CN102303518A - Power coupling device for hybrid loader - Google Patents
Power coupling device for hybrid loader Download PDFInfo
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- CN102303518A CN102303518A CN201110183725A CN201110183725A CN102303518A CN 102303518 A CN102303518 A CN 102303518A CN 201110183725 A CN201110183725 A CN 201110183725A CN 201110183725 A CN201110183725 A CN 201110183725A CN 102303518 A CN102303518 A CN 102303518A
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- 230000007246 mechanism Effects 0.000 claims description 33
- 230000009977 dual effect Effects 0.000 claims description 5
- 238000005452 bending Methods 0.000 description 12
- 239000000463 material Substances 0.000 description 12
- 230000001172 regenerating effect Effects 0.000 description 8
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Abstract
The invention discloses a power coupling device for a hybrid loader. The power coupling device is characterized by comprising a double star planet mechanism consisting of a sun gear, a planet carrier and a gear ring; the sun gear is connected with a power output shaft of engines; one end of the planet carrier is connected with a power output shaft of a driving motor and the other end of the planer carrier is connected with a driving part of a C1 clutch, and the gear ring is connected with a driving part of a C2 clutch; and driven parts of the C1 clutch and the C2 clutch are connected with a transmission input shaft. The power coupling device has the advantages that: a torque converter of the conventional loader is saved, the electric power moment conversion is realized in an electric power moment conversion mode of the hybrid loader; moreover, the working modes of the hybrid loader such as a motor driving mode, an engine driving mode, a motor assistance mode, a driving power generation mode and a regeneration brake mode and the like are realized, and flexible switching among various working modes is realized by joint control over the C1 clutch and the C2 clutch, and control over the working states of the engines and the driving motor.
Description
Technical field
The present invention relates to a kind of engineering machinery field that is used for, and particularly relates to a kind of hybrid power loader dynamic coupling device that in construction machinery and equipments such as loader, with the hybrid power technology power of drive motor and driving engine is coupled.
Background technology
Construction machinery and equipments such as loader have characteristics such as dust cycle is short, the horsepower output cyclic fluctuation is strong, driving efficiency is low, energy consumption is high, exhaust emission is serious.The hybrid power technology is particularly good at and solves this horsepower output energy-saving and emission-reduction problem of the motor device of regular fluctuation within the specific limits.
The typical condition of loader can be described as: insert material-shovel dress-lifting-unloading-no-load return trip, wherein inserting operating mode needs very big tractive force, but the speed of a motor vehicle is extremely low.The tradition loader is realized " increase and turn round reduction of speed " function through equipment turbine transformer in transmission system; The torque of driving engine is amplified several times to satisfy loader to the tractive force requirement; Along with the increase speed of a motor vehicle of tractive force constantly reduces, the speed of a motor vehicle levels off to zero when tractive force reaches maximum.This moment, driving engine was in the oepration at full load state, and rate of fuel consumption is very high, though the very big speed of a motor vehicle of the tractive force of loader is extremely low at this moment, so the net output of loader is lower, and the driving efficiency that finally shows as loader is very low.The driving efficiency of loader insertion material operating mode is low to be what to be caused in the lower characteristic of high converter torque ratio section driving efficiency by turbine transformer.In addition, because the turbine transformer of loader does not generally possess " locking " function, cause loader transportation operating mode driving system driving efficiency very low; The turbine transformer of loader does not generally possess " negative wearing " characteristic; After the tradition loader is transformed into the hybrid power loader; Be difficult to realize that the braking energy of hybrid power system reclaims function; And comprise 3 times braking procedure in the working cycle of loader at least; And the loader complete vehicle quality is huge; Be again full-time 4 wheel drive structures, its braking procedure is containing huge energy, and the hybrid power loader will be a big defective as not reclaiming braking energy.
Domesticly announced that the patent about mixed power coupling device mainly concentrates on automotive field, less and all concentrate in the transformation and energy recovery function of hydraulic efficiency pressure system about the patent of hybrid power engineering machinery.
