CN103322157A - Hydraulic mechanical torque converter - Google Patents
Hydraulic mechanical torque converter Download PDFInfo
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- CN103322157A CN103322157A CN2013102538404A CN201310253840A CN103322157A CN 103322157 A CN103322157 A CN 103322157A CN 2013102538404 A CN2013102538404 A CN 2013102538404A CN 201310253840 A CN201310253840 A CN 201310253840A CN 103322157 A CN103322157 A CN 103322157A
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- driven gear
- gear
- turbine
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- pump impeller
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Abstract
A hydraulic mechanical torque converter is characterized in that a pump impeller P is connected with a first gear pair Z4/Z2, an output end of a turbine t is connected to a second gear pair Z3/Z1, the first driven gear Z4 and the second driven gear Z3 of the two gear pairs are converged to output power through an overrun clutch; in heavy load and low speed conditions, the overrun clutch are unlocked, the pump impeller P and the first driven gear Z4 and the second driven gear Z3 of the gear pair of the turbine t are unlocked, and the turbine t of a torque converter outputs the power via the first gear pair Z4/Z2; in light load and high speed conditions, the overrun clutch is closed, the pump impeller P and the first driven gear Z4 and the second driven gear Z3 of the turbine t are integrally locked, part of the power is rigidly outputted to the second driven gear Z3 via the second gear pair Z3/Z1, and the other part of the power is outputted via a first gear pair Z4/Z2 of a hydraulic torque converter turbine t. The hydraulic mechanical torque converter has the advantages that total transmission efficiency of a system can be significantly improved, and the hydraulic mechanical torque converter is simple in structure, convenient to control and promising in application prospect.
Description
Technical field
The present invention relates to a kind of application fluid torque converter and realizes infinite variable speed vehicle drive system, is specially adapted to promote fluid torque converter efficient, improves the hydraulic machine torque-converters of VE Vehicle Economy.
Background technique
The efficiengy-increasing of fluid torque converter mainly contains the technology of two kinds of raising efficiencies at present to improving the fuel economy important in inhibiting of vehicle.A kind of is guide wheel freewheel structure, namely increase unidirectional freewheel at guide wheel, guide wheel oppositely dallies when the liquid flow impact vacuum side of blade, thereby makes torque-converters enter the coupling operating mode, efficient is 45 degree straight lines and rises, and this technology can obviously promote the efficient in the high rotating ratio of torque-converters zone.Another kind is turbine locking technology, and it mainly controls locking and the release of face of fluid torque converter and turbine by a hydraulic control clutch.System becomes the rigid mechanical transmission during clutch locking, and efficient is 100%, reverts to again hydraudynamic drive during release, realizes stepless change.This technology is taken into account hydraudynamic drive and mechanically operated advantage, and comprehensive transmission efficiency promotes more obvious.
For above-mentioned the first guide wheel freewheel structure technology scheme, though it can promote torque converter, the coupling operating point only just begins when the turbine outlet liquid flow impact guide vane back side, and it can not adjust control according to the variation of vehicle working condition.
For above-mentioned the second turbine locking technological scheme, its control system need to combine with the gear shift of gearbox, control system is required sternly, and manufacture cost is high.
Summary of the invention
Purpose of the present invention just provides the total transmission efficiency of a kind of system and can obviously promote, and is simple in structure, and control is convenient, and application prospect is the hydraulic machine torque-converters widely.
Solution of the present invention is such:
The present invention is based on a certain single-stage three element fluid torque converter, the pump impeller, turbine and the guide wheel that comprise fluid torque converter, power is inputted from pump impeller, pump impeller is connected with the first gear pair, the turbine output terminal is connected with the second gear pair, and the first driven gear of two pairs of gear pairs and the second driven gear are by the free wheel device outputting power that confluxes; In the heavy-duty low-speed operating mode, the free wheel device release, the first driven gear of pump impeller and turbo tooth wheel set and the second driven gear release, power is only exported through the first gear pair by the turbine of fluid torque converter; During the underloading high-speed working condition, the free wheel device locking, the first driven gear of pump impeller and turbo tooth wheel set and the second driven gear locking are integrated, part power outputs to the second driven gear through the second gear pair rigidity of pump impeller, and another part power is exported through transformer turbine the first gear pair.
Technological scheme also comprises more specifically: the operating mode of described free wheel device heavy-duty low-speed operating mode when being lower than the rotating speed of the second driven gear when the rotating speed of the first driven gear; When the operating mode of underloading high-speed working condition when being higher than the rotating speed of the second driven gear when the rotating speed of the first driven gear.
