CN102146987A - Power shift speed changing box for matching engineering machine - Google Patents
Power shift speed changing box for matching engineering machine Download PDFInfo
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- CN102146987A CN102146987A CN2011100232753A CN201110023275A CN102146987A CN 102146987 A CN102146987 A CN 102146987A CN 2011100232753 A CN2011100232753 A CN 2011100232753A CN 201110023275 A CN201110023275 A CN 201110023275A CN 102146987 A CN102146987 A CN 102146987A
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- 230000001050 lubricating effect Effects 0.000 claims description 4
- 238000000034 method Methods 0.000 abstract description 3
- 238000005265 energy consumption Methods 0.000 description 3
- 230000003139 buffering effect Effects 0.000 description 2
- 230000008878 coupling Effects 0.000 description 2
- 238000010168 coupling process Methods 0.000 description 2
- 238000005859 coupling reaction Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- 238000005461 lubrication Methods 0.000 description 2
- 230000006978 adaptation Effects 0.000 description 1
- 210000004712 air sac Anatomy 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000004134 energy conservation Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
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Abstract
The invention relates to a power shift speed changing box for matching an engineering machine, wherein a box body (8) is provided with a low-pressure gear pump (30) which is linked with a driving shaft; the low-pressure gear pump (30) is connected with an overflow valve (29); the overflow port of the overflow valve (29) is respectively connected with six clutches through an oil pipe; the overflow valve (29) is externally connected with an energy valve through a throttle valve; and the overflow valve (29) is also connected with an electric magnetic valve for controlling the clutch. The set speed of each gear reaches an ideal state, and the working efficiency is higher; the transmission efficiency is more than 90% in high-speed running, the transmission efficiency reaches more than 95% in the process of low-speed shovelling; compared with the existing loading machine matching with a motor with equivalent power, the spading force is doubled; and normally the power of the power shift speed changing box is 30%-40% less than the power of the matched motor for the loading machine, the shovel force is 10%-15% greater than that of the speed changing box, and oil is saved by 30%-40%.
Description
Technical field the present invention relates to a kind of hydraulic power manual transmission.
The following shortcoming of the existing hydraulic power manual transmission of background technique ubiquity: the first, because adopt fluid torque converter to cooperate the power gear shifting gear shift mode, so transmission efficiency is low, and energy consumption is higher.And be easy to generate high temperature, cause gearbox not work, need preheating under the low temperature, influence working efficiency.The cost height.The second,, cause one grade of power shortcoming and high-grade forward velocity is not enough because transmission design is unreasonable.Three, generally adopt manual draw bar to handle gearshift, install, operate inconvenience.Four, pneumatic jack oil braking booster is generally adopted in brake, has cost, the too high shortcoming of energy consumption.Five, for the small sized loader below a ton, because transmission efficiency is lower, energy consumption is higher relatively, adopts prior art can't realize the hydraulic power gearshift.
Summary of the invention technical problem to be solved by this invention is, a kind of engineering machine adapted Powershift transmission is provided, first, by solenoid directional control valve control gearshift, and fitting operation is more convenient, and eliminates shift impact, reaches the purpose of steady crash change of speed.The second, realize the output of two cover speed, and low first gear speed is lower, power is more sufficient, and high third speed is higher, thereby adapts to the various operating modes of engineering machine better, and more energy-conservation.Three, push up oily mode by oil and brake, to cut down the consumption of energy.Four, realize overload protection.
