Dust collector gearbox bearing assembly with shock-resistant transmission shaft

Abstract

The invention discloses a dust collector gear box bearing assembly with an anti-vibration transmission shaft, relates to the technical field of transmission structures, and aims at carrying out key optimization on a bearing part aiming at the high rotating speed requirement of a dust collector transmission part, and on the basis of a conventional outer shaft ring and a conventional inner shaft ring, firstly, a lubricating system in a gear box is not influenced; an oil seal action set is only additionally arranged at the outer position of a bearing part, and the key effect of the oil seal action set is that small-amplitude hydraulic change is driven by the relative rotation process of an inner shaft ring and an outer shaft ring, and the elastic buffering effect of a ball sleeve set is matched, so that the hydraulic change is transmitted to a shaft body in a wedge transmission mode; the shaft body bears the stress fluctuation process generated in the rotation action, in addition, when accidental vibration occurs on the shaft body, the vibration process on the shaft body can be converted into hydraulic change through the reverse transmission process, and the overall purpose is to avoid large work abrasion and work burden on a transmission shaft and a work piece in a mutual cooperation vibration reduction mode.

Description

Technical Field

[0001] The present invention relates to the technical field of transmission structures, and in particular to a vacuum cleaner gearbox bearing assembly with a vibration-resistant transmission shaft. Background Art

[0002] Vacuum cleaners mainly use series-excited motors or brushless motors. To meet the requirement of high wind speed, their speed can reach 125,000 rpm. They use a speed-increasing gearbox as the power conversion structure. The essence is to change the transmission ratio between the gears on the power shaft and the output shaft. However, during long-term high-speed rotation, the following problems arise:

[0003] 1. When the drive shaft rotates at high speed, if there is uneven mass distribution (such as balance sheet falling off or shaft deformation), the periodic change of centrifugal force will cause violent vibration, and the vibration amplitude is positively correlated with the speed;

[0004] 2. When subjected to high-speed alternating loads for a long time, the drive shaft may undergo plastic bending deformation, exacerbating dynamic balance failure and inducing resonance;

[0005] 3. When running at high speed, the centrifugal force of the rolling element increases, causing the grease to be thrown away from the contact area, intensifying dry friction. Local temperature rise can cause material annealing or adhesion.

[0006] It can be directly understood that when the transmission shaft rotates at high speed and is subjected to high-speed alternating loads, obvious vibration will occur on the transmission shaft, which will affect the transmission process inside the entire gearbox. The key is to intensify the degree of wear between the gears and the transmission shaft. In this regard, this application proposes the following technical solutions. Summary of the Invention

[0007] The purpose of the present invention is to provide a vacuum cleaner gearbox bearing assembly with a shock-resistant drive shaft. According to the operating principle of the vacuum cleaner, in order to meet the use requirements, the transmission shaft speed is ensured to meet the requirements. However, when the transmission shaft rotates at high speed for a long time, it is subjected to high-speed alternating loads, which will have a negative impact on the transmission shaft. Specifically, the transmission shaft produces obvious vibration, which increases the workload of the transmission shaft and gear parts and directly affects the transmission efficiency.

[0008] The objectives of the present invention can be achieved by the following technical solutions: a vacuum cleaner gearbox bearing assembly with a vibration-resistant drive shaft, comprising an outer shaft ring and an inner shaft ring, wherein balls and a ball sleeve for matching the balls are arranged between the inner wall of the outer shaft ring and the outer wall of the inner shaft ring, an oil seal action group is arranged at a corresponding position outside the gearbox on the outer shaft ring and the inner shaft ring, and a rear end cover is arranged at a corresponding position inside the gearbox on the outer shaft ring and the inner shaft ring, and a shaft body is arranged in the inner shaft ring;

[0009] The oil seal action group includes a second-stage end cover, a first-stage end cover and an outer end cover. An oil ring groove is opened on the outer wall position close to the second-stage end cover and the first-stage end cover. The outer end cover is respectively provided with an action wedge and a passive wedge. A vibration jumping rod is installed on the outer wall position of the passive wedge close to the shaft body.

