CN106762196A - A kind of hydraulic motor-driven variable-compression-ratio piston - Google Patents
A kind of hydraulic motor-driven variable-compression-ratio piston Download PDFInfo
- Publication number
- CN106762196A CN106762196A CN201710156279.6A CN201710156279A CN106762196A CN 106762196 A CN106762196 A CN 106762196A CN 201710156279 A CN201710156279 A CN 201710156279A CN 106762196 A CN106762196 A CN 106762196A
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- Prior art keywords
- hydraulic
- hydraulic motor
- runner
- piston
- compression
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F3/00—Pistons
- F02F3/0015—Multi-part pistons
-
- 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
- F02B75/04—Engines with variable distances between pistons at top dead-centre positions and cylinder heads
- F02B75/044—Engines with variable distances between pistons at top dead-centre positions and cylinder heads by means of an adjustable piston length
-
- 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
-
- 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
- F02D15/04—Varying compression ratio by alteration of volume of compression space without changing piston stroke
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D2700/00—Mechanical control of speed or power of a single cylinder piston engine
- F02D2700/03—Controlling by changing the compression ratio
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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)
- Hydraulic Motors (AREA)
Abstract
The present invention discloses a kind of hydraulic motor-driven variable-compression-ratio piston, including top land, piston skirt, hydraulic motor mechanism, runner, deceleration device and import and export oil duct；Top land respectively has a cavity with piston skirt, hydraulic motor mechanism is placed in the cavity of piston skirt, runner is in the cavity of top land, four circle spiral plates on runner are engaged with four semi-circular projections of top land, contact portion between hydraulic motor and runner is the deceleration device constituted with driving gear, planetary gear and internal gear, and hydraulic motor is made up of the oblong cavity of hydraulic base, hydraulic vane, hydraulic baffle plate, Packing spring and piston skirt；Pressure oil enters in oval oil pocket from oil duct so that hydraulic vane is rotated, so as to drive runner to rotate, in the presence of guide rod so that top land is relative to piston skirt relative motion so as to change the compression ratio of engine.
Description
Technical field
The present invention relates to a kind of piston of automotive engine, it is more particularly related to a kind of hydraulic motor-driven
Variable-compression-ratio piston.
Background technology
Compression ratio is the ratio of cylinder total volume and combustion chamber volume, when it represents that piston moves to top dead centre by lower dead center
The degree that cylinder interior gas are compressed, is the important parameter of measured engine performance, be influence engine efficiency it is most important because
One of element.In general, compression ratio is higher, and the performance of engine is better.For traditional engine, pressed once its is designed
Contract than being changeless, because combustion chamber volume and displacement are all fixed parameters.Modern Automobile Engine
Compression ratio gasoline engine is generally 8~12, and diesel engine is generally 12-22.
A kind of technology of the changeable compression ratio technique primarily directed to engine with supercharger.Fixed compression ratio can not give full play to
The performance of engine, in fact in Smaller load, low-speed running, the thermal efficiency of engine is low, and correspondingly comprehensive comparison is poor,
At this moment larger compression ratio can be used, and in big load, rotation speed operation high, if compression ratio is too high, is easy to pinking
And very big thermic load and mechanical load is produced, at this moment can use less compression ratio.As the change of load continuously adjusts pressure
Contracting ratio, can to greatest extent excavate the potentiality of engine, make it that the thermal efficiency is effectively improved in whole conditioned area, Jin Erti
The combination property of engine high.
Can using changeable compression ratio technique：
1. the thermal efficiency of engine is improve, the fuel economy of engine is largely improved.
2. discharge is advantageously reduced.
3. there is good fuel tolerance.
4. structure can reach small-displacement high-power, high pulling torque with more compact in the case of identical power output.
5. dynamic property during fuel economy and big load when taking into account sub-load, improves low engine speed power performance
While also avoid risk for knock in combustion process.
6. operation stability can be improved to a certain extent, reduce noise.
The current general all complex structures of variable compression ratio of engines both at home and abroad, it usually needs carried out significantly to engine structure
Change, processing difficulties sometimes, how to simplify the internal structure of an organization to realize that in limited space preferable effect is that need to solve one asks
Topic；The movable parts such as those newly-increased controls and auxiliary body result in the increase of vibration, friction loss and abrasion, also make
Engine quality increases, and the mobile needs of these big mass bodies expend a big chunk energy；Change engine exactly in good time
Compression ratio, it is necessary to corresponding high precision control apparatus, difficulty of matching is big；When compression ratio is too high, gas leakage can consume engine
Power, and cause the failure of the parts such as engine body.If excessive gaseous mixture is leak into crankcase, lubricating oil can be caused
It is rotten；Research and develop and be more expensive to manufacture.
