CN106704005A - Mechanism capable of continuously changing engine compression ratio - Google Patents
Mechanism capable of continuously changing engine compression ratio Download PDFInfo
- Publication number
- CN106704005A CN106704005A CN201510769605.1A CN201510769605A CN106704005A CN 106704005 A CN106704005 A CN 106704005A CN 201510769605 A CN201510769605 A CN 201510769605A CN 106704005 A CN106704005 A CN 106704005A
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- China
- Prior art keywords
- sliding
- rotor
- vane motor
- eccentric bushing
- designed
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D15/00—Varying compression ratio
- F02D15/02—Varying compression ratio by alteration or displacement of piston stroke
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D2200/00—Input parameters for engine control
- F02D2200/02—Input parameters for engine control the parameters being related to the engine
- F02D2200/10—Parameters related to the engine output, e.g. engine torque or engine speed
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D2200/00—Input parameters for engine control
- F02D2200/02—Input parameters for engine control the parameters being related to the engine
- F02D2200/10—Parameters related to the engine output, e.g. engine torque or engine speed
- F02D2200/101—Engine speed
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Output Control And Ontrol Of Special Type Engine (AREA)
- Rotary Pumps (AREA)
Abstract
The invention provides a mechanism capable of continuously changing the engine compression ratio. According to the mechanism, one end of a crankshaft is assembled with a hydraulically-powered vane motor, and a vane motor shell and the crankshaft rotate together; a driving shaft is assembled in a central hole of a main crankshaft neck close to the vane motor; one end of the driving shaft is connected with a rotor in the vane motor and can be driven by the rotor to rotate; the other end of the driving shaft is assembled with a driving disc, and the driving disc can drive an eccentric bushing assembled on a crank throw shaft neck to rotate; the pressure of oil entering a hydraulic cavity of the vane motor is controlled through a proportional electromagnetic valve, and the locking angle, relative to the shell, of the vane motor rotor is changed, so that the locking angle, relative to the crank throw shaft neck, of the eccentric bushing is changed, and change of the effective work radius of a crank throw is achieved; and accordingly, the height of a piston can be changed, and the engine compression ratio is changed.
Description
Technical field
The present invention relates to vehicular engine field, and in particular to the variable technical field of engine compression ratio.
Background technology
According to automobile engine thermal efficiency theoretical formula η=1-1/CR(5-1)(the η thermals efficiency, CR compression ratios, K is exhausted
Heat number), the larger compression ratio of engine is obtained in that the larger thermal efficiency.But start during by full load
The limitation of the condition such as machine parts intensity and Engine Knock, engine compression ratio selection can not be too big.It is preferable
State be that the thermal efficiency higher is obtained using larger compression ratio during part load engine, and during big load
Larger power and moment of torsion is obtained using less compression ratio.But the compression ratio of existing automobile engine is can not
Become, therefore, make engine compression ratio it is variable be development of engine a kind of direction.
The content of the invention
The present invention seeks to realize engine compression ratio continuous variable, will pass through the regulation of compression ratio, make pressure
Contracting ratio is matched with engine operating condition, engine is obtained optimal fuel economy all the time.To realize above-mentioned mesh
, the invention provides a kind of continuous mechanism for changing engine compression ratio：Bent axle one end is equipped with hydraulic pressure drive
Dynamic sliding-vane motor, sliding-vane motor shell is together rotated with bent axle.In the main bearing journal of sliding-vane motor
Drive shaft is equipped with heart hole, the rotor in one end connection sliding-vane motor of drive shaft can be driven by the rotor
Rotation；The other end of drive shaft is equipped with drive disk.Drive disk can drive the bias assembled on crank throw axle journal
Set rotation.Passing ratio solenoid valve control enters the oil pressure of the hydraulic cavities of sliding-vane motor, changes sliding-vane motor and turns
The locking angle of sub- opposite shell, so as to change locking angle of the eccentric bushing with respect to crank throw axle journal, realizes crank throw
The change of effective radius of clean-up, further makes depth pistion variable, so as to change engine compression ratio.
The effective radius of clean-up of crank throw refers to distance of the bent axle rotation centerline to the cylindrical axial line of eccentric bushing.
Described drive disk is gear, and gear is engaged with the tooth of eccentric bushing end, and gear is by positioning key and drive
Moving axis end is fixedly connected.
Can be first, described drive disk is swing arm part, can be put around bent axle pivot under drive shaft driving
Arm edge inner side is distributed with sliding tooth along circular arc, and sliding tooth is engaged with the tooth of eccentric bushing end, the rotation of swing arm part
It is fixedly connected with driveshaft end centrally through positioning key.
Between 0 to 360/N degree, N is rotor leaf to described sliding-vane motor rotor opposite shell anglec of rotation a
The blade quantity of piece.Described drive disk is a/180 with the engaged transmission ratio of eccentric bushing.
Main bearing journal radial direction against sliding-vane motor is designed with two-way oilhole, the two-way oilhole by than
Example solenoid valve control, two-way oilhole is respectively communicated with the hydraulic cavities of sliding-vane motor blade both sides by oil circuit.
Oilhole of the described oil circuit comprising axial direction in crankshaft journal, oilhole one end connection main bearing journal
The oilhole of radial direction design, the other end connects the hydraulic cavities of sliding-vane motor rotor.
Optionally, oilhole of the oil circuit comprising shaft center design, on oilhole one end connection main bearing journal
The oilhole all the way of radial direction, the hydraulic cavities of other end connection sliding-vane motor rotor blade side.
Optionally, oil circuit includes the oil circuit gap between drive shaft outer surface and main bearing journal center bore inner wall,
Another road binders hole of radial direction on oil circuit gap one end connection main bearing journal, other end connection blade horse
Up to the hydraulic cavities of rotor blade opposite side.
Optionally, check valve is housed on the oil circuit of the proportion magnetic valve oil inlet front end.Engine main oil gallery
Interior pressure oil can only flow to motor hydraulic cavities by check valve through proportional solenoid valve control, and be unable to reverse flow
To main oil gallery.
Described drive shaft passes through main bearing journal centre bore, and one end is fixedly connected with sliding-vane motor rotor, separately
One end is fixedly connected by positioning key with drive disk.
Optionally, drive shaft one end is connect with sliding-vane motor rotor by circumferentially positioned being bonded, and can axially be slided relatively
It is dynamic.
Optionally, it is indirectly connected with by excessively set between drive shaft one end and sliding-vane motor rotor.Excessively in set
Circumferentially positioned key is all designed with hole and outer wall, respectively with the cooperation of drive shaft and rotor, can axially be slided relatively
It is dynamic.
The endoporus of described eccentric bushing is relatively cylindrical with certain offset.Eccentric bushing is designed to centre position
There is the oilhole of inside and outside wall connection, for lubricating eccentric bushing inside and outside wall faying face.Eccentric bushing end is designed with drive
Dynamic tooth, sliding tooth is equal to endoporus centre distance, and the sliding tooth is engaged with the sliding tooth on drive disk.
Optionally, the endoporus wall of eccentric bushing is designed with antifriction alloy layer.
Optionally, the cylindrical wall of eccentric bushing is designed with antifriction alloy layer.
