Reduction gearbox body and reduction gearbox for fracturing equipment

Abstract

The utility model provides a reduction gearbox body and a reduction gearbox. A box body space used for containing a speed reduction mechanism is formed in the speed reduction box body, and bearing seats used for supporting a plurality of gear shafts are formed on the two opposite sides of the speed reduction box body at the assembling positions of the multiple gear shafts of the speed reduction mechanism respectively. The at least one bearing seat is formed in the mode that in the section in the axial direction of the speed reducing mechanism, the annular outer wall of the bearing seat inclines from the middle to the two sides relative to the annular inner wall, so that the bearing seat is provided with a polygonal section shape with the thick middle and the two thin sides. The reduction gearbox comprises a reduction mechanism, an input flange, an output gear shaft and the reduction gearbox body. According to the reduction gearbox body, the strength of the root of the bearing seat of the reduction gearbox body can be ensured, meanwhile, the weight of the bearing seat can be properly reduced, and therefore the weight reduction requirement of the reduction gearbox body is met.

Description

Technical Field

[0001] The present disclosure relates to the field of fracturing equipment, and more specifically, to a reduction gearbox used in conjunction with the fracturing equipment, and more specifically, to a reduction gearbox housing having a bearing seat with higher mechanical strength and a reduction gearbox having such a reduction gearbox housing. Background Art

[0002] In recent years, with the large-scale exploration and development of oil, natural gas, shale gas, etc., fracturing equipment has received more and more attention in the field of oil and gas extraction. The reduction box is the transmission system of the entire fracturing equipment. Its function is to convert the power output by the prime mover (including internal combustion engine, motor, turbine engine, etc.) through the different speed ratio changes of the gears inside the reduction box, so as to achieve the effect of speed reduction and torque increase or speed increase and torque reduction, providing different transmission capabilities for fracturing equipment.

[0003] Generally speaking, the commonly used fracturing reduction gearbox assemblies in this field have two structural forms: single parallel stage (1P) and parallel + planetary double stage (2P), and have a speed ratio in the range of 5:1 to 15:1. The structure of the reduction gearbox with 1P structure is relatively simple, mainly relying on the mutually meshing input side pinion and output side large gear to reduce the speed and increase the torque. The structure of the reduction gearbox with 2P structure is more complicated, with a two-stage gear transmission system of interconnected parallel stage gear mechanism and planetary stage gear mechanism. Regardless of whether the 1P structure or the 2P structure is adopted, the function of the reduction gearbox housing is similar. The housing is mainly used to provide a bearing mounting position for the gear shaft of the gear mechanism, thereby providing support and rotation center limit for the gear contained therein and moving at high speed. In addition, the housing of the reduction gearbox provides a closed working space for the mutually meshing gears, preventing external dust and impurities from entering and wearing the tooth surface and bearings, and ensuring the safety and normal operation of the internal gear mechanism.

[0004] The housing of the reduction gearbox in the prior art is usually formed by welding steel plates. Since welding is a local rapid heating and cooling process, the molten metal in the welding area is constrained by the surrounding housing body and cannot expand and contract freely. During the cooling and shrinking process, it will be subjected to the tensile stress of the housing body material. Although the internal stress caused by the volume change can be eliminated through the heat treatment process, the unmelted parent material around the weld (heat affected zone) will produce uneven tissue distribution under the action of the welding heat cycle. Once the internal stress caused by the tissue change is generated and cannot be eliminated, it is very easy to become the source of fatigue cracks in the housing.

[0005] In addition, during the operation of the gearbox, the gearbox housing is mainly subjected to force and torque from the gear speed change mechanism contained and supported by the housing. The gears transmit the force and torque to the bearings, and then to the bearing seat of the housing. Therefore, the bearing seat is the key stress-bearing area of ​​the reduction gearbox housing. In the prior art, since the reduction gearbox housing is formed by welding steel plates, the connection between the bearing seat and the housing body joined by welding may have the hidden danger of fatigue cracks as described above. In addition, the shape and size of the bearing seat are limited by the welding process, and it is difficult to carry out local reinforcement design according to specific stress conditions. In order to solve the above problems, one solution is to design the bearing seat and its connection part to be as wide and thick as possible. However, such a bearing seat will increase the weight of the reduction gearbox housing. Utility Model Content

[0006] Technical issues to be solved

[0007] In view of the above problems, the present disclosure aims to provide a reduction gearbox housing and a reduction gearbox having such a reduction gearbox housing, so that the bearing seat in the key stress-bearing area of ​​the reduction gearbox can take into account the ideal stress-bearing requirements and weight-reduction requirements of the reduction gearbox housing.

[0008] Technical Solution

[0009] In order to achieve the above-mentioned purpose, the present disclosure provides a reduction gear box housing, wherein a housing space for accommodating a reduction mechanism is formed inside the reduction gear box housing, and at the assembly position with a plurality of gear shafts of the reduction gear mechanism, bearing seats for supporting the plurality of gear shafts are respectively formed on opposite sides of the reduction gear box housing. At least one of the bearing seats is formed such that, in a cross section along the axial direction of the reduction gear mechanism, the annular outer wall of the bearing seat is inclined from the middle to both sides relative to the annular inner wall, so that the bearing seat has a polygonal cross-sectional shape that is thick in the middle and thin on both sides.

