CN105459799A - Driving system used for hybrid vehicle and provided with centrifugal overrunning clutch - Google Patents
Driving system used for hybrid vehicle and provided with centrifugal overrunning clutch Download PDFInfo
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- CN105459799A CN105459799A CN201510810569.9A CN201510810569A CN105459799A CN 105459799 A CN105459799 A CN 105459799A CN 201510810569 A CN201510810569 A CN 201510810569A CN 105459799 A CN105459799 A CN 105459799A
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
- B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
- B60K6/22—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
- B60K6/38—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the driveline clutches
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/62—Hybrid vehicles
Abstract
The invention discloses a driving system used for a hybrid vehicle and provided with a centrifugal overrunning clutch. The driving system comprises an internal combustion engine, a first motor, the clutch, a second motor and an output set. The output set comprises a first input end, a second input end and an output end. The driving system is characterized in that the centrifugal overrunning clutch serves as the clutch, and the internal combustion engine is connected with the first input end of the output set sequentially through the first motor and the centrifugal overrunning clutch; the second motor is connected with the second input end of the output set, and the first input end and the second input end of the output set drive the output end together; the first motor and the second motor are connected with a battery pack through a circuit control system. The driving system has the advantages that the starting condition of the centrifugal overrunning clutch is determined by the rotating speed of an output shaft so that an automatic speed changing system and hybrid power configuration in the driving system used for the hybrid vehicle can be achieved, stepless speed changing in the whole course can be achieved, and the fuel utilization rate is increased.
Description
Technical field
The present invention relates to a kind of drive system using the motor vehicle driven by mixed power of centrifugal overriding clutch.
Background technology
Power-transfer clutch has been widely used at mechanical drive technical field tool, and the power-transfer clutch used now is of a great variety, is specifically applied to the power-transfer clutch mainly overriding clutch in automotive power drop-gear box at present.Overriding clutch utilizes the velocity variations of driving and driven raceway or the conversion of hand of rotation to realize clutch voluntarily, when the speed of active raceway is identical with the speed of driven raceway, and ability transferring power, otherwise be relative sliding.By the initial conditions of active raceway, traditional overriding clutch can only determine that it is enabled or stops using, and can not be decided by the output state of driven raceway.Therefore traditional overriding clutch is utilized can not to realize the multistage automatic speed changing on a large scale.
Summary of the invention
The object of the invention is to overcome the deficiencies in the prior art, provide and a kind ofly by the rotating speed of output shaft to determine the centrifugal overriding clutch enabled or stop using of power-transfer clutch, and the automatic speed-changing system of this centrifugal overriding clutch and the drive system of motor vehicle driven by mixed power can be used.
The present invention is achieved by the following technical solutions:
A kind of centrifugal overriding clutch, comprise outer sleeve and middle star axle, described middle star axle is evenly distributed with the little groove of outer imperial palace, centrifugal wedging block is provided with in described groove, described centrifugal wedging block rotates along groove bottom in groove, described centrifugal wedging block side connects one end of retracing spring, the described retracing spring other end is fixed on the middle star axle of groove first side, described retracing spring is in compressive state, and the opposite side of described centrifugal wedging block is pressed in the second side of groove by described retracing spring; When described centrifugal wedging block is static, its top does not contact the inside face of outer sleeve, the maximum radial height of described centrifugal wedging block motion is greater than the distance of groove bottom to the inside face of described outer sleeve of middle star axle, and described centrifugal overriding clutch decides it by the tachometer value of middle star axle and the rotation speed relation of middle star axle and outer sleeve and starts or close.
As the optimization of centrifugal overriding clutch, described groove bottom and centrifugal wedging block bottom are the circular arc matched, and the arc radius of described centrifugal wedging block bottom is less than the arc radius of groove bottom.
As the optimization of centrifugal overriding clutch, described retracing spring is fixed by screws on middle star axle.
A kind of automatic speed-changing system using centrifugal overriding clutch as above, comprise input shaft, output shaft and connect many groups variable gear and the power-transfer clutch of described input shaft and output shaft, it is characterized in that: described power-transfer clutch is centrifugal overriding clutch, corresponding centrifugal overriding clutch is connected with in described each group of variable gear, the outer sleeve of described centrifugal overriding clutch connects with the input end of each group of corresponding variable gear, and the middle star axle of described centrifugal overriding clutch connects with the mouth of each group of corresponding variable gear.