Wherein have following two patents relevant with this patent:
1,200920099353.6 " planetary mechanism power couplers "; This utility model patent is structurally similar with the present invention; But Duoed one group of (Wet-type multi-disc) drg than the present invention; Want much loaded down with trivial details from structural arrangement and mode of operation control; And this mechanism is applied on the hybrid vehicle, is inappropriate for special applying working condition and functional characteristic in the loader field.
2,200710077643.6 " hybrid power plant for engineering machinery "; This invention profit and the present invention belong to engineering machinery field together; Realize driving engine independent drive or motor independent drive controllable function through a covering device; Adopt motor-driven in the convenient job location of inserting power supply, at the job location employing engine drive of being inconvenient to insert power supply.
Summary of the invention
The object of the invention just provides a kind of special applying working condition and functional characteristic that is suitable for the loader field; Can realize 6 kinds of mode of operations such as electric power bending moment pattern (the corresponding material operating mode of inserting), motor drive mode, engine drive pattern, motor assistant mode, driving generating and regenerative brake pattern of hybrid power loader; And, make hybrid power load the hybrid power loader dynamic coupling device that function is switched flexibly between various mode of operations through to the Engagement Control of C1 power-transfer clutch and C2 power-transfer clutch and the mode of operation control of driving engine and drive motor.
Solution of the present invention is such: the present invention has by sun wheel; The double star planetary mechanism that pinion carrier and gear ring constitute; Described sun wheel is to link to each other with the power take-off shaft of driving engine; One end of described pinion carrier is to link to each other with the power take-off shaft of drive motor; The other end of pinion carrier links to each other with the A end of C1 power-transfer clutch, and described gear ring links to each other with the A end of C2 power-transfer clutch; The secondary part of described C1 power-transfer clutch and described C2 power-transfer clutch links to each other with input shaft.
Technique scheme; Utilize the 2DOF structure of planetary mechanism to realize the specific (special) requirements that the double dynamical input of hybrid power loader-single action power is exported; And through the engaged/disengaged control of C1 power-transfer clutch and C2 power-transfer clutch and the running state control of driving engine and drive motor; Realize the electric power bending moment pattern (the corresponding material operating mode of inserting) of hybrid power loader; The engine drive pattern; Motor drive mode; Drive power generation mode; 6 kinds of mode of operations such as motor assistant mode and regenerative brake pattern satisfy the power requirement of loader to operating mode complicated and changeable.
In order to adapt to the requirement that loader drives equipment, described change-speed box is the dual output change-speed box, and one of them output shaft links to each other with steering pump with working barrel, and another output shaft links to each other with the drive axle of loader.
Advantage of the present invention is to cancel the turbine transformer of traditional loader; Utilize the electric power bending moment pattern (the corresponding material operating mode of inserting) of hybrid power loader to realize the electric power bending moment; But also can realize motor drive mode, engine drive pattern, motor assistant mode, drive the mode of operation of 6 kinds of hybrid power loaders such as generating and regenerative brake pattern, be controlled at switching flexibly between the various mode of operations through mode of operation to the Engagement Control of C1 power-transfer clutch and C2 power-transfer clutch and driving engine and drive motor.
Description of drawings
Accompanying drawing is embodiments of the invention.
Accompanying drawing 1 is a structural representation of the present invention.
Accompanying drawing 2 is the present invention's power transfer path scheme drawings at electric power bending moment pattern (inserting the material operating mode) hybrid power loader dynamic coupling device.
Accompanying drawing 3 is power transfer path scheme drawings of hybrid power loader dynamic coupling device under motor drive mode of the present invention and the regenerative brake pattern.
Accompanying drawing 4 is engine drive pattern of the present invention, the power transfer path scheme drawing that drives hybrid power loader dynamic coupling device under power generation mode and the motor assistant mode.
Accompanying drawing 5 is mode of operations of explanation mode of operation of the present invention and associated components.
