CN106763525B - High-bearing gear box - Google Patents
High-bearing gear box Download PDFInfo
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- CN106763525B CN106763525B CN201611109029.9A CN201611109029A CN106763525B CN 106763525 B CN106763525 B CN 106763525B CN 201611109029 A CN201611109029 A CN 201611109029A CN 106763525 B CN106763525 B CN 106763525B
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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
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
- F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
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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
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/042—Guidance of lubricant
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E10/00—Energy generation through renewable energy sources
- Y02E10/70—Wind energy
- Y02E10/72—Wind turbines with rotation axis in wind direction
Abstract
The invention discloses a high-bearing gear box, which comprises a machine base, an input shaft, a first cycloid gear, a second cycloid gear, a hypocycloid gear ring, an output shaft and a large end cover, wherein the input shaft, the first cycloid gear, the second cycloid gear, the hypocycloid gear ring, the output shaft and the large end cover are arranged in the machine base; and an inner swing blocking assembly and an outer swing blocking assembly are sequentially arranged on the input shaft at the outer side of the first bearing outwards. Through using the gear box that this application described, can simplify the structure, easy dismounting, cycloidal gear manufacturability is good, the rigidity is good, utilizes interior to get rid of and keeps off the subassembly and get rid of the dual oil retaining mechanism of keeping off the subassembly mutually supporting, dredges the oil body and returns the oil return passageway, has solved the seepage phenomenon of gear box input shaft effectively.
Description
Technical Field
The invention relates to a high-bearing gear box.
Background
As is well known, the pin wheel output pin pendulum planetary transmission speed reducer has high bearing capacity, high transmission efficiency and high cost performance, so that the pin wheel output pin pendulum planetary transmission speed reducer is approved by the market, but the existing pin wheel output pin pendulum planetary transmission speed reducer still has a plurality of problems, the manufacturing cost of a pin wheel needle bearing is too high, the disassembly is difficult, the gap is difficult to control, and the gap vibration and noise are increased; the gap is too small to be blocked, the traditional simple pin structure is insufficient in bearing capacity, and oil leakage at the position of the input shaft is serious. The prior art has a strong bearing capacity, stable operation and high bearing gear box for preventing oil leakage.
Disclosure of Invention
The invention aims to overcome the defects in the prior art and provide a high-bearing gear box with strong bearing capacity and stable operation.
In order to achieve the aim, the technical scheme of the invention provides a high-bearing gear box, which comprises a machine base and a hypocycloid speed reduction transmission part arranged in the machine base, wherein the hypocycloid speed reduction transmission part comprises an input shaft, a first cycloid gear, a second cycloid gear, a hypocycloid gear ring, an output shaft and a large end cover, the input shaft is supported in a central hole of the large end cover by a first bearing, the phase difference between the first cycloid gear and the second cycloid gear is 180 degrees, the output shaft is supported in the central hole of the machine base by a second bearing and a third bearing, the large end cover is connected with the input end of the machine base,
the shaft extension end of the input shaft is a double eccentric section with a phase difference of 180 degrees, two first sliding bearings are arranged on the double eccentric section, and the two sliding bearings are respectively connected with the first cycloid gear and the second cycloid gear in a supporting way;
the peripheries of the first cycloid gear and the second cycloid gear are uniformly provided with a plurality of pin holes, a second sliding bearing is matched in each pin hole, the first cycloid gear and the second cycloid gear are connected to the double eccentric shafts through the second sliding bearing in a supporting manner, and two ends of the double eccentric shafts are respectively supported in corresponding connecting holes of the annular ring and the large end cover through third sliding bearings; the circular ring and the large end cover are connected into a rigid body; the hypocycloid gear ring is connected with a disc of the output shaft;
and an inner swing blocking assembly and an outer swing blocking assembly are sequentially arranged on the input shaft at the outer side of the first bearing outwards.
By using the gear box, the structure can be simplified, the disassembly and assembly are convenient, and the cycloidal gear has good technological performance and good rigidity; the running noise of the sliding bearing of the device is 3-5 dB lower than that of the rolling bearing; the pins are uniformly stressed and do work, and the pins can be designed to be large enough in diameter, so that the bearing capacity is high; the oil body is led back to the oil return passage by utilizing the mutual matching of the double oil retaining mechanisms of the inner and outer swing retaining assemblies, so that the leakage phenomenon of the input shaft of the gearbox is effectively solved, the labor intensity of fault treatment of parts is greatly reduced, and the practicability and reliability of the equipment are improved.