As wherein a kind of embodiment of automatic speed-changing system, described automatic speed-changing system comprises two groups of variable gears and corresponding two centrifugal overriding clutchs, the outer sleeve of first centrifugal overriding clutch is connected with the input end of first group of variable gear, and the middle star axle of first centrifugal overriding clutch is connected with the mouth of first group of variable gear; The outer sleeve of second centrifugal overriding clutch is connected with the input end of second group of variable gear, and the middle star axle of second centrifugal overriding clutch is connected with the mouth of second group of variable gear.
A kind of drive system using the motor vehicle driven by mixed power of centrifugal overriding clutch as above, comprise combustion engine, first electrical motor, power-transfer clutch, second electrical motor, output group, described output group comprises first input end, second input end and mouth, described power-transfer clutch is centrifugal overriding clutch, described combustion engine is successively through the first electrical motor, centrifugal overriding clutch is connected with the first input end of output group, described second electrical motor is connected with the second input end of output group, the first input end of described output group and the common drive output of the second input end, described first electrical motor is connected with battery pack by circuit control system with the second electrical motor.
As the another kind of mode of the drive system of motor vehicle driven by mixed power, described output group is the front and back wheel of vehicle, and front vehicle wheel is connected with the second electrical motor, and rear wheel is connected with the middle star axle of centrifugal overriding clutch.
The drive system of above-mentioned motor vehicle driven by mixed power also can be used for combustion engine and pneumatic system, comprise combustion engine, first air motor, power-transfer clutch, second air motor, output group, described output group comprises first input end, second input end and mouth, described power-transfer clutch is centrifugal overriding clutch, described combustion engine is successively through the first air motor, centrifugal overriding clutch is connected with the first input end of output group, described second air motor is connected with the second input end of output group, the first input end of described output group and the common drive output of the second input end, described first air motor is connected with gaholder by control cock system with the second air motor.
As the another kind of mode of the drive system of the motor vehicle driven by mixed power for combustion engine and pneumatic system, described output group is the front and back wheel of vehicle, and front vehicle wheel is connected with the second air motor, and rear wheel is connected with the middle star axle of centrifugal overriding clutch.
The present invention has the following advantages compared to existing technology:
Centrifugal overriding clutch provided by the invention, combine the feature of centrifugal clutch and overriding clutch, the function of " S/CO " can be realized, namely, only when the middle star axle rotating speed be connected with output shaft reaches rated value and the rotating speed of the outer sleeve be connected with input shaft is greater than the middle star axle rotating speed be connected with output shaft, centrifugal overriding clutch could be opened; When the rotating speed of output shaft is lower than rated value, centrifugal overriding clutch is in "off" state.Therefore, the entry condition of this centrifugal overriding clutch is that the rotating speed of output shaft reaches rated value, before this, regardless of the rotary regimes of input shaft, all cannot start power-transfer clutch to combine, this can not exist in traditional overriding clutch, because just cannot transmit power like this.That is, the invention provides to the conditions for use of centrifugal overriding clutch be determined by output shaft, instead of to be determined by the initial conditions of input shaft.Just the hybrid power configuration in the drive system of the automatic speed changing of described automatic speed-changing system in large speed range and motor vehicle driven by mixed power can be realized thus, omnidistance stepless change can be realized, improve fuel utilization, energy-saving and emission-reduction, improve the life-span of whole drive system.
Accompanying drawing explanation
Fig. 1 is the cross-sectional view of centrifugal overriding clutch off-state of the present invention.
Fig. 2 is the cross-sectional view of centrifugal overriding clutch bonding state of the present invention.
Fig. 3 is automatic speed-changing system structural representation of the present invention.
Fig. 4 is the structural representation of the drive system of motor vehicle driven by mixed power of the present invention.
Detailed description of the invention
Elaborate to embodiments of the invention below, the present embodiment is implemented under premised on technical solution of the present invention, give detailed embodiment and concrete operating process, but protection scope of the present invention is not limited to following embodiment.