When mechanism of the present invention applies to Multi-Cylinder Diesel Engine, bent axle has multiple crank throw axle journals and main shaft diameter.Above-mentioned bias
Set two ends are all designed with sliding tooth.Power transmission shaft is equipped with the centre bore of the main shaft diameter in the middle of two neighboring crank throw,
Power transmission shaft two ends are respectively fitted with drive disk by positioning key, the sliding tooth of drive disk respectively with two crank throws on
Eccentric bushing sliding tooth engagement.The annexation of follow-up other crank throws is similar.
Optionally, bent axle is sectional combination structure, and eccentric bushing is overall cyclic structure.
Optionally, bent axle is overall structure, and eccentric bushing is by two semicircle sheet bearing shells to being bonded into.
When drive disk is gear, it is also equipped with feeding back eccentric bushing angle position on the radius bar of bent axle one end
Signal panels.The signal panels can swing around crankshaft axis, axially be fixed by radius bar and cylinder body main bearing seat.
One section of tooth being distributed along arc is designed with signal panels, is engaged with the sliding tooth of eccentric bushing.When eccentric bushing is rotated,
Signal panels can be driven to swing certain angle with respect to crankshaft center.Signal teeth is designed with signal panels, be mounted in
Sensor on engine cylinder-body provides angle position signal.Therefore, signal panels are different with respect to crank rotation
Angle, correspond to eccentric bushing and rotates different angles relative to crank throw axle journal, that is, correspond to different crank throws effective
The radius of clean-up, finally correspond to the different compression ratio of engine.
Return spring is designed between signal panels and crankshaft crooked connecting lever.(such as start when engine oil pressure is relatively low
When machine starts or shuts down), return spring drive signal disk swings, and drives eccentric bushing to turn to big compression ratio state.
Optionally, the number of teeth limitation eccentric bushing rotation 180 of the tooth for being engaged with the sliding tooth of eccentric bushing on signal panels
Degree.
Optionally, when drive disk is swing arm part, independent signal panels are not designed, the signal teeth of signal panels is direct
Design is at a swing arm edge for drive disk.Return spring is designed between drive disk and crankshaft crooked connecting lever.
The sliding-vane motor told is mounted in crankshaft front end.
Optionally, sliding-vane motor is integrated in the vibration damper of engine crankshaft front end installation.Sliding-vane motor
Shell on be designed with inertia ring and drive multi-rib-belt multiple wedge slot.The shell and crankshaft front end of sliding-vane motor
It is threadably secured connection.The hydraulic cavities of motor are divided into multiple chambers by blade rotor.
Optionally, sliding-vane motor is mounted in crankshaft rear end.
Further alternative, sliding-vane motor is integrated in the flywheel of engine crankshaft rear end installation.Sliding-vane motor
Shell on the gear ring of flywheel is driven when being designed with inertia ring and engine start.The shell of sliding-vane motor and song
Shaft rear end is bolted to connection.The hydraulic cavities of motor are divided into multiple chambers by blade rotor.
Control method and principle：
When engine is operated, sliding-vane motor and bent axle are together rotated.Engine ECU according to engine load,
The signal teeth position signals of rotating speed and signal panels, judge whether current compression ratio is target compression ratio.Institute
The target compression ratio stated is the compression ratio of engine development mark timing setting or calculating.When need adjust compression ratio
When, the oil pressure pressure of the rotor blade both sides of Engine ECU control proportion magnetic valve regulation sliding-vane motor makes
With respect to housing into rotation, rotor is rotated and drives drive shaft turns rotor, and drive shaft turns drive drive disk to rotate,
And then drive eccentric bushing to rotate, change the effective radius of clean-up of crank throw.When the sensor on cylinder body detects signal
When the angle position of the signal teeth of disk reaches target angular position, Engine ECU controls proportion magnetic valve by leaf
The rotor of piece motor with respect to case lock, will eccentric bushing with respect to crank throw angle position lock, sliding-vane motor turn
Son is rotated with crankshaft-synchronous, completes the regulation of compression ratio.
When the present invention applies to Multi-Cylinder Diesel Engine, bent axle has multiple crank throw axle journals and main shaft diameter, and above-mentioned regulation makes bias
Set rotation, the sliding tooth of the other end of eccentric bushing drives the drive disk of the side of power transmission shaft to rotate, so as to drive
The drive disk of the opposite side of power transmission shaft is rotated, and then drives the adjacent eccentric bushing turned on shaft neck to rotate, complete
Into the regulation of effective radius of clean-up of adjacent crank throw, the i.e. regulation of compression ratio.Follow-up each crank throw axle journal compression
The Principles of Regulation of ratio are similar.
In technical solution of the present invention, because the regulation of compression ratio is by changing the effective radius of clean-up of crank throw come real
Existing, that is, change the stroke of engine.Therefore, the actual displacement of engine can be with the change of compression ratio
Change.Engine is relative in big compression ratio to have larger discharge capacity in small reduction ratio.
In technical solution of the present invention, the material of rotor can be the material that sliding-vane motor is commonly used.For single leaf rotor,
For the vibrations that the mass unbalance for reducing rotation causes, on the premise of intensity is met, rotor need to do lightweight
Design, or rotor material select lightweight aluminum alloy materials；Other parts are manufactured using common steel.
