CN117267317B - Coaxial high-speed gearbox of power branch - Google Patents
Coaxial high-speed gearbox of power branch Download PDFInfo
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- CN117267317B CN117267317B CN202311538958.1A CN202311538958A CN117267317B CN 117267317 B CN117267317 B CN 117267317B CN 202311538958 A CN202311538958 A CN 202311538958A CN 117267317 B CN117267317 B CN 117267317B
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- 238000007789 sealing Methods 0.000 claims description 65
- 230000008878 coupling Effects 0.000 claims description 23
- 238000010168 coupling process Methods 0.000 claims description 23
- 238000005859 coupling reaction Methods 0.000 claims description 23
- 230000003068 static effect Effects 0.000 claims description 11
- 244000126211 Hericium coralloides Species 0.000 claims description 8
- 230000002457 bidirectional effect Effects 0.000 abstract description 6
- 230000001133 acceleration Effects 0.000 abstract description 2
- 230000005540 biological transmission Effects 0.000 description 14
- 239000003921 oil Substances 0.000 description 13
- 230000000694 effects Effects 0.000 description 7
- 239000012530 fluid Substances 0.000 description 4
- 239000010687 lubricating oil Substances 0.000 description 3
- 239000000956 alloy Substances 0.000 description 2
- 229910045601 alloy Inorganic materials 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- 238000005096 rolling process Methods 0.000 description 2
- 235000004443 Ricinus communis Nutrition 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 239000012528 membrane Substances 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
- F16H1/20—Toothed gearings for conveying rotary motion without gears having orbital motion involving more than two intermeshing members
- F16H1/22—Toothed gearings for conveying rotary motion without gears having orbital motion involving more than two intermeshing members with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/027—Gearboxes; Mounting gearing therein characterised by means for venting gearboxes, e.g. air breathers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/029—Gearboxes; Mounting gearing therein characterised by means for sealing the gearboxes, e.g. to improve airtightness
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H2057/02086—Measures for reducing size of gearbox, e.g. for creating a more compact transmission casing
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Gear Transmission (AREA)
Abstract
A power branch coaxial high-speed gear box relates to the field of engineering machinery design. The invention aims to solve the problem that the existing power branch coaxial high-speed gearbox cannot meet the requirement of high-speed heavy-load operation. The invention comprises an input side coupler, an input shaft, an output side coupler, two branch shafts, two torsion shafts I and two torsion shafts II, wherein the middle part of the torsion shaft I is sequentially sleeved with a first-stage gear and a second-stage right-side bevel gear from outside to inside along the axial direction, the first-stage gear is fixedly connected with the torsion shaft I and the torsion shaft II respectively, the second-stage right-side bevel gear is fixedly connected with the torsion shaft I, the middle part of the branch shaft is fixedly connected with a second-stage left-side bevel gear, the inner side end of the branch shaft is sleeved and fixedly connected with the outer side of the inner side end of the torsion shaft II, the low-speed input shaft gear is meshed with the first-stage gear, and the second-stage right-side bevel gear and the second-stage left-side bevel gear are respectively meshed with a high-speed output shaft gear. The invention is used for a gearbox for bidirectional rotation, acceleration or deceleration.
Description
Technical Field
The invention relates to the field of engineering machinery design, in particular to a power branch coaxial high-speed gear box.
Background
The high-speed gear box is widely applied to various transmission fields of aviation, aerospace, navigation, industry and the like at present, wherein the high-precision industries of aviation, aerospace, navigation and the like have higher requirements on the gear box. On the premise of ensuring high reliability, light weight, miniaturization, high power density and smaller starting (running) power consumption, the transmission structure form, compactness, high-speed heavy load, transmission efficiency, sealing performance and better dynamics of the gear box are subjected to stringent technical requirements.
When the application environment is high-speed heavy load, the prior power branch coaxial high-speed gearbox mostly adopts sliding bearings on the design of a transmission shaft system, but the problems are that the lubricating oil quantity requirement and starting (running) power consumption of the sliding bearings are increased more than those of the sliding bearings, and the prior power branch coaxial high-speed gearbox is not applicable to the application environment with strict requirements on power consumption and lubrication. If the gearbox is required to realize bidirectional rotation, speed increasing or speed reducing, the adoption of the sliding bearing support is limited due to the change of the stress direction, and if the axial distance of the whole transmission device is increased by adopting the sliding bearing, the volume and the weight of the whole gearbox are correspondingly increased. At present, the high-pressure oil gas exists in the box body due to the fact that the rotating speed of the existing high-speed heavy-load gearbox is high, the heating value is large, the lubricating oil quantity is large, and the phenomenon of poor sealing performance is commonly caused. How to consider the transmission structure form, compactness, high-speed heavy load, transmission efficiency, sealing performance and better dynamics of a gear box in design is a problem to be solved in the design.
