CN100551731C - Hybrid drive - Google Patents
Hybrid drive Download PDFInfo
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- CN100551731C CN100551731C CNB2005100629194A CN200510062919A CN100551731C CN 100551731 C CN100551731 C CN 100551731C CN B2005100629194 A CNB2005100629194 A CN B2005100629194A CN 200510062919 A CN200510062919 A CN 200510062919A CN 100551731 C CN100551731 C CN 100551731C
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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 provides a kind of hybrid drive, have the 3 elements planetary wheel (P1) that connects 2 motors (MG1, MG2), be connected, also pass through the deceleration planetary wheel (P2) of the control switch mode of power-transfer clutch (C-1) and drg (B-1) with its driving.Be provided with connection and slow down, utilize and slow down, can realize the direct-connected pattern of 3 elements with planetary direct-connected with the power-transfer clutch (C-2) of planetary any 2 elements.Like this, the direct-connected pattern of 4 elements in the past when running at high speed is compared, and has reduced motor output, and the energy recovery efficiency when having improved regeneration.
Description
Technical field
The present invention relates to a kind of while mounting has the actuating device of the hybrid vehicle of driving engine (combustion engine) and rotating machine, particularly a kind of actuating device that utilizes 2 rotating machines and 2 differential gear mechanism change drive patterns.
Background technology
Existing 2 motor types separate in the shape hybrid drive, as the actuating device that in motor vehicle driven by mixed power, is connected lift-launch with driving engine, adopt 2 rotating machines (in this specification sheets for convenience's sake, be called motor or motor generator) and 2 differential gear mechanisms, combination by 2 binding members, discharge and control differential gear mechanism, corresponding with vehicle running state and switch 3-4 element (with reference to patent documentation 1).This actuating device can be realized the deceleration mode of 3 elements when low vehicle speeds, when running at high speed, can realize the direct-connected pattern of 4 elements.
Patent documentation 1: No. 2002/0142876 specification sheets of U.S. Patent Application Publication.
But, the acting characteristic of above-mentioned patent documentation 1 described actuating device as shown in figure 12, when the deceleration mode (3Lo) of 3 elements, draw relation that the output Pmg1 and bearing of a side motor cancels out each other between the opposing party's the output Pmg2 of motor of its antagonistic force along with the increase and decrease of speed of a motor vehicle straight line, and when the direct-connected pattern (4Hi) of 4 elements, these relations are with respect to the curved variation of the speed of a motor vehicle, and the increment rate of drawing the output of side's motor becomes big along with the increase of the speed of a motor vehicle.Because this relation, above-mentioned patent documentation 1 described actuating device is when the direct-connected pattern of 4 elements, and there are the following problems.
When 1, regenerating, owing to 1 motor is in reproduced state, another motor is in traction state, will carry out transformation of electrical energy greater than the electric power of deceleration energy, so energy recovery efficiency is poor.
2, in the high speed of a motor vehicle, low driving force zone (negative Mixed Zone), the power converter rate increases, and transmission efficiency is poor.
Summary of the invention
The objective of the invention is to, by appending 1 frictional engagement element, on the direct-connected pattern of the deceleration mode of 3 elements and 4 elements, append the direct-connected pattern of 13 element again, thereby address the above problem.
For achieving the above object, the basic comprising of hybrid drive of the present invention is, input block 12 with propulsive effort of accepting driving engine, output block 19 to the wheel output drive strength, the 1st rotating machine MG1 and the 2nd rotating machine MG2, the 1st differential gear mechanism P1 and the 2nd differential gear mechanism P2 that have 3 teeth parts at least, has 3 1-the 3rd frictional engagement element C-1 at least, C-2, B-1,3 teeth parts of wherein above-mentioned the 1st differential gear mechanism respectively with above-mentioned input block, the 1st rotating machine, and the 2nd rotating machine connects, 1 teeth parts of above-mentioned the 2nd differential gear mechanism are connected with above-mentioned output block, by above-mentioned 1-the 3rd frictional engagement selection of components combination, above-mentioned output block and above-mentioned the 2nd differential gear mechanism is direct-connected, thus realization comprises the multiple output mode of non-deceleration output.Specifically, 3 teeth parts of above-mentioned the 1st differential gear mechanism respectively with above-mentioned input block, the 1st rotating machine, and the 2nd rotating machine connects, 3 teeth parts of above-mentioned the 2nd differential gear mechanism respectively with above-mentioned output block, the 3rd frictional engagement element B-1, and the 2nd rotating machine connects, in above-mentioned the 2nd differential gear mechanism with the teeth parts of above-mentioned the 3rd frictional engagement combination of elements by above-mentioned the 1st frictional engagement element C-1 with remove with the direct coupled teeth parts of above-mentioned the 2nd differential gear mechanism outside above-mentioned the 1st differential gear mechanism in arbitrary teeth parts be connected, and any 2 teeth parts in above-mentioned the 2nd differential gear mechanism interconnect by the 2nd frictional engagement element C-2.
Above-mentioned the 3rd frictional engagement element in this structure slows down in conjunction with the rotating speed that makes above-mentioned the 2nd rotating machine MG2 by it.Also have, above-mentioned the 2nd frictional engagement element makes above-mentioned output block and the 2nd rotating machine be rotated with same rotational speed by its combination.
In this hybrid drive, when the rotating speed of above-mentioned output block rotation and above-mentioned the 1st rotating machine MG1 is approximately 0, combination by removing above-mentioned the 3rd frictional engagement element, make above-mentioned the 1st frictional engagement combination of elements, carry out the mode switch of 3 elements and 4 elements.Also have, when the rotation of above-mentioned output block and above-mentioned input block, output block, the 1st rotating machine, and the 2nd rotating machine in when having at least 2 rotating speed roughly the same, by removing the combination of above-mentioned the 1st frictional engagement element, make above-mentioned the 2nd frictional engagement combination of elements, carry out the mode switch of 4 elements and 3 elements.Also have, the the above-mentioned the 1st and the 2nd differential gear mechanism is by the combination of above-mentioned the 1st frictional engagement element, become wheel word with 4 degree of freedom, this have 4 degree of freedom wheel word each teeth parts respectively with above-mentioned input block, output block, the 1st rotating machine, and the 2nd rotating machine be connected.
