62 to radial direction movement while).Therefore, it is possible to easily the retainer 34 (35) being assembled with the state of roller 60 (62) is assembled in gearing 10.
In addition, in this mode of execution, in order to maximum improve lubricity and adjacent all recess 34E (34F) staggered in the axial direction, but this structure not necessarily, such as, on multiple adjacent union body, recess 34E (34F) can be formed with in axial same position.Further, the axial position of recess 34E (34F) can change every 2 union bodies or 3 union bodies in the circumferential.Its result, as long as the position that the recess being formed in arbitrary adjacent union body departs from each other vertically, then (compared with the situation being formed at axial same position with whole recess) can improve lubricity further.
The example of other mode of executions of the present invention shown in Fig. 7 ~ Fig. 9.
Fig. 7 is the plan view and side view that represent that the local that other retainers involved by present embodiment is assembled with the state of roller is disrumpent feelings, and Fig. 8 is the sectional view that the major component of Fig. 7 is amplified, and Fig. 9 is the arrow IX direction line view of Fig. 7 of this retainer.
Retainer 70 involved by this mode of execution is also identical with mode of execution before, possesses the 1st, the 2nd ring body 70A, 70B and union body 70C.Further, the radial dimension L8 being adjacent to the base end part 70C1 of the 1st, the 2nd ring body 70A, 70B of union body 70C is greater than the radial dimension L9 of the part being formed with recess 70E.But, in this mode of execution, be only formed with the recess 70E of 1 wider width at the central part of axis as recess.In addition, as variation, also can form the recess of identical wide cut in outer circumferential side (or) on outer circumferential side also.
And, as shown in Figure 9, the circumferential thickness D2 that the union body 70C of the retainer 70 in this mode of execution is formed as the region comprising recess 70E is greater than the circumferential thickness D1 (D1 < D2) being adjacent to the base end part 70C1 of the 1st, the 2nd ring body 70A, 70B of union body 70C.That is, its circumferential thickness of union body 70C is not constant (circumferential thickness changes in the axial direction) in the axial direction.This means that union body 70C and roller 76 also anisotropically contact at axial integral, but the part that roller 76 is only thicker in the circumferential with union body 70C (thickness beyond base end part 70C1 is D2 part) contacts.In other words, relatively there is a little gap between the base end part 70C1 of union body 70C that formed of unfertile land and roller 76 in the circumferential.Can be acted on as follows according to this structure.
That is, when keeping roller 76 by the union body 70C of retainer 70, if because some reason roller 76 is by deflection (spin axis of roller 76 is for tilting), then the end of roller 76 produces the excessive stresses being called as what is called " edge load ".But, in this mode of execution, the circumferential thickness D1 of the base end part 70C1 of union body 70C is less than the circumferential thickness D2 in the region comprising recess 70E, and near this base end part 70C1, (and the gap between roller 76) can keep oiling agent comfortably, so be difficult to this edge load occurs.
And, even if its result roller 76 deflection a little, the phenomenon that the slip resistance of roller 76 end increases with this deflection is not almost had yet, so deflection (due to Fast Convergent deflection) can not be encouraged because of the increase of this slip resistance, therefore, it is possible to extremely round and smooth and stably keep roller 76.
And then, in this mode of execution, relative broad range throughout axis is formed with recess 70E, but because be formed with the region (D1 < D2) comprising this recess 70E compared with base end part 70C1 relatively thickly, even if so the recess 70E forming wide cut also can guarantee the intensity of the union body 70C comprising this recess 70E part fully.In addition, in this mode of execution, comprise recess 70E and throughout the scope wider than the axial range of this recess 70E to form its circumferential thickness D2 with the circumferential thickness D1 making it be greater than base end part 70C1.But, when more preferably considering lubricity, such as, also only the axial range identical with recess can be formed as the circumferential thickness being greater than base end part.Further, also can only the scope (only by a part for the axial range of recess) being narrower than the axial range of recess be formed as to be greater than the circumferential thickness of base end part.And then, such as, during intensity in the base end part that relatively more misgivings and ring body adjoin, the circumferential thickness in the region comprising recess also can be made to be less than base end part.In a word, the setting (changing method) of the thickness of the circumferencial direction axially of union body may not link with the position of recess, also on the bases such as the position of the length of the radial direction of the base end part of consideration union body, recess, shape, axial extent or the radial direction degree of depth, suitably can set according to the relation between the intensity wanting to guarantee or edge load.
In addition, for other structures of the concrete structure of claw 70G, 70H of comprising for keeping roller 76 in the radial direction, because substantially identical with mode of execution before, so omit repeat specification.
