CN110030276B - Lubricating structure of rolling bearing - Google Patents
Lubricating structure of rolling bearing Download PDFInfo
- Publication number
- CN110030276B CN110030276B CN201811540338.0A CN201811540338A CN110030276B CN 110030276 B CN110030276 B CN 110030276B CN 201811540338 A CN201811540338 A CN 201811540338A CN 110030276 B CN110030276 B CN 110030276B
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- oil
- rolling bearing
- oil guide
- shaft
- space
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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
- F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
- F16C33/6659—Details of supply of the liquid to the bearing, e.g. passages or nozzles
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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
- F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
- F16C33/6659—Details of supply of the liquid to the bearing, e.g. passages or nozzles
- F16C33/6677—Details of supply of the liquid to the bearing, e.g. passages or nozzles from radial inside, e.g. via a passage through the shaft and/or inner ring
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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
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/042—Guidance of lubricant
- F16H57/043—Guidance of lubricant within rotary parts, e.g. axial channels or radial openings in shafts
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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
- F16H57/0467—Elements of gearings to be lubricated, cooled or heated
- F16H57/0469—Bearings or seals
- F16H57/0471—Bearing
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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
- F16H57/048—Type of gearings to be lubricated, cooled or heated
- F16H57/0487—Friction gearings
- F16H57/0489—Friction gearings with endless flexible members, e.g. belt CVTs
Abstract
The invention provides a lubricating structure of a rolling bearing, which can stably supply oil to a pair of rolling bearings supporting two ends of a rotating shaft. The oil guide plate (59) is provided with: a cylindrical insertion portion (59a) which is pressed into an oil passage (23a) of the rotating shaft (23); and an oil guide portion (59b) that is expanded in a funnel shape from one end side of the insertion portion (59a) to the space (60), and a gap (alpha) that guides oil in the space (60) to the 1 st rolling bearing (21) is formed between an outer peripheral portion of the oil guide portion (59b) and an inner wall surface (12b) of the housing (12) that defines the space (60), so that even if an oil surface of the oil in the space (60) drops, the oil can be supplied to the 1 st rolling bearing (21) through the gap (alpha) without any trouble, and the oil can be smoothly guided to the oil passage (23a) of the reduction shaft (23) by the oil guide portion (59b) expanded in the funnel shape and supplied to the 2 nd rolling bearing (22).
Description
Technical Field
The present invention relates to a lubricating structure for a rolling bearing, in which one end portion and the other end portion of a rotating shaft are supported by a 1 st rolling bearing and a 2 nd rolling bearing, respectively, in a housing, an oil passage penetrates through the rotating shaft in an axial direction, and oil supplied to a space facing the one end portion of the rotating shaft is guided to the 1 st rolling bearing and the oil passage by an oil guide plate provided at the one end portion of the rotating shaft, and is guided from the oil passage to the 2 nd rolling bearing.
Background
The following structure is known from patent document 1 below: the shaft end portion of the drive shaft is supported by the knuckle via the ball bearing, the outer peripheral portion of an annular oil guide plate (seal portion) is sandwiched and fixed between the knuckle and the outer ring of the ball bearing, and an annular gap is formed between the inner peripheral portion of the oil guide plate and the outer peripheral surface of the drive shaft, whereby foreign matter contained in lubricating oil supplied to the ball bearing along the outer peripheral surface of the drive shaft is captured by the oil guide plate.
Documents of the prior art
Patent document
Patent document 1: japanese laid-open patent publication No. 2009-115257
Disclosure of Invention
Problems to be solved by the invention
However, in the above-described conventional configuration, the outer peripheral portion of the oil guide plate is sandwiched and fixed between the knuckle and the outer ring of the ball bearing, and a gap is formed between the inner peripheral portion of the oil guide plate and the outer peripheral surface of the drive shaft, so that when the flow rate of oil supplied along the outer peripheral surface of the drive shaft decreases, only the lower half portion of the drive shaft and the oil guide plate enters the oil. In this state, the oil supplied along the outer peripheral surface of the lower half portion of the drive shaft needs to be supplied to the ball bearing across the lower half portion of the oil guide plate, and therefore there is a problem that the supply of the oil to the ball bearing becomes unstable.
