CN101776129A - Gear interlinking speed reducer - Google Patents
Gear interlinking speed reducer Download PDFInfo
- Publication number
- CN101776129A CN101776129A CN200910060479A CN200910060479A CN101776129A CN 101776129 A CN101776129 A CN 101776129A CN 200910060479 A CN200910060479 A CN 200910060479A CN 200910060479 A CN200910060479 A CN 200910060479A CN 101776129 A CN101776129 A CN 101776129A
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- gear
- eccentric bushing
- speed
- middling speed
- shaft assembly
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Abstract
The invention relates to a gear interlinking speed reducer which comprises an ordinary gear shunting and speed reducing part and a double crank connecting link inner gear interlinking transmission part. The speed reducer is characterized in that power is input from a high-speed power shaft, and after power shunting and speed reducing are realized through the engagement of a high-speed gear, an idle gear, a left intermediate speed gear and a right intermediate speed gear, the power is input onto a left intermediate speed shaft assembly and a right intermediate speed shaft assembly simultaneously; the left intermediate speed shaft assembly and the right intermediate speed shaft assembly synchronously operate in the same direction to drive an outside low speed inner gear plate A, an outside low speed inner gear plate B and a middle low speed inner gear plate to do plane motions; the central inner gear holes of the inner gear plates and low speed gears have planetary engagement with small teeth difference to realize power synthesis; and a low speed high torque is output from a low speed shaft to realize transmission. The invention has the characteristics of compact structure, large transmission ratio, strong loading and overloading capacity, and the like and can be widely applied to mechanical transmission.
Description
Technical field
The present invention relates to a kind of gear interlinking speed reducer, realize slowing down by gear and few tooth difference train.
Background technique
Existing retarder has been widely used in metallurgy, the mine, on the various heavy duty equipments such as chemical industry, and bring into play enormous function aborning, these retarders are because of its structural design difference, the kind difference, usability is also different, as three-ring speed reducer, although overcome many shortcomings than traditional retarder, but still there is following shortcoming: be not suitable for running up, the problems such as having the unbalanced couple square that runs up, these retarders can both transmitting torque at present, play decelerating effect, but needing under the situation of low-speed heave-load when mechanical, existing various model retarders just can not adapt to the demand of modern science and technology.
Summary of the invention
The purpose of this invention is to provide a kind of gear interlinking speed reducer, the idle pulley of shunting and being installed on the lower velocity shaft by gear reduction carries out the transition on left middling speed shaft assembly and the right middling speed shaft assembly, finally can realize large speed ratio, the output heavy load, the retarder of big driving torque, the while has also been dwindled the volume of retarder.
Above-mentioned purpose can realize by a kind of gear interlinking speed reducer, on casing, be fixed on the idle pulley engagement of high gear with the band external tooth of band external tooth on the high speed line shaft, the transition of idle pulley by the band external tooth, idle pulley meshes with the left intermediate gear of band external tooth and the right intermediate gear of band external tooth respectively, power deceleration shunting is passed on left middling speed axle and the right middling speed axle, shunting simultaneously decelerates to the outside low speed internal gear A of center pore area internal tooth, on the outside low speed internal gear B of center pore area internal tooth and the middle low speed internal gear of center pore area internal tooth, at last power is synthesized on the low speed gear of band external tooth, from lower velocity shaft output, and be delivered on the work mechanism.
In left middling speed shaft assembly, A2 eccentric bushing, B2 eccentric bushing and C2 eccentric bushing are fixed on the left middling speed axle, be in series at interval along direction of axis line, on left middling speed axle, the cylindrical of A2 eccentric bushing and B2 eccentric bushing and endoporus shaft axis coincide, serves as with reference to becoming 180 ° of layouts with the shaft axis of C2 eccentric bushing cylindrical with the shaft axis of left middling speed axle, and three center lines are parallel to each other, and in a plane; In right middling speed shaft assembly, A1 eccentric bushing, B1 eccentric bushing and C1 eccentric bushing are fixed on the right middling speed axle, be in series at interval along direction of axis line, on right middling speed axle, the cylindrical of A1 eccentric bushing, B1 eccentric bushing and the shaft axis of endoporus coincide, serves as with reference to becoming 180 ° of layouts with the cylindrical shaft axis of C1 eccentric bushing with the shaft axis of right middling speed axle, and three center lines are parallel to each other, and in a plane.