Disclosure of Invention
The invention aims to solve the problem that the existing power branch coaxial high-speed gear box cannot meet the requirement of high-speed heavy-load operation, and further provides the power branch coaxial high-speed gear box.
The technical scheme adopted for solving the technical problems is as follows:
the utility model provides a coaxial high-speed gear box of power branch, including input side shaft coupling, the input shaft, the output side shaft coupling, two branch fulcrum shafts, two torsion shaft I and two torsion shaft II, input side shaft coupling is connected with the outside end of input shaft, the middle part rigid coupling of input shaft has a low-speed input shaft gear, the both sides of input shaft respectively are equipped with a torsion shaft I, torsion shaft II coaxial cartridge is in torsion shaft I's middle part, torsion shaft I's middle part is equipped with I level gear and II level right side bevel gear from outside to inside in proper order in the axial direction, I level gear respectively with torsion shaft I and torsion shaft II rigid coupling, II level right side bevel gear and torsion shaft I rigid coupling, the output shaft sets up the inboard end at the input shaft, the middle part rigid coupling of output shaft has two high-speed output shaft gears, the both sides of output shaft respectively are equipped with a branch fulcrum shaft, the middle part rigid coupling of branch fulcrum shaft has II level left side bevel gear, the inboard end suit of branch fulcrum shaft is in torsion shaft II outside the inboard end, low-speed input shaft gear and I level gear phase-engaging with I level right side bevel gear and II level bevel gear phase, the output shaft is equipped with the output shaft of high-speed phase shaft coupling respectively, the output shaft is equipped with the output shaft of high-speed phase shaft side shaft coupling with the outside of the output shaft, the output shaft is connected with the high-speed bevel gear phase gear.
Further, the input shaft and the low-speed input shaft gear are of an integral structure, the branch shaft and the II-stage left bevel gear are of an integral structure, and the output shaft and the high-speed output shaft gear are of an integral structure.
Further, the outer side end of the input shaft is sequentially sleeved with the four-point contact ball bearing and the cylindrical roller bearing from outside to inside along the axial direction, the outer side end of the first-stage gear is sequentially sleeved with the four-point contact ball bearing and the cylindrical roller bearing from outside to inside along the axial direction, the inner side end of the II-stage right-side bevel gear is sequentially sleeved with the four-point contact ball bearing and the cylindrical roller bearing from inside to outside along the axial direction, and the outer side end of the branch shaft is sequentially sleeved with the four-point contact ball bearing and the cylindrical roller bearing from outside to inside along the axial direction.
Further, two ends of the output shaft are sleeved with sliding bearings capable of rotating bidirectionally.
Further, the inner side end of the input shaft, the inner side end of the I-stage gear, the outer side end of the II-stage right-side bevel gear and the inner side end of the branch shaft are sleeved with low-speed cylindrical roller bearings.
Further, oil slingers are respectively sleeved at the outer side ends of the input shaft and the output shaft, and the oil slingers are respectively arranged at the inner sides of the high-speed sealing ring and the low-speed sealing ring.
Further, the high-speed sealing ring and the low-speed sealing ring are respectively provided with an air pressure balance joint.
Further, the high-speed sealing ring and the low-speed sealing ring are both of two-layer comb tooth sealing structures, each of the two-layer comb tooth sealing structures comprises a first-level static ring, a first-level movable ring sealing tooth, a second-level movable ring sealing tooth and a second-level static ring, the second-level movable ring sealing tooth is arranged on the outer side of the first-level movable ring sealing tooth, the first-level static ring and the first-level movable ring sealing tooth are matched to form an inner-layer comb tooth sealing structure, and the second-level static ring and the second-level movable ring sealing tooth are matched to form an outer-layer comb tooth sealing structure.
Further, the high-speed sealing ring is fixedly connected to the output side coupler, and the I-stage moving ring sealing tooth and the II-stage moving ring sealing tooth are fixedly connected with the output side coupler through screws.
