CN117940685A - Shell-shaped roller bearing and fixing structure of shell-shaped roller bearing - Google Patents
Shell-shaped roller bearing and fixing structure of shell-shaped roller bearing Download PDFInfo
- Publication number
- CN117940685A CN117940685A CN202280061402.5A CN202280061402A CN117940685A CN 117940685 A CN117940685 A CN 117940685A CN 202280061402 A CN202280061402 A CN 202280061402A CN 117940685 A CN117940685 A CN 117940685A
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- China
- Prior art keywords
- outer ring
- shell
- roller bearing
- main body
- housing
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 230000002093 peripheral effect Effects 0.000 claims abstract description 5
- 229910001234 light alloy Inorganic materials 0.000 claims description 7
- 230000003247 decreasing effect Effects 0.000 claims description 3
- 238000005452 bending Methods 0.000 description 7
- 238000005096 rolling process Methods 0.000 description 5
- 238000003825 pressing Methods 0.000 description 4
- 229910052782 aluminium Inorganic materials 0.000 description 3
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 3
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical compound [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 description 2
- 229910052751 metal Inorganic materials 0.000 description 2
- 239000002184 metal Substances 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 229910045601 alloy Inorganic materials 0.000 description 1
- 239000000956 alloy Substances 0.000 description 1
- 238000000137 annealing Methods 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 238000005255 carburizing Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000012447 hatching Effects 0.000 description 1
- 230000006698 induction Effects 0.000 description 1
- 229910052742 iron Inorganic materials 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000010791 quenching Methods 0.000 description 1
- 230000000171 quenching effect Effects 0.000 description 1
- 239000013585 weight reducing agent Substances 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
- F16C19/44—Needle bearings
- F16C19/46—Needle bearings with one row or needles
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/58—Raceways; Race rings
-
- 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
- F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
- F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
- F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
- F16C35/067—Fixing them in a housing
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Rolling Contact Bearings (AREA)
- Mounting Of Bearings Or Others (AREA)
Abstract
The housing outer ring (11) is provided with a cylindrical outer ring main body (12) which is pressed and fixed to the opening of the axle box, and a flange part (14) which protrudes from the axial end part of the outer ring main body to the inner diameter side, wherein a conical surface (15) is arranged on the outer peripheral surface of one axial end part of the outer ring main body, and the cone angle theta of the conical surface (15) is included in the range of 0.5 degrees to less than 5 degrees.
Description
Technical Field
The present invention relates to a shell outer ring of a shell-shaped roller bearing which receives radial load.
Background
As a shell-shaped needle roller bearing to be inserted into a compressor for an air conditioner of an automobile, conventionally, for example, as described in japanese patent application laid-open No. 2008-038986 (patent document 1), a shell-shaped needle roller bearing including a shell outer ring, a cage to be inserted into an inner diameter side of the shell outer ring, and a needle roller as a rolling element to be held by the cage is known. In the case outer ring of patent document 1, both axial end portions located on the axially outer side are folded back 180 ° toward the inner diameter side. The outer peripheral surfaces of both axial end portions are formed in a tapered shape. These taper angles are 5 degrees to 25 degrees. For this reason, when the taper angle is 5 to 25 degrees, the introduction of the guide opening is guided by the taper surface, and therefore, tilting or scoring of the outer ring of the case when the outer ring of the case is pressed into the opening of the case can be suppressed, and smooth assembly can be performed using a general-purpose tool. When the taper angle is less than 5 degrees, the fitting width at the time of pressing the housing outer ring into the opening of the housing cannot be sufficiently ensured, and the stability of the housing outer ring with respect to the housing becomes insufficient.
Prior art literature
Patent literature
Patent document 1: japanese patent laid-open No. 2008-038986
Disclosure of Invention
Problems to be solved by the invention
With recent demands for weight reduction, light alloy-based axleboxes mainly composed of aluminum or the like are often used as axleboxes into which shell-shaped needle bearings are pressed. The risk of occurrence of scratches on the outer ring of the case is increased in the light alloy-based axlebox as compared with the iron-based axlebox. As a countermeasure against scratches, patent document 1 proposes to apply a taper of 5 degrees or more and 25 degrees or less to the outer periphery of the end portion in the axial direction of the housing outer ring, but when a taper of 5 degrees or more is applied, the axial dimension of the housing outer ring in contact with the axle box is inevitably reduced, that is, the end portion in the axial direction of the housing outer ring is separated from the axle box, and a sufficient fixing force is not obtained, which may cause the housing needle bearing to come off from the axle box depending on the temperature conditions.
