CN101806349A - Crawler-type traveling power transmission - Google Patents
Crawler-type traveling power transmission Download PDFInfo
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- CN101806349A CN101806349A CN 201010160188 CN201010160188A CN101806349A CN 101806349 A CN101806349 A CN 101806349A CN 201010160188 CN201010160188 CN 201010160188 CN 201010160188 A CN201010160188 A CN 201010160188A CN 101806349 A CN101806349 A CN 101806349A
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Abstract
The invention relates to a crawler-type traveling power transmission, which comprises an engine, a hydraulic torque converter, a hydraulic gearbox and a power-transmission output system, wherein a power output shaft of the engine is connected with an elastic connecting plate of the hydraulic torque converter; the power output shaft of the hydraulic torque converter is connected with an input assembly of the hydraulic gearbox; the output end of the hydraulic gearbox is a gear shaft; the power of the gear shaft is transmitted to a second shaft main gear and a second shaft pinion by a first shaft; a variable speed control device and a steering control device are arranged outside the second shaft main gear and the second shaft pinion; and the output shaft of the steering control device is a final-drive driving shaft. The crawler-type traveling power transmission has the advantages of automatic torque conversion, suitability for operation with large amplitude load change, rational drive structure and high drive efficiency.
Description
Technical field
The present invention relates to a kind of power-transmitting unit, particularly a kind of be used for track-laying vehicle infinite variable speed actuating unit.
Background technique
Usually, domestic is wheeled or cat all is to adopt the transmission of mechanical friction type clutch.This clutch is that its performance requirement of dry type or wet type is all very high, and requirement can be transmitted the motor all torsion torque reliably, does not produce sliding wear behind the joint; Separate and want thorough, rapid; Engage smooth-going, to reduce the impulsive load in the tractor starting-up process; The secondary part rotary inertia is little, the impulsive load during with minimizing gearbox engage a gear; Good and the handiness of heat radiation.And the mechanical type friction clutch not too is applicable to the operation that external load changes significantly, because when the resistance that runs into when vehicle driving is increasing, will constantly step on clutch, gear is dropped to low-grade state, this often causes the pause of operation, simultaneously, before the resistance area that has increased, also be difficult to starting again after the gear shift.Sometimes, if having little time to change, before excessive resistance area, be easy to cause engine misses to low-grade location.When operation at the beginning, just use low-grade location, carry out with low speed that then work efficiency can be very low.When external load ceaselessly changed significantly, transmission system was easy to generate very big vibrations and impact, and this vibrations and impact can make motor and other parts be affected, and the operating mode of motor is constantly changed, thereby influence its life-span.And the power transmission arrangment complexity of present crawler-type traveling power transmission, transmission efficiency is lower.
Summary of the invention
The objective of the invention is to problem, a kind of crawler-type traveling power transmission is provided at the existing crawler actuating unit existence described in the background technique.
Realize that technological scheme of the present invention is as follows:
A kind of crawler-type traveling power transmission, it comprises motor, fluid torque converter, hydraulic gearbox and transmission of power output system, the pto of motor is connected with the elasticity connecting plate of fluid torque converter, the pto of fluid torque converter connects the input line shaft of hydraulic gearbox, the output terminal of hydraulic gearbox is the tooth axle, the power of tooth axle is delivered to second gearwheel and second small gear by first, second gearwheel and second small gear arranged outside have gear change control device and steering control device, and the output shaft of steering control device is final transmission driving shaft.
Be provided with elasticity connecting plate, turbine, guide wheel and pump impeller in the described fluid torque converter, described pump impeller is arranged on the Pump wheel shaft, Pump wheel shaft is the power input shaft of fluid torque converter, described turbine is arranged on the turbine shaft, turbine shaft is the pto of fluid torque converter, and described guide wheel is arranged between pump impeller and the turbine.
Described first is provided with first gearwheel and first small gear, tooth axle pinion on first gearwheel and the tooth axle that is positioned at its right side, first small gear meshes with the tooth axle gearwheel that is positioned at its right side, second pinion in first gearwheel and left side, second gearwheel engagement in first small gear and left side.
Described gear change control device is speed shelves gear disks, speed shelves gear disk is fixedlyed connected with second, the lower end surface of the upper-end surface of second gearwheel and second small gear is respectively arranged with external splines, and speed shelves gear disk center is provided with the internal spline that is used for the engagement of the external splines of second gearwheel and second small gear.
