CN103189626A - Drive system - Google Patents

Drive system Download PDF

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Publication number
CN103189626A
CN103189626A CN2011800518227A CN201180051822A CN103189626A CN 103189626 A CN103189626 A CN 103189626A CN 2011800518227 A CN2011800518227 A CN 2011800518227A CN 201180051822 A CN201180051822 A CN 201180051822A CN 103189626 A CN103189626 A CN 103189626A
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CN
China
Prior art keywords
bent axle
cylinder
driving force
generation device
swing
Prior art date
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Granted
Application number
CN2011800518227A
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Chinese (zh)
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CN103189626B (en
Inventor
市川和树
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Honda Motor Co Ltd
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Honda Motor Co Ltd
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Publication of CN103189626A publication Critical patent/CN103189626A/en
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Publication of CN103189626B publication Critical patent/CN103189626B/en
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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
    • B60K6/42—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 the architecture of the hybrid electric vehicle
    • B60K6/48—Parallel type
    • B60K6/485—Motor-assist type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B73/00—Combinations of two or more engines, not otherwise provided for
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/06—Engines with means for equalising torque
    • F02B75/065—Engines with means for equalising torque with double connecting rods or crankshafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D25/00—Controlling two or more co-operating engines
    • F02D25/04—Controlling two or more co-operating engines by cutting-out engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H21/00—Gearings comprising primarily only links or levers, with or without slides
    • F16H21/10—Gearings comprising primarily only links or levers, with or without slides all movement being in, or parallel to, a single plane
    • F16H21/16—Gearings comprising primarily only links or levers, with or without slides all movement being in, or parallel to, a single plane for interconverting rotary motion and reciprocating motion
    • F16H21/18—Crank gearings; Eccentric gearings
    • F16H21/20—Crank gearings; Eccentric gearings with adjustment of throw
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H31/00—Other gearings with freewheeling members or other intermittently driving members
    • F16H31/001—Mechanisms with freewheeling members
    • 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
    • B60K6/42—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 the architecture of the hybrid electric vehicle
    • B60K6/48—Parallel type
    • B60K2006/4808—Electric machine connected or connectable to gearbox output shaft
    • 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

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Transmission Devices (AREA)

Abstract

Provided is a drive system which does not require a gear mechanism for reversing the direction of the rotation of the drive shaft, and which reduces vibration. This drive system (1) is provided with: a first internal combustion engine (10) having a first crank shaft (12); a second internal combustion engine (20), having a second crank shaft (22) which is positioned parallel to the first crank shaft (12) and rotates in the reverse direction of the first crank shaft (12); a first vibration conversion rod (40A) which converts the rotational movement of the first crank shaft (12) into a vibrational movement; output shafts (first output shaft (71A) and second output shaft (71B)) which are rotated in a single direction by force provided by the first internal combustion engine (10) and the second internal combustion engine (20); and a first one-way clutch (60A) that transmits the force of a first vibration conversion rod (40A), generated only in one direction, to the output shaft.

Description

Drive system
Technical field
The present invention relates to have the drive system of a plurality of live axles.
Background technique
The known internal-combustion engine (with reference to patent documentation 1) that an output shaft that possesses a plurality of bent axles (the 1st live axle, the 2nd live axle) independently and be rotated by the power from these a plurality of bent axles is arranged in the past.
The prior art document
Patent documentation
Patent documentation 1: Japanese Patent Publication 63-35822 communique
Summary of the invention
Invent problem to be solved
Herein, in possessing the internal-combustion engine of a plurality of bent axles, when the sense of rotation with a plurality of bent axles is made as same direction, the vibration that produces in each bent axle etc. becomes same phase, therefore be made as preferably that the sense of rotation that makes a bent axle is opposite, the structure of the vibration of between a plurality of bent axles, cancelling out each other etc., thereby reduce the vibration of internal-combustion engine.
Therefore, also consider the sense of rotation opposite configuration append gear and to make a bent axle, but except components number increased, the transmission efficiency of power reduced also.
Therefore, problem of the present invention is to provide a kind of drive system that neither needs to have reduced again be used to the opposite gear mechanism of the sense of rotation that makes live axle vibration.
Be used for solving the means of problem
As the means that are used for solving described problem, the present invention is a kind of drive system, it is characterized in that, it has: the 1st driving force generation device, and it has the 1st live axle; The 2nd driving force generation device, it has 2nd live axle opposite with described the 1st live axle with described the 1st live axle parallel configuration and sense of rotation; The 1st swing converter unit, it is transformed to oscillating motion with rotatablely moving of described the 1st live axle; Output shaft, it is by from the power of described the 1st driving force generation device and described the 2nd driving force generation device, rotates in a direction as the sense of rotation of described the 2nd live axle; And the 1st overrunning clutch, its only with the transmission of power of the oscillating motion of a direction of described the 1st swing converter unit to described output shaft.
According to this drive system, the 1st swing converter unit is transformed to oscillating motion with rotatablely moving of the 1st live axle, the 1st overrunning clutch only with the transmission of power of the oscillating motion of a direction of the 1st swing converter unit to the output shaft towards the rotation of direction.That is, can be under the situation via the opposite gear of the sense of rotation that is used for making live axle not, the power of the 1st live axle and the 2nd live axle is delivered to output shaft with keeping higher transfer efficient.
In addition, the sense of rotation of the 1st live axle is opposite with the sense of rotation of the 2nd live axle, and therefore the vibration that produces in the 1st live axle is opposite with the phase place of the vibration that produces in the 2nd live axle, the vibration of cancelling out each other.Thus, can reduce the vibration of drive system integral body.
In addition, in described drive system, preferably have: the 2nd swing converter unit, it is transformed to oscillating motion with rotatablely moving of described the 2nd live axle; And the 2nd overrunning clutch, its only with the transmission of power of the oscillating motion of a direction of described the 2nd swing converter unit to described output shaft.
According to this drive system, can rotatablely moving of the 2nd live axle be transformed to oscillating motion by the 2nd swing converter unit, by the 2nd overrunning clutch only with the transmission of power of the oscillating motion of a direction of the 2nd swing converter unit to output shaft.
In addition, in described drive system, preferably, described the 1st swing converter unit has the 1st rotary part that is rotated by rotatablely moving of described the 1st live axle, with the 1st swing part that carries out oscillating motion by the rotation of described the 1st rotary part, described the 2nd swing converter unit has the 2nd rotary part that is rotated by rotatablely moving of described the 2nd live axle, with the 2nd swing part that carries out oscillating motion by the rotation of described the 2nd rotary part, described drive system also has: the 1st turning radius change mechanism, it changes the angular velocity of described the 1st swing part by the turning radius of described the 1st rotary part of change; And the 2nd turning radius change mechanism, it changes the angular velocity of described the 2nd swing part by the turning radius of described the 2nd rotary part of change.