The low speed gear of band external tooth, adopt the key ways of connecting to be fixed on the lower velocity shaft, the outside low speed internal gear A of the outside low speed internal gear B of center pore area internal tooth and center pore area internal tooth is assemblied in the middle low speed internal gear of center pore area internal tooth middle along left middling speed axle and right middling speed axle direction of axis line evenly; A left side middling speed axle and right middling speed axle are eccentric shaft with the shaft axis of the cylindrical of A2 eccentric bushing, B2 eccentric bushing, C2 eccentric bushing and A1 eccentric bushing, B1 eccentric bushing, C1 eccentric bushing respectively, engagement by the external tooth of the internal tooth of the middle low speed internal gear of the outside low speed internal gear A of the outside low speed internal gear B of center pore area internal tooth, center pore area internal tooth and center pore area internal tooth and low speed gear drives the lower velocity shaft running, forms a chain of drive part of double-crank connecting rod internal tooth.
The endoporus of the idle pulley of band external tooth is connected with the bearing top circle transition fit, endoporus by bearing is connected with the lower velocity shaft interference fit, the high gear of band external tooth is fixed on the high speed line shaft, the low speed gear of band external tooth is fixed on the lower velocity shaft, left side middling speed axle, right middling speed axle, low speed output shaft and high speed line shaft rely on bearing to be installed in parallel on the casing respectively indirectly.
Left side middling speed axle and right middling speed axle are d-axis, be separately installed with the left intermediate gear of band external tooth and the right intermediate gear of band external tooth on left side middling speed axle and the right middling speed axle, idle pulley with the band external tooth meshes respectively, do not have the transmission of moment of torsion between idle pulley and the lower velocity shaft, the idle pulley of band external tooth meshes with the high gear of band external tooth.A left side middling speed axle and right middling speed axle are that eccentric shaft forms with left middling speed axle with the cylindrical of A2 eccentric bushing, B2 eccentric bushing, C2 eccentric bushing and A1 eccentric bushing, B1 eccentric bushing, C1 eccentric bushing respectively is that of center has the left middling speed shaft assembly of three center lines and is the right middling speed shaft assembly (these two assemblies also can directly be made an integral shaft respectively, also can replace eccentric bushing with capacity eccentric bearing) that three center lines are arranged at center with right middling speed axle.
Power is imported from the high speed line shaft, high gear and the idle pulley engagement of being with external tooth through the band external tooth, idle pulley meshes with the right intermediate gear that is installed in the left intermediate gear on the left middling speed shaft assembly and be installed on the right middling speed shaft assembly respectively, power dividing is decelerated on left middling speed shaft assembly and the right middling speed shaft assembly, realize shunting and slow down from a high speed to middling speed, left side middling speed shaft assembly and the run-in synchronism in the same way of right middling speed shaft assembly, dependence is installed in the A2 eccentric bushing on the left middling speed shaft assembly, the B2 eccentric bushing, C2 eccentric bushing and the A1 eccentric bushing that is installed on the right middling speed shaft assembly, the B1 eccentric bushing, the C1 eccentric bushing is in the same way under the run-in synchronism, the outside low speed internal gear A of drive center pore area internal tooth, the outside low speed internal gear B of center pore area internal tooth and the middle low speed internal gear of center pore area internal tooth are done plane motion, make their internal tooth and the external tooth of low speed external gear do fewer differential teeth planetary gear motion (internal tooth is than the external tooth 1-3 of manying tooth), make the lower velocity shaft continuously and smoothly ground that low speed gear is installed produce rotation, at last power is synthesized to lower velocity shaft and is delivered on the work mechanism output of realization low speed high torque.