Preferably, the inner slinger assembly comprises an inner slinger and an inner slinger matched with the inner slinger for use; the inner oil retainer comprises an inner oil retainer ring plate and an inner oil retainer ring pipe, the inner oil retainer ring plate is arranged along the radial direction of the input shaft, the inner oil retainer ring pipe is vertically arranged at the outer edge of the inner oil retainer ring plate, the inner oil retainer ring pipe and the inner oil retainer ring plate are integrally formed, and the outer edge of the inner oil retainer ring pipe is fixed with the inner wall of the central hole of the large end cover;
an inner oil leakage port is arranged at the bottom of the inner oil retainer, and an oil return passage matched with the inner oil leakage port is arranged on the base; the inner oil slinger comprises an inner oil slinger plate and an inner oil slinger ring pipe, wherein the inner oil slinger plate is radially arranged along the input shaft, the inner oil slinger ring pipe is vertically arranged at the inner edge of the inner oil slinger plate, and an oil passing gap is reserved between the outer wall of the inner oil slinger ring pipe and the inner edge of the inner oil slinger. The design is convenient for utilizing the inner oil retainer of the inner throwing baffle assembly and preventing oil body leakage by matching with the inner oil retainer.
Preferably, the outer flinger assembly comprises an outer flinger and an outer flinger matched with the outer flinger for use; the outer edge of the outer oil retainer is fixed with the inner wall of the central hole of the large end cover, and a space is reserved between the inner edge and the input shaft; an outer oil leakage port is arranged at the bottom of the outer oil retainer, and an oil return passage matched with the outer oil leakage port is arranged on the base;
the outer oil retainer comprises an outer oil retainer plate and an outer oil retainer pipe, wherein the outer oil retainer plate is radially arranged along the input shaft, the outer oil retainer pipe is vertically arranged at the outer edge of the outer oil retainer plate, the outer oil retainer pipe and the outer oil retainer plate are integrally formed, the outer edge of the outer oil retainer pipe is fixed with the inner wall of a central hole of the large end cover in a sealing manner, and the outer oil retainer plate is arranged in the middle of the outer oil retainer ring pipe;
the outer oil slinger is arranged on the outer side of the outer oil slinger, the inner edge of the outer oil slinger is fixedly connected with the input shaft in a sealing way, and the outer edge of the outer oil slinger is an outer oil slinger tip; an outer guiding bent plate which is bent towards the outer oil retainer is arranged between the inner edge and the outer edge of the outer oil slinger. The design is convenient for utilizing the outer oil retainer of the outer throwing baffle assembly and preventing oil body leakage by matching with the outer oil retainer.
Preferably, the double eccentric shafts rotate when the speed reducer works, and the circular ring and the large end cover are connected into a rigid body by means of 4-8 pins. The pins are uniformly stressed and do work, and the pins can be designed to be large enough in diameter, so that the bearing capacity is high.
The invention has the advantages and beneficial effects that:
(1) The price of the cast zinc-based alloy sliding bearing or JF800 bimetal sliding bearing is far lower than that of a tapered roller bearing, so that the manufacturing cost can be reduced by 20-30%, and in addition, the weight of the whole machine can be reduced by 10-20%; (2) The cycloidal gear has the advantages of simple structure, convenient disassembly and assembly, good technological performance and good rigidity; (3) The running noise of the sliding bearing of the device is 3-5 dB lower than that of the rolling bearing; (4) The pins are uniformly stressed and do work, and the pins can be designed to be large enough in diameter, so that the bearing capacity is high; (5) The oil body is led back to the oil return passage by utilizing the mutual matching of the double oil retaining mechanisms of the inner and outer swing retaining assemblies, so that the leakage phenomenon of the input shaft of the gearbox is effectively solved, the labor intensity of fault treatment of parts is greatly reduced, and the practicability and reliability of the equipment are improved.
Drawings
FIG. 1 is a schematic diagram of the structure of the present invention;
FIG. 2 is a schematic diagram of a cooling system piping connection according to the present invention;
FIG. 3 is an enlarged schematic view of the input shaft seal structure of the present invention;
FIG. 4 is a schematic view of the structure of the inner oil retainer with inner oleophobic texture of the present invention;
FIG. 5 is a cross-sectional view of the inner oil retainer with inner oleophobic grain of the present invention;
FIG. 6 is a schematic view showing the structure of an inner oil slinger with an inner oil groove according to the present invention
FIG. 7 is a schematic view of the structure of the outer oil retainer with outer oleophobic texture of the present invention;
fig. 8 is a schematic view of the structure of the outer oil slinger provided with the outer oil guiding groove of the present invention.
