CN102562962B - Multi-shaft linkage gearbox - Google Patents
Multi-shaft linkage gearbox Download PDFInfo
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- CN102562962B CN102562962B CN201010602828.6A CN201010602828A CN102562962B CN 102562962 B CN102562962 B CN 102562962B CN 201010602828 A CN201010602828 A CN 201010602828A CN 102562962 B CN102562962 B CN 102562962B
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Abstract
The invention discloses a multi-shaft linkage gearbox, which belongs to the technical field of combined tests for traction systems and aims to solve problems that combined test systems for the traction systems in the prior art are complicated, low in reliability and the like. The multi-shaft linkage gearbox comprises a box, a gear transmission component is arranged inside the box and comprises at least three transmission shafts including a first transmission shaft, a second transmission shaft and a third transmission shaft parallel to each other, transmission gear pairs are respectively arranged between the first transmission shaft and the second transmission shaft and between the first transmission shaft and the third transmission shaft, and two ends of the first transmission shaft, two ends of the second transmission shaft and two ends of the third transmission shaft extend out of the box to form six transmission ends. The multi-shaft linkage gearbox is used for one, two or four power plants to realize synchronous transmission, is particularly applicable to the combined test systems for the traction systems, wide in applicable range, simple in structure, easy to manufacture and low in cost, and substitutes for the complicated combined structure of multiple gear box systems in the prior art.
Description
Technical field
The present invention relates to trailer system combined test technology, particularly relate to a kind of Multiaxis linkage gear box.
Background technique
Along with going deep into of technology transfer, domestic " Harmony " motor train unit traction system combined test becomes particularly important, existing each different research institution domestic always faces the test requirements document that test stand is difficult to meet " Harmony " EMU when carrying out the combined test of trailer system, be mainly manifested in when " Harmony " EMU of technology transfer is tested, need to test the performance parameter of four traction motors simultaneously, be connected with the power end of four traction motors respectively by a set of traction convertor, domestic existing test stand can only meet the performance test requirement of separate unit traction motor, need when testing four traction motors simultaneously could realize test requirements document by many sleeve gears case system in combination of complexity.Usually adopt output terminal connection synchronous gear box electronic for four tractions in process of the test, to simulate the synchronous axial system in locomotive running, in addition, need to connect load to simulate the actual motion state of locomotive at synchronous gear box output terminal, load adopts generator (so being also load generator) usually, because the rotating speed of load generator is lower relative to the traction motor rotating speed of locomotive, therefore, usually between traction motor with synchronous gear box, reduction gear box is connected in simulation test, reduce the rotating speed of traction motor to adapt to the operation of load generator, load generator can be used as the load in traction motor simulation locomotive actual moving process in process of the test, can generate electricity in process of the test again.
Existing technological scheme is generally following two kinds, as shown in Figure 1 and Figure 2.
Four-axle linked experimental bench system in Fig. 1 is made up of four traction motor M1, M2, M3, M4, the first reduction gear box 11, second reduction gear box 21, the 3rd reduction gear box 31, the 4th reduction gear box 41, first synchronous gear box 12, second synchronous gear box 22, the 3rd synchronous gear box 32, the 4th synchronous gear box 42, four load generator G1, G2, G3, G4 etc.First reduction gear box 11, second reduction gear box 21, the 3rd reduction gear box 31, the 4th reduction gear box 41 correspondence are four traction motors M1, M2, M3, M4 and the torque transmitter between four load generators G1, G2, G3, G4, synchronous gear box ensure that the run-in synchronism of four traction motors at load input end, and the speed being arranged on four drive units (comprising traction motor, reduction gear box and synchronous gear box) on two bogies when being used for simulating actual locomotive operation is consistent.Adopt the experimental bench system shown in Fig. 1, first, increase the complexity of system largely.Whole system is connected by four cover reduction gear boxes, four cover synchronous gear boxes and four load generators, and the gear-box of One's name is legion must need huge lubrication system to ensure, these both increase the complexity of system undoubtedly.Secondly, the reliability of system is had a strong impact on.For system complex machinery, medium tache is many, and system reliability is low, and the probability of system malfunctions is improved greatly, also can reduce the operational efficiency of system simultaneously.Finally, the cost of experimental bench system is high, system complex, and number of devices is many, and take up room large, the resource making system use the aspect such as installation, maintenance, repair of front and back to take is many, and these all can increase the user cost of system.
