CN212615937U - Polyamide retainer of cylindrical roller bearing for high speed and heavy load and bearing - Google Patents
Polyamide retainer of cylindrical roller bearing for high speed and heavy load and bearing Download PDFInfo
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- CN212615937U CN212615937U CN202022121702.9U CN202022121702U CN212615937U CN 212615937 U CN212615937 U CN 212615937U CN 202022121702 U CN202022121702 U CN 202022121702U CN 212615937 U CN212615937 U CN 212615937U
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Abstract
The utility model discloses a high-speed, heavy load is with polyamide system holder and bearing of cylindrical roller bearing, the holder includes two annular boundary beams and many crossbeams, form the pocket hole between the adjacent crossbeam, be equipped with at least one clamping part on the crossbeam of pocket hole side, the clamping part includes first fore shaft boss, second fore shaft boss and convex part, convex part sets up between first fore shaft boss and second fore shaft boss, the clamping part can carry out radial spacing to the rolling element, be equipped with the decompression recess on the crossbeam, be equipped with tip recess, bellying, guide contact part and guide non-contact part on the annular boundary beam; a bearing is also included. The utility model provides a cage is equipped with the space region on the contact looks facial features with the rolling element, reduce and the rolling element between the sliding friction, be equipped with the sunk area on the face is led to the holder external diameter, reduce and outer lane flange internal diameter between the friction generate heat, suitable railway high speed, heavy load vehicle axle box is with cylindrical roller bearing's cage structure.
Description
Technical Field
The utility model relates to a bearing holder field, concretely relates to high-speed, heavy load are with cylindrical roller bearing's polyamide system holder and bearing.
Background
The cylindrical roller bearing includes an inner ring, an outer ring surrounding the inner ring, a cage located between the inner ring and the outer ring, and cylindrical rollers (rolling elements) located in the cage and spaced apart from each other. The guidance of the rolling bodies in the rolling bearing is kept stable by means of a cage, which generally has two side rings, between which a cross beam extends, between which pockets are formed which cooperate with the rolling bodies. The area of the circumferential guide surface of the retainer is a basic factor influencing the friction force of the guide surface, and the area of the circumferential guide surface of the traditional bearing retainer is generally larger, so that the friction force is increased, and the performance of the bearing is reduced. Meanwhile, the flow bypassing resistance generated by the relative motion between the rolling body and the lubricating grease is related to the size of the rolling body, and in the application process of the traditional engineering, the relative guide area between the rolling body and the retainer is large, so that the flow bypassing resistance is large, and the performance of the bearing is reduced.
SUMMERY OF THE UTILITY MODEL
The utility model discloses to the proposition of above problem, and the polyamide system holder and the bearing of cylinder roller bearing for high-speed, heavy load of research design, the circumference guide area who solves traditional cylinder roller bearing holder is great, the relative guide area between rolling element and the holder is great, and causes the great shortcoming of frictional force. The utility model discloses a technical means as follows:
a polyamide retainer and a bearing of a cylindrical roller bearing for high speed and heavy load comprise a retainer body, wherein the retainer body is arranged between an outer ring and an inner ring, the retainer body comprises two annular boundary beams and a plurality of cross beams which axially connect the two annular boundary beams, a pocket hole is formed between the adjacent cross beams, at least one clamping part is arranged on the cross beam on the side surface of the pocket hole, the clamping part comprises a first fore shaft boss, a second fore shaft boss and an arc-shaped part which is mutually supported with a rolling body, the arc-shaped part is arranged between the first fore shaft boss and the second fore shaft boss, the first fore shaft boss and the second fore shaft boss can radially limit the rolling body, a pressure reducing groove is arranged on one side of the cross beam far away from the center of the retainer body, an end part groove and at least one lug boss are arranged on the annular boundary beam on the side surface of the pocket hole, and the lug bosses and the end part grooves are crossly, the bulge can carry out axial spacing to the rolling element, be equipped with a plurality of guide contact portions and guide non-contact portion on the external diameter face of annular boundary beam, the diameter of guide contact portion is greater than the diameter of guide non-contact portion.
Preferably, the decompression groove is arranged along the axial direction of the retainer body, the length of the decompression groove is smaller than the axial length of the pocket, and the length of the decompression groove is not smaller than the axial distribution range of the clamping part.
Preferably, the first locking boss is arranged on one side, far away from the center of the retainer body, of the cross beam, the second locking boss is arranged on one side, close to the center of the retainer body, of the cross beam, and the depth of the pressure reduction groove is not smaller than the radial length of the first locking boss.
Preferably, the pocket hole is the rectangle, the bellying is followed the radial setting of holder body, all be equipped with two bellyings on each side annular boundary beam in pocket hole, form the tip recess between two bellyings, all be equipped with two clamping parts on each side crossbeam in pocket hole, be equipped with the space portion between two clamping parts, four angles in pocket hole are equipped with the bight recess.