Herein, " rotation of the 1st rotary part " refer to that the fulcrum of the 1st rotary part (is the 1st fulcrum O3, Fig. 4) (is input central axis O1, Fig. 4) rotation in mode of execution described later around the central axis of the 1st live axle in mode of execution described later.Like this too about the 2nd rotary part.
According to this drive system, the 1st turning radius change mechanism can change angular velocity (swing speed) and the pendulum angle (wobble amplitude) of the 1st swing part by the turning radius of change the 1st rotary part.In addition, the 2nd turning radius change mechanism can change angular velocity and the pendulum angle of the 2nd swing part by the turning radius of change the 2nd rotary part.
That is, as long as the 1st turning radius change mechanism increases the turning radius of the 1st rotary part, just can increase angular velocity and the pendulum angle of the 1st swing part.On the other hand, as long as the 1st turning radius change mechanism reduces the turning radius of the 1st rotary part, just can reduce angular velocity and the pendulum angle of the 1st swing part.
In addition, like this too about the 2nd turning radius change mechanism.
In addition, in described drive system, preferably, described the 1st driving force generation device and described the 2nd driving force generation device are Reciprocating engines, and disposed adjacent, described the 1st live axle is the 1st bent axle, described the 2nd live axle is the 2nd bent axle, the sense of rotation of the sense of rotation of described the 1st bent axle and described the 2nd bent axle is set to: in the axial view of described the 1st bent axle and described the 2nd bent axle, in the medial region of described the 1st bent axle and described the 2nd bent axle, become expansion stroke, described the 1st driving force generation device has the 1st cylinder, described the 2nd driving force generation device has the 2nd cylinder, described the 1st cylinder is put to the lateral deviation near described the 2nd cylinder, and described the 2nd cylinder is put to the lateral deviation near described the 1st cylinder.
Herein, the 2nd cylinder that " the 1st driving force generation device and the 2nd driving force generation device disposed adjacent " refers to the 1st cylinder of the 1st driving force generation device and the 2nd driving force generation device the 1st bent axle or the 2nd bent axle axially at least a portion overlapping, the adjacent arrangement of at least a portion of the 1st driving force generation device (the 1st cylinder) and the 2nd driving force generation device (the 2nd cylinder).That is, not only can be the 1st driving force generation device and the 2nd driving force generation device overlapping form fully, jagged form is overlapped, for example is at least a portion that also comprises the 1st driving force generation device and the 2nd driving force generation device.
In addition, not only can be the 1st cylinder axis form parallel with the 2nd cylinder axis at the center of passing through the 2nd cylinder by the center of the 1st cylinder, for example also be included in the axial view of the 1st bent axle and the 2nd bent axle, the 1st cylinder axis and the 2nd cylinder axis are the form of " V font ".
In addition, " sense of rotation of the sense of rotation of the 1st bent axle and the 2nd bent axle is set to: in the axial view of the 1st bent axle and the 2nd bent axle, become expansion stroke in the medial region of the 1st bent axle and the 2nd bent axle " refers to that the sense of rotation of the 1st bent axle and the sense of rotation of the 2nd bent axle are set to: the 1st crank pin of the 1st bent axle in the expansion stroke and the 2nd crank pin of the 2nd bent axle in the expansion stroke are in " inboard " of the 1st bent axle (line) and the 2nd bent axle (line) rotation.
According to this drive system, the 1st driving force generation device and the 2nd driving force generation device are the offset crankshaft structures, therefore in expansion stroke, the lateral force that is applied to the 2nd piston of the 1st piston of the 1st driving force generation device and the 2nd driving force generation device diminishes, thereby can reduce the friction (frictional force) that generates between piston and cylinder side face.
In addition, the 1st cylinder and the 2nd cylinder are put towards a lateral deviation that approaches mutually, therefore are difficult for forming dead space between the 1st driving force generation device and the 2nd driving force generation device, thereby can make entire system miniaturization/lightweight.That is, be under the situation of one-body molded product at the 1st cylinder block that is formed with the 1st cylinder with the 2nd cylinder block that is formed with the 2nd cylinder for example, can make cylinder block integral miniaturization/lightweight.
In addition, in described drive system, preferably, described the 1st driving force generation device and described the 2nd driving force generation device are Reciprocating engines, and disposed adjacent, described the 1st live axle is the 1st bent axle, described the 2nd live axle is the 2nd bent axle, the sense of rotation of the sense of rotation of described the 1st bent axle and described the 2nd bent axle is set to: in the axial view of described the 1st bent axle and described the 2nd bent axle, in the exterior lateral area of described the 1st bent axle and described the 2nd bent axle, become expansion stroke, described the 1st driving force generation device has the 1st cylinder, described the 2nd driving force generation device has the 2nd cylinder, described the 1st cylinder is put to the lateral deviation away from described the 2nd cylinder, and described the 2nd cylinder is put to the lateral deviation away from described the 1st cylinder.
Herein, " sense of rotation of the sense of rotation of the 1st bent axle and the 2nd bent axle is set to: in the axial view of the 1st bent axle and the 2nd bent axle, become expansion stroke in the exterior lateral area of the 1st bent axle and the 2nd bent axle " refers to that the sense of rotation of the 1st bent axle and the sense of rotation of the 2nd bent axle are set to: the 1st crank pin of the 1st bent axle in the expansion stroke and the 2nd crank pin of the 2nd bent axle in the expansion stroke are in " outside " of the 1st bent axle (line) and the 2nd bent axle (line) rotation.
According to this drive system, the 1st driving force generation device and the 2nd driving force generation device are the offset crankshaft structures, therefore in expansion stroke, the lateral force that is applied to the 2nd piston of the 1st piston of the 1st driving force generation device and the 2nd driving force generation device diminishes, thereby can reduce the friction (frictional force) that generates between piston and cylinder side face.
In addition, the 1st cylinder and the 2nd cylinder towards mutually away from a lateral deviation put, therefore the space between the 2nd head of the 1st head of the 1st driving force generation device (the 1st internal-combustion engine) and the 2nd driving force generation device (the 2nd internal-combustion engine) becomes big, layout changing valve system easily for example, the rotational speed of this change valve system and bent axle changes the switching opportunity of suction valve/outlet valve accordingly.
And, the passage of can also the space content between the 1st head and the 2nd head change places layout air inlet or exhaust.
The effect of invention
According to the present invention, can provide a kind of drive system that neither needs to have reduced again be used to the opposite gear mechanism of the sense of rotation that makes live axle vibration.And, about each side of the present invention and effect and other effects and further feature, become clearer by the detailed description of the present invention exemplary and nonrestrictive mode of execution that will narrate with reference to accompanying drawing in the back.