In the figure: 1. an inner oil slinger; 2. a spiral labyrinth seal groove; 5. an inner oil retainer; 6. an inner oil leakage port; 8. an oil return passage; 9. an inner oil slinger plate; 10. an inner oil-collecting ring pipe; 11. an inner oil baffle ring plate; 12. an inner baffle oil collecting ring pipe; 13. an inner oil throwing tip; 14. an inner oil guiding groove; 15. an inner oil collecting groove; 16. inner oleophobic texture; 17. sealing the end cover; 18. an oil guiding notch; 101. an outer oil slinger; 501. An outer oil slinger; 601. an outer oil leakage port; 901. An outer guide curved plate; 1101. an outer oil retaining ring plate; 1201. an outer oil catcher ring tube; 1301. an oil tip is thrown out from the outside; 1401. an outer oil guiding groove; 1601. an outer oleophobic texture; 102. a base; 202. a second bearing; 302. a third bearing; 402. an output shaft; 502. a disc; 602. double eccentric shafts; 702. a first cycloidal gear; 802. hypocycloid gear ring; 902. a large end cover; 1002. a second cycloidal gear; 1102. a second sliding bearing; 1202. a third sliding bearing; 1302. a first sliding bearing; 1402. an input shaft; 1502. a first bearing; 1602. a pin; 1702. a circular ring; 1802. a cooling cavity; 1902. a superconducting heat pipe; 2002. a cooling liquid; 2102. a jacket layer; 2202. a cooling line 2302, a water inlet; 2402. a water outlet end; 2502. a micro water pump; 2602. the speed reducer housing heats a high-temperature area; 2702. the speed reducer housing heats a relatively low temperature region.
Detailed Description
The following describes the embodiments of the present invention further with reference to the drawings and examples. The following examples are only for more clearly illustrating the technical aspects of the present invention, and are not intended to limit the scope of the present invention.
As shown in fig. 1 to 8, a high-load-bearing gear box comprises a base 102 and a hypocycloidal reduction transmission member arranged in the base 102, wherein the hypocycloidal reduction transmission member comprises an input shaft 1402, a first cycloidal gear 702, a second cycloidal gear 1002, a hypocycloidal gear ring 802, an output shaft 402 and a large end cover 902, the input shaft 1402 is supported in a central hole of the large end cover 902 by a first bearing 1502, the first cycloidal gear 702 is 180 degrees out of phase with the second cycloidal gear 1002, the output shaft 402 is supported in the central hole of the base 102 by a second bearing 202 and a third bearing 302, the large end cover 902 is connected at the input end of the base 102,
the shaft extension end of the input shaft 1402 is a double eccentric section with a phase difference of 180 degrees, two first sliding bearings 1302 are arranged on the double eccentric section, and the two sliding bearings are respectively connected with the first cycloid gear 702 and the second cycloid gear 1002 in a supporting way;
the peripheries of the first cycloid gear 702 and the second cycloid gear are uniformly provided with a plurality of pin holes, a second sliding bearing 1102 is matched in the pin holes, the first cycloid gear 702 and the second cycloid gear 1002 are in supporting connection with the double eccentric shafts 602 through the second sliding bearing 1102, and two ends of the double eccentric shafts 602 are respectively supported in corresponding connecting holes of the circular ring 1702 and the large end cover 902 through third sliding bearings 1202; circular ring 1702 is connected to large end cap 902 as a rigid body; the hypocycloidal gear ring 802 is connected to the disk 502 of the output shaft 402;
an inner fling-stop assembly and an outer fling-stop assembly are sequentially arranged on the input shaft 1402 outside the first bearing 1502.
The inner slinger assembly comprises an inner slinger 5 and an inner slinger 1 matched with the inner slinger 5 for use; the inner oil retainer 5 comprises an inner oil retainer ring plate 11 radially arranged along the input shaft 1402 and an inner oil retainer tube 12 vertically arranged at the outer edge of the inner oil retainer ring plate 11, the inner oil retainer tube 12 and the inner oil retainer plate 11 are integrally formed, and the outer edge of the inner oil retainer ring tube 12 is fixed with the inner wall of the central hole of the large end cover 902;
an inner oil leakage port 6 is formed in the bottom of the inner oil retainer 5, and an oil return passage 8 matched with the inner oil leakage port 6 is formed in the base 102; the inner oil slinger 1 comprises an inner oil slinger plate 9 and an inner oil slinger tube 10, wherein the inner oil slinger plate 9 is radially arranged along the input shaft 1402, the inner oil slinger tube 10 is vertically arranged on the inner edge of the inner oil slinger plate 9, and an oil passing gap is reserved between the outer wall of the inner oil slinger tube 10 and the inner edge of the inner oil slinger 5.
The outer slinger assembly comprises an outer slinger 501 and an outer slinger 101 which is matched with the outer slinger 501 for use; the outer edge of the outer oil retainer 501 is fixed with the inner wall of the central hole of the large end cover 902, and a space is reserved between the inner edge and the input shaft 1402; an outer oil leakage port 601 is formed in the bottom of the outer oil retainer 501, and an oil return passage 8 matched with the outer oil leakage port 601 is formed in the base 102;
the outer oil retainer 501 comprises an outer oil retainer plate 1101 and an outer oil retainer pipe 1201, wherein the outer oil retainer plate 1101 is arranged along the radial direction of the input shaft 1402, the outer oil retainer pipe 1201 is vertically arranged at the outer edge of the outer oil retainer plate 1101, the outer oil retainer pipe 1201 and the outer oil retainer plate 1101 are integrally formed, the outer edge of the outer oil retainer pipe 1201 is fixedly sealed with the inner wall of the central hole of the large end cover 902, and the outer oil retainer plate 1101 is arranged in the middle of the outer oil retainer pipe 1201;
the outer oil slinger 101 is arranged on the outer side of the outer oil slinger 501, the inner edge of the outer oil slinger 101 is fixedly connected with the input shaft 1402 in a sealing way, and the outer edge of the outer oil slinger 101 is an outer oil slinger tip 1301; between the inner and outer edges of the outer slinger 101 is an outer guide bent plate 901 which is bent towards the outer slinger 501.
