CN111005996A - End face cam gear-pushing speed reducer - Google Patents
End face cam gear-pushing speed reducer Download PDFInfo
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- CN111005996A CN111005996A CN201911394336.XA CN201911394336A CN111005996A CN 111005996 A CN111005996 A CN 111005996A CN 201911394336 A CN201911394336 A CN 201911394336A CN 111005996 A CN111005996 A CN 111005996A
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- input shaft
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- 239000003638 chemical reducing agent Substances 0.000 title claims abstract description 57
- 230000005540 biological transmission Effects 0.000 claims abstract description 18
- 238000002347 injection Methods 0.000 claims abstract description 15
- 239000007924 injection Substances 0.000 claims abstract description 15
- 210000004907 gland Anatomy 0.000 claims abstract description 14
- 238000007789 sealing Methods 0.000 claims abstract description 8
- 125000006850 spacer group Chemical group 0.000 claims abstract description 8
- 239000003921 oil Substances 0.000 claims description 19
- 239000010687 lubricating oil Substances 0.000 claims description 3
- 239000010705 motor oil Substances 0.000 claims description 3
- 239000003129 oil well Substances 0.000 abstract description 6
- 230000009467 reduction Effects 0.000 description 8
- 230000033001 locomotion Effects 0.000 description 5
- 230000009471 action Effects 0.000 description 4
- 230000001965 increasing effect Effects 0.000 description 3
- 230000007246 mechanism Effects 0.000 description 3
- 230000002708 enhancing effect Effects 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000000605 extraction Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 239000003208 petroleum Substances 0.000 description 1
- 230000008569 process Effects 0.000 description 1
Images
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
- F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
- F16H25/08—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for interconverting rotary motion and reciprocating motion
- F16H25/12—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for interconverting rotary motion and reciprocating motion with reciprocation along the axis of rotation, e.g. gearings with helical grooves and automatic reversal
- F16H25/125—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for interconverting rotary motion and reciprocating motion with reciprocation along the axis of rotation, e.g. gearings with helical grooves and automatic reversal having the cam on an end surface of the rotating element
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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
- F16H53/00—Cams or cam-followers, e.g. rollers for gearing mechanisms
- F16H53/02—Single-track cams for single-revolution cycles; Camshafts with such cams
- F16H53/025—Single-track cams for single-revolution cycles; Camshafts with such cams characterised by their construction, e.g. assembling or manufacturing features
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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
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/02—Toothed members; Worms
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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)
- Retarders (AREA)
- Transmission Devices (AREA)
Abstract
本发明公开一种端面凸轮推齿减速机，包括机体外壳、输入轴、输出轴、推齿、推齿滑道固定在一起，安装法兰固定在机体外壳上，将端面凸轮推齿减速机与潜油电机安装在一起；所述机体外壳包括输入端壳体、输出端壳体、注油连接压盖和注油螺塞；所述输入轴通过二口推力轴承及隔套装入输入端壳体，所述输出轴通过二口推力轴承及隔套装入输出端壳体；所述推齿滑道通过螺纹连接在输入端壳体和输出端壳体之间，所述推齿设置多个，安装在推齿滑道内，所述机体外壳的螺纹连接处设置均设置密封O圈。本发明适应油井地下的多项极端工况，具有传动性能好、结构紧凑、传动比小、传动扭矩大的特点。
The invention discloses an end face cam push gear reducer, which comprises a body casing, an input shaft, an output shaft, a push gear and a push gear slideway fixed together, a mounting flange is fixed on the body casing, and the end face cam push gear reducer is connected with the end face cam push gear reducer. The submersible motor is installed together; the body shell includes an input end casing, an output end casing, an oil injection connection gland and an oil injection screw plug; the input shaft is inserted into the input end casing through two thrust bearings and a spacer, so The output shaft is inserted into the output end casing through two thrust bearings and a spacer; the push tooth slideway is connected between the input end casing and the output end casing through threads, and a plurality of the push teeth are arranged and are installed on the push teeth. In the tooth slideway, sealing O-rings are arranged at the threaded connections of the body shell. The invention adapts to a number of extreme working conditions in the underground of oil wells, and has the characteristics of good transmission performance, compact structure, small transmission ratio and large transmission torque.
