Multi-raceway precision bearing

Abstract

The utility model discloses a multi-raceway precision bearing which comprises an outer ring shell sleeve, an inner ring shell sleeve, an inner roller, a middle sliding block, an outer roller and a pressure pre-tightening mechanism. A pressure pre-tightening mechanism is arranged on the axial outer side in a necking-down type annular clamping channel between an outer ring shell sleeve and an inner ring shell sleeve and exerts radial and axial pre-tightening force on an inner roller and an outer roller at the same time, so that the inner roller and the outer roller can be tightly attached to an inner ring shell sleeve and the outer ring shell sleeve all the time, and then zero-approaching self-compensation adjustment of a clearance is achieved. The bearing precision stability is obviously enhanced, and the bearing has the advantages of being simple in structure, easy to adjust, high in adjusting precision, good in precision stability, high in durability and practicability and the like.

Description

Technical Field

[0001] The utility model relates to bearing equipment, in particular to a multi-roller precision bearing, belonging to the technical field of precision bearings. Background Art

[0002] Bearing is an important component in modern mechanical equipment. Its main function is to support the mechanical rotating body, reduce the friction coefficient during its movement, and ensure its rotation accuracy. Bearings are generally composed of four parts: outer ring, inner ring, rolling element and cage.

[0003] According to ISO's grading standards, bearings are divided into: P0, P6, P5, P4, P2, with the grades increasing in sequence, of which P0 is ordinary precision and the other grades are precision grades. Of course, different grading standards and different types of bearings have different grading methods, but the meaning is the same. The performance of precision bearings requires the rotating body to have high runout accuracy, high-speed rotation, and small friction and friction change.

[0004] Precision bearings have high requirements for use, especially for precision equipment, which has more stringent requirements on the accuracy fluctuation of precision bearings. Even extremely precise bearings will have larger bearing clearance after being used for a period of time due to the wear of the rolling elements and the inner and outer rings, and cannot meet the use requirements of precision equipment. Therefore, new precision bearings need to be replaced frequently. However, due to the high precision requirements of precision bearings themselves, their prices are relatively expensive. Frequent replacement greatly increases production costs and is not conducive to the continuous operation of precision equipment. Frequent replacement operations can also easily increase the connection error between the bearing and the precision equipment, which seriously affects the working accuracy of the precision equipment.

[0005] It is of great significance to realize the self-compensation adjustment of the bearing, thereby prolonging the service life of the bearing, reducing the production cost and improving the production efficiency. CN214118742U discloses an adaptive adjustment bearing, which mainly controls the depth of the first and second limit plates extending into the gap between the ball and the inner and outer walls by adjusting the spring and the movable plate to realize the compensation of the clearance, so as to improve the rotation accuracy of the bearing. After automatic adjustment, the ball is no longer directly in contact with the inner and outer walls, but contacts with multiple limit plates, which requires a high material of the limit plate to ensure that the wear and loss between the ball and each limit plate is consistent, otherwise it is difficult to continue to ensure the bearing accuracy; and because the limit plate is a movable part, the ball does not directly act on the inner and outer walls, resulting in a large gap between the inner and outer walls, and the effect of a tight bearing cannot be achieved. CN213332052U discloses a tapered roller bearing clearance adjustment structure, which provides a cavity in the outer ring of the bearing, and installs a spring and a ball perpendicular to the surface of the rolling body in the cavity, so as to apply a radial force to the rolling body so that the other side of the rolling body is always in contact with the inner ring wall of the bearing. In order to ensure the accuracy, a set of spring and ball mechanisms need to be provided for each rolling body, which has the disadvantages of complex structure, inconvenient maintenance and high preparation cost. In addition, since the spring is in direct contact with the surface of the rolling body through the ball, when the rolling body rotates, since the surfaces of the two adjacent rolling bodies are not in a plane, when the ball rolls between the two rolling bodies, the ball is stuck between the two rolling bodies, so that the rolling body cannot rotate. CN2735068Y discloses a single-row tapered roller bearing capable of maintaining a minimum clearance, which achieves a close fit between the roller and the inner and outer rings by pushing the inner ring with a spiral spring. The implementation of this solution must rely on the relative sliding between the inner ring and the shaft rod as a prerequisite. It is obviously not suitable for precision bearings in which the shaft rod and the inner ring are fixedly connected. Its applicability is limited and it cannot be used as a precision bearing.

[0006] In summary, the prior art still has many deficiencies in the self-compensation adjustment of precision bearings, and cannot meet the stability and durability of the precision self-compensation adjustment of precision bearings during long-term use. Utility Model Content

[0007] In view of the problems of poor stability and durability, high preparation cost and inconvenient maintenance and replacement in the existing technology for self-compensation adjustment of bearing precision, the utility model provides a multi-race precision bearing, which applies radial and axial pre-tightening forces to the inner roller and the outer roller by arranging a pressure pre-tightening mechanism on the axial outer side of the shrinking annular clamp between the outer ring shell and the inner ring shell, so that the inner roller and the outer roller can always fit tightly with the inner ring shell and the outer ring shell, thereby realizing self-compensation adjustment of the clearance to zero, significantly enhancing the stability of the bearing precision, and the overall structure is simple, maintenance and replacement are convenient, and the service life of the bearing is also significantly increased.