Brief description of the drawings
Fig. 1 is integrated in the variable compression ratio assembly figure in the crankshaft vibration damper of front end for sliding-vane motor
Fig. 2 is the exploded view of the variable compression ratio assembly shown in Fig. 1
Fig. 3 is the characteristic pattern of bent axle 100
Fig. 4 is the sectional view of bent axle 100
Fig. 5 is the characteristic pattern of eccentric bushing 200
The characteristic pattern of Fig. 6 opposite opened semi-circular structure eccentric bushings
Fig. 7 is the characteristic pattern of drive shaft assembly 300
Fig. 8 is the characteristic pattern of power transmission shaft 400
Fig. 9 is the characteristic pattern of gear 500
Figure 10 is the characteristic pattern of signal panels 600
Figure 11 is the characteristic pattern of return spring 700
Figure 12 is the exploded view of sliding-vane motor assembly 800
Figure 13 is the assembly characteristic pattern of motor shell 801
Figure 14 is the characteristic pattern of rotor 802 of sliding-vane motor
Figure 15 is the characteristic pattern of locating ring 803
Figure 16 is the characteristic pattern of dividing plate 804
Figure 17 is the characteristic pattern of dividing plate alignment pin 805
Figure 18 is the characteristic pattern of sealing strip 806
Figure 19 is the characteristic pattern of rotor cover 807
Figure 20 is that sliding-vane motor installs the characteristic pattern of nut 809
Figure 21 is 810 characteristic patterns of excessive set
Figure 22 is the characteristic pattern of blanking cover 811
Figure 23 is the variable compression ratio sectional view shown in Fig. 1
Figure 24 is the partial enlarged drawing of Figure 23
Figure 25 is the cut-away view of sliding-vane motor
Figure 26 is the prosecutor method and principle schematic diagram of variable compression ratio
The comparison diagram of crank throw effective radius of clean-up when Figure 27 is big compression ratio and small reduction ratio state
Figure 28 another kind sliding-vane motors are integrated in the variable compression ratio partial sectional view in crankshaft vibration damper
Variable compression ratio cut-away view shown in Figure 29 Figure 28
Figure 30 is the rotor characteristic figure of the variable compression ratio shown in Figure 28
Figure 31 is the characteristic pattern of the drive shaft of the variable compression ratio shown in Figure 28
Figure 32 is the characteristic pattern of the rotor cover of the variable compression ratio shown in Figure 28
Figure 33 is integrated in the variable compression ratio assembly figure in crankshaft rear end flywheel for sliding-vane motor
Figure 34 is the exploded view of the variable compression ratio assembly shown in Figure 33
Figure 35 is the characteristic pattern of bent axle 101
Figure 36 is the sectional view of the bent axle of bent axle 101
Figure 37 is the characteristic pattern of drive shaft assembly 301
Figure 38 is the exploded view of sliding-vane motor assembly 900
Figure 39 is the characteristic pattern of motor shell 901
Figure 40 is the characteristic pattern of rotor 905 of sliding-vane motor
Figure 41 rotor fixed positions pin 904 and the assembling schematic diagram of rotor 905
Figure 42 is the characteristic pattern of rotor cover 907
Figure 43 is integrated in the variable compression ratio sectional view in flywheel for sliding-vane motor
Figure 44 is the partial enlarged drawing of Figure 43
Figure 45 is the cut-away view of the sliding-vane motor shown in Figure 43
Figure 46 another kind sliding-vane motors are integrated in the variable compression ratio partial sectional view in flywheel
Variable compression ratio cut-away view shown in Figure 47 Figure 46
Figure 48 is the motor shell characteristic pattern shown in Figure 46
Figure 49 is the rotor characteristic figure shown in Figure 46
Figure 50 is the characteristic pattern of the shown drive shaft in Figure 46
Figure 51 is the characteristic pattern of the shown rotor cover in Figure 46
Figure 52 sliding-vane motor rotors are three variable compression ratio figures of blade
Figure 53 be Figure 52 in the sliding tooth of drive disk engage figure with the sliding tooth of eccentric bushing
Figure 54 is the characteristic pattern of drive disk in Figure 52
Figure 55 is the sliding-vane motor exploded view shown in Figure 52
Figure 56 is the blade rotor characteristic pattern shown in Figure 55
Figure 57 is the characteristic pattern of the rotor chamber shown in Figure 55
Figure 58 is the characteristic pattern of the bent axle terminal pad shown in Figure 55
Figure 59 is the characteristic pattern of the bent axle shown in Figure 52
Figure 60 is the variable compression ratio partial sectional view shown in Figure 52
Specific embodiment
In order that the purpose of the present invention, feature and effect can be more obvious understandable, with reference to accompanying drawing to the present invention
Specific embodiment elaborate.
Many details are elaborated in the following description in order to fully understand the present invention, but it is of the invention
Can also be different from mode described here using other to implement, therefore the present invention does not receive following public tool
The limitation of body embodiment.
Embodiment one
Fig. 1 is integrated in the variable compression ratio assembly figure in the crankshaft vibration damper of front end for sliding-vane motor.Bent axle
It is 4 cylinder machine crankshafts, return spring and signal panels is equipped with the radius bar of crankshaft front end.Assembled on crank throw
The centre bore for having eccentric bushing, crankshaft main-shaft diameters that gear drives is equipped with power transmission shaft, drive shaft and gear.
Fig. 2 is the exploded view of the variable compression ratio assembly shown in Fig. 1.Mechanism assembly is included：Bent axle 100,
Timing driving wheel 110, positioning key 120, eccentric bushing 200, drive shaft assembly 300, power transmission shaft 400, gear
500th, signal panels 600, return spring 700, sliding-vane motor assembly 800.
Fig. 3 is the characteristic pattern of bent axle 100.The connection screw thread 100a of assembling sliding-vane motor is designed with crankshaft front end
With positioning spline 100b；The boss 100c of compression spring is also devised with the radius bar of front end.With reference to Fig. 4 bent axles
Sectional view, the through hole that main bearing journal Center has through hole 100d, wherein crankshaft front end is provided with shoulder hole
Macropore 100e；The crankshaft main-shaft diameters of front end are provided with the two-way communicated with shoulder hole macropore 100e in the radial direction
Oilhole 100f and 100g；Two-way oilhole connection corresponding with the oilhole on cylinder body base bearing, and by ratio battery
The control of valve.To reduce crank throw because setting-up eccentricity covers increased quality, each crank throw axle journal is designed with loss of weight
Hole 100h.
Fig. 5 is the characteristic pattern of eccentric bushing 200.Eccentric bushing is designed with sliding tooth 200a, sliding tooth to two ends
Distance to endoporus 200b centers is equal.Axle journal periphery 200c in the middle of eccentric bushing has with respect to endoporus 200b
There is certain offset.Annular oil groove 200d is also devised with the hole wall in endoporus 200b axial directions centre position.It is interior
Hole 200b radial directions are also devised with the oilhole 200e with axle journal periphery 200c and oil groove 200d insertions.It is right
In the eccentric bushing for being applied to integral one-piece crankshaft, for the ease of assembling, eccentric bushing is set using opposite opened semi-circular structure
Meter, it is shown in Figure 6.Eccentric bushing endoporus 200b and crankshaft crank journal engagement, the axle journal in the middle of eccentric bushing
Periphery 200c coordinates with crank pin end pore.In order to reduce friction, eccentric bushing endoporus 200b and axle journal are cylindrical
Face 200c can apply antifriction material or inlay anti-attrition bearing shell.
Fig. 7 is the characteristic pattern of drive shaft assembly 300.Drive shaft assembly is multistage multi-diameter shaft, the axle of both end of which
Neck 300a and 300b are respectively designed with positioning key 300c and 300d.Two sections of middle axle journals 300e and 300f
Equal diameters, the shoulder hole macropore 100e with crankshaft front end coordinates.The ladder of axle journal 300b and crankshaft front end
Hole aperture 100d coordinates.The oil groove 300g of axial direction is evenly equipped with axle journal 300e is cylindrical.Axle journal 300f
Axial medium design has endless oil groove 300h.Drive shaft assembly Center has oilhole 300i, oilhole 300i
One end is closed, and the other end is closed with plug screw.Axle journal 300a peripheries and endless oil groove 300h pass through footpath respectively
Connected with oilhole 300i to the oilhole 300k and 300j in direction.
Fig. 8 is the characteristic pattern of power transmission shaft 400.Power transmission shaft two ends are designed with positioning key 400a and 400b, to install
Gear provides positioning.It is loss of weight, center transmission shaft is designed with lightening hole 400c.Power transmission shaft periphery 400d with
The central through hole 100d of crankshaft main-shaft diameters coordinates, and can relatively rotate.