[0010] Preferably, the bearing seat can be connected to the housing body of the reduction gearbox via a transition connection portion formed in the middle of the annular outer wall, and the transition connection portion can be a rounded connection portion protruding outward from the annular outer wall along the circumference of the bearing seat.

[0011] Preferably, in the cross section along the axial direction of the reduction mechanism, the annular outer walls inclined from the middle to both sides can be formed to have the same angle θ with the axial direction and 0°≤θ≤15°. Alternatively, preferably, in the cross section along the axial direction of the reduction mechanism, the annular outer walls inclined from the middle to both sides can be formed to have different angles θ1 and θ2 with the axial direction, and 0°≤θ1≤15° and 0°≤θ2≤15°.

[0012] Preferably, the radius of the fillet of the transition connection portion may be greater than or equal to 8 mm.

[0013] Preferably, the reduction box housing may include a main housing and an input side housing. The bearing seat may include a first bearing seat and a second bearing seat provided on the main housing, and a third bearing seat and a fourth bearing seat provided on the input side housing, the first bearing seat and the third bearing seat supporting the first gear of the reduction mechanism, and the second bearing seat and the fourth bearing seat supporting the second gear of the reduction mechanism. In addition, preferably, the main housing and the first bearing seat and the second bearing seat are integrally formed, and the input side housing and the third bearing seat and the fourth bearing seat are integrally formed.

[0014] Preferably, the reduction box housing may include a main housing, an input side housing located on one side of the main housing, and an output side housing located on the other side of the main housing. The bearing seat may include a first bearing seat and a second bearing seat provided on the main housing, and a third bearing seat and a fourth bearing seat provided on the input side housing, wherein the first bearing seat and the third bearing seat support the first gear of the reduction mechanism, and the second bearing seat and the fourth bearing seat support the second gear of the reduction mechanism.

[0015] Preferably, the main housing, the first bearing seat and the second bearing seat are integrally formed, and the input side housing, the third bearing seat and the fourth bearing seat are integrally formed.

[0016] According to another aspect of the present disclosure, a reduction gearbox for a fracturing device is provided, the reduction gearbox comprising a reduction mechanism, an input flange, an output gear shaft and a reduction gearbox housing, the reduction mechanism is assembled in the reduction gearbox housing, one end of the input flange is connected to the input gear shaft of the reduction mechanism, the other end of the input flange is used to connect to a power source, one end of the output gear shaft is connected to the output terminal of the reduction mechanism, and the other end of the output gear shaft is used to connect to the crankshaft input end in the crankcase of the fracturing device. The reduction gearbox housing is the reduction gearbox housing as described above.

[0017] Beneficial Effects

[0018] The reduction gearbox housing formed by integral molding according to the present disclosure and the reduction gearbox having such reduction gearbox housing have a thickness that gradually decreases from the middle part to both sides. Therefore, while ensuring the strength of the root of the bearing seat of the reduction gearbox housing, the weight of the bearing seat can be appropriately reduced, thereby meeting the weight reduction requirements of the reduction gearbox housing. In addition, the transition connection portion of the bearing seat of the reduction gearbox housing formed by integral molding according to the present disclosure is formed to have a large-size fillet. Therefore, the strength of the root of the bearing seat can be improved, and stress concentration at the corners with sudden changes in curvature can be avoided. At the same time, the punching efficiency of molten iron during casting can be improved, and defects such as shrinkage and cold cracking of the casting due to metal structure accumulation and stress concentration can be avoided, thereby improving the mechanical properties of the reduction gearbox housing as a whole and extending its service life.

[0019] The beneficial effects of the reduction gearbox housing and the reduction gearbox according to the present disclosure are not limited to the above-mentioned beneficial effects, but may be any beneficial effects described herein and any beneficial effects that can be obtained by the structural features described herein. BRIEF DESCRIPTION OF THE DRAWINGS

[0020] The drawings in the specification which constitute a part of this application are used to provide a further understanding of the utility model. The schematic embodiments of the utility model shown in the drawings and their descriptions are only used to explain the technical solution of the utility model and do not constitute an improper limitation of the utility model. In the drawings:

[0021] Figure 1 is a schematic diagram illustrating main components of a transmission structure of a 1P reduction gearbox according to the present disclosure;

[0022] Figure 2A and Figure 2B It is a schematic structural diagram showing a reduction gearbox housing of a 1P reduction gearbox according to the present disclosure from different angles;

[0023] Figure 3 is a schematic diagram illustrating main components of a transmission structure of a 2P reduction gearbox according to the present disclosure;

[0024] Figure 4A and Figure 4B Schematic diagrams showing the structure of a reduction gearbox housing of a 2P reduction gearbox according to the present disclosure from different angles;

[0025] Figure 5 is a partial perspective sectional view illustrating a structural example of a first embodiment of a reduction gearbox housing of a reduction gearbox according to the present disclosure;

[0026] Figure 6 is a cross-sectional view illustrating a first embodiment of a reduction gear box housing of a reduction gear box according to the present disclosure;

[0027] Figure 7is a partially enlarged cross-sectional view illustrating an example of a bearing seat structure of a first embodiment of a reduction gear box housing of a reduction gear box according to the present disclosure;

[0028] Figure 8 1 is a partial perspective sectional view illustrating a structural example of a second embodiment of a reduction gear box housing of a reduction gear box according to the present disclosure. DETAILED DESCRIPTION

[0029] In order to make the purpose, technical solution and advantages of the present disclosure more clear, the present disclosure is further described in detail below in conjunction with the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are only used to explain the present application and are not used to limit the present application.