Experimental bench system in Fig. 2, Fig. 3 is primarily of the first engine truck, the second engine truck, the first counter weight device 14, second counter weight device 24, first synchronous gear box 17, second synchronous gear box 27, first load generator G1, the second load generator G2, four traction motor M1, M2, M3, M4 compositions; Wherein four traction motors M1, M2, M3, M4 are connected with the first engine truck respectively by the first pair of rollers 15, second pair of rollers 25,3rd pair of rollers 35, the 4th pair of rollers 45 are connected with the second engine truck, and traction motor M1, M2, M3, M4 are connected with the first synchronous gear box 17, second synchronous gear box 27 respectively by first stud gear case 16, second stud gear case 26, the 3rd speed-change gear box 36, the 4th speed-change gear box 46; Fig. 2 technological scheme two and maximum not being both of Fig. 1 technological scheme one adopt engine truck and test stand pair of rollers to replace reduction gear box, although decrease the quantity of two synchronous gear boxes and load generator, but experimental bench system needs to be equipped with the pair of rollers coordinated with engine truck, simultaneously must custom-made locomotive traction bogie, add the complexity of Iarge-scale system, add the difficulty of system Installation and Debugging, have impact on the reliability of system to a great extent, increase the cost of experimental bench system.
Summary of the invention
The invention provides a kind of Multiaxis linkage gear box, in order to solve complex structure in prior art, reliability is low, cost is high defect, realize simplified structure, reduce Installation and Debugging difficulty, improve system reliability, reduce system maintenance cost.
The invention provides a kind of Multiaxis linkage gear box, comprise the casing that inside is provided with gear-driven assembly, described gear-driven assembly comprises at least three transmission shafts be arranged in parallel, is respectively the first transmission shaft, second driving shaft and the 3rd transmission shaft; Described first transmission shaft and second driving shaft, described first transmission shaft and and the 3rd transmission shaft between gear driving pair is set respectively; Described first transmission shaft, second driving shaft and the 3rd transmission shaft two ends are all stretched out described casing outside and are formed six driving ends.
Further, described first transmission shaft, second driving shaft and the 3rd transmission shaft are provided with a gear; The gear be arranged on described second driving shaft and the 3rd transmission shaft is shifting slide gear, and described shifting slide gear comprises at least two and coaxially arranges and the different shifting gear of the number of teeth; 4th transmission shaft is set between described first transmission shaft and second driving shaft, described first transmission shaft and the 3rd transmission shaft the 5th transmission shaft; Described 4th transmission shaft and the 5th transmission shaft are respectively arranged with at least two carrier gears correspondences to engage with shifting gear, wherein have a carrier gear all the time with the gears meshing be arranged on the first transmission shaft.
Wherein, the number of teeth of described shifting gear is all less than described carrier gear or is arranged on the number of teeth that the first transmission shaft cogs.
Particularly, described shifting gear and carrier gear are two, and described shifting gear is respectively the first shifting gear, the second shifting gear, and described carrier gear is respectively the first carrier gear, the second carrier gear; Wherein, described shifting slide gear correspondence is positioned at the first gear being located at second driving shaft and being located on the 3rd transmission shaft, and the first carrier gear all engages with the gear be located on the first transmission shaft and the first shifting gear; Described shifting slide gear correspondence is positioned at the second gear being located at second driving shaft and being located on the 3rd transmission shaft, the first carrier gear and the gears meshing, the second carrier gear and the second gear gears meshing that are located on the first transmission shaft.