Fig. 9 is the characteristic pattern of gear 500.Gear 500 is distributed with and the sliding tooth of eccentric bushing 200 on excircle
The tooth 500a that 200a coordinates.Gear center hole 500b is designed with positioning key 500c.For integral one-piece crankshaft,
Power transmission shaft is more long, during assembling, it is impossible to directly insert bent by the space between the balance weight of crank throw axle journal both sides
In the central through hole of axle main shaft diameter.Therefore, during assembling, power transmission shaft is needed by the central through hole of crankshaft front end
It is sequentially inserted into the central through hole of each main shaft diameter.When gear 500 is assembled with power transmission shaft 400, in gear 500
Heart hole 500b is connected with the axle journal 400d interference of power transmission shaft 400, and by positioning key 500c and power transmission shaft 400
Positioning key 400a and 400b it is circumferentially positioned.When gear 500 is assembled with drive shaft assembly 300, gear 500
Centre bore 500b is connected with the axle journal 300b interference of drive shaft assembly 300, and by positioning key 500c and drive
The positioning key 300d of moving axis assembly 300 is circumferentially positioned.
Figure 10 is the characteristic pattern of signal panels 600.Signal panels 600 are steel stamping part, by centre bore 600a
Coordinate with the main shaft diameter of bent axle first, can be swung around main shaft diameter, axially through radius bar and cylinder body spindle hole seat limit
Position.Signal panels 600 are along the circumferential direction designed with the one section of tooth 600b coordinated with the sliding tooth 200a of eccentric bushing 200,
Signal panels 600 are along the circumferential direction also devised with arcuation spring bracing 600c and signal teeth 600d.
Figure 11 is the characteristic pattern of return spring 700.The center line of return spring 700 is arcuation, during assembling, is returned
Position spring 700 is sheathed on the spring bracing 600c of signal panels 600, spring one end and signal panels 600
Spring bracing 600c ends contacts, the spring other end is compressed by the boss 100c on crankshaft front end radius bar.
The driving eccentric bushing when engine oil pressure is relatively low that act as of return spring 700 swings, and drives eccentric bushing rotation,
Engine is set to be in big compression ratio state.
Figure 12 is the exploded view of sliding-vane motor assembly 800.Sliding-vane motor is integrated in crankshaft vibration damper.Blade
Motor is included：Motor shell assembly 801, motor rotor 802, locating ring 803, dividing plate 804, dividing plate are fixed
Position pin 805 (2), sealing strip 806 (3), rotor cover 807, rotor bonnet bolt 808 (8), leaf
Piece motor installs nut 809, excessively set 810, blanking cover 811.
Figure 13 is the assembly characteristic pattern of motor shell 801.Motor shell assembly is by inertia ring 801a and housing 801b
And connect both vulcanised rubber layer 801c compositions.Rotor chamber 801d, rotor are designed with housing 801b
A 2 alignment pin counterbore 801e and tapped through hole 801f are designed with the wall of chamber 801d sides.Housing 801b justifies
Circumferential direction is distributed with screwed hole 801g for fixed rotor lid.Housing 801b Centers have with before engine
The axle journal 801h that oil sealing coordinates, is designed with shoulder hole in axle journal, the respectively mounting hole 801i of locating ring 803,
Nut 809 installs counterbore 801j, crankshaft front end journal hole 801k and 801m.Also set on the 801m inwalls of hole
In respect of positioning spline 801n.Housing 801b it is cylindrical on be also devised with the multiple wedge slot 801p of drive belt.
Figure 14 is the characteristic pattern of rotor 802 of sliding-vane motor.Rotor 802 is designed with a blade, blade end
It is designed with sealing strip mounting groove 802a.To reduce rotary inertia, in the case where intensity is met, rotor is used
Alloy in lightweight is manufactured, and multiple lightening holes are designed with blade.Blade both sides be respectively designed with rotor
The oilhole 802c and 802d of heart hole 802b connections.Multiple keyways are also distributed with rotor bore 802b inwalls
802e.The center of rotor side is also devised with the mounting hole 802f of locating ring 803.Rotor bore 802b is straight
It is easy to nut to pass through when installing more than the maximum gauge of nut 809 in footpath.The thickness and motor shell of rotor 802
The deep equality of the assembly rotor chamber 801d of body 801.
Figure 15 is the characteristic pattern of locating ring 803.Locating ring 803 be an annulus, annulus outer wall respectively with motor shell
The hole 801i of body assembly 801 and the hole 802f of rotor 802 coordinate, and annulus diameter of bore is more than nut 809
Maximum gauge, be easy to nut to pass through when installing.
Figure 16 is the characteristic pattern of dividing plate 804.The two ends of dividing plate 804 are designed with sealing strip mounting groove 804a, to reduce
Rotary inertia, in the case where intensity is met, dividing plate is manufactured using alloy in lightweight.3 are designed with dividing plate 804
Individual hole, two alignment pins and a bolt are passed through, and dividing plate is fixed on sliding-vane motor housing 801.
The deep equality of the thickness of dividing plate 804 and the rotor chamber 801d of the assembly of motor shell 801.
Figure 17 is the characteristic pattern of dividing plate alignment pin 805.It is loss of weight, alignment pin 805 uses thin-walled roll of steel plate system.
During installation, alignment pin passes through dividing plate pin-and-hole, and the alignment pin counterbore 801e of motor shell 801 is inserted at two ends respectively
In the alignment pin counterbore of rotor cover
Figure 18 is the characteristic pattern of sealing strip 806.The use of sealing strip 806 is wear-resisting and with the material system of certain elasticity
Make.
Figure 19 is the characteristic pattern of rotor cover 807.Rotor cover 807 is formed by sheet fabrication, is round pie.Cake
Edge distribution has bolt mounting holes 807a.The Center of rotor cover 807 has screwed hole 807b, and screwed hole is minimum
With diameter greater than the maximum gauge of nut 908.Also designed on rotor cover 807 and the binding face of motor shell 801
There are the counterbore 807c and bolt mounting holes 807d of fixed locating stud 805.
Figure 20 is that sliding-vane motor installs the characteristic pattern of nut 809.The flanged face of nut, sleeve is tightened to reduce
Diameter, nut screwing clamping face uses positive 8 side shape.
Figure 21 is 810 characteristic patterns of excessive set.It is distributed with and the keyway 802e of rotor 802 on excessive set 810 is cylindrical
The key 810a of cooperation.Cylindrical axial medium design has annular oil groove 810b, oil groove 810b to pass through radial direction oil hole
810c is connected with centre bore 810d, and one section of positioning key 810e is designed with centre bore 810d.Excessively cover 810
Both sides are designed with ring-type positive stop lug boss 810f, limit the axial position in motor assembly 800 of transition sleeve 810
Put, communicate the oilhole 802d in the middle of annular oil groove 810b and rotor 802, and make oilhole 801c and drive
The oilhole 300k of moving axis assembly 300 is communicated.Positive stop lug boss 810f radial directions are designed with what pressure oil passed through
Gap 810g.Excessively 810 both sides of set are also devised with the oilhole 810h of connection.During installation, excessively in set 810
Heart hole 810d and positioning key 810e coordinates with the axle journal 300a and positioning key 300c of drive shaft assembly 300.
Figure 22 is the characteristic pattern of blanking cover 811.Blanking cover 811 is the screw thread blanking cover in flanged face, and flange face outside sets
In respect of regular pentagon counterbore, moment of torsion is provided when tightening blanking cover for spanner.