See Fig. 1 and Fig. 2, centrifugal overriding clutch provided by the invention, it is the feature combining centrifugal clutch and Wedge type over running clutch, the middle star axle 1 of power-transfer clutch is evenly distributed with the little groove of outer imperial palace 6, centrifugal wedging block 2 is provided with in groove 6, groove 6 bottom and centrifugal wedging block 2 bottom are the circular arc matched, and the arc radius of centrifugal wedging block 2 bottom is less than the arc radius of groove 6 bottom, and centrifugal wedging block 2 rotates along groove 6 bottom in groove 6.Centrifugal wedging block 2 side connects one end of retracing spring 3, the other end of retracing spring 3 is fixed on by screw 4 on the middle star axle 1 of groove 6 first side, retracing spring 3 is in compressive state, and the opposite side of centrifugal wedging block 2 spring 3 that is reset is pressed on the second skew back face of groove 6; When centrifugal wedging block 2 is static, its top does not contact the inside face of outer sleeve 5.The maximum radial height that centrifugal wedging block 2 moves is greater than the distance from groove 6 bottom of middle star axle 1 to the inside face of outer sleeve 5.Centrifugal overriding clutch decides it by the tachometer value of middle star axle 1 and the rotation speed relation of middle star axle 1 and outer sleeve 5 and starts or close.
At middle star axle 1 when static or cw low speed rotation, centrifugal wedging block 2 spring 3 that is reset is pressed on the second large inclined-plane, side of groove 6, and now, outer sleeve 5 does not contact with middle star axle 1, is in complete released state, as shown in Figure 1.When the dextrorotation rotary speed of middle star axle 1 reaches critical value, centrifugal wedging block 2 under the influence of centrifugal force, overcomes the pressure of retracing spring 3, starts to expand to groove 6 first side.But, when middle star axle 1 and outer sleeve 5 cw rotating Vortex, and when middle star axle 1 rotating speed is higher than outer sleeve 5, because the direction of friction force is opened to the side at its original place i.e. the second thruster of groove 6 by centrifugal wedging block 2, so centrifugal wedging block 2 and outer sleeve 5 inside face still can not be in conjunction with, be in a kind of unidirectional disengaging mode of operation of overriding clutch.The rotating speed when middle star axle 1 is only had to meet or exceed critical value, when outer sleeve 5 rotating speed exceedes middle star axle 1 rotating speed simultaneously, now the direction of friction force is promoted to groove 6 first side by centrifugal wedging block 2, maximum height due to centrifugal wedging block 2 motion is greater than the distance from groove 6 bottom of middle star axle 1 to the inside face of outer sleeve 5, therefore now centrifugal wedging block 2 is centrifuged power and friction lock, be in self-locking state, power-transfer clutch could combine under the combined action of centnifugal force and friction force, as shown in Figure 2.Therefore the unlatching of centrifugal overriding clutch provided by the present invention must meet two conditions simultaneously: the first middle star axle 1 rotating speed be connected with output shaft reaches rated value; Second outer sleeve be connected with input shaft 5 rotating speed is greater than the rotating speed of the middle star axle 1 be connected with output shaft, could connect.Open the rotating speed critical value of the centrifugal wedging block 2 of centrifugal overriding clutch, can by the tightened position of adjustment fix screw 4, the predetermincd tension changing retracing spring 3 realizes.