[0008] In order to achieve the above technical objectives, the technical solutions adopted by the present utility model are specifically described as follows:

[0009] A multi-race precision bearing, the bearing comprises an outer ring shell, an inner ring shell, an inner roller, an intermediate slider, an outer roller and a pressure preload mechanism. The outer ring shell is sleeved on the outside of the inner ring shell, and a constricted annular channel along the axial direction is formed between the radial inner wall of the outer ring shell and the radial outer wall of the inner ring shell. The intermediate slider is an annular slider arranged in the middle of the annular channel, an inner raceway is formed between the radial inner wall of the intermediate slider and the radial outer wall of the inner ring shell, and an outer raceway is formed between the radial outer wall of the intermediate slider and the radial inner wall of the outer ring shell. The inner roller is arranged in the inner raceway, and the outer roller is arranged in the outer raceway. The pressure preload mechanism is arranged at the wider axial outer end of the annular channel, and the axial inner end of the pressure preload mechanism is in contact and connected with the axial outer side of the intermediate slider.

[0010] Preferably, a plurality of inner rollers are evenly arranged along the circumferential direction of the inner ring shell, and the plurality of inner rollers are sequentially connected in series through an inner retaining frame to form a ring shape.

[0011] Preferably, a plurality of outer rollers are evenly arranged along the circumferential direction of the outer ring shell, and the plurality of outer rollers are sequentially connected in series through an outer retaining frame to form a ring shape.

[0012] Preferably, the axial cross section of the intermediate slider is an inverted trapezoidal surface, that is, the radial width of the axial cross section of the intermediate slider gradually decreases from the wide side end to the narrow side end of the annular clamp. Preferably, arc-shaped grooves that fit the inner roller and the outer roller are respectively provided on the radial inner wall and the radial outer wall of the intermediate slider.

[0013] Preferably, the depth of the arc-shaped groove on the radial inner wall of the middle slider is smaller than the radius of the inner roller. The depth of the arc-shaped groove on the radial outer wall of the middle slider is smaller than the radius of the outer roller.

[0014] Preferably, the pressure preload mechanism comprises a pressure transmission roller, a ring pressure block and a ring top plate. The pressure transmission roller, the ring pressure block and the ring top plate are all arranged at the wide side end in the annular channel and are located axially outside the middle slider. The axial inner side of the ring pressure block is connected to the axial outer side of the middle slider through the pressure transmission roller, and the axial outer side of the ring pressure block is connected to the axial inner side of the ring top plate through the preload elastic member. The radial sides of the ring top plate are respectively connected to the outer ring shell and the inner ring shell.

[0015] Preferably, the pressure preload mechanism includes a plurality of pressure transmission rollers, and in the circumferential direction, the plurality of pressure transmission rollers are connected in series in a ring shape through a roller retainer. Preferably, in the radial direction, a plurality of ring-shaped pressure transmission rollers are arranged between the ring pressure block and the intermediate slider. Preferably, the pressure transmission roller is a ball or a roller.

[0016] Preferably, a lower ring groove matching the pressure transmission roller is provided on the axial outer side surface of the middle slider in the circumferential direction.

[0017] Preferably, an upper ring groove matching the pressure transmission roller is provided on the axial inner side surface of the ring pressure block along the circumferential direction.

[0018] Preferably, the number of the lower ring grooves is consistent with the number of the upper ring grooves and corresponds one to one.

[0019] Preferably, a plurality of columnar protrusions are arranged in the middle of the axial outer side surface of the ring pressure block, which are evenly distributed in the circumferential direction and protrude outward in the axial direction. A preload elastic member is sleeved on each columnar protrusion, and the protrusion height of the columnar protrusion is not greater than the height of the preload elastic member after preload. Preferably, an annular edge protrusion whose height is lower than the columnar protrusion and extends in the circumferential direction is also arranged on the edge of the ring pressure block on both sides of the columnar protrusion in the radial direction, that is, a limiting groove for the preload elastic member to be placed is formed between the annular edge protrusion and the columnar protrusion (or a circle of annular limiting grooves for the preload elastic member to be placed is provided on the ring pressure block located around the bottom of the columnar protrusion).

[0020] Preferably, the preload elastic member is one of a spring, a tubular spring sheet or a tubular rubber body.

[0021] Preferably, an annular U-groove extending in the circumferential direction is provided on the axial inner side surface of the ring top plate, and the radial width of the annular U-groove is not less than the maximum radial outer diameter of the preload elastic member, so that the end of the preload elastic member away from the ring pressure block is completely sleeved inside the annular U-groove.

[0022] Preferably, the top plate is threadedly connected to the outer ring shell and the inner ring shell, and the width of the annular channel in the radial direction is consistent in the area where the threads are provided on the outer ring shell and the inner ring shell. Preferably, the axial downward depth of the threaded area provided on the side walls of the outer ring shell and the inner ring shell is greater than the maximum thickness of the top plate.

[0023] Preferably, a rotating protrusion and / or a rotating concave hole is further provided on the axial outer surface of the ring top plate, and the rotating protrusion and / or the rotating concave hole drive the ring top plate to rotate in the circumferential direction, thereby adjusting the depth of the ring top plate axially penetrating into the annular channel.

[0024] Preferably, multiple layers of inner rollers connected in series to form a ring are arranged along the axial direction of the annular clamping channel.

[0025] Preferably, multiple layers of outer rollers connected in series to form a ring are arranged along the axial direction of the annular clamping channel.

[0026] Preferably, the inner roller and the outer roller are each independently a ball or a roller.

[0027] Preferably, the axial cross-section of the annular channel is trapezoidal or triangular.