It is as follows that the present invention solves the problems of the technologies described above the technological scheme that is adopted:
A kind of engineering machine adapted Powershift transmission comprises casing, the I axle that is arranged in parallel, II axle, III axle, IV axle, V axle, VI axle and VII axle respectively by Bearing Installation in casing, wherein the I axle is an input shaft, the VII axle is an output shaft, it is characterized in that:
The I axle is connected with II shaft drive; The Z5 gear also is installed on the II axle;
Be separately installed with III shaft clutch, IV shaft clutch, V shaft clutch and VI shaft clutch on III axle, IV axle, V axle and the VI axle, the Z7 gear is housed on the III shaft clutch, the Z6 gear is housed on the IV shaft clutch, the Z8 gear is housed on the V shaft clutch, the Z9 gear is housed on the VI shaft clutch; Also be installed with the Z10 gear on the III axle, also be installed with the Z12 gear on the IV axle, also be installed with Z13 and Z14 gear on the V axle, also be installed with Z16 gear and Z15 gear on the VI axle; The Z5 gear is meshed with Z6 gear, Z8 gear respectively, and the Z6 gear is meshed with the Z7 gear, and the Z8 gear is meshed with the Z9 gear, and the Z12 gear is meshed with the Z13 gear, and the Z14 gear is meshed with the Z15 gear;
The Z11 gear is installed on the VII axle, and the Z11 gear is meshed with the Z10 gear; Z17 gear and the oil hydraulic cylinder that is used to control Z17 gear axial position also are installed on the VII axle;
The low pressure gear pump that links with the I axle also is installed on casing, and low pressure gear pump is connected with relief valve, and the flow-off of relief valve is connected with described six clutches respectively by oil pipe; Relief valve is associated with accumulator outward by throttle valve;
Relief valve also is associated with the two-position three way pilot operated directional control valve outward by throttle valve, the two-position three way pilot operated directional control valve is connected with 3-position 4-way electromagnetic switch first valve and 3-position 4-way electromagnetic switch second valve respectively, and described 3-position 4-way electromagnetic switch first valve is connected with III shaft clutch, IV shaft clutch, V shaft clutch and the oil cylinder of VI shaft clutch respectively with 3-position 4-way electromagnetic switch second valve.
Described I axle 1 is in transmission connection with II axle 2 and is meant: left clutch and right clutch are installed on the I axle 1, the Z1 gear is housed on the left clutch, the Z3 gear is housed on the right clutch;
Z2 gear, Z4 gear also are installed on the II axle, and wherein, the Z2 gear is meshed with the Z1 gear, and the Z4 gear is meshed with the Z3 gear.
Relief valve is connected with the first throttle valve and second throttle valve respectively, and wherein, the first throttle valve is connected with first accumulator and two-position four-way solenoid directional control valve respectively, and the two-position four-way solenoid directional control valve links with described left clutch and right clutch respectively; The output terminal of second throttle valve is connected with two oil pipes, and one is connected with second accumulator, mutually bi-bit bi-pass electromagnetic switch second valve in parallel and one-way valve, the 3rd accumulator in turn, and it two is connected with the two-position three way pilot operated directional control valve.
Be provided with bi-bit bi-pass electromagnetic switch first valve between second throttle valve and second accumulator, the oil outlet tube of bi-bit bi-pass electromagnetic switch first valve is connected with the inner chamber of casing.
The output terminal of relief valve also is connected with brake control valve, and brake control valve is connected with the oil that is used for linking to each other with brake and pushes up oily booster; Wherein the 3rd throttle valve, the 4th throttle valve stepped on selector valve and the spool by the two-position three way pin of brake control valve formed; The oily booster in oil top is connected with the brake lubricating cup.
One or two gear pumps that link with the II axle can also be installed on casing.
Good effect of the present invention is:
The first, gearbox has adopted 6 hydraulic couplinges.Realized 6 forward gearss, 2 retreat shelves.Make the work of loading under the various situations of functional adaptation.The setting of each grade speed has reached perfect condition, and working efficiency is than higher.Gearbox is a mechanical transmission, and transmission efficiency is than higher.Transmission efficiency is more than 90% when walking at a high speed, and transmission efficiency reaches more than 95% during low speed shovel soil.When joining equal power engine with existing loader, spading power is twice.Existing loader adapted engine power is to dispose according to required spading power size.And loader of the present invention is to dispose according to the walking power demand.General than the little 30%-40% of existing engine power that loader is allotted.And the also big 10%-15% of spading power, fuel-economizing 30%-40%.
The second, be provided with the two-position three way pilot operated directional control valve of conduct brake unloading valve, four clutches all separate during brake.
Three, last two clutches are controlled by two four-way electromagnetic reversing valves.The working state next one has been realized the output of two cover speed in conjunction with a separation.And gear shift control is flexible, quick, light.
Four, realize buffering by two piston accumulators, solved the shift impact problem.When one of one grade, second gear, reverse clutch in conjunction with the time, accumulator is drained the oil, and fast clutch oil cylinder is full of.Clutch in conjunction with and pressure is less, transmitting torque is also less.Along with restriction gives accumulator oil-filled, clutch pressure increases, and transmitting torque increases, and the oil-filled time changes adjustable by choke area, generally be controlled at about 1 second.Three class gear shift is higher, needs buffer time longer.DT1 and DT6 connect simultaneously when changing third gear.Two accumulators are oil-filled to the oil cylinder that third gear clutch oil cylinder, output shaft and gear Z17 link simultaneously, and it is oil-filled that at this moment restriction is given two accumulators, and the time also doubles.So the buffer time of third gear is about 2 seconds, has played the effect of steady speedup.The buffering of high and low shift hydraulic coupling is with same principle.Only reduced buffer time, generally about 0.6 second.Therefore, under the situation of not feeling to impact, shorten buffer time, improved working efficiency.