The present invention adopts the design of technique scheme as follows:
Getting all machinery driving efficiencies is 1.At the free wheel device released state, system is pure fluid torque converter operating mode, and all through hydraudynamic drive output, the mechanical part accounting is zero to power, and system total efficiency is fluid torque converter efficient.
At the free wheel device lockup state, system's input power can be defined as follows according to law of conservation of energy in the shunting rule of mechanical part and fluid power part:
In the formula
Formula (1) is converted to
(4)
System's output power is defined as follows:
Total efficiency
(6)
Fluid torque converter efficient wherein
(7)
In the formula
-----output power
Can release according to formula (2), (6), (7):
System total efficiency
(8)
Formula (8) can be found out:
When system is hydraudynamic drive entirely, namely
The time, total efficiency
, i.e. hydraudynamic drive efficient is exactly total efficiency;
When system is mechanical transmission entirely, namely
The time, total efficiency
Therefore, formula (8) can be regarded the total efficiency equation of this hydraulic mechanical transmission system as, and can make fluid torque converter in different transmission efficiencies
The time, the total transmission efficiency of system
With hydraudynamic drive power dividing ratio
Variation diagram, see shown in the accompanying drawing 2.Fluid power transmitted power split ratio
Less, the total transmission efficiency of system is higher, and under the rotating ratio of a certain hydraudynamic drive,
With
Increase and dull decline.
For the hydraudynamic drive part,
The torque-converters rotating ratio
(9)
The velocity ratio of two pairs of gear pairs
(10)
At the free wheel device blocking, the second driven gear gear Z3 is identical all the time with the first driven gear Z4 rotating speed, namely
, can release according to formula (9), (10):
In the above-mentioned formula:
T
1, T
2, T-
3, T
4Represent respectively gear Z
1, Z
2, Z
3, Z
4Moment of torsion, n
1, n
2, n
3, n
4Represent respectively gear Z
1, Z
2, Z
3, Z
4Rotating speed, Te is the moment of torsion of motor, T
pThe moment of torsion of pump impeller,
So can sum up following rule according to formula (11):
(1) at the free wheel device blocking, the torque-converters rotating ratio
Complete velocity ratio by two pairs of gear pairs
With
Ratio determine;
(2) velocity ratio of gear pair is controlled, and the working speed of fluid torque converter ratio
Along with the gear pair velocity ratio
With
Determine and be fixed on certain a bit, no longer change;
(3) efficient of fluid torque converter
With rotating ratio
Rising and change, and a bit reach peak at certain
, can be according to self external characteristics of torque-converters the working speed of this torque-converters ratio
Be controlled at best efficiency point
Near, farthest improve system total efficiency.
The course of action of the present invention under different operating modes is as follows:
When vehicle during in the heavy-duty low-speed operating mode, the free wheel device release, the first driven gear of pump impeller and turbo tooth wheel set and the second driven gear release, power is only exported through the first gear pair by the turbine of fluid torque converter, system is pure torque-converters operating mode, guarantees the power performance of vehicle; When vehicle enters the underloading high-speed working condition, the free wheel device locking, the first driven gear of pump impeller and turbo tooth wheel set and the second driven gear locking are integrated.This moment, a part of power outputed to the second driven gear through the second gear pair rigidity of pump impeller, and another part power is through the output of transformer turbine the first gear pair, and system is the mixed flow regime of machinery and hydraulic systems.This system inherited the power character of hydraulic systems, effectively promoted simultaneously the total transmission efficiency of system.Because the mechanical efficiency transmission is high, close to 100%, it has reduced the hydraulic losses ratio from originally just having been shunted a part through the merit of fluid torque converter transmission.
Adopt technique scheme, by the combination of the speed ratio that confluxes, can optimize the present invention program's efficient.
When total number of teeth changed, the speed ratio of gear pair also can change, and is still identical with technological scheme of the present invention.
Advantage of the present invention is that the total transmission efficiency of system can obviously promote, and simple in structure, control is convenient, and application prospect is extensive.
Description of drawings
Fig. 1 is transmission principle figure of the present invention.
Fig. 2 is the total transmission efficiency of system of the present invention
With hydraudynamic drive power dividing ratio
Variation diagram.
Fig. 3 is that the present invention is confluxed the gear pair speed ratio fixedly the time
Graph of a relation.
Fig. 4 is power dividing ratio of the present invention
In the time of fixedly
Graph of a relation.
