CN104533612B - Six-stroke engine and vehicle having same - Google Patents
Six-stroke engine and vehicle having same Download PDFInfo
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- CN104533612B CN104533612B CN201410596398.XA CN201410596398A CN104533612B CN 104533612 B CN104533612 B CN 104533612B CN 201410596398 A CN201410596398 A CN 201410596398A CN 104533612 B CN104533612 B CN 104533612B
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Abstract
The invention provides a six-stroke engine and a vehicle having the same. The six-stroke engine comprises a cylinder body, a cylinder head, a main piston, an inlet valve, an exhaust valve and an auxiliary piston. The cylinder head, the cylinder body and the main piston define a combustion chamber. An auxiliary piston chamber is formed in the cylinder head. The auxiliary piston chamber is communicated with the combustion chamber. The auxiliary piston is movably fit in the auxiliary piston chamber. When the main piston is at the main piston top dead center of a compression stroke, the auxiliary piston is at a first position, and when the main piston is at the main piston top dead center of a recompression stroke, the auxiliary piston is at a second position, wherein the distance from the first position to the auxiliary piston top dead center is smaller than that from the second position to the auxiliary piston top dead center. According to the six-stroke engine provided by the invention, the compression ratio of the recompression stroke is reduced to reduce the compression negative work of the recompression process; besides, the energy exhaust gas is fully utilized, the thermal efficiency is increased and the oil consumption is reduced.
Description
Technical field
The present invention relates to automobile technical field, more particularly to a kind of Six-stroke engine and with the Six-stroke engine
Vehicle.
Background technology
In correlation technique, Six-stroke engine include suction stroke, compression travel, expansion space stroke, recompression stroke, remake
Work(stroke and instroke, in correlation technique, Six-stroke engine is not exhausted after expansion space stroke terminates, due to work done row
Journey burning produces High Temperature High Pressure waste gas, and is not exhausted after expansion space stroke terminates, and in recompression stroke greatly pressure can be caused
Contracting negative work, greatly reduces the potentiality that oil consumption drops in six-stroke technology, there is room for improvement.
The content of the invention
In view of this, it is contemplated that proposing a kind of Six-stroke engine, not to be exhausted after expansion space stroke terminates
While, by the compression ratio for reducing recompression stroke, the compression negative work of recompression process is reduced, while making full use of waste gas energy
Amount, the raising thermal efficiency and reduction oil consumption.
To reach above-mentioned purpose, the technical scheme is that what is be achieved in that：
A kind of Six-stroke engine, including：There is cylinder in cylinder block, the cylinder body, in the cylinder master is provided with
Piston；Cylinder head, the cylinder head is arranged on the top of the cylinder block, the cylinder head, the cylinder block and the main work
Combuster is limited between plug, auxiliary piston chamber, the auxiliary piston chamber and the combustion chamber are also formed with the cylinder head；
Inlet valve and exhaust valve, the inlet valve and the exhaust valve are arranged in the cylinder head；Auxiliary piston, the auxiliary piston is along institute
The centrage for stating auxiliary piston chamber movably coordinates in the auxiliary piston chamber；Wherein described main piston has main piston top dead centre
With main piston lower dead center, the auxiliary piston has auxiliary piston top dead centre and auxiliary piston lower dead center, in the main piston in compression
The auxiliary piston is in first position during the main piston top dead centre of stroke, in main piston of the main piston in recompression stroke
The auxiliary piston is in the second position during top dead centre, wherein the first position is less than apart from the distance of the auxiliary piston top dead centre
Distance of the second position apart from the auxiliary piston top dead centre.
Further, the second position is the position that the auxiliary piston moves to the auxiliary piston lower dead center.
Further, the first position is any in the auxiliary piston top dead centre to the auxiliary piston lower dead center
Position.
Further, the first position is less than the first position apart from institute apart from the distance of the auxiliary piston top dead centre
State the distance of auxiliary piston lower dead center.
Further, the auxiliary piston chamber is arranged in air inlet side or exhaust side.
Further, the auxiliary piston chamber is arranged in the exhaust side, and the auxiliary piston is driven by exhaust cam shaft.
Further, be provided with the exhaust cam shaft it is convex turn, auxiliary piston connecting rod is provided with the auxiliary piston, it is described
Auxiliary piston connecting rod is connected with convex the turning.
Further, each described combustor is corresponded to described in two described inlet valves and an exhaust valve and one
Auxiliary piston chamber；Each described combustor of correspondence is provided with the aerofluxuss for driving the exhaust valve on the exhaust cam shaft
Cam and one are used to drive the convex of the auxiliary piston to turn, described convex to turn adjacent with the corresponding exhaust cam.