Description of drawings
Fig. 1 is the structural drawing of the drive system of present embodiment.
Fig. 2 is the 1st internal-combustion engine of present embodiment and the sectional view of the 2nd internal-combustion engine.
Fig. 3 is the 1st speed changer of present embodiment and the sectional view of the 1st overrunning clutch.
Fig. 4 is the 1st speed changer of present embodiment and the side view of the 1st overrunning clutch.
Fig. 5 is the 1st speed changer of present embodiment and the side view of the 1st overrunning clutch, (a) show turning radius r1(offset) maximum and the less state of gear ratio i, (b) show that turning radius r1 mediates and gear ratio i is medium state, (c) show turning radius r1 and be 0 and gear ratio i be the state of ∞ (infinity).
Fig. 6 (a)～(d) is the side view of the 1st speed changer and the 1st overrunning clutch, shows rotatablely moving and oscillating motion under the state of turning radius r1 " maximum " and gear ratio i " less ".
Fig. 7 (a)～(d) is the side view of the 1st speed changer and the 1st overrunning clutch, and showing turning radius r1 is that " centre " and gear ratio i are rotatablely moving and oscillating motion under the state of " medium ".
Fig. 8 (a)～(d) is the side view of the 1st speed changer and the 1st overrunning clutch, and showing turning radius r1 is that " 0 " and gear ratio i are rotatablely moving and oscillating motion under the state of " ∞ (infinity) ".
Fig. 9 is the plotted curve that the relation between the angular velocity omega 2 of the angle of swing θ 1 of input shaft and outer race (swing part) is shown.
Figure 10 is the plotted curve that the relation between the Sliding velocity of the angle of swing θ 1 of input shaft and outer race (swing part) is shown.
Figure 11 is the 1st internal-combustion engine of variation and the sectional view of the 2nd internal-combustion engine.
Embodiment
Below with reference to Fig. 1～Figure 10 an embodiment of the invention are described.
" structure of drive system "
The drive system 1 of present embodiment shown in Figure 1 is equipped on not shown hybrid vehicle (vehicle, moving body), is the system that produces the driving force of hybrid vehicle.
But the kind of vehicle is not limited thereto, and also can be gasoline car.In addition, being not limited to four-wheel wagon, also can be cart, tricycle.
Drive system 1 has: the 1st internal-combustion engine 10(the 1st driving force generation device) and the 2nd internal-combustion engine 20(the 2nd driving force generation device); The 1st speed changer 30A and the 2nd speed changer 30B; The 1st one-way clutch apparatus (with reference to Fig. 3) with a plurality of (being 6 herein) the 1st overrunning clutch 60A; The 2nd one-way clutch apparatus (with reference to Fig. 3) with a plurality of (being 6 herein) the 2nd overrunning clutch 60B; When vehicle advances, become one and towards the positive direction (unidirectional) rotation the 1st output shaft 71A and the 2nd output shaft 71B; And system carried out electronically controlled ECU80(Electronic Control Unit, electric control device).
In addition, " forward " is the direction corresponding with the direction of advance of vehicle, and " oppositely " is the direction corresponding with the direction of retreat of vehicle.
＜the 1 internal-combustion engine, the 2nd internal-combustion engine 〉
In the present embodiment, the 1st internal-combustion engine 10 and the 2nd internal-combustion engine 20 be respectively series connection twin cylinder type and constitute can drive Reciprocating engine.
The 1st cylinder block 11 of the 1st internal-combustion engine 10 and the 2nd cylinder block 21 of the 2nd internal-combustion engine 20 constitute (with reference to Fig. 2) by one-body molded product, and the 1st internal-combustion engine 10 and the 2nd internal-combustion engine 20 be adjacent alignment arrangements integratedly.In addition, in Fig. 1, for easy understanding, the 1st internal-combustion engine 10 and the 2nd internal-combustion engine 20 have been put down in writing respectively suitably.
Two the 1st cylinders 13 of the 1st internal-combustion engine 10, two the 2nd cylinders 23 of the 13 and the 2nd internal- combustion engine 20,23 are at the 1st bent axle 12(or the 2nd bent axle 22) axially on do not stagger (with reference to Fig. 1).In addition, the 2nd cylinder axis L23 parallel (with reference to Fig. 2) at the 1st cylinder axis L13 at the center by the 1st cylinder 13 and center by the 2nd cylinder 23.
But the 1st cylinder 13, the 13 and the 2nd cylinder 23,23 not only can be overlapping arrangements fully so in the axial direction, for example can also overlap, and the 1st cylinder 13, the 13 and the 2nd cylinder 23,23 indentations are arranged.
The 1st bent axle 12(the 1st live axle of the 1st internal-combustion engine 10) with the 2nd bent axle 22(the 2nd live axle of the 2nd internal-combustion engine 20) spin axis dispose in parallel to each other, and in Fig. 2, be designed to the 1st bent axle 12 to anticlockwise, the 2nd bent axle 22 is to right rotation.That is, the sense of rotation of the 1st bent axle 12 and the 2nd bent axle 22 is opposite each other.
The words that further describe, as shown in Figure 2, the sense of rotation (to right rotation) of the sense of rotation of the 1st bent axle 12 (to anticlockwise) and the 2nd bent axle 22 is set to: in the side view (axial view of the 1st bent axle 12, the 2nd bent axle 22) of the 1st internal-combustion engine 10 and the 2nd internal-combustion engine 20, become expansion stroke in the medial region of the 1st bent axle 12 and the 2nd bent axle 22.
Thus, the 1st bent axle 12 is opposite with the sense of rotation of the 2nd bent axle 22, therefore follow the 1st bent axle 12 rotation vibration with follow the vibration of the rotation of the 2nd bent axle 22 to cancel out each other, thereby reduced the vibration of the 1st internal-combustion engine 10 and the 2nd internal-combustion engine 20.
In addition, the 1st internal-combustion engine 10 and the 2nd internal-combustion engine 20 have adopted the offset crankshaft structure respectively, and the 1st cylinder 13 and the 2nd cylinder 23 are setovered with respect to the 1st bent axle 12, the 2nd bent axle 22 in the mode that approaches mutually.
That is, the 1st cylinder 13 is to putting near a lateral deviation of the 2nd cylinder 23, and the 2nd cylinder 23 of the 2nd internal-combustion engine 20 is put to the lateral deviation near the 1st cylinder 13 of the 1st internal-combustion engine 10.