[0030] It should be noted that in the following detailed description and claims, the use of expressions such as "approximately" and "approximately" is to take into account factors such as manufacturing tolerances and processing accuracy that are understood by ordinary technicians in the field, and will not lead to ambiguity in the description and unclear scope of protection. In addition, the directions such as "upper", "lower", "left", and "right" that appear in this article are only for the convenience of explanation and are defined in combination with the directions shown in the drawings or the common installation or working conditions of the device. After reading this article, ordinary technicians in this field can obviously easily know the direction corresponding to the direction described in this article when the device presents an orientation inconsistent with the orientation described in this article due to flipping or movement.

[0031] Below, the description will be given in the following order.

[0032] 1. Overview of the reduction gearbox housing and reduction gearbox according to the present disclosure

[0033] 2. The first embodiment of the reduction gearbox housing according to the present disclosure

[0034] 3. The second embodiment of the reduction gearbox housing according to the present disclosure

[0035] In order to highlight the technical focus of the present disclosure and simplify the description, in the following, the same or similar components in each embodiment and modification will be marked with the same figure marks and no repeated description will be given.

[0036] 1. Overview of the reduction gearbox housing and reduction gearbox according to the present disclosure

[0037] The present disclosure provides a reduction box housing for a reduction box of a fracturing device and a reduction box having such a housing. The reduction box housing according to the present disclosure is formed in an integrally formed manner and can be applied to a parallel stage housing (i.e., a reduction box housing) of a reduction box for a medium-low speed power source (hereinafter referred to as a 1P reduction box) with a parallel stage primary structure, and can also be applied to a parallel stage housing in a reduction box for a medium-high speed power source (hereinafter referred to as a 2P reduction box) with a parallel stage and a planetary stage two-stage structure.

[0038] Figure 1 FIG. 2 is a schematic diagram of the main components of the transmission structure of the 1P reduction box according to the present disclosure. Figure 1 As shown in , the transmission structure of the 1P reducer mainly includes an input flange 11, an input gear 12, an output gear 13 and an output gear shaft 14. The reduction mechanism 15 of the 1P reducer includes an input gear 12 and an output gear 13, and is contained and supported in the 1P reducer housing to be described in detail below. The input flange 11 is connected to the gear shaft of the input gear 12. The power source is connected to the input flange 11 to input torque and speed into the transmission structure of the 1P reducer. The input gear 12 is meshed with the output gear 13 for transmission. The output gear shaft 14, which serves as an output terminal, is connected to the output gear 13. The output gear shaft 14 is connected to the crankshaft input spline in the crankcase of the fracturing equipment, and outputs the speed and torque adjusted by the reducer to the crankshaft of the fracturing equipment. Transmission teeth such as drum teeth are formed on the output gear shaft 14.

[0039] Figure 2A and Figure 2B Schematic diagrams of the reduction gearbox housing of the 1P reduction gearbox according to the present disclosure are shown from different angles. Figure 2A In the embodiment, the reduction mechanism 15 of the 1P reduction box mentioned above has been installed in the reduction box body. Figure 2A and Figure 2B As can be seen in the figure, the reduction gearbox housing according to the present disclosure includes a main housing 110 and an input side housing 120. The input side housing 120 is joined to the main housing 110 at its peripheral portion to form a reduction gearbox housing of the 1P reduction gearbox. The transmission structure of the 1P reduction gearbox described above is accommodated in the space inside the housing and is supported by the reduction gearbox housing.

[0040] The main housing 110 and the input side housing 120 are respectively integrally formed parts by casting, 3D printing, etc. Therefore, a first bearing seat 111 and a second bearing seat 112 are formed on the main housing 110, which are integrally formed with other parts of the main housing 110, and a third bearing seat 113 and a fourth bearing seat 114 are formed on the input side housing 120, which are integrally formed with other parts of the input side housing 120. The first bearing seat 111 and the third bearing seat 113 are both formed at positions corresponding to the assembly position of the gear shaft of the input gear 12 and jointly support the input gear 12, and the second bearing seat 112 and the fourth bearing seat 114 are formed at positions corresponding to the assembly position of the gear shaft of the output gear 13 and jointly support the output gear 13. The distance between the center of the first bearing seat 111 and the center of the second bearing seat 112 and the distance between the center of the third bearing seat 113 and the center of the fourth bearing seat 114 are both the center distances between the input gear 12 and the output gear 13. The first bearing seat 111 to the fourth bearing seat 114 are all annular cylinders that rotate around the axis of the corresponding gear shaft. Due to the use of an integrated manufacturing process, at least one of the first bearing seat 111 to the fourth bearing seat 114 can be formed into a polygonal cross-sectional shape with a thick middle and thin sides according to design requirements. Compared with the rectangular cross-sectional shape in the prior art, such a cross-sectional shape can not only ensure the strength of the root of the bearing seat, but also appropriately reduce the weight of the bearing seat, thereby meeting the weight reduction requirements of the reduction gearbox housing. In addition, a larger-sized rounded transition portion can be formed at the connection between the first bearing seat 111 and the second bearing seat 112 and the main housing 110, and at the connection between the third bearing seat 113 and the fourth bearing seat 114 and the input side housing 120. This is conducive to improving the strength of the root of the bearing seat and avoiding stress concentration at the corners with sudden changes in curvature. At the same time, the rounded transition portion can improve the punching efficiency of the molten iron during casting, and avoid defects such as shrinkage and cold cracking of the casting due to metal structure accumulation and stress concentration.