Preferably, the clamping portions on two sides of the pocket are symmetrically arranged along the axial direction of the rolling body, the difference between the distance between two opposite first locking bosses and the diameter of the rolling body is equal to (1-2)/54 times of the diameter of the rolling body, the difference between the distance between two opposite second locking bosses and the diameter of the rolling body is equal to (1-2)/27 times of the diameter of the rolling body, the two ends of the outer ring are respectively provided with a flange, the difference between the inner diameter of the flange and the outer diameter of the guide contact portion is equal to (1-2)/27 times of the diameter of the rolling body, and the difference between the diameter of the guide contact portion and the diameter of the guide non-contact portion is equal to (1-2)/27 times of the diameter of the rolling body.
Preferably, the number of the guide contact portions and the number of the guide non-contact portions are the same as the number of the rolling elements, and the ratio of the circumferential length of the guide contact portions to the circumferential length of the annular side beam is 1: 3, the annular boundary beam deviates from one side of pocket hole is equipped with the ring channel, be equipped with the strengthening rib in the ring channel, the degree of depth of ring channel with the axial length's of annular boundary beam ratio is less than 1: 3.
preferably, the ratio of the width of the projection to the diameter of the rolling element is 1: (5-6), the ratio of the width of the end groove to the width of the boss is 2: 1, the axial length ratio of the pocket to the axial length of the clamping part is 6: 1, the ratio of the axial length of the pocket to the axial length of the rolling body is 61: 60, the ratio of the diameter of the circular arc part to the diameter of the rolling element is 1.015: 1.
preferably, the breaking tensile force value of the annular edge beam at the reinforcing rib is not less than 1.3 times of the product value of the diameter of the rolling element and the axial length of the rolling element, the breaking tensile force value of the annular edge beam at the annular groove is not less than 3 times of the product value of the diameter of the rolling element and the axial length of the rolling element, and the tensile breaking force value of the cross beam is not less than 3 times of the area value of the end face of the rolling element.
A bearing comprises the retainer, the outer ring, the inner ring and a plurality of rolling bodies, wherein the rolling bodies are arranged in the pocket.
Preferably, the bearing is a cylindrical roller bearing.
Compared with the prior art, the polyamide system holder and the bearing of the high-speed, heavy-load cylindrical roller bearing have the beneficial effects that: the rolling bearing retainer of the utility model has a mixed guide mode which generates a guide relation with the rolling body and the outer diameter, a plurality of friction-reducing gap areas are arranged on the contact surface of the rolling body, the sliding friction between the rolling body and the retainer is reduced, a certain amount of grease is stored, and the lubrication state of the contact surface between the rolling body and the retainer is improved; the outer diameter guide surface is provided with recessed areas with the same number as the rolling bodies, so that the friction heating between the outer diameter guide surface of the retainer and the inner diameter of the flange of the outer ring during high-speed operation is reduced, and the polyamide retainer structure is suitable for the cylindrical roller bearing for the axle box of the high-speed and heavy-duty railway vehicle.
Drawings
FIG. 1 is a schematic structural diagram of the installation of the retainer in the embodiment of the present invention (section 1/4 of the bearing outer ring);
FIG. 2 is a diagram showing the state of the retainer assembled with the rolling elements in the embodiment of the present invention;
FIG. 3 is a schematic view of the overall structure of the retainer in the embodiment of the present invention;
FIG. 4 is a partial structural view of a retainer according to an embodiment of the present invention;
FIG. 5 is a diagram showing the contact state between the pockets and the rolling elements in the embodiment of the present invention;
FIG. 6 is a schematic view of the assembly of the cage guide surface and the bearing outer race according to the embodiment of the present invention;
FIG. 7 is a schematic view of the structural dimensions of an annular edge beam in an embodiment of the present invention;
FIG. 8 is a schematic structural dimension view of an axial cross section at a reinforcing rib of a side beam of the retainer in an embodiment of the present invention;
FIG. 9 is a schematic structural dimension view of a minimum cross section of an edge beam according to an embodiment of the present invention;
FIG. 10 is a schematic axial cross-sectional view of a cross beam in an embodiment of the present invention;
FIG. 11 is a schematic size view of pockets and rolling elements in an embodiment of the present invention;
FIG. 12 is a schematic view showing the holding state of the pockets and the rolling elements in the embodiment of the present invention;
FIG. 13 is a cross sectional view of the cross beam and a groove structure of the side beam according to the embodiment of the present invention;
fig. 14 is a schematic view of a minimum radial cross section of a cross beam in an embodiment of the invention.