Description
Technical Field
The invention relates to the field of speed reducers for underground driving oil extraction systems, in particular to an end face cam gear-pushing speed reducer.
Background
Currently, in some petroleum downhole devices, such as screw pumps, turbine power drills, etc. with motors placed downhole, a reduction gearing is often required to achieve optimal operating conditions. In the existing concentric speed reduction transmission, an involute small-tooth-difference speed reducer, a cycloidal pin speed reducer, a harmonic speed reducer, a movable-tooth speed reducer and the like have the characteristics of compact structure, high bearing capacity, high mechanical efficiency and the like, and the speed reducer is originally the preferred type of the underground speed reducer, but the speed reduction ratio of the speed reducer is generally large, so that the speed reducer is limited in underground transmission application. For the most common underground submersible motor reducer, the reduction ratio is too large, the output rotating speed is too low, the single-day yield of an oil well is seriously influenced, the equipment is not suitable for most oil well working conditions, the popularization range is small, and the market competitiveness is lost.
If the speed reducers are combined in an inverted series mode, the purpose of finally reducing the speed ratio can be achieved by firstly reducing the speed with a large reduction ratio and then increasing the speed with a small speed ratio, but the stress of a machine part is increased as a result of the speed reducers, the structure is correspondingly increased, and the original advantages are lost. At the same time, the structure of the whole speed reducing mechanism is more complicated.
Meanwhile, the speed reducers have respective defects under the special working condition of the underground oil field: the involute small-tooth-difference speed reducer and the oscillating-tooth speed reducer are complex in design and calculation, the application range of the involute small-tooth-difference speed reducer and the oscillating-tooth speed reducer is seriously influenced, and meanwhile, the involute small-tooth-difference speed reducer adopts internal meshing with small tooth number difference, so that the interference condition is also complex; the radial size of the cycloidal needle speed reducer is difficult to reach the working condition size of underground use due to the existence of the cycloidal needle wheel; the material of the flexible gear of the harmonic reducer is difficult to ensure the service life of the oil well under the conditions of high temperature and high pressure at a certain depth.
In practical use, involute planetary gear reducers and involute internal meshing differential mechanisms have also been used in downhole transmissions. These two types of transmission also have their drawbacks: the involute planetary gear reducer is limited by the radial dimension, so that the modulus selected by the gear is small, the load is small, and the involute planetary gear reducer is not suitable for transmission of large torque. The involute inner gearing differential mechanism is a plus machine, the efficiency is low, and the service life is short. The service life is an important index for examining the underground oil production equipment, and the corresponding higher cost is caused by each time of the underground operation and the well lifting operation.
Disclosure of Invention
In order to solve the problems, the invention provides an end face cam gear-pushing speed reducer.
The technical scheme of the invention is as follows:
the end face cam gear-pushing speed reducer comprises a machine body shell, an input shaft, an output shaft, a gear-pushing slide rail and a gear-pushing slide rail, wherein the machine body shell is fixed together:
the mounting flange is fixed on the machine body shell, and the end face cam gear-pushing speed reducer and the submersible motor are mounted together;
the machine body shell comprises an input end shell, an output end shell, an oil injection connecting gland and an oil injection plug screw, wherein one end of the oil injection connecting gland is connected to the mounting flange through threads, and the other end of the oil injection connecting gland is mounted on the input end shell through threads;
the input shaft is arranged in the input end shell through the two-port thrust bearing and the spacer bush, and the output shaft is arranged in the output end shell through the two-port thrust bearing and the spacer bush; the screw thread positions of the input shaft and the output shaft are respectively provided with a nut fastener a, a nut fastener b, a shaft elastic check ring and a set screw, and the nut fastener a and the shaft elastic check ring on the input shaft are arranged on the input shaft; the set screw is fixed on the nut b and is screwed on the thread on the input end shell along with the nut b, and the nut a on the output shaft and the elastic retainer ring for the shaft are arranged on the output shaft; the set screw is fixed on the nut b and is screwed on the thread on the output end shell along with the nut b; the threads of the nut a on the input shaft and the output shaft are used for adjusting the play of the bearing to achieve the purpose of free rotation movement, and the elastic retainer ring, the set screw and the nut b for the shaft are used for enhancing the installation precision and preventing the expansion of the bearing play and the unscrewing of the nut a.