Thus, in order to avoid the falling off, there is a method of providing a negative gap to increase the interference, but this increases the risk of scratches. Therefore, further improvement from patent document 1 is required.
In view of the above, an object of the present invention is to provide a structure capable of preventing scratches at the time of press-fitting when the housing outer ring is fixed to the axle housing, and capable of firmly fixing the housing outer ring to the axle housing.
Means for solving the problems
For this purpose, the shell-shaped roller bearing of the present invention is provided with a shell outer ring, a cage inserted into the shell outer ring, and rollers held by the cage and rolling on the inner diameter surface of the shell outer ring. The housing outer ring includes a cylindrical outer ring main body press-fitted and fixed to an opening of the axle box, and flange portions protruding from both axial end portions of the outer ring main body toward an inner diameter side, and tapered surfaces having an outer diameter gradually decreasing from an inner side toward an outer side in the axial direction are provided on an outer peripheral surface of one axial end portion of the outer ring main body, and a taper angle of the tapered surfaces is included in a range of 0.5 degrees or more and less than 5 degrees.
According to the present invention, since the tapered surface is formed to be gentle as compared with the conventional one, the tapered surface of the outer ring of the housing is brought into surface contact with the inner diameter surface of the opening by pressing the outer ring of the housing into the opening of the axle box. This ensures a contact area between the housing outer ring and the axle housing, and the housing outer ring is firmly pressed into and fixed to the axle housing. In addition, the outer ring of the shell is led into the opening by the conical surface without inclination, thereby preventing scratches. The tapered surface having an outer diameter gradually decreasing from the inside toward the outside in the axial direction is a tapered shape having an outer diameter that decreases toward the axial end as viewed from the center in the axial direction. The tapered surface is provided on at least one of the axially opposite ends of the outer ring of the case, which is pressed in. That is, the tapered surfaces may be provided at both axial end portions of the outer ring of the case, or may be provided only at either end.
The thickness of the flange portion is not particularly limited, but in the case of bending the edge portion of the cylindrical body to form the flange portion, the flange portion is preferably thin in order to ensure ease of bending processing. However, in order to ensure rigidity for introduction into the opening by press fitting, the flange portion is preferably thick. In one embodiment of the present invention, the thickness of the flange portion provided at one end portion of the outer ring main body in the axial direction is included in a range of 40% to 75% of the thickness of the outer ring main body. According to such a configuration, both ease of bending and rigidity for securing press-fitting can be satisfied.
In a preferred embodiment of the present invention, the outer end surface in the axial direction of the flange portion and the tapered surface are connected via a chamfer formed at one end in the axial direction of the outer ring main body, the axial dimension of the outer ring of the case is 6mm or more, and the total of the axial dimension of the tapered surface and the axial dimension of the chamfer is included in a range of 1.5mm or more and 3.5mm or less. According to such a configuration, the easiness of press-fitting and the securing of the contact area can be achieved.
The radial dimension of the tapered surface is not particularly limited, but as a further preferred embodiment of the present invention, the radial dimension of the tapered surface is included in a range of 1.1 to 1.5 times the interference obtained by subtracting the inner diameter radius of the opening from the outer diameter radius of the housing outer ring. According to such a configuration, scratches can be prevented and a contact area can be ensured.
The fixing structure of the shell-shaped roller bearing of the present invention includes the above-described shell outer ring, a cage inserted into the shell outer ring, rollers held by the cage and rolling on an inner diameter surface of the outer ring main body, and an axle housing having an opening of an inner diameter dimension smaller than an outer diameter dimension of the shell outer ring and an inner diameter surface of the opening being closely contacted with the outer diameter surface of the outer ring main body in a negative gap. As an aspect of the present invention, the axle housing is formed of a light alloy. The light alloy is, for example, a light metal such as aluminum or an alloy containing a light metal such as aluminum as a main component.
ADVANTAGEOUS EFFECTS OF INVENTION
According to the present invention, it is possible to prevent scratches of the axlebox and firmly fix the shell-shaped roller bearing to the axlebox.
Drawings
Fig. 1 is a longitudinal sectional view showing a shell-shaped roller bearing of an embodiment of the present invention.
Fig. 2 is a longitudinal sectional view showing the embodiment press-fitted and fixed to the axle box.
