CN1085803C - Double inclined plate synchronous rotation internal power split stream hydraulic variable speed unit - Google Patents
Double inclined plate synchronous rotation internal power split stream hydraulic variable speed unit Download PDFInfo
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- CN1085803C CN1085803C CN99107365A CN99107365A CN1085803C CN 1085803 C CN1085803 C CN 1085803C CN 99107365 A CN99107365 A CN 99107365A CN 99107365 A CN99107365 A CN 99107365A CN 1085803 C CN1085803 C CN 1085803C
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- pump
- motor
- swash plate
- output shaft
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Abstract
The present invention relates to a hydraulic stepless speed change device with double inclined plates, synchronous rotation and internal power shunting. An input shaft and an output shaft of the stepless speed change device are coaxial; a pump cylinder is arranged on the input shaft and is directly driven by the input shaft; a motor cylinder and a pump casing are fixed; the motor cylinder and the output shaft are coaxial; an inclined plate of a pump and an inclined plate of a motor are positioned between the pump cylinder and the motor cylinder and are simultaneously arranged on the output shaft to synchronously rotate along with the output shaft. The device has the advantages of high transmission efficiency, simple structure, low cost, long service life and easy manufacture. The device can be widely applied to the technical fields needing stepless speed regulation, such as internal combustion locomotives, engineering vehicles, cars, machine tools, blowers, water pumps, etc.
Description
The present invention relates to a kind of double inclined plate synchronous rotation internal power shunting hydraulic variable speed unit, it can be widely used in the field that internal combustion locomotive, engineering vehicle, automobile, lathe, blower fan, water pump etc. need stepless speed regulation.
Existing interior power shunting hydraulic variable speed unit, typical structure is as " the interior power shunting stepless speed changes devices of the motor differential of the 1637th page of introduction of oilhydraulic engineering handbook one book.The working principle of this class speed change gear requires pump or motor to make housing and cylinder body all is the double-acting structure of rotation.In the connection of oil circuit between pump and the motor, a swivel coupling must be housed, could be communicated with the oil circuit between pump and the motor.Because of swivel coupling on the motor casing of rotation or on the pump case of rotation, and the matching gap of swivel coupling is very little in 0.01mm, have certain volume to leak.This supporting precision that just requires to support motor casing or pump case bearing is quite high, and the malalignment of the spin axis of motor casing or pump case and the spin axis of swivel coupling is not more than 0.005mm, and the existing processes level is difficult to reach.In addition, the output shaft of motor cylinder is bearing on the motor casing of rotation or the input shaft of pump cylinder is bearing on the pump case of rotation, the structure more complicated is rotated because of motor casing or pump case, and the control set for adjusting of motor swashplate or pump swash plate is also very complicated.And also has trouble in the dynamic balancing.Because of this class speed change gear complex structure, manufacturing difficulty are seldom used.
U.S. Pat 5,423,183 disclose a kind of hydraulic machinery that has the wedge shape swash plate, and the pump swash plate of this hydraulic machinery and motor swashplate are one and are installed on the output shaft that it is simple in structure, and is easy to manufacture, the transmission efficiency height.But make one because of its pump swash plate and motor swashplate, the discharge capacity sum of pump delivery and motor is invariable when speed governing, and its slewing range changes between the maximum pump discharge of pump 0, thereby its slewing range is little; The pressure that its output torque of while equals pump multiply by pump delivery, thereby output torque is little.
The purpose of this invention is to provide a kind of double inclined plate synchronous rotation internal power shunting hydraulic variable speed unit, this device slewing range is wide, and transmitted power density is big, and output torque is big, and volume is little.