Particularly, described shifting gear and carrier gear are three; Described shifting gear is respectively the first shifting gear, the second shifting gear, third gear gear, and described carrier gear is respectively the first carrier gear, the second carrier gear, the 3rd carrier gear; Wherein, described shifting slide gear correspondence is positioned at the first gear being located at second driving shaft and being located on the 3rd transmission shaft, and the first carrier gear all engages with the gear be located on the first transmission shaft and the first shifting gear; Described shifting slide gear correspondence is positioned at the second gear being located at second driving shaft and being located on the 3rd transmission shaft, and the first carrier gear all engages with the gear be located on the first transmission shaft, the second carrier gear and the second gear gears meshing; Described shifting slide gear correspondence is positioned at the third gear being located at second driving shaft and being located on the 3rd transmission shaft, the first carrier gear and the gears meshing be located on the first transmission shaft, the 3rd carrier gear and third gear gears meshing.
Wherein, have at least on one in described 3rd transmission shaft and the 4th transmission shaft and be provided with limit gear, described shifting slide gear is positioned at limit gear, and the shifting gear forming described shifting slide gear all departs from all carrier gears and engages.
Further, described 3rd transmission shaft and the 4th is spline joint between transmission shaft and shifting slide gear disposed thereon.
Multiaxis linkage gear box provided by the invention, the driving end at the first transmission shaft two ends connects load generator respectively as output terminal, second driving shaft is connected traction motor with the driving end at the 3rd transmission shaft two ends respectively as input end, second driving shaft and the 3rd transmission shaft all drive the first drive axis by gear driving pair, to realize synchronous axial system, the rotating speed of traction motor can be changed by the velocity ratio specifically arranging gear driving pair to adapt to the operation of load generator simultaneously, four traction motors in hinge structure scheme one all need by four traction motors in the kind of drive of speed-change gear box and synchronous gear box and prior art two by four test stand pairs of rollers and speed-change gear box, the kind of drive of two engine trucks and synchronous gear box, synchronous gear box and speed-change gear box are arranged to one, enormously simplify system architecture, decrease unnecessary medium tache, improve overall operation efficiency and the reliability of system, the difficulty of reduction system Installation and Debugging, manufacture cost and installation, maintenance cost.
Accompanying drawing explanation
Fig. 1 is the structural representation of this prior art one.
Fig. 2 is the structural representation of prior art two of the present invention.
Fig. 3 is the plan structure schematic diagram of Fig. 2.
Fig. 4 is the structural representation of Multiaxis linkage gear box embodiment one of the present invention.
Fig. 5 is the structural representation of Multiaxis linkage gear box embodiment two of the present invention.
Fig. 6 is the structural representation of Multiaxis linkage gear box embodiment three of the present invention.
Fig. 7 is the structural representation of Multiaxis linkage gear box embodiment four of the present invention.
Reference character:
First reduction gear box 11; Second reduction gear box 21; First balancing weight 14;
3rd reduction gear box 31; 4th reduction gear box 41; Second balancing weight 24;
First synchronous gear box 12; Second synchronous gear box 22; First pair of rollers 15;
3rd synchronous gear box 32; 4th synchronous gear box 42; Second pair of rollers 25;
First stud gear case 16; Second stud gear case 26; 3rd pair of rollers 35;
3rd speed-change gear box 36; 4th speed-change gear box 46; 4th pair of rollers 45;
First synchronous gear box 17; Second synchronous gear box 27; Casing 1;
Driving end 01; Driving end 02; Driving end 03;
Driving end 04; Driving end 001; Driving end 002;
First transmission shaft 10; Second driving shaft 20; 3rd transmission shaft 30;
4th transmission shaft 40; 5th transmission shaft 50; Gear 05;
First carrier gear 61; Second carrier gear 62; 3rd carrier gear 63;
Gear 07; First shifting gear Z1; Second shifting gear Z2;
Third gear gear Z3; First gear 71; Second gear 72;
Third gear 73; Limit gear 70.