Sliding-vane motor 800 install when, first by motor shell assembly 801, motor rotor 802, locating ring 803,
Dividing plate 804, dividing plate alignment pin 805 (2), sealing strip 806 (3), rotor cover 807, rotor cover spiral shell
Bolt 808 (8) part is individually assembled up.Crankshaft front end is enclosed within again and is close to timing driving wheel 110, and lead to
Cross positioning key 120 circumferentially positioned；Then by nut 809 sequentially pass through rotor cover 807 screwed hole 807b and
The centre bore 810d of rotor 802, is tightened on the connection screw thread 100a of bent axle 100；Reinstall excessively set
810, blanking cover 811 is finally installed.The advantage of the design is being started sliding-vane motor 800 as general assembly
On machine crankshaft, engine production efficiency is improved.
Figure 23 is the variable compression ratio sectional view shown in Fig. 1.The assembling that each part is illustrated in figure is closed
System.Figure 24 is the partial enlarged drawing of Figure 23.Figure 25 is the cut-away view of sliding-vane motor.With reference to Figure 14,
Figure 21, by the pressure oil of the control of proportion magnetic valve, along the oil circuit shown in Figure 24 and Figure 25 solid arrows
One of pressure chamber is flowed to, the curved arrow direction for driving rotor to press Figure 25 rotates, so as to drive drive shaft
Rotated with eccentric bushing；The oil of another pressure chamber is by along the road shown in Figure 24 and Figure 25 dotted arrows simultaneously
Oil, controls by ratio battery valve, is excreted in engine sump tank.When rotor needs to reversely rotate,
Then the pressure oil of proportional solenoid valve control is along solid arrow inverse direction draining to engine sump tank, while
Along dotted arrow inverse direction oil-feed, rotor reversion is driven.
Control method and principle：
Figure 26 is the prosecutor method and principle schematic diagram of variable compression ratio.Engine ECU receives to come to air throttle
The signal such as position sensor, speed of crankshaft and position sensor, signal panels signal teeth position sensor, and root
Go out the compression ratio and target compression ratio of present engine according to the signal analysis of sensor, and both are compared, such as
In the target compression ratio of setting is interval, then ECU controls proportion magnetic valve, locks fruit present engine compression ratio
Surely into the oil pressure of rotor blade both sides hydraulic cavities, so as to lock sliding-vane motor rotor, current compression ratio is kept
It is constant；If present engine compression ratio is interval outer in the target compression ratio of setting, ECU control ratio electricity
Magnet valve, regulation enters the oil pressure of rotor blade both sides hydraulic cavities, driving blade motor rotor with respect to housing into rotation,
Until Engine ECU detects current compression ratio in target compression ratio is interval, then sliding-vane motor rotor is locked.
The comparison diagram of crank throw effective radius of clean-up when Figure 27 is big compression ratio and small reduction ratio state.Wherein Figure 27
Left figure is big compression ratio state, and Figure 27 right figures are small reduction ratio state.Crank throw effective work during big compression ratio state
Making the effective radius of clean-up of radius ratio small reduction ratio crank throw increases Δ L.
Embodiment two
Figure 28 shows the variable compression ratio partial cutaway that another sliding-vane motor is integrated in crankshaft vibration damper
View.Figure 29 shows its cut-away view.The bent axle of the mechanism also designs axial oil duct in preceding end-journal,
Pressure oil oil-feed and oil extraction are carried out along the oil circuit shown in arrow.Sliding-vane motor housing directly passes through with crankshaft front end
Threaded connection, it is not necessary to nut, it is not required that the blanking cover excessively on set and rotor cover；Inner rotator and driving
Axle directly passes through to be bonded to connect.The mechanism structure is simple, but sliding-vane motor can not in advance be assembled into an assembly
Part is refilled in crankshaft front end, but needs for the part of sliding-vane motor to be arranged on crankshaft front end one by one.
Figure 30 is the rotor characteristic figure of the variable compression ratio shown in Figure 28.Rotor axis interlude endoporus
One section of spline is designed with, can be rotated a certain angle during assembling and be inserted on the splined shaft of drive shaft again.In spline
The smooth porose area at two ends further respectively has the both sides that oilhole connects rotor blade, and hydraulic oil is respectively by the two oil
The oil pocket of the into or out blade both sides in hole.The both sides of rotor center axle are all higher than vane end faces, during assembling,
In the section roller insertion sliding-vane motor shell bores and the shrinkage pool of rotor cover being higher by, rotor is fixed on center
Position.Rotor tip is designed with sealing strip mounting groove.
Figure 31 is the characteristic pattern of the drive shaft of the variable compression ratio shown in Figure 28.One end of axle is designed with
Gear positioning key, the other end is designed with spline.Axostylus axostyle is also devised with endless oil groove near gear positioning key one end,
Endless oil groove radial direction is designed with oilhole, and the oilhole is communicated with shaft center oilhole；Shaft center oil
Hole is communicated with the axial end of splined end, and shaft center oilhole is then closed by gear positioning key one end.
Figure 32 is the characteristic pattern of the rotor cover of the variable compression ratio shown in Figure 28.With turning shown in Figure 19
Son lid is compared, and the rotor cover center does not have screwed hole, but is designed with shrinkage pool, for positioning rotor.Other
Structure is identical with Figure 19.
The control method and principle of embodiment two are identical with embodiment one, are not repeated.
Embodiment three
Figure 33 is integrated in the variable compression ratio assembly figure in crankshaft rear end flywheel for sliding-vane motor.Bent axle is
4 cylinder machine crankshafts.Return spring and signal panels are equipped with the radius bar of crankshaft front end.Assembled on crank throw with teeth
The eccentric bushing of wheel drive, the centre bore of crankshaft main-shaft diameters is equipped with power transmission shaft, drive shaft and gear.
Figure 34 is the exploded view of the variable compression ratio assembly shown in Figure 33, comprising：Bent axle 101, bias
Set 200, drive shaft assembly 301, power transmission shaft 400, gear 500, signal panels 600, return spring 700,
Sliding-vane motor assembly 900.
Figure 35 is the characteristic pattern of bent axle 101.The boss 101c of compression spring is also devised with the radius bar of front end.
With reference to the sectional view of Figure 36 bent axles, main bearing journal Center has through hole 101d, and wherein crankshaft rear end is logical
Hole is provided with shoulder hole macropore 101e；The crankshaft main-shaft diameters of rear end are provided with and shoulder hole macropore in the radial direction
Two-way oilhole 101f and 101g that 101e is communicated, two-way oilhole connection corresponding with the oilhole on cylinder body, and
Controlled by ratio battery valve.Increase quality because setting-up eccentricity covers to reduce crank throw, each crank throw axle journal
It is designed with lightening hole 101h
Figure 37 is the characteristic pattern of drive shaft assembly 301.Drive shaft assembly is multistage multi-diameter shaft, the axle of both end of which
Neck 301a and 301b are respectively designed with positioning key 301c and 301d, middle larger axle journal 301e and 301f
Equal diameters, the shoulder hole macropore 101e with crankshaft rear end coordinates.The ladder of axle journal 301b and crankshaft rear end
Hole aperture 101d coordinates.The oil groove 301g of axial direction, axle journal 301f are evenly equipped with axle journal 301e is cylindrical
Axial medium design has endless oil groove 301h.Drive shaft assembly Center has oilhole 301i, oilhole 301i
One end is closed, and the other end is closed using plug screw.Axle journal 301a peripheries and endless oil groove 301h pass through respectively
The oilhole 301k and 301j of radial direction is connected with oilhole 301i.