Described steering control device is to be arranged at second break and brake coupling of going up the gear change control device outside, the output terminal of brake coupling is connected with final transmission driving shaft, final drive shaft is provided with output gear, output gear and the engagement of the final drive gear above the 5th, the 5th output terminal is connected with Athey wheel.
The input line shaft of described hydraulic gearbox is provided with hydraulic coupling, the hydraulic coupling both sides are respectively arranged with forward gears gear and reverse gear gear, forward gears gear and the output gear engagement of being fixed on the output shaft, big idle pulley engagement on reverse gear gear and the idler shaft, smaller idler wheel on the idler shaft and output gear engagement, the output shaft left end is provided with angular wheel, this angular wheel and the spiral bevel gear engagement that is arranged at tooth axle lower end.
Described transmission of power output system left end is connected with the back power output system, it comprises the 3rd, the 3rd gearwheel, the 3rd small gear, the 4th, duplicate gear, the 4th axial cone gear and back output bevel gear, duplicate gear is fixed on the 4th, duplicate gear comprises duplex gearwheel and duplex small gear, the right-hand member of the 3rd gearwheel and described second gearwheel engagement, the 3rd gearwheel fixedlyed connected with the 3rd, the left end of the 4th axial cone gear and the engagement of back output bevel gear are provided with free wheel device in described the 4th axial cone gear.
The present invention compares beneficial effect and is to pass through the elasticity connecting plate by engine-driving because of fluid torque converter of the present invention with existing crawler actuating unit, drive the pump impeller rotation, makes liquid stream flow into turbine at a high speed along its direction blade, and the promotion turbine rotates.Guide wheel makes torque-converters produce the bending moment effect, by turbine shaft moment of torsion is passed to hydraulic transmission gearbox input line shaft, when external load increases, the load that the input shaft assembly bears increases, the secondary speed of the fluid torque converter that is attached thereto reduces automatically, guide wheel can not be rotated by unidirectional clutch wedging, the moment of torsion that liquid stream acts on guide wheel is reacted on the turbine, and to making moment of torsion on the turbine equal the moment of torsion sum of pump impeller and guide wheel, thereby output torque is greater than input torque, produce automatic torque-changing, the turbine output torque increases thereupon, to overcome the external load that has increased, when external load reduces, secondary speed raises again automatically, increasing the speed of tractor, when the ratio of secondary speed and pump impeller rotating speed during greater than a certain value, guide wheel and overrunning clutch disengagement, freely rotate, bending moment stops; In the process of load change, the moment of torsion of the pump impeller that links to each other with motor, rotating speed can remain unchanged substantially outside, thereby guarantee that motor often approaches declared working condition, have improved the productivity and the Economy of tractor, have simplified variable speed operation.This stepless change performance of fluid torque converter makes it be specially adapted to the operation that load changes significantly.Fluid torque converter makes tractor can bring into play very big driving force when low speed, prevents engine stalling, guarantees that tractor has good starting performance, overcomes the ability and the acceleration performance of external load.Fluid torque converter uses the medium of liquid as work, the vibration and the impact of the transmission system that can absorb and decay, and prolongation part working life, minimizing is to the influence of motor.Fluid torque converter can produce great velocity ratio, and dilatory function is travelled with extremely low speed, thereby has strengthened the load performance of tractor and in cross-country ability moist, the muddy terrain.Gearbox adopts hydraulic gearbox, is provided with hydraulic coupling in the hydraulic gearbox, controls forward gears, the neutral gear of tractor and retreats between the shelves by hydraulic coupling and change.The power transmission arrangment of transmission of power output system is simple, and transmission efficiency is higher; The mode that adopts the speed shelves gear disk gear different with the diameter on second to mesh is controlled velocity ratio, and then realizes quick gear, the switching of gear and neutral position at a slow speed.The arranged outside of speed shelves gear disk has brake coupling on second, by brake coupling control final transmission driving shaft with second between be connected and disconnection, and then control the turning to of tractor, when the brake coupling that has only the top is controlled final transmission driving shaft and second disconnection, the final transmission driving shaft of top stops power output, and then tractor turns to upward; On the contrary, when the brake coupling that has only the below was controlled final transmission driving shaft and second disconnection, tractor turned to downwards; When the brake coupling of above and below was controlled final transmission driving shaft and second and all disconnected, tractor stopped power output.Described transmission of power output system left end is connected with the back power output system, the 3rd gearwheel and second gearwheel engagement on the 3rd of back power output system, duplicate gear is fixedlyed connected with the 4th, by the duplex small gear of control on the duplicate gear with the 3rd on the gearwheel engagement or the duplex gearwheel with the 3rd on pinion, control the state at a slow speed soon of back power output system; Be provided with the 4th axial cone gear the 4th lower end, be provided with free wheel device in the 4th axial cone gear, because free wheel device can only carry out unidirectional rotation, so only tractor advance or second on speed gear when being in the neutral position, back power output system can outputting power, when tractor is moveed backward, the 4th can not drive free wheel device and rotate, can only dally, therefore not have power output, make the power output system of tractor more reasonable by such setting.