In the figure, 1, a cage body; 2. a rolling body; 3. an outer ring; 4. an inner ring; 11. an annular edge beam; 12. a cross beam; 13. a pocket hole; 111. a boss portion; 112. an end portion groove; 113. corner grooves; 114. an annular groove; 115. reinforcing ribs; 116. a guide contact portion; 117. a guide non-contact portion; 121. a pressure reducing groove; 122. a clamping portion; 123. a void portion; 1221. a first fore shaft boss; 1222. a second fore shaft boss; 1223. a circular arc-shaped portion.
Rg01, Lg 01: a first clearance part (corner groove) between the retainer and the end part of the rolling body;
rf01, Lf 01: a first holding part (convex part) between the retainer and the end part of the rolling body;
rmg01, Lmg 01: a gap part (end part groove) between the retainer and the end part of the rolling body;
rf02, Lf 02: a second holding part (convex part) between the retainer and the end part of the rolling body;
rg02, Lg 02: a second clearance part (corner groove) between the retainer and the end part of the rolling body;
ff01, Bf 01: a first holding part (clamping part) between the retainer and the rolling surface of the rolling body;
fmg01, Bmg 01: a gap part (air gap part) between the retainer and the rolling surface of the rolling body;
ff02, Bf 02: a second holding part (clamping part) between the retainer and the rolling surface of the rolling body;
ls01, Rs 01: a flange of the outer ring;
dc: the diameter of a guide contact part of the retainer guided by outer ring flanges Ls01 and Rs 01;
d2: the diameter of the inner diameter surface of the bearing outer ring guide retainer;
dc 1: the diameter of the guide non-contact part of the outer ring of the bearing is supported by the retainer;
s delta: the retainer depends on the circumferential length of the guiding non-contact part of the outer ring of the bearing;
SL: the retainer depends on the circumferential length of the guide contact part of the bearing outer ring;
δ r: the width of the reinforcing ribs;
bc: the total width of the cage;
lc: pocket length;
l δ e: the axial width of the clamping part (the first locking boss, the second locking boss and the circular arc part); δ f: the axial depth difference between the boss and the end recess;
bc 1: the axial width of the annular edge beam (including the boss);
bc 2: the axial width of the annular edge beam (excluding the boss);
and hc: the radial height of the annular edge beam;
sweld: the cross-sectional area of the annular edge beam (excluding the boss);
hc 1: the radial height of the annular groove;
bc: the axial depth of the annular groove;
sb: the minimum cross-sectional area of the annular edge beam;
and c, Lec: the axial length of the relief groove;
lwe: the axial length of the rolling body;
dwe: rolling surface diameter of the rolling body;
dwc: the diameter of the arc-shaped surface of the arc-shaped part where the retainer and the rolling body are mutually held;
δ i: the distance between two second fore shaft bosses on two opposite sides in the pocket;
δ e: the distance between two first locking bosses on two opposite sides in the pocket;
δ b: cross-sectional minimum width of the beam;
he: the radial height of the first fore shaft boss;
δ c: the radial depth of the relief groove;
δ b 1: the cross-sectional half width of the cross-beam relief groove portion;
tf: the width of the protruding part of the annular edge beam and the end part of the rolling body are mutually supported;
TFg: the spacing distance between the two convex parts is formed by the annular edge beam and the end part of the rolling body;
scb: the beam cuts the area of the smallest cross section.
Detailed Description
As shown in fig. 1 to 3, a polyamide cage for a high-speed heavy-duty cylindrical roller bearing includes a cage body 1, and the cage body 1 is mounted between an outer ring 3 and an inner ring 4 of the bearing. The retainer body 1 comprises two annular boundary beams 11 and a plurality of cross beams 12 which axially connect the two annular boundary beams 11, the cross beams 12 extend from the annular boundary beam 11 on the right side to the annular boundary beam 11 on the left side in the figure, and the two annular boundary beams 11 are symmetrically arranged in a plane. Pockets 13 capable of being filled with the rolling bodies 2 are formed between the adjacent cross members 12, the number of the pockets 13 is the same as the number of the rolling bodies 2, and each pocket 13 contains one rolling body 2. At least one clamping portion 122 is arranged on the cross beam 12 on the side of the pocket 13, the clamping portion 122 includes a first locking boss 1221, a second locking boss 1222 and an arc portion 1223, the first locking boss 1221 is arranged on one side of the cross beam 12 away from the center of the body of the cage body 1 (one side close to the outer diameter surface of the cross beam 12), the second locking boss 1222 is arranged on one side of the cross beam 12 close to the center of the body of the cage body 1 (one side close to the inner diameter surface of the cross beam 12), and the arc portion 1223 is arranged between the first locking boss 1221 and the second locking boss 1222. The beam 12 is held with the rolling element 2 by the arc-shaped portion 1223, and the rolling element 2 is radially limited by the first locking boss 1221 and the second locking boss 1222 to keep the rolling element 2 from being separated inward or outward, and the cage body 1 is suitable for single-row, double-row or multi-row rolling bearings.