The objective of the invention is to finish in the following manner: a kind of double inclined plate synchronous rotation internal power shunting hydraulic variable speed unit, comprise axial piston pump, motor and control set for adjusting, its pump cylinder is coaxial with motor cylinder; Motor cylinder and pump case maintain static, and motor cylinder is coaxial with output shaft, and pump swash plate and motor swashplate also are installed in simultaneously on the output shaft between pump cylinder and motor cylinder and rotate synchronously with output shaft; On the output shaft between pump swash plate and the motor swashplate, be fixed with the swash plate bearing, two half-cylindrical supporting surfaces on the described swash plate bearing match with the semicylinder of pump swash plate and motor swashplate, and the axis of oscillation of pump swash plate and motor swashplate is parallel to each other and perpendicular to output shaft.
In double inclined plate synchronous rotation internal power shunting hydraulic variable speed unit of the present invention, its slewing range is being regulated between the positive and negative maximum pump discharge of pump and between the positive and negative maximum pump discharge of motor, has therefore increased the slewing range of this speed change gear; Under the identical condition of pressure same displacement, the transmitted power density of this speed change gear is big, and max. output torque is two times of max. output torque of documents 1 (US5423183), and volume is relatively little.
This speed change gear transport characteristics is as follows:
Velocity ratio: i
21=V
p/ V
p+ V
m
The hydraulic power split ratio; ε
h=1-i
21
Mechanical output split ratio: ε
m=i
21
Describe the embodiment of double inclined plate synchronous rotation internal power shunting hydraulic variable speed unit of the present invention in detail below in conjunction with accompanying drawing.
Shown in Figure 1 is the double inclined plate synchronous rotation internal power shunting hydraulic variable speed unit sectional view that is applied on the automobile;
Fig. 2 is the partial sectional view along A-A direction shown in Figure 1;
Shown in Figure 3 is is applied in shunting hydraulic variable speed unit sectional view in the synchronous rotary power of diclinic dish that pump swash plate on blower fan, the water pump and motor swashplate be one;
Fig. 4 is the partial sectional view along A-A direction shown in Figure 3;
Shown in Figure 5 is is applied in the double inclined plate synchronous rotation internal power shunting hydraulic variable speed unit sectional view that pump swash plate on the lathe and motor swashplate bearing are one;
Fig. 6 is the sectional view along A-A direction shown in Figure 5.
First embodiment
Double inclined plate synchronous rotation internal power shunting hydraulic variable speed unit illustrated in figures 1 and 2 is mainly used in automotive field.
Input shaft 1 is coaxial with output shaft 19, and pump cylinder 2 is fixed on the input shaft 1.Plunger hole 4 on the pump cylinder 2 is a through hole, and the piston shoes 33 of axial hydrostatic thrust bearing are equipped with on the left side, and pump plunger 5 is equipped with on the right, and the plunger hole 17 on the motor cylinder 18 is a blind hole, and motor plunger 16 is equipped with on the left side of plunger hole 17.Motor cylinder 18 maintains static with pump case 3.Be fixed with swash plate bearing 26 on the output shaft 19, swash plate bearing 26 is between pump cylinder 2 and motor cylinder 18, two semi-cylindrical supporting surfaces 27 are arranged on the swash plate bearing 26,25, be used to support pump swash plate 28 and motor swashplate 24, two halves cylindrical bearing surface 27,25 axis is parallel to each other and perpendicular to output shaft 19, two halves cylindrical bearing surface 27 on the swash plate bearing 26, there are two to be used to connect pump and motor advances between 25, fuel-displaced main oil gallery 36, wherein be used for being communicated with on the main oil gallery 36 in pump and motor low pressure oil district and have an oil inlet hole 39 to be communicated with, be used for replenishing the hydraulic oil that leaks with the hydraulic oil of pump case 3.Pump swash plate 28, motor swashplate 24 are