Description of drawings
Fig. 1 is a power transmission schematic representation of the present invention;
Among the figure, 1 is motor, and 2 is the elasticity connecting plate, 3 is turbine, and 4 is guide wheel, and 5 is pump impeller, 6 is turbine shaft, 7, fluid torque converter, 8 is the forward gears gear, 9 is hydraulic gearbox, and 10 is hydraulic coupling, and 11 is the reverse gear gear, 12 is the input shaft assembly, and 13 is the tooth axle, and 14 is first small gear, 15 is first, and 16 is first gearwheel, and 17 is second gearwheel, 18 is second small gear, 19 is final transmission driving shaft, and 20 is final drive gear, and 21 is the 5th, 22 is Athey wheel, 23 is brake coupling, and 24 is the 3rd small gear, and 25 is the 3rd, 26 is duplicate gear, 27 is the 4th, and 28 is back output bevel gear, and 29 is the 4th axial cone gear, 30 is the 3rd gearwheel, 31 is break, and 32 is speed shelves gear disks, and 33 is second, 34 is big idle pulley, 35 is angular wheel, and 36 is spiral bevel gear, and 37 is idler shaft, 38 is smaller idler wheel, 39 is output shaft, and 40 is output gear, and 41 is tooth axle gearwheel, 42 is tooth axle small gear, 43 is the duplex gearwheel, and 44 is the duplex small gear, and 45 is free wheel device.
Embodiment
With reference to a kind of crawler-type traveling power transmission shown in the accompanying drawing 1, it comprises motor 1, fluid torque converter 7, hydraulic gearbox 9 and transmission of power output system, fluid torque converter 7 is driven by motor 1 by elasticity connecting plate 2, drive pump impeller 5 rotations, make liquid stream flow into turbine 3 at a high speed, promote turbine 3 rotations along its direction blade.The input line shaft of hydraulic gearbox 9 is provided with hydraulic coupling 10, hydraulic coupling 10 both sides are respectively arranged with forward gears gear 8 and reverse gear gear 11, forward gears gear 8 and output gear 40 engagements of being fixed on the output shaft 39, big idle pulley 34 engagements on reverse gear gear 11 and the idler shaft 37, smaller idler wheel 38 on the idler shaft 37 and output gear 40 engagements, output shaft 39 left ends are provided with angular wheel 35, this angular wheel 35 and spiral bevel gear 36 engagements that are arranged at tooth axle 13 lower ends, the output terminal of hydraulic gearbox 9 is a tooth axle 13, be fixedly connected with tooth axle gearwheel 41 and tooth axle small gear 42 on this tooth axle 13, tooth axle gearwheel 41 and first small gear, 14 engagements that are arranged on first 15 of its left side, first gearwheel, 16 engagements on tooth axle small gear 42 and first 15, second gearwheel, 17 engagements in first small gear 14 and left side, second small gear, 18 engagements in first gearwheel 16 and left side, the lower end surface of the upper-end surface of second gearwheel 17 and second small gear 18 is respectively arranged with external splines, second both sides up and down are respectively arranged with speed shelves gear disk 32, speed shelves gear disk 32 is fixedlyed connected with second 33, the center of speed shelves gear disk 32 is provided with the internal spline that is used for the engagement of the external splines of second gearwheel 17 and second small gear 18, second both sides about in the of 33 is respectively arranged with break 31 and brake coupling 23, the output terminal of brake coupling 23 is connected with final transmission driving shaft 19, final drive shaft is provided with output gear 40, output gear 40 and 20 engagements of the final drive gear above the 5th 21, the 5th 21 output terminals are connected with Athey wheel 22.Described transmission of power output system left end is connected with the back power output system, it comprises the 3rd 25, the 3rd gearwheel 30, the 3rd small gear 24, the 4th 27, duplicate gear 26, the 4th axial cone gear 29 and back output bevel gear 28, duplicate gear 26 is fixed on the 4th 27, duplicate gear 26 comprises duplex gearwheel 43 and duplex small gear 44, the right-hand member of the 3rd gearwheel 30 and 17 engagements of described second gearwheel, the 3rd gearwheel 30 fixedlyed connected with the 3rd 25, the left end of the 4th axial cone gear 29 and 28 engagements of back output bevel gear are provided with free wheel device 45 in described the 4th axial cone gear 29.