[0010] It is further configured as follows: the second-stage end cover, the first-stage end cover and the rear end cover are mounted on the outer shaft ring by screws, and the inner wall position of the second-stage end cover, the inner wall position of the rear end cover and the inner shaft ring are rotationally connected.

[0011] It is further configured as follows: the second-stage end cover is close to the outer wall of the outer shaft ring, the first-stage end cover is located in the middle of the second-stage end cover and the outer end cover, and the outer end cover and the first-stage end cover are fixedly connected.

[0012] It is further configured as follows: the diameter of the ball is equal to the diameter difference between the outer shaft ring and the inner shaft ring; the ball sleeve assembly consists of an axial spring bar, a lateral spring bar and a ball sleeve; the ball is arranged in the ball sleeve; and the axial spring bar and the lateral spring bar are installed at a middle position of the ball sleeve between two adjacent positions.

[0013] It is further configured as follows: the lateral spring bars are symmetrically arranged along the length direction of the shaft body, and the lateral spring bars are curved in an arch shape in the direction close to the rear end cover or the oil seal action group, and the axial spring bars are curved in an arch shape in the direction close to or away from the center point of the outer shaft ring, and the bending direction of the axial spring bars is staggered along the annular contour direction of the outer shaft ring.

[0014] It is further configured as follows: an oil port corresponding to the oil ring groove is opened at a position of the second-stage end cover close to the outer shaft ring, the cross-section of the oil ring groove along the horizontal plane of the center point of the outer shaft ring is a transverse ellipse, and the action wedge is installed with a rubber pressure ball in the internal position of the oil ring groove corresponding to the action wedge, and the outer diameter of the rubber pressure ball is smaller than the minor axis diameter of the oil ring groove.

[0015] It is further configured as follows: a connecting rod is provided between the action wedge block and the rubber pressure ball, and the connecting rod is slidably connected to the first-stage end cover along the length direction of the shaft body.

[0016] It is further configured that: the action wedge is slidably connected at the inner ring wall position of the outer end cover along the direction parallel to the length of the shaft body, the passive wedge is slidably connected at the inner side wall position of the outer end cover along the direction perpendicular to the length of the shaft body, the upper end position of the jumping rod is slidably connected to the outer end cover, and the lower end position of the jumping rod is installed with a pressure bead corresponding to the shaft body.

[0017] It is further configured that: a ring spring strip is provided at the middle section of the vibration jumping rod.

[0018] The present invention has the following beneficial effects:

[0019] 1. The present invention is an improved solution for optimizing associated bearing components for high-speed transmission processes. Specifically, taking devices such as vacuum cleaners as an example, to meet the high-speed operating requirements, a ball sleeve is first installed between the outer and inner shaft rings for the balls. Specifically, it is mainly composed of lateral and axial spring bars. The balls are retained in the sleeve, and the sleeve does not interfere with the normal rolling process of the balls. The key is to cooperate with the centrifugal force generated by the device during high-speed operation. When one or more balls are negatively affected by the centrifugal force, the lateral and axial spring bars can undergo annular and axial deformation. The purpose is to "absorb" the non-directional stress caused by the centrifugal force on the balls through this deformation process while maintaining the normal rolling of the balls, thereby avoiding the problem of localized vibration caused by the uneven rolling of the balls.

[0020] 2. Through the improvement process of the ball, an oil seal action group is further set for the position of the bearing relative to the external position of the gearbox. The oil seal action group cooperates with the directional rolling process of the ball to generate flow differences of hydraulic oil. Its purpose is to convert the centrifugal force difference into hydraulic change, which is specifically utilized in the rubber pressure ball in the oil ring groove, and further set up an inclined wedge transmission structure composed of an action wedge block and a passive wedge block for the rubber pressure ball. The key is to add a jumping rod on the passive wedge block to cooperate with the shaft body. The jumping rod has a two-way cooperative effect. On the one hand, it "disperses" the mechanical stress converted from the hydraulic change to the shaft body through the transmission process of the inclined wedge structure. Secondly, it can also transmit the vibration on the shaft body back to the inside of the bearing part, and use the hydraulic oil medium inside the bearing part to reversely bear the vibration frequency of the shaft body, mainly playing the triple role of vibration reduction, buffering and protection. BRIEF DESCRIPTION OF THE DRAWINGS

[0021] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the following briefly introduces the drawings required for use in the embodiments or the description of the prior art. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying any creative work.