The specific embodiment
Each label is detailed as follows in the accompanying drawing:
The 1-drive motor; The 2-sun wheel; The 3-driving engine; The 4-engine power output shaft; 5-drive motor rotor; 6-drive motor power take-off shaft; 7-planetary mechanism dynamic coupling device; The 8-gear ring; The 9-pinion carrier; The 10-C1 power-transfer clutch; The 11-C2 power-transfer clutch; The 12-input shaft; The 13-change-speed box; The 14-working barrel; The 15-steering pump; The 16-inner planet gear; The 17-exterior epicyclic gear; 18-double star planetary mechanism; The virtual lever of 19-planetary mechanism rotating speed; The stressed motion analysis figure of 20-dual planetary gear mechanism; The torque of 21-pinion carrier; 22-pinion carrier rotating speed; 23-pinion carrier torque/speed coordinate axle; 24-gear ring torque/speed coordinate axle; 25-sun wheel torque/speed coordinate axle; The torque of 26-gear ring; 27-gear ring rotating speed; 28-sun wheel rotating speed; The torque of 29-sun wheel; 30-motor power output shaft; The drive axle of 31-loader
The present invention has by sun wheel 2; The double star planetary mechanism 18 of pinion carrier 9 and gear ring 8 formations; Described sun wheel 2 is to link to each other with engine power output shaft 4; One end of described pinion carrier 9 is to link to each other with drive motor power take-off shaft 6; The other end of pinion carrier 9 links to each other with the A end of C1 power-transfer clutch 10, and described gear ring 8 links to each other with the A end of C2 power-transfer clutch 11; The secondary part of described C1 power-transfer clutch 10 and described C2 power-transfer clutch 11 links to each other with input shaft 12.
Described sun wheel 2 is to be meshed with inner planet gear 16, and inner planet gear 16 is to be meshed with exterior epicyclic gear 17, and all on pinion carrier 9, exterior epicyclic gear 17 is to be meshed with gear ring 8 to the center of gyration of inner planet gear 16 and exterior epicyclic gear 17.
Should drive the requirement that driving system drives equipment again in order to adapt to loader, described change-speed box is the dual output change-speed box, and one of them output shaft links to each other with steering pump 15 with working barrel 14, and another output shaft links to each other with the drive axle 31 of loader.
This power connection mode can realize 6 kinds of mode of operations such as electric power bending moment pattern (the corresponding material operating mode of inserting), motor drive mode, engine drive pattern, motor assistant mode, driving generating and regenerative brake pattern of hybrid power loader; And, make the hybrid power loader can switch to more energy-conservation mode of operation fast through the Engagement Control of C1 power-transfer clutch 10 and C2 power-transfer clutch 11 and the mode of operation of driving engine 3 and drive motor 1 are controlled at switching flexibly between the various drive patterns.
Describe a working example of the present invention in detail below in conjunction with accompanying drawing.
1, electric power bending moment pattern (inserting the material operating mode)
As shown in Figure 2, electric power bending moment pattern requires C1 power-transfer clutch 10 to separate, and C2 power-transfer clutch 11 engages, and driving engine 3 drives, drive motor 1 counter-rotating generating, and the mode of operation of each parts is shown in accompanying drawing 5.This moment, the double star planetary mechanism 18 of dynamic coupling device was in the 2DOF state, and it is stressed, motion and power transmission characteristic analysis are following:
The core component of dynamic coupling device is the double star planetary mechanism 18 among Fig. 2, and each member rotating speed of this mechanism and torque relation are shown in the formula of (1) (2):
（1）
- the sun wheel speed, that is, the engine speed;
- planet carrier rotational speed, the rotational speed of the motor is driven;
- ring gear speed, assuming the power coupling device output speed;
The rotating speed coincidence formula (1) of 3 members of double star planetary mechanism 18, the total in-line of node in Fig. 2 on 3 virtual levers 19 of member rotating speed planetary mechanism rotating speed of expression.
- the carrier torque is the torque drive motor;
The torque coincidence formula (2) of 3 members of double star planetary mechanism 18; In Fig. 2,3 suffered " torques " of member on the virtual lever 19 of planetary mechanism rotating speed are regarded as as acting on " power " on the lever; " distance " between 3 mechanism's torques (21,26,29) regarded " arm of force " as lever as; Be " fulcrum " then with any point; The long-pending lever balance theory that satisfies of other 2 " power " value and " arm of force " value, therefore virtual lever concerns it is instrument easily for the rotating speed of analyzing planetary mechanism and torque.