[0028] In the prior art, some precision equipment inevitably needs to use precision bearings to ensure the stability and durability of the operating accuracy of the precision equipment. However, after a period of use, the general precision bearings will have a larger bearing clearance due to friction loss and other reasons, which will affect the stability of the overall accuracy of the precision equipment. Frequent replacement has a large cost investment and causes problems such as poor fit between the bearing and the precision equipment. Some existing bearings with self-compensation functions either have poor accuracy stability, complex structure and high manufacturing cost, or poor durability and poor applicability and cannot be used as precision bearings. The utility model specifically provides a precision bearing with a bearing clearance pressure preload self-compensation mechanism (i.e., a pressure preload mechanism), which can automatically compensate for the change of the bearing clearance at any time through a preloaded elastic member, so that the change of the bearing clearance can be infinitely zeroed (almost unchanged, and then in the best state to maintain the operating accuracy), which greatly ensures the stability of the bearing accuracy, and the entire pressure preload mechanism can realize self-preload adjustment, with the characteristics of simple structure and durability. The precision bearing is an independent component. The inner ring and outer ring of the precision bearing only contact and act with other parts of the device, and cannot be directly connected and fixed; that is to say, the precision bearing requires that its inner ring and outer ring are relatively movable relative to the parts in contact with them.

[0029] In the utility model, the intermediate slider is a closed-loop annular slider extending circumferentially along the annular channel, and its axial cross-section is an inverted trapezoidal surface, that is, the radial width of the axial cross-section of the intermediate slider gradually decreases from the wide side end to the narrow side end of the annular channel (consistent with the change in the radial width of the annular channel), and the intermediate slider with a trapezoidal cross-section and the two side walls of the annular channel (the inner side wall of the outer ring shell and the outer side wall of the inner ring shell) form two raceways (inner raceway and outer raceway) extending axially for installing rollers (inner roller and outer roller), and the radial widths of the two raceways in the axial direction are equal, so that they can better fit and resist the rollers, and mainly apply radial force to the rollers to prevent the rollers from shifting in the axial direction, which is beneficial to ensuring the stability of the bearing during rotation.

[0030] Furthermore, arc-shaped grooves fitting the inner roller and the outer roller are respectively provided on the radial inner wall and the radial outer wall of the middle slider. The arc-shaped grooves are circumferentially provided on the radial side walls of the middle slider, corresponding to the inner roller and the outer roller respectively, and the depression depth of the two arc-shaped grooves is generally smaller than the radius of the corresponding rollers. Their main function is to improve the installation stability of the rollers in the raceway, avoid the deviation of the rollers in the axial direction, and further ensure the stability of the bearing during rotation.

[0031] In the utility model, the pressure preload mechanism includes a pressure transmission roller, a ring pressure block, a preload elastic member and a ring top plate. The pressure transmission roller, the ring pressure block and the ring top plate are all arranged at the wide side end in the annular channel and are located axially outside the middle slider. That is, along the direction from the axial outside to the inside of the annular channel, the ring top plate, the preload elastic member, the ring pressure block, the pressure transmission roller and the middle slider are connected in series in sequence. The two radial sides of the ring top plate are respectively fixed to the outer ring shell and the inner ring shell, and the axial inner wall thereof is connected to the preload elastic member, so that a preload force can be applied to the preload elastic member, so that the preload elastic member presses the ring pressure block in the axial inner direction. After being pressurized, the ring pressure block continues to apply an axial inward force to the middle slider through the pressure transmission roller in the axial direction. That is, when the clearance between the inner roller or the outer roller and the inner ring shell or the outer ring shell increases due to wear, the middle slider is able to drive the two groups of rollers to move axially inward in real time after receiving the preload force from the pressure transmission roller, thereby ensuring that the clearance does not change significantly due to roller wear, thereby improving the accuracy and stability of the precision bearing.

[0032] In the utility model, a plurality of columnar protrusions are arranged in the middle of the axial outer side surface of the ring pressure block, which are evenly distributed along the circumferential direction and protrude axially outward. A preload elastic member is sleeved on each columnar protrusion. By evenly arranging a plurality of columnar protrusions along the circumference of the ring pressure block and then installing a plurality of preload elastic members between the ring pressure block and the ring top plate, while improving the preload pressurization effect, the circumferential displacement of the preload elastic member can be effectively avoided, which is conducive to ensuring that the preload force of each preload elastic member is axial. In addition, the protrusion height of the columnar protrusion is not greater than the height of the preload elastic member after preload. In other words, there is no contact between the ring pressure block and the ring top plate. Even after the preload elastic member is compressed and preloaded, there is still a certain gap between the top of the columnar protrusion of the ring pressure block and the ring top plate, so as to facilitate the subsequent adjustment of the preload force of the preload elastic member axially inward through the ring top plate.

[0033] Furthermore, an annular edge protrusion whose height is lower than the columnar protrusion and extends in the circumferential direction is further provided on the edge of the ring pressure block on both sides of the columnar protrusion in the radial direction, that is, a limiting groove for the preload elastic member to be placed is formed between the annular edge protrusion and the columnar protrusion. Through the joint action of the annular edge protrusion and the columnar protrusion, the axial inner end of the preload elastic member is fixed around the inner end of the columnar protrusion as much as possible, further ensuring the consistency of the preload force direction.

[0034] In the present invention, the preloaded elastic member is one or more of a spring, a cylindrical spring sheet, and a cylindrical rubber body, including but not limited to any product similar to a spring or spring sheet made of existing materials that can generate elastic force by compression.