When the hydraulic coupling 10 of hydraulic gearbox 9 combines with forward gears gear 8,8 rotations of forward gears gear, drive output gear 40 rotations, because output gear 40 is fixedlyed connected with output shaft 39, therefore drive output shaft 39 rotations, and then the angular wheel 35 that drives output shaft 39 left ends rotates, angular wheel 35 and spiral bevel gear 36 engagements, so drive spiral bevel gear 36 rotations, and then drive tooth axle 13 rotations, because be fixedly connected with tooth axle gearwheel 41 and tooth axle small gear 42 on the tooth axle 13, so gearwheel and small gear be rotation and then, because gearwheel and first small gear 14 engagement, small gear and first gearwheel 16 engagement, therefore drive first small gear 14 and first gearwheel 16 rotation, because first gearwheel 16 and second small gear 18 engagement, first small gear 14 and second gearwheel 17 engagement, therefore, drive second gearwheel 17 and second small gear 18 rotation, the lower end surface of the upper-end surface of second gearwheel 17 and second small gear 18 is respectively arranged with external splines, second 33 both sides up and down are respectively arranged with speed shelves gear disk 32, speed shelves gear disk 32 is fixedlyed connected with second 33, the center of speed shelves gear disk 32 is provided with the internal spline that is used for the engagement of the external splines of second gearwheel 17 and second small gear 18, mesh by adjusting speed shelves gear disk 32 gear different with the diameter on second 33, and then realize quick gear, the switching of gear and neutral position at a slow speed, change second 33 rotating speed, second 33 two ends are provided with brake coupling 23, by second 33 of brake coupling 23 control and final being connected and disconnection of transmission driving shaft 19, and then control the turning to of tractor, when the brake coupling 23 final transmission driving shafts 19 of control that have only the top and second 33 disconnection, the final transmission driving shaft 19 of top stops power output, and then tractor turns to upward; On the contrary, when the brake coupling 23 final transmission driving shafts 19 of control that have only the below and second 33 disconnection, tractor turns to downwards; When the final transmission driving shafts 19 of brake coupling 23 control of above and below all disconnected with second 33, tractor stopped power and exports.Output gear 40 on the final transmission driving shaft 19 and final drive gear 20 engagements, final drive gear 20 is fixedlyed connected with the 5th 21, and the 5th 21 is connected with Athey wheel 22.When the hydraulic coupling 10 of hydraulic gearbox 9 combines with reverse gear gear 11,11 rotations of reverse gear gear, because 34 engagements of the big idle pulley on reverse gear gear 11 and the idler shaft 37, smaller idler wheel 38 rotates under the drive of idler shaft 37, because smaller idler wheel 38 and output gear 40 engagements, so driving output gear 40 rotates, and then the angular wheel 35 that drives output shaft 39 left ends rotates, angular wheel 35 and spiral bevel gear 36 engagements, so drive spiral bevel gear 36 rotations, and then drive 13 rotations of tooth axle, identical under the kind of drive of back and the forward mode.Because the transmission of power of transmitting from reverse gear gear 11 is to big idle pulley 34, be transferred to smaller idler wheel 38 by idler shaft 37 then, smaller idler wheel 38 is identical with big idle pulley 34 sense of rotation, be delivered to output gear 40 again, so under the sense of rotation of output gear 40 and the forward gears state is opposite, therefore can realize the reversing of tractor.Under the neutral state, hydraulic coupling 10 does not all combine with forward gear gear and reverse gear gear 11, so forward gear gear and reverse gear gear 11 all do not rotate, does not have power output.Back power output system be fixed in second gearwheel, 17 engagements on the 3rd gearwheel 30 on the 3rd 25 and second 33, with three 25 of the power transmission to the of second gearwheel 17, driving the 3rd small gear 24 rotates, be fixed in the position of the duplicate gear 26 on the 4th 27 by adjustment, can change the power output situation of back power output system, in the time of duplex small gear 44 and the 3rd gearwheel 30 engagements, be quick mode, the 3rd gearwheel 30 transmits power to the 4th 27 by the 4th small gear, the 4th axial cone gear 29 that drives the 4th 27 lower ends rotates, and then the back output bevel gear 28 that drive is engaged with is rotated, because output bevel gear 28 is fixedlyed connected with rear output shaft in the back, therefore, from the rear output shaft outputting power; In the time of duplex gearwheel 43 and the 3rd small gear 24 engagements, be slow speed mode, the 3rd small gear 24 transmits power to the 4th 27 by the 4th gearwheel, the 4th axial cone gear 29 that drives the 4th 27 lower ends rotates, and then drive back output bevel gear 28 rotations that are engaged with, from the rear output shaft outputting power; When duplicate gear 26 and the 3rd gearwheel 30 and the 3rd small gear 24 were all out of mesh, rear output shaft did not have power output.
