CN101439668A - Single motor hybrid automobile power drive mechanism based on planetary gear train - Google Patents

Single motor hybrid automobile power drive mechanism based on planetary gear train Download PDF

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Publication number
CN101439668A
CN101439668A CNA2007101503775A CN200710150377A CN101439668A CN 101439668 A CN101439668 A CN 101439668A CN A2007101503775 A CNA2007101503775 A CN A2007101503775A CN 200710150377 A CN200710150377 A CN 200710150377A CN 101439668 A CN101439668 A CN 101439668A
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CN
China
Prior art keywords
shaft
motor
tween drive
drive shaft
planetary gear
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Pending
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CNA2007101503775A
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Chinese (zh)
Inventor
袁庆强
赵春明
吴志新
马宁
李磊
余楚礼
窦汝振
范京
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QINGYUAN ELECTRIC VEHICLE CO Ltd TIANJIN
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QINGYUAN ELECTRIC VEHICLE CO Ltd TIANJIN
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Priority to CNA2007101503775A priority Critical patent/CN101439668A/en
Publication of CN101439668A publication Critical patent/CN101439668A/en
Pending legal-status Critical Current

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Abstract

The invention relates to a hybrid vehicle driving mechanism based on a planetary gear train, consisting of a planetary gear train; a sun wheel of the planetary gear train is provided with a central axis which is connected with an output shaft of a power source, a planet frame of the planetary gear train is a power output shaft of the driving mechanism, a gear ring of the planetary gear train is provided with a gear pair connected with a preposing intermediate shaft, the power output shaft is provided with a gear pair connected with a post-positioned intermediate shaft, and a motor shaft is provided with transmission shafts respectively connected with the preposing intermediate shaft and the post-positioned intermediate shaft; electronic control clutches are arranged between the transmission shafts and the preposing intermediate shaft as well as the post-positioned intermediate shaft, and a shaft brake is positioned on the preposing intermediate shaft. The driving mechanism leads the power source to be coupled with the power of a motor by the planetary gear train, and can cause the direct corresponding relations between the operating points of an engine and whole vehicle speed to be separated from each other, thus conveniently realizing optimal control for the working efficiency of the engine. Compared with the existing hybrid vehicle driving mechanism applying the planetary gear train, the invention has the remarkable advantages simpler structure.

