CN109838461B - Self-lubricating high-speed bearing - Google Patents
Self-lubricating high-speed bearing Download PDFInfo
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- CN109838461B CN109838461B CN201910213792.3A CN201910213792A CN109838461B CN 109838461 B CN109838461 B CN 109838461B CN 201910213792 A CN201910213792 A CN 201910213792A CN 109838461 B CN109838461 B CN 109838461B
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Abstract
The invention discloses a self-lubricating high-speed bearing, which comprises an inner ring, a first rolling body, a differential ring, a second rolling body and an outer ring, wherein the inner ring is arranged on the inner ring; the inner ring is positioned in the differential ring, and the differential ring is positioned in the outer ring. The bearing further comprises end face supporting components, the end face supporting components are respectively fixed on two end faces of the outer ring, and the end face supporting components are in rolling contact with two end faces of the differential ring. The first retainer is provided with a first lubricating groove, and the second retainer is provided with a second lubricating groove. The rotating shaft is radially supported by using a double-layer rolling body structure, so that the rotation speed of each layer of rolling bodies can be greatly reduced, and the vibration and the heat productivity are reduced; the end face supporting component reliably supports the differential ring in the axial direction, so that the stability of the bearing structure is ensured; the arrangement of the lubricating grooves on the retainer can reduce the contact area of the retainer and the roller, the needle roller or the rolling ball so as to reduce the friction force, and meanwhile, the lubricating grooves can allow lubricating grease on the surfaces of the roller, the needle roller or the rolling ball to pass through.
Description
Technical Field
The invention relates to the field of bearings, in particular to a self-lubricating high-speed bearing.
Background
The bearing is used for supporting and installing the running shaft in the shaft seat, the bearing is divided into a sliding bearing and a rolling bearing, and the sliding bearing has larger friction loss compared with the rolling bearing because a rotating part and a sliding part of the sliding bearing are in sliding friction, so that the limitation of the use working condition of the sliding bearing is larger; the rolling bearing is in rolling friction, so that friction loss is reduced, and the working condition adaptability of the rolling bearing is very strong, so that the rolling bearing is widely used in industry. The rotating speed of many machines is higher along with the processing requirement or the use requirement, and the core support of the rotating part is the bearing, but the rotating speed of the bearing is influenced by the temperature rise of the bearing, when the rotating speed of the bearing is higher, the friction power is higher, the heat generation is more, the temperature of the bearing is increased due to the heat which is not emitted in time, the bearing clearance is influenced, the bearing supporting performance is reduced, the bearing vibration caused by disturbance factors is amplified when the bearing runs at high speed, the bearing or the machine is possibly damaged, and the limit rotating speed limit of the bearing is often the bottleneck of the rotating speed of the machine.
In the prior art, the rotating speed of a bearing is mostly improved by changing a cooling or lubricating mode, for example, a circulating oil mist subjected to heat exchange by a heat exchanger is used for lubricating a bearing rolling body, and heat is taken away while lubrication is carried out; using a low coefficient of friction cage to reduce friction and thereby reduce heat generation; also, the use of harder bearing steel subjected to surface nitriding for the production of rolling elements, inner and outer races, smoother surface working, etc. has been used to increase the rotational speed limit of bearings. These methods are either complicated in form, require a complicated lubricating and cooling structure to be designed in the bearing mounting structure, have limited rotational speed increase, or have great requirements on processing manufacturability, and are not perfect economically or in use convenience. It is a challenge to the bearing industry how to structurally raise the bearing rotational speed limit.
Disclosure of Invention
The invention aims to provide a self-lubricating high-speed bearing to solve the problems in the prior art.
In order to achieve the purpose, the invention provides the following technical scheme:
a self-lubricating high-speed bearing is of a double-layer rolling body structure. When the bearing rotational speed is higher, if only one deck rolling element, the rotational speed difference of that layer of rolling element both sides is great, and the rotation speed of rolling element around the bearing axis are all higher, and some slight disturbance or device vibration can be enlargied in rolling element department, lead to the bearing vibration stronger, and the heat that the friction produced is concentrated moreover, and the rolling element is the bulging deformation easily, is unfavorable for the bearing and uses steadily.
Further, the self-lubricating high-speed bearing comprises an inner ring, a first rolling body, a differential ring, a second rolling body and an outer ring; the inner ring, the differential ring and the outer ring are all annular, the axes of the inner ring, the differential ring and the outer ring are coincident, the inner ring is positioned in the differential ring, and the differential ring is positioned in the outer ring; the first rolling element is disposed between the inner race and the differential ring, and the second rolling element is disposed between the differential ring and the outer race.