The present invention compares beneficial effect and is to be driven by motor 1 by elasticity connecting plate 2 because of fluid torque converter 7 of the present invention with existing crawler actuating unit, drive pump impeller 5 rotations, make liquid stream flow into turbine 3 at a high speed, promote turbine 3 rotations along its direction blade.Guide wheel 4 makes torque-converters produce the bending moment effect, by turbine shaft 6 moment of torsion is passed to hydraulic transmission gearbox input line shaft, when external load increases, the load that input shaft assembly 12 bears increases, turbine 3 rotating speeds of the fluid torque converter 7 that is attached thereto reduce automatically, guide wheel 4 can not be rotated by unidirectional clutch wedging, the moment of torsion that liquid stream acts on guide wheel 4 is reacted on the turbine 3, and to making moment of torsion on the turbine 3 equal the moment of torsion sum of pump impeller 5 and guide wheel 4, thereby output torque is greater than input torque, produce automatic torque-changing, turbine 3 output torques increase thereupon, to overcome the external load that has increased, when external load reduces, turbine 3 rotating speeds raise again automatically, increasing the speed of tractor, when the ratio of turbine 3 rotating speeds and pump impeller 5 rotating speeds during greater than a certain value, guide wheel 4 and overrunning clutch disengagement, freely rotate, bending moment stops; In the process of load change, moment of torsion, the rotating speed of the pump impeller 5 that links to each other with motor 1 can remain unchanged substantially outside, thereby guarantee that motor 1 often approaches declared working condition, have improved the productivity and the Economy of tractor, have simplified variable speed operation.This stepless change performance of fluid torque converter 7 makes it be specially adapted to the operation that load changes significantly.Fluid torque converter 7 makes tractor can bring into play very big driving force when low speed, prevents that motor 1 overload is flame-out, guarantees that tractor has good starting performance, overcomes the ability and the acceleration performance of external load.Fluid torque converter 7 uses the medium of liquid as work, the vibration and the impact of the transmission system that can absorb and decay, and prolongation part working life, minimizing is to the influence of motor 1.Fluid torque converter 7 can produce great velocity ratio, and dilatory function is travelled with extremely low speed, thereby has strengthened the load performance of tractor and in cross-country ability moist, the muddy terrain.Gearbox adopts hydraulic gearbox 9, is provided with hydraulic coupling 10 in the hydraulic gearbox 9, controls forward gears, the neutral gear of tractors and retreats between the shelves by hydraulic coupling 10 and change.The power transmission arrangment of transmission of power output system is simple, and transmission efficiency is higher; The mode that adopts speed shelves gear disk 32 gear different with the diameter on second 33 to mesh is controlled velocity ratio, and then realizes quick gear, the switching of gear and neutral position at a slow speed.The arranged outside of speed shelves gear disk 32 has brake coupling 23 on second 33, by the final transmission driving shaft 19 of brake coupling 23 control with second 33 between be connected and disconnection, and then control the turning to of tractor, when the brake coupling 23 final transmission driving shafts 19 of control that have only the top and second 33 disconnection, the final transmission driving shaft 19 of top stops power output, and then tractor turns to upward; On the contrary, when the brake coupling 23 final transmission driving shafts 19 of control that have only the below and second 33 disconnection, tractor turns to downwards; When the final