As shown in fig. 4, the ring-shaped edge beam 11 is provided with a plurality of guide contact portions 116, and the guide contact portions 116 are flush with the radial length of the surface of the cross beam 12 and are of an integral structure with the cross beam 12. The outer diameter of the cross member 12 serves as an outer guide contact surface, while the guide contact portion 116 of the ring side member 11 also serves as an outer guide contact surface, and the ring side member 11 is designed in a recessed shape to guide the non-contact portion 117 in the remaining portion of the pocket 13. When the bearing rotates, only the guide contact portion 116 and the left flange Ls01 and flange of the outer ring 3Rs01 makes guiding contact, reducing the contact area and thus the guiding surface friction force FCLAnd the performance of the bearing is improved.
Two protruding parts 111 are arranged on the annular edge beam 11 on each side of the pocket 13, the protruding parts 111 are arranged along the radial direction of the body of the cage body 1, an end part groove 112 is formed between the two protruding parts 111, and the annular edge beam 11 is supported with the end part of the rolling body 2 through the protruding parts 111 to axially limit the rolling body 2. The pocket 13 is rectangular, corner grooves 113 are formed in four corners of the pocket 13, and the protruding portions 111 of the annular side beams 11 are connected with the corner grooves 113 respectively. When the bearing rotates, the structure can reduce the circumferential flow resistance F of the end part of the rolling bodydAnd the bearing performance is improved.
The cross member 12 on each side of the pocket 13 is provided with two clamping portions 122, the clamping portions 122 of the cross member 12 are respectively connected to the corner grooves 113, the cross member 12 is held against the rolling surfaces of the rolling elements 2 by the clamping portions 122, and a gap 123 is provided between the two clamping portions 122. When the bearing rotates, only the arc-shaped part 1223 is in contact with the rolling surface of the rolling element 2, the contact area with the circumference of the rolling element 2 is reduced, and the circumferential streaming resistance F of the rolling element is reducedd。
The crossbeam 12 is equipped with non-through decompression recess 121 in the middle of keeping away from the one side (the external diameter face of crossbeam 12) at holder body 1 center, and decompression recess 121 sets up along holder body 1's axial, and the axial length of the length of decompression recess 121 is less than pocket 13, guarantees that the intensity of annular boundary beam 11 can not receive the influence. The axial distribution range of clamping part 122 does not exceed the length of relief groove 121, and in this embodiment, relief groove 121 has covered the position of two clamping parts 122 at axial position, and the convenience is being extracted in the middle of two crossbeams 12 when carrying out the drawing, and the pocket 13 mold core is easily followed, and does not damage first lock mouthful boss 1221.
As shown in fig. 5, the rolling elements 2 operate with 8 holding contact portions and 8 clearance non-contact portions in the pockets 13 of the cage. The contact parts of the end surfaces of the rolling bodies 2 and the pockets 13 are four convex parts 111: rf01, Rf02, Lf01, Lf02, the contact parts of the rolling surface of the rolling element 2 and the pocket 13 are four clamping parts 122: ff01, Ff02, Bf01, Bf 02; the non-contact gap part between the end surface of the rolling body 2 and the pocket 13 is four corner grooves 113: rg01, Rg02, Lg01, Lg02, and two end grooves 112: rmg01, Lmg01, and the non-contact portions between the rolling surfaces of the rolling elements 2 and the pockets 13 are two void portions 123: fmg01 and Bmg 01.
As shown in fig. 6, the cage body 1 and the rolling elements 2 are mounted in the gap between the outer ring 3 and the inner ring 4, the end of the outer ring 3 is designed with two flanges Ls01 and Rs01, the inner diameters of the flanges Ls01 and Rs01 are D2, the outer diameter of the guide contact part 116 of the cage body 1 is Dc, and the difference between the inner diameter of the flange and the outer diameter of the guide contact part 116 is equal to (1-2)/27 times the diameter value of the rolling elements 2, i.e., D2-Dc is (1-2) Dwe/27. In the present embodiment, in order to accommodate high-speed operation, the outer diameter Dc of the guide contact portion 116 is smaller than the inner diameter D2 of the Ls01 or Rs01 by at least 1 to 2mm, that is, Dc is D2- (1 to 2). The guide clearance directly influences the guide resistance, and the guide clearance disclosed by the scheme can reduce friction heating, reduce vibration, improve the operation stability of the retainer, reduce the slip rate of the rolling body 2 and improve the stability of the bearing.