Embodiment
For making the object of the embodiment of the present invention, technological scheme and advantage clearly, below in conjunction with the accompanying drawing in the embodiment of the present invention, technological scheme in the embodiment of the present invention is clearly and completely described, obviously, described embodiment is the present invention's part embodiment, instead of whole embodiments.Based on the embodiment in the present invention, those of ordinary skill in the art, not making the every other embodiment obtained under creative work prerequisite, belong to the scope of protection of the invention.
As the first specific embodiment of Multiaxis linkage gear box of the present invention, as shown in Figure 4, comprise casing 1, three transmission shafts are arranged with in parallel in described casing 1, be respectively the first transmission shaft 10, second driving shaft 20 and the 3rd transmission shaft 30, first transmission shaft 10 establishes gear 05, second driving shaft 20 and the 3rd transmission shaft 30 is respectively arranged with gear 07, two gears 07 all with gear 05 engagement travel two pairs of gear driving pairs.Wherein casing outside is stretched out at the first transmission shaft 10, second driving shaft 20 and the 3rd transmission shaft 30 two ends respectively, forms driving end 001, driving end 002, driving end 01, driving end 02, driving end 03, driving end 04.
As the second specific embodiment, as shown in Figure 5, the first transmission shaft 10 is established two gears 05, second driving shaft 20, the 3rd transmission shaft 30 all establish gear 07, two gears 07 correspondences and two gear 05 engagement travel, two pairs of gear driving pairs.
In above-mentioned first specific embodiment and the second specific embodiment, driving end 001 is the first output terminal 001, driving end 002 is that the second output terminal 002 connects load generator G1, load generator G2 respectively, and driving end 01 is first input end 01, driving end 02 is the second input end 02, driving end 03 is the 3rd input end 03, driving end 04 is that four-input terminal 04 correspondence connects traction motor M1, traction motor M2, traction motor M3, traction motor M4; Wherein, due to the first transmission shaft engaging respectively as second driving shaft and the common output shaft of the 3rd transmission shaft by gear 05 and gear 07, synchronous axial system is achieved; First transmission shaft is equal with the velocity ratio between the first transmission shaft with the 3rd transmission shaft with the velocity ratio between second driving shaft, is gear 05 and the gear ratio of driven gear 07, achieves the speed change in synchronous axial system situation; Because the first driving end 01, second driving end 02 is wholely set with second driving shaft 20,3rd driving end 03, the 4th driving end 04 and the 3rd transmission shaft 30 are wholely set, and then realize the first driving end 01, second driving end 02, the 3rd driving end 03 and the 4th driving end 04 synchronous axial system i.e. synchronous axial system of four traction motors, identical with synchronous gear box effect; The number of teeth opposed gear 05 of gear 07 is less, can realize slowing down, and is equal to reduction gear box effect; According to the rotating speed of the traction motor of test, suitable velocity ratio can be set to adapt to the test under friction speed in addition, compare with existing technological scheme, synchronous gear box and speed-change gear box are set to integrative-structure, realize four-axle linked, decrease the quantity of same gear-box and speed-change gear box, simplify Installation and Debugging flow process.
As the 3rd specific embodiment of the present invention, as shown in Figure 6, described two gears 07 are shifting slide gear, two shifting slide gears and be spline joint between second driving shaft and the 3rd transmission shaft, described shifting slide gear comprises two numbers of teeth shifting gear different from each other, is respectively the first shifting gear Z1 and the second shifting gear Z2, described second driving shaft 20 and the 3rd transmission shaft 30 are respectively equipped with limit gear 70, first gear 71 and the second gear 72, first transmission shaft 10 and second driving shaft 20 establish the 4th transmission shaft 40, the 5th transmission shaft 50 is established between first transmission shaft 10 and the 3rd transmission shaft 30, on described 4th transmission shaft 40 and the 5th transmission shaft 50, corresponding first gear 71 position is provided with the first carrier gear 61, the second carrier gear 62 is established in corresponding second gear 72 position, shifting slide gear is positioned at the first gear 71, described first carrier gear 61 being positioned at the first gear 71 engages formation first group of velocity ratio with the gear 05 be located on the first transmission shaft and the first shifting gear Z1 simultaneously, shifting slide gear is positioned at the second gear 72, first carrier gear 61 and engages with the gear 05 be located on the first transmission shaft, and the second carrier gear 62 engages formation second group of velocity ratio with the second shifting gear Z2, shifting slide gear is positioned at limit gear 70, first shifting gear Z1 and the second shifting gear Z2 and departs from the first carrier gear 61 and the second carrier gear 62 respectively and engage.