The content of the invention
The technical problems to be solved by the invention be overcome that mechanism structure existing for prior art is complicated, part is more,
A kind of the problems such as manufacturability is poor, R＆D costs are high, it is proposed that hydraulic motor-driven variable-compression-ratio piston.
In order to solve the above technical problems, the present invention adopts the following technical scheme that realization：
A kind of hydraulic motor-driven variable-compression-ratio piston, it is characterised in that described hydraulic motor-driven is variable
Traditional combustion engine piston is divided into top land and two, piston skirt part by compression ratio piston；Eight Packing springs are placed on liquid
In pressing the circular hole of base, and eight hydraulic vanes are placed on the rectangular opening of hydraulic base, hydraulic vane connects with Packing spring
Touch, fastening parts spring, Packing spring, hydraulic base are assembled into hydraulic rotation mechanism and are arranged on the circular groove of piston skirt
In, the hydraulic pressure plate washer in hydraulic rotation mechanism upper cover, part hydraulic base, hydraulic vane, hydraulic baffle plate, Packing spring and work
The oblong cavity assembling for filling in skirt section constitutes hydraulic motor；By in the splined hole of spline insertion hydraulic base；By The gear deceleration
Mechanism cause runner slow down, increase turn round, runner boss side surfaces place ball bearing, and with two panels end cap by runner be fixed on around
In the free degree of axial-movement, the arch hole on end cap is penetrated by the circular port fixed seat of hydraulic baffle plate, then places snap ring
In the annular groove of piston skirt, for fixing end cap；Top land is placed on piston skirt, the column rod of top land
Insert in the circular port fixed seat of hydraulic baffle plate, top land is play the guiding role, the semi-cylindrical hill and runner of top land
On spiral plate linear contact lay.
Described piston top partial cut-away center is a big cavity, and the bottom surface periphery of cavity uniformly stretches out four columns
Rod, inwardly respectively has a semi-cylindrical hill in the centre position of column rod.
The disjunction face center of described piston skirt is drilled with a circular cavity, and cavity side has a circle annular groove, cavity
Bottom surface be drilled with a big slotted eye, elliptical aperture bottom surface is also drilled with a circular groove, for laying hydraulic base, piston
Pin-and-hole left and right side at skirt section is each to be drilled with an oil duct upwards, and left and right oil duct length is different, and two sections of terminals of oil duct are all in water
Square extend along oval bore edges to the circular arc with 30 degree and 150 degree, subsequently into slotted eye.
Described runner is a cylindrical structure, four spiral plates is uniformly distributed in the outside of cylinder, in cylinder
The base of body is a column, and the bottom of column is round boss, for the fixation of circle wheel, internal tooth is drilled with boss inner face
Wheel.
Described reducing gear be three planetary gears respectively simultaneously with driving gear external toothing, with runner boss in
Gear internal messing constitutes reducing gear.
The main body of described hydraulic vane is a cuboid, and is rounded down, and is a cylinder in the end face of cuboid
Support stick.
Described hydraulic base is a cylindrical structure, and the centre of cylinder upper surface is drilled with splined hole, the side of cylinder
Eight rectangular apertures are uniform-distribution with, the medial surface level of rectangular opening is inwardly drilled with circular hole.
Described hydraulic baffle plate is a circular plate type structure, and the centre of plectane is a circular hole, and four are distributed around plectane
Individual circle hole shape fixed seat.
The side of described hydraulic vane is in close contact with the elliptical aperture side of piston skirt, and because Packing spring applies
There is certain precompression between the pretightning force of hydraulic vane causes the elliptical aperture contact surface of hydraulic vane and piston skirt.
Compared with prior art the beneficial effects of the invention are as follows：
1. the present invention is only processed to internal piston and increases corresponding part and a set of hydraulic control system, and not
Change the overall structure of cylinder so that mechanism structure is simple.
2. the present invention is used as driving force by the rotation of hydraulic motor, and compact conformation, overall size are smaller, noise is low, the longevity
Life length.