Also have, in the said structure can be connected with the teeth parts that are connected in the 3rd frictional engagement element in above-mentioned the 2nd differential gear mechanism by above-mentioned the 1st frictional engagement element with teeth parts above-mentioned the 1st rotating machine bonded assembly the 1st differential gear mechanism.Perhaps, can be connected with the teeth parts that are connected in the 3rd frictional engagement element in above-mentioned the 2nd differential gear mechanism by above-mentioned the 1st frictional engagement element with input block bonded assembly teeth parts in above-mentioned the 1st differential gear mechanism.
According to the invention described above, the direct-connected pattern of 3 elements is travelled when utilizing the high speed of a motor vehicle, and the deceleration energy recovery efficiency in the time of can improving regeneration improves the efficient of negative Mixed Zone simultaneously.Also have, compare, can realize miniaturization by the output that reduces the 1st rotating machine with the situation of 2 patterns of deceleration mode that has only 3 elements and direct-connected pattern.
Description of drawings
Fig. 1 is the schematic diagram of the train of gears of the actuating device of expression the present invention the 1st embodiment.
The combination of the frictional engagement element when Fig. 2 realizes each pattern of train of gears for expression, releasing in conjunction with chart.
Fig. 3 is the speed line chart of the action of each pattern of expression train of gears.
Fig. 4 is the expression actuating device and the graph of a relation cooresponding input speed of the speed of a motor vehicle, motor torque and motor output.
Fig. 5 is mode switch figure.
Fig. 6 combines the figure that describes for representing the series of gears system of other embodiments of the invention and the annexation of each structural constituent thereof and the speed line chart of action.
Fig. 7 combines the figure that describes for representing other series of gears systems and the annexation of each structural constituent thereof and the speed line chart of action.
Fig. 8 combines the figure that describes for representing other other series of gears systems and the annexation of each structural constituent thereof and the speed line chart of action.
Fig. 9 combines the figure that describes for representing the series of gears system of other type and the annexation of each structural constituent thereof and the speed line chart of action.
Figure 10 combines the figure that describes for representing other series of gears systems of other type and the annexation of each structural constituent thereof and the speed line chart of action.
Figure 11 combines the figure that describes for representing other other series of gears systems of other type and the annexation of each structural constituent thereof and the speed line chart of action.
Figure 12 is the figure of the speed of a motor vehicle and the relation that motor is exported of expression actuating device in the past.
Among the figure: 12-input shaft (input block), 19-output shaft (output block), MG1-motor generator (the 1st rotating machine), MG2-motor (the 2nd rotating machine), P1-3 element planetary wheel (the 1st differential gear mechanism), P2-slows down with planetary wheel (the 2nd differential gear mechanism), S1, S2-sun wheel (teeth parts), C1, C2-pinion carrier (teeth parts), R1, R2-gear ring (teeth parts), C-1-power-transfer clutch (the 1st frictional engagement element), C-2-power-transfer clutch (the 2nd frictional engagement element), B-1-drg (the 3rd frictional engagement element).
The specific embodiment
Adopt in the actuating device of the present invention, wish to combine with the teeth parts that are connected the 3rd frictional engagement element of the 2nd differential gear mechanism by the 1st frictional engagement element with the teeth parts of the 2nd rotating machine bonded assembly the 1st differential gear mechanism.By this structure, from 3 element mode switch to 4 element patterns the time, can be at the rotating speed of the 1st rotating machine under 0 the state and carry out mode switch, when comprising arbitrary patterns switching from 4 element mode switch to 3 element patterns, can will in conjunction with the friction material of frictional engagement element do not have to carry out speed change under the state of speed discrepancy, therefore can reduce speed change and impact the thermal load of the material of reducing friction.
(the 1st embodiment)
Below, embodiments of the present invention are described with reference to the accompanying drawings.Fig. 1 adopts the schematic diagram of the train of gears of actuating device of the present invention for expression.As shown in the figure, this actuating device is the longitudinal that is used for F/F-rear wheel drive vehicle, is connected to engine output shaft by the drive plate 11 that has the flywheel attenuating device.On 1 axle of actuating device, connect side, dispose motor generator MG1, the 1st differential gear mechanism P1, motor MG2, the 2nd differential gear mechanism P2, and be housed in the same actuating device housing from driving engine.As drg B-1, the power-transfer clutch C-1 of 3 frictional engagement elements, and power-transfer clutch C-2 and the 2nd differential gear mechanism disposed adjacent.
In this train of gears, the input block of accepting the propulsive effort of driving engine is an input shaft 12, output block to the wheel output drive strength is an output shaft 19, the 1st rotating machine is motor generator MG1, the 2nd rotating machine is motor MG2, the 1st differential gear mechanism that has 3 teeth parts at least is double pinion planetary wheel (the following 3 element planetary wheels that are called in the present embodiment) P1, and same the 2nd differential gear mechanism is double pinion planetary wheel (following being called in the present embodiment slows down with 3 element planetary wheels) P2.3 elements with 3 teeth parts of planetary wheel P1 respectively with input shaft 12, motor generator MG1, and motor MG2 is connected, slow down with 3 teeth parts of planetary wheel P2 respectively with output shaft 19, drg B-1, and 3 elements with the teeth parts connection that is connected motor MG2 of planetary wheel P1.Slowing down is connected with the arbitrary teeth parts outside the direct coupled teeth parts of the teeth parts of planetary wheel P1 with removing with 3 elements by power-transfer clutch C-1 with the teeth parts of the connection drg B-1 of planetary wheel P2, and deceleration interconnects by power-transfer clutch C-2 with any 2 teeth parts of planet P2.