Description

A kind of single motor hybrid automobile power drive mechanism based on planet circular system
Technical field
The invention belongs to the double-driving automobile drive system, particularly relate to a kind of single motor hybrid automobile power drive mechanism based on planet circular system.
Background technology
Hybrid vehicle generally adopts the common drive scheme that drives of single motor or double-motor and driving engine at present.Double-motor scheme cost is higher, single motor scheme generally is connected with engine crankshaft motor by power-transfer clutch, change-speed box or direct mechanical, when starting or quickening, motor can provide extra torque like this, slow down or glancing impact, the braking energy recovery can be used for generating electricity.But the engine speed of this pattern is along with the speed of a motor vehicle changes, and this just makes the operation point of driving engine select to be restricted, and has increased difficulty for further controlling engine behavior.
Summary of the invention
The objective of the invention is to follow the technical matters that the car load driving cycle changes, and disclose a kind of single motor hybrid automobile power drive mechanism based on planet circular system in order to overcome engine working point.
The present invention takes following technical scheme for achieving the above object: this driver train is made up of planet circular system, the sun wheel of its planet circular system is provided with center shaft, described center shaft is connected with the output shaft of propulsion source, the pinion carrier of planet circular system is connected with the power take-off shaft of this driver train, the gear ring of planet circular system is provided with the gear pair that connects preposition tween drive shaft, power take-off shaft is provided with the gear pair that connects rearmounted tween drive shaft, motor shaft is provided with the transmission shaft that connects preposition tween drive shaft and rearmounted tween drive shaft respectively, be provided with electric control clutch between each transmission shaft and preposition tween drive shaft and the rearmounted tween drive shaft, preposition tween drive shaft is provided with shaft brake.
The present invention can also take following technical measures:
Described planet circular system, its gear ring is provided with the hollow shaft that is set in power take-off shaft, and hollow shaft is provided with the gear pair that connects preposition tween drive shaft.
Described motor is the both-end spindle motor, and each end axle of motor is provided with the transmission shaft that connects preposition tween drive shaft and rearmounted tween drive shaft respectively, is provided with coupler between each transmission shaft and pairing preposition tween drive shaft or the rearmounted tween drive shaft.
Described motor is single-ended spindle motor, and motor shaft is provided with the driving gear of commutating tooth wheel set, and each transmission shaft that connects preposition tween drive shaft and rearmounted tween drive shaft respectively is connected in corresponding driven gear.
Described sun wheel is provided with between its center shaft and the propulsion source output shaft and slows down or speed increasing mechanism.
Described power take-off shaft is provided with change-speed box.
Beneficial effect of the present invention and advantage are: in this driver train, the power of propulsion source and the power of motor are coupled by planet circular system, when needs improve the torque of power take-off shaft, by electric control clutch motor is connected with the power take-off shaft pinion carrier, the electric energy of electrokinetic cell is changed into kinetic energy output to power take-off shaft so that additional torque to be provided.During brake snub, motor is connected with power take-off shaft by electric control clutch becomes electrical generator, and kinetic energy is changed into electrical power storage in electrokinetic cell.This driver train can make the operation point of driving engine and the direct corresponding relation of the car load speed of a motor vehicle be separated, thereby realizes the optimal control to engine operation efficient easily.In other words, when the torque of power take-off shaft demand changed, motor promptly was connected with gear ring, satisfied the variation of speed/torque by motor output, thereby helped stablizing the operation point of driving engine.This driver train only is provided with the shaft brake of indirectly-acting in gear ring, utilize existing whole-control system can be easily between different operating mode patterns such as pure electronic, in parallel, traditional mode, to switch, compare with the existing hybrid automobile power drive mechanism of using planet circular system and have the better simply outstanding advantage of structure.
Description of drawings