3. the present invention realizes pressure by the threaded engagement between runner and top land after the torque that hydraulic motor is provided
The change of contracting ratio, reliable operation.
4. the present invention is few because processing part, and is the reprocessing carried out to piston, so low cost of manufacture.
Brief description of the drawings
The present invention is further illustrated below in conjunction with the accompanying drawings：
Fig. 1 is the main sectional view of hydraulic motor-driven variable-compression-ratio piston of the present invention.
Fig. 2 is the C-C projection views shown in Fig. 1.
Fig. 3 is the D-D projection views shown in Fig. 1.
Fig. 4 is the E-E projection views shown in Fig. 1.
Fig. 5 is the oblique view removed after top land of invention components.
Fig. 6 is the front view of runner part of the present invention.
Fig. 7 is the top view of runner part of the present invention.
Fig. 8 is the front view of inventive piston top piece.
Fig. 9 is the B-B projection views of front view in Fig. 8.
Figure 10 is the front view of hydraulic vane.
Figure 11 is the left view of hydraulic vane.
Figure 12 is the front view of hydraulic base.
Figure 13 is the A-A projection views of front view in Figure 12.
Figure 14 is the main sectional view of piston skirt.
Figure 15 is the B-B projection views of the main section views of Figure 14.
Figure 16 is the C-C projection views of the main section views of Figure 14.
In figure：1- top lands, 2- fastening springs, 3- runners, 4- snap rings, 5- end caps, 6- ball bearings, 7- hydraulic pressure gear
Plate, 8- hydraulic vanes, 9- Packing springs, 10- piston skirts, 11- splines, 12- hydraulic bases, 13- planetary gears, 14- is actively
Gear.
Specific embodiment
The present invention is explained in detail below in conjunction with the accompanying drawings：
Refering to Fig. 1 and Fig. 2, piston is divided into top land 1 and the two large divisions of piston skirt 10 along disjunction face, in two parts structure
Into the built-in equipped hydraulic motor of cavity, reducing gear and runner 3, be drilled with two oil ducts in piston skirt 10, be hydraulic motor
There is provided and import and export oil circuit, there is connection of the pitman for fastening spring 2 in four circular holes of point section rim of top land 1.
Refering to Fig. 8 and Fig. 9, the center in the disjunction face of top land 1 is a big cavity, uniform in the bottom periphery of cavity
Four column rods of distribution, respectively there is a projection for semi-circular structure on column rod, direction is inside, by semi-circular projection and the spiral shell of runner
Rotating plate linear contact lay so that top land 1 can opposing pistons skirt section 10 move.
Refering to Figure 14, Figure 15 and Figure 16, the disjunction face center of piston skirt 10 is a big cavity, the side surface upper part of cavity
It is drilled with a circle annular groove, cavity is shaped as circular cavity, and the bottom surfaces of circular cavity are slotted eye, oval major axis and piston
The cavity radius at top 1 are equal, and the elliptical aperture bottom surface of piston skirt 10 is drilled with a circular groove, and circular groove is used for hydraulic pressure bottom
The fixation of seat 12, the edge in the disjunction face of piston skirt 10 is uniformly distributed four arch holes corresponding with top land 1, same in arch hole
Sample has pitman；Left and right oil duct is drilled with along piston axis direction in the pin-and-hole left and right sides of piston skirt 10, two oil duct length are not
Together, the terminal of left oil duct is extended with 30 degree of horizontal direction, 150 degree along oval bore edges respectively, subsequently into elliptical aperture, equally
, the terminal of right oil duct is reversely extended for 30 degree, 150 degree with horizontal direction along oval bore edges, subsequently into elliptical aperture.
Refering to Fig. 1 and Fig. 2, hydraulic baffle plate 7 is a circular plate type structure, and the centre of plectane is a circular hole, the week of plectane
Enclose four circle hole shape fixed seats of distribution.
Refering to Fig. 6 and Fig. 7, runner 3 is a cylindrical structural, and four spiral tabular knots are dispersed with the outside of cylinder
Structure, is a column in the bottom of cylinder, and the bottom of column is round boss, and for the fixation of runner 3, boss inner side is
The structure of internal gear.
Refering to Figure 10 and Figure 11, the main body of hydraulic vane 8 is a cuboid, and is rounded down, in the end face of cuboid
It is a cylindrical body supports rod.