Further, the low-speed input shaft gear and the first-stage gear are monoclinic gears, and empty knife grooves are arranged on the surfaces of the monoclinic gears along the circumferential direction.
Compared with the prior art, the invention has the following beneficial effects:
the coaxial high-speed gearbox with the power branches has the advantages of compactness, high speed and heavy load, transmission efficiency, sealing performance and good dynamics on the premise of meeting the requirement of a coaxial gear transmission structure form.
The low-speed stage supporting bearing of the whole gear box adopts a rolling bearing, and the high-speed output adopts a sliding bearing for supporting, so that the use functions of coaxial input and output, bidirectional rotation and speed increase (speed reduction) can be realized. In addition, the oil slinger and the membrane disc coupler are arranged on the gear shaft, and the two layers of grate teeth are arranged in a sealing mode, so that high-pressure oil and gas mixed in the gear box can be conveniently discharged out of the gear box through a small amount of leaked oil gas after the two layers of grate teeth are sealed and pressed, and the sealing effect of the gear box is greatly improved.
Drawings
FIG. 1 is a schematic illustration of a power-branched coaxial high-speed gearbox of the present invention;
FIG. 2 is a schematic view of a partial construction of a power-branched coaxial high-speed gearbox of the present invention;
FIG. 3 is a schematic view of the structure of the low speed seal ring of the present invention;
FIG. 4 is a schematic view of the structure of the high speed seal ring of the present invention;
FIG. 5 is a schematic view of the structure of torsion shafts I and II of the present invention;
FIG. 6 is a cross-sectional view taken along line V1-V1 of FIG. 2;
fig. 7 is a cross-sectional view taken along line V2-V2 in fig. 2.
The device comprises a 1-input side coupler, a 2-low speed input shaft gear, a 3-I-stage gear, a 4-torsion shaft I, a 5-torsion shaft II, a 6-II-stage right-side bevel gear, a 7-II-stage left-side bevel gear, an 8-high speed output shaft gear, a 9-high speed sealing ring, a 10-sliding bearing, a 11-output side coupler, a 12-low speed sealing ring, a 13-four-point contact ball bearing, a 14-cylindrical roller bearing, a 15-oil slinger, a 16-I-stage stationary ring, a 17-I-stage movable ring sealing tooth, a 18-II-stage movable ring sealing tooth, a 19-II-stage stationary ring, a 20-round nut, a 21-locking gasket, a 22-air pressure balance joint and 23-screws.
Detailed Description
In order to make the technical problems, technical schemes and beneficial effects solved by the invention more clear, the invention is further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are for purposes of illustration only and are not intended to limit the scope of the invention.
The first embodiment is as follows: referring to fig. 1 to 7, the embodiment is described in this embodiment, the coaxial high-speed gearbox with power branching includes an input side coupling 1, an input shaft, an output side coupling 11, two branch shafts, two torsion shafts I4 and two torsion shafts II5, the input side coupling 1 is connected with the outer side end of the input shaft, the middle part of the input shaft is fixedly connected with a low-speed input shaft gear 2, two sides of the input shaft are respectively provided with a torsion shaft I4, the torsion shafts II5 are coaxially inserted in the middle part of the torsion shaft I4, the middle part of the torsion shaft I4 is sequentially sleeved with a first stage gear 3 and a second stage right bevel gear 6 from outside to inside along the axial direction, the first stage gear 3 is fixedly connected with the torsion shafts I4 and II5, the second stage right bevel gear 6 is fixedly connected with the torsion shafts I4, the output shaft is arranged at the inner side end of the input shaft, the middle part of the output shaft is fixedly connected with two high-speed output shaft gears 8, two branch shafts II are respectively provided with a third stage bevel gears 7 fixedly connected with the inner side end of the input shaft 8, the left side end of the third stage bevel gear 7 is fixedly connected with the output shaft 8, the outer side end of the third stage bevel gear 3 is meshed with the second stage output shaft 8, and the second stage bevel gear 3 is meshed with the second stage output shaft 8.