[0035] In the utility model, the ring top plate is fixedly connected to the outer ring shell and the inner ring shell by threads. As the use time of the bearing increases, the wear of the pressure transmission roller increases, so that the preset preload force of the preload elastic member will be gradually released, resulting in insufficient elastic force (or the elasticity of the preload elastic member becomes weak after a long time). At this time, the preload elastic member cannot well realize the continuous pressure on the pressure transmission roller (the pressure effect becomes worse). In this case, it is only necessary to twist the ring top plate to displace it in the axial inner direction according to actual needs, so as to compress the preload elastic member and generate a new preload force that meets the working conditions. In addition, due to the thread adjustment, the compression adjustment accuracy of the preload elastic member is higher (for example, half a circle, quarter of a circle, etc. non-full circle thread rotation adjustment can be performed), and the accuracy stability of the precision bearing can be quickly restored without replacing the bearing or the preload elastic member, thereby greatly improving the service life of the bearing. In addition, since it is a threaded adjustment, in the initial state, it is also possible to adjust the problem of excessive force exerted on the pressure transmission roller due to excessive preload of the preload elastic part, causing accelerated wear of the pressure transmission roller. That is, the preload force of the preload elastic part can be adaptively adjusted according to the actual working conditions. On the premise of meeting the self-compensation requirements of the rolling body clearance, the wear of the pressure transmission roller is increased as little as possible without changing phase, thereby further improving the service life of the precision bearing and reducing the production input cost.

[0036] In the utility model, the pressure preload mechanism provided has a simple structure and can be self-adjusted. Without changing the overall structure of the pressure preload mechanism, multiple circles of inner rollers or outer rollers surrounding the middle slider can be arranged in the axial direction, that is, the pressure preload mechanism can simultaneously perform pressure-increasing self-compensation on multiple circles of rollers, which is beneficial to increasing the load-bearing upper limit of the tight bearing, and also helps to increase the axial width of the bearing so that it is suitable for different working conditions, thereby improving the applicability of the bearing.

[0037] In the utility model, a rotating protrusion and / or a rotating concave hole are arranged on the axial outer surface of the ring top plate. The ring top plate is driven to rotate in the circumferential direction by rotating the protrusion and / or the rotating concave hole manually or by twisting a matching wrench, thereby adjusting the depth of the ring top plate in the annular channel along the axial direction. The utility model has the advantages of quick and simple adjustment, and can be adjusted in both positive and negative directions, with high adjustment accuracy.

[0038] In the utility model, the axial downward depth of the threaded area on the side wall of the outer ring shell and the inner ring shell is greater than the maximum thickness of the ring top plate. That is to say, the ring top plate can be completely downward into the annular clamping channel through the thread, or it can be partially protruded to the axial outer side of the annular clamping channel or the axial outer side surface of the ring top plate is flush with the axial outer side end surface of the outer ring shell and the inner ring shell, thereby improving the upper and lower adjustment limits of the ring top plate and greatly improving the adjustability of the bearing.

[0039] In the present invention, it should be noted that, for the sake of convenience, the "inside" and "outside" mentioned herein are relative references. Without other special instructions, it should be generally considered in this article that: in the axial direction: the wider side of the narrowed annular channel between the outer ring shell and the inner ring shell is the axial outer side, and vice versa is the axial inner side. In the radial direction: the side close to the inner ring shell is the radial inner side, and the side close to the outer ring shell is the radial outer side.

[0040] Compared with the prior art, the beneficial technical effects of the utility model are as follows:

[0041] 1: The utility model provides a pressure preload mechanism on the axial outer side of the annular clamping channel that changes in an axially shrinking manner, so that the radial and axial preload forces can be applied to the inner roller and the outer roller at the same time, so that the inner roller and the outer roller can always fit closely with the annular shell, the middle slider and the inner annular shell, thereby realizing the zero self-compensation adjustment of the clearance, which greatly ensures the stability of the bearing accuracy.

[0042] 2: The pressure preload mechanism of the utility model has a simple structure, is easy to adjust, and has high adjustment accuracy. It can greatly guarantee and improve the precision stability, durability and practicality of the bearing, significantly reduce production and maintenance costs, effectively ensure production continuity, and improve production efficiency. BRIEF DESCRIPTION OF THE DRAWINGS

[0043] Figure 1 It is a schematic diagram of the axial cross-section structure of the utility model when it has a single-layer ring-shaped inner roller and a ring-shaped outer roller.

[0044] Figure 2 It is a schematic diagram of the axial cross-section structure of the utility model when it has a double-layer ring-shaped inner roller and a ring-shaped outer roller.

[0045] Figure 3 It is a half-section three-dimensional structural schematic diagram when the inner roller and the outer roller of the utility model are both rollers.

[0046] Figure 4 It is a structural schematic diagram of the ring pressure block of the utility model.

[0047] Figure 5 It is a structural schematic diagram of the roller cage of the utility model.

[0048] Figure 6 This is a schematic diagram of the exploded structure when both the inner roller and the outer roller of the utility model are rollers.

[0049] Figure numerals: 1: outer ring shell; 2: inner ring shell; 3: inner roller; 4: intermediate slider; 5: outer roller; 6: pressure preload mechanism; 601: pressure transmission roller; 602: ring pressure block; 603: ring top plate; 604: preload elastic member; 605: roller cage; 7: inner cage; 8: outer cage. DETAILED DESCRIPTION

[0050] The technical solution of the utility model is illustrated below, and the scope of protection requested for the utility model includes but is not limited to the following embodiments.

[0051] A multi-race precision bearing, the bearing comprises an outer ring shell 1, an inner ring shell 2, an inner roller 3, an intermediate slider 4, an outer roller 5 and a pressure preload mechanism 6. The outer ring shell 1 is sleeved on the outside of the inner ring shell 2, and a shrinking annular channel along the axial direction is formed between the radial inner wall of the outer ring shell 1 and the radial outer wall of the inner ring shell 2. The intermediate slider 4 is an annular slider arranged in the middle of the annular channel, an inner raceway is formed between the radial inner wall of the intermediate slider 4 and the radial outer wall of the inner ring shell 2, and an outer raceway is formed between the radial outer wall of the intermediate slider 4 and the radial inner wall of the outer ring shell 1. The inner roller 3 is arranged in the inner raceway, and the outer roller 5 is arranged in the outer raceway. The pressure preload mechanism 6 is arranged at the wider axial outer end of the annular channel, and the axial inner end of the pressure preload mechanism 6 is in contact and connected with the axial outer side of the intermediate slider 4.