[0022] Figure 1 This is a schematic structural diagram of a vacuum cleaner gearbox bearing assembly with a vibration-resistant transmission shaft proposed by the present invention;

[0023] Figure 2 For the present invention Figure 1 sectional view of

[0024] Figure 3 For the present invention Figure 1 Cross-section diagram of the outer and inner shaft rings;

[0025] Figure 4 For the present invention Figure 1 Split diagram of ;

[0026] Figure 5 Schematic diagram of the structure of the ball set in the present invention;

[0027] Figure 6 This is a cutaway diagram of the outer end cover of the present invention.

[0028] In the figure: 1. Rear end cover; 2. Shaft body; 3. Outer shaft ring; 4. First-stage end cover; 5. Outer end cover; 6. Ball; 7. Second-stage end cover; 8. Ball bearing assembly; 801. Axial spring bar; 802. Lateral spring bar; 803. Ball sleeve; 9. Pressure ball; 10. Inner shaft ring; 11. Actuating wedge; 12. Passive wedge; 13. Vibration-jumping rod; 14. Rubber pressure ball; 15. Oil ring groove. DETAILED DESCRIPTION

[0029] The technical solutions of the present invention will be clearly and completely described below in conjunction with the embodiments. Obviously, the embodiments described are only some embodiments of the present invention, not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making creative efforts are within the scope of protection of the present invention.

[0030] Example 1: Based on the operating principle of the vacuum cleaner, in order to meet the use requirements and ensure that the transmission shaft speed meets the requirements, but when the transmission shaft is subjected to high-speed alternating loads during long-term high-speed rotation, it will have a negative impact on the transmission shaft, which is specifically manifested in obvious vibration of the transmission shaft, increasing the workload of the transmission shaft and gear parts, which will directly affect the transmission efficiency. In this regard, the following technical solutions are proposed:

[0031] Reference Figures 1 to 6 In this embodiment, the vacuum cleaner gearbox bearing assembly with a vibration-resistant drive shaft includes an outer shaft ring 3 and an inner shaft ring 10. Balls 6 and a ball sleeve 8 that cooperate with the balls 6 are arranged between the inner wall of the outer shaft ring 3 and the outer wall of the inner shaft ring 10. An oil seal action group is arranged at the outer shaft ring 3 and the inner shaft ring 10 at the corresponding positions outside the gearbox, and a rear end cover 1 is arranged at the inner position of the gearbox corresponding to the outer shaft ring 3 and the inner shaft ring 10. A shaft body 2 is arranged in the inner shaft ring 10.

[0032] The oil seal action group includes a second-stage end cover 7, a first-stage end cover 4 and an outer end cover 5. An oil ring groove 15 is provided on the outer wall position close to the second-stage end cover 7 and the first-stage end cover 4. The outer end cover 5 is respectively provided with an action wedge 11 and a passive wedge 12. The passive wedge 12 is installed with a vibration jumping rod 13 on the outer wall position close to the shaft body 2. The second-stage end cover 7, the first-stage end cover 4 and the rear end cover 1 are installed on the outer shaft ring 3 by screws, and the inner wall position of the second-stage end cover 7, the inner wall position of the rear end cover 1 and the inner shaft ring 10 are rotationally connected. The second-stage end cover 7 is close to the outer wall position of the outer shaft ring 3, the first-stage end cover 4 is located in the middle position between the second-stage end cover 7 and the outer end cover 5, and the outer end cover 5 and the first-stage end cover 4 are fixedly connected.