Ignoring under the friction situation, the horsepower input that gets the double star planetary mechanism according to the power balance principle equals horsepower output, that is:
The propulsion source output torque of loader is determined that by load the present invention is in electric power bending moment pattern (inserting the material operating mode), and the suffered pull-up torque of loader has determined the torque of driving engine and motor, and (2) formula is deformed into (4) formula and (5) formula:
Namely: the output torque of the engine 3 loaders traction torque
times, the equivalent of seven planetary bodies power coupling device amplifies the engine's torque
times.Meanwhile, the role of the torque to the drive motor 5 is loaders traction torque
times.
(1) formula is deformed into the form of representing engine speed with gear ring 8 rotating speeds and motor speed:
(4) (5) (6) formula substitutions (3) formula is got
（7）
(7) Average number of the first term on the left of the output power of the engine 3; No. 2 to drive the power output of the motor 1, 2 in Figure 22 shows the carrier rotational speed, the motor speed is negative, the motor speed moments (
) is positive, a drive motor power is negative at this time, the power generation state; equal right as loaders output power.
Can know by formula (7); Be divided into two parts at electric power bending moment pattern (inserting the material operating mode) driving engine 3 power; A part is used to drive loader and overcomes the resistance that inserts material, reduces to " 0 " with low speed driving until the speed of a motor vehicle, this moment loader insertion resistance maximum but driving power is " 0 "; Another part drags the 5 counter-rotating generatings of drive motor rotor; Generated output is " 0 " during beginning; Along with the increase of inserting resistance and the reduction generated output of the speed of a motor vehicle constantly increase, generated output reached maximum when the speed of a motor vehicle was reduced to " 0 ", that is: the whole power of driving engine 3 usefulness are used to drag drive motor 1 generating.The dotted line position of corresponding virtual lever 16 during electric power bending moment pattern among Fig. 2 (inserting the material operating mode) beginning; Sun wheel rotating speed 28 (corresponding engine speed) remains unchanged; Pinion carrier rotating speed 22 (corresponding drive motor counter-rotating generating rotating speed) constantly raises (negative value); Gear ring rotating speed 28 (the corresponding loader speed of a motor vehicle) constantly reduces; The gear ring rotating speed will be " 0 " when inserting the end of material operating mode; The power of driving engine 3 is driven motor 1 fully and absorbs, and this moment, drive motor 1 generated output reached maximum.Electric power bending moment pattern effectively utilizes the torque that planetary mechanism has amplified driving engine 3, has cancelled turbine transformer, the hydraulic loss of having avoided traditional loader to be caused by turbine transformer.
2, motor drive mode
Shown in accompanying drawing 5, when the state-of-charge (SOC) of (like operating modes such as transportations) and closed-center system was higher when loader power drive system load is low, then the hybrid power loader got into motor drive mode.As shown in Figure 3, motor drive mode requires C1 power-transfer clutch 10 to engage, and C2 power-transfer clutch 11 separates, tail-off, and drive motor 1 is in driving condition.The power of drive motor rotor 5 is through 6 outputs of drive motor power take-off shaft; Be passed on the pinion carrier 9 of double star planetary mechanism 18; Pinion carrier 9 is again with the A end of transmission of power to C1 power-transfer clutch 10; Because C1 power-transfer clutch 10 engages; Power is passed to input shaft 12 through the secondary part of C1 power-transfer clutch 10, finally drives the drive axle 31 of working barrel 14, steering pump 15 and the loader of loader.
3, engine drive pattern
Shown in accompanying drawing 5, when the loader power system was in moderate duty, then the hybrid power loader got into the engine drive pattern.As shown in Figure 4, the engine drive pattern requires C1 power-transfer clutch 10 to engage, and C2 power-transfer clutch 11 also engages; Double star planetary mechanism 18 degenerates into the rigid body of a single degree of freedom, only plays transferring power, and driving engine 3 drives; Drive motor 1 outage, 5 idle running of drive motor rotor.The power of driving engine 3 is through engine power output shaft 4 outputs; Be passed on the sun wheel 2 of double star planetary mechanism 18; Sun wheel 2 drives whole double star planetary mechanism 18 and rotates with speed; And power is passed to the A end of C1 power-transfer clutch 10 from pinion carrier 9; Be passed to the A end of C2 power-transfer clutch 11 from gear ring 8; Because C1 power-transfer clutch 10, C2 power-transfer clutch 11 all engage; Power is passed to input shaft 12 through the secondary part of C1 power-transfer clutch 10, C2 power-transfer clutch 11, drives the drive axle 31 of working barrel 14, steering pump 15 and the loader of loader.