When there is only one layer of rolling bodies, reference is made to the most basic structure of the prior art bearing: the inner ring rotates synchronously along with the rotating shaft, the outer ring is static, the rotation angular speed of the rolling body axis around the bearing axis is approximately half of that of the inner ring (when the diameter of the inner ring is larger than the rotation radius of the rolling body, the approximation can be made, the description is qualitative analysis and excessive calculation description is not needed), then the rotation angular speed is converted into the rolling body axis linear speed and then divided by the self radius to obtain the rotation angular speed, when the rotation speed of the inner ring is very large, the angular speed of the rolling body is also very large, if the rolling body vibrates during operation due to the fact that fine foreign matters and the like enter the rolling body or the processing errors on the structure cause the rolling body to operate, the structure is possibly damaged when the rolling body operates at high speed, the rotation speed is large, the friction power is also large, the heating value is high, when the heating play, basically, the above two aspects (vibration and heat generation) restrict the rotating speed of the bearing, other similar lubricating conditions and the like can use the lubricating conditions in the prior art, and the maximum rotating speed of the bearing caused by the lubricating conditions is not limited in the discussion range of the invention. Can reduce the biggest rotation speed of rolling element during double-deck rolling element, be favorable to stable in structure because the differential ring acts as an intermediate member, and the differential ring is as a rotary part, and its rotational speed is zero to the median of inner circle rotational speed, specifically is that the zero several times of inner circle rotational speed need according to the structure size: the diameters of the inner ring, the differential ring and the outer ring and the rotating diameters of the first rolling body and the second rolling body are determined and are only one theoretical nominal value, and the rotating speed of the differential ring can fluctuate due to different friction conditions of the first rolling body and the second rolling body in actual use, so that qualitative analysis can be performed only. The differential ring has a rotation speed, so that the rotation speed difference of two sides of the first rolling body can be greatly reduced, the rotation angular speed of the first rolling body can be greatly reduced (but the rotation of the first rolling body around the axis of the bearing is basically unchanged), and similarly, the rotation speed of the second rolling body is also smaller, so that the double-layer rolling body structure can enhance the rotation stability of the first rolling body and the second rolling body, reduce the vibration of the bearing, and the heat generation is distributed at two positions, so that the cooling is better carried out.
Furthermore, the self-lubricating high-speed bearing further comprises two groups of end face supporting assemblies, the end face supporting assemblies are respectively fixed on two end faces of the outer ring, and the end face supporting assemblies are in rolling contact with two end faces of the differential ring. The inner ring can be axially positioned through a positioning component in the form of a shaft sleeve and the like, the outer ring can also be statically arranged on a shell of a machine, the differential ring is different from a rotating shaft and is also a static component because the rotating speed of the differential ring is different from that of the rotating shaft, the assembly difficulty of the bearing is greatly increased if the first rolling body or the second rolling body is used for axially positioning the differential ring, and the rolling support performance of the rolling bodies can be influenced if the rolling bodies are used for axially positioning the differential ring, so that the differential ring is arranged on two end faces of the outer ring and is axially supported by the end face support components, the differential ring is a differential ring support structure which is stable in structure and convenient to install, and the end face support components can be considered as two.
Furthermore, the first rolling body comprises a plurality of rollers and a first retainer, the rollers are stepped cylinders and comprise a middle section and a conical section, the conical section is arranged at two ends of the middle section, the diameter of the middle section is larger than the maximum diameter of the conical section, the large-diameter end of the conical section is connected with the middle section, and a plurality of roller grooves for containing the rollers are uniformly distributed on the circumference of the first retainer; the two ends of the inner surface of the differential ring are provided with differential ring working inclined planes which are contacted with the conical section, the middle part of the outer surface of the differential ring is contacted with the second rolling body, the end surface of the differential ring is provided with a differential ring groove, and the differential ring groove is annular; the second rolling body comprises a plurality of roller pins and a second retainer, the roller pins are contacted with the middle part of the outer surface of the differential ring, and a plurality of roller pin grooves for accommodating the roller pins are uniformly distributed on the circumference of the second retainer; the end face supporting component comprises a ring body and a thrust rolling body, the ring body comprises a stepped hole arranged on one side, the stepped hole comprises a positioning surface, a first bottom surface, a second bottom surface and an inner hole surface, the positioning surface is sleeved on an outer cylindrical surface of an outer ring, the first bottom surface is abutted against the end face of the outer ring, a ring body groove is formed in the second bottom surface and is annular, the ring body groove is opposite to the differential ring groove, the thrust rolling body comprises a plurality of rolling balls and a third retainer, the rolling balls are arranged in the third retainer, the rolling balls are respectively in contact with the ring body groove and the differential ring groove, and the hole diameter of the inner hole surface.
The roller is designed into a step shape so as to further reduce the rotating speed of the differential ring, and the design concept is as follows: the large-diameter section of the roller is contacted with the inner ring, the rotating speed of the inner ring is transmitted through the linear speed on the large-diameter section of the roller, and the roller is of an integral structure, so that the conical section and the middle section have the same rotation angular speed, the linear speed transmitted to the outer edge of the conical section is reduced in proportion once, and the linear speed of the outer edge of the conical section is transmitted to the differential ring again to cause the differential ring to rotate. The conical section of the roller is matched with the working inclined surface of the differential ring, so that the axial position of the first rolling body on the differential ring can be axially positioned, and because the contact surface of the roller and the differential ring is the outer circular surface of the conical section rather than the outer circular surface of the middle section, the middle section of the roller, which is accommodated in the annular groove, is arranged in the middle of the inner surface of the differential ring; the differential ring groove is used for contacting with the end face supporting component, the ring body is a static part of the end face supporting component and is fixed to two ends of the outer ring through screws and the like, one side of the thrust rolling body is contacted with the ring body, and the other side of the thrust rolling body is contacted with the differential ring groove to axially support the differential ring. The positioning surface is axially matched with the outer cylindrical surface hole of the outer ring to perform radial positioning; the first bottom surface is abutted against the two ends of the outer ring for axial positioning. The bore diameter of the inner bore surface is greater than the inner diameter of the inner ring to ensure that a shaft mounted in the inner ring does not contact the stationary ring body during use.