Further, the auxiliary piston is driven by exhaust cam or admission cam；And the Six-stroke engine is also wrapped
Include：Elastic construction, the elastic construction is arranged so that the auxiliary piston is often convex in the exhaust cam or air inlet against coordinating
On wheel.
Relative to prior art, Six-stroke engine of the present invention has the advantage that：
(1) Six-stroke engine of the present invention, is provided with main piston and auxiliary piston, and main piston coordinates in cylinder, secondary
Piston coordinates in the auxiliary piston chamber being arranged in cylinder head, pair when main piston is in the main piston top dead centre of compression travel
Piston is in first position, and when the main piston is in the main piston top dead centre for recompressing stroke, the auxiliary piston is in second
Position, wherein the first position is less than the second position apart from the auxiliary piston apart from the distance of the auxiliary piston top dead centre
The distance of top dead centre so that the compression ratio of recompression stroke is less than the compression ratio of compression travel, so as to reduce recompressing stroke
Compression negative work, makes full use of exhaust energy, by during two stage combustion, employing two kinds of different compression ratios, while full
Demand of the different combustion systems of two kinds of foot to compression ratio, improves engine thermal efficiency, oil consumption is reduced, while preferably reducing
Control and development difficulty.
Another object of the present invention is to propose a kind of vehicle.
To reach above-mentioned purpose, the technical scheme is that what is be achieved in that：
A kind of vehicle, including above-mentioned Six-stroke engine.
The vehicle has the advantage that identical with above-mentioned Six-stroke engine relative to prior art, and here is no longer gone to live in the household of one's in-laws on getting married
State.
Description of the drawings
The accompanying drawing for constituting the part of the present invention is used for providing a further understanding of the present invention, the schematic reality of the present invention
Apply example and its illustrate, for explaining the present invention, not constituting inappropriate limitation of the present invention.In the accompanying drawings：
Fig. 1 is the structural representation of the Six-stroke engine described in the embodiment of the present invention；
Fig. 2 is the main piston and the trip map of auxiliary piston of the Six-stroke engine described in the embodiment of the present invention.
Fig. 3 is the structural representation of the exhaust cam shaft of the embodiment of the present invention.
Fig. 4 is the sectional view of the exhaust side of the Six-stroke engine described in the embodiment of the present invention.
Fig. 5 is the sectional view of the air inlet side of the Six-stroke engine described in the embodiment of the present invention.
Fig. 6 is the structural representation of the cylinder head of the Six-stroke engine described in the embodiment of the present invention.
Description of reference numerals：
100- Six-stroke engines, 101- suction strokes, 102- compression travels, 103- expansion space strokes, 104- recompression rows
Journey, 105- expansion space strokes again, 106- instrokes, 1- cylinder block, 11- cylinders, 2- cylinder head, 21- auxiliary piston chambers, 22- air inlets
Seat ring, 23- exhaust valve seat inserts, 3- main pistons, 31- main piston connecting rods, 4- auxiliary pistons, 41- auxiliary piston connecting rods, 5- combustor,
61- inlet valves, 62- exhaust valves, 7- exhaust cam shafts, 71- is convex to turn, 72- exhaust cams, 8- admission cam shafts, 90- timing chains
Bar, 91- crank throws, 92- crankshaft timing sprockets, 93- air inlet timing sprockets, 94- exhaust timing sprockets, TDC1- main piston top dead centres,
BDC1- main piston lower dead center, TDC2- auxiliary piston top dead centres, BDC2- auxiliary piston lower dead center.
Specific embodiment
It should be noted that in the case where not conflicting, the embodiment and the feature in embodiment in the present invention can phase
Mutually combination.
Below with reference to the accompanying drawings and in conjunction with the embodiments describing the present invention in detail.It is understood that Six-stroke engine
100 include suction stroke 101, compression travel 102, expansion space stroke 103, recompression stroke 104, again expansion space stroke 105 and aerofluxuss
106 6 strokes of stroke.
As shown in figs 1 to 6, Six-stroke engine 100 includes cylinder block 1, cylinder head 2, inlet valve 61, exhaust valve 62, pair
Piston 4.