Simultaneously see Fig. 3, automatic speed-changing system provided by the invention make use of above-mentioned centrifugal overriding clutch.Be different from existing automatic transmission with hydraulic torque converter, the progression scope of its speed change can increase arbitrarily in theory, and we illustrate for two-stage speed change now.Input shaft 7 is connected output shaft 8 respectively by first group of variable gear 11 with second group of variable gear 21, first centrifugal overriding clutch 12 is connected with in described first group of variable gear 11, the outer sleeve 5 of described first centrifugal overriding clutch 12 is connected with the input end of first group of variable gear 11, and the middle star axle 1 of described first centrifugal overriding clutch 12 is connected with the mouth of first group of variable gear 11.Second centrifugal overriding clutch 22 is connected with in described second group of variable gear 21, the outer sleeve 5 of described second centrifugal overriding clutch 22 is connected with the input end of second group of variable gear 21, and the middle star axle 1 of described second centrifugal overriding clutch 22 is connected with the mouth of second group of variable gear 21.Here suppose that the reduction ratio of first group of variable gear 11 be the reduction ratio of 3, second group of variable gear 21 is 2.The joint critical speed of first centrifugal overriding clutch 12 is adjusted to 400 rpms, and the joint critical speed of second centrifugal overriding clutch 22 is adjusted to 800 rpms.Just illustratively self-shifting process below.First suppose that output shaft 8 rotating speed has reached 400 rpms, but lower than 600 rpms, the joint critical speed condition of first centrifugal overriding clutch 12 is so only had to meet, after input shaft 7 rotating speed is more than 1200 rpms, rotating speed after the first group of variable gear 11 being then 3 through speed ratio slows down will exceed the rotating speed of output shaft 8, first centrifugal overriding clutch 12 engages, input shaft 7 is delivered to power on output shaft 8 by first group of variable gear, 11, first centrifugal overriding clutch 12, and reduction ratio is 3.When the rotating speed of input shaft 7 reaches 1800 rpms time, the rotating speed of output shaft 8 is accelerated to 600 rpms, now the joint critical speed condition of second centrifugal overriding clutch 22 meets, and the input speed after being slowed down by second group of variable gear 21 that speed ratio is 2 is 900 rpms, exceed the rotating speed 600 rpms of output shaft 8, thus second centrifugal overriding clutch 22 engages, input shaft 7 is delivered to power on output shaft 8 by second group of variable gear 21 and second centrifugal overriding clutch 22, and reduction ratio becomes 2.Reduction ratio due to second group of variable gear 21 is less than first group of variable gear 11, output shaft 8 is accelerated faster, the mouth rotating speed of first centrifugal overriding clutch 12 is made to be greater than input end, first centrifugal overriding clutch 12 automatically disengages, and can not cause the situation that two groups of variable gears interfere with each other.If now reduce input power, the rotating speed of input shaft 7 is made to be reduced to less than 1200 rpms, then the rotating speed of output shaft 8 drops to less than 600 rpms, second centrifugal overriding clutch 22 departs from, when output shaft 8 drops to less than 400 rpms, first centrifugal overriding clutch 12 engages, and reduction ratio becomes 3 from 2.Another kind may be that the load of output shaft 8 increases, and make rotating speed drop to less than 600 rpms, second centrifugal overriding clutch 22 departs from, and waits the rotating speed of output shaft 8 to drop to 400 rpms, and first centrifugal overriding clutch 12 engages, and reduction ratio becomes 3 from 2.Therefore, as long as the suitable reduction ratio of adjustment variable gear and the critical speed of power-transfer clutch, just can realize converter speed ratio automatically to change according to the input and output rotation speed relation of setting, when output shaft 8 rotating speed significantly changes, maintain the range of speed of input shaft 7 in the interval needed.On this basis, the 3rd group, the 4th group is added ... variable gear, coordinates the 3rd, the 4th ... power-transfer clutch, just can increase the progression of converter speed ratio always.
See Fig. 4, the drive system of motor vehicle driven by mixed power provided by the invention, core component is centrifugal overriding clutch automatic speed-changing system, here only for level system, while simplification mechanical system, is also enough to the requirement of satisfied most of power configuration.If vehicle needs larger speed range, the centrifugal overriding clutch automatic speed-changing system of two-stage or more level can be used.The drive system of motor vehicle driven by mixed power comprises combustion engine 31, first electrical motor 32, centrifugal overriding clutch 33, second electrical motor 41, output gear wheels 9, here electrical motor can use as electrical generator under different operating mode, and output gear wheels 9 comprise first input end 91, second input end 92 and mouth 93.Combustion engine 31 is directly connected with the first electrical motor 32 main shaft, and the first electrical motor 32 main shaft is connected with centrifugal overriding clutch 33, and centrifugal overriding clutch 33 is connected with the first input end 91 of output gear wheels 9.And the second electrical motor 41 connects the second input end 92 of output gear wheels 9, mouth 93 outputting power of common driver output gear cluster 9.Two motors is connected with battery pack 61 with by circuit control system 51, is determined the mode of operation of the first electrical motor 32 and the second electrical motor 41 by circuit control system 51.If the mouth 93 removing output gear wheels 9, first electrical motor 32 and centrifugal overriding clutch 33 can drive the front and back wheel of vehicle respectively, form four wheel drive.