The invention has the beneficial effects as follows that carrying and overload capacity are strong, compact structure, volume is less, in light weight, velocity ratio is big, efficient is high, and the part kind is few, and part does not have special material and processing method just can be made, and applicability is wide.
Below in conjunction with Figure of description the present invention is described in detail.
Description of drawings
Accompanying drawing 1: the cross-sectional plan view of gear interlinking speed reducer inventive embodiments
Accompanying drawing 2: be a sectional view along direction shown in the A-A line arrow among Fig. 1
Accompanying drawing 3: be left middling speed shaft assembly structural drawing
Accompanying drawing 4: the left view that is accompanying drawing 3
Accompanying drawing 5: be right middling speed shaft assembly structural drawing
Accompanying drawing 6: the left view that is accompanying drawing 5
Accompanying drawing 7: be gear interlinking speed reducer motion simulation figure (about two break points)
Accompanying drawing 8: the motion simulation figure (at two break points up and down) that is gear interlinking speed reducer
In the accompanying drawing: 1-left side intermediate gear, 2-left side middling speed axle, 3-idle pulley, 4-high speed line shaft, the right intermediate gear of 5-, the right middling speed axle of 6-, 7-casing, 8-A1 eccentric bushing, the 9-C1 eccentric bushing, 10-B1 eccentric bushing, 11-low speed gear, 12-lower velocity shaft, the 13-C2 eccentric bushing, 14-A2 eccentric bushing, 15-B2 eccentric bushing, 16-outside low speed internal gear B, low speed internal gear in the middle of the 17-, 18-outside low speed internal gear A, 19-case lid, the 20-high gear, 21-left side middling speed shaft assembly, the right middling speed shaft assembly of 22-.
Embodiment
Shown in Figure of description 1 and the accompanying drawing 2: on casing 7, the high gear 20 of band external tooth is fixed on the high speed line shaft 4, power is from 4 inputs of high speed line shaft, rely on the engagement of high gear 20 with the idle pulley 3 of band external tooth of band external tooth, power delivery is given the idle pulley 3 of band external tooth, idle pulley 3 installing and locating are on lower velocity shaft 12, there is not the transmission of force and work rate between idle pulley 3 and the lower velocity shaft 12, be assemblied on the lower velocity shaft 12, the idle pulley 3 that has external tooth meshes with the right intermediate gear 5 that is fixed on the left intermediate gear 1 on the left middling speed shaft assembly 21 and be fixed on the right middling speed shaft assembly 22 respectively, form common cylinder gear shunting deceleration part, power dividing is slowed down to pass on left middling speed shaft assembly 21 and the right middling speed shaft assembly 22; Under the synchronous drive in the same way of left middling speed shaft assembly 21 and right middling speed shaft assembly 22, drive the outside low speed internal gear A18 of center pore area internal tooth and the low speed internal gear B16 of center pore area internal tooth and the middle low speed internal gear 17 of center pore area internal tooth and do plane motion, the middle low speed internal gear 17 of the outside low speed internal gear A18 of center pore area internal tooth and the outside low speed internal gear B16 of center pore area internal tooth and center pore area internal tooth is done double-crank connecting rod fewer differential teeth planetary gear motion with the low speed gear 11 of band external tooth, and power is transferred to work mechanism by low speed gear 11 and lower velocity shaft 12.