The input power transmits torque to the low-speed input shaft gear 2 via the input-side coupling 1 to mesh with the I-th stage gear 3. Torque is respectively transmitted to the torsion shafts I4 and II5 through the internal spline teeth of the I-stage gear 3, so that power split is realized. The torsion shafts I4 and II5 respectively transmit torque to the II-stage right-side bevel gear 6 and the II-stage left-side bevel gear 7, and respectively mesh with the high-speed output shaft gear 8 to realize power confluence, so that the torque is transmitted to the output side coupler 11 and then transmitted to a load, and the power density of the whole gearbox is improved. Under the condition of meeting the strength of the transmission shaft, the purpose of adjusting the dynamic characteristics of the shafting can be achieved by changing the torsional rigidity of the torsion shafts I4 and II 5.
The sealing effect of the gearbox is improved by the high-speed sealing ring 9 and the low-speed sealing ring 12.
The input side coupling 1 is an input side low speed stage film disk coupling, and the output side coupling 11 is an output side high speed stage film disk coupling.
The internal spline teeth of the first-stage gear 3 are meshed with the torsion shafts I4 and II5 at the same time, the axial fixation is realized through the round nuts 20 and the locking gaskets 21 to realize power split, and the power is respectively transmitted to the second-stage right-side bevel gear 6 and the second-stage left-side bevel gear 7 through the respective torsion shafts. How to ensure the equal load of power transmission is carried out, the corresponding meshing marks of the working tooth surface are required to be checked, the specific requirements are shown in the section view V1-V1 and the section view V2-V2 in the figure 2, when the gear meshing working surface is determined to be the A or B surface, in order to ensure that the equal load deviation of the power of the torsion shafts I4 and II5 is not large, the meshing marks of the meshing working surface A1/A2 or B1/B2 are required to be checked to be consistent during assembly, and the II-stage right bevel gear 6 and the II-stage left bevel gear 7 are respectively meshed with the high-speed output shaft gear 8 to realize power confluence to transmit the power to a load, so that the power density of the whole gear box is improved. Under the condition of meeting the strength of the transmission shaft, the torsional rigidity of the torsion shaft can be changed by changing the shaft diameter size of the torsion shaft I/II so as to achieve the purpose of adjusting the dynamic characteristics of the shaft system.
The second embodiment is as follows: the present embodiment is described with reference to fig. 1 to 7, in which the input shaft and the low-speed input shaft gear 2 are of an integral structure, the branch shaft and the II-stage left bevel gear 7 are of an integral structure, and the output shaft and the high-speed output shaft gear 8 are of an integral structure. The technical features not disclosed in this embodiment are the same as those of the first embodiment.
The input shaft and the low-speed input shaft gear 2 are integral gear shafts, and the branch shaft and the II-stage left bevel gear 7 are integral gear shafts.
And a third specific embodiment: referring to fig. 1 to 7, in this embodiment, the outer end of the input shaft is sequentially sleeved with the four-point contact ball bearing 13 and the cylindrical roller bearing 14 from outside to inside in the axial direction, the outer end of the first-stage gear 3 is sequentially sleeved with the four-point contact ball bearing 13 and the cylindrical roller bearing 14 from outside to inside in the axial direction, the inner end of the second-stage right-side bevel gear 6 is sequentially sleeved with the four-point contact ball bearing 13 and the cylindrical roller bearing 14 from inside to outside in the axial direction, and the outer end of the branch shaft is sequentially sleeved with the four-point contact ball bearing 13 and the cylindrical roller bearing 14 from outside to inside in the axial direction. The technical features not disclosed in this embodiment are the same as those of the second embodiment.
The four-point contact ball bearing 13 bears the axial force generated by gear meshing, so that axial positioning is realized, and the cylindrical roller bearing 14 bears the large radial force generated by meshing.
The specific embodiment IV is as follows: the present embodiment will be described with reference to fig. 1 to 7, in which the two ends of the output shaft are each fitted with a bidirectional rotary slide bearing 10. The technical features not disclosed in this embodiment are the same as those of the third embodiment.
The low-speed stage supporting bearings of the whole gear box are rolling bearings, namely four-point contact ball bearings 13 and cylindrical roller bearings 14, and the high-speed output shaft is supported by adopting a sliding bearing 10, so that the use functions of coaxial input and output, bidirectional rotation, power input, speed increase or speed reduction can be realized, and the gear box has lower starting operation power consumption loss and smaller oil quantity.
The II-stage right bevel gear 6 and the II-stage left bevel gear 7 are respectively provided with bevel gears with opposite directions, when the high-speed output shaft gear 8 is meshed with the bevel gears, the axial force is counteracted, and the bidirectional rotation of the whole gear box, lower starting power consumption loss and lubricating oil quantity can be realized by adopting the radial sliding bearing 10 capable of bidirectionally rotating.