As shown in fig. 7, the guide non-contact portion 117 of the annular side member 11 has an outer diameter Dc1, and the difference between the diameter of the guide contact portion 116 and the diameter of the guide non-contact portion 117 is equal to (1-2)/27 times the diameter of the rolling element 2, that is, Dc1 is Dc- (1-2) Dwe/27. In the present embodiment, the diameter of the guide non-contact portion 117 is smaller than the diameter Dc of the guide contact portion 116 by 1 to 2mm, that is, Dc1 is Dc- (1-2), excluding the guide frictional resistance of the guide non-contact portion 117. The circumferential length SL of the guide contact portion 116 is about 1/3 of the circumferential length of the portion of the annular side rail 11 near the pocket 13, and the circumferential length S δ of the guide non-contact portion 117 is about 2/3 of the circumferential length of the portion of the annular side rail 11 near the pocket 13, i.e., SL ═ Dc/Z)/3 and S δ ═ 2 (pi Dc/Z)/3, whereby the guide frictional resistance of 2/3 is reduced.
As shown in fig. 8 to 9, the cage body 1 has a total width Bc, the pocket 13 has an axial length Lc, and the axial length Lc of the pocket 13 is 1/60 longer than the length Lwe of the rolling elements 2 so as to be engaged with the rolling elements 2, i.e., Lc is Lwe + Lwe/60. The clearance between the pockets 13 and the rolling bodies 2 effectively ensures the guide clearance between the rolling bodies 2 and the cage body 1, and has the effects of reducing friction heating, reducing vibration, improving the operation stability of the cage body 1, the slip rate of the rolling bodies 2 and the like.
The axial width of the clamping portion 122 (i.e., the first latching projection 1221, the second latching projection 1222, and the arc-shaped portion 1223) of the cross member 12 that is in contact with the rolling elements 2 is L δ e, which is 1/6 of the axial length Lc of the pocket 13, i.e., L δ e is Lc/6. The contact area of the circular arc 1223 and the outer diameter surface of the rolling element 2 is reduced by 2/3, and the rotational flow resistance Fd of the rolling element 2 is effectively reduced.
The non-contact part of the ring-shaped edge beam 11 and the end of the rolling body 2 has four corner grooves 113: rg01, Rg02, Lg01, Lg02, and two end grooves 112: rmg01, Lmg01, the contact part of the ring-shaped edge beam 11 and the end part of the rolling body 2 has four convex parts 111: rf01, Rf02, Lf01 and Lf 02. The annular edge beam 11 has an axial thickness Bc1, and the depth of the non-contact portion of the annular edge beam 11 relative to the contact portion is δ f, which is selected to be 0.5mm, i.e., the recess depth of the non-contact portion of Rg01, Rg02, Rmg01, etc. is 0.5 mm. The friction streaming resistance between non-contact parts such as Rg01, Rg02 and Rmg01 and the end part of the rolling element 2 is eliminated through the structural design, the friction resistance between the annular edge beam 11 and the rolling element 2 is reduced, and the bearing performance is improved.
The end face of the annular side beam 11 departing from the pocket 13 is provided with an annular groove 114, a weld mark is arranged in the middle of the annular groove 114, and a reinforcing rib 115 is arranged at the weld mark to form a weld mark part. The remaining axial thickness of the annular edge beam 11 after the non-contact part is removed is Bc2, the radial height of the annular edge beam 11 is hc, and the cross-sectional area of the weld mark part of the annular edge beam 11 is Sweld, that is, Sweld is Bc2 × hc. In designing Sweld, the weld mark tensile strength σ t finally formed by the injection molding process is generally about 50% of the tensile strength σ of the body material, and the fracture tensile force F of the weld mark is the product of the weld mark tensile strength σ t and the weld mark cross-sectional area Sweld, that is, F ═ σ t · Sweld. Fully considering the operation condition of the axle box part of a high-speed and heavy-duty railway vehicle, the fracture tensile force F of the weld mark part is not less than 1.3 times Dwe × Lwe, namely F ═ sigma t ≥ Sweld ≥ 1.3Dwe × Lwe, Sweld ≥ 1.3Dwe ≥ Lwe/sigma t, and the method can be used as a basic method for checking the strength of the weld mark part of the side beam. If the breaking tensile force F of the weld mark is less than 1.3Dwe × Lwe, there is a risk of the weld mark breaking during the operation of the high-speed and heavy-duty railway vehicle.
The annular groove 114 has an axial depth Bc, a radial height hc1, and a cross-sectional area (excluding the cross-sectional area of the annular groove 114) of the annular edge beam 11 Sb, i.e., Sb-Bc 2 hc-Bc hc 1. The axial depth Bc of the annular groove 114 should be less than 1/3 of the axial length Bc2 of the annular edge beam 11, and the radial height hc1 of the annular groove 114 is hc-2Bc, i.e., hc1 ═ hc-2 Bc. The tensile breaking force F1 of the end face of the annular side beam 11 (with the annular groove 114) is the product of Sb and the tensile strength σ of the body material, i.e., F1 ═ Sb σ, F1 should be no less than 3 times Dwe × Lwe, i.e., F1 ≥ 3 ≤ Dwe ≤ Lwe, Sb ≥ 3 ≤ Dwe ≥ Lwe, and Sb ≥ 3 ≥ Dwe ≥ Lwe/σ, and can be used as a basic method for checking the strength of the side beam. If the side sill tensile breaking force F1 is less than 3 x Dwe x Lwe, there is a risk of side sill breakage and deformation during operation of a high speed, heavy duty railway vehicle.