circular semicylinder, respectively be processed with the joining on the pasta of pump swash plate 28, motor swashplate 24 in high pressure oil area, both sides, low pressure oil district two mutual disconnected semi-round ring shapes into and out of oily distributing groove 34,38.Be processed with two oilholes 35,37 that are used to be communicated with the main oil gallery 36 on oily distributing groove 34,38 and the swash plate bearing 26 joining of pump swash plate 28, motor swashplate 24 between pasta and the semi-cylindrical, the semicylinder of pump swash plate 28, motor swashplate 24 is being pressed under the effect of two springs 40 on the swash plate bearing 26 two halves cylindrical sliding support faces 27,25 all the time.Pump swash plate 28, motor swashplate 24 can be under the controls of control set for adjusting (not shown), drive the dial 29 of pump, the dial 23 of motor by the variable piston 32 of pump, the variable piston 21 of motor, the driving lever 30 of the dial 23 driven pump swash plates of the dial 29 by pump, motor, the driving lever 22 of motor swashplate again, make the axis swing of pump swash plate 28, the motor swashplate 24 two halves cylindrical bearing surface 27,25 on swash plate bearing 26, change the inclination angle of pump swash plate 28, motor swashplate 24.Pump swash plate 28, motor swashplate 24 rotate synchronously with swash plate bearing 26 and output shaft 19.Be processed with on pump plunger 5, the motor plunger 16 larger aperture into and out of oilhole 6,15, pump piston shoes 8, also be processed with above the motor piston shoes 13 larger aperture into and out of oilhole 7,14.Pump oil distribution casing 9 is between pump piston shoes 8 and pump swash plate 28, and motor oil distribution casing 11 is between motor swashplate 24 and motor piston shoes 13.Pump pressure dish 31 with pump piston shoes 8, pump oil distribution casing 9 certain intervals be pressed on the pump swash plate 28, pump pressure dish 31 is fixing with pump oil distribution casing 9.Motor platen 20 with motor piston shoes 13, motor oil distribution casing 11 certain intervals be pressed on the motor swashplate 24, motor platen 20 is fixing with motor oil distribution casing 11.On the pump oil distribution casing 9 into and out of oilhole 10 respectively on the pump piston shoes 8 on oilhole 7, the pump plunger 5 into and out of oilhole 6 corresponding connections, simultaneously again with pump swash plate 28 on be communicated with into and out of oily distributing groove 34.On the motor oil distribution casing 11 into and out of oilhole 12 respectively with motor piston shoes 13 on oilhole 14, the motor plunger 16 into and out of oilhole 15 corresponding connections, be communicated with turnover oil distributing groove 38 on the motor swashplate 24 again simultaneously, pump oil distribution casing 9 rotates with input shaft 1 synchronously with pump piston shoes 8, pump plunger 5 pump cylinders 2, and motor oil distribution casing 11, motor piston shoes 13, motor plunger 16 do not rotate.Motor oil distribution casing 11 is done torsional movement.When pump swash plate 28 has certain inclination angle, when pump cylinder 2 relative pump swash plates 28 relatively rotate, pump plunger 5 to-and-fro motion in the plunger hole 4 on pump cylinder 2 under 28 effects of pump swash plate, by the oil of joining of the turnover oil distributing groove 34 on oilhole 10 and the pump swash plate 28 on oilhole 7, the pump oil distribution casing 9 on oilhole 6, the pump piston shoes 8 on the pump plunger 5, realize pressure oil, the oil suction of pump.
When motor swashplate 24 has certain inclination angle, the high pressure oil of pump is by the oil duct 35 on the pump swash plate 28, oil duct 36 on the swash plate bearing 26, oil duct 37 on the motor swashplate 24 enters the distributing groove 38 of motor swashplate 24, by the join oil of motor swashplate 24 with motor oil distribution casing 11, high pressure oil enters in the motor plunger hole 17 on the motor cylinder 18 and promotes to move reciprocatingly in the motor plunger hole 17 of motor plunger 16 on motor cylinder 18, the to-and-fro motion of motor plunger 16 by motor swashplate 24, drive output shaft 19 and rotate.Thereby realize the interior power shunting transmission of this speed change gear.