Furthermore, a plurality of first lubricating grooves are formed in the first retaining frame, the first lubricating grooves are located on the contact surface of the first retaining frame and the roller, and two ends of each first lubricating groove are respectively connected with the inner wall and the outer wall of the first retaining frame; a plurality of second lubricating grooves are formed in the second retainer, the second lubricating grooves are located on the contact surface of the second retainer and the roller pins, and two ends of each second lubricating groove are connected with the inner wall and the outer wall of the second retainer respectively; and a plurality of third lubricating grooves are formed in the third retainer, the third lubricating grooves are positioned on the contact surface of the third retainer and the rolling balls, and two ends of each third lubricating groove are respectively connected with two end surfaces of the third retainer. Because the retainer can only rotate around the axis of the inner ring and cannot be provided with a special structure at each roller groove or each needle groove and each rolling ball groove to rotate around the axes of the roller, the roller pin and the rolling ball, the first retainer can be in sliding contact with the roller, the second retainer can be in sliding contact with the roller pin, and the third retainer can be in sliding contact with the rolling ball, and the lubricating grooves arranged on the contact surfaces can reduce the sliding contact area on one hand and allow lubricating grease on the surfaces of the roller, the roller pin and the rolling ball to pass through on the other hand so as to fully lubricate the rolling elements. Taking the first retainer and the roller as an example, the first lubricating groove allows grease between the inner ring and the differential ring to pass through, the grease on the surface of the roller is in a strip shape after passing through the first lubricating groove, the amount of the grease is large, the roller is used for lubricating when contacting with the inner ring or the differential ring, if the first lubricating groove is not provided, the contact part of the first retainer and the roller can completely scrape the grease on the surface of the roller, the grease of the first rolling body layer is accumulated on two side lines of the first retainer, which are diagonally opposite to the inner wall surface and the outer wall surface of the roller groove, when the remaining amount of the grease in the bearing is large, the remaining amount of the grease in the bearing is still enough, and when the grease is consumed for a while, most of the rotating surface of the roller cannot be lubricated, so that the temperature of the bearing is rapidly increased, and then the bearing is damaged. The principle of the second lubricating groove and the third lubricating groove is the same as that of the first lubricating groove; the retainer is made of nylon, so that the retainer is light in texture and small in friction coefficient, and the retainer is made of a material with lubricating property.
Preferably, the first lubricating groove is obliquely arranged, and the second lubricating groove is obliquely arranged. The first lubricating groove arranged obliquely can make the grease move some distance along the axis of the roller when passing through the first lubricating groove, so as to paint some roller surfaces which are scraped by the first retainer to remove the grease; the design concept that the second lubricating groove is obliquely arranged is the same as that of the first lubricating groove.
Furthermore, two ends of the outer surface of the inner ring are provided with inner ring inclined planes, and the diameter of one side, close to the end face of the inner ring, of each inner ring inclined plane is smaller than that of one side, far away from the end face of the inner ring, of each inner ring inclined plane; the two ends of the outer surface of the differential ring are provided with differential ring outer inclined planes, and the diameter of one side of the differential ring outer inclined plane, which is close to the end face of the differential ring, is smaller than the diameter of one side of the differential ring outer inclined plane, which is far away from the end face of the differential ring. The inner ring inclined plane can facilitate the assembly of the inner ring, the inner ring inclined plane has a guiding function for the first rolling element, and the design of the form ensures that the inner ring and other parts in the bearing are separable in the actual use process, and the inner ring can be detached without detaching other parts of the bearing under the conditions of maintenance and the like, because the inner ring is often arranged on the shaft in an interference fit manner when the bearing is actually used, the rotor assembly of the machine can be detached and installed on site conveniently in the separable form of the inner ring; the outer inclined surface of the differential ring can also play a guiding role, and the second rolling body is not easy to damage when the differential ring is axially arranged in the second rolling body.
Preferably, the inclined angle of the inner ring inclined plane and the inclined angle of the differential ring outer inclined plane relative to the axis of the inner ring are 15-20 degrees. 15~20 inclination has the guide effect concurrently and retrencies the inclined plane size: if the inclination angle is too large, the guiding effect is reduced, the inclined surface can damage the rolling body when colliding with the rolling body, and if the inclination angle is too small, the axial length of the inclined surface is longer under the same chamfering depth, the structures at the two ends of the inner ring and the differential ring are longer, and the part does not work in the bearing operation process, and the size and the weight of the bearing are increased.
Furthermore, the side of the outer ring is provided with a plurality of grease injection holes, the grease injection holes penetrate through the wall surface of the outer ring, and the grease injection holes are positioned between the two end face supporting components. Annotate the fat hole and can make things convenient for the external world to add lubricating grease to the bearing, in concrete machinery, also radially set up a through-hole on the casing of bearing installation position department, will annotate the hole of fat hole and the pore pair on the casing when this bearing of installation, just so the external world can be followed and annotated the hole and add lubricating grease toward the bearing in, add the hole that finishes on the back with the casing and seal can. The adding mode does not need to disassemble the machine, and is very convenient.
Furthermore, 4, 6 or 8 grease injection holes are arranged and are uniformly distributed along the circumference of the axis of the outer ring; the axis of the grease injection hole is vertical to the outer ring, and threads are arranged on one side of the grease injection hole, which is close to the outer wall surface of the outer ring; the grease injection hole is internally provided with a screw plug. 4. The 6 or 8 grease injection holes can be selected by a user conveniently, and more than two corresponding holes can be formed in the shell and are used as spare holes in actual use; the other 4, 6 or 8 are the number of circumferentially equispaced openings commonly used in industrial machines. When the grease injection hole is not used, a screw plug is used for sealing, sealing strips such as a raw material strip are preferably wound on the screw plug before screwing in, the screw plug is reliable in sealing, when grease is required to be injected and then taken out, and under the condition that the screw plug is additionally arranged, a corresponding hole in the shell is larger and at least larger than the major diameter of the screw plug. In addition, a cooling area is constructed by the outer ring, the shell and the two end face supporting components, the cooling area can be used for cooling after being isolated relative to the interior of the bearing by using the screw plugs, more than two corresponding holes are formed in the shell, cooling water is introduced into the shell in one inlet and one outlet, the bearing can be cooled when the machine operates, and the water-cooled cooling effect is good.