In the left middling speed shaft assembly 21 shown in Figure of description 3 and the Figure of description 4, A2 eccentric bushing 14, B2 eccentric bushing 15 and C2 eccentric bushing 13 are fixed on the left middling speed axle 2, be in series at interval along direction of axis line, formation is that of axle has the crankshaft group of three center lines (also can directly this assembly be made an integral shaft with left middling speed axle 2, promptly A2 eccentric bushing 14, B2 eccentric bushing 15 and C2 eccentric bushing 13 and left middling speed axle 2 are made an integral shaft, also can replace A2 eccentric bushing 14, B2 eccentric bushing 15 and C2 eccentric bushing 13) with capacity eccentric bearing; In left middling speed shaft assembly 21, A2 eccentric bushing 14 and B2 eccentric bushing 15 cylindrical shaft axiss coincide, and serve as with reference to becoming 180 ° of layouts with the cylindrical shaft axis of C2 eccentric bushing 13 with the shaft axis of left middling speed axle 2, and three center lines are parallel to each other, and in a plane; In left middling speed shaft assembly 21, A2 eccentric bushing 14, B2 eccentric bushing 15 and C2 eccentric bushing 13 adopt the mode of key connecting to be fixed on the left middling speed axle 2.
In the right middling speed shaft assembly 22 shown in Figure of description 5 and the Figure of description 6, A1 eccentric bushing 8, B1 eccentric bushing 10 and C1 eccentric bushing 9 are fixed on the right middling speed axle 6, be in series at interval along direction of axis line, formation is that of axle has the crankshaft group of three center lines (also can directly this assembly be made an integral shaft with right middling speed axle 6, promptly A1 eccentric bushing 8, B1 eccentric bushing 10 and C1 eccentric bushing 9 and right middling speed axle 6 are made an integral shaft, also can replace A1 eccentric bushing 8, B1 eccentric bushing 10 and C1 eccentric bushing 9) with capacity eccentric bearing; On right middling speed shaft assembly 22, the cylindrical shaft axis of A1 eccentric bushing 8, B1 eccentric bushing 10 coincides, and serves as with reference to becoming 180 ° of layouts with the cylindrical shaft axis of C1 eccentric bushing 9 with the shaft axis of right middling speed axle 6, and three center lines are parallel to each other, and in a plane; In right middling speed shaft assembly 22, A1 eccentric bushing 8, B1 eccentric bushing 10, C1 eccentric bushing 9 also adopt the mode of key connecting to be fixed on the right middling speed axle 6.
Shown in Figure of description 7 and the Figure of description 8, the outside low speed internal gear B16 movement locus of the outside low speed internal gear A18 of center pore area internal tooth and center pore area internal tooth is consistent, arrive limit on the left point or limit on the right-right-hand limit point simultaneously, the middle low speed internal gear 17 of center pore area internal tooth reaches limit on the right-right-hand limit point or limit on the left point simultaneously; The outside low speed internal gear B16 movement locus of the outside low speed internal gear A18 of center pore area internal tooth and center pore area internal tooth is to arrive limes superiors point or limit inferior point simultaneously, and low speed internal gear 17 reaches limit inferior point or limes superiors point in the middle of the pore area internal tooth of center simultaneously.
Shown in Figure of description 1 and the Figure of description 2: the two ends of high speed line shaft 4, left middling speed shaft assembly 21, lower velocity shaft 12 and right middling speed shaft assembly 22 rely on bearing to be installed in indirectly on the casing 7; The endoporus of middle low speed internal gear 17 1 ends of center pore area internal tooth relies on bearing to be connected with left middling speed shaft assembly 21 and locatees, and the endoporus of middle low speed internal gear 17 the other ends of center pore area internal tooth relies on bearing to be connected with right middling speed shaft assembly 22 and locatees; The endoporus of outside low speed internal gear A18 one end of center pore area internal tooth relies on bearing to be connected with left middling speed shaft assembly 21 and locatees, and the endoporus of the outside low speed internal gear A18 the other end of center pore area internal tooth relies on bearing to be connected with right middling speed shaft assembly 22 and locatees; The endoporus of outside low speed internal gear B16 one end of center pore area internal tooth relies on bearing to be connected with left middling speed shaft assembly 21 and locatees, and the endoporus of the outside low speed internal gear B16 the other end of center pore area internal tooth relies on bearing to be connected with right middling speed shaft assembly 22 and locatees; Idle pulley 3 relies on Bearing Installation to be positioned on the lower velocity shaft 12, can not carry-over moment between idle pulley 3 and the lower velocity shaft 12, and the mode of low speed gear 11 employing key connecting is fixed on the lower velocity shaft 12.