[0052] Preferably, a plurality of inner rollers 3 are evenly arranged along the circumferential direction of the inner ring shell 2, and the plurality of inner rollers 3 are sequentially connected in series through an inner retainer 7 to form a ring shape.

[0053] Preferably, a plurality of outer rollers 5 are evenly arranged along the circumferential direction of the outer ring shell 1, and the plurality of outer rollers 5 are sequentially connected in series through an outer retainer 8 to form a ring shape.

[0054] Preferably, the axial cross section of the intermediate slider 4 is an inverted trapezoidal surface, that is, the radial width of the axial cross section of the intermediate slider 4 gradually decreases from the wide side end to the narrow side end of the annular clamp. Preferably, arc-shaped grooves that fit the inner roller 3 and the outer roller 5 are respectively opened on the radial inner wall and the radial outer wall of the intermediate slider 4.

[0055] Preferably, the depth of the arc-shaped groove on the radial inner wall of the middle slider 4 is smaller than the radius of the inner roller 3 . The depth of the arc-shaped groove on the radial outer wall of the middle slider 4 is smaller than the radius of the outer roller 5 .

[0056] Preferably, the pressure preload mechanism 6 comprises a pressure transmission roller 601, a ring pressure block 602 and a ring top plate 603. The pressure transmission roller 601, the ring pressure block 602 and the ring top plate 603 are all arranged at the wide side end in the annular channel and are located axially outside the middle slider 4. The axial inner side of the ring pressure block 602 is connected to the axial outer side of the middle slider 4 through the pressure transmission roller 601, and the axial outer side of the ring pressure block 602 is connected to the axial inner side of the ring top plate 603 through the preload elastic member 604. The radial sides of the ring top plate 603 are respectively connected to the outer ring shell 1 and the inner ring shell 2.

[0057] Preferably, the pressure preload mechanism 6 includes a plurality of pressure transmission rollers 601, and in the circumferential direction, the plurality of pressure transmission rollers 601 are sequentially connected in series through a roller retainer 605 to form a ring shape. Preferably, in the radial direction, a plurality of ring-shaped pressure transmission rollers 601 are arranged between the ring pressure block 602 and the intermediate slider 4. Preferably, the pressure transmission rollers 601 are one of balls and rollers.

[0058] Preferably, a lower ring groove matching with the pressure-transmitting roller 601 is provided on the axial outer side surface of the middle slider 4 along the circumferential direction.

[0059] Preferably, an upper ring groove matching with the pressure transmission roller 601 is provided on the axial inner side surface of the ring pressure block 602 along the circumferential direction.

[0060] Preferably, the number of the lower ring grooves is consistent with the number of the upper ring grooves and corresponds one to one.

[0061] Preferably, a plurality of columnar protrusions evenly distributed in the circumferential direction and protruding outward in the axial direction are provided in the middle of the axial outer side surface of the ring pressure block 602, and a preload elastic member 604 is sleeved on each columnar protrusion, and the protrusion height of the columnar protrusion is not greater than the height of the preload elastic member 604 after preload. Preferably, annular edge protrusions with a height lower than the columnar protrusion and extending in the circumferential direction are also provided on the edges of the ring pressure block 602 on both sides of the columnar protrusion in the radial direction, that is, a limiting groove for the preload elastic member 604 to be placed is formed between the annular edge protrusion and the columnar protrusion.

[0062] Preferably, the preload elastic member 604 is a spring, a cylindrical spring sheet or a cylindrical rubber body.

[0063] Preferably, an annular U-groove extending in the circumferential direction is opened on the axial inner side surface of the ring top plate 603, and the radial width of the annular U-groove is not less than the maximum radial outer diameter of the preload elastic member 604, so that the end of the preload elastic member 604 away from the ring pressure block 602 is completely sleeved inside the annular U-groove.

[0064] Preferably, the top plate 603 is connected to the outer ring shell 1 and the inner ring shell 2 by threads, and the width of the annular channel in the radial direction is consistent in the area where the threads are provided on the outer ring shell 1 and the inner ring shell 2. Preferably, the axial downward depth of the threaded area provided on the side wall of the outer ring shell 1 and the inner ring shell 2 is greater than the maximum thickness of the top plate 603.

[0065] Preferably, a rotating protrusion and / or a rotating concave hole are further provided on the axial outer surface of the ring top plate 603. The rotating protrusion and / or the rotating concave hole drive the ring top plate 603 to rotate in the circumferential direction, thereby adjusting the depth of the ring top plate 603 in the annular channel along the axial direction.

[0066] Preferably, multiple layers of inner rollers 3 connected in series to form a ring are arranged along the axial direction of the annular channel.

[0067] Preferably, multiple layers of outer rollers 5 connected in series to form a ring are arranged along the axial direction of the annular channel.

[0068] Preferably, the inner roller 3 and the outer roller 5 are each independently a ball or a roller.

[0069] Preferably, the axial cross-section of the annular channel is trapezoidal or triangular.

[0070] Example 1

[0071] like Figure 1-3 As shown, a multi-race precision bearing includes an outer ring shell 1, an inner ring shell 2, an inner roller 3, an intermediate slider 4, an outer roller 5 and a pressure preload mechanism 6. The outer ring shell 1 is sleeved on the outside of the inner ring shell 2, and a shrinking annular channel along the axial direction is formed between the radial inner wall of the outer ring shell 1 and the radial outer wall of the inner ring shell 2. The intermediate slider 4 is an annular slider arranged in the middle of the annular channel, an inner raceway is formed between the radial inner wall of the intermediate slider 4 and the radial outer wall of the inner ring shell 2, and an outer raceway is formed between the radial outer wall of the intermediate slider 4 and the radial inner wall of the outer ring shell 1. The inner roller 3 is arranged in the inner raceway, and the outer roller 5 is arranged in the outer raceway. The pressure preload mechanism 6 is arranged at the wider axial outer end of the annular channel, and the axial inner end of the pressure preload mechanism 6 is in contact with and connected to the axial outer side of the intermediate slider 4.