One, positive modulation speed
When the inclination angle of pump swash plate 28 is zero, output speed n
2=0, motor is in separated state.
When the inclination angle of pump swash plate 28 increases (inclination angle of pump swash plate 28 is opposite with the direction at the inclination angle of motor swashplate 24), the rotation speed n of output shaft 19 gradually by zero
2Also increase gradually by zero.
When the inclination angle of pump swash plate 28 reaches maximum value, (V
p Max=V
m Max) rotating speed of output shaft 19 reaches input
Axle 1 rotation speed n
1Half, n
2=0.5n
1, output torque M at this moment
2Maximum: M
2=2M
1
The inclination angle maximum of pump swash plate 28 is constant, changes the speed regulation process at the inclination angle of motor swashplate 24.
When the inclination angle of motor swashplate 24 is reduced gradually by maximum, the rotating speed of output shaft 19 continues to increase.When the inclination angle of motor swashplate 24 was reduced to zero, the rotating speed of output shaft 19 equaled the rotation speed n of input shaft 1
2=n
1, output torque at this moment equals input torque M2=M1, ε at this moment
h=0 rotational efficienty reaches peak value, and η is more than 0.9.
When the inclination angle of motor swashplate 24 by zero during to reverse increases (at this moment the inclination angle of the inclination angle of pump swash plate 28 and motor swashplate 24 in the same way), the rotating speed continuation increase of output shaft 19.(V when the inclination angle of motor swashplate 24 equals the inclination angle of 1/2 pump swash plate 28
m=-0.5V
p Max), at this moment the rotating speed of output shaft 19 equals the rotation speed n of 2 times input shaft 1
2=2n
1, output torque M
2=0.5M
1, as output speed n
2At i2
1In=0-2 the speed adjustable range during speed governing, the high all the time hydraulicefficiency of transmission efficiency, η is between 0.8-0.9.
When the inclination angle of motor swashplate 24 continues to increase, the rotation speed n of output shaft 19
2Continue to increase, but transmission efficiency descends rapidly (being lower than hydraulicefficiency).
Common automobile output speed speed adjustable range i
21Between 0-2.Operate mainly in i
21In near=1 the efficient district.
Two, counter-rotating speed governing
The inclination angle maximum of motor swashplate 24, the inclination angle of change pump swash plate 28.
When the inclination angle of pump swash plate 28 increases (inclination angle of the inclination angle of pump swash plate 28 and motor swashplate 24 is in the same way) gradually by zero, output shaft 19 counter-rotatings and by zero increase gradually, when the inclination angle of pump swash plate 28 equals the inclination angle of 1/2 motor swashplate 24, (V
p=-0.5V
m Max) rotating speed of output shaft 19 is n
2=-n
1Transmission efficiency when reversing speed governing in this zone can satisfy the needs of rolling-back of car fully a little less than hydraulicdriven transmission efficiency.Continue to increase when the inclination angle of pump swash plate 28, the counter-rotating rotating speed further raises, but transmission efficiency descends rapidly.For the engineering vehicle that often is operated in the reverse gear zone, need add a mechanical gear reversing device.In the efficient district that this speed change gear always is operated in just changeing.
When the inclination angle of pump swash plate 28 motor swashplates 24 is zero simultaneously, automobile will be in the neutral gear sliding state.
This speed change gear can dispense the clutch and the mechanical gearbox of automobile, compares with automobile-used hydraulic automatic speed variator, and it has higher transmission efficiency, littler volume, weight, lower cost.
Second embodiment
Fig. 3 and shown in Figure 4 be that pump swash plate, motor swashplate are shunting hydraulic variable speed unit in the synchronous rotary power of diclinic dish of one, it is mainly used in the occasion that blower fan, water pump etc. need permanent moment of torsion speed governing.