Fifth embodiment: referring to fig. 1 to 7, the present embodiment is described in which the low-speed cylindrical roller bearings are respectively fitted to the inner end of the input shaft, the inner end of the I-stage gear 3, the outer end of the II-stage right-side bevel gear 6, and the inner end of the branch shaft. The technical features not disclosed in this embodiment are the same as those of the fourth embodiment.
Specific embodiment six: in the present embodiment, the outer ends of the input shaft and the output shaft are respectively sleeved with the oil slinger 15, and the oil slinger 15 is respectively arranged on the inner sides of the high-speed sealing ring 9 and the low-speed sealing ring 12, as described in the present embodiment, with reference to fig. 1 to 7. The technical features not disclosed in this embodiment are the same as those of the first embodiment.
Seventh embodiment: the present embodiment will be described with reference to fig. 1 to 7, in which the high-speed seal ring 9 and the low-speed seal ring 12 according to the present embodiment are provided with air pressure balance joints 22, respectively. The technical features not disclosed in this embodiment are the same as those of the first embodiment.
By adopting the oil slinger 15, the two-layer castor sealing structure and the air pressure balance joint 22, the sealing effect of the gear box is greatly improved. The air pressure balance joint 22 is convenient for discharging a small amount of leaked oil gas out of the gear box after the high-pressure oil gas mixed in the gear box is sealed and pressed by the two layers of grate teeth, so that the sealing effect of the gear box is greatly improved.
Eighth embodiment: referring to fig. 1 to 7, in this embodiment, the high-speed seal ring 9 and the low-speed seal ring 12 each adopt a two-layer labyrinth seal structure, the two-layer labyrinth seal structure includes a stage i stationary ring 16, a stage i movable ring seal tooth 17, a stage ii movable ring seal tooth 18 and a stage ii stationary ring 19, the stage ii movable ring seal tooth 18 is disposed on the outer side of the stage i movable ring seal tooth 17, the stage i stationary ring 16 and the stage i movable ring seal tooth 17 cooperate to form an inner layer labyrinth seal structure, and the stage ii stationary ring 19 and the stage ii movable ring seal tooth 18 cooperate to form an outer layer labyrinth seal structure. The technical features not disclosed in this embodiment are the same as those of the seventh embodiment.
The sealing principle of the two-layer grate teeth is that the two-layer grate teeth are formed by the I-stage stationary ring 16, the I-stage movable ring sealing teeth 17, the II-stage movable ring sealing teeth 18 and the II-stage stationary ring 19, a series of gaps and dissipation air cavities are formed between the movable ring sealing teeth and the stationary ring, when leakage fluid passes through the gaps, rapid acceleration expansion is carried out, speed energy is dissipated into heat energy by turbulent vortex when the leakage fluid passes through the dissipation cavities, and the pressure of the leakage fluid is gradually reduced due to throttling and thermodynamic effects of the fluid so as to achieve the sealing effect.
The bar type alloy is cast on the surfaces of the I-level static ring 16 and the II-level static ring 19 respectively, so that the bar type alloy can play a role in protecting, can bear a small contact between the sealing teeth of the movable ring and the static ring, can naturally form a minimum gap, and achieves the best sealing effect.
Detailed description nine: in the present embodiment, the high-speed seal ring 9 is fixed to the output-side coupling 11, and the first-stage seal ring tooth 17 and the second-stage seal ring tooth 18 are fixed to the output-side coupling 11 by screws 23, as described with reference to fig. 1 to 7. The technical features not disclosed in this embodiment are the same as those of the eighth embodiment.
The I-stage movable ring seal tooth 17 and the II-stage movable ring seal tooth 18 are fixedly connected with the output side coupler 11 through screws 23 to form an integrated structure.
Detailed description ten: the present embodiment is described with reference to fig. 1 to 7, in which the low-speed input shaft gear 2 and the I-th stage gear 3 are single bevel gears, and the single bevel gears have empty pockets arranged in the circumferential direction on the gear surface. The technical features not disclosed in this embodiment are the same as those of the first embodiment.