[0072] Example 2

[0073] The embodiment 1 is repeated, except that a plurality of inner rollers 3 are evenly arranged along the circumferential direction of the inner ring shell 2, and the plurality of inner rollers 3 are sequentially connected in series through the inner retainer 7 to form a ring shape.

[0074] Example 3

[0075] The second embodiment is repeated, except that a plurality of outer rollers 5 are evenly arranged along the circumferential direction of the outer ring shell 1, and the plurality of outer rollers 5 are sequentially connected in series through the outer cage 8 to form a ring shape.

[0076] Example 4

[0077] Embodiment 3 is repeated, except that the axial cross section of the intermediate slider 4 is an inverted trapezoidal surface, that is, the radial width of the axial cross section of the intermediate slider 4 gradually decreases from the wide side end to the narrow side end of the annular channel.

[0078] Example 5

[0079] The fourth embodiment is repeated, except that arc-shaped grooves fitting the inner roller 3 and the outer roller 5 are respectively provided on the radial inner wall and the radial outer wall of the middle sliding block 4 .

[0080] Example 6

[0081] Repeat Example 5, except that the depth of the arc-shaped groove on the radial inner wall of the middle slider 4 is smaller than the radius of the inner roller 3. The depth of the arc-shaped groove on the radial outer wall of the middle slider 4 is smaller than the radius of the outer roller 5.

[0082] Example 7

[0083] Example 6 is repeated, except that the pressure preload mechanism 6 includes a pressure transmission roller 601, a ring pressure block 602 and a ring top plate 603. The pressure transmission roller 601, the ring pressure block 602 and the ring top plate 603 are all arranged at the wide side end in the annular channel and are located axially outside the middle slider 4. The axial inner side of the ring pressure block 602 is connected to the axial outer side of the middle slider 4 through the pressure transmission roller 601, and the axial outer side of the ring pressure block 602 is connected to the axial inner side of the ring top plate 603 through the preload elastic member 604. The radial sides of the ring top plate 603 are respectively connected to the outer ring shell 1 and the inner ring shell 2.

[0084] Example 8

[0085] Example 7 is repeated, except that the pressure preload mechanism 6 includes a plurality of pressure transmission rollers 601, and in the circumferential direction, the plurality of pressure transmission rollers 601 are connected in series in sequence through a roller retainer 605 to form a ring shape.

[0086] Example 9

[0087] Example 8 is repeated, except that in the radial direction, a plurality of ring-shaped pressure-transmitting rollers 601 are arranged between the ring pressure block 602 and the middle slider 4 .

[0088] Example 10

[0089] Repeat Example 9, except that the pressure transfer roller 601 is a roller.

[0090] Embodiment 11

[0091] Example 9 is repeated, except that the pressure-transmitting roller 601 is a ball.

[0092] Example 12

[0093] Example 11 is repeated, except that a lower ring groove matching the pressure transmission roller 601 is opened circumferentially on the axial outer side surface of the middle slider 4.

[0094] Embodiment 13

[0095] Example 12 is repeated, except that an upper ring groove matching with the pressure transmission roller 601 is opened along the circumferential direction on the axial inner side surface of the ring pressure block 602.

[0096] Embodiment 14

[0097] Repeat Example 13, except that the number of the lower ring grooves is consistent with the number of the upper ring grooves and corresponds one to one.

[0098] Embodiment 15

[0099] Example 14 is repeated, except that a plurality of columnar protrusions are evenly distributed in the circumferential direction and protruding axially outward are provided in the middle of the axial outer side surface of the ring pressure block 602, and a preload elastic member 604 is sleeved on each columnar protrusion, and the protrusion height of the columnar protrusion is not greater than the height of the preload elastic member 604 after preload.

[0100] Example 16

[0101] Example 15 is repeated, except that annular edge protrusions with a height lower than the columnar protrusion and extending circumferentially are further provided on the edges of the ring pressure block 602 on both radial sides of the columnar protrusion, that is, a limiting groove for the preload elastic member 604 to be placed is formed between the annular edge protrusion and the columnar protrusion.

[0102] Embodiment 17

[0103] Example 16 is repeated, except that the preload elastic member 604 is a spring.

[0104] Embodiment 18

[0105] Example 17 is repeated, except that an annular U-groove extending in the circumferential direction is provided on the axial inner side surface of the ring top plate 603, and the radial width of the annular U-groove is not less than the maximum radial outer diameter of the preload elastic member 604, so that the end of the preload elastic member 604 away from the ring pressure block 602 is completely sleeved inside the annular U-groove.

[0106] Embodiment 19

[0107] Example 18 is repeated, except that the top plate 603 and the outer ring shell 1 and the top plate 603 and the inner ring shell 2 are both connected by threads, and the width of the annular channel in the radial direction is consistent in the area where the outer ring shell 1 and the inner ring shell 2 are provided with threads.

[0108] Embodiment 20

[0109] Example 19 is repeated, except that the axial downward depth of the threaded areas arranged on the side walls of the outer ring shell 1 and the inner ring shell 2 is greater than the maximum thickness of the ring top plate 603.