[0041] Figure 3 FIG. 2 is a schematic diagram of the main components of the transmission structure of the 2P reduction box according to the present disclosure. Figure 3As shown in the figure, the transmission structure of the 2P reduction box mainly includes a planetary stage reduction mechanism 21, a gear reduction mechanism 22, an input flange 23 and an output gear shaft 24. The planetary stage reduction mechanism 21 and the gear reduction mechanism 22 together constitute a reduction mechanism 29, which is installed in the reduction box housing to be described in detail below, and is supported by the reduction box housing and the bearing assembly. The input flange 23 is connected to the gear shaft of the input gear 25 of the gear reduction mechanism 22 constituting the reduction mechanism 29. The power source is connected to the input flange 23 to input torque and speed into the transmission structure of the 2P reduction box. The input gear 25 of the gear reduction mechanism 22 is meshed with the output gear 26 for transmission. The output gear 26 of the gear reduction mechanism 22 is connected to the sun gear (not shown in the figure) of the planetary stage reduction mechanism 21 through a drum gear, and the sun gear is meshed with N (N≥2) planetary gears 27, and the planetary gears 27 are meshed with the fixed output side housing 230 to be described below. All the planetary gears 27 are mounted on the planetary carrier 28 through the planetary gear shaft. The planetary gear 27 revolves around the sun gear, thereby driving the planet carrier 28 to rotate. The planet carrier 28, which is the output terminal of the planetary stage reduction mechanism 21 constituting the reduction mechanism 29, is connected to the output gear shaft 24. The output gear shaft 24 is connected to the crankshaft input spline in the crankcase of the fracturing equipment, and outputs the speed and torque adjusted by the reduction box to the crankshaft of the fracturing equipment. Transmission teeth such as drum teeth are formed on the output gear shaft 24.

[0042] Figure 4A and Figure 4B The schematic diagram of the assembly of the reduction gearbox housing of the 2P reduction gearbox according to the present disclosure is shown from different angles, wherein the transmission structure of the 2P reduction gearbox mentioned above has been installed in the reduction gearbox housing supporting it. Figure 4A and Figure 4B It can be seen that the gearbox housing according to the present disclosure includes a main housing 210 (or referred to as the main housing 210), an input side housing 220 and an output side housing 230. The input side housing 220 is fixedly connected to the input side of the main housing 210 at its radial peripheral portion by means of fastening bolts or the like. The output side of the main housing 210 is fixedly connected to the output side housing 230 at the radial peripheral portion of the main housing 210 by means of fastening bolts or the like. The main housing 210, the input side housing 220 and the output side housing 230 are respectively integrally formed components by casting, 3D printing, etc. By comparison Figure 3 and Figure 4A and Figure 4B It can be seen that the gear reduction mechanism 22 is located in the parallel-stage housing space surrounded by the main housing 210 and the input side housing 220, while the planetary-stage reduction mechanism 21 is located in the planetary-stage housing space surrounded by the intermediate housing 100 and the output side housing 230.

[0043] The main housing 210 is provided with a first bearing seat 211 and a second bearing seat 212 which are integrally formed with other components of the main housing 210, and the input side housing 220 is provided with a third bearing seat 213 and a fourth bearing seat 214 which are integrally formed with other components of the input side housing 220. The first bearing seat 211 and the third bearing seat 213 are both formed at positions corresponding to the assembly positions of the gear shafts of the input gear 25 and jointly support the input gear 25, and the second bearing seat 212 and the fourth bearing seat 214 are formed at positions corresponding to the assembly positions of the gear shafts of the output gear 26 and jointly support the output gear 26. The distance between the center of the first bearing seat 211 and the center of the second bearing seat 212 and the distance between the center of the third bearing seat 213 and the center of the fourth bearing seat 214 are both the center distances between the input gear 25 and the output gear 26. The first bearing seat 211 to the fourth bearing seat 214 are all annular cylinders that rotate around the axis of the corresponding gear shaft. Due to the use of an integrated manufacturing process, at least one of the first bearing seat 211 to the fourth bearing seat 214 can be formed into a polygonal cross-sectional shape with a thick middle and thin sides according to design requirements. Compared with the rectangular cross-sectional shape in the prior art, such a cross-sectional shape can not only ensure the strength of the root of the bearing seat, but also appropriately reduce the weight of the bearing seat, thereby meeting the weight reduction requirements of the reduction gearbox housing. In addition, a larger-sized rounded transition portion can be formed at the connection between the first bearing seat 211 and the second bearing seat 212 and the main housing 210, and at the connection between the third bearing seat 213 and the fourth bearing seat 214 and the input side housing 220. This is conducive to improving the strength of the root of the bearing seat and avoiding stress concentration at the corners with sudden changes in curvature. At the same time, the rounded transition portion can improve the punching efficiency of the molten iron during casting, and avoid defects such as shrinkage and cold cracking of the casting due to metal structure accumulation and stress concentration.