The plurality of push teeth are arranged and mounted in the push tooth slide way, the push teeth do reciprocating linear motion in the push tooth slide way, and the push tooth slide way restrains the push teeth to complete normal transmission;
and sealing O rings are arranged at the threaded connection parts of the machine body shell.
According to the preferable scheme of the end face cam gear-pushing speed reducer, the gear-pushing is designed to be of an asymmetric structure, and the line lengths on two sides of the tooth-shaped peak of the gear-pushing are different and the inclination angles are different.
In the above end face cam gear-pushing reducer, preferably, a locus of a point on a tooth profile of the gear-pushing is identical to a locus of a point on the corresponding output shaft end face cam.
In the above end cam tooth pushing speed reducer, preferably, the circumferential expansion of the linear tracks of the end cams on the input shaft and the output shaft may be set as a formula curve, a cycloid, an involute or a lattice according to a certain rule.
In the above end-face cam tooth-pushing speed reducer, preferably, the curve on the end-face cam of the input shaft is a single-period curve composed of a wave crest and a wave trough; the curve on the end face cam of the output shaft is a multi-period curve, and the numerical value of the period determines the speed ratio of the end face cam gear-pushing speed reducer. The single period of the curve on the input shaft end face cam and the curve on the output shaft end face cam are functions of the same corresponding relation, namely: when the circumferential angle theta is taken as an independent variable, the linear tracks of the curves on the end face cams of the input shaft and the output shaft satisfy the following conditions: f (θ) ═ f (n θ) is a functional relationship.
The end face cam gear-pushing speed reducer has the preferable scheme that when motor oil of the submersible motor is different from lubricating oil of the end face cam gear-pushing speed reducer, a mechanical seal and a mechanical seal seat are additionally arranged, the mechanical seal seat is fixed on an oil injection connection gland through a screw, a fixed ring of the mechanical seal is arranged on the mechanical seal seat, and a movable ring is arranged on an input shaft.
The invention discloses an end face cam gear-pushing speed reducer, wherein an input shaft and an output shaft both adopt the form of end face cams, when power equipment transmits torque to the input shaft, the cams on the end face of the input shaft transmit power to a group of gear-pushing teeth in a contact type transmission mode, the group of gear-pushing teeth transmit power to the cams on the end face of the output shaft in a contact type transmission mode, and finally the power is output by the output shaft.
The principle of formation of the transmission with a fixed reduction ratio of the invention is analyzed with respect to the reciprocating motion of a single pushing tooth: under the action of torque generated by power equipment, thrust is generated at the wave crest of the input shaft, the torque is transmitted to the push teeth through contact action, the push teeth are abutted against the wave troughs of the cam line on the end face of the output shaft, which are also restrained by the output end shell, under the action of the thrust and the restraint of the push tooth slide way, and at the moment, the push teeth move to the end of the output shaft; when the input shaft rotates a certain angle to reach the end surface cam trough of the input shaft, the push teeth are abutted against the wave crest of the end surface cam line of the output shaft, which is also restrained by the output end shell, under the action of the push force and the restraint of the push tooth slide way, and at the moment, the push teeth move to the end of the input shaft. The two end faces of the push tooth are always kept in close contact with the two end faces of the input shaft and the output shaft under all stress in the process. The stress state of each rest push tooth is the same as the example. Because the linear track design of the end face cams of the input shaft and the output shaft meets the following requirements: f (theta) is a function of f (n theta), so that after the input shaft has rotated through one revolution, 360 deg., under the power plant, the output shaft has also rotated through one cycle, 360/n deg.. The fixed reduction ratio of the speed reducer is n, the number of the push teeth is also determined by the value of n, and the maximum sum is the number of cycles of the input shaft and the output shaft.