[0110] Embodiment 21

[0111] The embodiment 20 is repeated, except that a rotation concave hole is further provided on the axial outer surface of the ring top plate 603. The ring top plate 603 is driven to rotate in the circumferential direction through the rotation concave hole, thereby adjusting the depth of the ring top plate 603 in the annular channel along the axial direction.

[0112] Embodiment 22

[0113] Example 21 is repeated, except that multiple layers of inner rollers 3 connected in series to form a ring are arranged along the axial direction of the annular channel.

[0114] Embodiment 23

[0115] Example 22 is repeated, except that multiple layers of outer rollers 5 connected in series to form a ring are arranged along the axial direction of the annular clamp.

[0116] Embodiment 24

[0117] Repeat Example 23, except that the inner roller 3 and the outer roller 5 are both balls.

[0118] Embodiment 25

[0119] Repeat Example 23, except that the inner roller 3 and the outer roller 5 are both rollers.

[0120] Embodiment 26

[0121] Example 25 is repeated except that the axial cross-section of the annular channel is trapezoidal.

Claims

1. A multi-race precision bearing, characterized in that: The bearing comprises an outer ring shell (1), an inner ring shell (2), an inner roller (3), an intermediate slider (4), an outer roller (5) and a pressure preload mechanism (6); the outer ring shell (1) is sleeved on the outside of the inner ring shell (2), and a constricted annular channel is formed along the axial direction between the radial inner wall of the outer ring shell (1) and the radial outer wall of the inner ring shell (2); the intermediate slider (4) is an annular slider arranged in the middle of the annular channel, an inner raceway is formed between the radial inner wall of the intermediate slider (4) and the radial outer wall of the inner ring shell (2), and an outer raceway is formed between the radial outer wall of the intermediate slider (4) and the radial inner wall of the outer ring shell (1); the inner roller (3) is arranged in the inner raceway, and the outer roller (5) is arranged in the outer raceway; the pressure preload mechanism (6) is arranged at the wider axial outer end of the annular channel, and the axial inner end of the pressure preload mechanism (6) is in contact and connected with the axial outer side of the intermediate slider (4).

2. The bearing according to claim 1, characterized in that: A plurality of inner rollers (3) are evenly arranged along the circumferential direction of the inner ring shell (2), and the plurality of inner rollers (3) are sequentially connected in series through an inner retainer (7) to form a ring shape; and / or A plurality of outer rollers (5) are evenly arranged along the circumferential direction of the outer ring shell (1), and the plurality of outer rollers (5) are sequentially connected in series through an outer retaining frame (8) to form a ring shape.

3. The bearing according to claim 1 or 2, characterized in that: The axial cross section of the middle slider (4) is an inverted trapezoidal surface, that is, the radial width of the axial cross section of the middle slider (4) gradually decreases in the direction from the wide side end to the narrow side end of the annular clamping channel.

4. The bearing according to claim 3, characterized in that: Arc-shaped grooves fitting the inner roller (3) and the outer roller (5) are respectively provided on the radial inner wall and the radial outer wall of the middle sliding block (4).

5. The bearing according to claim 4, characterized in that: The depth of the arc-shaped groove on the radial inner wall of the middle slider (4) is smaller than the radius of the inner roller (3); the depth of the arc-shaped groove on the radial outer wall of the middle slider (4) is smaller than the radius of the outer roller (5).

6. The bearing according to any one of claims 1-2, 4-5, characterized in that: The pressure preload mechanism (6) comprises a pressure transmission roller (601), a ring pressure block (602) and a ring top plate (603); the pressure transmission roller (601), the ring pressure block (602) and the ring top plate (603) are all arranged at the wide side end in the annular clamp and are located axially outside the middle slider (4); the axial inner side of the ring pressure block (602) is connected to the axial outer side of the middle slider (4) through the pressure transmission roller (601), and the axial outer side of the ring pressure block (602) is connected to the axial inner side of the ring top plate (603) through the preload elastic member (604); the radial sides of the ring top plate (603) are respectively connected to the outer ring shell (1) and the inner ring shell (2).

7. The bearing according to claim 3, characterized in that: The pressure preload mechanism (6) comprises a pressure transmission roller (601), a ring pressure block (602) and a ring top plate (603); the pressure transmission roller (601), the ring pressure block (602) and the ring top plate (603) are all arranged at the wide side end in the annular clamp and are located axially outside the middle slider (4); the axial inner side of the ring pressure block (602) is connected to the axial outer side of the middle slider (4) through the pressure transmission roller (601), and the axial outer side of the ring pressure block (602) is connected to the axial inner side of the ring top plate (603) through the preload elastic member (604); the radial sides of the ring top plate (603) are respectively connected to the outer ring shell (1) and the inner ring shell (2).

8. The bearing according to claim 6, characterized in that: The pressure preload mechanism (6) comprises a plurality of pressure transmission rollers (601), and in the circumferential direction, the plurality of pressure transmission rollers (601) are sequentially connected in series through a roller retainer (605) to form a ring shape.

9. The bearing according to claim 7, characterized in that: The pressure preload mechanism (6) comprises a plurality of pressure transmission rollers (601), and in the circumferential direction, the plurality of pressure transmission rollers (601) are sequentially connected in series through a roller retainer (605) to form a ring shape.

10. The bearing according to claim 8 or 9, characterized in that: In the radial direction, a plurality of ring-shaped pressure transmission rollers (601) are arranged between the ring pressure block (602) and the middle slider (4).

11. The bearing according to claim 6, characterized in that: The pressure transmission roller (601) is a ball or a roller.

12. The bearing according to any one of claims 7 to 9, characterized in that: The pressure transmission roller (601) is a ball or a roller.