That is, the 1st axis L12 that the 1st cylinder axis L13 compares by the 1st bent axle 12 puts to the 2nd cylinder 23 1 lateral deviations, and the 2nd axis L22 that the 2nd cylinder axis L23 compares by the 2nd bent axle 22 puts to the 1st cylinder 13 1 lateral deviations.
In addition, the 1st crank axle L12 is imaginary line parallel with the 1st cylinder axis L13 and the spin axis by the 1st bent axle 12.In addition, the 2nd crank axle L22 is imaginary line parallel with the 2nd cylinder axis L23 and the spin axis by the 2nd bent axle 22.
Thus, because the 1st internal-combustion engine 10 and the 2nd internal-combustion engine 20 have adopted the offset crankshaft structure, therefore in expansion stroke, the lateral force that is applied to the 2nd piston 24 of the 1st piston 14 of the 1st internal-combustion engine 10 and the 2nd internal-combustion engine 20 diminishes respectively.
Thus, reduced respectively between the inner peripheral surface of the 1st piston 14 and the 1st cylinder 13 and the friction (frictional force) that generates between the inner peripheral surface of the 2nd piston 24 and the 2nd cylinder 23.Consequently, distance between the 1st cylinder 13 and the 2nd cylinder 23 diminishes, namely can attenuate the 1st cylinder 13 and the 2nd cylinder 23 between cylinder wall portion, thereby can realize the 1st cylinder block 11(the 1st internal-combustion engine 10) and the 2nd cylinder block 21(the 2nd internal-combustion engine 20) miniaturization/lightweight.
The air displacement of this 1st internal-combustion engine 10 and the 2nd internal-combustion engine 20 is unequal, is made of different air displacemenies.For example, the 1st internal-combustion engine 10 is designed to 600cc, the 2nd internal-combustion engine 20 is designed to 1000cc.
Thus, the 1st internal-combustion engine 10 has different efficient points with the 2nd internal-combustion engine 20.And, in the present embodiment, in efficient point selection driving the 1st internal-combustion engine 10 and/or the 2nd internal-combustion engine 20, the 1st speed changer 30A, the 2nd speed changer 30B also with the request amount of travelling (accelerator open degree etc.) accordingly with power speed changing and be delivered to output shaft (the 1st output shaft 71A and the 2nd output shaft 71B), so the rideability of hybrid vehicle can not descend.
In addition, efficient point refers to the less zone of value of brake horsepower specific fuel consumption (BSFC:Brake Specific Fuel Consumption).
＜the 1 speed changer, the 2nd speed changer 〉
As Fig. 1, shown in Figure 3, the 1st speed changer 30A is following mechanism: rotatablely moving of the 1st bent axle 12 is transformed to oscillating motion, this oscillating motion is delivered to the 1st overrunning clutch 60A, and with its angular velocity omega 2(swing speed)/pendulum angle θ 2(wobble amplitude) be made as variable (with reference to Fig. 4), make gear ratio i(ratio) speed change infinitely infinitely.
In addition, " rotational speed of the rotational speed of gear ratio i=input shaft 51/the 1st output shaft 71A ", " rotational speed of the 1st output shaft 71A " under this situation are " rotational speeies of only swinging (power) the 1st output shaft 71A when being rotated with the forward of outer race 62 ".
As shown in Figure 3, Figure 4, this 1st speed changer 30A has: 6 the 1st swing conversion rod 40A(the 1st swing converter units that rotatablely moving of the 1st bent axle 12 are transformed to oscillating motion); And the 1st turning radius change 50A of mechanism, its by change continuously owing to be transfused to rotary base ring 41(the 1st rotary part of each the 1st swing conversion rod 40A that rotatablely moving of the 1st bent axle 12 rotate) turning radius r1, change swing part 42(the 1st swing part) angular velocity omega 2(swing speed) and pendulum angle θ 2(wobble amplitude).
In addition, turning radius r1 is input central axis O1 and as the distance between the 1st fulcrum O3 at the center of disk 52.In addition, the oscillation center of swing part 42 is fixed on the output center axes O 2 of the 1st output shaft 71A, the distance between pendulum radius r2(the 2nd fulcrum O4 and the output center axes O 2) also fixing.
In addition, the 1st swing conversion rod 40A, the described later the 2nd quantity of swinging conversion rod 40B, eccentric part 51b, disk 52 etc. can freely be changed.
Then, as Fig. 1, shown in Figure 3, the 2nd speed changer 30B is following mechanism: rotatablely moving of the 2nd bent axle 22 is transformed to oscillating motion, this oscillating motion is delivered to the 2nd overrunning clutch 60B, and with its angular velocity omega 2(swing speed)/pendulum angle θ 2(wobble amplitude) be made as variable (with reference to Fig. 4), make gear ratio i(ratio) speed change infinitely infinitely.
As shown in Figure 3, Figure 4, this 2nd speed changer 30B has: 6 the 2nd swing conversion rod 40B(the 2nd swing converter units that rotatablely moving of the 2nd bent axle 22 are transformed to oscillating motion); And the 2nd turning radius change 50B of mechanism, its by change continuously owing to be transfused to rotary base ring 41(the 2nd rotary part of the 2nd swing conversion rod 40B that rotatablely moving of the 2nd bent axle 22 rotate) turning radius r1, change swing part 42(the 2nd swing part) angular velocity omega 2(swing speed) and pendulum angle θ 2(wobble amplitude).
Herein, the 1st speed changer 30A is identical structure with the 2nd speed changer 30B, therefore following the 1st speed changer 30A is specifically described.
＜the 1 speed changer-the 1st turning radius change mechanism 〉
As shown in Figure 3, Figure 4, the 1st turning radius change 50A of mechanism has: connect and be transfused to the input part 51 of the power of the 1st bent axle 12 with the 1st bent axle 12; 6 disks 52; Change turning radius r1(eccentric arm, offset by making the 52 relative rotations of input shaft 51 and disk) small gear 53; The direct current motor 54 that small gear 53 is rotated; And reducing gear 55.
Input shaft 51 is supported the 58a of wall portion, the 58b of wall portion that constitutes case of transmission 58 via bearing 59a, 59b with free rotation mode.In addition, the input central axis O1 consistent with the spin axis of the 1st bent axle 12 (with reference to Fig. 3) of input shaft 51.
In Fig. 3, the right-hand member side (is distolateral) of input shaft 51 connects with the 1st bent axle 12.And, input shaft 51 and the 1st bent axle 12 integratedly with angular velocity omega 1(with reference to Fig. 4) rotation.
In addition, input shaft 51 has the hollow portion 51a that allows small gear 53 insert with free rotation mode on its input central axis O1.In addition, the part of hollow portion 51a is at the radial outside opening, thus small gear 53 and internal gear 52b engagement (with reference to Fig. 4).