But in the present invention, the concrete structure for the device being assembled with retainer is not particularly limited.Shown in Figure 10, the retainer 70 of Fig. 7 ~ Fig. 9 is assembled in the example of the gearing 110 involved by other structures.This gearing 110 is also oscillating internal engagement type gearing.But, the small gear 124 of the small gear 24 be equivalent in the mode of execution of Fig. 1 and 3 distribution gear 28A ~ 28C and 3 distribution gear 128A ~ 128C (only illustrating distribution gear 128A in Figure 10) are configured at the axially central authorities (not the axial side of gearing 110) of 2 external gears 116,118.Therefore, 2 retainers 70,70 can not directly contact, but contact with the sidepiece of distribution gear 128A ~ 128C respectively.
Gearing involved by the mode of execution of other structures and Fig. 1 ~ Fig. 6 is before identical.Therefore, the symbol that two digits is identical with the mark of the mode of execution of Fig. 1 after same or similar part is added, and omit repeat specification.
In addition, in the present invention, if apply retainer when being assembled in this oscillating internal engagement type gearing, then can obtain significant effect, but be not necessarily defined in and be applied to oscillating internal engagement type gearing, as long as comprise axle and be embedded in the device of the gomphosis part on the periphery of this axle by the multiple rollers kept by retainer, just various device can be applied to.Such as, also can be applied on the retainer keeping the roller be configured between the planet pin of simple planetary gear device and planetary pinion.
Claims (11)
1. the retainer of a roller, its by the 1st external gear of the 1st eccentric body swing rotary and by the 2nd external gear internal messing of the 2nd eccentric body swing rotary in the oscillating internal engagement type gearing of internal gear, keep the multiple rollers be arranged between described 1st eccentric body and the 1st external gear and between described 2nd eccentric body and the 2nd external gear, it is characterized in that possessing:
A pair ring body, locates described multiple roller end positions separately; And
Union body, links this pair ring body and locates the circumferential locations of described multiple roller,
Described union body axially intermediate portion is formed with the recess of the passage becoming oiling agent, and,
The radial dimension being adjacent to the base end part of described ring body of described union body is greater than the radial dimension of the part being formed with described recess,
Described recess is formed at the radial direction outer circumferential side of described union body, and has the degree of depth along radial direction,
The described recess being formed at radial direction outer circumferential side of the described union body adjoined each other is formed at the position offset vertically each other,
In inner end and the outboard end of the radial direction of described union body, be formed with the claw preventing described roller from coming off,
Described roller is greater than the offset of described 1st eccentric body and the 2nd eccentric body between described claw to the scope of radial direction movement with the state kept by described union body.
2. the retainer of a roller, its by the 1st external gear of the 1st eccentric body swing rotary and by the 2nd external gear internal messing of the 2nd eccentric body swing rotary in the oscillating internal engagement type gearing of internal gear, keep the multiple rollers be arranged between described 1st eccentric body and the 1st external gear and between described 2nd eccentric body and the 2nd external gear, it is characterized in that possessing:
A pair ring body, locates described multiple roller end positions separately; And
Union body, links this pair ring body and locates the circumferential locations of described multiple roller,
Described union body axially intermediate portion is formed with the recess of the passage becoming oiling agent, and,
The radial dimension being adjacent to the base end part of described ring body of described union body is greater than the radial dimension of the part being formed with described recess,
Described recess is formed at the radial direction inner circumferential side of described union body, and has the degree of depth along radial direction,
The described recess being formed at radial direction inner circumferential side of the described union body adjoined each other is formed at the position offset vertically each other,
In inner end and the outboard end of the radial direction of described union body, be formed with the claw preventing described roller from coming off,
Described roller is greater than the offset of described 1st eccentric body and the 2nd eccentric body between described claw to the scope of radial direction movement with the state kept by described union body.
3. the retainer of roller as claimed in claim 1 or 2, is characterized in that,
Described recess is formed at radial direction inner circumferential side and the outer circumferential side both sides of described union body.
4. the retainer of roller as claimed in claim 1 or 2, is characterized in that,
Described recess is formed as the size of the pitch circle not exceeding described roller.
5. the retainer of roller as claimed in claim 3, is characterized in that,
Described recess is formed as the size of the pitch circle not exceeding described roller.
6. the retainer of roller as claimed in claim 1 or 2, is characterized in that,
Described claw is only formed at a part for the axis of described union body.
7. the retainer of roller as claimed in claim 1 or 2, is characterized in that,
Described claw throughout the axis of described union body total length and formed.
8. the retainer of roller as claimed in claim 1 or 2, is characterized in that,
The circumferential thickness of described union body changes in the axial direction.
9. the retainer of roller as claimed in claim 8, is characterized in that,
The thickness comprising the circumference in the region of described recess is greater than the thickness being adjacent to the circumference of the base end part of described ring body of described union body.
10. the retainer of roller as claimed in claim 1 or 2, is characterized in that,
Described retainer is formed by the resin comprising glass fibre.