Five, the design of gear of the present invention and velocity ratio is more reasonable, is fit to various operating modes.Top gear has higher speed, and bottom gear has bigger shovel power in when material shovel, can cold-starting, under the high temperature condition without radiator.Littler by 35% than engine power that same model loader is allotted, and bigger shovel power is arranged.High working efficiency 30%, fuel-economizing 30%-40%, transmission efficiency is big by 92%, and handiness is installed, and installation and maintenance cost reduce greatly.
Six, this dynamic power shift gear box can be supporting with loaders such as ZL05, ZL06, ZL08, ZL10, ZL12, ZL16, ZL20, ZL30, ZL40, ZL50, ZL60, ZL80, ZL100, ZL120.Can replace simultaneously gearbox with the supporting all devices of fluid torque converter.
Seven, the oily mode in oil top is adopted in brake, has utilized the pressure source on the gearbox, has both reduced cost, has saved power again.
Eight, by bi-bit bi-pass solenoid directional control valve DT7 is set, realized overload protection between second throttle valve and second accumulator.
Description of drawings Fig. 1 is a structural representation of the present invention.
Fig. 2 is seven distribution schematic diagrams of the present invention.
Embodiment further specifies the present invention below in conjunction with drawings and Examples.
As shown in Figure 1, 2, the present invention includes casing 8, the I axle 1 that is arranged in parallel, II axle 2, III axle 3, IV axle 4, V axle 5, VI axle 6 and VII axle 7 respectively by Bearing Installation in casing 8, wherein I axle 1 is an input shaft, is used to connect motor.VII axle 7 is an output shaft, is used to connect the bridge of engineering machine, is equipped with to pull brake 10 on VII axle 7.
I axle 1 is in transmission connection with II axle 2.Described being in transmission connection is meant: left clutch 32 and right clutch 31 are installed on the I axle 1, the Z1 gear is housed on the left clutch 32, the Z3 gear is housed on the right clutch 31; Z2 gear, Z4 gear also are installed on the II axle 2, and wherein, the Z2 gear is meshed with the Z1 gear, and the Z4 gear is meshed with the Z3 gear.The Z5 gear also is installed on the II axle 2.
Be separately installed with III shaft clutch 14, IV shaft clutch 13, V shaft clutch 12 and VI shaft clutch 11 on III axle 3, IV axle 4, V axle 5 and the VI axle 6, the Z7 gear is housed on the III shaft clutch 14, the Z6 gear is housed on the IV shaft clutch 13, the Z8 gear is housed on the V shaft clutch 12, the Z9 gear is housed on the VI shaft clutch 11; Also be installed with the Z10 gear on the III axle 3, also be installed with the Z12 gear on the IV axle 4, also be installed with Z13 and Z14 gear on the V axle 6, also be installed with Z16 gear and Z15 gear on the VI axle 6; The Z5 gear is meshed with Z6 gear, Z8 gear respectively, and the Z6 gear is meshed with the Z7 gear, and the Z8 gear is meshed with the Z9 gear, and the Z12 gear is meshed with the Z13 gear, and the Z14 gear is meshed with the Z15 gear.
The Z11 gear is installed on the VII axle 7, and the Z11 gear is meshed with the Z10 gear; Z17 gear and the oil hydraulic cylinder 9 that is used to control Z17 gear axial position also are installed on the VII axle 7.
The low pressure gear pump 30 that links with the I axle also is installed on casing 8, and low pressure gear pump 30 is connected with relief valve 29, and the flow-off of relief valve 29 is connected with described six clutches respectively by oil pipe, gives six clutch lubrications and heat radiation.