And, input shaft 51 have 6 in axial view with respect to input central axis O1 with the eccentric part 51b(of the circular of certain eccentric distance bias with reference to Fig. 3, Fig. 4).In the present embodiment, 6 eccentric part 51b input shaft 51 axially on uniformly-spaced configuration (with reference to Fig. 3), and week upwards with uniformly-spaced (60 ° of intervals) configuration.
Thus, the phase place of the oscillating motion of 6 outer races 62 of 6 the 1st overrunning clutch 60A described later staggers (with reference to Figure 10) with uniformly-spaced (60 ° of intervals), consequently, transmit the power forward of the oscillating motion of 6 outer races 62 continuously to inner race 61 from phase shifting and 6 outer races 62 carrying out oscillating motion.
6 disks 52 are arranged at 6 eccentric part 51b(respectively with reference to Fig. 3).
Further specify, as shown in Figure 4, each disk 52 is rounded.And, in the position of departing from as the 1st fulcrum O3 at the center of disk 52, be formed with circular eccentric opening 52a, in eccentric opening 52a, rotatably be embedded with eccentric part 51b.In addition, the inner peripheral surface at eccentric opening 52a is formed with internal gear 52b, internal gear 52b and small gear 53 engagements.
Small gear 53 has: (1) locking eccentric part 51b and disk 52(keep relative position) and the function of maintenance turning radius r1; (2) make eccentric part 51b and the disk 52 relative functions of rotating and changing turning radius r1.
At small gear 53 and eccentric part 51b(input shaft the 51, the 1st bent axle 12) when rotating synchronously, be small gear 53 and eccentric part 51b(input shaft the 51, the 1st bent axle 12) when rotating with same rotational speed, keep the relative position between eccentric part 51b and the disk 52, namely, eccentric part 51b and the rotation of disk 52 one keep turning radius r1.
On the other hand, at small gear 53 and eccentric part 51b during with different rotational speed (high rotational speed/low rotational speed) rotation, rotate around eccentric part 51b is relative at the disk 52 of internal gear 52b place engagement with small gear 53, the result can change turning radius r1.
Direct current motor 54 makes small gear 53 rotate with suitable rotational speed according to the instruction rotation of ECU80.The output shaft of direct current motor 54 is via reducing gear 55(planetary gears) be connected with small gear 53, the output of direct current motor 54 is decelerated to about 120:1, and is imported into small gear 53.
＜the 1 speed changer-the 1st swing arm 〉
As shown in Figure 4, the 1st swing conversion rod 40A has: rotary base ring 41, and it is transfused to rotatablely moving of input shaft 51; Swing part 42, itself and rotary base ring 41 are one, and its oscillating motion is outputed to the 1st overrunning clutch 60A; And bearing 43.
Rotary base ring 41 is configured to via the bearing 43 outer disks 52 that are embedded into.Swing part 42 is attached to the outer race 62 of the 1st overrunning clutch 60A in the mode of freely rotating via pin 44.
Thus, rotary base ring 41 can relatively freely rotate with disk 52.Therefore, rotary base ring 41 with centered by input central axis O1 and with the disk 52 of turning radius r1 rotation, rotate synchronously, but rotary base ring 41 relatively rotates with disk 52, and therefore the 1st swing conversion rod 40A integral body is not rotated, thereby the 1st swing conversion rod 40A roughly keeps this posture.
And when rotary base ring 41 rotated a circle, no matter the size of turning radius r1 how, swing part 42 all carried out a reciprocating swing motion with circular-arc, and outer race 62 also carries out a reciprocating swing motion with circular-arc.
＜the 1 one-way clutch apparatus, the 2nd one-way clutch apparatus 〉
The 1st one-way clutch apparatus is as lower device: have 6 the 1st overrunning clutch 60A, 6 the 1st overrunning clutch 60A are only with the transmission of power of the forward of the swing part 42 of 6 the 1st swing conversion rod 40A the 1st output shaft 71A to the right side.
The 2nd one-way clutch apparatus is as lower device: have 6 the 2nd overrunning clutch 60B, 6 the 2nd overrunning clutch 60B are only with the transmission of power of the forward of the swing part 42 of 6 the 2nd swing conversion rod 40B the 2nd output shaft 71B to the left side.
But, the configuration of the 1st one-way clutch apparatus (the 1st overrunning clutch 60A), the 2nd one-way clutch apparatus (the 2nd overrunning clutch 60B) is not limited thereto, and for example can be only to the right the configuration of the 1st output shaft 71A transferring power of the 1st～the 2nd one-way clutch apparatus.
The 2nd overrunning clutch 60B is the structure identical with the 1st overrunning clutch 60A, therefore following the 1st overrunning clutch 60A is described.
At first, as shown in Figure 3, the 1st output shaft 71A(the 2nd output shaft 71B) be cylindric, via bearing 59c, bearing 59d, free rotation mode is supported the 58a of wall portion, the 58b of wall portion that constitutes case of transmission 58 centered by output center axes O 2.
And as shown in Figure 3, Figure 4, each the 1st overrunning clutch 60A has: inner race 61(clutch inner race), the outer circumferential face one of itself and the 1st output shaft 71A is fixed and is rotated with the 1st output shaft 71A one; Outer race 62(outer clutch race), it is arranged to the outer inner race 61 that is embedded into; The edge circumferentially is provided with a plurality of roller 63 between inner race 61 and outer race 62; And to the helical spring 64(force application part of each roller 63 application of force).
The swing part 42 that outer race 62 is swung conversion rod 40A in the mode and the 1st of freely rotating connects, and oscillating motion is carried out in the oscillating motion of outer race 62 and swing part 42 (reference arrow A1)/oppositely (reference arrow A2) in linkage towards the positive direction.
Roller 63 is made as mutual lock state/unlock state with inner race 61 and outer race 62, and each helical spring 64 becomes roller 63 courts the direction application of force of described lock state.
And, as shown in figure 10, surpassed inner race 61(the 1st output shaft 71A at the swing speed of the forward of outer race 62) the situation of rotational speed of forward under, outer race 62 and the 1st output shaft 71A become lock state (power delivery status) by roller 63.Thus, via the 1st overrunning clutch 60A the positive power that the 1st swing conversion rod 40A carries out the swing part 42 of oscillating motion is delivered to the 1st output shaft 71A, thereby the 1st output shaft 71A is rotated driving.
In addition, in Figure 10, represent the state of 61 transferring power from outer race 62 to inner race with thick line.In addition, as shown in figure 10, even the swing speed of the forward of outer race 62 below the rotational speed of inner race 61, in predetermined interval, also by the elastic force of roller 63, is delivered to inner race 61 with power from outer race 62.