Input shaft 101 is coaxial with output shaft 129, and pump cylinder 102 is fixing with input shaft 101.Pump cylinder 102 is bearing on the pump case 104 by axial thrust bearing 103, radial bearing 127, plunger hole on the pump cylinder 102 is a blind hole, pump plunger 106, stage clip 105 are equipped with in the inside, motor cylinder 119 maintains static with pump case 104, plunger hole on the motor cylinder 119 is a blind hole, and motor plunger 114, stage clip 115 are equipped with in the inside.Output shaft 129 is bearing in respectively in pump cylinder 102, the motor cylinder 119 by two radial bearings 128,120, has swash plate supporting axle 122 on the output shaft 129.Swash plate 110 is between pump cylinder 102, motor cylinder 119, and swash plate 110 is fixing with swash plate supporting axle 122.Control panel 116 is installed on the motor cylinder 119, and the square threaded form on the control panel 116 cooperates with square threaded form on the motor cylinder 119.When control panel 116 rotated, control panel 116 can be along the axis move left and right of output shaft 129, and drove swash plates 110 swings by bi-directional axial thrust-bearing 118, bearing pin 117, linkage mechanism 121, changed the inclination angle of pump, motor swashplate simultaneously.Two of swash plate 110 is joined on the pasta, side at high pressure oil area is processed with pump distributing groove, the motor distributing groove 135 that interconnects, side at low pressure area is processed with pump distributing groove, the motor distributing groove 134 that interconnects, and has filler opening 132 to be communicated with hydraulic oil in the pump case.Pump, the piston shoes 108 of motor, 111 is hemisphere, bigger turnover oilhole 109 is arranged above, 112, pump, the plunger 106 of motor, 114 head is half ball-and-socket type, bigger turnover oilhole 107 is arranged above, 113, pump oil distribution casing 125, motor oil distribution casing 124 lays respectively at pump piston shoes 108, swash plate 110, motor piston shoes 111, between the swash plate 110, advancing on the pump oil distribution casing 125, oil outlet 126 respectively with pump piston shoes 108 on advance, oil outlet 109,107 corresponding connections of turnover oilhole on the pump plunger 106, turnover oilhole 123 on the motor oil distribution casing 124 respectively with motor piston shoes 111 on turnover oilhole 112, the turnover oilhole 113 corresponding connections on the motor plunger 114.Pump dial 131 is fixing with pump oil distribution casing 125.Pump plunger 106 ball-and-socket face under the effect of spring 105 compresses the sphere of pump piston shoes 108, and the slip surface of pump piston shoes 108 compresses the one side of pump oil distribution casing 125, and the another side of pump oil distribution casing 125 compresses on the swash plate 110 pump and joins pasta.Pump oil distribution casing 125 rotates with pump cylinder 102 under the drive of pump piston shoes 108 synchronously by pump dial 131.Motor plunger 114 ball-and-socket face under the effect of spring 115 compresses the sphere of motor piston shoes 111, and the slip surface of motor piston shoes 111 compresses the one side of motor oil distribution casing 124, and the another side of motor oil distribution casing 124 compresses on the swash plate 110 motor and joins pasta.Motor oil distribution casing 124 is done torsional movement by motor dial 130 under the effect of motor piston shoes 111 and swash plate 110.When pump cylinder 102 relative to swash plate 110 rotate, when swash plate 110 rotates relative to motor cylinder 119, by pump oil distribution casing 125 oil of joining with swash plate 110, the oil of joining of motor oil distribution casing 124 and swash plate 110 is realized the interior power shunting transmission of this speed change gear.Gimbal 133 is used for the centrifugal force of balance swash plate center of gravity off-centre.
The transport characteristics of this speed change gear:
Under rated working pressure permanent moment of torsion output, M
2=constant.
Velocity ratio i
21=V
p(V
p=0-1)
Slewing range i
21=0-1
Work as i
21=1 o'clock, ε
h=0, transmission efficiency η can reach more than 0.93, in whole speed change zone higher transmission efficiency is arranged all.