4, drive power generation mode
Shown in accompanying drawing 5, when the SOC of (like operating modes such as transportations) and closed-center system was low when loader power drive system load is low, then the hybrid power loader got into and drives power generation mode.As shown in Figure 4, drive power generation mode and require C1 power-transfer clutch 10 to engage, C2 power-transfer clutch 11 also engages, and double star planetary mechanism 18 degenerates into the rigid body of a single degree of freedom, only plays the effect of transferring power, and driving engine 3 drives, drive motor 1 generating.The power of driving engine 3 is through engine power output shaft 4 outputs; Be passed on the sun wheel 2 of double star planetary mechanism 18; Sun wheel 2 drives whole double star planetary mechanism 18 and rotates with speed; And with the power separated into two parts of driving engine 3; A part is passed to drive motor rotor 5 through pinion carrier 9 and drags drive motor 1 generating, and the SOC of closed-center system is improved fast; Another part power is passed to input shaft 12 through C1 power-transfer clutch 10 and C2 power-transfer clutch 11, drives the drive axle 31 of working barrel 14, steering pump 15 and the loader of loader.
5, motor assistant mode
Shown in accompanying drawing 5, when the loader power drive system is loaded when higher, and the SOC of closed-center system is when sufficient, and the hybrid power loader gets into the motor assistant mode.As shown in Figure 4, the motor assistant mode requires C1 power-transfer clutch 10 to engage, and C2 power-transfer clutch 11 also engages, and double star planetary mechanism 18 degenerates into the rigid body of a single degree of freedom, only plays the effect of transferring power, and driving engine 3 all is in driving condition with drive motor 1.The power of driving engine 1 is through engine power output shaft 4 outputs; Be passed on the sun wheel 2 of double star planetary mechanism 18; The power of drive motor rotor 5 is through drive motor power take-off shaft 6; Be passed on the pinion carrier 9 of double star planetary mechanism 18; Power on the double star planetary mechanism 18 is from pinion carrier 9 and gear ring 8 outputs; Be passed to input shaft 12 through C1 power-transfer clutch 10 and C2 power-transfer clutch 11, drive the drive axle 31 of working barrel 14, steering pump 15 and the loader of loader.
6, regenerative brake pattern
Shown in accompanying drawing 5, when being lower than, goes up in limited time the SOC of loader braking and closed-center system, and then the hybrid power loader gets into the regenerative brake pattern.As shown in Figure 3, the regenerative brake pattern requires C1 power-transfer clutch 10 to engage, and C2 power-transfer clutch 11 separates, and tail-off (or idling), drive motor rotor 5 are in just transmits electricity condition.Lock torque on the loader wheel reaches input shaft 12 after the transmission system speedup at this moment; C1 power-transfer clutch 10 is in engagement state at this moment; Lock torque reaches pinion carrier 9 through C1 power-transfer clutch 10 and drags drive motor power take-off shaft 6; And then drag drive motor rotor 5 generating, with the kinetic energy on the wheel be converted into electrical power storage in the closed-center system with subsequent use.This moment, the dual planetary gear planetary mechanism of dynamic coupling device was in the single degree of freedom state.
Claims (3)
1. hybrid power loader dynamic coupling device; It is characterized in that having by sun wheel (2); The dual planetary gear planetary mechanism that pinion carrier (9) and gear ring (8) constitute; Described sun wheel (2) is to link to each other with the power take-off shaft (4) of driving engine (3); One end of described pinion carrier (9) is to link to each other with the power take-off shaft (6) of drive motor (1); The other end of pinion carrier (9) links to each other with the A end of C1 power-transfer clutch (10), and described gear ring (8) links to each other with the A end of C2 power-transfer clutch (11); The secondary part of described C1 power-transfer clutch (10) and described C2 power-transfer clutch (11) links to each other with input shaft (12).