Figure 38 is the exploded view of sliding-vane motor assembly 900.Comprising：Motor shell 901, dividing plate 902, dividing plate
Alignment pin 903 (2), rotor supports pin 904 (3), motor rotor 905, sealing strip 906 (3),
Rotor cover 907, rotor bonnet bolt 908 (11), motor installation bolt 909 (6), screw plug 910 (6
It is individual).
Figure 39 is the characteristic pattern of motor shell 901.Engine start gear ring 901a is designed with housing is cylindrical,
Housing side is designed with rotor chamber 901b, and the bottom design of rotor chamber has motor installation bolt through hole 901c, turns
Sub- supporting pin counterbore 901d, dividing plate alignment pin counterbore 901e, rotor cover bolt thread through hole 901f.Shell ends
Face is along the circumferential direction distributed the tapped through hole 901g installed for rotor cover and clutch, basis on another side end face
Requirement for dynamic balance can process multiple duplicate removal counterbore 901h.Casing center is designed with the convex with crankshaft rear end
The positioning through hole 901i that platform coordinates.
Figure 40 is the characteristic pattern of rotor 905 of sliding-vane motor.Rotor 905 is designed with a blade, blade end
It is designed with sealing strip mounting groove 905a.To reduce rotary inertia, in the case where intensity is met, rotor is used
Alloy in lightweight is manufactured, and multiple lightening holes are designed with blade.Blade side is designed with and rotor bore
The oilhole 905c of 905b connections, blade opposite side connects rotor center gusset both sides by two oilhole 905d
Oil pocket area.The oil pocket of center gusset both sides passes through multiple through hole 905e and connects, through hole 905e with diameter greater than
The maximum gauge of motor installation bolt 909, passes through when being easy to bolt 908 to install.In rotor bore 905b
Positioning key 905f is designed with wall, the positioning key 905f and positioning key 301c in drive shaft coordinates during installation.
Rotor side is also devised with location hole 905g, on motor shell 901 install multiple rotor fixed position pins 904 with
Location hole 905g is tangent, is installed for rotor and provides centralized positioning, referring to Figure 41.The oil of location hole 905g sides
More than the bolt head of motor installation bolt 909 highly, rotor 905 avoids pacifying with motor when rotated chamber depth
The bolt head interference of dress bolt 909.The axial width of rotor 905 and the rotor chamber 901b of motor shell 901
Deep equality.
Figure 42 is the characteristic pattern of rotor cover 907.Rotor cover 907 is processed by steel plate, is round pie.Cake
Edge distribution has rotor bonnet bolt to install shoulder hole 907a and clutch installation bolt through hole 907b.Rotor cover
907 Centers have boss, and boss Center has shrinkage pool 907c, for supporting transmission shaft.Shrinkage pool 907c
Surrounding is distributed with tapped through hole 907d, and tapped through hole 907d minimum diameters are straight more than the maximum of the head of bolt 909
Footpath, passes through when being easy to bolt 909 to install.Also designed on rotor cover 907 and the binding face of motor shell 901
There are counterbore 907e and rotor bonnet bolt that alignment pin 903 is installed that shoulder hole 907f is installed.
When sliding-vane motor assembly 900 is installed, first by motor shell 901, dividing plate 902, dividing plate alignment pin 903
(2), rotor supports pin 904 (3), motor rotor 905, sealing strip 906 (3), rotor cover
907th, rotor bonnet bolt 908 (11) part is individually assembled up, and forms an assembly part, then be enclosed within
On the positioning boss of crankshaft rear end, then the screw threads that motor installation bolt 909 (6) is passed through into rotor cover 907
The through hole 905e of through hole 907d and motor rotor 905 is installed on the screw thread of crankshaft rear end, finally by screw plug 910
(6) are fixed on the tapped through hole 907d of rotor cover 907.The advantage of the design is by sliding-vane motor 900
As general assembly on engine crankshaft, engine production efficiency is improved.
Figure 43 is integrated in the variable compression ratio sectional view in flywheel for sliding-vane motor.Each is illustrated in figure
The assembly relation of part.Figure 44 is the partial enlarged drawing of Figure 43.Figure 45 is the sliding-vane motor shown in Figure 43
Cut-away view.With reference to Figure 40, Figure 44 and Figure 45, by the pressure oil of proportional solenoid valve control along real
Oil circuit shown in line arrow flows to one of pressure chamber, drives rotor blade to press Figure 45 curved arrows direction and turns
It is dynamic, so as to drive drive shaft and eccentric bushing to rotate；The oil of another pressure chamber is by along dotted arrow institute simultaneously
The road binders for showing, is excreted in engine sump tank by proportional solenoid valve control.When rotor needs to reversely rotate
When, then proportional solenoid valve control pressure oil along solid arrow inverse direction draining to engine sump tank, together
When along dotted arrow inverse direction oil-feed, drive rotor blade reversion.
The control method and principle of embodiment three are identical with embodiment one, are not repeated.
Example IV
Figure 46 shows the variable compression ratio partial sectional view that another sliding-vane motor is integrated in flywheel.
Figure 47 shows its cut-away view.The bent axle of the mechanism also designs axial oil duct, pressure in rear end-journal
Oily oil-feed and oil extraction are carried out along the oil circuit shown in arrow.Inner rotator passes through spline connection with drive shaft.Blade
The hole passed through when motor installation bolt is installed is not intended on motor rotor and rotor cover.Sliding-vane motor can not be prior
It is assembled into an assembly part to refill in crankshaft rear end, but needs one by one to install the sub- part of sliding-vane motor
In crankshaft rear end.
Figure 48 is the motor shell characteristic pattern shown in Figure 46.Compared with the motor shell 901 shown in Figure 39,
The counterbore of rotor supports pin has been lacked at motor shell center shown in Figure 48, but increased and crankshaft rear end journal shaft
To the oilhole that oil duct is connected.Other structures are identical with the motor shell 901 shown in Figure 39.
Figure 49 is the rotor characteristic figure shown in Figure 46.Spline is designed with rotor bore, can during assembling
Be inserted on the splined shaft of drive shaft again with being rotated a certain angle.The both sides oil pocket of rotor center gusset leads to respectively
Oil-through hole connects the both sides of rotor blade.Rotor center is deeper near the oil pocket of crankshaft side, it is to avoid with motor shell
The installation bolt of body 901 is interfered.Blade end is designed with sealing strip mounting groove.
Figure 50 is the characteristic pattern of the shown drive shaft in Figure 46.One end of axle is designed with positioning key, another
End is designed with larger spline, and splined central is designed with counterbore.Axostylus axostyle interlude is also devised with endless oil groove,
Endless oil groove radial direction is designed with oilhole, and the oilhole is communicated with shaft center oilhole；Shaft center oil
Hole is communicated with the counterbore base of splined end, and shaft center oilhole is then closed by one end of positioning key.
