Power head main shaft load-bearing bearing elastic pressing structure

Abstract

The utility model discloses a power head main shaft load-bearing bearing elastic pressing structure which comprises a load-bearing bearing, an elastic pressing assembly, a main shaft and a mounting base, the load-bearing bearing is arranged on the main shaft in a sleeved mode, the main shaft is rotatably supported on the mounting base through the load-bearing bearing, and the elastic pressing assembly is arranged between the load-bearing bearing and the mounting base in a clamped mode. The elastic pressing assembly has elastic force for pushing the outer ring of the load-bearing bearing to be tightly attached to the inner ring or pushing the inner ring to be tightly attached to the outer ring. Through the design, when the load-bearing bearing works for a long time to generate abrasion and a gap is generated between the inner ring and the outer ring, the elastic pressing assembly can tightly press the inner ring and the outer ring through the elastic force of the elastic pressing assembly, the working stability of the load-bearing bearing is kept, and the load-bearing bearing is adjusted in real time through the elastic pressing assembly; the load-bearing bearing can be always kept in a tight fit state within a reasonable abrasion range.

Description

Technical Field

[0001] The utility model belongs to the field of geological exploration equipment, in particular to a heavy bearing spring-pressing structure of a main bearing of a power head. Background Art

[0002] The power head of the drilling rig can be divided into two parts, one is the shell part fixed to the mounting base, and the other is the rotating part rotatably connected to the shell part. The shell part transfers its own weight to the mounting base. The rotating part can only be connected to the shell part through rotating parts such as bearings due to the need to drive the drill rod to rotate.

[0003] The working states of the power head include a vertical working state perpendicular to the ground and a horizontal working state horizontal to the ground. When the power head is in the vertical working state, the heavy bearing of the rotating part will bear the entire weight of the rotating part itself and the drill pipe. Therefore, the load-bearing bearing is extremely easy to wear, and a gap will be generated between the inner and outer rings of the bearing and the rollers in the bearing. If the power head is always in the vertical working state, the gap between the inner and outer rings of the bearing and the rollers will be compacted by the deadweight of the rotating part and the weight of the drill pipe. However, when the power head is adjusted to the horizontal working state, the load-bearing bearing will produce abnormal noise due to the gap and cannot meet the strength requirements for normal use. Therefore, it is necessary to provide a load-bearing spring-pressing structure for the main bearing of the power head. Utility Model Content

[0004] The utility model aims to provide a load-bearing spring-pressing structure for a main bearing of a power head, so as to solve the technical problem that when the power head is in a vertical working state, the heavy bearing of the rotating part will bear the entire weight of the rotating part itself and the drill rod, the load-bearing bearing is very easy to wear, and a gap is generated between the inner and outer rings of the bearing and the rollers in the bearing. When the power head is adjusted to a horizontal working state, the load-bearing bearing will produce abnormal noise due to the gap and cannot meet the strength requirements for normal use.

[0005] To achieve the above purpose, the specific technical solution of the utility model is as follows:

[0006] A load-bearing spring-pressing structure of a main shaft of a power head includes a load-bearing, a spring-pressing assembly, a main shaft and a mounting base, wherein the load-bearing bearing is sleeved on the main shaft, the load-bearing bearing supports the main shaft rotationally on the mounting base, the spring-pressing assembly is clamped between the load-bearing bearing and the mounting base, and the spring-pressing assembly has an elastic force that pushes the outer ring of the load-bearing bearing toward the inner ring, or the inner ring toward the outer ring. With such a design, when the load-bearing bearing is worn out after working for a long time and a gap is generated between the inner ring and the outer ring, the spring-pressing assembly can rely on its own elastic force to press the inner ring and the outer ring tightly to maintain the working stability of the load-bearing bearing, and the spring-pressing assembly can adjust the load-bearing bearing in real time, so that the load-bearing bearing can always remain in a tight state within a reasonable wear range.

[0007] The main shaft has a load-bearing abutment formed by radial expansion, and the mounting base has a load-bearing boss protruding toward the axis of the main shaft. The inner ring of the load-bearing bearing abuts against the load-bearing abutment, and the outer ring abuts against the load-bearing boss, or the outer ring abuts against the load-bearing abutment, and the inner ring abuts against the load-bearing boss. Through such a design, the load-bearing bearing connects the inner ring and the outer ring to the main shaft and the mounting base respectively, which can not only fix the main shaft and the mounting base, but also enable the main shaft to rotate relative to the mounting base.