Embodiment
As shown in Figure 1, the present invention includes pump impeller P, turbine t and the guide wheel s of fluid torque converter, power is inputted from pump impeller P, pump impeller P is connected with the first gear pair Z4/Z2, turbine t output terminal is connected with the second gear pair Z3/Z1, and the first driven gear Z4 of two pairs of gear pairs and the second driven gear Z3 are by the free wheel device outputting power that confluxes; In the heavy-duty low-speed operating mode, the free wheel device release, the first driven gear Z4 of pump impeller P and turbine t gear pair and the second driven gear Z3 release, power is only exported through the first gear pair Z4/Z2 by the turbine t of fluid torque converter; During the underloading high-speed working condition, the free wheel device locking, the first driven gear Z4 of pump impeller P and turbine t gear pair and the second driven gear Z3 locking are integrated, part power outputs to the second driven gear Z3 through the second gear pair Z3/Z1 rigidity of pump impeller P, and another part power is exported through transformer turbine t the first gear pair Z4/Z2.
The operating mode of described free wheel device heavy-duty low-speed operating mode when being lower than the rotating speed of the second driven gear Z3 when the rotation speed n 4 of the first driven gear Z4; When the operating mode of underloading high-speed working condition when being higher than the rotating speed of the second driven gear Z3 when the rotation speed n 4 of the first driven gear Z4.
Example according to the technical program design one cover power dividing scheme is as follows:
(1) determine the to conflux gear pair speed ratio of mechanism:
The gear vice president number of teeth is 50, pump impeller gear pair i2=Z4/Z2=23/27 wherein, turbine output gear wheel set i1=Z3/Z1=26/24.Fluid torque converter rotating ratio i=i2/i1=0.786 in the time of can finding the solution the free wheel device locking according to formula (11), according to torque-converters primary characteristic parameter, and the efficiency eta y that utilizes interpolation to find the solution torque-converters this moment is 84.2%, close to best efficiency point.And from rotating ratio i=0.786
Operating point begins, and the total transmission efficiency η of system is along with fluid power power dividing ratio
Reduce and increase, see shown in the accompanying drawing 3.
(2) determine fluid power split ratio α:
Under certain split ratio α, can concern to control the lifting of total efficiency by the adjusting secondary speed ratio of organization gear that confluxes, the total transmission efficiency of system changes along with the variation of the speed ratio of gear pair, it for total transmission efficiency control provide may, see shown in the accompanying drawing 4.
When the general gear of gear pair was 50, the speed ratio of gear pair had multiple choices:
Work as i1=Z3/Z1=26/24, during i2=Z4/Z2=23/27, efficient is shown in the curve 1 in the accompanying drawing 4.
Work as i1=Z3/Z1=26/24, during i2=Z4/Z2=22/28, efficient is shown in the curve 2 in the accompanying drawing 4.
Work as i1=Z3/Z1=26/24, during i2=Z4/Z2=21/29, efficient is shown in the curve 3 in the accompanying drawing 4.
Above-mentioned three different embodiments show, by the combination of the speed ratio that confluxes, can optimize the present invention program's efficient.
When total number of teeth changed, the speed ratio of gear pair also can change, but technological scheme is identical with technical solution of the present invention.
The course of action of this example is as follows:
When vehicle during in the heavy-duty low-speed operating mode, the free wheel device release, the first driven gear Z4 of pump impeller P and turbine t gear pair and the second driven gear Z3 release, power is only exported through the first gear pair Z4/Z2 by the turbine t of fluid torque converter, system is pure torque-converters operating mode, guarantees the power performance of vehicle; When vehicle enters the underloading high-speed working condition, the free wheel device locking, the first driven gear Z4 of pump impeller P and turbine t gear pair and the second driven gear Z3 locking are integrated.This moment, a part of power outputed to the second driven gear Z3 through the second gear pair Z3/Z1 rigidity of pump impeller P, and another part power is through transformer turbine t the first gear pair Z4/Z2 output, and system is the mixed flow regime of machinery and hydraulic systems.This system inherited the power character of hydraulic systems, effectively promoted simultaneously the total transmission efficiency of system.Because the mechanical efficiency transmission is high, close to 100%, it has reduced the equipment hydrodynamic transmission losses and its ratio from originally just having been shunted a part through the merit of fluid torque converter transmission.