Several situations run with regard to the drive system of motor vehicle driven by mixed power below elaborate:
Work as stationary vehicle, combustion engine 31 starts, and drives combustion engine 31 to start by the first electrical motor 32, and now, because first input end 91 rotating speed of output gear wheels 9 is very low, so centrifugal overriding clutch 33 is separated, combustion engine 31 is equivalent to No Load Start;
When vehicle low cruise, now, first input end 91 rotating speed of output gear wheels 9 is lower, centrifugal overriding clutch 33 still can not be in conjunction with, no matter combustion engine 31 is in startup or is in high-speed operation state, all can not directly to first input end 91 outputting power of output gear wheels 9, and can only be unloaded or drive the first electrical motor 32 to generate electricity;
When vehicle high-speed runs, combustion engine 31 starts.Although the centnifugal force that now first input end 91 of output gear wheels 9 rotates is enough to the centrifugal wedging block 2 of centrifugal overriding clutch 33 to be opened, but because the rotating speed of combustion engine 31 main shaft is lower than the first input end 91 of output gear wheels 9, so centrifugal overriding clutch 33 is still in released state, combustion engine 31 is still equivalent to No Load Start;
When vehicle continues high-speed cruising, combustion engine 31 high-speed cruising, and rotating speed is higher than the rotating speed of the first input end 91 of output gear wheels 9.Two conditions that now centrifugal overriding clutch 33 starts all are satisfied, combustion engine 31 is directly by first input end 91 outputting power of centrifugal overriding clutch 33 pairs of output gear wheels 9, the state of the first electrical motor 32 now can be selected to be power-assisted, idle running or generating, to determine according to the needs of vehicle;
When first input end 91 low speed and reverse of output gear wheels 9, combustion engine 31 starts or runs, and now centnifugal force is not opened centrifugal wedging block 2, and centrifugal overriding clutch 33 is separated, and combustion engine 31 is unloaded or drive the first electrical motor 32 to generate electricity;
When first input end 91 high speed reverse rotation of output gear wheels 9, combustion engine 31 starts or runs, now two conditions of centrifugal overriding clutch 33 are all satisfied, due to combustion engine 31 and output gear wheels 9 first input end 91 turn to contrary, can cause very large impact and infringement to mechanical system, but this situation can not occur in vehicle normally runs.
These above mode of operations, most important for the high-efficiency operation realizing hybrid electric vehicle, be just illustrated one by one in conjunction with each mode of operation of automobile below.
Mode of operation one: combustion engine 31 stops, centrifugal overriding clutch 33 is in released state, as long as now vehicle is forward travel state, centrifugal overriding clutch 33 would not close, and combustion engine 31 exports with active force and is separated.Car load work is in all-electric state, and speeds control is realized by the circuit control system 51 of electrical motor, and the second electrical motor 41 rotating speed realizes automatically controlled completely.This is mainly applicable to urban highway, and the state of battery electric quantity abundance, can decreasing pollution, economy might as well, and common electric automobile is as broad as long.
Mode of operation two: combustion engine 31 starts.This step manually can be realized by the pure electronic switch to hybrid power by one, also can be realized according to battery electric quantity and condition of loading by computer.The startup of combustion engine 31 directly can drive main shaft to start by the first electrical motor 32, under this operating mode, can realize following multiple operation scheme:
Mode 1, low speed accelerator, mainly refers to vehicle launch acceleration mode, and combustion engine 31 keeps rotating speed and the moment of torsion running of peak efficiency, the first electrical motor 32 is driven to generate electricity, by circuit control system 51, the electric energy of collaborative battery pack 61, for the second electrical motor 41, output drive strength, because vehicle wheel rotational speed is low, centnifugal force is not enough to engage centrifugal overriding clutch 33, so driving engine is not directly to wheel outputting power.Now, pin step on the accelerator is in acceleration mode, and the mode of operation that circuit control system 51 controls the first electrical motor 32 is Generator Status, is converted into electric energy by from the rotating speed of combustion engine 31 and moment, send into battery pack 61 through circuit control system 51 to store, or directly for the second electrical motor 41.The voltage at the second electrical motor 41 two ends then increases because throttle is in acceleration mode, be operated in Power output state, the moment of input passes through the second input end 92 of output gear wheels 9, and drive main output shaft to rotate and accelerate, then the first input end 91 of output gear wheels 9 dallies.This stage should be the stage that the second electrical motor 41 work efficiency is the highest.Now combustion engine 31 generating, is similar to the output form of conventional tandem hybrid electric vehicle.