[0008] The load-bearing bearing is a cone bearing, which includes a cone inner ring and a cone outer ring, wherein the cone inner ring abuts against the load-bearing abutment, and the cone outer ring abuts against the load-bearing boss. With such a design, the cone bearing can bear a larger radial weight, and has a longer service life as a load-bearing bearing than other bearings.

[0009] The spring pressure assembly includes a spring sleeve and a thrust spring. A spring mounting hole is provided on one side of the spring sleeve close to the cone bearing. The thrust spring is fixedly mounted in the spring mounting hole. The thrust spring is elastically supported between the spring sleeve and the thrust bearing. With such a design, the thrust spring is installed in the spring mounting hole without tilting due to external force.

[0010] The cone outer ring is mounted on the top of the spring mounting hole and covers the spring mounting hole, and the spring sleeve is fitted with the mounting base on one side close to the mounting base, and has a first rotation gap with the main shaft on the other side close to the main shaft. With such a design, the spring sleeve will not interfere with the rotation of the main shaft.

[0011] The main shaft sleeve is provided with a ball bearing, the ball bearing is sandwiched between the spring sleeve and the bearing boss, the ball bearing includes an inner ball ring and an outer ball ring, the inner ball ring is fixed to the main shaft, and the outer ball ring is supported between the spring sleeve and the bearing boss. Through such a design, the ball bearing maintains the stability of the main shaft rotation.

[0012] The bottom of the spring sleeve is close to the protrusion on the outer ring side of the ball to form a first supporting boss, and the top of the load-bearing boss is close to the protrusion on the outer ring side of the ball to form a second supporting boss.

[0013] A second rotation gap is left between the load-bearing boss and the main shaft, a skeleton oil seal is arranged in the second rotation gap, and the skeleton oil seal is fixedly connected to the load-bearing boss. Through such a design, the sewage power head is prevented from entering the ball bearing and the cone bearing through the second rotation gap during use, and the airtightness of the power head main shaft is maintained to a certain extent.

[0014] The beneficial effects of the utility model are as follows: when the load-bearing bearing is worn out due to long-term work and a gap is generated between the inner ring and the outer ring, the spring-pressing component can rely on its own elastic force to press the inner ring and the outer ring tightly to maintain the working stability of the load-bearing bearing, and the spring-pressing component adjusts the load-bearing bearing in real time, so that the load-bearing bearing can always remain in a tight state within a reasonable wear range. BRIEF DESCRIPTION OF THE DRAWINGS

[0015] Figure 1 It is a schematic diagram of the planing structure of the utility model installed inside the whole power head;

[0016] Figure 2 for Figure 1 A schematic diagram of the enlarged structure of part A;

[0017] Figure 3 It is a schematic diagram of the structure of the power head and the mounting base;

[0018] Figure 4 This is a schematic diagram of the assembly structure of the utility model and the power head;

[0019] Figure 5 This is a schematic diagram of the utility model and the main shaft assembly structure;

[0020] Figure 6 It is a schematic diagram of the assembly structure of the spring-pressing component and the tapered bearing of the utility model;

[0021] Figure 7 This is a schematic diagram of the structure of the spring-pressing component of the utility model;

[0022] Explanation of the markings in the figure: 1. Load-bearing bearing; 2. Spring-pressing assembly; 3. Main shaft; 4. Mounting base; 5. Load-bearing abutment; 6. Load-bearing boss; 7. Conical bearing; 8. Conical inner ring; 9. Conical outer ring; 10. Spring sleeve; 11. Thrust spring; 12. Spring mounting hole; 14. First rotation gap; 15. Ball bearing; 16. Ball inner ring; 17. Ball outer ring; 18. First supporting boss; 19. Second supporting boss; 20. Second rotation gap; 21. Skeleton oil seal. DETAILED DESCRIPTION

[0023] Exemplary embodiments will be described in detail herein, examples of which are shown in the accompanying drawings. When the following description refers to the drawings, the same numbers in different drawings represent the same or similar elements unless otherwise indicated. The embodiments described in the following exemplary embodiments do not represent all embodiments consistent with the present disclosure. Instead, they are merely examples of devices and methods consistent with some aspects of the present disclosure as detailed in the appended claims.

[0024] Tapered bearings are split bearings, consisting of an outer ring, rollers and an inner ring. Both the inner and outer rings of the bearing have tapered raceways.

[0025] like Figures 1 to 7 shown.