[0044] According to the present invention, a housing space for accommodating a reduction mechanism is formed inside the reduction gear box housing, and at positions corresponding to the assembly positions of the multiple gear shafts of the reduction gear mechanism, multiple bearing seats (corresponding to the first to fourth bearing seats mentioned above) for supporting multiple gear shafts are formed on opposite sides of the reduction gear box housing. At least one of the multiple bearing seats is formed as follows: in a cross section along the axial direction of the reduction gear mechanism, the annular outer wall of the bearing seat is inclined from the middle to both sides relative to the annular inner wall, so that the bearing seat has a polygonal cross-sectional shape that is thick in the middle and thin on both sides. In addition, a transition connection portion is formed at the middle position of the root of the bearing seat. The transition connection portion protrudes outward from the annular outer wall of the bearing seat along the circumference of the bearing seat. The bearing seat is connected to the housing body of the reduction gear box housing via the transition connection portion. The transition connection portion is formed as a transition connection portion with a larger rounded corner.

[0045] Specific embodiments of the reduction gear box body of the reduction gear box according to the present disclosure will be described in detail below with reference to the accompanying drawings.

[0046] 2. The first embodiment of the reduction gearbox housing according to the present disclosure

[0047] Figures 5 to 7 1 is a schematic structural diagram illustrating a first embodiment of a reduction gearbox housing of a reduction gearbox according to the present disclosure. Figure 5 is a side perspective view illustrating a structural example of a first embodiment of a reduction gearbox housing of a reduction gearbox according to the present disclosure, Figure 6 is a cross-sectional view illustrating a first embodiment of a reduction gear box housing of a reduction gear box according to the present disclosure, Figure 7 FIG. 1 is a partial cross-sectional view illustrating an example of a bearing seat structure of a first embodiment of a reduction gearbox housing of the reduction gearbox of the present disclosure. Figure 6 In the figure, it is shown that in the first embodiment, the housing of the parallel-stage gear reduction box in the 2P reduction box mentioned above is taken as an example for explanation.

[0048] like Figure 5 and Figure 6 As shown, the reduction gearbox housing according to the first embodiment of the present disclosure includes a main housing 210 and an input side housing 220. The main housing 210 includes a side panel 215 and an end panel 216. The side panel 215 extends from the peripheral portion of the end panel 216 along the axial direction of the reduction gearbox until the thickness of the housing that can accommodate the gear reduction mechanism 22 is formed. The length of the side panel 215 extending in the axial direction (the thickness of the housing) basically depends on the axial length of the gear shaft of the input gear 25 and the output gear 26 of the gear reduction mechanism 22 in the reduction mechanism 29. In other words, the outer shape and size of the main housing 210 and the input side housing 220 are determined according to the shape and size of the input gear 25 and the output gear 26. The input gear 25 corresponds to the first gear of the present application, and the output gear 26 corresponds to the second gear of the present application.

[0049] like Figure 5 and Figure 6As shown in, a first bearing seat 211 and a second bearing seat 212 are formed at the central position of the main housing 210, which are integrally formed with other components of the main housing 210. The first bearing seat 211 and the second bearing seat 212 each have a transition connection portion 217 connected to the main body of the main housing 210. In addition, a third bearing seat 213 and a fourth bearing seat 214 are formed at the central position of the input side housing 220, which are integrally formed with other components of the input side housing 220. The third bearing seat 213 and the fourth bearing seat 214 each have a transition connection portion 218 connected to the main body of the input side housing 220. When there is no need to distinguish between the transition connection portion 217 and the transition connection portion 218, they can be collectively referred to as transition connection portions. The transition connection portions are all formed at the middle position of the outer peripheral surface of the corresponding bearing seat along the axial direction of the gear shaft (i.e., the axial direction of the reduction gear box). In other words, the first bearing seat 211 to the fourth bearing seat 214 are all formed to extend from the corresponding housing body via the transition connection portion and along the axial direction of the reduction gearbox toward the inner and outer sides of the corresponding housing body to form an annular inner wall supporting the bearing and an annular outer wall opposite to the annular inner wall.

[0050] The first bearing seat 211 and the third bearing seat 213 are both formed at positions corresponding to the assembly position of the gear shaft of the input gear 25. The gear shaft of the input gear 25 is supported by the first bearing seat 211 and the third bearing seat 213 on both sides of the housing via bearings. The second bearing seat 212 and the fourth bearing seat 214 are formed at positions corresponding to the assembly position of the gear shaft of the output gear 26. The gear shaft of the output gear 26 is supported by the second bearing seat 212 and the fourth bearing seat 214 on both sides of the housing via bearings. The distance between the center of the first bearing seat 211 and the center of the second bearing seat 212 and the distance between the center of the third bearing seat 213 and the center of the fourth bearing seat 214 are both the center distances between the input gear 25 and the output gear 26.