Above-mentioned structure, because the rotating speed of shifting slide gear is consistent with the rotating speed of traction motor to be measured, usually at more than 7000r/min or higher, the setting of carrier gear avoids shifting gear and engages with the direct of the gear be located on the first transmission shaft, reduce machining accuracy installation requirement, meanwhile, being arranged so that the adjustment of shifting slide gear between the first gear and second becomes and more accurately facilitating of carrier gear.
Shifting slide gear on wherein second driving shaft 20 is allocated to limit position 70, each shifting gear of this shifting slide gear of formation is all departed from each carrier gear engage, like this, connect corresponding with the driving end at the 3rd transmission shaft 30 two ends respectively for two traction motors, the driving end at the first transmission shaft 10 two ends connects load generator, the test of two traction motors can also be used for, be applicable to the pilot system that single cover traction convertor is connected with the power end of two traction motors; In addition, if the rotating speed of the rotating speed relative load generator of the traction motor of test is lower, traction motor correspondence can be connected to the driving end at the first transmission shaft 10 two ends, load generator be connected to the driving end at the 3rd transmission shaft 30 two ends; Shifting slide gear on 3rd transmission shaft 30 is also allocated to limit position 70, and like this, two shifting slide gears all depart from carrier gear and engage; Traction motor connects the driving end of the first transmission shaft 10 wherein one end, and load generator connects the driving end of first transmission shaft 10 the other end.Adopt multi-gear transmitting assemblies, in the Traction Drive mode of satisfied different rail motor set, the practicability of strengthen test system.
As the 4th specific embodiment of the present invention, as shown in Figure 7, shifting slide gear comprises coaxial setting and the number of teeth the first shifting gear Z1, the second shifting gear Z2, third gear gear Z3 different from each other, and second driving shaft 20 and the 3rd transmission shaft 30 arrange limit gear 70, first gear 71, second gear 72, third gear 73 respectively; On 4th transmission shaft 40 and the 5th transmission shaft 50, corresponding first gear 71, second gear 72, third gear 73 establish the first carrier gear 61, second axle gear 62, the 3rd to cross 63 successively; Wherein, described shifting slide gear is positioned at the first gear 71, first carrier gear 61 and engages formation first group of velocity ratio with the gear 05 be located on the first transmission shaft and the first shifting gear Z1; Shifting slide gear is positioned at the second gear 72, first carrier gear and engages with the gear 05 be located on the first transmission shaft, and the second carrier gear 62 engages formation second group of velocity ratio with the second shifting gear Z2; Shifting slide gear is positioned at third gear 73, and the first carrier gear 61 engages with the gear 05 be located on the first transmission shaft, the 3rd carrier gear 63 with engage formation the 3rd group of velocity ratio.Described shifting slide gear is positioned at limit gear 70, first shifting gear Z1, the second shifting gear Z2 and third gear gear Z3 and departs from the first carrier gear 61, second carrier gear 62 and the 3rd carrier gear 63 respectively and engage.