After assembling was finished, the cylindrical center line of A2 eccentric bushing 14 was all equal to the distance between center line of the cylindrical of C1 eccentric bushing 9 to the distance between center line and the C2 eccentric bushing 13 cylindrical center lines of the cylindrical of B1 eccentric bushing 10 to distance between center line, the B2 eccentric bushing 15 cylindrical center lines of the cylindrical of A1 eccentric bushing 8.
The gear interlinking speed reducer gear meshing is the engagement of the external tooth of the external tooth of high gear 20 and idle pulley 3, the external tooth of idle pulley 3 respectively with the engagement of left intermediate gear 1 and right intermediate gear 5 external tooths, be fixed on the external tooth of the low speed gear 11 on the lower velocity shaft 12 and the center hole internal tooth on the low speed internal gear A18 of the outside, the center hole internal tooth on the low speed internal gear B16 of the outside and the center hole internal tooth on the middle low speed internal gear 17 and do the fewer differential teeth planetary engagement.
The working procedure of this gear interlinking speed reducer: power source is from 4 inputs of high speed line shaft, engagement through the external tooth that is fixed on external tooth on the high gear 20 on the high speed line shaft 4 and idle pulley 3, transmission of power is given the idle pulley 3 of band external tooth, idle pulley 3 is shunted power to both sides, give left intermediate gear 1 and right intermediate gear 5 with transmission of power respectively, and facilitate left intermediate gear 1 consistent with the sense of rotation of right intermediate gear 5, the A2 eccentric bushing 14 that left side intermediate gear 1 drives on the left middling speed shaft assembly 21, B2 eccentric bushing 15 and C2 eccentric bushing 13 are around the shaft axis rotation of left middling speed axle 2, right intermediate gear 5 also drives the A1 eccentric bushing 8 on the right middling speed shaft assembly 22 in the same way synchronously simultaneously, B1 eccentric bushing 10 and C1 eccentric bushing 9 are around the shaft axis rotation of right middling speed axle 6, idle pulley 3 is synthesized to outside low speed internal gear A18 to the power of both sides shunting, on outside low speed internal gear B16 and the middle low speed internal gear 17, outside low speed internal gear A18, outside low speed internal gear B16 and middle low speed internal gear 17, under the power drive of left middling speed shaft assembly 21 and right middling speed shaft assembly 22, with A1 eccentric bushing 8, B1 eccentric bushing 10, C1 eccentric bushing 9, A2 eccentric bushing 14, the center line of B2 eccentric bushing 15 and C2 eccentric bushing 13 cylindricals is that crank forms drag link, does regular plane motion together; The center hole internal tooth is done the fewer differential teeth planetary gear motion with the external tooth that is fixed on the low speed gear 11 on the lower velocity shaft 12 respectively on outside low speed internal gear A18, outside low speed internal gear B16 and the middle low speed internal gear 17, power is synthesized on low speed gear 11 and the lower velocity shaft 12 the most at last, the power of output low-speed heave-load; A left side middling speed shaft assembly 21 and right middling speed shaft assembly 22 respectively with the outside low speed internal gear A18 that connects in succession therebetween, outside low speed internal gear B16 and middle low speed internal gear 17 have formed three and have overlapped the drag link of synchronous operation in the same way, drag link is at left middling speed shaft assembly 21, under the driving of the synchronizing power in the same way of right middling speed shaft assembly 22, drive outside low speed internal gear A18, outside low speed internal gear B16 and middle low speed internal gear 17 are done regular plane motion together, at this moment, outside low speed internal gear A18, outside low speed internal gear B16 and middle low speed internal gear 17 are along with plane motion is done in the rotation of left middling speed shaft assembly 21 and right middling speed shaft assembly 22 together, make their center hole internal