Mode 2, middling speed operative condition, mainly vehicle normally travels at urban highway, and now, vehicle wheel rotational speed reaches critical value, set the optimum efficiency rotating speed of this speed a little less than combustion engine 31.If the output speed of combustion engine 31 has exceeded the rotating speed of the first input end 91 of output gear wheels 9, when reaching optimum efficiency rotating speed, because centnifugal force reaches required critical value, centrifugal overriding clutch 33 engages automatically, the power of combustion engine 31 and rotating speed act on the first input end 91 of output gear wheels 9, and the common driver output axle of the second electrical motor 41.Now, combustion engine 31 and the second electrical motor 41 act synergistically, and can keep higher efficiency and rational moment of torsion.
Mode 3, high-speed operation state, for vehicle traveling on a highway.Now, centrifugal overriding clutch 33 still engages, whole power of combustion engine 31 are all directly exported by the first input end 91 of output gear wheels 9, now, the energy maintaining car speed mainly offsets windage and mill resistance, the general power that all can be less than combustion engine 31, so the mode of operation that can adjust the second electrical motor 41 by circuit control system 51 is Generator Status, is recovered to part energy in battery pack 61 from output gear wheels 9.The mode of operation of the first electrical motor 32 can regulate as required, needs to strengthen just in electric motor state work when exporting, just in Generator Status work when needing recuperated energy.
Mode 4, deceleration regime, is applicable to vehicle and runs into red light or descending, or when needing to brake, the speed of a motor vehicle be subtracted.Now, the voltage of the first electrical motor 32 and the second electrical motor 41 can be changed with circuit control system 51 simultaneously, allow them all as generator operation, the Conversion of Energy of most combustion engine 31 is electric energy by the first electrical motor 32, the kinetic transformation of vehicle is then electric energy by the second electrical motor 41 from output gear wheels 9, thus reach the object of energy regenerating, also to coordinate conventional brake simultaneously, guarantee safety.When the speed of a motor vehicle drops to certain phase, centrifugal overriding clutch 33 disconnects automatically.If parking period is longer, and battery pack 61 is also close to when being full of, and directly can close combustion engine 31, fuel saving consumption.
Mode 5, state of rolling backward, now no matter the mode of operation of combustion engine 31 is how, because vehicle wheel rotational speed is lower, the centnifugal force of the first input end 91 of output gear wheels 9 is much smaller than critical value, and centrifugal overriding clutch 33 disconnects, and the first input end 91 of output gear wheels 9 dallies, the second electrical motor 41 contrarotation can be controlled, realize car-backing function.
The advantage using centrifugal overriding clutch automatic speed-changing system to realize hybrid power configuration has:
1. greatly reduce the complexity of mechanical system, wholely instead of complex structure, the transmission system that fault rate is high;
2. coordinate electric motor system, omnidistance stepless change can be realized, and the rotating speed of combustion engine 31 only needs slightly to adjust in optimized efficiency range, because the electric-control system ratio of electrical motor is easier to realize speed governing, reduce the control difficulty of speed change system;
3. combustion engine 31 can remain within the scope of peak efficiency and optimum speed, improves fuel utilization, also extends the service life of combustion engine 31;
4. can be optimized distribution to the energy of power system, can the energy that originally will consume be reclaimed, so reduce the waste of energy, energy-saving and emission-reduction;
5. compare with common single combustion engine 31 power system, the efficient electric energy of relative clean can be made full use of, decrease pollution, reduce use cost, compare with motor power system, the embedding of combustion engine 31, considerably increase the sustainable work-hours of power system.