Fig. 3 is an enlarged sectional view showing an upper left side portion of the paper surface of the housing outer ring in fig. 1.
Fig. 4 is an enlarged cross-sectional view showing a right side portion of a paper surface upper portion of the case outer race in fig. 1.
Fig. 5 is an enlarged cross-sectional view showing a right side portion of a paper surface upper portion of the case outer ring in fig. 1.
Detailed Description
Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying drawings. Fig. 1 is a longitudinal sectional view showing a shell-shaped roller bearing of an embodiment of the present invention. Fig. 2 is a longitudinal sectional view showing the embodiment pressed and fixed to the opening of the axle box. The shell-shaped roller bearing 10 includes a shell outer ring 11, a cage 21, and rollers 31, and is press-fitted and fixed to an opening 41 of the axlebox 40 as shown in fig. 2. In order to avoid complicating the drawings, the cross-sectional views of fig. 1 to 5 show patterns in cross-section that are not shown.
The case outer ring 11 is an integral body and includes an outer ring main body 12 and flange portions 13 and 14. The flange portion 13 is raised at substantially 90 degrees from one axial end of the cylindrical outer ring main body 12 toward the inner diameter side. The outer ring main body 12 has a plate thickness substantially equal to that of the flange portion 13, or the flange portion 13 has a large plate thickness. The flange portion 14 is raised at substantially 90 degrees from the other end of the cylindrical outer ring main body 12 in the axial direction toward the inner diameter side. The flange portion 14 has a smaller plate thickness than the outer ring main body 12. Substantially 90 degrees means that the angle of the flange portion 14 may have a difference of 90±10 degrees with respect to the outer ring main body 12.
The flange portion 14 is formed by gradually bending the other edge of the cylindrical material toward the inner diameter side in the axial direction, and is also referred to as an edge bending portion. In order to ensure ease of bending, the plate thickness of the flange portion 14 is a predetermined value in a range of 40% to 75% inclusive of the plate thickness in the axial center region of the outer ring main body 12.
A retainer 21 and rollers 31 are disposed between the pair of flange portions 13, 14. The outer diameter of the retainer 21 is larger than the inner diameter of the flange 13 and/or the flange 14. The cylindrical retainer 21 is inserted into the inner diameter side of the housing outer ring 11, and is restrained from moving in the axial direction by the flange portions 13 and 14. A plurality of pockets 22 are formed in the retainer 21 at intervals in the circumferential direction. The rollers 31 are disposed in the pockets 22, and the rollers 31 are held by roller stoppers (not shown) formed in the retainer 21 so as to prevent the rollers from falling off. The rollers 31 are, for example, needle rollers, and roll on the inner diameter surface 12c of the outer ring main body 12. Therefore, the inner diameter surface 12c of the outer ring main body 12 corresponds to the outer raceway surface.
Fig. 3 is an enlarged cross-sectional view showing one end portion in the axial direction of the flange portion 13 of the case outer ring and the outer ring main body 12. One axial end of the outer ring main body 12 is formed into a gentle taper surface 15. The taper angle θ of the taper surface 15 is a predetermined angle included in a range of 0.5 degrees or more and less than 5 degrees. Regarding the inward flange 13, the outer end surface 13b of the flange 13 and the tapered surface 15 form an R portion 16 having an arc-shaped cross section. The R portion 16 is a chamfer of a convex curved surface, and smoothly connects with the outer end surface 13b and the tapered surface 15. As shown in fig. 3, the axial position of the R portion 16 is included in the axial position of the flange portion 13. In contrast, the axial position of the tapered surface 15 overlaps the axial positions of the flange portion 13 and the outer ring main body 12. The flange portion 14, the tapered surface 15, and the R portion 16 are also the same in the other axial direction.
Referring to fig. 4, a recessed portion 18 in the shape of an annular groove is formed in the inner peripheral surface of the other end portion in the axial direction of the outer ring main body 12. The recess 18 is set back on the outer diameter side from the inner diameter surface 12 c. The surface of the recess 18 is connected to the inner diameter surface 12c on the inner side in the axial direction, and is connected to the inner end surface of the flange 14 on the outer side in the axial direction. By the recessed portion 18, formation of the flange portion 14 by bending processing becomes easy.