[0033] Basic principle: The present invention is mainly suitable for related equipment with high-speed working state. Taking the vacuum cleaner as an example, its speed can reach 125,000 rpm. It mainly uses the gear box as the power conversion action of the speed-increasing type, and the bearing of the transmission shaft is the key structure. For this, the present invention makes specific improvements to the bearing parts. The conventional bearing parts are essentially the outer shaft ring, the inner shaft ring and the ball. Therefore, this embodiment does not improve the basic structure of the bearing parts. The key is to add an optimized structure such as the ball set 8 for the ball, and combine it with Figure 2 and Figure 4 To illustrate, in order to ensure that lubricating oil, hydraulic oil and other oil media are completely filled in the middle position between the outer shaft ring 3 and the inner shaft ring 10, the rear end cover 1 and the second-stage end cover 7 in the present invention serve as a cover structure for the internal space of the outer shaft ring 3 and the inner shaft ring 10. To this end, it is necessary to ensure that the rear end cover 1 and the second-stage end cover 7 are directly mounted on the outer shaft ring 3 in a screw-fixing manner, but the rear end cover 1, the second-stage end cover 7 and the inner shaft ring 10 have the ability to rotate, and a mechanical sealing device is provided. This part will not be explained in detail;

[0034] Therefore, during the installation process, the shaft body 2 is mainly installed in the inner shaft ring 10, and on the basis of ensuring the free rotation of the inner shaft ring 10, a medium such as lubricating oil is always filled in the middle position between the inner shaft ring 10 and the outer shaft ring 3.

[0035] Example 2: Explanation of the ball bearing assembly in Example 1:

[0036] The diameter of the ball 6 is equal to the difference in diameter between the outer shaft ring 3 and the inner shaft ring 10. The ball sleeve 8 consists of an axial spring bar 801, a lateral spring bar 802, and a ball sleeve 803. The ball 6 is disposed in the ball sleeve 803. The axial spring bar 801 and the lateral spring bar 802 are mounted in the middle position of the ball sleeve 803 between two adjacent positions. The lateral spring bars 802 are symmetrically arranged along the length of the shaft body 2, and the lateral spring bars 802 are curved in an arch shape in the direction approaching the rear end cover 1 or the oil seal actuating group. The axial spring bar 801 is curved in an arch shape in the direction approaching or away from the center point of the outer shaft ring 3. The curvature direction of the axial spring bars 801 is staggered along the annular contour of the outer shaft ring 3.

[0037] Solution description: Regarding the ball structure in conventional bearings, its key role is to optimize the rolling friction mode and stress distribution. In order to maintain the relative position of each ball, some bearing parts can also be equipped with a fixed ball rack for the ball. However, the present invention optimizes the ball to form a ball set 8. For details, refer to Figure 5 To explain:

[0038] Conventional ball cages primarily maintain the relative positions of the balls. Unless damaged, the relative positions of the balls remain constant. However, the present invention utilizes ball sleeves 803 as mounting structures for the balls 6. The sleeves 803 do not interfere with the normal rolling of the balls 6. However, because each sleeve 803 is primarily "fixed" by axial and lateral spring bars 801 and 802, and these bars inherently possess a certain degree of elasticity, the relative positions of the balls 6 may change during actual operation. However, because the axial and lateral spring bars 801 and 802 have upper limits on their deformation, direct contact between the balls 6 and the sleeves 803 is avoided.

[0039] When the shaft 1 rotates at high speed, causing each ball 6 to experience high centrifugal force and undergo local positional changes, the axial spring strips 801 and lateral spring strips 802 in these locations will undergo directional bending. The purpose of this is to "absorb and store" the uneven stress distribution caused by the centrifugal force through the deformation process of the axial spring strips 801 and lateral spring strips 802. This is explained in the following two aspects:

[0040] Aspect 1: First, the bending direction of the lateral spring strip 802 is restricted, and the force of the ball sleeve 803 approaching is reduced by bending both sides outward at the same time, thereby preliminarily reducing the influence of the centrifugal force on the ball 6;

[0041] Aspect 2: The axial spring strips 801 are also elastic members in nature, but the only difference is that the bending directions of adjacent axial spring strips 801 are completely opposite. Figure 5 Taking the axial spring strip 801 in the middle as an example, when the ball 6 deviates, the stress is first dispersed symmetrically and evenly by the lateral spring strips 802. One of the axial spring strips 801 bends toward the inner race 10, while the adjacent axial spring strip 801 can only bend toward the outer race 3. This is to transfer the stress generated by the deviation of the ball 6 to the outer race 3 and the inner race 10.