The present invention has been made in view of the above circumstances, and an object thereof is to stabilize the supply of oil to a pair of rolling bearings that support both end portions of a rotating shaft.
Means for solving the problems
In order to achieve the above object, according to the invention described in claim 1, there is provided a lubricating structure for a rolling bearing in which one end portion and the other end portion of a rotating shaft are supported by a first rolling bearing and a second rolling bearing, respectively, a housing, an oil passage penetrates through the rotating shaft in an axial direction, and oil supplied to a space where the one end portion of the rotating shaft faces is guided to the first rolling bearing and the oil passage by an oil guide plate provided at the one end portion of the rotating shaft, and is guided from the oil passage to the second rolling bearing, the oil guide plate comprising: a cylindrical insertion portion that is press-fitted into the oil passage; and an oil guide portion that expands in a funnel shape from one end side of the insertion portion toward the space, and a gap that guides oil in the space to the 1 st rolling bearing being formed between an outer peripheral portion of the oil guide portion and an inner wall surface of the housing that defines the space.
Further, according to the invention described in claim 2, in addition to the structure of claim 1, there is provided a lubrication structure of a rolling bearing, wherein the 1 st rolling bearing and the 2 nd rolling bearing are tapered roller bearings.
Further, according to the invention described in claim 3, in addition to the structure of claim 1 or 2, a lubricating structure of a rolling bearing is proposed, wherein a contact portion that comes into contact with an axial end surface on one end side of the rotating shaft is formed in the oil guide portion.
Further, according to the invention described in claim 4, in addition to the structure described in any one of claims 1 to 3, there is provided a lubricating structure for a rolling bearing, characterized in that a blocking portion for narrowing a flow passage of oil is formed by bending the other end portion of the insertion portion radially inward.
The right housing 11 and the intermediate housing 12 of the embodiment correspond to the housing of the present invention, the 1 st tapered roller bearing 21 and the 2 nd tapered roller bearing 22 of the embodiment correspond to the rolling bearing of the present invention, and the reduction shaft 23 of the embodiment corresponds to the rotating shaft of the present invention.
Effects of the invention
According to the structure of claim 1, one end portion and the other end portion of the rotating shaft are supported by the housing by the 1 st rolling bearing and the 2 nd rolling bearing, respectively, and the oil passage penetrates through the rotating shaft in the axial direction. The oil supplied into the space where the one end portion of the rotating shaft faces is guided to the 1 st rolling bearing and the oil passage by the oil guide plate provided at the one end portion of the rotating shaft, and is guided from the oil passage to the 2 nd rolling bearing.
The oil guide plate is provided with: a cylindrical insertion portion that is press-fitted into the oil passage; and an oil guide portion that expands in a funnel shape from one end side of the insertion portion toward the space, and a gap that guides oil in the space to the 1 st rolling bearing is formed between an outer peripheral portion of the oil guide portion and an inner wall surface of the housing that defines the space, so that even if an oil surface of the oil in the space drops, the oil can be supplied to the 1 st rolling bearing through the gap without any trouble, and the oil can be smoothly guided to the oil passage of the reduction shaft by the oil guide portion that expands in the funnel shape and supplied to the 2 nd rolling bearing. Since the oil guide plate is fixed to the reduction shaft by pressing the insertion portion into the oil passage, the preload of the 1 st rolling bearing and the preload of the 2 nd rolling bearing are not affected.
According to the structure of claim 2, when the 1 st rolling bearing and the 2 nd rolling bearing are tapered roller bearings, the variation in the preload may adversely affect the rotation resistance or the durability, but since it is not necessary to sandwich and fix the oil deflector between the housing and the outer ring, the variation in the preload due to the plate thickness fluctuation of the oil deflector can be avoided.