Refering to Figure 12 and Figure 13, hydraulic base 12 is a cylindrical structure, and splined hole, cylinder are drilled with the center of cylinder
Side to being evenly distributed with eight cuboid openings at the axis of cylinder, the opening surface of cuboid opening and the end face of cylinder
Concordantly, the one side in cuboid is drilled with circular hole for the installation of Packing spring.
Refering to Fig. 1, Fig. 2 and Fig. 5, Packing spring 9 is placed in the circular hole of hydraulic base 12, then by eight hydraulic vanes
In the circular hole of 8 cylindrical portion insertion hydraulic base 12, part 8,9,12 constitutes hydraulic rotation mechanism, by hydraulic rotation above
Motivation structure is laid on the circular hole of the slotted eye bottom surface of piston skirt 10 by hydraulic base 12, part hydraulic base 12, hydraulic pressure leaf
The oblong cavity assembling of piece 8, hydraulic baffle plate 7, Packing spring 9 and piston skirt 10 constitutes hydraulic motor, eight hydraulic vanes 8
Side be in contact with the slotted eye side of piston skirt 10, and cause there is certain pre- between contact surface by Packing spring 9
Clamp force.Hydraulic baffle plate 7 is placed on the top of hydraulic rotation mechanism, side and the piston skirt 10 of hydraulic baffle plate 7 are that interference is matched somebody with somebody
Close；During spline 11 inserted into the splined hole of hydraulic base 12, the upper end of spline 11 is driving gear 14, and three planetary gears 13 are uniform
The internal gear being distributed on driving gear 14 and runner 3 between, planetary gear 13 and the external toothing of driving gear 14, three planets
Internal gear internal messing on gear 13 and runner 3, the inner headed face of ball bearing 6 and the contacts side surfaces of the boss of runner 3, two panels end cap
5 are placed on hydraulic baffle plate 7 and are compressed runner 3 with the lower surface of end cap 5, and the arch hole of end cap 5 penetrates the circle of hydraulic baffle plate 7
Hole fixed seat, and fixed end cap 5 with snap ring 4；The circular hole that four column rods of top land 1 are placed on hydraulic baffle plate 7 is consolidated
In reservation, coordinate with gap is combined into, and the spiral plate linear contact lay on semi-circular projection structure on column rod and runner 3, piston top
The disjunction face in portion 1 overlaps with the disjunction face of piston skirt 10, then passes through pitman by top land 1 with four fastening springs 2
Coupled together with piston skirt 10, prevent piston make because of inertia force and atmospheric pressure during the strenuous exercise top land 1 with
Piston skirt 10 produces uncontrolled relative motion.
Refering to Fig. 1, Fig. 3, Fig. 4, Figure 14, when engine needs high compression ratio, hydraulic pump is by hydraulic oil through bent axle, connecting rod
Oil circuit imported into the left oil duct at the pin-and-hole of piston skirt 10, and then hydraulic oil is flowed upwardly into and level edge along piston axis direction
30 degree flow into oblong cavity with 150 degree, and the oil pocket area in oil suction chamber is more than fuel-displaced cavity area, and oil-feed cavity pressure is more than fuel-displaced
Cavity pressure, so hydraulic vane 8 is rotated forward, drives driving gear 14 to rotate forward by spline 11, now the rotating speed of driving gear 14 it is high,
Torque is small, and the deceleration by planetary gear 13 increases torsion effect, and the rotating speed of runner 3 diminishes, and torque increase, runner 3 passes through spiral plate
With the contact of the semi-circular projection of top land 1, through the guide effect of the circular hole fixed seat on hydraulic baffle plate 7 so that 1 gram of top land
The effect of the pretightning force of fastening spring 2 is taken relative to piston skirt 10 apart from rising, now compression ratio increase.
Refering to Fig. 1, Fig. 3, Fig. 4 and Figure 14, similarly, when engine needs low compression ratio, hydraulic pump is by hydraulic oil through song
Axle, connecting rod oil circuit imported into the right oil duct at the pin-and-hole of piston skirt 10, then right oil of the hydraulic oil from the pin-and-hole of piston skirt 10
Hole flows upwardly into and level flows into oblong cavities along 30 degree with 150 degree, now, goes out the pressure of oil pocket more than the pressure in oil suction chamber
Power, so hydraulic vane 8 is inverted, hydraulic vane 8 deceleration of planetary gear 13, increases and turns round, by torque through the transmission of driving gear 14
Runner 3 is passed to, runner 3 is inverted, top land 1 subtracts under the pretightning force effect of fastening spring relative to the distance of piston skirt 10
Small, now engine has low compression ratio.