Relief valve 29 is connected with the first throttle valve 26 and second throttle valve 20 respectively, wherein, first throttle valve 26 is connected with first accumulator 24 and two-position four-way solenoid directional control valve 25 respectively, and two-position four-way solenoid directional control valve 25 links with described left clutch 32 and right clutch 31 respectively.The output terminal of second throttle valve 20 is connected with two oil pipes, one is connected with second accumulator 23 in turn, bi-bit bi-pass electromagnetic switch second valve 22 and one-way valve 21 in parallel mutually, the 3rd accumulator 18, it two is connected with two-position three way pilot operated directional control valve 17, two-position three way pilot operated directional control valve 17 is connected with 3-position 4-way electromagnetic switch first valve 15 and 3-position 4-way electromagnetic switch second valve 16 respectively, described 3-position 4-way electromagnetic switch first valve 15 and 3-position 4-way electromagnetic switch second valve 16 respectively with III shaft clutch 14, IV shaft clutch 13, V shaft clutch 12 is connected with the oil cylinder of VI shaft clutch 11.Described accumulator can adopt piston accumulator, also can adopt the air sac type accumulator, the present invention preferred the former.
In order to realize the overload protection of engineering machine, between second throttle valve 20 and second accumulator 23, be provided with bi-bit bi-pass electromagnetic switch first valve 19, the oil outlet tube of bi-bit bi-pass electromagnetic switch first valve 19 is connected with the inner chamber of casing 8.
Braking device of the present invention is made up of brake control valve 33, the oily booster 27 in oil top, brake lubricating cup 28.Brake control valve 33 is connected the output terminal of relief valve 29, and brake control valve 33 is connected with the oil that is used for linking to each other with brake and pushes up oily booster 27; Wherein the 3rd throttle valve 33-1, the 4th throttle valve 33-2 that are stepped on selector valve and the spool by the two-position three way pin of brake control valve 33 forms; The oily booster 27 in oil top is connected with brake lubricating cup 28.
When spool during in highest order, pressure source disconnects, oil top booster 26 connected tanks, in the spool folding process, it is less to begin the 3rd throttle valve 33-1 restriction flow area, the 4th throttle valve 33-2 restriction flow area is bigger, at this moment brake control valve 33 outlet oil pressure are less, along with the flow area of the restriction that moves down the 3rd throttle valve 33-1 of spool increases, the choke area of the 4th throttle valve 33-2 reduces, thereby the outlet pressure of brake control valve 33 is increased, the spool of brake control valve 33 during to least significant end the 4th throttle valve 33-2 restriction close, brake control valve 33 outlet pressure maximums (delivery pressure of pump) are finally accomplished speed brake control.
One or two gear pumps that link with II axle 2 also are installed on casing.One is to be loader work usefulness, and another is to use for control loader direction.
Be that example further specifies the present invention with ZL20 loader adapted gearbox below.Engine model 490,2300 rev/mins of rated speeds.Join bridge rotating ratio be 1: 25.66, diameter of tyres is 1100mm.
By motor by transmission shaft to gearbox I axle, the I axle is equipped with two clutches.By the control of two-position four-way solenoid directional control valve, when the DT5 no electric circuit, left side clutch is combined into to shelves.When DT5 switched on, the right clutch was combined into top grade.Left side clutch is by gear Z1 (33), and Z2 (56) is to two.The right clutch passes through gear Z3 (44) Z4 (45) to two.A loader has low pressure gear pump, is gearbox control lubrication pressure source.Can adorn two gear pumps for two.One is to be loader work usefulness, and another is to use for control loader direction.
Adorn a clutch on III axle, IV axle, V axle, the VI axle respectively, the gear on the clutch is respectively Z7 (53) Z6 (47) Z8 (56) Z9 (44), and two Z5 that cog (30) are meshed with Z6, Z7, Z8, Z9.
During the DT4 energising, the VI shaft clutch is in conjunction with being engaged to output shaft VII by Z16 and Z17.
In DT3 when energising,, the V shaft clutch is in conjunction with being engaged to output shaft VII by Z14 and Z15, Z16 and Z17.
In DT2 when energising,, the IV shaft clutch is in conjunction with being engaged to output shaft VII by Z12 and Z13, Z14 and Z15, Z16 and Z17.
During the DT1 energising, the III shaft clutch is in conjunction with being engaged to output shaft VII by Z10 and Z11.
Output shaft VII is delivered to wheel variation speed bridge by transmission shaft and arrives wheel again.
Left side clutch is combined into to shelves on one.The V shaft clutch is combined into low-grade 1, speed ratio is: Z2/Z1 * Z8/Z5 * Z15/Z14 * Z17/Z16=56/33 * 56/30 * 67/33 * 54/30=11.576, forward gears 1 speed be 1.674 kms/hour, the VI shaft clutch be combined into low-grade 2 speed ratios that advance be Z2/Z1 * Z9/Z5 * Z17/Z16=56/33 * 44/30 * 54/30=6.977 advance low-grade 2 speed be 4.326 kms/hour.