Further, according to the configuration of claim 3, since the oil guide portion is formed with the abutting portion that abuts against the axial end surface on the one end side of the rotary shaft, when the insertion portion of the oil guide plate is press-fitted into the oil passage of the rotary shaft, not only can the press-fitting depth be fixed to improve the assembly accuracy, but also the assembly posture of the oil guide plate with respect to the rotary shaft can be stabilized.
Further, according to the structure of claim 4, since the other end portion of the insertion portion is bent radially inward to form the blocking portion that narrows the flow path of the oil, the ratio of the amount of oil supplied to the 1 st rolling bearing to the amount of oil supplied to the 2 nd rolling bearing can be adjusted with a simple structure.
Drawings
Fig. 1 is a longitudinal sectional view of a belt type continuously variable transmission.
Fig. 2 is an enlarged view of part 2 of fig. 1.
Fig. 3 is an enlarged view of a portion 3 of fig. 2.
Fig. 4 is a diagram showing a comparative example corresponding to fig. 3.
Description of the reference symbols
11: a right housing (case);
12: a middle case (housing);
12 b: an inner wall surface;
21: the 1 st tapered roller bearing (the 1 st rolling bearing);
22: a 2 nd tapered roller bearing (2 nd rolling bearing);
23: a deceleration shaft (rotation shaft);
23 a: an oil passage;
23 d: a shaft end face;
59: an oil guide plate;
59 a: an insertion portion;
59 b: an oil guide part;
59 c: an abutting portion;
59 d: a blocking section;
60: a space;
α: a gap.
Detailed Description
Embodiments of the present invention will be described below with reference to fig. 1 to 4.
As shown in fig. 1, the belt type continuously variable transmission T for a vehicle includes a right housing 11, an intermediate housing 12, and a left housing 13, a main shaft 16 is supported by the intermediate housing 12 and the left housing 13 via ball bearings 14 and 15, respectively, a sub shaft 20 is supported by the right housing 11, the intermediate housing 12, and the left housing 13 via ball bearings 17, ball bearings 18, and roller bearings 19, respectively, and a reduction shaft 23 is supported by the intermediate housing 12 and the right housing 11 via a 1 st tapered roller bearing 21 and a 2 nd tapered roller bearing 22, respectively. The right end of the input shaft 24, whose left end outer periphery is fitted to the right end inner periphery of the main shaft 16 so as to be relatively rotatable, is coaxially opposed to the left end of the crankshaft 25 of the engine E at the opening of the right housing 11.
A torque converter 26 is disposed inside the right housing 11 so as to surround the outer periphery of the right end of the input shaft 24, a forward/reverse switching mechanism 27 formed of a planetary gear mechanism is disposed inside the intermediate housing 12 so as to surround the outer periphery of the fitting portion between the input shaft 24 and the main shaft 16, and an oil pump 28 is disposed adjacent to the radially outer side of the forward/reverse switching mechanism 27.
The forward/reverse switching mechanism 27 includes a ring gear, a sun gear, a carrier, a forward clutch 43, and a reverse brake 44, the ring gear, which is an input member of the forward/reverse switching mechanism 27, is connected to the input shaft 24, which is an output member of the torque converter 26, and the sun gear, which is an output member of the forward/reverse switching mechanism 27, is connected to the main shaft 16. When the forward clutch 43 is engaged, the ring gear is coupled to the sun gear, and the input shaft 24 is directly connected to the main shaft 16, thereby establishing a forward drive gear. When the reverse brake 44 is engaged, the carrier is restrained from rotating, and the rotation of the ring gear is reversed and transmitted to the sun gear, so that the reverse travel gear is established.
An annular metal belt 31 is wound around a drive pulley 29 provided on the outer periphery of the main shaft 16 and a driven pulley 30 provided on the outer periphery of the sub shaft 20 inside the intermediate housing 12. The drive pulley 29 includes a fixed pulley half body 29a and a movable pulley half body 29b that can be moved toward and away from the fixed pulley half body 29a, and the groove width can be controlled by the hydraulic pressure acting on the oil chamber 32. Similarly, the driven pulley 30 includes a fixed pulley half 30a and a movable pulley half 30b that can be moved toward and away from the fixed pulley half 30a, and the groove width can be controlled by the hydraulic pressure acting on the oil chamber 33.