13. The bearing according to claim 6, characterized in that: A lower ring groove that matches the pressure transmission roller (601) is provided on the axial outer side surface of the middle slider (4) along the circumferential direction; and / or An upper ring groove that matches the pressure transmission roller (601) is provided on the axial inner side surface of the ring pressure block (602) along the circumferential direction.

14. The bearing according to any one of claims 7 to 9 and 11, characterized in that: A lower ring groove that matches the pressure transmission roller (601) is provided on the axial outer side surface of the middle slider (4) along the circumferential direction; and / or An upper ring groove that matches the pressure transmission roller (601) is provided on the axial inner side surface of the ring pressure block (602) along the circumferential direction.

15. The bearing according to claim 13, characterized in that: The number of the lower ring grooves is consistent with the number of the upper ring grooves and corresponds one to one.

16. The bearing according to claim 14, characterized in that: The number of the lower ring grooves is consistent with the number of the upper ring grooves and corresponds one to one.

17. The bearing according to claim 6, characterized in that: A plurality of columnar protrusions are arranged in the middle of the axial outer side surface of the ring pressure block (602), which are evenly distributed in the circumferential direction and protrude axially outward. A preload elastic member (604) is sleeved on each columnar protrusion, and the protrusion height of the columnar protrusion is not greater than the height of the preload elastic member (604) after preload.

18. The bearing according to any one of claims 7-9, 11, 13, 15-16, characterized in that: A plurality of columnar protrusions are arranged in the middle of the axial outer side surface of the ring pressure block (602), which are evenly distributed in the circumferential direction and protrude axially outward. A preload elastic member (604) is sleeved on each columnar protrusion, and the protrusion height of the columnar protrusion is not greater than the height of the preload elastic member (604) after preload.

19. The bearing according to claim 17, characterized in that: An annular edge protrusion whose height is lower than the columnar protrusion and extends circumferentially is also provided on the edges of the annular pressure block (602) on both radial sides of the columnar protrusion, that is, a limiting groove for accommodating the preload elastic member (604) is formed between the annular edge protrusion and the columnar protrusion.

20. The bearing according to claim 18, characterized in that: An annular edge protrusion whose height is lower than the columnar protrusion and extends circumferentially is also provided on the edges of the annular pressure block (602) on both radial sides of the columnar protrusion, that is, a limiting groove for accommodating the preload elastic member (604) is formed between the annular edge protrusion and the columnar protrusion.

21. The bearing according to claim 6, characterized in that: The preload elastic member (604) is one of a spring, a tubular spring sheet or a tubular rubber body.

22. The bearing according to any one of claims 7-9, 11, 13, 15-17, 19-20, characterized in that: The preload elastic member (604) is one of a spring, a tubular spring sheet or a tubular rubber body.

23. The bearing according to any one of claims 17, 19-21, characterized in that: An annular U-groove extending in the circumferential direction is provided on the axial inner side surface of the annular top plate (603), and the radial width of the annular U-groove is not less than the maximum radial outer diameter of the preload elastic member (604), so that the end of the preload elastic member (604) away from the annular pressure block (602) is completely sleeved inside the annular U-groove.

24. The bearing according to claim 18, characterized in that: An annular U-groove extending in the circumferential direction is provided on the axial inner side surface of the annular top plate (603), and the radial width of the annular U-groove is not less than the maximum radial outer diameter of the preload elastic member (604), so that the end of the preload elastic member (604) away from the annular pressure block (602) is completely sleeved inside the annular U-groove.

25. The bearing according to claim 6, characterized in that: The annular top plate (603) is threadedly connected to the outer annular shell (1) and to the inner annular shell (2), and in the area where the threads are provided on the outer annular shell (1) and the inner annular shell (2), the width of the annular clamping channel in the radial direction is consistent.

26. The bearing according to any one of claims 7-9, 11, 13, 15-17, 19-21, 24, characterized in that: The annular top plate (603) is threadedly connected to the outer annular shell (1) and to the inner annular shell (2), and in the areas where the threads are provided on the outer annular shell (1) and the inner annular shell (2), the width of the annular clamping channel in the radial direction is consistent.

27. The bearing according to claim 25, characterized in that: The axial downward depth of the threaded areas arranged on the side walls of the outer ring shell (1) and the inner ring shell (2) is greater than the maximum thickness of the ring top plate (603).

28. The bearing according to claim 26, characterized in that: The axial downward depth of the threaded areas arranged on the side walls of the outer ring shell (1) and the inner ring shell (2) is greater than the maximum thickness of the ring top plate (603).

29. The bearing according to claim 6, characterized in that: A rotating protrusion and / or a rotating recessed hole are also provided on the axial outer surface of the ring top plate (603); the rotating protrusion and / or the rotating recessed hole drive the ring top plate (603) to rotate in the circumferential direction, thereby adjusting the depth of the ring top plate (603) penetrating into the annular channel along the axial direction.

30. The bearing according to any one of claims 7-9, 11, 13, 15-17, 19-21, 24-25, 27-28, characterized in that: A rotating protrusion and / or a rotating recessed hole are also provided on the axial outer surface of the ring top plate (603); the rotating protrusion and / or the rotating recessed hole drive the ring top plate (603) to rotate in the circumferential direction, thereby adjusting the depth of the ring top plate (603) penetrating into the annular channel along the axial direction.

31. The bearing according to claim 2, characterized in that: Multiple layers of inner rollers (3) connected in series to form a ring are arranged along the axial direction of the annular channel; and / or Multiple layers of outer rollers (5) connected in series to form a ring are arranged along the axial direction of the annular clamping channel.

32. The bearing according to claim 2, characterized in that: The inner roller (3) and the outer roller (5) are independently balls or rollers; The axial cross section of the annular clamping channel is trapezoidal or triangular.

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