transmission driving shafts 19 of brake coupling 23 control of above and below all disconnected with second 33, tractor stopped power and exports.Described transmission of power output system left end is connected with the back power output system, the 3rd gearwheel 30 and second gearwheel 17 engagement on the 3rd 25 of back power output system, duplicate gear 26 is fixedlyed connected with the 4th 27, by the duplex small gear 44 of control on the duplicate gear 26 with the 3rd 25 on the gearwheel engagement or duplex gearwheel 43 with the 3rd 25 on pinion, control the state at a slow speed soon of back power output system; Be provided with the 4th axial cone gear 29 the 4th 27 lower ends, be provided with free wheel device 45 in the 4th axial cone gear 29, because free wheel device 45 can only carry out unidirectional rotation, so only tractor advance or second 33 on speed gear when being in the neutral position, back power output system can outputting power, when tractor is moveed backward, can not drive free wheel device 45 for the 4th 27 rotates, can only dally, therefore do not have power output, make the power output system of tractor more reasonable by such setting.
Claims (7)
1. crawler-type traveling power transmission, it is characterized in that: it comprises motor, fluid torque converter, hydraulic gearbox and transmission of power output system, the pto of motor is connected with the elasticity connecting plate of fluid torque converter, the pto of fluid torque converter connects the input line shaft of hydraulic gearbox, the output terminal of hydraulic gearbox is the tooth axle, the power of tooth axle is delivered to second gearwheel and second small gear by first, second gearwheel and second small gear arranged outside have gear change control device and steering control device, and the output shaft of steering control device is final transmission driving shaft.
2. crawler-type traveling power transmission according to claim 1, it is characterized in that: be provided with elasticity connecting plate, turbine, guide wheel, pump impeller and overrunning clutch in the described fluid torque converter, described pump impeller is arranged on the Pump wheel shaft, Pump wheel shaft is the power input shaft of fluid torque converter, described turbine is arranged on the turbine shaft, turbine shaft is the pto of fluid torque converter, and described guide wheel is arranged between pump impeller and the turbine.
3. crawler-type traveling power transmission according to claim 1, it is characterized in that: described first is provided with first gearwheel and first small gear, tooth axle pinion on first gearwheel and the tooth axle that is positioned at its right side, first small gear meshes with the tooth axle gearwheel that is positioned at its right side, second pinion in first gearwheel and left side, second gearwheel engagement in first small gear and left side.
4. crawler-type traveling power transmission according to claim 1, it is characterized in that: described gear change control device is speed shelves gear disks, speed shelves gear disk is fixedlyed connected with second, the lower end surface of the upper-end surface of second gearwheel and second small gear is respectively arranged with external splines, and speed shelves gear disk center is provided with the internal spline that is used for the engagement of the external splines of second gearwheel and second small gear.
5. crawler-type traveling power transmission according to claim 1, it is characterized in that: described steering control device is to be arranged at second break and brake coupling of going up the gear change control device outside, the output terminal of brake coupling is connected with final transmission driving shaft, final drive shaft is provided with output gear, output gear and the engagement of the final drive gear above the 5th, the 5th output terminal is connected with Athey wheel.
6. crawler-type traveling power transmission according to claim 1, it is characterized in that: the input line shaft of described hydraulic gearbox is provided with hydraulic coupling, the hydraulic coupling both sides are respectively arranged with forward gears gear and reverse gear gear, forward gears gear and the output gear engagement of being fixed on the output shaft, big idle pulley engagement on reverse gear gear and the idler shaft, smaller idler wheel on the idler shaft and output gear engagement, the output shaft left end is provided with angular wheel, this angular wheel and the spiral bevel gear engagement that is arranged at tooth axle lower end.