When this speed change gear is applied in blower fan, water pump stepless speed governing, compare, wideer efficient district is arranged with traditional hydraulic couplers, electromagnetic adjustable speed motor.Compare with RHVC, at high-power transmission field (hundreds of KW is to several thousand KW), this speed change gear has bigger advantage at cost, technology manufacture view.
This speed change gear also can be constant-power speed regulation device usefulness, max. output torque Mmax=PmaxVmax.
The 3rd embodiment
Fig. 5 and shown in Figure 6 be that pump swash plate and motor swashplate bearing are the double inclined plate synchronous rotation internal power shunting hydraulic variable speed unit of one, this speed change gear mainly is used in the occasion that lathe etc. needs constant-power speed regulation.
This speed change gear and first embodiment's difference is that pump swash plate 204 is an one with the motor swashplate bearing, the one side of pump swash plate 204 is an inclined-plane 205, it joins pasta for the pump swash plate, another side is that the half-cylindrical supporting surface 203 of motor swashplate cooperates with the semicylinder of motor swashplate 202, the axis normal of the half-cylindrical supporting surface 203 of motor swashplate is in output shaft 201, pump swash plate 204 is fixed on the output shaft 201, by changing the inclination angle speed governing of motor swashplate 202.
The transport characteristics of this speed change gear is:
Under rated working pressure, be constant-power speed regulation, velocity ratio i
21=0.5-∞.
At i
21Transmission efficiency η＞0.85 in the speed change zone of=0.5-2, max. output torque are 2 times with discharge capacity hydraulic transmission max. output torque.When being used in the lathe speed governing, it can make the gearbox of lathe oversimplify.
Compare with existing dc speed-regulating motor system, it has lower cost, during with the supporting use of retarder, can be widely used in the field of low speed constant-power speed regulation.
Also can cancel the connection pump according to different needs among above-mentioned 3 embodiments, oil inlet hole in the motor main oil gallery low pressure oil district, directly connect pump at swash plate bearing or swash plate, adding high pressure oil area, the low pressure oil district that two one-way valves make two main oil gallerys between the motor on two main oil gallerys can exchange, the filler opening place also can add filter cleaner, for the highest input, the output speed that further the improves speed change gear axial sealer that can add high pressure on input shaft, output shaft makes the oil pressure in the pump case reach 0.2-3Mpa.The Maximum operating pressure that on main oil gallery, also can add relief valve restriction speed change gear.
Among above-mentioned first embodiment, being used on the swash plate bearing is communicated with main oil gallery between pump, the motor, also can connects two main oil gallerys out with a swivel coupling by output shaft, for automobile and accumulator logotype, can make this speed change gear have brake energy storage, functions such as engine start.The high pressure oil that comes out for engineering vehicle or the also available connection of other machinery directly drives other hydraulic pressure installation.
Among above-mentioned first and the 3rd liang of embodiment, in dial, also can adorn a two-way hydrodynamic sliding bearing (sliding bearing is a disc-shape), drive a driving lever by sliding bearing and make the swash plate swing.
Among above-mentioned first and the 3rd liang of embodiment, circular semicylinder swash plate also should add counter weight device, and the center of gravity of swash plate is overlapped with the intersection point of output shaft axis with the axis of oscillation of swash plate.
Among above-mentioned first embodiment, input shaft can directly or indirectly drive an auxiliary oil pump, is used for the fuel feeding of variable piston.
Obviously, therefore other embodiments different with the foregoing description that do not depart from the present invention design should be appreciated that the specific embodiment that provides in order to determine claim not only is provided in the present invention within protection scope of the present invention.