Furthermore, an O-shaped ring is arranged between the outer ring and the end face supporting assembly and is located at the junction of the positioning face and the first bottom face. The O-shaped ring seals the contact surface of the outer ring and the end face supporting component, and cooling water is prevented from leaking from a cooling area to the inside of the bearing.
Compared with the prior art, the invention has the beneficial effects that: the invention uses the double-layer rolling body structure to radially support the rotating shaft, thereby greatly reducing the rotation speed of each layer of rolling body and reducing the vibration and the heat productivity; the end face supporting component reliably supports the differential ring in the axial direction, so that the stability of the bearing structure is ensured; the arrangement of the lubricating grooves on the retainer can reduce the contact area of the retainer and the roller, the rolling needle or the rolling ball so as to reduce the friction force, and meanwhile, the lubricating grooves can allow the lubricating grease on the surface of the roller, the rolling needle or the rolling ball to pass through, so that the lubricating grease is uniformly coated on the surface of the roller, the rolling needle or the rolling ball; the grease injection hole in the outer ring is convenient for the outside to add lubricating grease to the bearing, and after the grease injection hole is sealed by the screw plug, the annular area formed by the outer ring, the shell and the two end face supporting assemblies can be used for cooling the bearing when the machine runs, and the water cooling effect is greatly superior to that of traditional air cooling and lubricating oil cooling.
Drawings
In order that the present invention may be more readily and clearly understood, a more particular description of the invention briefly described above will be rendered by reference to specific embodiments that are illustrated in the appended drawings.
FIG. 1 is a cross-sectional structural view of the present invention;
FIG. 2 is view A of FIG. 1;
FIG. 3 is a cross-sectional structural view of the differential ring of the present invention;
FIG. 4 is a front view of the roller of the present invention;
FIG. 5 is view B of FIG. 1;
FIG. 6 is a cross-sectional view of the end support assembly of the present invention;
FIG. 7 is an exploded view of the present invention;
FIG. 8 is a perspective cross-sectional structural view of the present invention;
FIG. 9 is a perspective view of a first rolling element of the present invention;
FIG. 10 is view C of FIG. 9;
FIG. 11 is view C of FIG. 9 with the rollers removed;
FIG. 12 is view D of FIG. 7;
FIG. 13 is view E of FIG. 7;
FIG. 14 is view G of FIG. 7;
fig. 15 is a view showing an installation structure of the present invention.
In the figure: 1-inner ring, 11-inner ring inclined plane, 2-first rolling body, 21-roller, 211-middle section, 212-conical section, 22-first retainer, 221-first lubricating groove, 3-differential ring, 31-differential ring working inclined plane, 32-differential ring outer inclined plane, 33-differential ring groove, 4-second rolling body, 41-rolling needle, 42-second retainer, 421-second lubricating groove, 5-outer ring, 51-grease injection hole, 6-end surface support component, 61-ring body, 611-positioning surface, 612-first bottom surface, 613-second bottom surface, 614-ring body groove, 615-inner hole surface, 62-thrust rolling body, 621-rolling ball, 622-third retainer, 6221-third lubricating groove, 7-O-shaped ring, 8-plug screw, 90-shaft, 91-bearing, 92-bearing gland, 93-shell and 94-connecting pipe.
Detailed Description
The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
As shown in fig. 1, 7 and 8, a self-lubricating high-speed bearing comprises an inner ring 1, a first rolling body 2, a differential ring 3, a second rolling body 4 and an outer ring 5; the inner ring 1, the differential ring 3 and the outer ring 5 are all annular and have coincident axes, the inner ring 1 is positioned in the differential ring 3, and the differential ring 3 is positioned in the outer ring 5; the first rolling elements 2 are arranged between the inner ring 1 and the differential ring 3, and the second rolling elements 4 are arranged between the differential ring 3 and the outer ring 5.
Can reduce the biggest rotation speed of rolling element during double-deck rolling element, be favorable to stable in structure because differential ring 3 acts as an intermediate member, and differential ring 3 is as a rotary part, and its rotational speed is zero to the median of 1 rotational speed of inner circle, specifically is that several times of zero of 1 rotational speed of inner circle need according to the structure size: the diameters of the inner ring 1, the differential ring 3 and the outer ring 5, and the rotating diameters of the first rolling body 2 and the second rolling body 4 are determined, and are only a theoretical nominal value, and the rotating speed of the differential ring 3 can fluctuate due to different friction conditions of the first rolling body 2 and the second rolling body 4 in actual use, so that only qualitative analysis can be performed. The differential ring 3 has a single rotational speed, and can greatly reduce the rotational speed difference between both sides of the first rolling element 2, so that the rotational angular speed of the first rolling element 2 can be greatly reduced (but the rotation thereof around the axis of the bearing 91 is basically unchanged), and similarly, the rotational speed of the second rolling element 4 is also small, so that the double-layer rolling element structure can enhance the rotational stability of the first rolling element 2 and the second rolling element 4, reduce the vibration of the bearing 91, and distribute the heat generation at two positions, so that the cooling is better performed.