tooth and low speed gear 11 make fewer differential teeth planetary gear motion (internal tooth is than the external tooth 1-3 of manying tooth), drive lower velocity shaft 12 and produce rotation, because on left middling speed shaft assembly 21, A2 eccentric bushing 14 and B2 eccentric bushing 15 and C2 eccentric bushing 13 cylindrical center lines serve as with reference to becoming 180 ° of layouts with the center line of left middling speed axle 2, A1 eccentric bushing 8 on the right middling speed shaft assembly 22, B1 eccentric bushing 10 and C1 eccentric bushing 9 cylindrical center lines serve as with reference to becoming 180 ° of layouts with the center line of right middling speed axle, therefore pass through the outside low speed internal gear A18 of drag link, the motion of the lower velocity shaft 12 that outside low speed internal gear B16 and middle low speed internal gear 17 drive is continuous, also being at the uniform velocity, also is low-speed big simultaneously.Gear interlinking speed reducer is reasonable in design, compact structure, and reduction speed ratio is big, and output torque is big, carrying and characteristics such as overload capacity is strong, but in the extensive use what mechanical transmission.
Claims (7)
1. a gear interlinking speed reducer is made up of ordinary gear shunting deceleration part and a chain of drive part of double-crank connecting rod internal tooth, it is characterized in that: on casing (7), be fixed on high speed line shaft (4) and go up the high gear (20) of band external tooth and location and installation goes up the band external tooth at lower velocity shaft (12) idle pulley (3) engagement, idle pulley (3) meshes with the left intermediate gear (1) and the right intermediate gear (5) on the right middling speed shaft assembly (22) that are fixed on the left middling speed shaft assembly (21) respectively, the power dividing deceleration is passed to left middling speed shaft assembly (21) and right middling speed shaft assembly (22), form gear shunting deceleration part; The low speed gear (11) of band external tooth, be fixed on the lower velocity shaft (12), on left middling speed shaft assembly (21) and right middling speed shaft assembly (22), in the middle of the outside low speed internal gear A (18) of center pore area internal tooth and the outside low speed internal gear B (16) of center pore area internal tooth are assemblied in the middle low speed internal gear (17) of center pore area internal tooth indirectly, by center pore area internal tooth outside low speed internal gear A (18), the engagement of the external tooth of the internal tooth of low speed internal gear (17) and low speed gear (11) in the middle of center pore area internal tooth outside low speed internal gear B (16) and the center pore area internal tooth, drive lower velocity shaft (12) running, form a chain of drive part of double-crank connecting rod internal tooth.
2. gear interlinking speed reducer according to claim 1, it is characterized in that: in left middling speed shaft assembly (21), left side middling speed axle (2) is a d-axis, A2 eccentric bushing (14), B2 eccentric bushing (15) and C2 eccentric bushing (13) are fixed on the left middling speed axle (2), be in series at interval along direction of axis line, installing and locating is on left middling speed axle (2), the cylindrical shaft axis of A2 eccentric bushing (14) and B2 eccentric bushing (15) coincides, serves as with reference to becoming 180 ° of layouts with the cylindrical shaft axis of C2 eccentric bushing (13) with the shaft axis of left middling speed axle (2), article three, center line is parallel to each other, and in a plane.
3. gear interlinking speed reducer according to claim 2 is characterized in that: in the left middling speed shaft assembly (21), left middling speed axle (2), A2 eccentric bushing (14), B2 eccentric bushing (15) and C2 eccentric bushing (13) can be made an integral shaft.
4. gear interlinking speed reducer according to claim 2 is characterized in that: in the left middling speed shaft assembly (21), left middling speed axle (2) is a d-axis, and the available capacity eccentric bearing of A2 eccentric bushing (14), B2 eccentric bushing (15) and C2 eccentric bushing (13) replaces.