The double eccentric shafts 602 rotate themselves when the speed reducer works, and the circular ring 1702 and the large end cover 902 are connected into a rigid body by means of 4-8 pins 1602.
Example 1
A high-load-bearing gearbox, which comprises a machine base 102 and a hypocycloidal speed reduction transmission part arranged in the machine base 102, wherein the hypocycloidal speed reduction transmission part comprises an input shaft 1402, a first cycloidal gear 702, a second cycloidal gear 1002, a hypocycloidal gear ring 802, an output shaft 402 and a large end cover 902, the input shaft 1402 is supported in a central hole of the large end cover 902 by a first bearing 1502, the first cycloidal gear 702 and the second cycloidal gear 1002 are 180 degrees out of phase, the output shaft 402 is supported in the central hole of the machine base 102 by a second bearing 202 and a third bearing 302, the large end cover 902 is connected with the input end of the machine base 102,
the shaft extension end of the input shaft 1402 is a double eccentric section with a phase difference of 180 degrees, two first sliding bearings 1302 are arranged on the double eccentric section, and the two sliding bearings are respectively in supporting connection with a first cycloid gear 7027 and a second cycloid gear 1002;
the peripheries of the first cycloid gear 702 and the second cycloid gear are uniformly provided with a plurality of pin holes, a second sliding bearing 1102 is matched in the pin holes, the first cycloid gear 702 and the second cycloid gear 1002 are in supporting connection with the double eccentric shafts 602 through the second sliding bearing 1102, and two ends of the double eccentric shafts 602 are respectively supported in corresponding connecting holes of the circular ring 1702 and the large end cover 902 through third sliding bearings 1202; circular ring 1702 is connected to large end cap 902 as a rigid body; the hypocycloidal gear ring 802 is connected to the disk 502 of the output shaft 402.
The double eccentric shafts 602 rotate themselves when the speed reducer works, and the circular ring 1702 and the large end cover 902 are connected into a rigid body by means of 4-8 pins 1602.
The number of the double eccentric shafts 602 is the same as the number of the pin holes, and 4, or 6, or 8 pin holes are uniformly distributed on the periphery of the first cycloid gear 702 and the periphery of the second cycloid gear.
The first sliding bearing 1302, the second sliding bearing 1102 and the third sliding bearing 1202 are cast zinc-based alloy sliding bearings.
The first sliding bearing 1302, the second sliding bearing 1102 and the third sliding bearing 1202 are JF800 bimetallic bearings.
Example 2:
one optimization for example 1: a high-load-bearing gear box, which comprises a machine base 102 and a hypocycloidal speed reduction transmission part arranged in the machine base 102, wherein the hypocycloidal speed reduction transmission part comprises an input shaft 1402, a first cycloidal gear 702, a second cycloidal gear 1002, a hypocycloidal gear ring 802, a pin, an output shaft 402 and a large end cover 902, the input shaft 1402 is supported in a central hole of the large end cover 902 by a first bearing 1502, the phase difference between the first cycloidal gear and the second cycloidal gear is 180 degrees, the output shaft 402 is supported in the central hole of the machine base 102 by a second bearing 202 and a third bearing 302, the large end cover 902 is connected with the input end of the machine base 102,
the shaft extension end of the input shaft 1402 is a double eccentric section with a phase difference of 180 degrees, and two first sliding bearings 1302 are arranged on the double eccentric section and used for supporting the first cycloid gear 702 and the second cycloid gear 1002 respectively;
4 or 6 or 8 pin holes are uniformly distributed around the first cycloid gear 702 and the second cycloid gear 1002, a second sliding bearing 1102 is matched in the pin holes, the first cycloid gear 702 and the second cycloid gear 1002 are supported on double eccentric shafts 602 by means of the second sliding bearing 1102, the number of the double eccentric shafts 602 is the same as that of the pin holes, two ends of each double eccentric shaft 602 are respectively supported in corresponding holes of a circular ring 1702 and a large end cover 902 by means of third sliding bearings 1202, the double eccentric shafts 602 rotate themselves when the speed reducer works, and the circular ring 1702 and the large end cover 902 are connected into a rigid body by means of 4-8 pins 1602;
the hypocycloidal gear ring 802 is connected to the disc 502 of the output shaft 402, and the hypocycloidal transmission is a transmission in which the hypocycloidal gear ring 802 is meshed with a cycloidal gear, and thus belongs to the technical field of cycloidal transmission. Because the hypocycloid gear ring 802 and the cycloid gear are in pure rolling engagement and have good lubrication, the bearing capacity of the double cycloid engagement pair is improved by about 50% compared with that of a general cycloid under the condition of the same input power. Considering the machining precision of the hypocycloid gear ring 802, the machining precision is reasonably calculated according to 30-40% improvement. The hypocycloidal gear ring 802 replaces the pin gear of a universal cycloid, and has the advantages of simple structure, fewer parts and no tooth extraction at the maximum reduction ratio 159.