3 elements with planetary wheel P1 by sun wheel S1, be meshing with each other and one with sun wheel S1 ingear miniature gears, support these miniature gearss and make its pinion carrier C1 that rotates freely, form with the gear ring R1 of another pinion, gear ring R1 is connected with input shaft 12 as input element, pinion carrier C1 as with rotor shaft 14 and differential rotating element of tween drive shaft 13 bonded assemblys of motor generator MG1, sun wheel S1 as with another differential rotating element of rotor shaft 15 bonded assemblys of motor MG2.
Slow down with planetary wheel P2 by sun wheel S2, be meshing with each other and one with sun wheel S2 ingear miniature gears, support these miniature gearss and make its pinion carrier C2 that rotates freely, and the gear ring R2 of another pinion form, gear ring R2 is connected with output shaft 19 as output element.This sun wheel S2 that uses planetary wheel P2 that slows down is connected with the sun wheel S1 of 3 elements with planetary wheel P1 by rotor shaft 15, is connected with pinion carrier C2 by power-transfer clutch C-2 simultaneously.This pinion carrier C2 is connected with tween drive shaft 13 by power-transfer clutch C-1, can be fixed on the actuating device housing 10 by drg B-1 simultaneously.
Above-mentioned in each, rotor shaft 14 is the inner quill shaft that is installed with input shaft 12, and periphery is by the support institute axle bearing of a pair of bearing driven device housing 10 in front and back.Equally, rotor shaft 15 also is the inner quill shaft that is installed with tween drive shaft 13, and periphery is by the support institute axle bearing of a pair of bearing driven device housing 10 in front and back.The periphery of input shaft 12 is passed through a pair of bearing in front and back by interior all institutes axle bearing of rotor shaft 14, so input shaft 12 supports by rotor shaft 14.Equally, the periphery of tween drive shaft 13 is passed through a pair of bearing in front and back by interior all institutes axle bearing of rotor shaft 15, so tween drive shaft 13 supports by rotor shaft 15.The periphery of output shaft 19 is supported by bearing at the rear wall place of actuating device housing 10.Symbol among Fig. 1 ● represent above-mentioned each bearing.
Actuating device by said structure, for above-mentioned 3 frictional engagement elements, as Fig. 2 in conjunction with shown in the chart, utilize the combination of drg B-1 to realize 3 elements low (Lo) pattern, utilize the combination of power-transfer clutch C-1 to realize 4 element patterns, utilize the combination of power-transfer clutch C-2 to realize 3 element height (Hi) patterns.Also have, in this chart, zero expression combination, * expression discharges.Action when then, each pattern being described.
(1) 3 element low mode
This pattern is an engine starting, electrical motor travels and start pattern when quickening, by the combination of drg B-1, the pinion carrier C2 that slows down with planetary wheel P2 is fixed on the actuating device housing 10, thereby realizes this pattern.In this pattern, motor MG2 drives the sun wheel S2 that slows down with planetary wheel P2 and draws, and pinion carrier C1 is fixed by the combination of drg B-1, and the rotation of gear ring R2 outputs to output shaft 19.The state of this moment is as the 1st pattern in the left side of the speed line chart of Fig. 3: shown in 3 elements (Lo).At this moment, if the rotating speed of gear ring bonded assembly driving engine is certain, sun wheel bonded assembly motor (MG2: when the rotating speed rotating machine of a side of output drive strength) is rising, according to the above-mentioned 3 elements differential relation with the planetary wheel side, (MG1: the rotating speed rotating machine of a side that bears the counter-force torque of driving engine) is then for descending (among the figure downwards shown in the dotted arrow) for pinion carrier bonded assembly motor generator.At this moment, use the planetary wheel side,,, export deceleration rotation from gear ring because drg supports in conjunction with the fixing counter-force of the pinion carrier that produces along with the rising of sun wheel bonded assembly motor rotary speed in deceleration.Therefore, in this pattern, along with the rising of the rotating speed of motor (MG2), output (OUT) rotating speed rises continuously.Zero interior digital 1-3 simply represents the stage of uphill process among the figure.Wherein, the output speeds of the expression of 3 in zero are the rotating speed that the rotating speed of motor generator (MG1) drops to 0 o'clock acquisition.
(2) 4 element patterns
The pattern of this pattern when travelling usually, combination by power-transfer clutch C-1,3 elements are connected with the pinion carrier C2 that slows down with planetary wheel P2 with the pinion carrier C1 of planetary wheel P1,3 elements are input to the pinion carrier C2 of the usefulness planetary wheel P2 that slows down with the differential rotation of planetary wheel P1, the rotation of motor MG2 is input to sun wheel S2, thereby realizes this pattern.In this pattern, with the benchmark that rotates to be of driving engine, by reducing the rotating speed of motor MG2, the rotation of gear ring R2 is risen along with the rising of the rotating speed of motor generator (MG1), and the rotation of this gear ring R2 outputs to output shaft 19.The state of this moment is as the 2nd pattern of the central authorities of the speed line chart of Fig. 2: shown in 4 elements.At this moment, if the rotating speed of driving engine for the rotating speed of certain, motor (MG2) with respect to 3 speed of fwd pattern descend (among the figure down shown in the arrow), along with the rising (shown in the dotted arrow that makes progress among the figure) of the rotating speed of motor generator (MG1), output (OUT) rotating speed rises continuously.At this moment, the digital 3-5 in zero also represents stage of uphill process among the figure.Wherein, the output speeds of the expression of 5 in zero are the whole rotating speeds that obtain when identical of the rotating speed of driving engine (Eng.), motor generator (MG1) and motor (MG2).
(3) 3 element height modes
This pattern is the pattern with feature of the present invention, is the pattern of cruising and regeneration.When this pattern, power-transfer clutch C-2 combination, deceleration is in fast slew mode with sun wheel S2 and the pinion carrier C2 of planetary wheel P2, slows down like this to be in the direct-connected state of integrated rotation with 3 elements of planetary wheel P2.Therefore, this moment is by traction motor MG2, and the rotation that outputs to output shaft 19 from gear ring R2 becomes the rotation of motor MG2.The state of this moment is as the 3rd pattern on the right side of the speed line chart of prior figures 2: shown in 3 elements (Hi).The output (OUT) of this moment is also risen continuously, but its ascending velocity is represented with the digital 5-8 in zero.In this pattern, concern with planetary differential according to 3 elements, the rotating speed of motor generator (MG1) descend along with the rising of the rotating speed of motor MG2 (among the figure to shown in the upward arrow) (among the figure downwards shown in the dotted arrow), in zero 7 shown in output speed the time become 0 rotating speed, and in zero 8 shown in output speed the time become contrarotation.