As shown in fig. 1, 7 and 8, the self-lubricating high-speed bearing further includes two sets of end face support assemblies 6, the end face support assemblies 6 are respectively fixed on two end faces of the outer ring 5, and the end face support assemblies 6 are in rolling contact with two end faces of the differential ring 3. The inner ring 1 can be axially positioned by a positioning component in the form of a shaft sleeve and the like, the outer ring 5 can also be statically installed on a shell 93 of a machine, the differential ring 3 is different from a rotating shaft and is not a static component because the rotating speed is different from that of a rotating shaft, the assembly difficulty of the bearing 91 is greatly increased if the first rolling body 2 or the second rolling body 4 is used for axially positioning the differential ring, and the rolling support performance of the rolling bodies can be influenced if the rolling bodies are used for axially positioning the differential ring 3, so that the differential ring 3 is axially supported by the end face support components 6 arranged on two end faces of the outer ring 5, the differential ring 3 is a differential ring 3 support structure which is stable in structure and convenient to install, and the end face support components 6 can be considered as two thrust bearings arranged on the.
As shown in fig. 2, 9 and 10, the first rolling element 2 includes a plurality of rollers 21 and a first retainer 22, as shown in fig. 4, the roller 21 is a stepped cylinder, and includes a middle section 211 and a conical section 212, the conical sections 212 are disposed at two ends of the middle section 211, the diameter of the middle section 211 is larger than the maximum diameter of the conical section 212, the large-diameter end of the conical section 212 is connected with the middle section 211, and a plurality of roller grooves are uniformly distributed on the circumference of the first retainer 22 for accommodating the rollers 21; as shown in fig. 1 and 3, the differential ring working inclined surfaces 31 are arranged at two ends of the inner surface of the differential ring 3, the differential ring working inclined surfaces 31 are in contact with the conical section 212, the middle part of the outer surface of the differential ring 3 is in contact with the second rolling elements 4, the differential ring grooves 33 are arranged on the end surfaces of the differential ring 3, and the differential ring grooves 33 are annular; the second rolling body 4 comprises a plurality of roller pins 41 and a second retainer 42, the roller pins 41 are contacted with the middle part of the outer surface of the differential ring 3, and a plurality of roller pin grooves are uniformly distributed on the circumference of the second retainer 42 and used for accommodating the roller pins 41; as shown in fig. 6, the end face support assembly 6 includes a ring body 61 and a thrust rolling body 62, the ring body 61 includes a stepped hole on one side, a positioning surface 611 is included in the stepped hole, a first bottom surface 612, a second bottom surface 613, and an inner hole surface 615, the positioning surface 611 is sleeved on an outer cylindrical surface of the outer ring 5, the first bottom surface 612 abuts against the end face of the outer ring 5, a ring body groove 614 is provided on the second bottom surface 613, the ring body groove 614 is annular, the ring body groove 614 faces the differential ring groove 33, the thrust rolling body 62 includes a plurality of rolling balls 621 and a third retainer 622, the rolling balls 621 are provided in the third retainer 622, the rolling balls 621 respectively contact with the ring body groove 614 and the differential ring groove 33, and the aperture of the inner hole. The rollers 21 are designed into a step shape so as to further reduce the rotating speed of the differential ring 3, and the design idea is as follows: the large-diameter section of the roller 21 is in contact with the inner ring 1, the rotating speed of the inner ring 1 is transmitted through the linear speed on the middle section 211 of the roller 21, and the roller 21 is of an integral structure, so that the conical section 212 and the middle section 211 have the same rotation angular speed, the linear speed transmitted to the outer edge of the conical section 212 is reduced in proportion once, and the linear speed of the outer edge of the conical section 212 is transmitted to the differential ring 3 again to cause the differential ring 3 to rotate. The conical section 212 of the roller 21 is matched with the working inclined surface 31 of the differential ring to axially position the axial position of the first rolling body 2 on the differential ring 3, and because the contact surface of the roller 21 and the differential ring 3 is the outer circular surface of the conical section 212 rather than the outer circular surface of the middle section 211, an annular groove is arranged in the middle of the inner surface of the differential ring 3 to accommodate the middle section of the roller 21; the differential ring groove 33 is a feature of the differential ring 3 for contacting the end face support member 6, the ring body 61 is a stationary portion of the end face support member 6, and is fixed to both ends of the outer ring 5 by screws or the like, and the thrust rolling bodies 62 contact the ring body 61 on one side and the differential ring groove 33 on the other side to axially support the differential ring 33; the positioning surface 611 is axially matched with an outer cylindrical surface hole of the outer ring 5 for radial positioning; the first bottom surface 612 is axially positioned against both ends of the outer race 5. The bore surface 615 having a larger diameter than the inner diameter of the inner ring 1 ensures that the shaft 90 mounted in the inner ring 1 does not touch the stationary ring body 61 during use, as shown in fig. 15.