Since the case outer ring 11 is press-fitted and fixed to the opening 41 having a circular cross section as shown in fig. 2, the outer diameter dimension of the case outer ring 11 in the original state before press-fitting and fixing is slightly larger than the inner diameter dimension of the opening 41 in the original state, and the difference in the dimension of the negative clearance is referred to as an interference region S, and is shown by hatching on the outer diameter portion of the outer ring main body in fig. 1, 3 to 5. The interference area S is occupied from one end to the other end of the outer ring main body 12 in the axial direction over the entire circumference, and overlaps the tapered surface 15.
However, according to the present embodiment, since the taper angle θ of the taper surface 15 is a predetermined value of 0.5 degrees or more and less than 5 degrees, the taper angle is relaxed as compared with the conventional one, and as shown in fig. 2, the interference area S is sufficiently ensured from one end to the other end in the axial direction of the housing outer ring 11. According to the present embodiment, the contact area between the housing outer ring 11 and the axlebox 40 is widened, and the housing outer ring 11 is fixed to the axlebox 40. Thus, the possibility of the housing outer race 11 coming off from the axle housing 40 is eliminated.
Further, since the present embodiment has the tapered surface 15, even in the case where the axle housing 40 is made of a light alloy, scratches of the axle housing 40 are prevented when the shell roller bearing 10 is pressed into the opening 41.
Incidentally, as shown in fig. 1, the axial dimension Ls of the case outer ring 11 of the present embodiment is 8mm or more. Referring to FIG. 4, in order to secure a contact area, the total Lq of the axial dimension of the tapered surface 15 on one side and the axial dimension of the R portion 16 is recommended to be 2.0.ltoreq.Lq.ltoreq.3.5 mm. The reason for this is that in the case where Lq < 2.0mm, scratches at the time of pressing may be generated. In addition, when Lq > 3.5mm, the contact area becomes insufficient, and the housing outer ring 11 falls off from the axle housing 40.
For the same reason, lq < 2.0mm is recommended in the case of Ls < 8 mm.
Based on this embodiment, when ls.gtoreq.6 mm, lq.ltoreq.1.5 mm is recommended.
In the embodiment shown in fig. 4, it can be appreciated that the interference area S reaches the R portion 16. That is, the relation between the radius Rs of the interference S and the radius Rt of the tapered surface 15 is satisfied
[ Formula 1] Rt/Rs < 1.0.
Here, the radial dimension Rs of the interference S is a value of half of the difference between the inner diameter dimension of the axlebox 40 and the outer diameter dimension of the outer ring main body 12. The radial dimension Rt of the tapered surface 15 is a value of the radial distance between the tapered generatrix and the point P, Q at which the outer diameter surface 17 and the R portion 16 of the outer ring main body 12 intersect.
According to equation 1, when the shell roller bearing 10 is pressed into the opening 41, the tapered surface 15 contacts the inner diameter surface of the opening 41, and the contact area of the shell outer ring 11 is ensured. As a result, the housing outer ring 11 is firmly fixed to the axle housing 40.
Alternatively, the modification shown in fig. 5 may be used instead of fig. 4. In this modification example, the number of the first and second modified examples,
Satisfies [ formula 2] 1.1.ltoreq.Rt/Rs.ltoreq.1.5.
According to equation 2, the shell roller bearing 10 can be smoothly pressed into the opening 41.
In the case where Rt/Rs exceeds 1.5, the shell roller bearing 10 can be pressed into the opening 41 without any problem, but in the manufacturing process, if the radial length of the tapered surface 15 is too long, the contact area of the shell outer ring 11 may not be ensured after the pressing.
According to the present embodiment, the plate thickness of the flange portion 14 is a predetermined value in the range of 40% to 75% inclusive of the plate thickness in the axial center region of the outer ring main body 12. As a result, the rigidity of the other end portion of the housing outer ring 11 in the axial direction including the flange portion 14 becomes low, and scratches of the axle box 40 can be prevented when the housing outer ring is pushed from the flange portion 14 into the opening 41. When the thickness of the flange portion 14 is less than 40% of the thickness of the outer ring main body 12, the rigidity of the other end portion of the case outer ring 11 in the axial direction may be too low, and may buckle during press-fitting. If the thickness of the flange portion 14 is less than 40% of the thickness of the outer ring main body 12, the rigidity of the other end portion of the outer ring 11 in the axial direction may be excessively high, and scratches may be generated in the axle box 40 during press-fitting.
In order to prevent buckling, in the present embodiment, carburizing and quenching are performed on the entire outer ring 11 of the case, and induction hardening and annealing are performed on the other end portion of the outer ring 11 including the flange portion 14 in the axial direction. This can improve the rigidity of the other end portion of the outer case ring 11 in the axial direction.