2. hybrid power loader dynamic coupling device according to claim 1; It is characterized in that described sun wheel (2) is to be meshed with inner planet gear (16); Inner planet gear (16) is to be meshed with exterior epicyclic gear (17); All on pinion carrier (9), exterior epicyclic gear (17) is to be meshed with gear ring (8) to the center of gyration of inner planet gear (16) and exterior epicyclic gear (17).
3. hybrid power loader dynamic coupling device according to claim 1; It is characterized in that described change-speed box is the dual output change-speed box; One of them output shaft links to each other with steering pump (15) with working barrel (14), and another output shaft links to each other with the drive axle (31) of loader.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201110183725A CN102303518A (en) | 2011-07-01 | 2011-07-01 | Power coupling device for hybrid loader |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201110183725A CN102303518A (en) | 2011-07-01 | 2011-07-01 | Power coupling device for hybrid loader |
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| CN201110183725A Pending CN102303518A (en) | 2011-07-01 | 2011-07-01 | Power coupling device for hybrid loader |
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Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2014023070A1 (en) * | 2012-08-07 | 2014-02-13 | 福建省福工动力技术股份公司 | Hybrid car braking energy recovery device and method based on motor controllable speed-raising |
| CN104999902A (en) * | 2015-07-06 | 2015-10-28 | 吉林大学 | Hybrid driving system with three-clutch automatic transmission and control method thereof |
| CN106545637A (en) * | 2016-10-31 | 2017-03-29 | 广西柳工机械股份有限公司 | Power distributes regulating system and loading machine dynamical system |
| CN108790775A (en) * | 2018-07-13 | 2018-11-13 | 天津工程机械研究院有限公司 | A kind of oil electric mixed dynamic loading machine transmission device |
| CN112937531A (en) * | 2021-03-30 | 2021-06-11 | 柳工柳州传动件有限公司 | Service braking system and method for engineering machinery |
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| CN201003577Y (en) * | 2006-12-27 | 2008-01-09 | 上海汽车股份有限公司 | Drive system of hybrid electric vehicle |
| CN201400082Y (en) * | 2009-03-12 | 2010-02-10 | 佳木斯大学 | Planetary mechanism power coupler |
| CN201627216U (en) * | 2009-12-23 | 2010-11-10 | 三一重工股份有限公司 | Hybrid backhoe loader |
-
2011
- 2011-07-01 CN CN201110183725A patent/CN102303518A/en active Pending
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN201003577Y (en) * | 2006-12-27 | 2008-01-09 | 上海汽车股份有限公司 | Drive system of hybrid electric vehicle |
| CN201400082Y (en) * | 2009-03-12 | 2010-02-10 | 佳木斯大学 | Planetary mechanism power coupler |
| CN201627216U (en) * | 2009-12-23 | 2010-11-10 | 三一重工股份有限公司 | Hybrid backhoe loader |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2014023070A1 (en) * | 2012-08-07 | 2014-02-13 | 福建省福工动力技术股份公司 | Hybrid car braking energy recovery device and method based on motor controllable speed-raising |
| CN104999902A (en) * | 2015-07-06 | 2015-10-28 | 吉林大学 | Hybrid driving system with three-clutch automatic transmission and control method thereof |
| CN104999902B (en) * | 2015-07-06 | 2017-12-12 | 吉林大学 | Hybrid electric drive system and control method with three clutch automatic gearboxes |
| CN106545637A (en) * | 2016-10-31 | 2017-03-29 | 广西柳工机械股份有限公司 | Power distributes regulating system and loading machine dynamical system |
| CN108790775A (en) * | 2018-07-13 | 2018-11-13 | 天津工程机械研究院有限公司 | A kind of oil electric mixed dynamic loading machine transmission device |
| CN112937531A (en) * | 2021-03-30 | 2021-06-11 | 柳工柳州传动件有限公司 | Service braking system and method for engineering machinery |
| CN112937531B (en) * | 2021-03-30 | 2023-01-03 | 柳工柳州传动件有限公司 | Service braking system and method for engineering machinery |
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Application publication date: 20120104 |