Fig. 4 represents the relation of the input speed with respect to the speed of a motor vehicle, motor torque and the motor output of above-mentioned 3 patterns.In the 1st pattern (3 element low mode) that left side in 3 zones that 2 vertical dotted lines are distinguished is represented, engine speed Ne is a timing, and from foregoing relation, the rotational speed N mg2 of MG2 is since 0, along with the rising of the speed of a motor vehicle, rise to above engine speed with certain slope always.The rotating speed Mng1 of MG1 is then opposite, drops to the rotation that is lower than engine speed with certain slope from the state that is higher than engine speed always.According to this relation, output speed No rises to certain slope near the engine speed from 0 rotating speed.Also have, for motor torque, the torque Tmg2 of MG2 reduces along with the increase of the speed of a motor vehicle, but reduced rate reduces gradually.The torque Tmg1 of MG1 then keeps certain value.Therefore, for motor output, the output Pmg2 of MG2 is along with the rising of the speed of a motor vehicle drops to 0 with certain slope, and the output Pmg1 of MG1 is then opposite, along with the rising of the speed of a motor vehicle rises to 0 with certain slope.
Also have, by being clipped in the 2nd pattern shown in 2 middle sections between vertical dotted line (4 element), same, engine speed Ne is certain, the rotational speed N mg2 of MG2 begins to descend with certain slope along with the rising of the speed of a motor vehicle from a certain value, thereby equates with engine speed.In contrast, the rotational speed N mg1 of MG1 increases to certain slope from the state that is lower than engine speed and equals engine speed.Also have, for motor torque, the torque Tmg2 of MG2 increases and reduces along with the speed of a motor vehicle, but reduction rate reduces.The same trend that occurs reducing of the torque Tmg1 of MG1 with the torque Tmg2 of MG2, but numerical value is higher than Tmg2.For motor output, the escalating rate of the output Pmg1 of MG1 reduces along with the rising of the speed of a motor vehicle, and the rate of descent of the output Pmg2 of MG2 reduces along with the rising of the speed of a motor vehicle.
In addition, same in the 3rd pattern (3 element height mode) shown in the right side area that 2 vertical dotted lines separate, engine speed Ne be that necessarily the rotational speed N mg2 of MG2 begins along with the rising of the speed of a motor vehicle is risen with certain slope from engine speed.In contrast, the rotational speed N mg1 of MG1 reduces with certain slope from engine speed.Also have, for motor torque, the torque Tmg2 of MG2 increases and reduces along with the speed of a motor vehicle, but reduction rate reduces.The torque Tmg1 of MG1 then keeps certain value.For motor output, the output Pmg2 of MG2 begins to descend with certain slope along with the rising of the speed of a motor vehicle from a certain value, becomes reproduced state through 0 at last.In contrast, the output Pmg1 of MG1 along with the rising of the speed of a motor vehicle is risen with certain slope, becomes traction state through 0 from a certain value of reproduced state at last.
(4) mode switch
The switching of above-mentioned each pattern is shown in the switching figure of Fig. 5.The transverse axis of this switching figure is the speed of a motor vehicle, and the longitudinal axis is the switching point as propulsive effort.As shown in the figure, as above-mentioned 3 element low modes, starting when quickening is slow speed of revolution high torque (HT) state.Needing the state of low driving force, shown in the switching point of figure heavy line, switch to 4 element patterns and 3 element height modes early at low speed, required driving torque is big more, and switching point then moves to high-speed side more.Fine rule is represented the representative type speed-change process among the figure, output speed in this process is with reference to fwd Fig. 3, the zone that comprises output speed 1-3 is 3 element low modes, and the zone that comprises output speed 3-5 is 4 element patterns, and the zone that comprises output speed 5-8 is 3 element height modes.At output speed 3 and output speed 5, carry out mode switch.During this switches, when 3 element low modes switch to 4 element patterns, make that drg B-1 discharges, power-transfer clutch C-1 combination, promptly carry out so-called two frictional engagement elements conversion.At this moment, the characteristic curve of velocity variations shown in Figure 3 and Fig. 4 as can be known from the front, the rotating speed of motor generator MG1 is 0, at 3 element low modes, owing to the braking of drg B-1 is in the pinion carrier C2 of the state of stopping the rotation and the rotation of tween drive shaft 13 also is 0, the power-transfer clutch C-1 that connects these parts carries out combination under the state that stops the rotation.Therefore, utilize this characteristic, can under the clutch friction parts have the state of speed discrepancy, not change, impact thereby can reduce speed change, and the thermal load of the parts of can reducing friction.Then, when 4 element patterns (4) switched to 3 element height modes (3Hi), from the characteristic curve of fwd Fig. 4 as can be known, the rotational speed N mg1 of output speed No, engine speed Ne, MG1 and the rotational speed N mg2 of MG2 all equated.This switching makes power-transfer clutch C-1 release, power-transfer clutch C-2 combination, promptly carries out so-called power-transfer clutch and changes mutually.By this characteristic, can under having the state of speed discrepancy, not change the clutch friction parts, and also can reduce speed change this moment and impact, and the thermal load of the parts of can reducing friction.