[0051] The first bearing seat 211 to the fourth bearing seat 214 are all annular solid cylinders that rotate around the axis of the corresponding gear shaft. Due to the use of an integrated manufacturing process, at least one of the first bearing seat 211 to the fourth bearing seat 214 can be formed into a polygonal cross-section shape with a thick middle and thin sides according to design requirements. For example, Figure 5 and Figure 6 As shown in the figure, in the cross section taken along the axial direction of the corresponding gear shaft (i.e., the axial direction of the reduction gear box), the annular outer wall of the second bearing seat 212 is no longer parallel to the annular inner wall in contact with the bearing, but is inclined toward both sides starting from the transition connection portion 217 located in the middle and connected to the main body of the main housing 210, so that the thickness of the second bearing seat 212 gradually decreases from the middle part to both sides in the axial direction. Figure 7 FIG. 2 shows a partial enlarged cross-sectional view of the second bearing seat 212. Figure 7 In the cross-sectional view shown, the annular outer wall of the second bearing seat 212 is formed to form an angle θ with the axial direction of the reduction box. The angle θ can be set according to the design requirements, as long as the strength of the bearing seat is not excessively weakened. For example, it can preferably be selected within the range of 0°≤θ≤15°. In addition, the figure shows that the angles formed by the annular outer walls on both sides of the transition connection 217 and the axial direction of the reduction box housing are equal and are all θ, but the angles formed by the annular outer walls on both sides of the transition connection 217 and the axial direction of the reduction box housing may also be unequal. In addition, the annular outer walls on both sides of the transition connection 217 may also be formed to have an arc. Compared with the rectangular cross-sectional shape in the prior art, such a second bearing seat 212 maintains a thicker thickness in the middle part connected to the main body of the main housing 210, but the thickness on both sides gradually decreases. Therefore, while ensuring the strength of the root of the main force of the bearing seat, the weight of the bearing seat can also be appropriately reduced to meet the weight reduction requirements of the reduction box housing.

[0052] In addition, if Figures 5 to 7 As shown in the figure, the second bearing seat 212 is connected to the housing body of the main housing 210 via a transition connection 217. In the illustrated embodiment, the transition connection 217 is formed as a transition connection with a large-size fillet. Here, "large-size fillet" means that the fillet formed is greater than or equal to R8 (that is, the arc radius R of the fillet is greater than or equal to 8mm). This is conducive to improving the strength of the root of the bearing seat and avoiding stress concentration at the corners with sudden changes in curvature. At the same time, the fillet transition portion can improve the punching efficiency of molten iron during casting, and avoid defects such as shrinkage and cold cracking of the casting due to accumulation of metal structure and stress concentration.

[0053] It should be noted that in Figures 5 to 7 In the reduction gearbox housing shown in the first embodiment of the present disclosure, only the second bearing seat 212 is formed to have a thickness that decreases from the middle to both sides, and only the transition connection portion 217 connected to the second bearing seat 212 is formed as a transition connection portion with a large-size fillet. However, it should be understood that in the first embodiment of the reduction gearbox housing according to the present disclosure, two, three or all of the first bearing seat 211 to the fourth bearing seat 214 can be formed to have the same structure as the second bearing seat 212 and the transition connection portion 217 described above. In other words, when there is no need to distinguish them, they can be collectively referred to as "bearing seats" and "transition connection portions". Therefore, repeated descriptions will not be repeated in this article.

[0054] 3. The second embodiment of the reduction gearbox housing according to the present disclosure

[0055] In the first embodiment described above, the case of the parallel-stage gearbox in the 2P speed reducer is described as an example. Next, the case of the gearbox as a 1P speed reducer is described as a second embodiment of the speed reducer case of the speed reducer according to the present disclosure. Figure 8 1 is a partial perspective sectional view illustrating a structural example of a second embodiment of a reduction gear box housing of a reduction gear box according to the present disclosure.

[0056] As described above, the reduction gearbox housing according to the second embodiment of the present disclosure includes a main housing 110 and an input side housing 120. The main housing 110 includes a side panel 115 and an end panel 116. The side panel 115 extends from the peripheral portion of the end panel 116 along the axial direction of the reduction gearbox until the thickness of the housing that can accommodate the input gear 12 and the output gear 13 is formed. The length of the side panel 115 extending in the axial direction (the thickness of the housing) basically depends on the axial length of the gear shaft of the input gear 12 and the output gear 13. In other words, the outer shape and size of the main housing 110 and the input side housing 120 are determined according to the shape and size of the input gear 12 and the output gear 13. The input gear 12 corresponds to the first gear of the present application, and the output gear 13 corresponds to the second gear of the present application.