Claims (9)
1. a kind of hydraulic motor-driven variable-compression-ratio piston, it is characterised in that described hydraulic motor-driven pressure-variable
Contracting includes top land (1), fastening spring (2), runner (3), snap ring (4), end cap (5), ball bearing (6), hydraulic pressure than piston
Baffle plate (7), hydraulic vane (8), Packing spring (9), piston skirt (10), spline (11), hydraulic base (12), planetary gear
(13), driving gear (14)；
Traditional combustion engine piston is divided into top land (1) and (10) two, piston skirt part；Eight Packing springs (9) are placed
In the circular hole of hydraulic base (12), and eight hydraulic vanes (8) are placed on the rectangular opening of hydraulic base (12), hydraulic vane
(8) it is in contact with Packing spring (9), fastening parts spring (2), Packing spring (9), hydraulic base (12) are assembled into hydraulic rotation
Mechanism is simultaneously arranged in the circular groove of piston skirt (10), hydraulic pressure plate washer (7), part liquid in hydraulic rotation mechanism upper cover
Pressure base (12), hydraulic vane (8), hydraulic baffle plate (7), the oblong cavity of Packing spring (9) and piston skirt (10) are assembled
Constitute hydraulic motor；By in the splined hole of spline (11) insertion hydraulic base (12)；By gear reduction so that runner (3)
Slow down, increase turn round, runner (3) boss side surfaces place ball bearing (6), and with two panels end cap (5) by runner (3) be fixed on around
In the free degree of axial-movement, the arch hole on end cap (5) is penetrated by the circular port fixed seat of hydraulic baffle plate (7), then will card
Ring (4) is placed in the annular groove of piston skirt (10), for fixing end cap (5)；Top land (1) is placed on piston skirt
(10) on, in the circular port fixed seat of column rod insertion hydraulic baffle plate (7) of top land (1), top land (1) is risen and is oriented to
Effect, the spiral plate linear contact lay on the semi-cylindrical hill and runner (3) of top land (1).
2. a kind of hydraulic motor-driven variable-compression-ratio piston according to claim 1, it is characterised in that described work
Plug top (1) disjunction face center is a big cavity, and the bottom surface periphery of cavity uniformly stretches out four column rods, in column rod
Inwardly respectively there is a semi-cylindrical hill in centre position.
3. a kind of hydraulic motor-driven variable-compression-ratio piston according to claim 1, it is characterised in that described work
The disjunction face center for filling in skirt section (10) is drilled with a circular cavity, and cavity side has a circle annular groove, and the bottom surface of cavity is drilled with one
Individual big slotted eye, elliptical aperture bottom surface is also drilled with a circular groove, for laying hydraulic base (12), piston skirt (10)
The pin-and-hole left and right side at place is each to be drilled with an oil duct upwards, and left and right oil duct length is different, and two sections of terminals of oil duct are all in level side
Extend along oval bore edges to the circular arc with 30 degree and 150 degree, subsequently into slotted eye.
4. a kind of hydraulic motor-driven variable-compression-ratio piston according to claim 1, it is characterised in that described turns
Wheel (3) is a cylindrical structure, and four spiral plates are uniformly distributed in the outside of cylinder, is one in the base of cylinder
Column, the bottom of column is round boss, for the fixation of runner (3), internal gear is drilled with raised head face.
5. a kind of hydraulic motor-driven variable-compression-ratio piston according to claim 1, it is characterised in that described subtracts
Fast mechanism be three planetary gears (13) respectively simultaneously with driving gear (14) external toothing, with runner (3) boss in internal gear
Internal messing is constituted.
6. a kind of hydraulic motor-driven variable-compression-ratio piston according to claim 1, it is characterised in that described liquid
The main body of pressure blade (8) is a cuboid, and is rounded down, and is a cylindrical support rod in the end face of cuboid.
7. a kind of hydraulic motor-driven variable-compression-ratio piston according to claim 1, it is characterised in that described liquid
Pressure base (12) is a cylindrical structure, and the centre of cylinder upper surface is drilled with splined hole, and the side of cylinder is uniform-distribution with eight
Individual rectangular aperture, the medial surface level of rectangular opening is inwardly drilled with circular hole.