As mentioned above, in this embodiment, that utilizes power-transfer clutch C-2 uses 2 teeth parts of planetary wheel P2 in conjunction with connecting to slow down, be in direct-connected state thereby can make slows down with planetary wheel P2, therefore by this direct-connected state, when the high speed of a motor vehicle, utilize the direct-connected pattern of 3 elements to travel, thereby improve the deceleration energy recovery efficiency when regenerating, improve the efficient of negative Mixed Zone simultaneously.Also have, compare, alleviated and drawn required motor output, can realize the miniaturization of motor with the situation of 2 patterns of the deceleration mode that has only 3 elements in past and direct-connected pattern.In addition, during when 3 element low modes switch to 4 element patterns and from 4 element mode switch to 3 element height modes, can not rotate at power-transfer clutch and carry out speed change under the poor state, impact thereby can reduce speed change, and the thermal load of the parts of can reducing friction.
(the 2nd embodiment)
Then, with reference to 6-11, the example of the various train of gearss that expression the present invention can be suitable for.Fig. 6 in these examples-example shown in Figure 8 is the example that changes substantially for the gear of the prior art introduced with front beginning, and Fig. 9-example shown in Figure 11 is the various modifications of the train of gears of different therewith new model.
At first, shown in Fig. 6 (A), 2 differential gear mechanisms are single pinion type, dispose the 1st rotating machine MG1 therebetween, axle head at outgoing side disposes the 2nd rotating machine MG2, the 2nd frictional engagement element (power-transfer clutch) C-2 connects sun wheel and the pinion carrier of the 2nd differential gear mechanism (slow down and use planetary wheel) P2, and exports from pinion carrier.3 elements in this train of gears are used, are slowed down and represent with the speed line chart at the left side of figure pictorialization with the annexation of two planetary wheel P1, P2 and motor MG1, driving engine E/G, output OUT and motor generator MG2.The teeth parts of 2 planetary wheel P1, P2 are represented in line in the chart, and file is represented the annexation between them.Also have, among Fig. 6-Fig. 8, being connected to of the element shown in the left column is direct-connected, and being connected to by the 1st frictional engagement element (power-transfer clutch) C-1 of the element shown in the right column connects.Among Fig. 9-Figure 11, being connected to of the element shown in the right column is direct-connected, and being connected to motor MG1 of the element shown in the left column is connected, and being connected to by power-transfer clutch C-1 of element is connected with driving engine E/G shown in the 2nd row of a left side.Also have, in this example, the S (sun wheel) of MG2 (motor generator) bonded assembly P2 (slow down and use planetary wheel) and the R (gear ring) of P1 (3 element planetary wheel) are direct-connected, E/G (driving engine) is connected with the C (pinion carrier) of P1, OUT (output) is connected with the C (pinion carrier) of P2, and the R (gear ring) of MG1 (motor) bonded assembly P2 and the S (sun wheel) of P1 are connected by C-1 (power-transfer clutch).This method for expressing is all identical in all embodiment described later.Also have, in this example, different with fwd embodiment is, the gear ring with planetary wheel P2 of slowing down is connected with drg B-1 and as the counter-force element, axle head disposes motor generator MG2, and input and output are not coaxial, becomes the counter gear output (OUT) of the parallel shafts that is fit to the FF car.
In Fig. 6 (B) institute example, the 1st differential gear mechanism is the double pinion planetary wheel, and the 2nd differential gear mechanism is single miniature gears planetary wheel.At this moment, the 2nd frictional engagement element (power-transfer clutch) C-2 is connected with pinion carrier with the sun wheel of slowing down with planetary wheel P2, exports from pinion carrier.In this example, gear ring with planetary wheel P2 is connected with drg B-1 and as the counter-force element though slow down, but since 3 elements with, the deceleration with disposing the 2nd rotating machine (motor generator) MG2 and the 1st rotating machine (motor) MG1 between two planetary wheel P1, the P2, thereby can carry out coaxial output with planetary wheel P2 from slowing down, become and to be used for the coaxial FR car of input and output, also can be used for the output (OUT) of FF car.
Below equally can be according to the configuration and the annexation of the form of the 1st differential gear mechanism and the 2nd differential gear mechanism, two rotating machines cooresponding with it, utilize the selection of the 2nd frictional engagement element bonded assembly teeth parts, constitute various train of gearss.For fear of redundancy, below each embodiment all adopt identical method for expressing, the only form of the configuration relation that can not represent on the instruction sheets, differential gear mechanism and annexation.
In Fig. 6 (C) institute example, the 1st differential gear mechanism P1 and the 2nd differential gear mechanism P2 are single miniature gears planetary wheel, and the sun wheel of the 2nd differential gear mechanism P2 is connected by the 2nd frictional engagement element C-2 with pinion carrier.At this moment, the gear ring of the 2nd differential gear mechanism P2 is and the 3rd frictional engagement element B-1 bonded assembly braking element.
In Fig. 6 (D) institute example, the 1st differential gear mechanism P1 is single miniature gears planetary wheel, and the 2nd differential gear mechanism P2 is the double pinion planetary wheel, and the sun wheel of the 2nd differential gear mechanism P2 is connected by the 2nd frictional engagement element C-2 with gear ring.At this moment, the pinion carrier of the 2nd differential gear mechanism P2 is and the 3rd frictional engagement element B-1 bonded assembly braking element.
In Fig. 6 (E) institute example, the 1st differential gear mechanism P1 is single miniature gears planetary wheel, and the 2nd differential gear mechanism P2 is the double pinion planetary wheel, and the pinion carrier of the 2nd differential gear mechanism P2 is connected by the 2nd frictional engagement element C-2 with gear ring.At this moment, the sun wheel of the 2nd differential gear mechanism P2 is and the 3rd frictional engagement element B-1 bonded assembly braking element.
In Fig. 6 (F) institute example, the 1st differential gear mechanism P1 is the double pinion planetary wheel, and the 2nd differential gear mechanism P2 is single miniature gears planetary wheel, and the sun wheel of the 2nd differential gear mechanism P2 is connected by the 2nd frictional engagement element C-2 with pinion carrier.At this moment, the gear ring of the 2nd differential gear mechanism P2 is and the 3rd frictional engagement element B-1 bonded assembly braking element.