The hypocycloid gear ring 802 outputs a speed reducer, and the first sliding bearing 1302, the second sliding bearing 1102 and the third sliding bearing 1202 are cast zinc-based alloy sliding bearings, which have the following advantages:
1. the casting performance is good, the casting is compact, the friction factor is small, the heat conductivity is high, and the finish turning surface roughness can reach 1.6;
2. 40% lighter than copper by weight and 40% lower than tin bronze by cost;
3. the service life is 2-3 times of that of tin bronze, and the self-lubricating and shock-absorbing functions are realized, so that the self-lubricating and shock-absorbing composite material is suitable for medium-low speed and heavy-load occasions;
4. the magnetic material has no magnetism and no spark performance, and is safe in dangerous occasions of inflammability and explosiveness.
The hypocycloid gear ring 802 output speed reducer, the first sliding bearing 1302, the second sliding bearing 1102 and the third sliding bearing 1202 are JF800 bimetal bearings, the JF800 bimetal bearings are steel copper alloy products with low carbon steel plates as matrix materials and CuPb10Sn10 or CuSn6Zn6Pb3 materials sintered on the surfaces, and the hypocycloid gear ring 802 output speed reducer is a high-load low-speed sliding bearing with wide application range and is commonly used as a balance bridge bushing and a gasket of a heavy truck; driven wheels of bulldozer; automotive steel bushings, and the like. JF800 bimetal bearing technical parameters: pressure-bearing 65N/mm2 and use temperature: 260 ℃, hardness: HB 70-100.
Example 3:
one optimization for example 2: the cooling system is arranged outside the machine base 102 and the shell to ensure that the speed reducer is maintained in a reasonable temperature range during operation, and the speed reducing effect of the speed reducer is prevented from being influenced due to overhigh temperature.
The cooling system comprises a cooling cavity 1802 arranged outside the shell, wherein cooling liquid 2002 is filled in the cooling cavity 1802, a superconducting heat pipe 1902 is further arranged in the cooling cavity 1802, and the superconducting heat pipe 1902 is in contact with the cooling liquid 2002;
such a design maintains the coolant 2002 in a lower temperature range through the superconducting heat pipe 1902, while the coolant 2002 is cooled in contact with the housing, maintaining the temperature of the entire speed reducer. The superconducting heat pipe 1902 is used for cooling the cooling liquid 2002, the structure is simple, circulation equipment of the cooling liquid 2002 is omitted, and the cooling efficiency is high.
The cooling cavity 1802 is provided in a heat generating high temperature region 2602 of the speed reducer housing (outside the housing near the first cycloid gear 702, and the hypocycloid ring gear 802), and the cooling cavity 1802 is enclosed and sealed by the outer jacket 2102 and the housing outer wall.
The cooling pipeline 2202 is further arranged outside the shell, cooling liquid 2002 is filled in the cooling pipeline 2202, the cooling pipeline 2202 is tightly attached to the shell, the cooling pipeline 2202 is spiral, the cooling pipeline 2202 comprises a water inlet end 2302 and a water outlet end 2402, and the water inlet end 2302 and the water outlet end 2402 are respectively communicated with the cooling cavity 1802.
The water inlet end 2302 is connected with the cooling cavity 1802 through a micro water pump 2502.
The cooling circuit 2202 is disposed in a relatively low temperature region 2702 of the heat generation of the reducer housing (relatively outside the housing proximate to the output shaft 402, the second bearing 202, and the third bearing 302).
By providing the cooling channels 2202 on the housing, the low heat areas of the housing can be cooled by the micro-circulation of the cooling channels 2202, ensuring the operating temperature of these areas, and particularly in a high temperature environment in summer, relieving the cooling pressure in the cooling cavity 1802; meanwhile, the micro water pump 2502 enables the cooling liquid 2002 in the cooling pipeline 2202 and the cooling liquid 2002 in the cooling cavity 1802 to circulate, so that the cooling liquid 2002 in the cooling pipeline 2202 can be replaced, meanwhile, the cooling liquid 2002 in the cooling cavity 1802 can be enabled to flow, and heat exchange with the superconducting heat pipe 1902 is accelerated, and two purposes are achieved.