Accompanying drawing 1 is the embodiment of the invention 1 a structural profile scheme drawing.
Accompanying drawing 2 is structural representations of embodiment shaft brake
Accompanying drawing 3 is the embodiment of the invention 2 structural profile scheme drawings.
Accompanying drawing 4 is principle of the invention scheme drawings.
Accompanying drawing 5 is that embodiment operating mode 1 can flow diagram.
Accompanying drawing 6 is that embodiment operating mode 2 can flow diagram.
Accompanying drawing 7 is that embodiment operating mode 3 can flow diagram.
Accompanying drawing 8 is that embodiment operating mode 4 can flow diagram.
Accompanying drawing 9 is that embodiment operating mode 5 can flow diagram.
Accompanying drawing 10 is that embodiment operating mode 6 can flow diagram.
Accompanying drawing 11 is that embodiment operating mode 7 can flow diagram.
Accompanying drawing 12 is that embodiment operating mode 8 can flow diagram.
Accompanying drawing 13 is car load control flow charts.
Number in the figure: 1 sun wheel center shaft, 2 sun wheels, 3 pinion carriers, 4 gear rings, 5 gear ring hollow shafts, 6 gear pairs, 7 power take-off shafts, electric control clutch before the 8 rearmounted tween drive shafts, 9a, electric control clutch behind the 9b, 10 rearmounted transmission shafts, 11 coupler, 12 motors, 12-1 commutating tooth wheel set, 13 preposition transmission shafts, 14 shaft brakes, 14-1 housing, 14-2 brake collar, 14-3 adjusts screw rod, 14-4 electromagnetic servo box, 14-4-1 push rod, 14-5 lever, the 14-6 push rod, 14-7 lug, 15 preposition tween drive shafts, 16 bodies.
The specific embodiment
Further specify the present invention below in conjunction with embodiment and accompanying drawing thereof.
Embodiment 1 as shown in Figure 1, is provided with the motor 12 of planet circular system and both-end axle in the body 16.The sun wheel 2 of planet circular system is provided with sun wheel center shaft 1, and its axle head can be connected in mechancocaloric propulsion source output shafts such as comprising conventional engine, rotating combustion engine, automotive gas turbine, steam engine via existing deceleration or speed increasing mechanism.
The pinion carrier 3 of planet circular system is connected with the power take-off shaft 7 of this driver train, and power take-off shaft 7 is connected with change-speed box (not shown) of the prior art.
The gear ring 4 of planet circular system is provided with the hollow shaft 5 that is set in power take-off shaft 7, and hollow shaft 5 is provided with the gear pair 6 that connects preposition tween drive shaft 15.
Power take-off shaft 7 rearward end are provided with the gear pair 5 that connects rearmounted tween drive shaft 8.
Motor 12 is both-end spindle motors, and its each end axle connects preposition transmission shaft 13 and rearmounted transmission shaft 10 via coupler 11 respectively.Preposition transmission shaft 13 is connected preposition tween drive shaft 15 and rearmounted tween drive shaft 8 via preceding electric control clutch 9a, back electric control clutch 9b respectively with rearmounted transmission shaft 10.The electric control clutch 9 of present embodiment adopts existing parts.
Preposition tween drive shaft 15 is provided with shaft brake 14, and present embodiment adopts the electromagnetic type shaft brake, and its structure is seen Fig. 2.
As shown in Figure 2, the electromagnetic type shaft brake by housing 14-1, be fixed in the electromagnetic servo box 14-4 of housing, the brake collar 14-2 of ring-type in the housing and constitute, brake collar 14-2 two ends are provided with lug 14-7, one end lug engages with the adjustment screw rod 14-3 of housing 14-1, other end lug engages with push rod 14-6, between the push rod 14-4-1 of electromagnetic servo box 14-4 and the push rod 14-6 lever 14-5 is set.Adjust the gap that screw rod 14-3 is used for adjusting the preposition tween drive shaft of brake collar 14-2 and brake collar, the braking of electromagnetic servo box 14-4 and push rod 14-4-1 thereof, lever 14-5 and push rod 14-6 execution whole-control system, release order.
Embodiment 2 as shown in Figure 3, are provided with the motor 12 of planet circular system and single-ended axle in the body 16.Because embodiment 2 adopts the motor of single-ended axle, so motor shaft is different with being connected with embodiment 1 of preposition transmission shaft 13 and rearmounted transmission shaft 10, and other structure is identical with embodiment 1.Below only narrated with regard to different motor shaft connecting bridge, other content no longer Zi, one of the lunar mansions is stated.
Among Fig. 3, the motor shaft of the motor 12 of single-ended axle is provided with commutating tooth wheel set 12-1, and it is made of a driving bevel gear and two driven bevel pinions, and motor shaft is connected in driving bevel gear, and preposition transmission shaft 13 is connected with driven bevel pinion respectively with rearmounted transmission shaft 10.