[0057] A first bearing seat 111 and a second bearing seat 112 are formed in the center of the main housing 110 and are integrally formed with other components of the main housing 110. In addition, a third bearing seat 113 and a fourth bearing seat 114 are formed in the center of the input side housing 120 and are integrally formed with other components of the input side housing 120. Figure 8 The second bearing seat 112 and the transition connection portion 117 formed in the main housing 110 will be described in detail.

[0058] like Figure 8 As shown, the transition connection portion 117 is formed at a middle position along the axial direction of the gear shaft (i.e., the axial direction of the reduction box) of the outer peripheral surface of the second bearing seat 112. In other words, the second bearing seat 112 is formed to extend from the housing body of the main housing 110 via the transition connection portion 117 along the axial direction of the reduction box toward the inside and outside of the housing body to form an annular inner wall supporting the bearing and an annular outer wall opposite to the annular inner wall.

[0059] The second bearing seat 112 is formed as a solid annular cylinder that rotates around the axis of the corresponding gear shaft. Due to the use of an integrated manufacturing process, the second bearing seat 112 can be formed into a polygonal cross-section shape with a thick middle and thin sides according to design requirements. For example, Figure 8As shown in the figure, in the cross section taken along the axial direction of the corresponding gear shaft (i.e., the axial direction of the reduction box), the annular outer wall of the second bearing seat 112 is no longer parallel to the annular inner wall in contact with the bearing, but is inclined toward both sides starting from the transition connection portion 117 located in the middle and connected to the housing body of the main housing 110, so that the thickness of the second bearing seat 112 gradually decreases from the middle part to both sides in the axial direction. Figure 8 Although not shown in the figure, in the second embodiment, the annular outer wall of the second bearing seat 112 is also formed to form an angle θ with the axial direction of the reduction box. The angle θ can be set according to the design requirements, as long as the strength of the bearing seat is not excessively weakened. For example, it can preferably be selected within the range of 0°≤θ≤15°. In addition, the figure shows that the angles formed by the annular outer walls on both sides of the transition connection 117 and the axial direction of the reduction box housing are equal and are all θ, but the angles formed by the annular outer walls on both sides of the transition connection 117 and the axial direction of the reduction box housing may also be unequal. In addition, the annular outer walls on both sides of the transition connection 117 may also be formed to have an arc. Compared with the rectangular cross-sectional shape in the prior art, such a second bearing seat 112 maintains a relatively thick thickness in the middle part connected to the housing body of the main housing 110, but the thickness on both sides gradually decreases. Therefore, while ensuring the strength of the root of the main force of the bearing seat, the weight of the bearing seat can also be appropriately reduced to meet the weight reduction requirements of the reduction box housing.

[0060] In addition, if Figure 8 As shown in the figure, the second bearing seat 112 is connected to the housing body of the main housing 110 via a transition connection portion 117. In the illustrated embodiment, the transition connection portion 117 is formed as a transition connection portion with large-size fillets. Here, "large-size fillets" means that the radius R of the arc of the fillet formed is greater than or equal to 8mm. This is conducive to improving the strength of the root of the bearing seat and avoiding stress concentration at the corners with sudden changes in curvature. At the same time, the fillet transition portion can improve the punching efficiency of molten iron during casting, and avoid defects such as shrinkage and cold cracking of the casting due to accumulation of metal structure and stress concentration.

[0061] It should be noted that in the above reference Figure 8In the description of the reduction gearbox housing according to the second embodiment of the present disclosure, only the following are illustrated and explained: the second bearing seat 112 is formed to have a thickness that decreases from the middle to both sides, and the transition connection portion 117 connected to the second bearing seat 112 is formed to have a transition connection portion with a large-size fillet. However, it should be understood that in the second embodiment of the reduction gearbox housing according to the present disclosure, two, three or all of the first bearing seat 111 to the fourth bearing seat 114 can be formed to have the same structure as the second bearing seat 112 and the transition connection portion 117 described above. In other words, when there is no need to distinguish them, they can be collectively referred to as "bearing seats" and "transition connection portions". Their specific descriptions will not be repeated in this article.

[0062] The above description is only the preferred embodiment and variant of the utility model, and is not intended to limit the utility model. For example, in the above, the gear reducer adopting the 1P structure and the parallel-stage gear reducer in the 2P structure reducer are respectively described as embodiments of the reducer case according to the utility model, but the utility model is not limited to this, but can obviously be applied to all reducer cases using similar reduction mechanisms in the field. In addition, in the above embodiment, the reducer case with four bearing seats supporting two gears is described as an example, but the utility model is not limited to this, but can obviously be applied to reducer cases with more bearing seats supporting more gears. For those skilled in the art, the utility model can have various changes and variations. Any modifications, equivalent substitutions, improvements, etc. made within the spirit and principles of the utility model should be included in the scope of protection of the utility model.