11. 1 kinds of oscillating internal engagement type gearings, by the external gear internal messing of eccentric body swing rotary in internal gear, is characterized in that,
Retainer according to any one of claim 1 to 10 is possessed as keeping the retainer of the multiple rollers be configured between described eccentric body and external gear.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2010-176571 | 2010-08-05 | ||
| JP2010176571A JP5492700B2 (en) | 2010-08-05 | 2010-08-05 | Roller retainer and swinging intermeshing gear device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102374237A CN102374237A (en) | 2012-03-14 |
| CN102374237B true CN102374237B (en) | 2015-04-15 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201110196207.7A Active CN102374237B (en) | 2010-08-05 | 2011-07-11 | Retainer for roller and oscillating internally meshing gear device |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP5492700B2 (en) |
| CN (1) | CN102374237B (en) |
| DE (1) | DE102011109191B4 (en) |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5973855B2 (en) * | 2012-09-13 | 2016-08-23 | ナブテスコ株式会社 | Gear transmission and crankshaft structure used therefor |
| JP5988429B2 (en) * | 2012-09-18 | 2016-09-07 | ナブテスコ株式会社 | Eccentric oscillating gear unit |
| JP6334289B2 (en) * | 2014-06-24 | 2018-05-30 | ナブテスコ株式会社 | Gear transmission |
| JP2019039549A (en) * | 2017-08-29 | 2019-03-14 | 日本電産シンポ株式会社 | transmission |
| JP7301641B2 (en) * | 2019-07-09 | 2023-07-03 | ナブテスコ株式会社 | Decelerator |
| JP2021067316A (en) * | 2019-10-23 | 2021-04-30 | ナブテスコ株式会社 | Speed reducer |
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| CN2781067Y (en) * | 2004-12-01 | 2006-05-17 | 徐国利 | Assembling cage for II kind bearing |
| CN201368121Y (en) * | 2009-03-13 | 2009-12-23 | 洛阳轴研科技股份有限公司 | Cylindrical roller bearing and solid retainer thereof |
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| DE1748426U (en) | 1953-10-06 | 1957-07-11 | Steatit Magnesia Ag | BEARING CAGE FOR BALL OR ROLLER BEARINGS. |
| DE1198623B (en) | 1958-04-01 | 1965-08-12 | Leipziger Kugellagerfabrik Dkf | Device for lubricating a needle and roller bearing |
| JPS469601Y1 (en) * | 1967-01-18 | 1971-04-05 | ||
| DE9111111U1 (en) * | 1991-09-07 | 1991-11-07 | Skf Gmbh, 8720 Schweinfurt, De | |
| JP2912532B2 (en) * | 1993-09-30 | 1999-06-28 | エヌティエヌ株式会社 | Needle roller with cage |
| JP3651812B2 (en) * | 1995-09-11 | 2005-05-25 | 光洋精工株式会社 | Synthetic resin cage for roller bearings |
| JP2002310162A (en) | 2001-04-11 | 2002-10-23 | Ntn Corp | Roller device with holder and planetary gear drive using it |
| JP2009047294A (en) * | 2007-08-23 | 2009-03-05 | Ntn Corp | Roller bearing for reduction gear |
| JP5069629B2 (en) * | 2008-07-30 | 2012-11-07 | ナブテスコ株式会社 | Eccentric oscillation gear device and roller bearing |
| JP5300369B2 (en) * | 2008-08-12 | 2013-09-25 | Ｎｔｎ株式会社 | Roller with cage |
| JP2010176571A (en) | 2009-01-30 | 2010-08-12 | Dmc:Kk | Touch panel |
| JP5654798B2 (en) | 2010-07-30 | 2015-01-14 | 住友重機械工業株式会社 | Roller retainer and swinging intermeshing gear device |
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2010
- 2010-08-05 JP JP2010176571A patent/JP5492700B2/en active Active
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2011
- 2011-07-11 CN CN201110196207.7A patent/CN102374237B/en active Active
- 2011-08-02 DE DE102011109191.6A patent/DE102011109191B4/en active Active
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2781067Y (en) * | 2004-12-01 | 2006-05-17 | 徐国利 | Assembling cage for II kind bearing |
| CN201368121Y (en) * | 2009-03-13 | 2009-12-23 | 洛阳轴研科技股份有限公司 | Cylindrical roller bearing and solid retainer thereof |
Also Published As
| Publication number | Publication date |
|---|---|
| JP5492700B2 (en) | 2014-05-14 |
| JP2012036947A (en) | 2012-02-23 |
| DE102011109191B4 (en) | 2021-11-04 |
| CN102374237A (en) | 2012-03-14 |
| DE102011109191A1 (en) | 2012-02-09 |
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