Claims (2)
1. hydraulic machine torque-converters, the pump impeller (P), turbine (t) and the guide wheel (s) that comprise fluid torque converter, power is inputted from pump impeller (P), it is characterized in that: pump impeller (P) is connected with the first gear pair (Z4/Z2), turbine (t) output terminal is connected with the second gear pair (Z3/Z1), and first driven gear (Z4) of two pairs of gear pairs and the second driven gear (Z3) are by the free wheel device outputting power that confluxes; In the heavy-duty low-speed operating mode, the free wheel device release, the first driven gear (Z4) and the second driven gear (Z3) release of pump impeller (P) and turbine (t) gear pair, power is only exported through the first gear pair (Z4/Z2) by the turbine (t) of fluid torque converter; During the underloading high-speed working condition, the free wheel device locking, pump impeller (P) is integrated with the first driven gear (Z4) and the second driven gear (Z3) locking of turbine (t) gear pair, part power outputs to the second driven gear (Z3) through the second gear pair (Z3/Z1) rigidity of pump impeller (P), and another part power is exported through transformer turbine (t) the first gear pair (Z4/Z2).
2. hydraulic machine torque-converters according to claim 1 is characterized in that: the operating mode when described free wheel device heavy-duty low-speed operating mode is lower than the rotating speed of the second driven gear (Z3) for the rotating speed (n4) as the first driven gear (Z4); When the operating mode of underloading high-speed working condition when being higher than the rotating speed of the second driven gear (Z3) when the rotating speed (n4) of the first driven gear (Z4).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310253840.4A CN103322157B (en) | 2013-06-25 | 2013-06-25 | Hydraulic mechanical torque converter |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310253840.4A CN103322157B (en) | 2013-06-25 | 2013-06-25 | Hydraulic mechanical torque converter |
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| Publication Number | Publication Date |
|---|---|
| CN103322157A true CN103322157A (en) | 2013-09-25 |
| CN103322157B CN103322157B (en) | 2016-03-30 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201310253840.4A Active CN103322157B (en) | 2013-06-25 | 2013-06-25 | Hydraulic mechanical torque converter |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106969128A (en) * | 2016-01-14 | 2017-07-21 | 熵零技术逻辑工程院集团股份有限公司 | A kind of energy adjustment system |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3258081A (en) * | 1959-09-26 | 1966-06-28 | Voith Gmbh J M | Power transmission to wheels and power take-off |
| SU1606786A1 (en) * | 1988-05-13 | 1990-11-15 | Производственное объединение "Волгоградский тракторный завод им.Ф.Э.Дзержинского" | Lockable hydraulic torque converter |
| CN101275658A (en) * | 2008-05-05 | 2008-10-01 | 四川大学 | High-efficiency hydraulic moment changeable transmission system |
| CN202017748U (en) * | 2010-12-21 | 2011-10-26 | 四川大学 | Hydraulic power and mechanical power combined transmission system |
| CN202215697U (en) * | 2011-09-16 | 2012-05-09 | 山推工程机械股份有限公司 | Structure of a hydraulic torque converter |
| CN202659774U (en) * | 2012-05-11 | 2013-01-09 | 广西柳工机械股份有限公司 | Overrunning clutch for twin-turbo hydraulic torque converter converging mechanism of loader |
-
2013
- 2013-06-25 CN CN201310253840.4A patent/CN103322157B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3258081A (en) * | 1959-09-26 | 1966-06-28 | Voith Gmbh J M | Power transmission to wheels and power take-off |
| SU1606786A1 (en) * | 1988-05-13 | 1990-11-15 | Производственное объединение "Волгоградский тракторный завод им.Ф.Э.Дзержинского" | Lockable hydraulic torque converter |
| CN101275658A (en) * | 2008-05-05 | 2008-10-01 | 四川大学 | High-efficiency hydraulic moment changeable transmission system |
| CN202017748U (en) * | 2010-12-21 | 2011-10-26 | 四川大学 | Hydraulic power and mechanical power combined transmission system |
| CN202215697U (en) * | 2011-09-16 | 2012-05-09 | 山推工程机械股份有限公司 | Structure of a hydraulic torque converter |
| CN202659774U (en) * | 2012-05-11 | 2013-01-09 | 广西柳工机械股份有限公司 | Overrunning clutch for twin-turbo hydraulic torque converter converging mechanism of loader |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106969128A (en) * | 2016-01-14 | 2017-07-21 | 熵零技术逻辑工程院集团股份有限公司 | A kind of energy adjustment system |
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|---|---|
| CN103322157B (en) | 2016-03-30 |
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Effective date of registration: 20200916 Address after: 545007 the Guangxi Zhuang Autonomous Region Liuzhou City Liu Tai Road No. 1 Co-patentee after: Liugong Liuzhou Foundry Co.,Ltd. Patentee after: GUANGXI LIUGONG MACHINERY Co.,Ltd. Address before: 545007 the Guangxi Zhuang Autonomous Region Liuzhou City Liu Tai Road No. 1 Patentee before: GUANGXI LIUGONG MACHINERY Co.,Ltd. |