Example 4
Optimization of any of embodiments 1 to 3:
the inside of the central hole of the large end cover 902 is connected with an input shaft 1402 through a first bearing 1502; an inner swing block assembly and an outer swing block assembly are sequentially arranged on the input shaft 1402 outside the first bearing 1502 outwards;
the inner slinger assembly comprises an inner slinger 5 and an inner slinger 1 matched with the inner slinger 5 for use; the inner oil retainer 5 comprises an inner oil retainer ring plate 11 radially arranged along the input shaft 1402 and an inner oil retainer tube 12 vertically arranged at the outer edge of the inner oil retainer ring plate 11, the inner oil retainer tube 12 and the inner oil retainer plate 11 are integrally formed, and the outer edge of the inner oil retainer ring tube 12 is fixed with the inner wall of the central hole of the large end cover 902;
an inner oil leakage opening 6 is formed in the bottom of the inner oil retainer 5, and an oil return passage 8 matched with the inner oil leakage opening 6 is formed in the bottom of the box body; the inner oil slinger 1 comprises an inner oil slinger plate 9 and an inner oil slinger pipe 10, wherein the inner oil slinger plate 9 is radially arranged along the input shaft 1402, the inner oil slinger pipe 10 is vertically arranged at the inner edge of the inner oil slinger plate 9, and an oil passing gap is reserved between the outer wall of the inner oil slinger pipe 10 and the inner edge of the inner oil slinger 5;
the outer slinger assembly comprises an outer slinger 501 and an outer slinger 101 which is matched with the outer slinger 501 for use; the outer edge of the outer oil retainer 501 is fixed with the inner wall of the central hole of the large end cover 902, and a space is reserved between the inner edge and the input shaft 1402; an outer oil leakage port 601 is formed in the bottom of the outer oil retainer 501, and an oil return passage 8 matched with the outer oil leakage port 601 is formed in the bottom of the box body;
the outer oil retainer 501 comprises an outer oil retainer plate 1101 and an outer oil retainer pipe 1201, wherein the outer oil retainer plate 1101 is arranged along the radial direction of the input shaft 1402, the outer oil retainer pipe 1201 is vertically arranged at the outer edge of the outer oil retainer plate 1101, the outer oil retainer pipe 1201 and the outer oil retainer plate 1101 are integrally formed, the outer edge of the outer oil retainer pipe 1201 is fixedly sealed with the inner wall of the central hole of the large end cover 902, and the outer oil retainer plate 1101 is arranged in the middle of the outer oil retainer pipe 1201;
the outer oil slinger 101 is arranged on the outer side of the outer oil slinger 501, the inner edge of the outer oil slinger 101 is fixedly connected with the input shaft 1402 in a sealing way, and the outer edge of the outer oil slinger 101 is an outer oil slinger tip 1301; between the inner and outer edges of the outer slinger 101 is an outer guide bent plate 901 which is bent towards the outer slinger 501.
The inner oil slinger plate 9 is arranged on the oil outlet side of the oil passing gap; the inner oil slinger pipe 10 is provided with pin holes fixed with the input shaft 1402, the inner oil slinger pipe 10 and the inner oil slinger plate 9 are integrally formed, and the outer end part of the inner oil slinger plate 9 is an inner oil slinger tip 13.
When the oil body splash at the outer end part of the connection cooperation of the input shaft 1402 and the bearing, the oil body passes through the blocking seal of the inner and outer swing baffle assemblies in sequence, so that a good oil leakage prevention effect is achieved; under the action of the inner baffle assembly, the oil body splashes onto the inner oil retainer 5 firstly, and particularly, most of the oil body splashes onto the joint of the inner oil retainer plate 11 and the inner oil retainer pipe 12 and the peripheral area thereof, the oil body is converged on the inner oil retainer plate 11 under the guidance of the inner oil retainer pipe 12, and the oil body on the inner oil retainer plate 11 flows downwards under the action of gravity and finally is converged on the inner oil leakage port 6, so that the oil flows back to the inner cavity from the oil return passage 8; a small part of oil body enters the inner oil slinger pipe 10 from the oil passing gap, gradually enters the inner oil slinger plate 9 under the outward seepage trend of the oil body, is slinged out from the inner oil slinger tip 13 under the action of centrifugal force, and enters the oil retaining function of the outer oil retaining ring 501 of the outer oil slinger assembly;
under the action of the outer baffle assembly, the oil body splashed from the inner oil slinger plate 9 splashes onto the outer oil slinger 501, and particularly most of the oil body splashes on the joint of the outer oil slinger plate 1101 and the outer oil slinger pipe 1201 and the peripheral area (inner surface area) thereof, the oil body is converged on the outer oil slinger plate 1101 under the guidance of the outer oil slinger pipe 1201, the oil body on the outer oil slinger plate 1101 flows downwards under the action of gravity and finally is converged on the outer oil leakage port 601, so that the oil flows back to the inner cavity from the oil return passage 8; a small part of oil body enters the outer oil slinger 101 from the space, is thrown out by the outer oil slinger tip 1301 under the guide of the outer guide curved plate 901 under the action of centrifugal force, gathers on the outer oil retaining ring plate 1101 (outer surface area), and the oil body on the outer oil retaining ring plate 1101 flows downwards under the action of gravity and finally gathers on the outer oil leakage port 601, so that the oil flows back to the inner cavity from the oil return passage 8; the oil seepage is prevented by the cooperation of the swing baffle and the swing baffle.