[0042] A brief explanation of the above is that the diameter of ball 6 must be exactly equal to the diameter difference between outer race 3 and inner race 10 to ensure that ball 6 is fully trapped between them and maintain rolling friction. Therefore, the relative deviation of ball 6 simply represents the annular sliding process generated between outer race 3 and inner race 10. Firstly, the lateral spring strips 802 directly distribute the stress differences generated by centrifugal force. Secondly, the multiple axial spring strips 801 form an annular wave structure, specifically transferring the stress differences to the bearing components. However, this stress is not limited to being "borne" solely by the outer race 3 or the inner race 10, but rather is shared and evenly distributed by both, thus avoiding the negative effects of ball 6.

[0043] Example 3: Based on the operation process of the ball bearing assembly in Example 2, the following working process of the oil seal action group is proposed:

[0044] The second-stage end cover 7 is provided with an oil port corresponding to the oil ring groove 15 at a position near the outer shaft ring 3. The cross-section of the oil ring groove 15 along the horizontal plane of the center point of the outer shaft ring 3 is a transverse ellipse. The action wedge 11 is installed with a rubber pressure ball 14 in the internal position of the oil ring groove 15. The outer diameter of the rubber pressure ball 14 is smaller than the minor axis diameter of the oil ring groove 15. A connecting rod is provided between the action wedge 11 and the rubber pressure ball 14. The connecting rod is slidingly connected to the first-stage end cover 4 along the length direction of the shaft body 2. The action wedge 11 is slidingly connected at the position of the inner ring wall of the outer end cover 5 in parallel with the length direction of the shaft body 2. The passive wedge 12 is slidingly connected at the position of the inner side wall of the outer end cover 5 in perpendicular to the length direction of the shaft body 2. The upper end position of the vibration jumping rod 13 is slidingly connected to the outer end cover 5, and the lower end position of the vibration jumping rod 13 is installed with a pressure bead 9 corresponding to the shaft body 2. The middle section of the vibration jumping rod 13 is provided with a ring spring strip.

[0045] Solution Description: Combined Figure 2 As described in Example 2, the outer shaft ring 3 and the inner shaft ring 10 are filled with a lubricating oil medium for lubricating the balls 6. In the present invention, it is necessary to ensure that the lubricating oil exists in a liquid form rather than a colloid or semi-fluid. The purpose is to ensure that part of the lubricating oil can also be pumped into the oil ring groove 15 in the oil seal action group. The following content needs to be explained:

[0046] S1: First, ensure the location of the oil seal action group. Because the oil seal action group also contains a pressure bead 9 that contacts the shaft body 2, the pressure bead 9 will not be set in the gearbox. Therefore, the oil seal action group can only be set outside the gearbox, while the rear end cover 1 can be set in the gearbox to prevent the lubricating oil in the gearbox from being pumped into the space between the outer shaft ring 3 and the inner shaft ring 10.

[0047] S2: Combined to Figure 2 and Figure 6 To explain: the oil ring groove 15 is essentially an elliptical ring structure, and the rubber pressure ball 14 is essentially located in the middle of the oil ring groove 15. Then, the lubricating oil inside the outer shaft ring 3 and the inner shaft ring 10 is affected by the centrifugal force or the relative displacement of the ball 6, resulting in part of the lubricating oil being pumped into the oil ring groove 15, which will generate a horizontal thrust on the rubber pressure ball 14, mainly directly driving the action wedge 11 to slide horizontally. However, because an oblique wedge transmission structure is formed between the action wedge 11 and the passive wedge 12, the passive wedge 12 can only slide in the direction pointing to the center of the shaft body 2, causing the jumping rod 13 therein to contact the shaft body 2. The purpose of this part is:

[0048] The negative impact of centrifugal force on the balls 6 is transferred to the shaft 2 through a hydraulic-mechanical conversion method. The essence of this method is that when adjacent balls 6 are displaced relative to each other, some of the hydraulic oil between them is squeezed into the oil ring groove 15, thereby driving the multiple active wedges 11 to receive the thrust from the lubricating oil and synchronously affect each passive wedge 12. During the hydraulic-mechanical conversion transfer process, the stress differences caused by centrifugal force inside the bearing components are dispersed.

[0049] S3: Further explanation in combination with S2: When the shaft 2 itself vibrates unexpectedly, it will also directly affect the jumping rod 13. Figure 4 and Figure 6 To illustrate, the pressing bead 9 maintains contact with the outer wall of the shaft body 1. The vibration on the shaft body 2 drives the pressing bead 9 to perform non-directional jumping along the diameter direction of the shaft body 2. First, the ring spring strip structure directly withstands the non-directional jumping process, playing a preliminary vibration reduction and buffering role. The key lies in:

[0050] The integral jumping rod 13 and the outer end cover 5 have the ability to slide. When the ring spring bar reaches the maximum deformation limit, the jumping rod 12 and the outer end cover 5 will slide, thereby indirectly driving the passive wedge 12 to slide in a direction parallel to the diameter of the shaft body 2, indirectly driving the action wedge 11 to move horizontally. The difference from S2 is that the action sequence of the key content of this part is opposite to that of S2. Specifically, through the transfer method of mechanical conversion-hydraulic conversion, the possible vibration sensation on the shaft body 2 is transferred to the oil ring groove 15, indirectly affecting the flow process of the lubricating oil between the outer shaft ring 3 and the inner shaft ring 10.

[0051] In combination with the above content, it is supplemented that the ball bearing set 8 and the oil seal action group are the basis, and the two are synergistic and interactive. The two can be performed independently, but the two influence each other and jointly play the role of anti-vibration protection to meet the protection purpose during high-speed operation.

[0052] In summary: in response to the high speed requirements of the vacuum cleaner transmission parts, the bearing parts are optimized, based on the conventional outer shaft ring and inner shaft ring. First of all, it does not affect the lubrication system in the gear box. Only an oil seal action group is added to the external position of the bearing part. The key role of the oil seal action group is: the relative rotation process of the inner and outer shaft rings drives a small hydraulic pressure change, and cooperates with the elastic buffering effect of the ball sleeve to transmit the hydraulic pressure change to the shaft body through the inclined wedge transmission method, so that the shaft body can withstand the stress fluctuation process generated by the rotation action. In addition, when unexpected vibration occurs on the shaft body, the vibration process on the shaft body can also be converted into hydraulic change through the reverse transmission process. Its overall purpose is to avoid greater working wear and work burden on the transmission shaft and working parts through mutual coordinated vibration reduction.

[0053] The preferred embodiments of the present invention disclosed above are intended only to help illustrate the present invention. These preferred embodiments do not exhaustively describe all details, nor do they limit the present invention to specific embodiments. Obviously, many modifications and variations are possible based on the contents of this specification. These embodiments are selected and described in detail in this specification to better explain the principles and practical applications of the present invention, thereby enabling those skilled in the art to better understand and utilize the present invention. The present invention is limited only by the claims and their full scope and equivalents.

Claims

1. A vacuum cleaner gearbox bearing assembly with a vibration-resistant transmission shaft, comprising an outer shaft ring (3) and an inner shaft ring (10), characterized in that: A ball (6) and a ball set (8) matching the ball (6) are provided between the inner wall of the outer shaft ring (3) and the outer wall of the inner shaft ring (10); an oil seal action group is provided at an outer position of the gear box corresponding to the outer shaft ring (3) and the inner shaft ring (10); a rear end cover (1) is provided at an inner position of the gear box corresponding to the outer shaft ring (3) and the inner shaft ring (10); and a shaft body (2) is provided in the inner shaft ring (10); The oil seal action group comprises a second-stage end cover (7), a first-stage end cover (4) and an outer end cover (5); an oil ring groove (15) is provided on the outer wall positions of the second-stage end cover (7) and the first-stage end cover (4) close to each other; an action wedge (11) and a passive wedge (12) are respectively provided in the outer end cover (5); and a vibration jumping rod (13) is installed on the outer wall position of the passive wedge (12) close to the shaft body (2).