A differential gear 36 is supported by the right housing 11 and the intermediate housing 12 via tapered roller bearings 34 and 35, respectively. The 1 st reduction gear 37 provided on the counter shaft 20 meshes with the 2 nd reduction gear 38 provided on the reduction shaft 23, and the final drive gear 39 provided on the reduction shaft 23 meshes with the final driven gear 40 provided on the outer periphery of the differential gear 36. Left and right drive shafts 41, 42 extending leftward and rightward from the differential gear 36 are connected to left and right wheels.
Therefore, when the rotation of the crankshaft 25 of the engine E is transmitted from the torque converter 26 to the main shaft 16 via the input shaft 24 and the forward-reverse switching mechanism 27, the rotation of the main shaft 16 is transmitted from the drive pulley 29 to the counter shaft 20 via the metal belt 31 and the driven pulley 30. At this time, if the groove width of the drive pulley 29 is widened and the groove width of the driven pulley 30 is narrowed, the gear ratio is continuously changed to the LO side, and conversely, if the groove width of the drive pulley 29 is narrowed and the groove width of the driven pulley 30 is widened, the gear ratio is continuously changed to the OD side.
The rotation of the counter shaft 20 is transmitted to the left and right wheels through a path of the 1 st reduction gear 37 → the 2 nd reduction gear 38 → the reduction shaft 23 → the final drive gear 39 → the final driven gear 40 → the differential gear 36 → the drive shafts 41, 42.
As shown in fig. 2 and 3, the reduction shaft 23 is a hollow shaft having a 2 nd reduction gear 38 spline-coupled to the left outer periphery thereof and a final drive gear 39 integrally formed on the right outer periphery thereof, and has an oil passage 23a axially penetrating therethrough.
The 1 st tapered roller bearing 21 that supports the left end of the reduction shaft 23 to the intermediate housing 12 includes: an inner ring 51 fitted in contact with the stepped portion 23b at the left end of the reduction shaft 23; an outer ring 52 fitted in abutment with the step portion 12a of the inner surface of the intermediate housing 12; a plurality of tapered rollers 53 disposed between the inner ring 51 and the outer ring 52; and a retainer 54 that retains the plurality of tapered rollers 53 at predetermined intervals.
The 2 nd tapered roller bearing 22 that supports the right end of the reduction shaft 23 in the right housing 11 has the same structure as the 1 st tapered roller bearing 21, and includes: an inner ring 55 fitted in contact with the stepped portion 23c at the right end of the reduction shaft 23; an outer ring 56 fitted in abutment with the step portion 11a of the inner surface of the right housing 11; a plurality of tapered rollers 57 disposed between the inner ring 55 and the outer ring 56; and a retainer 58 that retains the plurality of tapered rollers 57 at predetermined intervals.
The 1 st tapered roller bearing 21 and the 2 nd tapered roller bearing 22 are angular bearings capable of supporting not only a load in the radial direction but also a load in the thrust direction, and the 1 st tapered roller bearing 21 supports a thrust load that biases the speed reduction shaft 23 leftward, and the 2 nd tapered roller bearing 22 supports a thrust load that biases the speed reduction shaft 23 rightward.
An oil guide plate 59 for guiding lubricating oil to the 1 st tapered roller bearing 21 and the 2 nd tapered roller bearing 22 is provided at the left end portion of the reduction shaft 23. The oil guide plate 59 is a member of a rotary body shape formed by press-working a metal plate, and includes: a cylindrical insertion portion 59 a; and an oil guide portion 59b that flares from the left end of the insertion portion 59a toward the space 60 in the middle housing 12. The oil guide portion 59b of the oil guide plate 59 is provided with an abutment portion 59c capable of abutting against the left shaft end surface 23d of the reduction shaft 23, and the right end of the insertion portion 59a of the oil guide plate 59 is bent radially inward to form a shut-off portion 59d that narrows the flow passage of the oil.