As shown in FIG. 10, the cross member 12 is provided with a pressure reducing groove 121, the axial length of the pressure reducing groove 121 is Lec, Lec is smaller than the axial length Lc of the pocket 13 and is larger than the axial maximum range size of the two clamping portions 122 held by the cross member 12 and the cylindrical surface of the rolling element 2, that is, Lc is not less than Lec not less than 2Lc/3, and may be expressed as Lec about 5 Lc/6. The utility model provides a holder adopts injection moulding holder, and above-mentioned structural design is convenient when carrying out the drawing die, and the pocket 13 mold core is easily pulled out from the middle of two crossbeams 12, and does not damage first fore shaft boss 1221, avoids the 12 root weak points of crossbeam of holder simultaneously, can not influence the structural strength of holder.
As shown in fig. 11, the diameter of the circular arc 1223 of the beam 12 that abuts against the cylindrical surface of the rolling elements 2 is Dwc, Dwc is larger than the diameter Dwe of the rolling elements 2, and the increase is about 0.015 times of Dwe, that is, Dwc is 0.015Dwe + Dwe. The design ensures the holding and guiding functions of the arc-shaped parts 1223, increases the rotation flexibility of the cylindrical surfaces of the rolling bodies 2 in the arc-shaped parts 1223, reduces friction heating, reduces vibration, and improves the operation stability of the retainer body 1, the slip rate of the rolling bodies 2 and other effects.
The clamping portions 122 on two sides of the pocket 13 are symmetrically arranged along the axial direction of the rolling element 2, the distance between two first locking bosses 1221 on two opposite sides in the pocket 13 is delta e, the difference value of the delta e and the diameter of the rolling element 2 is equal to (1-2)/54 times of the diameter value of the rolling element 2, namely Dwe-delta e is equal to (1-2) Dwe/54; the distance between the two second latching projections 1222 on opposite sides in the pocket 13 is δ i, and the difference between δ i and the diameter of the rolling element 2 is equal to (1-2)/27 times the diameter of the rolling element 2, that is, Dwe- δ i is (1-2) Dwe/27. In the embodiment, δ e is at most 1mm smaller than the diameter Dwe of the rolling element 2, and δ i is at least 1mm smaller than the diameter Dwe of the rolling element 2, so that the loading and the separation of the rolling element 2 are facilitated.
As shown in fig. 12, it can be seen that the gap 123 and the corner groove 113 do not contact the rolling surface, and frictional heat generation between the rolling element 2 and the cage is reduced.
As shown in fig. 13, the cross member 12 has a minimum cross-sectional width δ b, the radial height of the first locking projection 1221 on the cross member 12 is he, and the depth of the relief groove 121 is δ c. This technical scheme requires that δ c should not be less than he, guarantees that relief groove 121 has sufficient deflection when the drawing die, and the pocket 13 mold core is easily pulled out from the middle of two crossbeams 12, and does not damage first lock mouthful boss 1221.
The cross section half width of the pressure reducing groove 121 part of the cross beam 12 is delta b1, delta b1 is required to be not less than 1/2 of delta b, namely delta b1 is more than or equal to delta b/2, and the consistency of the cross section of the cross beam 12 is ensured.
The width of the protruding part 111 where the annular edge beam 11 and the end part of the rolling body 2 are in a holding state is TF, and the TF is required to be about 1/5-1/6 of the diameter Dwe of the rolling body 2 in the technical scheme; the distance between two adjacent protrusions 111 (the width of the end groove 112) is TFg, which is about 2 times TF, i.e. TFg 2 TF. The design reduces 2/3 the contact area between the convex part 111 and the end of the rolling element 2, effectively reducing the sliding and streaming resistance Fd of the end of the rolling element 2.
As shown in FIG. 14, the minimum cross-sectional area of the beam 12 is Scb, and the technical solution requires that the product F2 (tensile breaking force of the beam 12) of Scb and the tensile strength σ of the body material should be not less than 3 times pi Dwe2(ii)/4, i.e., Scb. sigma. gtoreq.3. pi. Dwe2/4，Scb≥3*π*Dwe2/(4 σ), as a basic method for checking the strength of the beam 12. If the tensile breaking force F2 of the beam 12 is less than 3 π Dwe2And 4, the risk of fracture and deformation of the cross beam 12 exists in the running process of the high-speed and heavy-load railway vehicle.