The III shaft clutch is combined into and advances low-gradely 3, and speed ratio is Z2/Z1 * Z7/Z5 * Z11/Z10=56/33 * 56/30 * 30/68=1.323, low-grade 3 speed of advancing be 14.65 kms/hour.
The IV shaft clutch is combined into and retreats low grade, and speed ratio is Z2/Z1 * Z6/Z5 * Z13/Z12 * Z15/Z14 * Z17/Z16=56/33 * 47/30 * 36/72 * 67/33 * 54/30=4.858, retreat geared-down speed and be 3.99 kms/hour.
The right clutch is combined into top grade on one.
It is Z4/Z3 * Z8/Z5 * Z15/Z14 * Z17/Z16=45/44 * 56/30 * 67/33 * 54/30=6.977 that the V shaft clutch is combined into high-grade 1 speed ratio that advances, high-grade 1 speed of advancing be 2.778 kms/hour.
The VI shaft clutch is combined into and advances high-gradely 2, and speed ratio is Z4/Z3 * Z9/Z5 * Z17/Z16=45/44 * 44/30 * 54/30=2.7, high-grade 2 speed of advancing be 7.178 kms/hour.
The III shaft clutch is combined into and advances high-gradely 3, and speed ratio is Z4/Z3 * Z7/Z5 * Z11/Z10=45/44 * 53/30 * 30/68=0.797, high-grade 3 speed of advancing be 24.318 kms/hour.
The IV shaft clutch is combined into and retreats top grade, and speed ratio is Z4/Z3 * Z6/Z5 * Z13/Z12 * Z15/Z14 * Z17/Z16=45/44 * 47/30 * 67/33 * 54/30=2.928, retreat high-grade speed and be 6.619 kms/hour.
Left side clutch in conjunction with the time be low-grade.
Advance 1 grade of 1.674 km/hour; Advance 2 grade of 4.326 km/hour; Advance 3 grade of 14.65 km/hour; Retreat shelves 3.99 kms/hour.
One the right clutch in conjunction with the time be the top grade.
Advance 1 grade of 2.778 km/hour; Advance 2 grade of 7.178 km/hour; Advance 3 grade of 24.318 km/hour; Retreat shelves 6.619 kms/hour.
High and low shift retreats shelves in conjunction with forming 62 of forward gearss.
Advance low 1 (1) grade of 1.674 km/hour; High 1 (2) grade of 2.778 km/hour; Low 2 (3) grades of 4.326 kms/hour; High 2 (4) grades of 7.178 kms/hour; Low 3 (5) grades of 14.65 kms/hour; High 3 (6) grades of 24.318 kms/hour.
Retreat low (1) shelves 3.99 kms/hour; High (2) shelves 6.619 kms/hour.
Claims (7)
1. engineering machine adapted Powershift transmission, comprise casing (8), the I axle (1) that is arranged in parallel, II axle (2), III axle (3), IV axle (4), V axle (5), VI axle (6) and VII axle (7) respectively by Bearing Installation in casing (8), wherein I axle (1) is an input shaft, VII axle (7) is an output shaft, it is characterized in that:
I axle (1) is in transmission connection with II axle (2); The II axle also is equipped with the Z5 gear on (2);
Be separately installed with III shaft clutch (14), IV shaft clutch (13), V shaft clutch (12) and VI shaft clutch (11) on III axle (3), IV axle (4), V axle (5) and the VI axle (6), the III shaft clutch is equipped with the Z7 gear on (14), the IV shaft clutch is equipped with the Z6 gear on (13), the V shaft clutch is equipped with the Z8 gear on (12), and the VI shaft clutch is equipped with the Z9 gear on (11); The III axle also is installed with the Z10 gear on (3), and the IV axle also is installed with the Z12 gear on (4), also is installed with Z13 and Z14 gear on the V axle (5), also is installed with Z16 gear and Z15 gear on the VI axle (6); The Z5 gear is meshed with Z6 gear, Z8 gear respectively, and the Z6 gear is meshed with the Z7 gear, and the Z8 gear is meshed with the Z9 gear, and the Z12 gear is meshed with the Z13 gear, and the Z14 gear is meshed with the Z15 gear;
The VII axle is equipped with the Z11 gear on (7), and the Z11 gear is meshed with the Z10 gear; Z17 gear and the oil hydraulic cylinder (9) that is used to control Z17 gear axial position also are installed on the VII axle (7);
The low pressure gear pump (30) that links with the I axle also is installed on casing (8), and low pressure gear pump (30) is connected with relief valve (29), and the flow-off of relief valve (29) is connected with described six clutches respectively by oil pipe; Relief valve (29) is associated with accumulator outward by throttle valve;
Relief valve (29) also is associated with two-position three way pilot operated directional control valve (17) outward by throttle valve, two-position three way pilot operated directional control valve (17) is connected with 3-position 4-way electromagnetic switch first valve (15) and 3-position 4-way electromagnetic switch second valve (16) respectively, and described 3-position 4-way electromagnetic switch first valve (15) is connected with III shaft clutch (14), IV shaft clutch (13), V shaft clutch (12) and the oil cylinder of VI shaft clutch (11) respectively with 3-position 4-way electromagnetic switch second valve (16).