Above-mentioned structure, four traction electric machines are arranged on driving end 01, driving end 02, driving end 03 and driving end 04, two load generators are arranged on driving end 001 and driving end 002, the transmitted power of gear-box is 4MW, can meet separate unit power in 1MW and following, the rotating speed test demand at the traction electric machine of below 7000rpm.Consider that different traction electric machines exists larger rotating speed difference, the velocity ratio selecting many gears to mate when design gear case (also can be set to the corresponding four groups of velocity ratios of fourth gear or the corresponding five groups of velocity ratios of five gears, do not limit at this), by shifting slide gear at the first gear, sliding between the second gear and third gear to change the velocity ratio of gear-box easily, run with the traction motor adapting to different rotating speeds.By to various experimental bench system project plan comparison in the past, the embodiment of the present invention eliminates in the past loaded down with trivial details medium tache, greatly reduce the factor of the system reliability difference that mechanical equipment installation too much causes, reduce the difficulty of system Installation and Debugging, utilize the machinery of simplifying to complete test objective.Adopt the technical program, the synchronous high-speed test of four traction electric machines can be realized, improve the reliability of experimental bench system to a great extent, reduce test stand cost.
Adopt the structure of this invention can realize four axle synchronous operations of gearbox high-speed end, reach four-axle linked object.Adopt that the gear box structure of the technical program can realize the running up of system, many gears velocity ratio is selected, meet the test needs of 7000rpm and following rotating speed, below 4MW power.
Last it is noted that above embodiment is only in order to illustrate technological scheme of the present invention, be not intended to limit; Although with reference to previous embodiment to invention has been detailed description, those of ordinary skill in the art is to be understood that: it still can be modified to the technological scheme described in foregoing embodiments, or carries out equivalent replacement to wherein portion of techniques feature; And these amendments or replacement, do not make the essence of appropriate technical solution depart from the spirit and scope of various embodiments of the present invention technological scheme.
Claims (4)
1. a Multiaxis linkage gear box, is characterized in that, comprises the casing that inside is provided with gear-driven assembly, and described gear-driven assembly comprises at least three transmission shafts be arranged in parallel, is respectively the first transmission shaft, second driving shaft and the 3rd transmission shaft; Described first transmission shaft and second driving shaft, between described first transmission shaft and the 3rd transmission shaft, gear driving pair is set respectively; Described first transmission shaft, second driving shaft and the 3rd transmission shaft two ends are all stretched out described casing outside and are formed six driving ends;
Described first transmission shaft, second driving shaft and the 3rd transmission shaft are provided with a gear; The gear be arranged on described second driving shaft and the 3rd transmission shaft is shifting slide gear, and described shifting slide gear comprises at least two and coaxially arranges and the different shifting gear of the number of teeth; Establish the 4th transmission shaft between described first transmission shaft and second driving shaft, described first transmission shaft and the 3rd transmission shaft establish the 5th transmission shaft; Described 4th transmission shaft and the 5th transmission shaft are respectively provided to few two carrier gears correspondence to engage with described shifting gear, wherein have a described carrier gear all the time with the gears meshing be located on the first transmission shaft;
Described shifting gear and carrier gear are two, and described shifting gear is respectively the first shifting gear, the second shifting gear, and described carrier gear is respectively the first carrier gear, the second carrier gear; Wherein, described shifting slide gear correspondence is positioned at the first gear being located at second driving shaft and being located on the 3rd transmission shaft, and the first carrier gear all engages with the gear be located on the first transmission shaft and the first shifting gear; Described shifting slide gear correspondence is positioned at the second gear being located at second driving shaft and being located on the 3rd transmission shaft, the first carrier gear and the gears meshing be located on the first transmission shaft, the second carrier gear and the second gear gears meshing;
Or described shifting gear and carrier gear are three; Described shifting gear is respectively the first shifting gear, the second shifting gear, third gear gear, and described carrier gear is respectively the first carrier gear, the second carrier gear, the 3rd carrier gear; Wherein, described shifting slide gear correspondence is positioned at the first gear being located at second driving shaft and being located on the 3rd transmission shaft, and the first carrier gear all engages with the gear be located on the first transmission shaft and the first shifting gear; Described shifting slide gear correspondence is positioned at the second gear being located at second driving shaft and being located on the 3rd transmission shaft, and the first carrier gear all engages with the gear be located on the first transmission shaft, the second carrier gear and the second gear gears meshing; Described shifting slide gear correspondence is positioned at the third gear being located at second driving shaft and being located on the 3rd transmission shaft, the first carrier gear and the gears meshing be located on the first transmission shaft, the 3rd carrier gear and third gear gears meshing.