The invention has the beneficial effects that:
(1) the invention is suitable for a plurality of extreme working conditions under the ground of an oil well, and has the characteristics of good transmission performance, compact structure, small transmission ratio and large transmission torque;
(2) the radial dimension of the speed reducer is small, the largest radial dimension is the end face diameters of the input shaft and the output shaft, the end face diameter values of the input shaft and the output shaft are selected according to the inner diameter of the oil well casing, when the inner diameter of the casing is small, the overall radial dimension of the speed reducer can be reduced, and when the torque requirement is not large, the radial dimension can reach 60 mm;
(3) the invention adopts the form of the end face cam, and compared with the speed reducer adopting gear transmission, the bearing capacity of the speed reducer is greatly improved;
(4) a mechanical seal and a mechanical seal seat are additionally arranged for isolating motor oil of the submersible motor from lubricating oil of the end face cam gear-pushing speed reducer;
(5) the invention has simple structure, small processing difficulty, reliable operation and long service life.
Drawings
FIG. 1 is a cross-sectional view of an end cam gear reduction unit;
FIG. 2 is a schematic view of an input shaft configuration;
FIG. 3 is a schematic view of an output shaft;
FIG. 4 is a schematic view of a pushing tooth structure;
FIG. 5 is a schematic view of a tooth pushing slide;
in the figure, 1-mounting flange; 2, mechanical sealing; 3-mechanical seal seat; 4-an input shaft; 5-two thrust bearings; 6-spacer bush; 7-input end housing; 8-pushing teeth; 9-a tooth-pushing slideway; 10-output shaft, 11-nut a; 12-circlip for shaft; 13-set screws; 14-Tight mother b; 15-output end shell; 16-sealing O-rings; 17-oil filling screw plug; 18-oiling connecting gland and 19-input shaft end cam; 20-output shaft end cam.
Detailed Description
As shown in fig. 1-5, an end-face cam gear-pushing speed reducer comprises a machine body shell, an input shaft 4, an output shaft 10, a gear-pushing 8 and a gear-pushing slideway 9, which are fixed together:
the mounting flange 1 is fixed on a machine body shell, and an end face cam gear-pushing speed reducer and an oil-submersible motor are mounted together;
the machine body shell comprises an input end shell 7, an output end shell 15, an oil injection connecting gland 18 and an oil injection plug screw 17, wherein one end of the oil injection connecting gland is connected to the mounting flange 1 through threads, and the other end of the oil injection connecting gland is mounted on the input end shell 7 through threads;
the input shaft 4 is arranged in the input end shell 7 through the two-port thrust bearing 5 and the spacer bush 6, and the output shaft 10 is arranged in the output end shell 15 through the two-port thrust bearing 5 and the spacer bush 6; the screw thread positions of the input shaft 4 and the output shaft 10 are respectively provided with a nut a11, a nut b14, a shaft elastic check ring 12 and a set screw 13, and the nut a11 and the shaft elastic check ring 12 on the input shaft 4 are arranged on the input shaft 4; the set screw 13 is fixed on the nut b14 and screwed on the screw thread on the input end shell 7 along with the nut b14, the nut a11 on the output shaft 10 and the elastic retainer ring 12 for the shaft are arranged on the output shaft 10; the set screw 13 is fixed on the nut b14 and is screwed on the thread on the output end shell 15 along with the nut b 14; the threads of the nut a11 on the input shaft 4 and the output shaft 10 are used for adjusting the play of the bearing to achieve the purpose of free rotation movement, and the circlip 12 for the shaft, the set screw 13 and the nut b14 are used for enhancing the installation precision, preventing the play of the bearing from expanding and preventing the nut a11 from being buckled.