The oil guide plate 59 is fixed to a position where the abutting portion 59c abuts against the shaft end surface 23d of the reduction shaft 23 by press-fitting the insertion portion 59a from the left end of the oil passage 23a of the reduction shaft 23. In this state, an annular gap α is formed between the outer peripheral portion of the oil guide portion 59b of the oil guide plate 59 and the inner wall surface 12b of the intermediate housing 12, and this gap α faces the left side surface of the 1 st tapered roller bearing 21.
A circular recess 11b is formed in the inner surface of the right housing 11 facing the right end portion of the reduction shaft 23, and this recess 11b faces the right side surface of the 2 nd tapered roller bearing 22.
Oil from an oil pump, not shown, is supplied to the space 60 (see fig. 1) of the intermediate housing 12 via an oil passage 13a formed inside the left housing 13 and an oil passage 12c formed inside the intermediate housing 12, and flows from there to the reduction shaft 23 side, thereby lubricating the 1 st tapered roller bearing 21 and the 2 nd tapered roller bearing 22.
Fig. 4 shows a comparative example of the present embodiment, and the structure other than the oil guide plate 59' is the same as that of the present embodiment.
That is, the oil guide plate 59' of the comparative example includes: a cylindrical insertion portion 59 e; and an annular oil guide portion 59f extending radially outward while being bent from one end side of the insertion portion 59 e. The oil deflector 59' is sandwiched and fixed between the step portion 12a of the intermediate housing 12 and the outer ring 52 of the 1 st tapered roller bearing 21. An annular projection 23e that projects radially inward is formed on one end side of the oil passage 23a of the reduction shaft 23, an annular gap β is formed between an insertion portion 59e inserted into the oil passage 23a and the annular projection 23e, and a plurality of oil holes 59g that face the 1 st tapered roller bearing 21 are formed at a radially intermediate position of the oil guide portion 59 f.
According to the comparative example having the above configuration, the oil supplied to the space 60 through the oil passage 13a of the left housing 13 and the oil passage 12c of the intermediate housing 12 flows to the right toward the oil guide plate 59 ', and a part thereof passes through the oil holes 59g formed in the oil guide portion 59f of the oil guide plate 59', thereby lubricating the 1 st tapered roller bearing 21. Another part of the oil supplied to the space 60 is supplied from the insertion portion 59e of the oil guide plate 59' to the oil passage 23a of the reduction shaft 23, from there through the gap β between the annular protrusion 23e of the oil passage 23a and the insertion portion 59e, to the 1 st tapered roller bearing 21, and collides with the recess 11c of the right housing 11 through the outlet of the oil passage 23a, thus changing the 180 ° direction to lubricate the 2 nd tapered roller bearing 22.
However, in the above comparative example, when the oil level of the oil in the space 60 is lowered and becomes lower than the lowest oil hole 59g, in order to supply the oil in the space 60 to the 1 st tapered roller bearing 21 and the 2 nd tapered roller bearing 22, the oil must be raised along the wall surface of the oil guide portion 59f that stands vertically and reach the oil hole 59g and the insertion portion 59e, and therefore the supply of the oil to the 1 st tapered roller bearing 21 and the 2 nd tapered roller bearing 22 may become unstable.
Further, since the outer peripheral portion of the oil guide portion 59f of the oil guide plate 59' is sandwiched and fixed between the step portion 12a of the intermediate housing 12 and the outer ring 52 of the 1 st tapered roller bearing 21, the load pressing the outer ring 52 of the 1 st tapered roller bearing 21 to the right side is changed by the plate thickness variation of the oil guide portion 59f, and the preload of the 1 st tapered roller bearing 21 is changed. When the preload of the 1 st tapered roller bearing 21 changes, the axial pressing load transmitted from the 1 st tapered roller bearing 21 via the speed reduction shaft 23 changes, and therefore the preload of the 2 nd tapered roller bearing 22 also changes. As a result, rolling resistance and durability of the 1 st and 2 nd tapered roller bearings 21 and 22 may be adversely affected.