Claims (3)
1, a kind of double inclined plate synchronous rotation internal power shunting hydraulic variable speed unit comprises axial piston pump, motor and control set for adjusting, and its pump cylinder is coaxial with motor cylinder; Motor cylinder and pump case maintain static, and motor cylinder is coaxial with output shaft, and pump swash plate and motor swashplate also are installed in simultaneously on the output shaft between pump cylinder and motor cylinder and rotate synchronously with output shaft; It is characterized in that: on the output shaft between pump swash plate and the motor swashplate, be fixed with the swash plate bearing, two half-cylindrical supporting surfaces on the described swash plate bearing match with the semicylinder of pump swash plate and motor swashplate, and the axis of oscillation of pump swash plate and motor swashplate is parallel to each other and perpendicular to output shaft.
2, double inclined plate synchronous rotation internal power shunting hydraulic variable speed unit according to claim 1, it is characterized in that: also be processed with the oilhole that is used to be communicated with main oil gallery between pump and the motor on pump swash plate, the motor swashplate, its high pressure oil area, low pressure oil district of joining on the pasta is processed with distributing groove respectively.
3, double inclined plate synchronous rotation internal power shunting hydraulic variable speed unit according to claim 2, it is characterized in that: the pump oil distribution casing is between pump swash plate and pump piston shoes, and the motor oil distribution casing is between motor swashplate and motor piston shoes.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN99107365A CN1085803C (en) | 1999-05-18 | 1999-05-18 | Double inclined plate synchronous rotation internal power split stream hydraulic variable speed unit |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN99107365A CN1085803C (en) | 1999-05-18 | 1999-05-18 | Double inclined plate synchronous rotation internal power split stream hydraulic variable speed unit |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1233720A CN1233720A (en) | 1999-11-03 |
| CN1085803C true CN1085803C (en) | 2002-05-29 |
Family
ID=5272739
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN99107365A Expired - Fee Related CN1085803C (en) | 1999-05-18 | 1999-05-18 | Double inclined plate synchronous rotation internal power split stream hydraulic variable speed unit |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1085803C (en) |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2004019836A (en) * | 2002-06-18 | 2004-01-22 | Yanmar Co Ltd | Hydraulic continuously variable transmission and power transmission apparatus |
| CN101922425B (en) * | 2009-06-09 | 2012-10-17 | 李基深 | Axial plunger pump for increasing flow and sealing pressure |
| CN105715532B (en) * | 2016-04-06 | 2018-08-24 | 北京理工大学 | A kind of conjuncted hydraulic pump motor of parallel-axis type |
| CN108506453A (en) * | 2018-04-17 | 2018-09-07 | 山西平阳重工机械有限责任公司 | Hydrostatic variable-speed torque-converting device |
| CN108953544B (en) * | 2018-09-11 | 2024-02-27 | 无锡威孚精密机械制造有限责任公司 | Hydrostatic stepless speed change device |
| CN109630646B (en) * | 2018-11-20 | 2021-02-23 | 重庆交通大学 | Stepless hydraulic speed variator |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4493189A (en) * | 1981-12-04 | 1985-01-15 | Slater Harry F | Differential flow hydraulic transmission |
| US4896585A (en) * | 1987-05-05 | 1990-01-30 | Linde Aktiengesellschaft | Adjustable axial piston machine |
| US5423183A (en) * | 1991-01-14 | 1995-06-13 | Advanced Power Technology, Inc. | Hydraulic machine with wedge-shaped swashplate |
-
1999
- 1999-05-18 CN CN99107365A patent/CN1085803C/en not_active Expired - Fee Related
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4493189A (en) * | 1981-12-04 | 1985-01-15 | Slater Harry F | Differential flow hydraulic transmission |
| US4896585A (en) * | 1987-05-05 | 1990-01-30 | Linde Aktiengesellschaft | Adjustable axial piston machine |
| US5423183A (en) * | 1991-01-14 | 1995-06-13 | Advanced Power Technology, Inc. | Hydraulic machine with wedge-shaped swashplate |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1233720A (en) | 1999-11-03 |
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