As shown in fig. 10 and 11, the first holder 22 is provided with a plurality of first lubrication grooves 221, the first lubrication grooves 221 are located on the contact surface between the first holder 22 and the rollers 21, and both ends of the first lubrication grooves 221 are respectively connected with the inner wall and the outer wall of the first holder 22; as shown in fig. 13, the second retainer 42 is provided with a plurality of second lubrication grooves 421, the second lubrication grooves 421 are located on the contact surface between the second retainer 42 and the needle roller 41, and two ends of the second lubrication grooves 421 are respectively connected with the inner wall and the outer wall of the second retainer 42; as shown in fig. 12, the third holder 622 is provided with a plurality of third lubrication grooves 6221, the third lubrication grooves 6221 are located on the contact surface between the third holder 622 and the rolling balls 621, and both ends of the third lubrication grooves 6221 are connected to both end surfaces of the third holder 622, respectively. Because the retainer can only rotate around the axis of the inner ring 1 and a special structure cannot be arranged at each roller groove or the roller groove and the rolling ball 621 to rotate around the axes of the roller 21, the rolling needle 41 and the rolling ball 621, the first retainer 22 and the roller 21, the second retainer 42 and the rolling needle 41 and the third retainer 622 can be in sliding contact with the rolling ball 621, and the lubricating grooves arranged on the contact surfaces can reduce the sliding contact area on one hand and allow grease on the surfaces of the roller 21, the rolling needle 41 and the rolling ball 621 to pass through so as to fully lubricate the rolling bodies on the other hand. Taking the first cage 22 and the roller 21 as an example, the first lubrication groove 221 allows grease between the inner ring 1 and the differential ring 3 to pass through, the grease on the surface of the roller 21 is stripped and has a large amount after passing through the first lubrication groove 221, the roller 21 is used for lubrication when contacting with the inner ring 1 or the differential ring 3, if the first lubrication groove 221 is not provided, the grease on the surface of the roller 21 is scraped off completely at the contact position of the first cage 22 and the roller 21, a large amount of grease of the first rolling element 2 layer is accumulated on two strip lines of the first cage 22 where the inner and outer wall surfaces of the roller groove are diagonally opposed, when the remaining amount of grease in the bearing 91 is still large, and when the grease is consumed for a while, the rotating surface of the roller 21 is mostly un-lubricated, the temperature of the bearing 91 is rapidly increased, and then the bearing 91 is damaged. The second lubricating groove 421 and the third lubricating groove 6221 are the same in principle as the first lubricating groove 221; the retainer is made of nylon, so that the retainer is light in texture and small in friction coefficient, and the retainer is made of a material with lubricating property.
As shown in fig. 11, the first lubrication groove 221 is inclined, and the second lubrication groove 421 is inclined. The first grease groove 221, which is disposed obliquely, allows grease to move some distance along the axis of the roller 21 while passing through the first grease groove 221, thereby smearing some of the grease on the surface of the roller 21 where the grease is scraped off by the first cage 22; the second lubrication groove 421 is inclined in the same design concept as the first lubrication groove 221.
As shown in fig. 1 and 2, two outer ends of the inner ring 1 are provided with inner ring inclined planes 11, and the diameter of one side of the inner ring inclined plane 11, which is close to the end surface of the inner ring 1, is smaller than the diameter of one side of the inner ring inclined plane 11, which is far away from the end surface of the inner ring 1; as shown in fig. 2 and 3, the differential ring outer inclined surfaces 32 are disposed at two ends of the outer surface of the differential ring 3, and the diameter of the differential ring outer inclined surfaces 32 near the end surface of the differential ring 3 is smaller than the diameter of the differential ring outer inclined surfaces 32 far from the end surface of the differential ring 3. The inner ring inclined plane 11 can facilitate the assembly of the inner ring 1, the inner ring inclined plane 11 has a guiding function for the first rolling element 2, and the design of the form enables the inner ring 1 and other components in the bearing 91 to be in a separable form in the actual use process, and the inner ring 1 can be detached without detaching other parts of the bearing 91 under the conditions of maintenance and the like, because the inner ring 1 is often installed on a shaft in an interference fit manner when the bearing 91 is actually used, the rotor assembly of a machine can be detached and installed on site conveniently in the separable form of the inner ring 1; the differential ring outer inclined surface 32 also serves as a guide, so that the second rolling elements 4 are not easily damaged when the differential ring 3 is axially inserted into the second rolling elements 4.
The inclined angles of the inner ring inclined plane 11 and the differential ring outer inclined plane 32 relative to the axis of the inner ring 1 are 15-20 degrees. 15~20 inclination has the guide effect concurrently and retrencies the inclined plane size: if the inclination angle is too large, the guiding effect is reduced, the inclined surface can damage the rolling body when colliding with the rolling body, and if the inclination angle is too small, the axial length of the inclined surface is longer under the same chamfering depth, the structures at the two ends of the inner ring 1 and the differential ring 3 are longer, and the part is not effective in the operation process of the bearing 91, and the size and the weight of the bearing 91 are increased.
As shown in fig. 5, the lateral surface of the outer ring 5 is provided with a plurality of grease injection holes 51, the grease injection holes 51 penetrate through the wall surface of the outer ring 5, and the grease injection holes 51 are located between the two end face support assemblies 6. The grease injection hole 51 can facilitate the external addition of lubricating grease to the bearing 91, as shown in fig. 15, in a specific machine, a through hole is also radially arranged on the housing 93 at the installation position of the bearing 91, when the bearing 91 is installed, the grease injection hole 51 is aligned with the hole on the housing 93, so that the external can add lubricating grease into the bearing from the grease injection hole 52, and after the addition is finished, the hole on the housing 93 is closed. The adding mode does not need to disassemble the machine, and is very convenient. 4. The 6 or 8 grease injection holes 51 can be selected by a user conveniently, and more than two corresponding holes can be formed in the shell 93 and are used as spare holes in actual use; the other 4, 6 or 8 are the number of circumferentially equispaced openings commonly used in industrial machines. When the grease injection hole 51 is not used, the screw plug 8 is used for sealing, sealing strips such as raw material strips are preferably wound on the screw plug 8 before screwing in, the screw plug 8 is sealed and reliable, when grease is required to be injected, the screw plug 8 is taken out, and under the condition that the screw plug 8 is additionally arranged, a corresponding hole in the shell 93 is larger in size and at least larger than the major diameter of the screw plug 8, so that the screw plug 8 can be conveniently taken out by using tools from the hole in the shell 93. In addition, the outer ring 5, the housing 93 and the two end face support assemblies 6 form a cooling area, as shown in fig. 15, after the cooling area is isolated from the interior of the bearing 91 by using the screw plugs 8, the cooling area can be used for cooling, more than two corresponding holes are formed in the housing 93, cooling water is introduced into the housing at one time, so that the bearing 91 can be cooled when the machine runs, and the water-cooling effect is good.