7. crawler-type traveling power transmission according to claim 1, it is characterized in that: described transmission of power output system left end is connected with the back power output system, it comprises the 3rd, the 3rd gearwheel, the 3rd small gear, the 4th, duplicate gear, the 4th axial cone gear and back output bevel gear, duplicate gear is fixed on the 4th, duplicate gear comprises duplex gearwheel and duplex small gear, the right-hand member of the 3rd gearwheel and described second gearwheel engagement, the 3rd gearwheel fixedlyed connected with the 3rd, the left end of the 4th axial cone gear and the engagement of back output bevel gear are provided with free wheel device in described the 4th axial cone gear.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010101601888A CN101806349B (en) | 2010-04-30 | 2010-04-30 | Crawler-type traveling power transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010101601888A CN101806349B (en) | 2010-04-30 | 2010-04-30 | Crawler-type traveling power transmission |
Publications (2)
| Publication Number | Publication Date |
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| CN101806349A true CN101806349A (en) | 2010-08-18 |
| CN101806349B CN101806349B (en) | 2012-01-18 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2010101601888A Active CN101806349B (en) | 2010-04-30 | 2010-04-30 | Crawler-type traveling power transmission |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103363056A (en) * | 2013-07-25 | 2013-10-23 | 巢湖华晨防爆动力机械制造有限公司 | Hydraulic stepless variable speed drive system of mine explosion-proof diesel locomotive |
| CN107240893A (en) * | 2017-08-04 | 2017-10-10 | 国网四川省电力公司广元供电公司 | A kind of cable puller suitable for out-of-flatness region |
| CN110307167A (en) * | 2019-08-19 | 2019-10-08 | 唐山瓦特合同能源管理有限公司 | The high-power resilience double drive resilience water circulating pump unit of hydraulic clutch |
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| JPH08258674A (en) * | 1991-08-22 | 1996-10-08 | Shin Nippon Hoiile Kogyo Kk | Parking brake device of self-mobile working machine |
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| JP2004224164A (en) * | 2003-01-22 | 2004-08-12 | Iseki & Co Ltd | Power vehicle |
| CN201124759Y (en) * | 2007-12-03 | 2008-10-01 | 内蒙古北方重工业集团有限公司 | Power drive for transport vehicle |
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| CN201677742U (en) * | 2010-04-30 | 2010-12-22 | 常州汉森机械有限公司 | Crawler travelling power transmission device |
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| JPH08258674A (en) * | 1991-08-22 | 1996-10-08 | Shin Nippon Hoiile Kogyo Kk | Parking brake device of self-mobile working machine |
| CN2585894Y (en) * | 2002-02-04 | 2003-11-12 | 中国人民解放军第六四四三工厂 | Power steering crawler dozer |
| JP2004224164A (en) * | 2003-01-22 | 2004-08-12 | Iseki & Co Ltd | Power vehicle |
| CN201124759Y (en) * | 2007-12-03 | 2008-10-01 | 内蒙古北方重工业集团有限公司 | Power drive for transport vehicle |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103363056A (en) * | 2013-07-25 | 2013-10-23 | 巢湖华晨防爆动力机械制造有限公司 | Hydraulic stepless variable speed drive system of mine explosion-proof diesel locomotive |
| CN107240893A (en) * | 2017-08-04 | 2017-10-10 | 国网四川省电力公司广元供电公司 | A kind of cable puller suitable for out-of-flatness region |
| CN107240893B (en) * | 2017-08-04 | 2018-09-11 | 国网四川省电力公司广元供电公司 | A kind of cable puller suitable for out-of-flatness region |
| CN110307167A (en) * | 2019-08-19 | 2019-10-08 | 唐山瓦特合同能源管理有限公司 | The high-power resilience double drive resilience water circulating pump unit of hydraulic clutch |
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| Publication number | Publication date |
|---|---|
| CN101806349B (en) | 2012-01-18 |
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Address after: 213034 No. 19 Tongjiang North Road, Chunjiang Town, Xinbei District, Changzhou City, Jiangsu Province Patentee after: Changzhou Hansen Machinery Co., Ltd. Address before: 213034 No. 19 Tongjiang North Road, Chunjiang Town, Xinbei District, Changzhou City, Jiangsu Province Patentee before: Changzhou Hansen Machinery Co., Ltd. |