In Fig. 7 (A) institute example, the 1st differential gear mechanism P1 is the double pinion planetary wheel, and the 2nd differential gear mechanism P2 is single miniature gears planetary wheel, and the pinion carrier of the 2nd differential gear mechanism P2 is connected by the 2nd frictional engagement element C-2 with gear ring.At this moment, the sun wheel of the 2nd differential gear mechanism P2 is and the 3rd frictional engagement element B-1 bonded assembly braking element.
In Fig. 7 (B) institute example, the 1st differential gear mechanism P1 and the 2nd differential gear mechanism P2 are the double pinion planetary wheel, and the pinion carrier of the 2nd differential gear mechanism P2 is connected by the 2nd frictional engagement element C-2 with gear ring.At this moment, the sun wheel of the 2nd differential gear mechanism P2 is and the 3rd frictional engagement element B-1 bonded assembly braking element.
In Fig. 7 (C) institute example, the 1st differential gear mechanism P1 is single miniature gears planetary wheel, and the 2nd differential gear mechanism P2 is the double pinion planetary wheel, and the sun wheel of the 2nd differential gear mechanism P2 is connected by the 2nd frictional engagement element C-2 with gear ring.At this moment, the pinion carrier of the 2nd differential gear mechanism P2 is and the 3rd frictional engagement element B-1 bonded assembly braking element.
In Fig. 7 (D) institute example, the 1st differential gear mechanism P1 and the 2nd differential gear mechanism P2 are the double pinion planetary wheel, and the sun wheel of the 2nd differential gear mechanism P2 is connected by the 2nd frictional engagement element C-2 with pinion carrier.At this moment, the pinion carrier of the 2nd differential gear mechanism P2 is and the 3rd frictional engagement element B-1 bonded assembly braking element.
In Fig. 7 (E) institute example, the 1st differential gear mechanism P1 and the 2nd differential gear mechanism P2 are single miniature gears planetary wheel, and the pinion carrier of the 2nd differential gear mechanism P2 is connected by the 2nd frictional engagement element C-2 with gear ring.At this moment, the sun wheel of the 2nd differential gear mechanism P2 is and the 3rd frictional engagement element B-1 bonded assembly braking element.
Then, in Fig. 8 (A) institute example, the 1st differential gear mechanism P1 is the double pinion planetary wheel, and the 2nd differential gear mechanism P2 is single miniature gears planetary wheel, and the pinion carrier of the 2nd differential gear mechanism P2 is connected by the 2nd frictional engagement element C-2 with gear ring.At this moment, the sun wheel of the 2nd differential gear mechanism P2 is and the 3rd frictional engagement element B-1 bonded assembly braking element.
In Fig. 8 (B) institute example, the 1st differential gear mechanism P1 is single miniature gears planetary wheel, and the 2nd differential gear mechanism P2 is the double pinion planetary wheel, compares with the front example, and its position relation is just opposite with respect to input, output.At this moment, the pinion carrier of the 2nd differential gear mechanism P2 is connected by the 2nd frictional engagement element C-2 with gear ring.At this moment, the sun wheel of the 2nd differential gear mechanism P2 is and the 3rd frictional engagement element B-1 bonded assembly braking element.
In Fig. 8 (C) institute example, the 1st differential gear mechanism P1 and the 2nd differential gear mechanism P2 are the double pinion planetary wheel, and the pinion carrier of the 2nd differential gear mechanism P2 is connected by the 2nd frictional engagement element C-2 with gear ring.At this moment, the sun wheel of the 2nd differential gear mechanism P2 is and the 3rd frictional engagement element B-1 bonded assembly braking element.
More than in Fig. 6-example shown in Figure 8 among each embodiment, when 3 element low modes (3Lo) switched to 4 element patterns (4), as previously mentioned, the MG1 rotating speed was 0.Therefore, this state uses down and combines with the power-transfer clutch C-1 of switch mode, utilize with from 4 element mode switch to 3 element height modes the time situation of conversion of drg B-1 and power-transfer clutch C-1 the same, owing to can under power-transfer clutch has the state of speed discrepancy, not carry out speed change, impact thereby can reduce speed change, and the thermal load of the parts of can reducing friction.
Then, in Fig. 9 (A) institute example, the 1st differential gear mechanism P1 and the 2nd differential gear mechanism P2 are single miniature gears planetary wheel, and the pinion carrier of the 2nd differential gear mechanism P2 is connected by the 2nd frictional engagement element C-2 with gear ring.At this moment, the sun wheel of the 2nd differential gear mechanism P2 is and the 3rd frictional engagement element B-1 bonded assembly braking element.
In Fig. 9 (B) institute example, the 1st differential gear mechanism P1 is single miniature gears planetary wheel, and the 2nd differential gear mechanism P2 is the double pinion planetary wheel, and the pinion carrier of the 2nd differential gear mechanism P2 is connected by the 2nd frictional engagement element C-2 with gear ring.At this moment, the sun wheel of the 2nd differential gear mechanism P2 is and the 3rd frictional engagement element B-1 bonded assembly braking element.
In Fig. 9 (C) institute example, the 1st differential gear mechanism P1 and the 2nd differential gear mechanism P2 are single miniature gears planetary wheel, and its position relation is just opposite with respect to input, output.This moment, the sun wheel of the 2nd differential gear mechanism P2 was connected by the 2nd frictional engagement element C-2 with pinion carrier.At this moment, the gear ring of the 2nd differential gear mechanism P2 is and the 3rd frictional engagement element B-1 bonded assembly braking element.
In Fig. 9 (D) institute example, the 1st differential gear mechanism P1 is single miniature gears planetary wheel, and the 2nd differential gear mechanism P2 is the double pinion planetary wheel, and its position relation is just opposite with respect to input, output.This moment, the sun wheel of the 2nd differential gear mechanism P2 was connected by the 2nd frictional engagement element C-2 with pinion carrier.At this moment, the pinion carrier of the 2nd differential gear mechanism P2 is and the 3rd frictional engagement element B-1 bonded assembly braking element.