The control principle of Fig. 1,3 embodiment is illustrated according to Fig. 4 and in conjunction with Fig. 5-12, is the planet circular system of this driver train in the frame of broken lines of Fig. 4, and the power of propulsion source output is drawn from 1 introducing of sun wheel center shaft, power take-off shaft 7.
For the planet circular system that this driver train adopted, the kinematic relation of its each several part is as follows:
Ns+K×Nr-(1+K)×Nc＝0 (1)
In the formula (1), Ns is the rotating speed of sun wheel, and Nr is the rotating speed of gear ring, and Nc is the rotating speed of pinion carrier, and K is the ratio of number of teeth of gear ring and sun wheel, and its implication of each parameter that relates to below this paper is identical with formula 1.
The planet circular system torque transmitted is closed:
Ts = 1 K Tr = 1 K + 1 Tc - - - ( 2 )
In the formula (2), Tr is the torque on the gear ring; Ts is the torque on the sun wheel, and Tc is the torque on the pinion carrier, and K is the ratio of number of teeth of gear ring and sun wheel, and its implication of each parameter that relates to below this paper is identical with formula 2.
The control combination of each controllable component can be satisfied the requirement of the various operating mode patterns of hybrid vehicle in this driver train, is specifically described as follows:
Operating mode 1 shown in Fig. 4,5: electric control clutch 9b combination, electric control clutch 9a disconnects, and motor shaft and pinion carrier 3 link, and sun wheel 2 is not rotated, gear ring 4 servo-actuateds.At this moment, the electric energy of electrokinetic cell changes into kinetic energy, and the torque major part of motor output passes to power take-off shaft 7, and few part is used for overcoming the torque of external propulsion source self inertia, and this driver train kinematic relation formula is as follows:
Ns＝0
K×Nr-(1+K)×Nc＝0
Under this operating mode, car load is in electric-only mode, can flow as shown in Figure 5 under this operating mode.
Operating mode 2 shown in Fig. 4,6: electric control clutch 9b combination, electric control clutch 9a disconnects, and motor shaft and pinion carrier 3 link, shaft brake 14 braking modes, gear ring 4 does not rotate, and sun wheel 2 is by motor-driven.At this moment, the electric energy of electrokinetic cell changes into when kinetic energy passes to power take-off shaft 7 and drives sun wheel center shaft 1, and its driver train kinematic relation formula is as follows:
Nr＝0
Ns-(1+K)×Nc＝0
Ts = 1 K Tr = 1 K + 1 Tc
Under this operating mode, car load is in start the engine pattern in electronic the travelling, and can flow as shown in Figure 6 under this operating mode.
Operating mode 3 shown in Fig. 4,7: electric control clutch 9b combination, electric control clutch 9a disconnects, and motor shaft and pinion carrier 3 link, shaft brake 14 braking modes, gear ring 4 does not rotate, and sun wheel 2 is by external drive power source.At this moment, power is provided for simultaneously power take-off shaft 7 by motor and external propulsion source, its driver train kinematic relation formula is as follows:
Nr＝0
Ns-(1+K)×Nc＝0
Ts = 1 K Tr = 1 K + 1 Tc
Under this operating mode, car load is in combination drive acceleration, climbing pattern, can flow as shown in Figure 7 under this operating mode.
Operating mode 4 shown in Fig. 4,8: electric control clutch 9b combination, electric control clutch 9a disconnects, motor shaft and pinion carrier 3 link, sun wheel 2 is not rotated, gear ring 4 servo-actuateds, this moment, motor changed into electric energy to battery charge as electrical generator axle 7 kinetic energy that output power, and provided braking torque to power take-off shaft 7, and its driver train kinematic relation formula is as follows:
Ns＝0
K×Nr-(1+K)×Nc＝0
Under this operating mode, car load is in the brake snub power generation mode, can flow as shown in Figure 8 under this operating mode.
Operating mode 5 shown in Fig. 4,9: electric control clutch 9b disconnects, electric control clutch 9a combination, motor shaft and pinion carrier 3 link, sun wheel 2 is by external drive power source, shaft brake 14 braking modes, be power take-off shaft 7 be forced to the braking, this moment external drive power source electric power generation, its driver train kinematic relation formula is as follows:
Nc＝0
Ns+K×Nr＝0
Ts = 1 K Tr = 1 K + 1 Tc
Under this operating mode, car load is in the parking power generation mode, can flow as shown in Figure 9 under this operating mode.
Operating mode 6 shown in Fig. 4,10: electric control clutch 9b disconnects, electric control clutch 9a combination, and motor shaft and gear ring 4 link, and sun wheel 2 is by external drive power source.Power and power take-off shaft 7 power demands that this moment, external propulsion source provided are almost equal, but when the power that provides when external propulsion source is slightly larger than power take-off shaft 7 power demands, motor is operated in generator mode by external drive power source, and its driver train kinematic relation formula is as follows:
Ns+K×Nr-(1+K)×Nc＝0
Ts = 1 K Tr = 1 K + 1 Tc
Under this operating mode, car load is in the cruise stabilization driving mode, can flow as shown in figure 10 under this operating mode.
Operating mode 7 shown in Fig. 4,11: electric control clutch 9b disconnects, electric control clutch 9a combination, and motor shaft and gear ring 4 link, and sun wheel 2 is by external drive power source.Power and power take-off shaft 7 power demands that this moment, external propulsion source provided are almost equal, but when the power that provides when external propulsion source is slightly less than power take-off shaft 7 power demands, motor gives power take-off shaft 7 supplemental capacities poor, under its driver train kinematic relation formula condition:
Ns+K×Nr-(1+K)×Nc＝0
Ts = 1 K Tr = 1 K + 1 Tc
Under this operating mode, car load is in the cruise stabilization driving mode, can flow as shown in figure 11 under this operating mode.
Operating mode 8 shown in Fig. 4,12: electric control clutch 9b disconnects, electric control clutch 9a combination, and shaft brake 14 braking modes, motor is not worked, and sun wheel 2 is by external drive power source.At this moment, the independent outputting power of external propulsion source is given power take-off shaft 7, under its driver train kinematic relation formula condition:
Nr＝0
Ns-(1+K)×Nc＝0
Ts = 1 K Tr = 1 K + 1 Tc
Car load is in external propulsion source traditional working mode under this operating mode, can flow as shown in figure 12 under this operating mode.
Below the control process that this hybrid power driving mechanism is applied on the automobile illustrates power complex method under the above-mentioned operating mode.In control process was analyzed, external propulsion source was specially driving engine.
As shown in figure 13, the signal that whole-control system transmits according to motor, battery, driving engine, car load is judged driver intention, whole vehicle state and power take-off shaft payload, and vehicle is switched between electric-only mode, hybrid mode and traditional mode.
(1) selection of electric-only mode:
As automobile power cell SOC during greater than a certain setting value, send enabled instruction at chaufeur, automotive operation speed is less than a certain setting value, and power is less than under arbitrary situations such as a certain setting value, and automobile works in electric-only mode.Logical expression is as follows:
[(Preq≤P0)∪(Vreq≤V0)]∩(SOC≥SOC0)
P in the formula ReqBe the actual driving power of car load, P0 is a certain setting lower-wattage, V ReqBe automobile real-world operation speed, V0 be a certain setting than low velocity, SOC is the current energy storage state of electrokinetic cell, SOC0 is a certain setting electrokinetic cell energy storage higher limit, following formula same-sign implication is identical therewith.
(2) selection of charge mode:
When car load stopped, SOC was lower than a certain setting value, and perhaps car deceleration or braking when required power is zero, works in energy recovery (charging) pattern.Logical expression is as follows:
SOC<SOC1
Preq≤0
SOC1 is for setting electrokinetic cell energy storage lower limit.
(3) selection of combination drive aero mode:
When the required torque of automobile when stablizing that driving engine can provide under the speed-regulating mode maximum torque and this moment, electrokinetic cell SOC was greater than a certain setting value, automobile works in combination drive pattern (accelerating mode).Logical expression is as follows:
(Treq≥T1)∩(SOC≥SOC1)
T1 stablizes driving engine maximum torque value under the speed-regulating mode for being set in the formula.
(4) selection of combination drive speed-regulating mode:
When the required torque of automobile stablize the maximum torque that driving engine can provide under the speed-regulating mode less than setting, and SOC is greater than setting electrokinetic cell energy storage lower limit, during less than a certain setting electrokinetic cell energy storage higher limit; Perhaps the speed of a motor vehicle is greater than a certain setting value, and SOC is when setting electrokinetic cell energy storage lower limit and need charge, and automobile works in stablizes the speed governing hybrid mode.Logical expression is as follows:
(Treq≤T1)∩(SOC1≤SOC≤SOC0)
Perhaps (∩ of V 〉=V1) (SOC≤SOC0)
Wherein, V1 is the lower velocity limit that automobile enters the cruising state.
(5) selection of traditional working mode:
But to be lower than energy storage lower limit, accumulator electric-quantity normal but automotive operation requires have optimum efficiency, automobile to work in the engine drive pattern in the cruising situation satisfying combination drive condition battery electric quantity.Logical expression is as follows:
(Treq≥T1)∩(SOC≤SOC0)。