For high-speed gear transmission, especially for single-bevel gear transmission, because the power transmitted is larger, the generated heat is more, and in order to prevent the gear from being meshed, the idle slot is added on the single-bevel gear because of larger thermal deformation caused by the too wide gear width. The single bevel gear is provided with a clearance groove in the circumferential direction of the gear surface, the diameter range of the groove bottom is selected from the range that the size of the base circle of the gear is larger than that of the root circle of the gear, the width of the clearance groove is 10-0.05 b (mm), and b is the width of the gear.
The foregoing has shown and described the basic principles and main features of the present invention and the advantages of the present invention. It will be understood by those skilled in the art that the present invention is not limited to the embodiments described above, and that the above embodiments and descriptions are merely illustrative of the principles of the present invention, and various changes and modifications may be made without departing from the spirit and scope of the invention, which is defined in the appended claims. The scope of the invention is defined by the appended claims and equivalents thereof.
Claims (6)
1. The utility model provides a coaxial high-speed gear box of power branch which characterized in that: the input shaft comprises an input side shaft coupling (1), an input shaft, an output side shaft coupling (11), two branch shafts, two torsion shafts I (4) and two torsion shafts II (5), wherein the input side shaft coupling (1) is connected with the outer side end of the input shaft, a low-speed input shaft gear (2) is fixedly connected in the middle of the input shaft, two torsion shafts I (4) are respectively arranged on two sides of the input shaft, the torsion shafts II (5) are coaxially inserted in the middle of the torsion shafts I (4), a first stage gear (3) and a second stage right oblique gear (6) are sequentially sleeved in the middle of the torsion shafts I (4) from outside to inside along the axial direction, the first stage gear (3) is fixedly connected with the torsion shafts I (4) and the torsion shafts II (5) respectively, the second stage right oblique gear (6) is fixedly connected with the torsion shafts I (4) respectively, the middle of the output shaft is fixedly connected with two high-speed output shaft gears (8) respectively, two branch shafts II are respectively arranged on two sides of the output shaft are respectively provided with a branch shaft, the left side branch shafts II are respectively sleeved with the first stage gears (7) and the second stage oblique gears (7) are meshed with the outer side of the output shaft (8) of the output shaft (2) respectively, the first stage right oblique gears (7) are meshed with the second stage oblique gears (8) respectively, the second stage right oblique gears (3) are meshed with the second stage oblique gears respectively, the outer side end of the input shaft is provided with a low-speed sealing ring (12), and the outer side end of the output shaft is provided with a high-speed sealing ring (9);
the outer side end of the input shaft is sequentially sleeved with a four-point contact ball bearing (13) and a cylindrical roller bearing (14) from outside to inside along the axial direction, the outer side end of the first-stage gear (3) is sequentially sleeved with the four-point contact ball bearing (13) and the cylindrical roller bearing (14) from outside to inside along the axial direction, the inner side end of the second-stage right-side bevel gear (6) is sequentially sleeved with the four-point contact ball bearing (13) and the cylindrical roller bearing (14) from inside to outside along the axial direction, and the outer side end of the branch shaft is sequentially sleeved with the four-point contact ball bearing (13) and the cylindrical roller bearing (14) from outside to inside along the axial direction;
two ends of the output shaft are sleeved with sliding bearings (10) capable of rotating bidirectionally;
the high-speed sealing ring (9) and the low-speed sealing ring (12) are respectively provided with an air pressure balance joint (22);
the high-speed sealing ring (9) and the low-speed sealing ring (12) are both of two-layer comb tooth sealing structures, each of the two-layer comb tooth sealing structures comprises a level I static ring (16), a level I moving ring sealing tooth (17), a level II moving ring sealing tooth (18) and a level II static ring (19), the level II moving ring sealing tooth (18) is arranged on the outer side of the level I moving ring sealing tooth (17), the level I static ring (16) and the level I moving ring sealing tooth (17) are matched to form an inner-layer comb tooth sealing structure, and the level II static ring (19) and the level II moving ring sealing tooth (18) are matched to form an outer-layer comb tooth sealing structure.
2. A power-branched coaxial high-speed gearbox according to claim 1, wherein: the input shaft and the low-speed input shaft gear (2) are of an integral structure, the branch shaft and the II-stage left bevel gear (7) are of an integral structure, and the output shaft and the high-speed output shaft gear (8) are of an integral structure.
3. A power-branched coaxial high-speed gearbox according to claim 2, wherein: the low-speed cylindrical roller bearings are sleeved at the inner side end of the input shaft, the inner side end of the I-stage gear (3), the outer side end of the II-stage right-side bevel gear (6) and the inner side end of the branch shaft.