[0063] Reference numerals list

[0064] 11 Input flange 12 Input gear 13 Output gear

[0065] 14 output gear shaft 15 speed reduction mechanism

[0066] 110 main box 120 input side box 111 first bearing seat

[0067] 112 second bearing seat 113 third bearing seat 114 fourth bearing seat

[0068] 115 side panel 116 end panel 117 transition connection part

[0069] 21 planetary reduction mechanism 22 gear reduction mechanism 23 input flange

[0070] 24 output gear shaft 25 input gear 26 output gear

[0071] 27 planetary gear 28 planetary carrier 29 speed reduction mechanism

[0072] 210 Main box 220 Input side box 230 Output side box

[0073] 211 first bearing seat 212 second bearing seat 213 third bearing seat

[0074] 214 fourth bearing seat 215 side panel 216 end panel

[0075] 217 transition connection portion 218 transition connection portion θ included angle.

Claims

1. A reduction gear box housing, wherein a housing space for accommodating a reduction mechanism (15, 29) is formed inside the reduction gear box housing, and at the assembly position with a plurality of gear shafts of the reduction gear mechanism (15, 29), bearing seats (111, 112, 113, 114, 211, 212, 213, 214) for supporting the plurality of gear shafts are formed on opposite sides of the reduction gear box housing, respectively. It is characterized in that At least one of the bearing seats (111, 112, 113, 114, 211, 212, 213, 214) is formed as follows: in a cross section along the axial direction of the reduction mechanism (15, 29), the annular outer wall of the bearing seat (111, 112, 113, 114, 211, 212, 213, 214) is inclined from the middle to both sides relative to the annular inner wall, so that the bearing seat (111, 112, 113, 114, 211, 212, 213, 214) has a polygonal cross-sectional shape that is thick in the middle and thin on both sides.

2. The reduction gearbox housing according to claim 1, characterized in that: The bearing seat (111, 112, 113, 114, 211, 212, 213, 214) is connected to the housing body of the reduction gearbox via a transition connection portion (117, 217, 218) formed in the middle of the annular outer wall, and the transition connection portion (117, 217, 218) is a rounded connection portion protruding outward from the annular outer wall along the circumference of the bearing seat (111, 112, 113, 114, 211, 212, 213, 214).

3. The reduction gearbox housing according to claim 1 or 2, characterized in that: In the cross section along the axial direction of the speed reduction mechanism (15, 29), the annular outer walls inclined from the middle to both sides are respectively formed to have the same angle θ with the axial direction and 0°≤θ≤15°.

4. The reduction gearbox housing according to claim 1 or 2, characterized in that: In the cross section along the axial direction of the speed reduction mechanism (15, 29), the annular outer wall inclined from the middle to both sides is formed to have different angles θ1 and θ2 with the axial direction, and 0°≤θ1≤15° and 0°≤θ2≤15°.

5. The reduction gearbox housing according to claim 2, characterized in that: The radius of the fillet of the transition connection portion (117, 217, 218) is greater than or equal to 8 millimeters.

6. The reduction gearbox housing according to claim 1 or 2, characterized in that: The reduction gearbox housing comprises a main housing (110) and an input side housing (120), and the bearing seats (111, 112, 113, 114, 211, 212, 213, 214) comprise a first bearing seat (111) and a second bearing seat (112) arranged on the main housing (110), and a third bearing seat (113) and a fourth bearing seat (114) arranged on the input side housing (120), wherein the first bearing seat (111) and the third bearing seat (113) support a first gear (12) of the reduction mechanism (15), and the second bearing seat (112) and the fourth bearing seat (114) support a second gear (13) of the reduction mechanism (15).

7. The reduction gearbox housing according to claim 6, characterized in that: The main housing (110) is integrally formed with the first bearing seat (111) and the second bearing seat (112), and the input side housing (120) is integrally formed with the third bearing seat (113) and the fourth bearing seat (114).

8. The reduction gearbox housing according to claim 1 or 2, characterized in that: The reduction gearbox housing comprises a main housing (210), an input side housing (220) located on one side of the main housing (210), and an output side housing (230) located on the other side of the main housing, and The bearing seats (111, 112, 113, 114, 211, 212, 213, 214) include a first bearing seat (211) and a second bearing seat (212) arranged on the main housing (210), and a third bearing seat (213) and a fourth bearing seat (214) arranged on the input side housing (220), wherein the first bearing seat (211) and the third bearing seat (213) support a first gear (25) of the reduction mechanism (29), and the second bearing seat (212) and the fourth bearing seat (214) support a second gear (26) of the reduction mechanism (29).

9. The reduction gearbox housing according to claim 8, characterized in that: The main housing (210) is integrally formed with the first bearing seat (211) and the second bearing seat (212), and the input side housing (220) is integrally formed with the third bearing seat (213) and the fourth bearing seat (214).

10. A reduction gearbox for a fracturing device, the reduction gearbox comprising at least a reduction mechanism (15, 29), an input flange (11, 23), an output gear shaft (14, 24) and a reduction gearbox housing, the reduction mechanism (15, 29) being assembled in the reduction gearbox housing, one end of the input flange (11, 23) being connected to the input gear shaft of the reduction mechanism (15, 29), the other end of the input flange (11, 23) being used to be connected to a power source, one end of the output gear shaft (14, 24) being connected to the output terminal of the reduction mechanism (15, 29), and the other end of the output gear shaft (14, 24) being used to be connected to the crankshaft input end in the crankcase of the fracturing device, characterized in that: The reduction gear box housing is the reduction gear box housing according to any one of claims 1 to 9.

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