The push tooth slide ways 9 are connected between the input end shell 7 and the output end shell 15 through threads, 8 push teeth 8 are arranged and installed in the push tooth slide ways 9, the push teeth 8 do reciprocating linear motion in the push tooth slide ways 9, and the push tooth slide ways 9 restrict the push teeth 8 to complete normal transmission; the push tooth 8 is designed to be in an asymmetric structure, the line lengths on two sides of the tooth-shaped wave crest of the push tooth 8 are different, the inclination angles are different, and the locus of a point on the tooth shape of the push tooth 8 is matched with the locus of a point on the end face cam 20 of the corresponding output shaft 10. The circumferential development of the linear tracks of the end face cams on the input shaft 4 and the output shaft 10 is set as a formula; the curve on the input shaft end face cam 19 is a single-cycle curve composed of a wave crest and a wave trough; the curve on the output shaft end face cam 20 is a multi-cycle curve, and the single cycle of the curve on the input shaft end face cam 19 and the single cycle of the curve on the output shaft end face cam 20 are functions of the same corresponding relationship, that is: when the circumferential angle θ is used as an independent variable, the linear locus of the curve on the input shaft end face cam 19 and the curve on the output shaft end face cam 20 satisfies: f (θ) ═ f (n θ) is a functional relationship.
The threaded connection of the machine body shell is provided with sealing O rings 16, the mechanical sealing seat 3 is fixed on the oil injection connecting gland 18 through screws, the fixed ring of the mechanical seal 2 is arranged on the mechanical sealing seat 3, and the movable ring is arranged on the input shaft 4.
Claims (6)
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201911394336.XA CN111005996B (en) | 2019-12-30 | 2019-12-30 | A kind of end face cam push gear reducer |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201911394336.XA CN111005996B (en) | 2019-12-30 | 2019-12-30 | A kind of end face cam push gear reducer |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN111005996A true CN111005996A (en) | 2020-04-14 |
| CN111005996B CN111005996B (en) | 2024-11-26 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201911394336.XA Active CN111005996B (en) | 2019-12-30 | 2019-12-30 | A kind of end face cam push gear reducer |
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| Country | Link |
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| CN (1) | CN111005996B (en) |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN201228754Y (en) * | 2008-03-23 | 2009-04-29 | 西南石油大学 | Downhole small teeth difference external tooth output decelerator |
| JP2010090907A (en) * | 2008-10-03 | 2010-04-22 | Ito Seisakusho:Kk | Rotary reduction gear |
| CN106931080A (en) * | 2017-03-14 | 2017-07-07 | 长江大学 | A kind of helix movable steel globe teeth drive deceleration device |
| JP3217060U (en) * | 2017-07-07 | 2018-07-12 | 深▲せん▼市領略数控設備有限公司 | Micro reducer |
| CN211624117U (en) * | 2019-12-30 | 2020-10-02 | 辽宁瑞邦石油技术发展有限公司 | End face cam gear-pushing speed reducer |
-
2019
- 2019-12-30 CN CN201911394336.XA patent/CN111005996B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN201228754Y (en) * | 2008-03-23 | 2009-04-29 | 西南石油大学 | Downhole small teeth difference external tooth output decelerator |
| JP2010090907A (en) * | 2008-10-03 | 2010-04-22 | Ito Seisakusho:Kk | Rotary reduction gear |
| CN106931080A (en) * | 2017-03-14 | 2017-07-07 | 长江大学 | A kind of helix movable steel globe teeth drive deceleration device |
| JP3217060U (en) * | 2017-07-07 | 2018-07-12 | 深▲せん▼市領略数控設備有限公司 | Micro reducer |
| CN211624117U (en) * | 2019-12-30 | 2020-10-02 | 辽宁瑞邦石油技术发展有限公司 | End face cam gear-pushing speed reducer |
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| Publication number | Publication date |
|---|---|
| CN111005996B (en) | 2024-11-26 |
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