In Fig. 9 (E) institute example, the 1st differential gear mechanism P1 is the double pinion planetary wheel, and the 2nd differential gear mechanism P2 is single miniature gears planetary wheel, and the pinion carrier of the 2nd differential gear mechanism P2 is connected by the 2nd frictional engagement element C-2 with gear ring.At this moment, the sun wheel of the 2nd differential gear mechanism P2 is and the 3rd frictional engagement element B-1 bonded assembly braking element.
In Fig. 9 (F) institute example, the 1st differential gear mechanism P1 and the 2nd differential gear mechanism P2 are single miniature gears planetary wheel, and the pinion carrier of the 2nd differential gear mechanism P2 is connected by the 2nd frictional engagement element C-2 with gear ring.At this moment, the sun wheel of the 2nd differential gear mechanism P2 is and the 3rd frictional engagement element B-1 bonded assembly braking element.
Then, in Figure 10 (A) institute example, the 1st differential gear mechanism P1 is the double pinion planetary wheel, and the 2nd differential gear mechanism P2 is single miniature gears planetary wheel, and the pinion carrier of the 2nd differential gear mechanism P2 is connected by the 2nd frictional engagement element C-2 with gear ring.At this moment, the sun wheel of the 2nd differential gear mechanism P2 is and the 3rd frictional engagement element B-1 bonded assembly braking element.
In Figure 10 (B) institute example, the 1st differential gear mechanism P1 and the 2nd differential gear mechanism P2 are the double pinion planetary wheel, and the pinion carrier of the 2nd differential gear mechanism P2 is connected by the 2nd frictional engagement element C-2 with gear ring.At this moment, the sun wheel of the 2nd differential gear mechanism P2 is and the 3rd frictional engagement element B-1 bonded assembly braking element.
In Figure 10 (C) institute example, the 1st differential gear mechanism P1 and the 2nd differential gear mechanism P2 are the double pinion planetary wheel, and the sun wheel of the 2nd differential gear mechanism P2 is connected by the 2nd frictional engagement element C-2 with pinion carrier.At this moment, the gear ring of the 2nd differential gear mechanism P2 is and the 3rd frictional engagement element B-1 bonded assembly braking element.
In Figure 10 (D) institute example, the 1st differential gear mechanism P1 and the 2nd differential gear mechanism P2 are the double pinion planetary wheel, and its position relation is just opposite with respect to input, output.This moment, the sun wheel of the 2nd differential gear mechanism P2 was connected by the 2nd frictional engagement element C-2 with pinion carrier.At this moment, the pinion carrier of the 2nd differential gear mechanism P2 is and the 3rd frictional engagement element B-1 bonded assembly braking element.
In Figure 10 (E) institute example, the 1st differential gear mechanism P1 is single miniature gears planetary wheel, and the 2nd differential gear mechanism P2 is the double pinion planetary wheel, and the pinion carrier of the 2nd differential gear mechanism P2 is connected by the 2nd frictional engagement element C-2 with gear ring.At this moment, the sun wheel of the 2nd differential gear mechanism P2 is and the 3rd frictional engagement element B-1 bonded assembly braking element.
In Figure 10 (F) institute example, the 1st differential gear mechanism P1 and the 2nd differential gear mechanism P2 are the double pinion planetary wheel, and the pinion carrier of the 2nd differential gear mechanism P2 is connected by the 2nd frictional engagement element C-2 with gear ring.At this moment, the sun wheel of the 2nd differential gear mechanism P2 is and the 3rd frictional engagement element B-1 bonded assembly braking element.
Then, in Figure 11 (A) institute example, the 1st differential gear mechanism P1 and the 2nd differential gear mechanism P2 are single miniature gears planetary wheel, and the sun wheel of the 2nd differential gear mechanism P2 is connected by the 2nd frictional engagement element C-2 with pinion carrier.At this moment, the gear ring of the 2nd differential gear mechanism P2 is and the 3rd frictional engagement element B-1 bonded assembly braking element.
In Figure 11 (B) institute example, the 1st differential gear mechanism P1 is the double pinion planetary wheel, and the 2nd differential gear mechanism P2 is single miniature gears planetary wheel, and the sun wheel of the 2nd differential gear mechanism P2 is connected by the 2nd frictional engagement element C-2 with pinion carrier.At this moment, the gear ring of the 2nd differential gear mechanism P2 is and the 3rd frictional engagement element B-1 bonded assembly braking element.
In Figure 11 (C) institute example, the 1st differential gear mechanism P1 is single miniature gears planetary wheel, and the 2nd differential gear mechanism P2 is the double pinion planetary wheel, and the sun wheel of the 2nd differential gear mechanism P2 is connected by the 2nd frictional engagement element C-2 with gear ring.At this moment, the pinion carrier of the 2nd differential gear mechanism P2 is and the 3rd frictional engagement element B-1 bonded assembly braking element.
At last, in Figure 11 (D) institute example, the 1st differential gear mechanism P1 and the 2nd differential gear mechanism P2 are the double pinion planetary wheel, and its position relation is just opposite with respect to input, output.This moment, the sun wheel of the 2nd differential gear mechanism P2 was connected by the 2nd frictional engagement element C-2 with pinion carrier.At this moment, the pinion carrier of the 2nd differential gear mechanism P2 is and the 3rd frictional engagement element B-1 bonded assembly braking element.
Also have, more than among each embodiment, the 2nd rotating machine MG2 is and the 2nd differential gear mechanism P2 direct connection, but the 2nd rotating machine MG2 also can be connected with the 2nd differential gear mechanism P2 by speed reduction gearing.At this moment, when speed reduction gearing is planetary gear apparatus, wherein 1 teeth parts are used for counter-force and support and be fixed, other 1 teeth parts is connected with the 2nd rotating machine MG2, among other 1 teeth parts and the 2nd differential gear mechanism P2 remove with the 1st rotating machine bonded assembly teeth parts be connected with teeth parts beyond the direct coupled teeth parts of the teeth parts of the 1st differential gear mechanism.As an example, for example can adopt that the sun wheel of planetary gear apparatus is connected with the 2nd rotating machine MG2, pinion carrier is fixed, the pinion carrier bonded assembly structure of gear ring and the 2nd differential gear mechanism P2.