However, according to the present embodiment shown in fig. 3, since the gap α that communicates the space 60 with the 1 st tapered roller bearing 21 is formed between the outer peripheral portion of the oil guide portion 59b of the oil guide plate 59 and the inner wall surface 12b of the intermediate housing 12, even if the oil level of the oil in the space 60 drops, the oil is smoothly supplied to the 1 st tapered roller bearing 21 through the lower portion of the gap α.
Further, even if the oil level of the oil in the space 60 falls, the oil guide portion 59b of the oil guide plate 59 is expanded in a funnel shape toward the space 60, so the oil flowing toward the oil guide plate 59 in the space 60 is guided by the oil guide portion 59b to be smoothly supplied to the oil passage 23a of the reduction shaft 23, and from there to the 2 nd tapered roller bearing 22.
Further, the oil deflector 59 is not sandwiched and fixed between the step portion 12a of the intermediate housing 12 and the outer ring 52 of the 1 st tapered roller bearing 21, but is fixed by press-fitting the insertion portion 59a into the oil passage 23a of the reduction shaft 23, so that the oil deflector 59 does not affect the preload of the 1 st tapered roller bearing 21 and the 2 nd tapered roller bearing 22.
Further, if the total opening area of the gap α in the present embodiment is set equal to the sum of the total opening area of the oil hole 59g and the total opening area of the gap β in the comparative example, the amount of oil supplied to the 1 st tapered roller bearing 21 when the space 60 is filled with oil can be set to be the same as in the comparative example.
Further, in the oil guide plate 59 of the present embodiment, when the insertion portion 59a is inserted into the oil passage 23a of the reduction shaft 23, the abutment portion 59c abuts against the shaft end surface 23d, and therefore, not only can the insertion portion 59a be inserted to a fixed depth to improve the assembly accuracy, but also the inclination of the oil guide plate 59 can be prevented to stabilize the assembly posture.
Further, since the distal end portion of the insertion portion 59a is bent to form the block portion 59d, the flow rate of the oil flowing through the oil passage 23a can be adjusted with a simple configuration, and the ratio of the amount of oil supplied to the 1 st tapered roller bearing 21 to the amount of oil supplied to the 2 nd tapered roller bearing 22 can be adjusted. Further, it is not necessary to form the oil hole 59g in the oil guide portion 59b (see fig. 4) and to form the annular projection 23e in the speed reduction shaft 23 (see fig. 4), so that the manufacturing cost can be reduced.
The embodiments of the present invention have been described above, but various design changes can be made in the present invention without departing from the scope of the invention.
For example, the rolling bearing of the present invention is not limited to the roller bearing of the embodiment, and may be a ball bearing or a needle bearing.
The rotating shaft of the present invention is not limited to the reduction shaft 23 of the belt type continuously variable transmission T of the embodiment.
Claims (5)
1. A lubricating structure of a rolling bearing, wherein one end portion and the other end portion of a rotating shaft (23) are supported by a 1 st rolling bearing (21) and a 2 nd rolling bearing (22) respectively in housings (11, 12), an oil passage (23a) penetrates in the rotating shaft (23) in the axial direction, oil supplied into a space (60) where the one end portion of the rotating shaft (23) faces is guided to the 1 st rolling bearing (21) and the oil passage (23a) by an oil guide plate (59) provided at the one end portion of the rotating shaft (23), and is guided from the oil passage (23a) to the 2 nd rolling bearing (22),
the lubricating structure of the rolling bearing is characterized in that,
the oil guide plate (59) is provided with: a cylindrical insertion portion (59a) that fixes the oil guide plate (59) to the rotary shaft (23) by being press-fitted into the oil passage (23 a); and an oil guide portion (59b) that widens in a funnel shape from one end side of the insertion portion (59a) toward the space (60), wherein a gap (α) that guides oil in the space (60) to the 1 st rolling bearing (21) is formed between an outer peripheral portion of the oil guide portion (59b) and an inner wall surface (12b) of the housing (12) that defines the space (60).