The change situation of＜turning radius r1 〉
Here, with reference to Fig. 5 the situation of turning radius r1 change is described, then, the disk 52(rotary base ring 41 when with reference to Fig. 6～Fig. 8 different turning radius r1 being described) rotatablely move and the oscillating motion of swing part 42.
Shown in Fig. 5 (a), constitute the center at the 1st fulcrum O3(disk 52) with input central axis O1 farthest the time, turning radius r1 becomes " maximum ".
And, be rotated with the rotational speed different with eccentric part 51b at small gear 53, and eccentric part 51b shown in Fig. 5 (b), constituting the 1st fulcrum O3 and approaches with input central axis O1 during with disk 52 relative rotations, turning radius r1 becomes " medium ".
When the further relative rotation of eccentric part 51b and disk 52, shown in Fig. 5 (c), it is overlapping with input central axis O1 to constitute the 1st fulcrum O3, and turning radius r1 becomes " 0 ".
Thus, can between " maximum " and " 0 ", control turning radius r1 continuously.
Then, be under the state of " maximum " at the turning radius r1 shown in Fig. 5 (a), when making eccentric part 15b and small gear 53 rotation synchronously, as shown in Figure 6, eccentric part 51b, disk 52 and small gear 53 rotate under the state that turning radius r1 is remained " maximum " integratedly.
Under this situation, swing part 42(outer race 62) angular velocity omega 2 and pendulum angle θ 2 become " maximum " (with reference to Fig. 9).
In addition, " rotational speed of the rotational speed of gear ratio i=input shaft 51/the 1st output shaft 71A ", " radius (the fixed value) * angular velocity omega 2 of the swing speed=outer race 62 of outer race 62 ", so gear ratio i is " little ".
Then, be under the state of " medium " at the turning radius r1 shown in Fig. 5 (b), when making eccentric part 15b and small gear 53 rotation synchronously, as shown in Figure 7, eccentric part 51b, disk 52 and small gear 53 rotate under the state that turning radius r1 is remained " medium " integratedly.
Under this situation, swing part 42(outer race 62) angular velocity omega 2 and pendulum angle θ 2 become " medium " (with reference to Fig. 9).And gear ratio i also becomes " medium ".
Then, be under the state of " 0 " at the turning radius r1 shown in Fig. 5 (c), when making eccentric part 15b and small gear 53 rotation synchronously, as shown in Figure 8, eccentric part 51b, disk 52 and small gear 53 rotate under the state that turning radius r1 is remained " 0 " integratedly.That is, eccentric part 51b, disk 52 and small gear 53 dally in rotary base ring 41, and the 1st swing conversion rod 40A does not move.
Under this situation, swing part 42(outer race 62) angular velocity omega 2 and pendulum angle θ 2 become " 0 " (with reference to Fig. 9).And gear ratio i becomes " ∞ (infinity) ".
Thus under the state that keeps turning radius r1 (states that eccentric part 51b and small gear 53 rotate synchronously), no matter the size of turning radius r1 how, all makes the deflection period of the period of rotation of input shaft 51 and swing part 42 and outer race 62 synchronous.
Namely, in the present embodiment, by the 1st swing conversion rod 40A, the 1st turning radius change 50A of mechanism and the 1st overrunning clutch 60A, having constituted with input central axis O1, output center axes O 2, the 1st fulcrum O3, the 2nd fulcrum O4, output center axes O 2 these 4 nodes is four node linkage mechanisms of run-on point.
And by rotatablely moving of the 1st fulcrum O3 centered by input central axis O1, the 2nd fulcrum O4 is that oscillation center is carried out oscillating motion with output center axes O 2.
In addition, change angular velocity omega 2 and the pendulum angle θ 2 of the 2nd fulcrum O4 by the 1st turning radius change 50A of mechanism change turning radius r1.
<ECU>
Returning Fig. 1 goes on to say.
ECU80 carries out electronically controlled control gear to drive system 1, constitutes to comprise CPU, ROM, RAM, various interface and electronic circuit etc., according to being stored in its inner program, brings into play various functions, the control various device.
＜other structures 〉
Then, other structures to drive system 1 describe.
＜other structure-Di 1, the 2nd clutch, differential cross pin 〉
Drive system 1 has the 1st clutch 91A, the 2nd clutch 91B and differential cross pin 92(differential mechanism).
Further specify, the 1st output shaft 71A is attached to the differential carrier 93(that constitutes differential cross pin 92 and is driven in rotation parts via the 1st clutch 91A that is controlled by ECU80).The 2nd output shaft 71B is attached to differential carrier 93 via the 2nd clutch 91B by ECU80 control.
The 1st clutch 91A transmits/blocks power between the 1st output shaft 71A and differential carrier 93, the 2nd clutch 91B transmits/block power between the 2nd output shaft 71B and differential carrier 93.
Differential cross pin 92 has side gear and small gear in differential carrier 93.And, the side gear on right side with and the driving wheel 94A on right side be that the 1st live axle 95A of one connects, the side gear in left side with and the driving wheel 94B in left side be that the 2nd live axle 95B of one connects.Thus, the 1st live axle 95A(driving wheel 94A) and the 2nd live axle 95B(driving wheel 94B) carry out differential rotation via differential cross pin 92.
In addition, when vehicle advances, be controlled to usually that the 1st clutch 91A connects the 1st output shaft 71A and differential carrier 93, the 2 clutch 91B connect the 1st output shaft 71A and differential carrier 93.Thus, when vehicle advanced, common the 1st output shaft 71A and the 2nd output shaft 71B became one, towards the positive direction (direction that vehicle advances) rotation.
＜other structure-Di 1, the 2nd motor generator set, battery 〉
Drive system 1 has the 1st motor generator set 101, the 2nd motor generator set 102 and battery 103.
Battery 103 for example is type lithium ion and constitutes and can discharge and recharge, the electric power of giving and accepting between the 1st motor generator set 101, the 2nd motor generator set 102 and above-mentioned direct current motor 54,54.
Output shaft at the 1st motor generator set 101 fixedly has the 1st gear 104, the 1 gears 104 and the 2nd gear 105 engagements that are fixed to differential carrier 93.Thus, constitute the power of giving and accepting between the 1st motor generator set 101 and differential carrier 93, the 1st motor generator set 101 is as motor or generator performance function.
That is, under the situation as motor performance function, the 1st motor generator set 101 as power supply, under the situation as generator performance function, is charged to battery 103 with the generation power of the 1st motor generator set 101 with battery 103.
The 1st bent axle 12 of the output shaft of the 2nd motor generator set 102 and the 1st internal-combustion engine 10 connects.