Industrial applicability
The present invention is advantageously used for rolling bearings of compressors for automobile air conditioners and rolling bearings inserted into light alloy axle boxes even in addition to compressors for automobile air conditioners.
Description of the reference numerals
The 10 shell-shaped roller bearing, the 11 shell outer ring, the 12 outer ring main body, the 12c inner diameter surface, the 13, 14 flange parts, the 15 conical surface, the 16R part, the 18 concave part, the 21 retainer, the 40 axle box and the 41 opening.
Claims (6)
1. A shell-type roller bearing, wherein,
The shell-shaped roller bearing is provided with:
A shell outer ring;
a retainer inserted into the housing outer ring; and
A roller which is held by the holder and rolls on an inner diameter surface of the housing outer ring,
The housing outer ring includes a cylindrical outer ring main body press-fitted and fixed to an opening of the axle housing, and flange portions protruding from both axial end portions of the outer ring main body toward an inner diameter side,
A tapered surface having an outer diameter gradually decreasing from the inner side to the outer side in the axial direction is provided on the outer peripheral surface of one axial end portion of the outer ring main body,
The taper angle of the taper surface is included in a range of 0.5 degrees or more and less than 5 degrees.
2. The shell-type roller bearing according to claim 1, wherein,
The thickness of the flange portion provided at one axial end of the outer ring body is within a range of 40% to 75% of the thickness of the outer ring body.
3. The shell-type roller bearing according to claim 1, wherein,
The flange portion has an axially outer end surface and the tapered surface connected via a chamfer formed at one axially end of the outer ring main body,
The axial dimension of the outer ring of the shell is more than 6mm,
The total of the axial dimension of the tapered surface and the axial dimension of the chamfer is included in a range of 1.5mm to 3.5 mm.
4. The shell-type roller bearing according to claim 1, wherein,
The radial dimension of the tapered surface is included in a range of 1.1 times to 1.5 times the interference obtained by subtracting the inner diameter radius of the opening from the outer diameter radius of the housing outer ring.
5. A fixing structure of a shell-shaped roller bearing, wherein,
The shell-shaped roller bearing fixing structure comprises:
the shell-shaped roller bearing of any one of claims 1 to 4; and
And an axle box having an opening with an inner diameter smaller than an outer diameter of the housing outer ring, wherein an inner diameter surface of the opening is closely contacted with an outer diameter surface of the outer ring main body in a negative clearance mode.
6. The fixing structure of a shell-shaped roller bearing according to claim 5, wherein,
The axle housing is formed of a light alloy.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2021-150919 | 2021-09-16 | ||
| JP2021150919A JP2023043353A (en) | 2021-09-16 | 2021-09-16 | Shell roller bearing and fixing structure for shell roller bearing |
| PCT/JP2022/031365 WO2023042603A1 (en) | 2021-09-16 | 2022-08-19 | Shell roller bearing and fixing structure for shell roller bearing |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN117940685A true CN117940685A (en) | 2024-04-26 |
Family
ID=85602787
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202280061402.5A Pending CN117940685A (en) | 2021-09-16 | 2022-08-19 | Shell-shaped roller bearing and fixing structure of shell-shaped roller bearing |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP2023043353A (en) |
| CN (1) | CN117940685A (en) |
| WO (1) | WO2023042603A1 (en) |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS4970042A (en) * | 1972-11-13 | 1974-07-06 | ||
| JPH0312016U (en) * | 1989-06-15 | 1991-02-07 | ||
| JPH11303863A (en) * | 1998-04-15 | 1999-11-02 | Nippon Seiko Kk | Shell type roller bearing |
| JP4408970B2 (en) * | 1998-06-05 | 2010-02-03 | Ｎｔｎ株式会社 | Needle roller bearings for swash plate compressors |
| JP2008038986A (en) * | 2006-08-03 | 2008-02-21 | Nsk Ltd | Shell type needle bearing |
-
2021
- 2021-09-16 JP JP2021150919A patent/JP2023043353A/en active Pending
-
2022
- 2022-08-19 WO PCT/JP2022/031365 patent/WO2023042603A1/en active Application Filing
- 2022-08-19 CN CN202280061402.5A patent/CN117940685A/en active Pending
Also Published As
| Publication number | Publication date |
|---|---|
| JP2023043353A (en) | 2023-03-29 |
| WO2023042603A1 (en) | 2023-03-23 |
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