4, 6 or 8 grease injection holes 51 are arranged, and the grease injection holes 51 are uniformly distributed along the circumference of the axis of the outer ring 5; as shown in fig. 5 and 14, the axis of the grease injection hole 51 is perpendicular to the outer ring 5, and a thread is arranged on one side of the grease injection hole 51 close to the outer wall surface of the outer ring 5; the grease injection hole 51 is internally provided with a screw plug 8.
As shown in fig. 5, an O-ring 7 is disposed between the outer ring 5 and the end face support assembly 6, and the O-ring 7 is located at the intersection of the positioning surface 611 and the first bottom surface 612. The O-ring 7 seals the contact surface between the outer ring 5 and the end face support member 6, and prevents cooling water from leaking from the cooling area into the bearing 91.
When the bearing is used, the inner ring 1 is sleeved on the shaft 90 and is positioned in a shaft sleeve mode and the like, then the end face support assembly 6 on one side abuts against a positioning spigot on the shell 93, a certain amount of lubricating grease is added to the position of the rolling body, and then the end face support assembly 6 on the other side is pressed tightly by using a bearing gland.
It will be evident to those skilled in the art that the invention is not limited to the details of the foregoing illustrative embodiments, and that the present invention may be embodied in other specific forms without departing from the spirit or essential attributes thereof. The present embodiments are therefore to be considered in all respects as illustrative and not restrictive, the scope of the invention being indicated by the appended claims rather than by the foregoing description, and all changes which come within the meaning and range of equivalency of the claims are therefore intended to be embraced therein. Any reference sign in a claim should not be construed as limiting the claim concerned.
Claims (6)
1. A self-lubricating high speed bearing characterized by: the self-lubricating high-speed bearing is of a double-layer rolling body structure;
the self-lubricating high-speed bearing comprises an inner ring (1), a first rolling body (2), a differential ring (3), a second rolling body (4) and an outer ring (5); the inner ring (1), the differential ring (3) and the outer ring (5) are all annular, the axes of the inner ring, the differential ring (3) and the outer ring are coincident, the inner ring (1) is positioned in the differential ring (3), and the differential ring (3) is positioned in the outer ring (5); the first rolling body (2) is arranged between the inner ring (1) and the differential ring (3), and the second rolling body (4) is arranged between the differential ring (3) and the outer ring (5); the self-lubricating high-speed bearing also comprises two groups of end face supporting assemblies (6), the end face supporting assemblies (6) are respectively fixed on two end faces of the outer ring (5), and the end face supporting assemblies (6) are in rolling contact with two end faces of the differential ring (3);
the first rolling body (2) comprises a plurality of rollers (21) and a first retainer (22), the rollers (21) are stepped cylinders and comprise middle sections (211) and conical sections (212), the conical sections (212) are arranged at two ends of each middle section (211), the diameter of each middle section (211) is larger than the maximum diameter of each conical section (212), the large-diameter ends of the conical sections (212) are connected with the middle sections (211), and a plurality of roller grooves are uniformly distributed on the circumference of the first retainer (22) and used for containing the rollers (21); the two ends of the inner surface of the differential ring (3) are provided with differential ring working inclined planes (31), the differential ring working inclined planes (31) are in contact with a conical section (212), the middle part of the inner surface of the differential ring (3) is provided with an annular groove, the middle section (211) is arranged in the annular groove, a gap is arranged between the outer surface of the middle section (211) and the annular groove, the middle part of the outer surface of the differential ring (3) is in contact with the second rolling body (4), the end surface of the differential ring (3) is provided with a differential ring groove (33), and the differential ring groove (33) is annular; the second rolling body (4) comprises a plurality of rolling needles (41) and a second retainer (42), the rolling needles (41) are in contact with the middle part of the outer surface of the differential ring (3), and a plurality of rolling needle grooves are uniformly distributed on the circumference of the second retainer (42) and used for accommodating the rolling needles (41); the end face support assembly (6) comprises a ring body (61) and a thrust rolling body (62), the ring body (61) comprises a step hole arranged at one side, the step hole comprises a positioning surface (611), a first bottom surface (612), a second bottom surface (613) and an inner hole surface (615), the positioning surface (611) is sleeved on the outer cylindrical surface of the outer ring (5), the first bottom surface (612) abuts against the end surface of the outer ring (5), the second bottom surface (613) is provided with a ring body groove (614), the ring body groove (614) is annular, the ring body groove (614) is opposite to the differential ring groove (33), the thrust rolling body (62) comprises a plurality of rolling balls (621) and a third retainer (622), the rolling balls (621) are arranged in the third retainer (622), the rolling balls (621) are respectively contacted with the ring body groove (614) and the differential ring groove (33), and the aperture of the inner hole surface (615) is larger than the inner diameter of the inner ring (1);
a plurality of first lubricating grooves (221) are formed in the first retainer (22), the first lubricating grooves (221) are located on the contact surface of the first retainer (22) and the roller (21), and two ends of each first lubricating groove (221) are respectively connected with the inner wall and the outer wall of the first retainer (22); a plurality of second lubricating grooves (421) are formed in the second retainer (42), the second lubricating grooves (421) are located on the contact surface of the second retainer (42) and the roller pin (41), and two ends of each second lubricating groove (421) are respectively connected with the inner wall and the outer wall of the second retainer (42); a plurality of third lubricating grooves (6221) are formed in the third retainer (622), the third lubricating grooves (6221) are positioned on the contact surface of the third retainer (622) and the rolling balls (621), and two ends of each third lubricating groove (6221) are respectively connected with two end surfaces of the third retainer (622);
the first lubricating groove (221) is obliquely arranged, and the second lubricating groove (421) is obliquely arranged; the first lubrication groove (221) arranged obliquely can enable the grease to move for a distance along the axis of the roller 21 when passing through the first lubrication groove (221), and the second lubrication groove (421) arranged obliquely can enable the grease to move for a distance along the axis of the roller pin (41) when passing through the second lubrication groove (421).