2. The vacuum cleaner gearbox bearing assembly with a vibration-resistant transmission shaft according to claim 1, characterized in that: The second-stage end cover (7), the first-stage end cover (4), and the rear end cover (1) are mounted on the outer shaft ring (3) by screws, and the inner wall position of the second-stage end cover (7), the inner wall position of the rear end cover (1) and the inner shaft ring (10) are rotatably connected.

3. The vacuum cleaner gearbox bearing assembly with a vibration-resistant transmission shaft according to claim 2, characterized in that: The second-stage end cover (7) is located close to the outer wall of the outer shaft ring (3), the first-stage end cover (4) is located in the middle of the second-stage end cover (7) and the outer end cover (5), and the outer end cover (5) and the first-stage end cover (4) are fixedly connected.

4. The vacuum cleaner gearbox bearing assembly with a vibration-resistant transmission shaft according to claim 1, characterized in that: The diameter of the ball (6) is equal to the diameter difference between the outer shaft ring (3) and the inner shaft ring (10). The ball sleeve (8) is composed of an axial spring strip (801), a lateral spring strip (802) and a ball sleeve (803). The ball (6) is arranged in the ball sleeve (803). The axial spring strip (801) and the lateral spring strip (802) are installed at a middle position of the ball sleeve (803) between two adjacent positions.

5. The vacuum cleaner gearbox bearing assembly with a vibration-resistant transmission shaft according to claim 4, characterized in that: The lateral spring strips (802) are symmetrically arranged along the length direction of the shaft body (2), and the lateral spring strips (802) are curved in an arch shape in a direction close to the rear end cover (1) or the oil seal action group. The axial spring strips (801) are curved in an arch shape in a direction close to or away from the center point of the outer shaft ring (3), and the bending direction of the axial spring strips (801) is staggered along the annular contour direction of the outer shaft ring (3).

6. The vacuum cleaner gearbox bearing assembly with a vibration-resistant transmission shaft according to claim 1, characterized in that: The second-stage end cover (7) is provided with an oil port corresponding to the oil ring groove (15) at a position close to the outer shaft ring (3). The cross section of the oil ring groove (15) along the horizontal plane of the center point of the outer shaft ring (3) is in a transverse elliptical shape. The action wedge (11) is provided with a rubber pressure ball (14) installed in a corresponding position inside the oil ring groove (15). The outer diameter of the rubber pressure ball (14) is smaller than the minor axis diameter of the oil ring groove (15).

7. The vacuum cleaner gearbox bearing assembly with a vibration-resistant transmission shaft according to claim 6, characterized in that: A connecting rod is provided between the action wedge (11) and the rubber pressure ball (14), and the connecting rod is slidably connected to the first-stage end cover (4) along the length direction of the shaft body (2).

8. The vacuum cleaner gearbox bearing assembly with a vibration-resistant transmission shaft according to claim 7, characterized in that: The action wedge (11) is slidably connected at the inner ring wall of the outer end cover (5) in a direction parallel to the length of the shaft (2); the passive wedge (12) is slidably connected at the inner side wall of the outer end cover (5) in a direction perpendicular to the length of the shaft (2); the upper end of the jumping rod (13) is slidably connected to the outer end cover (5), and a pressure bead (9) corresponding to the shaft (2) is installed at the lower end of the jumping rod (13).

9. The vacuum cleaner gearbox bearing assembly with a vibration-resistant transmission shaft according to claim 8, characterized in that: A ring spring strip is provided at the middle section of the jumping rod (13).

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