2. engineering machine adapted Powershift transmission as claimed in claim 1 is characterized in that described I axle (1) and II axle (2) are in transmission connection to be meant:
Left clutch (32) and right clutch 31 are installed on the I axle (1)), left clutch is equipped with the Z1 gear on (32), and right clutch is equipped with the Z3 gear on (31);
Z2 gear, Z4 gear also are installed on the II axle (2), and wherein, the Z2 gear is meshed with the Z1 gear, and the Z4 gear is meshed with the Z3 gear.
3. engineering machine adapted Powershift transmission as claimed in claim 2 is characterized in that:
Relief valve (29) is connected with first throttle valve (26) and second throttle valve (20) respectively, wherein, first throttle valve (26) is connected with first accumulator (24) and two-position four-way solenoid directional control valve (25) respectively, and two-position four-way solenoid directional control valve (25) links with described left clutch (32) and right clutch (31) respectively; The output terminal of second throttle valve (20) is connected with two oil pipes, one is connected with second accumulator (23), mutually bi-bit bi-pass electromagnetic switch second valve (22) in parallel and one-way valve (21), the 3rd accumulator 18 in turn), it two is connected with two-position three way pilot operated directional control valve (17).
4. engineering machine adapted Powershift transmission as claimed in claim 3, it is characterized in that: be provided with bi-bit bi-pass electromagnetic switch first valve (19) between second throttle valve (20) and second accumulator (23), the oil outlet tube of bi-bit bi-pass electromagnetic switch first valve (19) is connected with the inner chamber of casing (8).
5. as claim 1 or 2 or 3 or 4 described engineering machine adapted Powershift transmissions, it is characterized in that: the output terminal of relief valve (29) also is connected with brake control valve (33), and brake control valve (33) is connected with the oil that is used for linking to each other with brake and pushes up oily booster (27); Wherein the 3rd throttle valve (33-1), the 4th throttle valve (33-2) stepped on selector valve and the spool by the two-position three way pin of brake control valve (33) formed; The oil oily booster in top (27) is connected with brake lubricating cup (28).
6. as claim 1 or 2 or 3 or 4 described engineering machine adapted Powershift transmissions, it is characterized in that: one or two gear pumps that link with II axle (2) also are installed on casing (8).
7. engineering machine adapted Powershift transmission as claimed in claim 5 is characterized in that: one or two gear pumps that link with II axle (2) also are installed on casing (8).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201110023275 CN102146987B (en) | 2011-01-18 | 2011-01-18 | Power shift speed changing box for matching engineering machine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201110023275 CN102146987B (en) | 2011-01-18 | 2011-01-18 | Power shift speed changing box for matching engineering machine |
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| Publication Number | Publication Date |
|---|---|
| CN102146987A true CN102146987A (en) | 2011-08-10 |
| CN102146987B CN102146987B (en) | 2013-02-06 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN 201110023275 Expired - Fee Related CN102146987B (en) | 2011-01-18 | 2011-01-18 | Power shift speed changing box for matching engineering machine |
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| CN103968012A (en) * | 2014-05-27 | 2014-08-06 | 王云高 | Three-clutch transmission of loading machine |
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| CN102900783A (en) * | 2012-11-09 | 2013-01-30 | 王云高 | Automatic hydraulic clutch based on automatic transmission gearbox |
| CN103968063A (en) * | 2014-05-27 | 2014-08-06 | 王云高 | Three-clutch transmission of small and medium loading machines |
| CN103968012A (en) * | 2014-05-27 | 2014-08-06 | 王云高 | Three-clutch transmission of loading machine |
| CN103968063B (en) * | 2014-05-27 | 2016-01-20 | 王云高 | Middle-size and small-size loader three clutch gearbox |
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| CN102146987B (en) | 2013-02-06 |
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