5. gear interlinking speed reducer according to claim 1, it is characterized in that: in right middling speed shaft assembly (22), right middling speed axle (6) is a d-axis, A1 eccentric bushing (8), B1 eccentric bushing (10) and C1 eccentric bushing (9) are fixed on the right middling speed axle (6), be in series at interval along direction of axis line, installing and locating is on right middling speed axle (6), A1 eccentric bushing (8), the cylindrical shaft axis of B1 eccentric bushing (10) coincides, serves as with reference to becoming 180 ° of layouts with the cylindrical shaft axis of C1 eccentric bushing (9) with the shaft axis of right middling speed axle (6), article three, center line is parallel to each other, and in a plane.
6. gear interlinking speed reducer according to claim 5 is characterized in that: in the right middling speed shaft assembly (22), right middling speed axle (6), A1 eccentric bushing (8), B1 eccentric bushing (10) and C1 eccentric bushing (9) can be made an integral shaft.
7. gear interlinking speed reducer according to claim 5 is characterized in that: in the right middling speed shaft assembly (22), right middling speed axle (6) is a d-axis, and the available capacity eccentric bearing of A1 eccentric bushing (8), B1 eccentric bushing (10) and C1 eccentric bushing (9) replaces.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN200910060479A CN101776129A (en) | 2009-01-12 | 2009-01-12 | Gear interlinking speed reducer |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN200910060479A CN101776129A (en) | 2009-01-12 | 2009-01-12 | Gear interlinking speed reducer |
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| CN101776129A true CN101776129A (en) | 2010-07-14 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN200910060479A Pending CN101776129A (en) | 2009-01-12 | 2009-01-12 | Gear interlinking speed reducer |
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Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102797797A (en) * | 2011-05-27 | 2012-11-28 | 吴小杰 | Three-ring decelerator with high bearing capacity |
| CN102797796A (en) * | 2011-05-27 | 2012-11-28 | 吴小杰 | Novel three-ring speed reducer |
| CN102996716A (en) * | 2012-10-09 | 2013-03-27 | 吴小杰 | Grease lubricated dynamic balancing involute three-ring speed reducer for bearing |
| CN103953691A (en) * | 2014-05-16 | 2014-07-30 | 袁正敏 | Cylindrical side sleeve type speed reducer |
| CN105538291A (en) * | 2015-12-21 | 2016-05-04 | 泉州丰泽鸿益建材机械有限公司 | Robot manipulator |
| CN106224449A (en) * | 2016-08-30 | 2016-12-14 | 江苏泰隆减速机股份有限公司 | The special three-ring gear reducer of steel billet roller-way |
-
2009
- 2009-01-12 CN CN200910060479A patent/CN101776129A/en active Pending
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102797797A (en) * | 2011-05-27 | 2012-11-28 | 吴小杰 | Three-ring decelerator with high bearing capacity |
| CN102797796A (en) * | 2011-05-27 | 2012-11-28 | 吴小杰 | Novel three-ring speed reducer |
| CN102797796B (en) * | 2011-05-27 | 2015-09-09 | 陈伟 | three-ring speed reducer |
| CN102996716A (en) * | 2012-10-09 | 2013-03-27 | 吴小杰 | Grease lubricated dynamic balancing involute three-ring speed reducer for bearing |
| CN103953691A (en) * | 2014-05-16 | 2014-07-30 | 袁正敏 | Cylindrical side sleeve type speed reducer |
| CN103953691B (en) * | 2014-05-16 | 2017-05-10 | 袁正敏 | Cylindrical side sleeve type speed reducer |
| CN105538291A (en) * | 2015-12-21 | 2016-05-04 | 泉州丰泽鸿益建材机械有限公司 | Robot manipulator |
| CN106224449A (en) * | 2016-08-30 | 2016-12-14 | 江苏泰隆减速机股份有限公司 | The special three-ring gear reducer of steel billet roller-way |
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Application publication date: 20100714 |