Certainly, this gear shift mode may be used for combustion engine and pneumatic system equally above, the first electrical motor 32 and the second electrical motor 41 is replaced with the first air motor and the second air motor, replace circuit control system 51 and battery pack 61 with control cock system, gaholder, adopt identical control policy.Except having the advantage of oil electric mixed dynamic system, this gas-oil hybrid system also has oneself advantage, because air pressure motor unit power is high, that can do is very little very light, and staring torque is large, is conducive to improving acceleration capacity, be not afraid of overload, also better in safety, heat radiation need not be considered.Storage tank is relative to battery, and pollute less, use cost is lower.
Visible, the above-mentioned automatic speed-changing system of centrifugal overriding clutch and the drive system of motor vehicle driven by mixed power used is just because of the distinctive opening and closing function by output shaft control clutch of centrifugal overriding clutch, namely reaching rated value by the rotating speed of output shaft just can make power-transfer clutch open, thus is just achieved the stepless change on a large scale.
The foregoing is only preferred embodiment of the present invention, not in order to limit the present invention, all any amendments done within the spirit and principles in the present invention, equivalent replacement and improvement etc., all should be included within protection scope of the present invention.
Claims (2)
1. one kind uses the drive system of the motor vehicle driven by mixed power of centrifugal overriding clutch, comprise combustion engine, first electrical motor, power-transfer clutch, second electrical motor, output group, described output group comprises first input end, second input end and mouth, it is characterized in that: described power-transfer clutch is centrifugal overriding clutch, described combustion engine is successively through the first electrical motor, centrifugal overriding clutch is connected with the first input end of output group, described second electrical motor is connected with the second input end of output group, the first input end of described output group and the common drive output of the second input end, described first electrical motor is connected with battery pack by circuit control system with the second electrical motor.
2. the drive system of motor vehicle driven by mixed power as claimed in claim 1, it is characterized in that: described output group is the front and back wheel of vehicle, and front vehicle wheel is connected with the second electrical motor, rear wheel is connected with the middle star axle of centrifugal overriding clutch.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310109679.3A CN103174774B (en) | 2013-03-29 | 2013-03-29 | Use the automatic speed-changing system of centrifugal free wheel device |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201310109679.3A Division CN103174774B (en) | 2013-03-29 | 2013-03-29 | Use the automatic speed-changing system of centrifugal free wheel device |
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| CN105459799A true CN105459799A (en) | 2016-04-06 |
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| CN201310109679.3A Expired - Fee Related CN103174774B (en) | 2013-03-29 | 2013-03-29 | Use the automatic speed-changing system of centrifugal free wheel device |
| CN201510810569.9A Pending CN105459799A (en) | 2013-03-29 | 2013-03-29 | Driving system used for hybrid vehicle and provided with centrifugal overrunning clutch |
| CN201510810439.5A Pending CN105333030A (en) | 2013-03-29 | 2013-03-29 | Drive system of hybrid vehicle using centrifugal overrunning clutch |
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| CN201310109679.3A Expired - Fee Related CN103174774B (en) | 2013-03-29 | 2013-03-29 | Use the automatic speed-changing system of centrifugal free wheel device |
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| CN201510810439.5A Pending CN105333030A (en) | 2013-03-29 | 2013-03-29 | Drive system of hybrid vehicle using centrifugal overrunning clutch |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN107719183A (en) * | 2016-08-10 | 2018-02-23 | 深圳市沃特玛电池有限公司 | A kind of pure electric automobile power assembly and its control method |
| CN111316010A (en) * | 2017-11-30 | 2020-06-19 | 舍弗勒技术股份两合公司 | Wedge clutch with centrifugal disengagement |
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| CN105128646B (en) * | 2015-09-02 | 2019-01-15 | 冯德洲 | A kind of fuel engines and motor linkage separation system |
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| JP7380552B2 (en) * | 2018-05-07 | 2023-11-15 | 日本精工株式会社 | Reverse input cutoff clutch and actuator |
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Also Published As
| Publication number | Publication date |
|---|---|
| CN103174774B (en) | 2016-04-27 |
| CN105333030A (en) | 2016-02-17 |
| CN103174774A (en) | 2013-06-26 |
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