In addition, make the 2nd motor generator set 102 as the situation of motor performance function, be about to battery 103 and drive to make it as the situation of motor performance function as power supply, for example be assist the 1st bent axle 12 rotation situation and as the situation of the starter motor performance function of the 1st internal-combustion engine 10.
On the other hand, making the 2nd motor generator set 102 is the situation that the generation power of the 2nd motor generator set 102 is charged to battery 103 as the situation of generator performance function.
＜other structure-lazy-tongs 〉
Drive system 1 has lazy-tongs 110, and these lazy-tongs 110 transmit/block power according to the instruction from ECU80 between the 2nd bent axle 22 and differential carrier 93.In addition, lazy-tongs 110 with transmission of power to the 2 bent axles 22, therefore also are known as starting clutch under the situation of starting the 2nd internal-combustion engine 20.
Lazy-tongs 110 have: the A gear 111 that is fixed to differential carrier 93; B gear 112, itself and A gear 111 mesh all the time, and are arranged to rotate freely around the 2nd bent axle 22; C gear 113, it is arranged to rotate around the 2nd bent axle 22 one; And sleeve 114, it is operated in the axial enterprising line slip of the 2nd bent axle 22 by the instruction according to ECU80, and C gear 113 and B gear 112 are carried out combination/releasing.
" effect/effect of drive system "
According to this drive system 1, obtain following effect, effect.
The sense of rotation of the 1st bent axle 12 and the 2nd bent axle 22 is opposite each other, therefore follow the 1st bent axle 12 rotation vibration with follow the vibration of the rotation of the 2nd bent axle 22 to cancel out each other, thereby can reduce the vibration of the 1st internal-combustion engine 10 and the 2nd internal-combustion engine 20.
In addition, the power of the power of the 1st internal-combustion engine 10 and the 2nd internal-combustion engine 20 not via gear be delivered to the 1st output shaft 71A, the 2nd output shaft 71B, so transmission efficiency can not reduce.
Owing to have the 1st turning radius change 50A of mechanism, the power that therefore can make the 1st bent axle 12 is speed change and be delivered to the 1st output shaft 71A infinitely infinitely.Owing to have the 2nd turning radius change 50B of mechanism, the power that therefore can make the 2nd bent axle 22 is speed change and be delivered to the 2nd output shaft 71B infinitely infinitely.
Thus, for example can also drive the 1st internal-combustion engine 10(600cc etc. at efficient point respectively) and the 2nd internal-combustion engine 20(1000cc etc.) in, suitably control gear ratio i by the 1st turning radius change 50A of mechanism and/or the 2nd turning radius change 50B of mechanism, and accelerate.
In addition, in the travelling of the power that utilizes the 2nd internal-combustion engine 20, be made as at the gear ratio i with the 1st turning radius change 50A of mechanism under the state of infinity (turning radius r1=0) and drive 102 generatings of the 1st internal-combustion engine 10 causes the 2nd motor generator set, and be charged to battery 103.
The 1st internal-combustion engine 10 and the 2nd internal-combustion engine 20 are offset crankshaft structures, and therefore in expansion stroke, the lateral force that is applied to the 1st piston 14 and the 2nd piston 24 diminishes, and can reduce the friction between the 1st piston 14 and the 2nd piston 24 and the cylinder inner peripheral surface.
In addition, the 1st cylinder 13 and the 2nd cylinder 23 are biased to mutually and approach, and therefore can make cylinder block integral miniaturization/lightweight.
" variation "
More than an embodiment of the invention are illustrated, but the invention is not restricted to this, for example can followingly change.
In the above-described embodiment, be made as and had the 1st swing conversion rod 40A(the 1st swing converter unit) and the 2nd swing conversion rod 40B(the 2nd swing converter unit) structure, do not have the 2nd swing conversion rod 40B but can be made as yet, and only have the structure of the 1st swing conversion rod 40A.
Under this situation, the mode that rotates towards the positive direction with the 2nd output shaft 71B directly connects the 2nd bent axle 22 and the 2nd output shaft 71B, and based on this situation, direction initialization is to be got final product by the 1st overrunning clutch 60A transferring power.
In the above-described embodiment, have eccentric part 51b, disk 52 and small gear 53 and constituted the 1st turning radius change 50A of mechanism, but concrete structure is not limited thereto.
For example, can be made as following structure: the plectane that and synchronous rotation coaxial with input shaft 51 are set, by along the sliding-groove that radially extends of this plectane etc., with the 1st fulcrum O3(with reference to Fig. 4) constitute and can slide diametrically, by actuator the 1st fulcrum O3 is radially slided, and be made as turning radius r1 variable.
In the above-described embodiment, be made as the structure (with reference to Fig. 4) of the turning radius r1 that changes the 1st fulcrum O3, but can substitute this with structure or except this structure, be made as by the 2nd fulcrum O4 is radially slided, change turning radius r2, and the structure of change angular velocity omega 2 and pendulum angle θ 2.
In addition, can also be made as following structure: telescopically constitutes the 1st swing conversion rod 40A, changes distance between the 1st fulcrum O3 and the 2nd fulcrum O4 by actuator, changes angular velocity omega 2 and pendulum angle θ 2 thus.
In the above-described embodiment, as shown in Figure 1, be made as the structure of have two internal-combustion engines (the 1st internal-combustion engine 10, the 2nd internal-combustion engine 20) and two speed changers (the 1st speed changer 30A, the 2nd speed changer 30B), but the quantity of internal-combustion engine and speed changer can be for more than 3.
In the above-described embodiment, as shown in Figure 2, illustration the 1st cylinder axis L13 structure parallel with the 2nd cylinder axis L23, but the 1st cylinder axis L13 and the 2nd cylinder axis L23 also can be " V fonts " slightly.In addition, even be " V font " like this, also we can say to belong to technical scope of the present invention.
In the above-described embodiment, as shown in Figure 2, illustration the 1st internal-combustion engine 10 and the 2nd internal-combustion engine 20 are structures of one, but the 1st internal-combustion engine 10 and the 2nd internal-combustion engine 20 also can be structures separately.Under situation about constituting so separately, the angle between the 1st internal-combustion engine 10 and the 2nd internal-combustion engine 20 can be set at 60 °, 180 ° etc. arbitrarily.
In the above-described embodiment, as shown in Figure 2, illustration the 1st bent axle 12 to anticlockwise, the 2nd bent axle 22 dextrorotary structures, but in addition, for example also can be as shown in Figure 11, be made as the structure of the 1st bent axle 12 to right rotation, the 2nd bent axle 22 to anticlockwise.And, when constituting like this, become expansion stroke in the exterior lateral area of the 1st bent axle 12 and the 2nd bent axle 22.