The polyamide cage structure for the cylindrical roller bearing comprises a plurality of beams extending in the axial directionA plurality of guide surfaces against the rolling elements 2 are formed, and a plurality of recesses are formed in the guide surface formed with the outer ring 3. When the rolling body 2 works, the area of the non-contact part of the retainer pocket 13 is about 2 times of the area of the holding contact part, and the increased non-contact gap part does not generate larger running resistance with the rolling body in the running process, thereby effectively reducing the rotating streaming resistance F of the rolling body 2d. Compared with the traditional retainer, the retainer structure has the advantages that the area of the contact part of the retainer structure is reduced 2/3, and the rotating and streaming resistance F of the rolling body 2 is effectively reducedd。
According to the existing design theory of the bearing, the friction force F of the guide surface of the retainerCLThe relationship only with the guide surface width Bc1 is based on the overall outer diameter guide surface of the solid metal cage, resulting in consideration of only the width effect of the guide surface during cage design. The utility model discloses the holder adopts polyamide injection moulding holder, makes the processing of external diameter face become the multistage curve and makes it possible, and circumference guide face "area" is just influence guide face frictional force FCLThe root factor of (c). The utility model discloses a holder guide face structure design method reduces circumference guide face "area" to original 1/3, reduces guide face frictional force FCLTo 1/3 original.
According to the existing design theory of the bearing, the flow-around resistance F generated by the relative motion between each rolling body and the lubricating greasedIn relation to the roller diameter Dw and the length l of the rolling element, the relative guide area between the rolling element and the cage is the bypass resistance F in practical engineering applicationdBy reducing the relative guide area between the rolling body and the retainer, the utility model relates to a method for reducing the flow resistance F of the rolling bodydThe design method of (1). The relative guide area between the rolling body and the retainer is reduced to the original 1/3, thereby reducing the bypass flow resistance F between the rolling body and the retainerdTo 1/3 original.
According to the present design theory of bearing, the method is checked to holder intensity is in the research stage, does not have practical holder boundary beam and crossbeam intensity design criterion, the utility model discloses a method is checked to holder boundary beam and crossbeam intensity is closely related with rolling element diameter and length, and suitable railway is high-speed, heavy vehicle axle box position is checked to the intensity of holder for the bearing.
The utility model provides a pair of structure antifriction design method and intensity check method of polyamide system holder effectively reduces operation guide face frictional resistance and operation and flows around the resistance, satisfies the big impact of railway high speed, heavy vehicle axle box position bearing, high rotational speed's application operating mode. The retainer structure can meet the impact acceleration of 1000g given to the axle box cylindrical roller bearing by the running of high-speed and heavy-duty vehicles of railways, and can meet the requirement that the dn value is not lower than 60 multiplied by 10 when the running equivalent dynamic load of the high-speed and heavy-duty vehicles of railways is 0.1Cr (bearing rated dynamic load)4mm r/min high-speed operation condition.
The utility model also provides a cylindrical roller bearing (also can be antifriction bearing types such as tapered roller bearing), including above-mentioned holder structure, outer lane, inner circle and a plurality of rolling element, the pocket of holder is located to the rolling element downthehole.
The above-mentioned embodiments are only for describing the preferred embodiments of the present invention, and are not intended to limit the scope of the present invention, and various modifications and improvements made by those skilled in the art without departing from the design spirit of the present invention should fall into the protection scope defined by the claims of the present invention.
Claims (10)
1. The utility model provides a high-speed, heavy load are with polyamide system holder of cylindrical roller bearing, includes holder body (1), between outer lane (3) and inner circle (4) are located in holder body (1), holder body (1) includes two annular boundary beams (11) and with two annular boundary beams (11) many crossbeams (12) of axial connection, forms pocket hole (13), its characterized in that between adjacent crossbeam (12): the rolling bearing is characterized in that at least one clamping part (122) is arranged on a cross beam (12) on the side surface of the pocket (13), the clamping part (122) comprises a first locking boss (1221), a second locking boss (1222) and an arc-shaped part (1223) which is mutually held by the rolling body (2), the arc-shaped part (1223) is arranged between the first locking boss (1221) and the second locking boss (1222), the first locking boss (1221) and the second locking boss (1222) can radially limit the rolling body (2), a pressure reducing groove (121) is arranged on one side of the cross beam (12) far away from the center of the cage body (1), an end groove (112) and at least one bulge (111) are arranged on an annular boundary beam (11) on the side surface of the pocket (13), the bulge (111) and the end groove (112) are distributed in a crossed manner, and the bulge (111) can axially limit the rolling body (2), the outer diameter surface of the annular edge beam (11) is provided with a plurality of guide contact parts (116) and guide non-contact parts (117), and the diameter of each guide contact part (116) is larger than that of each guide non-contact part (117).