Figure 51 is the characteristic pattern of the shown rotor cover in Figure 46.Compared with the rotor cover shown in Figure 42, should
Rotor cover Center has the counterbore of indent, for transmission shaft provides support, does not have shown in Figure 42 around counterbore
Screwed hole.Other structures are identical with Figure 42.
The control method and principle of example IV are identical with embodiment one, are not repeated.
Embodiment five
Figure 52 displaying sliding-vane motor rotors are three variable compression ratio figures of blade.Sliding-vane motor is integrated in
In the crankshaft vibration damper of crankshaft front end.In order to show the rotor chamber internal structure of sliding-vane motor, rotor cover is in figure
In it is unassembled.Because sliding-vane motor rotor is three uniform blades, the relatively above-mentioned single leaf of the rotor anglec of rotation
The anglec of rotation of piece rotor is small, in order to drive eccentric bushing to rotate 180 degree, the sliding tooth of drive disk
Driving radius are larger, engaged with the sliding tooth on the outside of the crank throw of eccentric bushing on crank throw, referring to shown in Figure 53.Phase
To single blade rotor, uniform multi-blade rotor has preferable dynamic balance performance, reduces when part rotates
Vibrations.
Figure 54 is the characteristic pattern of drive disk in Figure 52.Center hole is driven to be designed with positioning key, drive disk side
Edge is designed with signal teeth and sliding tooth and installs the support frame of return spring.It is uneven in order to reduce drive disk
Weight vibrations when rotated, drive disk is also devised with balance and removes repeated hole.
Figure 55 is the sliding-vane motor exploded view shown in Figure 52.Sliding-vane motor by blade rotor, rotor chamber, turn
Son lid and bent axle terminal pad and installation bolt are constituted.
Figure 56 is the characteristic pattern of the blade rotor shown in Figure 55.Rotor has three uniform blades, rotor
Blade side is connected with one end of rotor bore by oilhole, rotor blade opposite side and rotor bore
The other end is connected also by oilhole.The diameter of the diameter compared with end hole in the hole in rotor bore axial direction centre position
It is small, and positioning key is designed with hole, coordinate for the positioning key with driveshaft end.
Figure 57 is the characteristic pattern of the rotor chamber shown in Figure 55.There are three uniform blades in rotor chamber inner ring,
Lightening hole is designed with each blade, blade tip and inner ring edge designs have bolt installation through-hole.Rotor chamber
Outer ring is designed with inertia ring and drives the multiple wedge slot of polywedge bet, and rotor inner ring and outer ring are connected by vulcanised rubber layer
Connect.By adjusting the performance of rotor outer ring inertia and vulcanised rubber layer, torsion during crankshaft operation can be reduced
Vibration, realizes the function of crankshaft vibration damper..
Figure 58 is the characteristic pattern of the bent axle terminal pad shown in Figure 55.Terminal pad is distributed with and coordinates with rotor chamber
The bolt thread hole of connection, the Center of bent axle terminal pad has oil sealing axle journal, and axle journal endoporus is screwed hole.
Turn timing with bent axle, be directly tightened in the threaded journal of crankshaft front end.
Figure 59 is the characteristic pattern of the bent axle shown in Figure 52.Crankshaft front end axle journal is designed with for bent axle terminal pad
The threaded journal of installation.The fan-shaped balance weight of the first radius bar is designed with groove along fan-shaped edge, shown in Figure 54
The support frame of return spring of drive disk be stuck in groove, can be slided in groove.Groove one end is designed with
One chain-wales, for return spring provides support.
Figure 60 is the variable compression ratio partial sectional view shown in Figure 52.Arrow represents pressure oil stream in figure
Dynamic schematic diagram.
The control method and principle of embodiment five are identical with embodiment one, are not repeated.
Figure 60 variable compression ratio need by the part of sliding-vane motor one by one be arranged on crankshaft front end.For
Raising engine production efficiency, it is also possible to according to the structure of the variable compression ratio shown in Figure 24, driving
Increase transition sleeve between moving axis and rotor.Sliding-vane motor is first assembled into total member, then by nut by blade horse
Crankshaft front end is fixed on up to assembly.
According to the intent of the present invention, mutliblade sliding-vane motor can also be integrated in the flywheel of crankshaft rear end, turned
Blades quantity can also be other quantity according to the configuration settings of engine, and the present invention is not repeated.
Although the present invention disclosed as above with preferred embodiment, its be not for limiting the present invention, it is any
Those skilled in the art without departing from the spirit and scope of the present invention, the method that may be by the disclosure above
Possible variation and modification are made to technical solution of the present invention with technology contents, therefore, it is every without departing from this hair
The content of bright technical scheme, any simple modification made to above example according to technical spirit of the invention,
Equivalent variations and modification, belong to the protection domain of technical solution of the present invention.
Claims (19)
1. it is a kind of it is continuous change engine compression ratio mechanism, it is characterised in that bent axle one end is equipped with hydraulic-driven
Sliding-vane motor, sliding-vane motor shell together rotates with bent axle.In the main bearing journal of sliding-vane motor
Drive shaft is equipped with heart hole, the rotor in one end connection sliding-vane motor of drive shaft can be driven by rotor
Dynamic rotation；The other end of drive shaft is equipped with drive disk.Drive disk can drive what is assembled on crank throw axle journal
Eccentric bushing rotates.Passing ratio solenoid valve control enters the oil pressure of the hydraulic cavities of sliding-vane motor, changes blade
The locking angle of motor rotor opposite shell, so that change locking angle of the eccentric bushing with respect to crank throw axle journal,
The change of the effective radius of clean-up of crank throw is realized, further makes depth pistion variable, so as to change engine pressure
Contracting ratio.
2. drive disk as claimed in claim 1, it is characterised in that drive disk is gear, gear and eccentric bushing end
The tooth engagement in portion, gear is fixedly connected by positioning key with driveshaft end.
3. drive disk as claimed in claim 1, it is characterised in that drive disk is swing arm part, swing arm edge inner side
Sliding tooth is distributed with along circular arc, sliding tooth is engaged with the tooth of eccentric bushing end, swing arm part pivot passes through
Positioning key is fixedly connected with driveshaft end.
4. mechanism as claimed in claim 1, it is characterised in that against the main bearing journal radial direction side of sliding-vane motor
To two-way oilhole is designed with, the two-way oilhole passing ratio solenoid valve control, two-way oilhole is divided by oil circuit
Not Lian Tong sliding-vane motor blade both sides hydraulic cavities.
5. oil circuit as claimed in claim 4, it is characterised in that oil of the oil circuit comprising axial direction in crankshaft journal
Hole, the oilhole of oilhole one end connection main bearing journal radial direction design, other end connection sliding-vane motor
The hydraulic cavities of rotor.
6. oil circuit as claimed in claim 4, it is characterised in that oilhole of the oil circuit comprising shaft center design,
The oilhole all the way of radial direction on oilhole one end connection main bearing journal, other end connection sliding-vane motor turns
The hydraulic cavities of blades side.