4. A power-branched coaxial high-speed gearbox according to claim 1, wherein: the oil slinger (15) is sleeved at the outer side ends of the input shaft and the output shaft, and the oil slinger (15) is respectively arranged at the inner sides of the high-speed sealing ring (9) and the low-speed sealing ring (12).
5. A power-branched coaxial high-speed gearbox according to claim 1, wherein: the high-speed sealing ring (9) is fixedly connected to the output side coupler (11), and the I-stage moving ring sealing teeth (17) and the II-stage moving ring sealing teeth (18) are fixedly connected with the output side coupler (11) through screws (23).
6. A power-branched coaxial high-speed gearbox according to claim 1, wherein: the low-speed input shaft gear (2) and the I-stage gear (3) are monoclinic gears, and empty cutter grooves are arranged on the surfaces of the monoclinic gears along the circumferential direction.
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| Application Number | Priority Date | Filing Date | Title |
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| CN202311538958.1A CN117267317B (en) | 2023-11-17 | 2023-11-17 | Coaxial high-speed gearbox of power branch |
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| CN202311538958.1A CN117267317B (en) | 2023-11-17 | 2023-11-17 | Coaxial high-speed gearbox of power branch |
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| CN117267317B true CN117267317B (en) | 2024-04-09 |
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| US4197758A (en) * | 1977-06-17 | 1980-04-15 | Compagnie Industrielle Des Telecommunications | Transmission by gears with divided trains |
| JPH08320054A (en) * | 1995-05-24 | 1996-12-03 | Toyota Motor Corp | Gear transmission |
| CN2721635Y (en) * | 2004-08-27 | 2005-08-31 | 重庆齿轮箱有限责任公司 | Speed reducer with power division and central transmission |
| EP1619386A2 (en) * | 2004-07-23 | 2006-01-25 | Wilhelm Schäfer | Transmission for high power wind generation installation |
| DE102012013834A1 (en) * | 2012-07-13 | 2014-01-16 | Renk Ag | Power-split transmission for use in wind power plant, has drive tooth formed at drive-sided shaft, and planetary gearings engaged with output tooth over respective coupling shafts, where coupling shafts run coaxial to drive-sided shaft |
| DE102012014273A1 (en) * | 2012-07-19 | 2014-05-15 | Renk Aktiengesellschaft | Gearbox with power split |
| CN106594185A (en) * | 2016-11-30 | 2017-04-26 | 中信重工机械股份有限公司 | Single-input and double-output gear box and multi-point meshing gear driving system of ultra-large-sized mill |
| WO2017071818A1 (en) * | 2015-10-27 | 2017-05-04 | Sew-Eurodrive Gmbh & Co. Kg | Gearing, having a gearing housing |
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2023
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Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4197758A (en) * | 1977-06-17 | 1980-04-15 | Compagnie Industrielle Des Telecommunications | Transmission by gears with divided trains |
| JPH08320054A (en) * | 1995-05-24 | 1996-12-03 | Toyota Motor Corp | Gear transmission |
| EP1619386A2 (en) * | 2004-07-23 | 2006-01-25 | Wilhelm Schäfer | Transmission for high power wind generation installation |
| CN2721635Y (en) * | 2004-08-27 | 2005-08-31 | 重庆齿轮箱有限责任公司 | Speed reducer with power division and central transmission |
| DE102012013834A1 (en) * | 2012-07-13 | 2014-01-16 | Renk Ag | Power-split transmission for use in wind power plant, has drive tooth formed at drive-sided shaft, and planetary gearings engaged with output tooth over respective coupling shafts, where coupling shafts run coaxial to drive-sided shaft |
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| DE102012014273A1 (en) * | 2012-07-19 | 2014-05-15 | Renk Aktiengesellschaft | Gearbox with power split |
| WO2017071818A1 (en) * | 2015-10-27 | 2017-05-04 | Sew-Eurodrive Gmbh & Co. Kg | Gearing, having a gearing housing |
| CN106594185A (en) * | 2016-11-30 | 2017-04-26 | 中信重工机械股份有限公司 | Single-input and double-output gear box and multi-point meshing gear driving system of ultra-large-sized mill |
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| Publication number | Publication date |
|---|---|
| CN117267317A (en) | 2023-12-22 |
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