Example 5
As a further optimization for the embodiment 4, a part of oil guiding groove bodies are arranged on the surface of the swing block assembly, and the flow direction and the flow velocity of the oil bodies are further optimized; meanwhile, mechanical energy of the labyrinth groove is increased to provide sealing protection for the last step.
The inner oil slinger plate 9 is a disc-shaped circular plate with a thicker middle part and thinner end parts, and an inner oil guide groove 14 is formed in the surface of the disc-shaped circular plate.
One way of grooving the inner oil guide groove 14: the inner oil guide groove 14 is opened along the radial direction of the disc-shaped circular plate. The design is favorable for the oil body to be thrown out along the outer edge of the inner oil guide groove 14 on the disc-shaped circular plate, improves throwing efficiency and force, and is convenient for the next step of collection of the inner oil retainer 5.
Another way of grooving the inner oil guide groove 14 is: the inner oil guide groove 14 extends along the center of the disc-shaped circular plate outwards along a spiral line. The design is favorable for the oil body to be thrown out along the outer edge of the inner oil guide groove 14 on the disc-shaped circular plate, improves throwing efficiency and force, and is convenient for the next step of collection of the inner oil retainer 5.
An inner oil collecting groove 15 is formed in the joint of the inner oil retaining ring plate 11 and the inner oil retaining ring pipe 12, and the inner oil collecting groove 15 is communicated with the inner oil leakage port 6; the inner oil retaining ring plate 11 is provided with inner oil drain lines 16 on the surface, the inner oil drain lines 16 are annular, and the lower end of the annular inner oil drain lines 16 is communicated with the inner oil leakage port 6. Such a design facilitates the collection of oil bodies (most of the oil bodies) splashed at the junction of the inner oil deflector ring plate 11 and the inner oil deflector ring tube 12 in the inner oil collection groove 15 and the discharge from the inner oil leakage port 6 along the inner oil collection groove 15; the rest small amount of oil body is along the inner oleophobic grain 16 to the inner oil leakage port 6, so that the oil body is prevented from entering the oil passing gap to the maximum extent.
The outer oil retainer plate 1101 is provided with outer oleophobic lines 1601 on the surface, the outer oleophobic lines 1601 are annular, and the lower end of the annular outer oleophobic lines 1601 is communicated with the outer oil leakage port 601. The oil body is prevented from entering the space to the greatest extent along the outer oleophobic grain 1601 to the outer oil leakage port 601.
The input shaft 1402 is further provided with a sealing end cover 17, the sealing end cover 17 is in sealing connection with the box body, the sealing end cover 17 is provided with an input shaft 1402 via hole, and a spiral labyrinth seal groove 2 matched and sealed with the input shaft 1402 is arranged in the input shaft 1402 via hole. In this design, the space between the input shaft 1402 and the seal cap 17 is sealed by the spiral labyrinth seal groove 2. Further improving the sealing effect.
The spiral labyrinth seal groove 2 has a spiral direction opposite to the rotation direction, an oil guiding notch 18 is arranged at the lower end of the spiral labyrinth seal groove 2, and the oil guiding notch 18 is communicated with the oil return passage 8. The spiral labyrinth seal groove 2 is configured to prevent oil from spreading to the outside of the input shaft 1402 during rotation of the input shaft 1402, by using the reverse direction of the spiral labyrinth seal groove 2, and to provide a final oil leakage preventing effect.
During assembly, the form and position tolerance of the gear box body is firstly checked, whether the part where the sealing structure is installed is deformed or not is checked, and if the roundness exceeds 0.3mm, correction is required to be carried out so as to ensure that the gear box does not generate interference and friction in the working process.
The foregoing is merely a preferred embodiment of the present invention, and it should be noted that it will be apparent to those skilled in the art that several modifications and variations can be made without departing from the technical principle of the present invention, and these modifications and variations should also be regarded as the scope of the invention.