7. oil circuit as claimed in claim 4, it is characterised in that oil circuit includes drive shaft outer surface and crank spindle
Oil circuit gap between neck center bore inner wall, radial direction on oil circuit gap one end connection main bearing journal
Another road binders hole, the other end connect sliding-vane motor rotor blade opposite side hydraulic cavities.
8. one end of drive shaft as claimed in claim 1 connects the rotor in sliding-vane motor, it is characterised in that drive
Moving axis passes through main bearing journal centre bore, and one end is fixedly connected with sliding-vane motor rotor, and the other end is by fixed
Position key is fixedly connected with drive disk.
9. one end of drive shaft as claimed in claim 1 connects the rotor in sliding-vane motor, it is characterised in that drive
Moving axis one end is connect with sliding-vane motor rotor by circumferentially positioned being bonded, and relative can axially be slided.
10. one end of drive shaft as claimed in claim 1 connects the rotor in sliding-vane motor, it is characterised in that drive
It is indirectly connected with by excessively set between moving axis one end and sliding-vane motor rotor.Excessively on set endoporus and outer wall all
Circumferentially positioned key is designed with, respectively with the cooperation of drive shaft and rotor, relative can axially be slided.
11. eccentric bushings as claimed in claim 1, it is characterised in that the endoporus of eccentric bushing is relatively cylindrical with certain
Offset.Eccentric bushing is designed with the oilhole that inside and outside wall is connected to centre position, for lubricating eccentric bushing
Inside and outside wall faying face.Eccentric bushing end is designed with sliding tooth, and sliding tooth is equal to endoporus centre distance.
12. eccentric bushings as claimed in claim 11, it is characterised in that the endoporus wall of eccentric bushing is designed with anti-attrition
Alloy-layer.
13. eccentric bushings as claimed in claim 11, it is characterised in that the cylindrical wall of eccentric bushing is designed with anti-attrition
Alloy-layer.
14. mechanisms as claimed in claim 1, it is characterised in that when the mechanism applies to Multi-Cylinder Diesel Engine, eccentric bushing two
End is all designed with sliding tooth.Power transmission shaft is equipped with the centre bore of the main shaft diameter in the middle of two neighboring crank throw,
Power transmission shaft two ends are respectively fitted with drive disk by positioning key, the sliding tooth of drive disk respectively with two crank throws
On eccentric bushing sliding tooth engagement.
15. mechanisms as claimed in claim 1, it is characterised in that when drive disk is gear, in the song of bent axle one end
It is also equipped with feeding back the signal panels of eccentric bushing angle position on connecting lever.The signal panels can be put around crankshaft axis
It is dynamic.One section of tooth being distributed along arc is designed with signal panels.Signal teeth is designed with signal panels, is mounted in hair
Sensor on motivation cylinder body provides angle position signal.It is designed with back between signal panels and crankshaft crooked connecting lever
Position spring.
16. mechanisms as claimed in claim 1, it is characterised in that when drive disk is swing arm part, do not design independent
Signal panels, the signal teeth of signal panels is directly designed at a swing arm edge for drive disk.Drive disk and bent axle
Return spring is designed between radius bar.
17. sliding-vane motors as claimed in claim 1, it is characterised in that before sliding-vane motor is integrated in engine crankshaft
Hold in the vibration damper installed.
18. sliding-vane motors as claimed in claim 1, it is characterised in that after sliding-vane motor is integrated in engine crankshaft
Hold in the flywheel installed.
19. mechanisms as claimed in claim 1, its control method and principle be characterised by, Engine ECU according to
The signal teeth position signals of engine load, rotating speed and signal panels, judge current compression ratio whether be
Target compression ratio.When regulation compression ratio is needed, Engine ECU control proportion magnetic valve regulation blade horse
The oil pressure pressure of the rotor blade both sides for reaching, makes rotor with respect to housing into rotation, and rotor is rotated and drives drive shaft
Rotate, drive shaft turns drive drive disk to rotate, and then drive eccentric bushing to rotate, change the effective work of crank throw
Make radius.When the angle position that the sensor on cylinder body detects the signal teeth of signal panels reaches angle on target
During position, Engine ECU controls proportion magnetic valve by the rotor of sliding-vane motor with respect to case lock, will
Eccentric bushing is locked with respect to crank throw angle position, and sliding-vane motor rotor is rotated with crankshaft-synchronous, completes compression ratio
Regulation.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510769605.1A CN106704005A (en) | 2015-11-12 | 2015-11-12 | Mechanism capable of continuously changing engine compression ratio |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510769605.1A CN106704005A (en) | 2015-11-12 | 2015-11-12 | Mechanism capable of continuously changing engine compression ratio |
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| Publication Number | Publication Date |
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| CN106704005A true CN106704005A (en) | 2017-05-24 |
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ID=58918852
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| Application Number | Title | Priority Date | Filing Date |
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| CN201510769605.1A Pending CN106704005A (en) | 2015-11-12 | 2015-11-12 | Mechanism capable of continuously changing engine compression ratio |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114673587A (en) * | 2022-03-23 | 2022-06-28 | 重庆长安汽车股份有限公司 | Engine displacement variable device, engine and vehicle |
| US11473939B2 (en) * | 2019-03-15 | 2022-10-18 | Honda Motor Co., Ltd. | Crank angle detection device for engine |
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| DE102008032665A1 (en) * | 2008-07-10 | 2010-01-21 | Audi Ag | Device for changing compression ratio of internal combustion engine, has free wheel which is arranged between rotary drive and gear wheel, where rotary drive is speed controlled or speed regulated |
| CN102889142A (en) * | 2012-10-08 | 2013-01-23 | 沈大兹 | Variable compression ratio device with self-locking structure |
| CN103047002A (en) * | 2012-12-17 | 2013-04-17 | 沈大兹 | Variable compression ratio device with connecting rod journals and eccentric sleeves |
| CN104405526A (en) * | 2014-11-07 | 2015-03-11 | 广西玉柴机器股份有限公司 | Crankshaft front-end structure of diesel engine |
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| US20100006069A1 (en) * | 2006-09-15 | 2010-01-14 | Honda Motor Co., Ltd. | Variable stroke engine |
| DE102008032665A1 (en) * | 2008-07-10 | 2010-01-21 | Audi Ag | Device for changing compression ratio of internal combustion engine, has free wheel which is arranged between rotary drive and gear wheel, where rotary drive is speed controlled or speed regulated |
| CN102889142A (en) * | 2012-10-08 | 2013-01-23 | 沈大兹 | Variable compression ratio device with self-locking structure |
| CN103047002A (en) * | 2012-12-17 | 2013-04-17 | 沈大兹 | Variable compression ratio device with connecting rod journals and eccentric sleeves |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| US11473939B2 (en) * | 2019-03-15 | 2022-10-18 | Honda Motor Co., Ltd. | Crank angle detection device for engine |
| CN114673587A (en) * | 2022-03-23 | 2022-06-28 | 重庆长安汽车股份有限公司 | Engine displacement variable device, engine and vehicle |
| CN114673587B (en) * | 2022-03-23 | 2023-09-22 | 重庆长安汽车股份有限公司 | Engine displacement variable device, engine and vehicle |
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Application publication date: 20170524 |