8. a kind of hydraulic motor-driven variable-compression-ratio piston according to claim 1, it is characterised in that described liquid
Pressure baffle plate (7) is a circular plate type structure, and the centre of plectane is a circular hole, four circle hole shapes is distributed around plectane and is fixed
Seat.
9. a kind of hydraulic motor-driven variable-compression-ratio piston according to claim 1, it is characterised in that described liquid
The side of pressure blade (8) is in close contact with the elliptical aperture side of piston skirt (10), and because Packing spring (9) is applied to hydraulic pressure
There is certain pretightning force between causing the elliptical aperture contact surface of hydraulic vane (8) and piston skirt (10) in the pretightning force of blade (8).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2016109074315 | 2016-10-18 | ||
| CN201610907431.5A CN106481477A (en) | 2016-10-18 | 2016-10-18 | A kind of hydraulic motor-driven variable-compression-ratio piston |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN106762196A true CN106762196A (en) | 2017-05-31 |
| CN106762196B CN106762196B (en) | 2023-05-23 |
Family
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201610907431.5A Withdrawn CN106481477A (en) | 2016-10-18 | 2016-10-18 | A kind of hydraulic motor-driven variable-compression-ratio piston |
| CN201710156279.6A Active CN106762196B (en) | 2016-10-18 | 2017-03-16 | Hydraulic motor driven variable compression ratio piston |
Family Applications Before (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201610907431.5A Withdrawn CN106481477A (en) | 2016-10-18 | 2016-10-18 | A kind of hydraulic motor-driven variable-compression-ratio piston |
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| CN (2) | CN106481477A (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106884734B (en) * | 2017-04-14 | 2023-05-09 | 吉林大学 | Variable compression ratio piston with shaft sleeve |
| CN106837592B (en) * | 2017-04-14 | 2023-05-09 | 吉林大学 | Double-screw transmission type variable compression ratio piston |
| CN107472818B (en) * | 2017-08-14 | 2019-12-24 | 上海沃典工业自动化有限公司 | Head pulley structure of APC power and free conveyor |
| CN113813860B (en) * | 2021-05-18 | 2022-07-22 | 苏州爱柯基科技有限公司 | Epoxy terrace coating stirring equipment capable of quantitatively feeding |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2000240477A (en) * | 1997-07-31 | 2000-09-05 | Fev Motorentechnik Gmbh & Co Kg | Method for influencing air-fuel mixture formation and air intake motion within cylinder of spark ignition type piston internal combustion engine |
| US20060249103A1 (en) * | 2005-05-09 | 2006-11-09 | Valdivia Francisco A | Concentric piston for variable compression ratio directly based on the combustion chamber pressure |
| CN204532541U (en) * | 2015-03-26 | 2015-08-05 | 天津潜景技术咨询有限公司 | Double-crankshaft variable compression ratio engine |
| CN105723070A (en) * | 2013-12-18 | 2016-06-29 | Fev有限责任公司 | Piston engine with support piston |
| CN206555024U (en) * | 2016-10-18 | 2017-10-13 | 吉林大学 | A kind of hydraulic motor-driven variable-compression-ratio piston |
-
2016
- 2016-10-18 CN CN201610907431.5A patent/CN106481477A/en not_active Withdrawn
-
2017
- 2017-03-16 CN CN201710156279.6A patent/CN106762196B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2000240477A (en) * | 1997-07-31 | 2000-09-05 | Fev Motorentechnik Gmbh & Co Kg | Method for influencing air-fuel mixture formation and air intake motion within cylinder of spark ignition type piston internal combustion engine |
| US20060249103A1 (en) * | 2005-05-09 | 2006-11-09 | Valdivia Francisco A | Concentric piston for variable compression ratio directly based on the combustion chamber pressure |
| CN105723070A (en) * | 2013-12-18 | 2016-06-29 | Fev有限责任公司 | Piston engine with support piston |
| CN204532541U (en) * | 2015-03-26 | 2015-08-05 | 天津潜景技术咨询有限公司 | Double-crankshaft variable compression ratio engine |
| CN206555024U (en) * | 2016-10-18 | 2017-10-13 | 吉林大学 | A kind of hydraulic motor-driven variable-compression-ratio piston |
Also Published As
| Publication number | Publication date |
|---|---|
| CN106762196B (en) | 2023-05-23 |
| CN106481477A (en) | 2017-03-08 |
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