2. The lubrication structure of a rolling bearing according to claim 1,
the 1 st rolling bearing (21) and the 2 nd rolling bearing (22) are tapered roller bearings.
3. The lubrication structure of a rolling bearing according to claim 1 or 2,
an abutting portion (59c) that abuts against a shaft end surface (23d) on one end side of the rotating shaft (23) is formed in the oil guide portion (59 b).
4. The lubrication structure of a rolling bearing according to claim 1 or 2,
the other end of the insertion section (59a) is bent radially inward to form a blocking section (59d) that narrows the oil flow path.
5. The lubrication structure of a rolling bearing according to claim 3,
the other end of the insertion section (59a) is bent radially inward to form a blocking section (59d) that narrows the oil flow path.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2018-003085 | 2018-01-12 | ||
| JP2018003085A JP6612903B2 (en) | 2018-01-12 | 2018-01-12 | Rolling bearing lubrication structure |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN110030276A CN110030276A (en) | 2019-07-19 |
| CN110030276B true CN110030276B (en) | 2021-03-26 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201811540338.0A Active CN110030276B (en) | 2018-01-12 | 2018-12-17 | Lubricating structure of rolling bearing |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP6612903B2 (en) |
| CN (1) | CN110030276B (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102021104473A1 (en) | 2021-02-25 | 2022-08-25 | Bayerische Motoren Werke Aktiengesellschaft | Hollow shaft device with passive liquid supply and drive device with hollow shaft device |
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| JPS57137767A (en) * | 1981-02-20 | 1982-08-25 | Nissan Motor Co Ltd | Lubricator for inside of gear |
| JP2572699B2 (en) * | 1992-06-04 | 1997-01-16 | 株式会社荏原製作所 | Bearing lubrication structure for rotating machinery |
| DE4418693C1 (en) * | 1994-05-28 | 1995-03-23 | Ford Werke Ag | Planet-carrier arrangement with an annular oil baffle plate |
| JP4197267B2 (en) * | 2003-04-18 | 2008-12-17 | 本田技研工業株式会社 | Drive shaft support structure for gear case of ship propulsion unit |
| JP5045497B2 (en) * | 2008-02-29 | 2012-10-10 | 日産自動車株式会社 | Electric drive |
| JP2014514227A (en) * | 2011-05-09 | 2014-06-19 | オーチス エレベータ カンパニー | Seal assembly for bearing assembly |
| CN202327031U (en) * | 2011-08-22 | 2012-07-11 | 江阴克威齿轮箱制造有限公司 | Oil return lubrication structure for speed reducer |
| JP2014173658A (en) * | 2013-03-08 | 2014-09-22 | Honda Motor Co Ltd | Oil guide plate |
-
2018
- 2018-01-12 JP JP2018003085A patent/JP6612903B2/en not_active Expired - Fee Related
- 2018-12-17 CN CN201811540338.0A patent/CN110030276B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR20040033980A (en) * | 2002-10-16 | 2004-04-28 | 현대자동차주식회사 | Lubricating structure of manual transmission |
| CN103403399A (en) * | 2010-11-26 | 2013-11-20 | 株式会社利富高 | Lubricating-oil collection guide |
| CN104603503A (en) * | 2012-08-20 | 2015-05-06 | 舍弗勒技术股份两合公司 | Plug-in shaft system, differential with plug-in shaft system, oil conduit system in shaft systems of transmissions, and steel oil drip pan for oiling shaft |
| WO2017162242A1 (en) * | 2016-03-23 | 2017-09-28 | Schaeffler Technologies AG & Co. KG | Planet drive with at least one planet carrier, planet gears, planet pins and a lubricating device |
Also Published As
| Publication number | Publication date |
|---|---|
| CN110030276A (en) | 2019-07-19 |
| JP6612903B2 (en) | 2019-11-27 |
| JP2019124237A (en) | 2019-07-25 |
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