[0026] Example 1

[0027] A load-bearing spring-pressing structure of a power head main shaft includes a load-bearing 1, a spring-pressing assembly 2, a main shaft 3 and a mounting base 4. The load-bearing 1 is sleeved on the main shaft 3. The load-bearing 1 supports the main shaft 3 for rotation on the mounting base 4. The spring-pressing assembly 2 is clamped between the load-bearing 1 and the mounting base 4. The spring-pressing assembly 2 has an elastic force that pushes the outer ring of the load-bearing 1 toward the inner ring, or the inner ring toward the outer ring.

[0028] The main shaft 3 has a load-bearing abutment 5 formed by radial expansion, and the mounting base 4 has a load-bearing boss 6 protruding toward the axis of the main shaft 3. The inner ring of the load-bearing bearing 1 abuts against the load-bearing abutment 5, and the outer ring abuts against the load-bearing boss 6, or the outer ring abuts against the load-bearing abutment 5, and the inner ring abuts against the load-bearing boss 6.

[0029] The implementation method of the above embodiment is as follows: when the load-bearing bearing 1 is worn out due to long-term work and a gap is generated between the inner ring and the outer ring, the spring-pressing component 2 can rely on its own elastic force to press the inner ring and the outer ring tightly to maintain the working stability of the load-bearing bearing 1, and the spring-pressing component 2 adjusts the load-bearing bearing 1 in real time, so that the load-bearing bearing 1 can always remain in a tight state within a reasonable wear range.

[0030] Example 2

[0031] The load-bearing bearing 1 is a tapered bearing 7 , and the tapered bearing 7 includes a tapered inner ring 8 and a tapered outer ring 9 . The tapered inner ring 8 abuts against the load-bearing abutment 5 , and the tapered outer ring 9 abuts against the load-bearing boss 6 .

[0032] The implementation method of the above embodiment is: the power head includes a vertical working state and a horizontal working state when working, so the load-bearing bearing 1 needs to be able to withstand both heavy radial force and heavy axial force, and the tapered bearing 7 is the preferred load-bearing bearing 1 of the power head.

[0033] The conical bearing 7 is a split bearing. When the conical bearing 7 is worn due to use, the conical outer ring 9 and the conical inner ring 8 facilitate the spring-pressing assembly 2 to push.

[0034] Example 3

[0035] The spring pressure assembly 2 includes a spring sleeve 10 and a thrust spring 11. A spring mounting hole 12 is provided on the side of the spring sleeve 10 close to the tapered bearing 7. The thrust spring 11 is fixedly installed in the spring mounting hole 12. The thrust spring 11 is elastically supported between the spring sleeve 10 and the thrust bearing.

[0036] The conical outer ring 9 is mounted on the top of the spring mounting hole 12 and covers the spring mounting hole 12 . The side of the spring sleeve 10 close to the mounting base 4 is in contact with the mounting base 4 , and the side close to the main shaft 3 leaves a first rotation gap 14 with the main shaft 3 .

[0037] The implementation of the above embodiment is as follows: the cone outer ring 9 is mounted on the top of the spring mounting hole 12, and the thrust of the thrust spring 11 on the cone outer ring 9 is in the middle of the cone outer ring 9, so that the thrust of the thrust spring 11 is more stable. The thrust spring 11 is in a compressed state when initially assembled into the spring mounting hole 12. When the cone bearing 7 becomes loose, the thrust spring 11 can obtain space for extension and squeeze the cone outer ring 9 toward the cone inner ring 8.

[0038] Example 4

[0039] The main shaft 3 is provided with a ball bearing 15, and the ball bearing 15 is clamped between the spring sleeve 10 and the load-bearing boss 6. The ball bearing 15 includes a ball inner ring 16 and a ball outer ring 17. The ball inner ring 16 is fixed to the main shaft 3, and the ball outer ring 17 is supported between the spring sleeve 10 and the load-bearing boss 6.

[0040] The bottom of the spring sleeve 10 is convex near the side of the ball outer ring 17 to form a first supporting boss 18, and the top of the load-bearing boss 6 is convex near the side of the ball outer ring 17 to form a second supporting boss 19.

[0041] The implementation method of the above embodiment is: when the main shaft 3 rotates, the ball bearing 15 and the tapered bearing 7 simultaneously generate a restraining force on the main shaft 3 in the radial direction of the main shaft 3. The ball bearing 15 and the tapered bearing 7 are at different heights, which can maintain the stability of the rotation of the main shaft 3.