2. The retainer of claim 1, which is made of polyamide for a high-speed and heavy-duty cylindrical roller bearing, and is characterized in that: the axial setting of decompression recess (121) along holder body (1), the length of decompression recess (121) is less than the axial length of pocket (13), the length of decompression recess (121) is not less than the axial distribution range of clamping part (122).
3. The retainer of claim 2, which is made of polyamide for a high-speed and heavy-duty cylindrical roller bearing, wherein: the first locking boss (1221) is arranged on one side, away from the center of the retainer body (1), of the cross beam (12), the second locking boss (1222) is arranged on one side, close to the center of the retainer body (1), of the cross beam (12), and the depth of the pressure reduction groove (121) is not smaller than the radial length of the first locking boss (1221).
4. The retainer of claim 1, which is made of polyamide for a high-speed and heavy-duty cylindrical roller bearing, and is characterized in that: pocket (13) are the rectangle, bellying (111) are followed the radial setting of holder body (1), all be equipped with two bellying (111) on each side annular boundary beam (11) of pocket (13), form tip recess (112) between two bellying (111), all be equipped with two clamping part (122) on each side crossbeam (12) of pocket (13), be equipped with space portion (123) between two clamping part (122), four angles of pocket (13) are equipped with bight recess (113).
5. The retainer of claim 4, which is made of polyamide for a high-speed and heavy-duty cylindrical roller bearing, wherein: clamping parts (122) at two sides of the pocket (13) are axially and symmetrically arranged along the rolling body (2), and the difference between the distance between two opposite first locking bosses (1221) and the diameter of the rolling body (2) is equal to (1-2)/54 times the diameter value of the rolling body (2), the difference between the distance between two opposite second locking bosses (1222) and the diameter of the rolling body (2) is equal to (1-2)/27 times the diameter value of the rolling body (2), both ends of the outer ring (3) are provided with flanges, the difference between the inner diameter of the flanges and the outer diameter of the guide contact part (116) is equal to (1-2)/27 times of the diameter value of the rolling body (2), the difference between the diameter of the guide contact portion (116) and the diameter of the guide non-contact portion (117) is equal to (1-2)/27 times the diameter value of the rolling element (2).
6. The retainer of claim 3 or 4, which is made of polyamide and used for a high-speed and heavy-duty cylindrical roller bearing, and is characterized in that: the number of the guide contact parts (116) and the number of the guide non-contact parts (117) are the same as the number of the rolling bodies (2), and the ratio of the circumferential length of the guide contact parts (116) to the circumferential length of the annular side beam (11) is 1: 3, annular boundary beam (11) deviates from one side of pocket (13) is equipped with ring channel (114), be equipped with strengthening rib (115) in ring channel (114), the degree of depth of ring channel (114) with the axial length's of annular boundary beam (11) ratio is less than 1: 3.
7. the retainer of claim 3 or 4, which is made of polyamide and used for a high-speed and heavy-duty cylindrical roller bearing, and is characterized in that: the ratio of the width of the convex part (111) to the diameter of the rolling body (2) is 1: (5-6), the ratio of the width of the end groove (112) to the width of the boss (111) is 2: 1, the ratio of the axial length of the pocket (13) to the axial length of the clamping portion (122) is 6: 1, the ratio of the axial length of the pocket (13) to the axial length of the rolling body (2) is 61: 60, the ratio of the diameter of the circular arc-shaped part (1223) to the diameter of the rolling element (2) being 1.015: 1.
8. the retainer of claim 6, which is made of polyamide and is used for a high-speed and heavy-duty cylindrical roller bearing, and is characterized in that: the product numerical value of rolling element (2) diameter and rolling element (2) axial length that fracture tensile force numerical value of strengthening rib (115) department annular boundary beam (11) is not less than 1.3 times, the product numerical value of rolling element (2) diameter and rolling element (2) axial length that fracture tensile force numerical value of annular boundary beam (11) is not less than 3 times is located in annular groove (114), the tensile fracture force numerical value of crossbeam (12) is not less than 3 times rolling element (2) end face area numerical value.
9. A bearing, characterized by: comprising the cage of any of claims 1-8, an outer race, an inner race, and a plurality of rolling elements disposed within the pockets.
10. A bearing according to claim 9, wherein: the bearing is a cylindrical roller bearing.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202022121702.9U CN212615937U (en) | 2020-09-24 | 2020-09-24 | Polyamide retainer of cylindrical roller bearing for high speed and heavy load and bearing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202022121702.9U CN212615937U (en) | 2020-09-24 | 2020-09-24 | Polyamide retainer of cylindrical roller bearing for high speed and heavy load and bearing |
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| Publication Number | Publication Date |
|---|---|
| CN212615937U true CN212615937U (en) | 2021-02-26 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202022121702.9U Active CN212615937U (en) | 2020-09-24 | 2020-09-24 | Polyamide retainer of cylindrical roller bearing for high speed and heavy load and bearing |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN212615937U (en) |
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