Claims (8)
1. a hybrid drive is characterized in that: have
Accept the input block (12) of the propulsive effort of driving engine;
Output block (19) to the wheel output drive strength;
The 1st rotating machine (MG1) and the 2nd rotating machine (MG2);
The 1st differential gear mechanism (P1) and the 2nd differential gear mechanism (P2) that have 3 teeth parts at least; With
Have 3 1-the 3rd frictional engagement element (C-1, C-2, B-1) at least,
Wherein, 3 teeth parts of above-mentioned the 1st differential gear mechanism respectively with above-mentioned input block, the 1st rotating machine, and the 2nd rotating machine be connected,
3 teeth parts of above-mentioned the 2nd differential gear mechanism respectively with above-mentioned output block, the 2nd rotating machine, and the 1st frictional engagement element (C-1) be connected,
Can be connected with above-mentioned the 2nd differential gear mechanism by above-mentioned the 1st frictional engagement element with 1 teeth parts in above-mentioned the 1st differential gear mechanism of above-mentioned the 1st rotating machine bonded assembly,
And any 2 teeth parts in above-mentioned the 2nd differential gear mechanism interconnect by the 2nd frictional engagement element (C-2).
2. hybrid drive according to claim 1 is characterized in that:
Above-mentioned the 3rd frictional engagement element is connected with teeth parts that are connected with above-mentioned the 1st frictional engagement element in above-mentioned the 2nd differential gear mechanism.
3. hybrid drive according to claim 2 is characterized in that:
Above-mentioned the 3rd frictional engagement element slows down in conjunction with the rotating speed that makes above-mentioned the 2nd rotating machine (MG2) by it.
4. hybrid drive according to claim 1 is characterized in that:
Above-mentioned the 2nd frictional engagement element makes above-mentioned output block and the 2nd rotating machine be rotated with same rotational speed by its combination.
5. hybrid drive according to claim 2 is characterized in that:
When the rotating speed of above-mentioned output block rotation and above-mentioned the 1st rotating machine (MG1) is approximately 0, remove the combination of above-mentioned the 3rd frictional engagement element, make above-mentioned the 1st frictional engagement combination of elements.
6. hybrid drive according to claim 1 is characterized in that:
When the rotation of above-mentioned output block and above-mentioned input block, output block, the 1st rotating machine, and the 2nd rotating machine in when having at least 2 rotating speed roughly the same, remove the combination of above-mentioned the 1st frictional engagement element, make above-mentioned the 2nd frictional engagement combination of elements.
7. hybrid drive according to claim 1 is characterized in that:
The the above-mentioned the 1st and the 2nd differential gear mechanism is by the combination of above-mentioned the 1st frictional engagement element, become wheel word with 4 degree of freedom, this have 4 degree of freedom wheel word each teeth parts respectively with above-mentioned input block, output block, the 1st rotating machine, and the 2nd rotating machine be connected.
8. hybrid drive according to claim 2 is characterized in that:
With the teeth parts of above-mentioned the 1st rotating machine bonded assembly the 1st differential gear mechanism, be connected with teeth parts that are connected with the 3rd frictional engagement element in above-mentioned the 2nd differential gear mechanism by above-mentioned the 1st frictional engagement element.
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|---|---|---|---|
| CNB2005100629194A CN100551731C (en) | 2005-03-30 | 2005-03-30 | Hybrid drive |
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| Application Number | Priority Date | Filing Date | Title |
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| CNB2005100629194A CN100551731C (en) | 2005-03-30 | 2005-03-30 | Hybrid drive |
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| CN100551731C true CN100551731C (en) | 2009-10-21 |
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Families Citing this family (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4222406B2 (en) * | 2006-10-24 | 2009-02-12 | トヨタ自動車株式会社 | Power output device and hybrid vehicle |
| JP4169081B1 (en) * | 2007-05-25 | 2008-10-22 | トヨタ自動車株式会社 | POWER OUTPUT DEVICE, HYBRID VEHICLE HAVING THE SAME, AND METHOD FOR CONTROLLING POWER OUTPUT DEVICE |
| JP4229205B1 (en) * | 2007-09-18 | 2009-02-25 | トヨタ自動車株式会社 | Control device for hybrid drive |
| JP5035631B2 (en) * | 2008-04-28 | 2012-09-26 | アイシン・エィ・ダブリュ株式会社 | Drive device |
| KR101020980B1 (en) * | 2009-04-23 | 2011-03-09 | 현대자동차주식회사 | Power train for Hybrid Vehicle |
| WO2011125777A1 (en) * | 2010-03-31 | 2011-10-13 | アイシン・エィ・ダブリュ株式会社 | Control device |
| CN102795093B (en) * | 2011-05-24 | 2015-03-18 | 上海华普汽车有限公司 | Hybrid power transmission device and hybrid power automobile |
| JP6252738B2 (en) * | 2013-09-13 | 2017-12-27 | 三菱自動車工業株式会社 | Transaxle device |
| JP2016020202A (en) * | 2014-06-19 | 2016-02-04 | トヨタ自動車株式会社 | Hybrid-vehicular drive system |
| CN104175860B (en) * | 2014-08-08 | 2017-02-15 | 郑州宇通客车股份有限公司 | Planetary series-parallel power system and vehicle adopting same |
| CN108099575A (en) * | 2016-11-25 | 2018-06-01 | 上海电驱动股份有限公司 | A kind of hybrid power system using double planet wheel rows of mixing configuration |
| CN108099577B (en) * | 2016-11-25 | 2024-02-09 | 潍坊佩特来电器有限公司 | Hybrid power system using multimode power coupling device |
| CN106627097B (en) * | 2017-02-28 | 2018-04-13 | 吉林大学 | Double planet wheel rows of mixing bimodulus power dividing type hybrid power system |
| CN111114280B (en) * | 2018-10-31 | 2021-12-07 | 比亚迪股份有限公司 | Power driving system and vehicle |
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