2. Multiaxis linkage gear box according to claim 1, is characterized in that, the number of teeth of described shifting gear is less than the number of teeth of described carrier gear.
3. according to the arbitrary described Multiaxis linkage gear box of claim 1-2, it is characterized in that, have at least on one in described 3rd transmission shaft and the 4th transmission shaft and be provided with limit gear, described shifting slide gear is positioned at limit gear, and the shifting gear forming described shifting slide gear all departs from all carrier gears and engages.
4. Multiaxis linkage gear box according to claim 3, is characterized in that, described 3rd transmission shaft and the 4th is spline joint between transmission shaft and shifting slide gear disposed thereon.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201010602828.6A CN102562962B (en) | 2010-12-20 | 2010-12-20 | Multi-shaft linkage gearbox |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201010602828.6A CN102562962B (en) | 2010-12-20 | 2010-12-20 | Multi-shaft linkage gearbox |
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| Publication Number | Publication Date |
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| CN102562962A CN102562962A (en) | 2012-07-11 |
| CN102562962B true CN102562962B (en) | 2015-04-29 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201010602828.6A Active CN102562962B (en) | 2010-12-20 | 2010-12-20 | Multi-shaft linkage gearbox |
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Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN113606318A (en) * | 2021-07-01 | 2021-11-05 | 王信辉 | Homodromous high moment of torsion gear box |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2080588U (en) * | 1989-11-03 | 1991-07-10 | 王德发 | High gear ratio cylindrical gear speed reduction unit |
| CN2799978Y (en) * | 2005-06-02 | 2006-07-26 | 杭州依维柯汽车变速器有限公司 | Transmission with double output shafts |
| FR2901003A1 (en) * | 2006-05-10 | 2007-11-16 | Peugeot Citroen Automobiles Sa | Gear motor for e.g. motor vehicle`s seat, has clutches establishing/breaking transmission of power to associated axles, where one of axles is used as input axle to transmit power to shaft for converting mechanical energy into another energy |
| CN201884573U (en) * | 2010-12-20 | 2011-06-29 | 永济新时速电机电器有限责任公司 | Multiaxis linkage gear box |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2928192B1 (en) * | 2008-02-28 | 2010-03-19 | Eurocopter France | POWER TRANSMISSION BOX HAVING AN ALTERNATIVE ROTATION SPEED AND CORRESPONDING METHOD OF OPERATION |
-
2010
- 2010-12-20 CN CN201010602828.6A patent/CN102562962B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2080588U (en) * | 1989-11-03 | 1991-07-10 | 王德发 | High gear ratio cylindrical gear speed reduction unit |
| CN2799978Y (en) * | 2005-06-02 | 2006-07-26 | 杭州依维柯汽车变速器有限公司 | Transmission with double output shafts |
| FR2901003A1 (en) * | 2006-05-10 | 2007-11-16 | Peugeot Citroen Automobiles Sa | Gear motor for e.g. motor vehicle`s seat, has clutches establishing/breaking transmission of power to associated axles, where one of axles is used as input axle to transmit power to shaft for converting mechanical energy into another energy |
| CN201884573U (en) * | 2010-12-20 | 2011-06-29 | 永济新时速电机电器有限责任公司 | Multiaxis linkage gear box |
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Address after: 044502 Yongji City, Shanxi Province, the city of motor street, No. 18, No. Patentee after: CRRC YONGJI ELECTRIC CO., LTD. Address before: 044502 No. 18 motor street, Shanxi, Yongji Patentee before: Yongji Xinshisu Motor Electrical Appliance Co., Ltd. |
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