And, under situation about constituting like this, also as shown in figure 11, the 1st internal-combustion engine 10 and the 2nd internal-combustion engine 20 are made as the offset crankshaft structure.That is, be made as the 1st cylinder 13 to putting away from a lateral deviation of the 2nd cylinder 23, the 2nd cylinder 23 is to the structure of putting away from a lateral deviation of the 1st cylinder 13.
Thus, it is big that space between the 2nd head of the 1st head of the 1st internal-combustion engine 10 and the 2nd internal-combustion engine 20 becomes, layout changing valve system easily for example, and the rotational speed of this change valve system and bent axle changes the switching opportunity of suction valve/outlet valve accordingly.In addition, can also the space content between the 1st head and the 2nd head the change places passage of layout air inlet or exhaust.
In the above-described embodiment, as shown in Figure 2, illustration the 1st internal-combustion engine 10 and the 2nd internal-combustion engine 20 be the structure of Reciprocating engine, but in addition, can be rotary engine, gas turbine etc. for example, and can be the structure after these structures of combination.
In addition, illustration the driving force generation device be the structure of internal-combustion engine, but in addition, for example can be electric motor, oil hydraulic motor, can also the combination motor motor etc. and internal-combustion engine.
In the above-described embodiment, illustration the 1st internal-combustion engine 10 and the 2nd internal-combustion engine 20 are petrolic structures of burns gasoline, but in addition, for example can be the diesel engine of burning light oil, the hydrogen engine of hydrogen combusted etc., and can make up these motors.
In the above-described embodiment, illustration drive system 1 carried the structure of hybrid vehicle (four-wheel, moving body), but in addition, for example also can be equipped on two take turns, the structure of three-wheel.
In addition, can be the structure of the small-sized tiller (standard equipment) that is equipped on hand-push-type, can also constitute the power source of the generator of fixed.
Label declaration
1: drive system
10: the 1 internal-combustion engines (the 1st driving force generation device)
11: the 1 cylinder blocks
12: the 1 bent axles (the 1st live axle)
13: the 1 cylinders
20: the 2 internal-combustion engines (the 2nd driving force generation device)
21: the 2 cylinder blocks
22: the 2 bent axles (the 2nd live axle)
23: the 2 cylinders
30A: the 1st speed changer
30B: the 2nd speed changer
40A: the 1st swing conversion rod (the 1st swing converter unit)
40B: the 2nd swing conversion rod (the 2nd swing converter unit)
41: rotary base ring (the 1st rotary part, the 2nd rotary part)
42: swing part (the 1st swing part, the 2nd swing part)
50A: the 1st turning radius change mechanism
50B: the 2nd turning radius change mechanism
51: input shaft
51b: eccentric part
52: disk
53: small gear
54: direct current motor
60A: the 1st overrunning clutch
60B: the 2nd overrunning clutch
71A: the 1st output shaft (output shaft)
71B: the 2nd output shaft (output shaft)
The 80:ECU(control unit)
L12: the 1st crank axle
L13: the 1st cylinder axis
L22: the 2nd crank axle
L23: the 2nd cylinder axis
O1: input central axis
O2: output center axis
O3: the 1st fulcrum
O4: the 2nd fulcrum
R1: turning radius
R2: pendulum radius

Claims (5)

1. drive system is characterized in that it has:
The 1st driving force generation device, it has the 1st live axle;
The 2nd driving force generation device, it has 2nd live axle opposite with described the 1st live axle with described the 1st live axle parallel configuration and sense of rotation;
The 1st swing converter unit, it is transformed to oscillating motion with rotatablely moving of described the 1st live axle;
Output shaft, it is by from the power of described the 1st driving force generation device and described the 2nd driving force generation device, rotates in a direction as the sense of rotation of described the 2nd live axle; And
The 1st overrunning clutch, its only with the transmission of power of the oscillating motion of a direction of described the 1st swing converter unit to described output shaft.
2. drive system according to claim 1 is characterized in that, it has:
The 2nd swing converter unit, it is transformed to oscillating motion with rotatablely moving of described the 2nd live axle; And
The 2nd overrunning clutch, its only with the transmission of power of the oscillating motion of a direction of described the 2nd swing converter unit to described output shaft.
3. drive system according to claim 2 is characterized in that,
Described the 1st swing converter unit has: the 1st rotary part that is rotated by rotatablely moving of described the 1st live axle; With the 1st swing part that carries out oscillating motion by the rotation of described the 1st rotary part,
Described the 2nd swing converter unit has: the 2nd rotary part that is rotated by rotatablely moving of described the 2nd live axle; With the 2nd swing part that carries out oscillating motion by the rotation of described the 2nd rotary part,
Described drive system also has:
The 1st turning radius change mechanism, it changes the angular velocity of described the 1st swing part by the turning radius of described the 1st rotary part of change; And
The 2nd turning radius change mechanism, it changes the angular velocity of described the 2nd swing part by the turning radius of described the 2nd rotary part of change.
4. according to any described drive system in the claim 1～3, it is characterized in that,
Described the 1st driving force generation device and described the 2nd driving force generation device are Reciprocating engines, and disposed adjacent,
Described the 1st live axle is the 1st bent axle, and described the 2nd live axle is the 2nd bent axle,
The sense of rotation of the sense of rotation of described the 1st bent axle and described the 2nd bent axle is set to: in the axial view of described the 1st bent axle and described the 2nd bent axle, in the medial region of described the 1st bent axle and described the 2nd bent axle, become expansion stroke,
Described the 1st driving force generation device has the 1st cylinder, and described the 2nd driving force generation device has the 2nd cylinder,
Described the 1st cylinder is put to the lateral deviation near described the 2nd cylinder,
Described the 2nd cylinder is put to the lateral deviation near described the 1st cylinder.
5. according to any described drive system in the claim 1～3, it is characterized in that,
Described the 1st driving force generation device and described the 2nd driving force generation device are Reciprocating engines, and disposed adjacent,
Described the 1st live axle is the 1st bent axle, and described the 2nd live axle is the 2nd bent axle,
The sense of rotation of the sense of rotation of described the 1st bent axle and described the 2nd bent axle is set to: in the axial view of described the 1st bent axle and described the 2nd bent axle, in the exterior lateral area of described the 1st bent axle and described the 2nd bent axle, become expansion stroke,
Described the 1st driving force generation device has the 1st cylinder, and described the 2nd driving force generation device has the 2nd cylinder,
Described the 1st cylinder is put to the lateral deviation away from described the 2nd cylinder,
Described the 2nd cylinder is put to the lateral deviation away from described the 1st cylinder.
CN201180051822.7A 2010-11-02 2011-10-14 Drive system Expired - Fee Related CN103189626B (en)

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