Claims (2)
1. A high load bearing gearbox, characterized by: the hypocycloid speed reduction transmission part comprises an input shaft, a first cycloid gear, a second cycloid gear, a hypocycloid gear ring, an output shaft and a large end cover, wherein the input shaft is supported in a central hole of the large end cover by a first bearing, the first cycloid gear and the second cycloid gear are 180 degrees out of phase, the output shaft is supported in the central hole of the base by a second bearing and a third bearing, and the large end cover is connected with the input end of the base;
the shaft extension end of the input shaft is a double eccentric section with a phase difference of 180 degrees, two first sliding bearings are arranged on the double eccentric section and are respectively connected with the first cycloid gear and the second cycloid gear in a supporting way:
the periphery equipartition of first cycloid wheel and two cycloid wheels has a plurality of pinholes, the pinhole intussuseption is fitted with second slide bearing, and first cycloid wheel and second cycloid wheel pass through second slide bearing and support to be connected on the double eccentric shaft, the both ends of double eccentric shaft are supported respectively in the corresponding connecting hole of ring circle and big end cover with third slide bearing: the circular ring and the large end cover are connected into a rigid body: the hypocycloid gear ring is connected with a disc of the output shaft, and the first sliding bearing, the second sliding bearing and the third sliding bearing are cast zinc-based alloy sliding bearings:
an inner swing blocking assembly and an outer swing blocking assembly are sequentially arranged on the input shaft at the outer side of the first bearing outwards;
the inner slinger assembly comprises an inner slinger and an inner slinger matched with the inner slinger for use: the inner oil retainer comprises an inner oil retainer plate radially arranged along the input shaft and an inner oil retainer ring pipe perpendicularly arranged at the outer edge of the inner oil retainer plate, the inner oil retainer pipe and the inner oil retainer plate are integrally formed, and the outer edge of the inner oil retainer pipe is fixed with the inner wall of a central hole of the large end cover:
the bottom of the inner oil retainer is provided with an inner oil leakage port, and the base is provided with an oil return passage matched with the inner oil leakage port: the inner oil slinger comprises an inner oil slinger plate and an inner oil slinger ring pipe, wherein the inner oil slinger plate is radially arranged along the input shaft, the inner oil slinger ring pipe is vertically arranged at the inner edge of the inner oil slinger plate, and an oil passing gap is reserved between the outer wall of the inner oil slinger ring pipe and the inner edge of the inner oil slinger;
the outer flinger assembly comprises an outer flinger and an outer flinger matched with the outer flinger for use: the outer edge of the outer oil retainer is fixed with the inner wall of the central hole of the large end cover, and a space is reserved between the inner edge and the input shaft; the bottom of the outer oil retainer is provided with an outer oil leakage port, and the base is provided with an oil return passage matched with the outer oil leakage port:
the outer oil retainer comprises an outer oil retainer plate and an outer oil retainer pipe, wherein the outer oil retainer plate is radially arranged along the input shaft, the outer oil retainer pipe is perpendicularly arranged at the outer edge of the outer oil retainer plate, the outer oil retainer pipe and the outer oil retainer plate are integrally formed, the outer edge of the outer oil retainer pipe is fixedly sealed with the inner wall of a central hole of a large end cover, and the outer oil retainer plate is arranged at the middle part of the outer oil retainer ring pipe:
the outer oil slinger is arranged on the outer side of the outer oil slinger, the inner edge of the outer oil slinger is fixedly connected with an input shaft in a sealing way, and the outer edge of the outer oil slinger is an outer oil slinger tip: an outer guiding bent plate which is bent towards the outer oil retainer is arranged between the inner edge and the outer edge of the outer oil slinger.
2. The high load gearbox of claim 1, wherein: the double eccentric shafts rotate when the speed reducer works, and the circular ring and the large end cover are connected into a rigid body by means of 4-8 pins.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201611109029.9A CN106763525B (en) | 2016-12-06 | 2016-12-06 | High-bearing gear box |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201611109029.9A CN106763525B (en) | 2016-12-06 | 2016-12-06 | High-bearing gear box |
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| CN106763525B true CN106763525B (en) | 2023-06-16 |
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| CN108953501A (en) * | 2018-09-19 | 2018-12-07 | 杭州星河传动机械研究院有限公司 | Multi-eccentric speed reducer |
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| US6343794B1 (en) * | 1999-10-01 | 2002-02-05 | Donald J. Brown | Lubricant seal having partition plate with gutter for drive motor gears and the like |
| CN201832693U (en) * | 2010-07-20 | 2011-05-18 | 四川矿山机器（集团）有限责任公司 | Large gear shaft sealing structure of ball mill |
| CN203730717U (en) * | 2013-12-13 | 2014-07-23 | 四川矿山机器（集团）有限责任公司 | Adjustable pinion sealing structure |
| JP2015137708A (en) * | 2014-01-22 | 2015-07-30 | 三菱重工コンプレッサ株式会社 | Oil thrower device and rotary machine |
| CN104196989A (en) * | 2014-08-06 | 2014-12-10 | 吴小杰 | Star wheel reduction gearbox for interlayer water-cooling box zinc-base alloy bearing support |
| CN205446649U (en) * | 2015-12-28 | 2016-08-10 | 南京高速齿轮制造有限公司 | Wind -driven generator gear case's end seal |
| CN206398017U (en) * | 2016-12-06 | 2017-08-11 | 江苏昊克传动科技股份有限公司 | High-mechanic gear-box |
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