Claims (7)

1, a kind of single motor hybrid automobile power drive mechanism based on planet circular system, formed by planet circular system, it is characterized in that: the sun wheel of planet circular system is provided with center shaft, described center shaft is connected with the output shaft of propulsion source, the pinion carrier of planet circular system is connected with the power take-off shaft of this driver train, the gear ring of planet circular system is provided with the gear pair that connects preposition tween drive shaft, power take-off shaft is provided with the gear pair that connects rearmounted tween drive shaft, motor shaft is provided with the transmission shaft that connects preposition tween drive shaft and rearmounted tween drive shaft respectively, be provided with electric control clutch between each transmission shaft and preposition tween drive shaft and the rearmounted tween drive shaft, preposition tween drive shaft is provided with shaft brake.
2, hybrid automobile power drive mechanism according to claim 1 is characterized in that.
3, hybrid automobile power drive mechanism according to claim 1 is characterized in that: described planet circular system, and its gear ring is provided with the hollow shaft that is set in power take-off shaft, and hollow shaft is provided with the gear pair that connects preposition tween drive shaft.
4, hybrid automobile power drive mechanism according to claim 1, it is characterized in that: described motor is the both-end spindle motor, each end axle of motor is provided with the transmission shaft that connects preposition tween drive shaft and rearmounted tween drive shaft respectively, is provided with coupler between each transmission shaft and pairing preposition tween drive shaft or the rearmounted tween drive shaft.
5, hybrid automobile power drive mechanism according to claim 1, it is characterized in that: described motor is single-ended spindle motor, motor shaft is provided with the driving gear of commutating tooth wheel set, and each transmission shaft that connects preposition tween drive shaft and rearmounted tween drive shaft respectively is connected in corresponding driven gear.
6, hybrid automobile power drive mechanism according to claim 1 is characterized in that: described sun wheel is provided with between its center shaft and the propulsion source output shaft and slows down or speed increasing mechanism.
7, hybrid automobile power drive mechanism according to claim 1 is characterized in that: described power take-off shaft is provided with change-speed box.
CNA2007101503775A 2007-11-23 2007-11-23 Single motor hybrid automobile power drive mechanism based on planetary gear train Pending CN101439668A (en)

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Application Number Priority Date Filing Date Title
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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102874089A (en) * 2012-09-29 2013-01-16 天津市松正电动汽车技术股份有限公司 Single-motor hybrid power driving system
CN103342124A (en) * 2013-07-25 2013-10-09 潍柴动力股份有限公司 Method and device for controlling force taking of power takeoff

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102874089A (en) * 2012-09-29 2013-01-16 天津市松正电动汽车技术股份有限公司 Single-motor hybrid power driving system
CN103342124A (en) * 2013-07-25 2013-10-09 潍柴动力股份有限公司 Method and device for controlling force taking of power takeoff
CN103342124B (en) * 2013-07-25 2016-08-10 潍柴动力股份有限公司 The control method of a kind of power takeoff power taking and device

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Open date: 20090527