2. A self-lubricating high speed bearing according to claim 1, wherein: the two ends of the outer surface of the inner ring (1) are provided with inner ring inclined planes (11), and the diameter of one side, close to the end surface of the inner ring (1), of each inner ring inclined plane (11) is smaller than that of one side, far away from the end surface of the inner ring (1), of each inner ring inclined plane (11); the outer two ends of the outer surface of the differential ring (3) are provided with differential ring outer inclined planes (32), and the diameter of one side, close to the end face of the differential ring (3), of each differential ring outer inclined plane (32) is smaller than the diameter of one side, far away from the end face of the differential ring (3), of each differential ring outer inclined plane (32).
3. A self-lubricating high speed bearing according to claim 2, wherein: the inclination angles of the inner ring inclined plane (11) and the differential ring outer inclined plane (32) relative to the axis of the inner ring (1) are 15-20 degrees.
4. A self-lubricating high speed bearing according to claim 2, wherein: the side of outer lane (5) is equipped with a plurality of notes fat hole (51), annotate fat hole (51) and run through outer lane (5) wall, annotate fat hole (51) and be located between two terminal surface supporting component (6).
5. A self-lubricating high speed bearing according to claim 4, wherein: 4, 6 or 8 grease injection holes (51) are arranged, and the grease injection holes (51) are uniformly distributed along the circumference of the axis of the outer ring (5); the axis of the grease injection hole (51) is vertical to the outer ring (5), and threads are arranged on one side, close to the outer wall surface of the outer ring (5), of the grease injection hole (51); a screw plug (8) is arranged in the grease injection hole (51).
6. A self-lubricating high speed bearing according to claim 5, wherein: an O-shaped ring (7) is arranged between the outer ring (5) and the end face supporting component (6), and the O-shaped ring (7) is located at the junction of the positioning face (611) and the first bottom face (612).
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| CN201910213792.3A CN109838461B (en) | 2019-03-20 | 2019-03-20 | Self-lubricating high-speed bearing |
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| CN201910213792.3A CN109838461B (en) | 2019-03-20 | 2019-03-20 | Self-lubricating high-speed bearing |
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| CN109838461A CN109838461A (en) | 2019-06-04 |
| CN109838461B true CN109838461B (en) | 2020-12-11 |
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| CN110439927B (en) * | 2019-08-30 | 2020-06-23 | 乐清市钜派企业管理咨询有限公司 | High-speed bearing with oil mist channel on outer ring |
| JP7256933B2 (en) * | 2020-03-18 | 2023-04-13 | 隆志 浜口 | How to install bearings. |
| CN111810527A (en) * | 2020-07-16 | 2020-10-23 | 苏州轴承厂股份有限公司 | High-speed high-concentricity combined needle roller bearing assembly |
| CN113550983B (en) * | 2021-07-28 | 2022-11-29 | 云南科力环保股份公司 | Sectional long shaft connecting and supporting transmission device |
| CN114704547A (en) * | 2022-04-07 | 2022-07-05 | 南通鹏亚精密机械科技有限公司 | Anti-shaking retainer device for automatic carrying trolley and implementation method |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN88201554U (en) * | 1988-03-13 | 1988-11-23 | 郭德明 | Radial-thrust double layer composite rolling needle bearing |
| CN2846875Y (en) * | 2005-12-07 | 2006-12-13 | 王桂栋 | Double layer rolling bearing |
| CN201763820U (en) * | 2010-09-09 | 2011-03-16 | 郑广辉 | Bearing and retainer thereof |
| CN202132383U (en) * | 2011-06-20 | 2012-02-01 | 常州市武进永达机械轴承有限公司 | Double-layer self-aligning ball bearing |
| CN202140430U (en) * | 2011-07-06 | 2012-02-08 | 常州市武进永达机械轴承有限公司 | Double-layer long-cylinder roller bearing |
| CN103195818A (en) * | 2013-04-17 | 2013-07-10 | 金晓娜 | Roller bearing |
| CN203322046U (en) * | 2013-07-03 | 2013-12-04 | 济宁精益轴承有限公司 | Double-layer inner ring closely-arranged cylindrical roller bearing |
| DE102013224462A1 (en) * | 2013-11-28 | 2015-05-28 | Schaeffler Technologies AG & Co. KG | planetary roller bearings |
| CN205226061U (en) * | 2015-11-09 | 2016-05-11 | 王钢 | Decelerating bearing |
| RU2618813C1 (en) * | 2016-05-04 | 2017-05-11 | Юрий Петрович Адашкевич | Second type reinforced reduction radial thrust bearing |
| CN107830052B (en) * | 2017-12-05 | 2024-02-06 | 大连交通大学 | Composite bearing |
| CN108278270A (en) * | 2017-12-06 | 2018-07-13 | 郑帆 | A kind of side impact bearing with ball oil-bearing structure |
| CN207864435U (en) * | 2017-12-18 | 2018-09-14 | 常州市宏成滚针轴承厂 | A kind of needle roller convenient for heat dissipation |
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Address after: 213000 No.3, Fengming Road, Wujin national high tech Industrial Development Zone, Changzhou City, Jiangsu Province Patentee after: Jiangsu Chihua Technology Co.,Ltd. Address before: 213000 No.3, Fengming Road, Wujin national high tech Industrial Development Zone, Changzhou City, Jiangsu Province Patentee before: JIANGSU CHIHUA BEARING CO.,LTD. |