[0042] Example 5

[0043] A second rotation gap 20 is reserved between the load-bearing boss 6 and the main shaft 3 . A skeleton oil seal 21 is disposed in the second rotation gap 20 . The skeleton oil seal 21 is fixedly connected to the load-bearing boss 6 .

[0044] The implementation method of the above embodiment is: preventing the sewage power head from entering the ball bearing 15 and the tapered bearing 7 through the second rotating gap 20 during use and maintaining the sealing of the power head main shaft to a certain extent, reducing the outflow of lubricating fluid in the power head main shaft.

[0045] It is understood that the present invention is described by some embodiments, and those skilled in the art are aware that various changes or equivalent substitutions may be made to these features and embodiments without departing from the spirit and scope of the present invention. In addition, under the teachings of the present invention, these features and embodiments may be modified to adapt to specific circumstances and materials without departing from the spirit and scope of the present invention. Therefore, the present invention is not limited to the specific embodiments disclosed herein, and all embodiments falling within the scope of the claims of this application are within the scope of protection of the present invention.

Claims

1. A heavy bearing spring pressure structure for a main bearing of a power head, characterized in that: The invention comprises a load-bearing bearing (1), a spring-pressing assembly (2), a main shaft (3) and a mounting base (4), wherein the load-bearing bearing (1) is sleeved on the main shaft (3), the load-bearing bearing (1) rotatably supports the main shaft (3) on the mounting base (4), the spring-pressing assembly (2) is clamped between the load-bearing bearing (1) and the mounting base (4), and the spring-pressing assembly (2) has an elastic force for pushing the outer ring of the load-bearing bearing (1) toward the inner ring, or the inner ring toward the outer ring.

2. The power head main bearing heavy bearing spring pressure structure according to claim 1, characterized in that: The main shaft (3) has a load-bearing abutment (5) formed by radially expanding outward, and the mounting base (4) has a load-bearing boss (6) protruding toward the axis of the main shaft (3); the inner ring of the load-bearing bearing (1) abuts against the load-bearing abutment (5), the outer ring abuts against the load-bearing boss (6), or the outer ring abuts against the load-bearing abutment (5), and the inner ring abuts against the load-bearing boss (6).

3. The power head main bearing heavy bearing spring pressure structure according to claim 2 is characterized in that: The load-bearing bearing (1) is a conical bearing (7), and the conical bearing (7) comprises a conical inner ring (8) and a conical outer ring (9), the conical inner ring (8) abuts against the load-bearing abutment (5), and the conical outer ring (9) abuts against the load-bearing boss (6).

4. The power head main bearing heavy bearing spring pressure structure according to claim 3 is characterized in that: The spring-pressing assembly (2) comprises a spring sleeve (10) and a thrust spring (11); a spring mounting hole (12) is provided on a side of the spring sleeve (10) close to the tapered bearing (7); the thrust spring (11) is fixedly mounted in the spring mounting hole (12); and the thrust spring (11) is elastically supported between the spring sleeve (10) and the thrust bearing.

5. The power head main bearing heavy bearing spring pressure structure according to claim 4 is characterized in that: The conical outer ring (9) is mounted on the top of the spring mounting hole (12) and covers the spring mounting hole (12); the side of the spring sleeve (10) close to the mounting base (4) is in contact with the mounting base (4), and the side close to the main shaft (3) leaves a first rotation gap (14) with the main shaft (3).

6. The heavy bearing spring pressure structure of the main bearing of the power head according to claim 5 is characterized in that: The main shaft (3) is provided with a ball bearing (15), the ball bearing (15) is sandwiched between the spring sleeve (10) and the load-bearing boss (6), the ball bearing (15) comprises a ball inner ring (16) and a ball outer ring (17), the ball inner ring (16) is fixed to the main shaft (3), and the ball outer ring (17) is supported between the spring sleeve (10) and the load-bearing boss (6).

7. The power head main bearing heavy bearing spring pressure structure according to claim 6, characterized in that: The bottom of the spring sleeve (10) protrudes close to the side of the ball outer ring (17) to form a first supporting boss (18), and the top of the load-bearing boss (6) protrudes close to the side of the ball outer ring (17) to form a second supporting boss (19).

8. The power head main bearing heavy bearing spring pressure structure according to claim 2 is characterized in that: A second rotation gap (20) is left between the load-bearing boss (6) and the main shaft (3), a skeleton oil seal (21) is provided in the second rotation gap (20), and the skeleton oil seal (21) is fixedly connected to the load-bearing boss (6).

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