Have in cylinder 11, cylinder 11 in cylinder block 1 and be provided with main piston 3.Cylinder head 2 is arranged on the top of cylinder block 1,
Limit in combuster 5, cylinder head 2 between cylinder head 2, cylinder block 1 and main piston 3 and be also formed with auxiliary piston chamber 21, auxiliary piston
Chamber 21 connects with combustor 5, and auxiliary piston 4 movably coordinates in pair along the centrage (such as the line L in Fig. 1) of auxiliary piston chamber 21
In plunger shaft 21.
Inlet valve 61 and exhaust valve 62 are arranged in cylinder head 2, and cylinder head 2 is provided with inlet valve seat ring 22 and exhaust valve seat
Circle 23, inlet valve 61 is arranged in inlet valve seat ring 22, and exhaust valve 62 is arranged in exhaust valve seat insert 23.
Inlet valve 61 is opened, and extraneous fresh air can be entered in cylinder 11, and exhaust valve 62 is opened due to fuel combustion
The waste gas of generation can be discharged from cylinder 11.The quantity of inlet valve 61 and exhaust valve 62 can be configured as the case may be.
For example, in one embodiment of the invention, as shown in fig. 6, each two inlet valve 61 of correspondence of combustor 5 and an exhaust valve
62。
Main piston 3 has main piston top dead centre TDC1 and main piston lower dead center BDC1, and auxiliary piston 4 has auxiliary piston top dead centre
TDC2 and auxiliary piston lower dead center BDC2.As shown in Fig. 2 the main piston top dead centre TDC1 in main piston 3 in compression travel 102
When (such as the A points in Fig. 2), auxiliary piston 4 is in first position (such as the B location in Fig. 2), in main piston 3 in recompression stroke
During 104 main piston top dead centre TDC1 (such as the C points in Fig. 2), auxiliary piston 4 is in the second position (such as the D positions in Fig. 2), its
Middle first position is less than distance of the second position apart from auxiliary piston top dead centre TDC2 apart from the distance of auxiliary piston top dead centre TDC2.
The ratio of the minimum volume after the maximum volume of the gas in compression front air cylinder 11 and compression is referred to as compression ratio, changes speech
It, compression ratio is equal to the ratio of cylinder total volume and in-cylinder combustion room volume, and for the present invention, cylinder total volume refers to main work
In main piston lower dead center BDC1, the volume of cylinder more than top of main piston 3, in-cylinder combustion room volume refers to that main piston 3 exists to plug 3
Volume during main piston top dead centre TDC1, more than the top of main piston 3.
Cylinder total volume holds including combustion chamber volume and auxiliary piston chamber 21 of the main piston 3 in main piston lower dead center BDC1
Product.In-cylinder combustion room volume includes combustion chamber volume and auxiliary piston chamber 21 volume of the main piston 3 in main piston top dead centre TDC1.
That is, for the present invention, the size of in-cylinder combustion room volume is determined by the position of auxiliary piston 4, wherein,
When auxiliary piston 4 is located at auxiliary piston top dead centre TDC2, in-cylinder combustion room volume is minimum, and auxiliary piston 4 is located at auxiliary piston lower dead center BDC2
When, the volume of in-cylinder combustion room is maximum.
The size of cylinder total volume also changes with the change in location of auxiliary piston 4, because auxiliary piston 4 coordinates in auxiliary piston chamber
In 21, and auxiliary piston chamber 21 is located in cylinder head 2, thus activity space of the auxiliary piston 4 in auxiliary piston chamber 21 is limited, thus leads
It is far smaller than main work that piston 3 moves the inswept during motion volume in auxiliary piston chamber 21 of auxiliary piston 4 in the time of a stroke
The inswept volume of one stroke of motion in cylinder 11 of plug 3, thus the cylinder total volume of compression travel 102 and recompression stroke
104 cylinder total volume can be considered as equal.
So, when first position is less than the second position apart from auxiliary piston top dead centre apart from the distance of auxiliary piston top dead centre TDC2
TDC2 apart from when, the in-cylinder combustion room volume of compression travel 102 less than recompression stroke 104 in-cylinder combustion room volume, from
And the compression ratio ε 1 of compression travel 102 is different from the compression ratio ε 2 of recompression stroke 104, and the ＜ ε 1 of ε 2.
With reference to shown in Fig. 2, in a specific embodiment of the present invention, the second position moves to secondary work for auxiliary piston 4
The position of plug lower dead center BDC2, first position is any position in auxiliary piston top dead centre TDC2 to auxiliary piston lower dead center BDC2
Put.First position can be designed according to the compression ratio needed for Six-stroke engine (100).
Further, first position is stopped less than first position apart from the distance of auxiliary piston top dead centre TDC2 under auxiliary piston
The distance of point BDC2, thus the in-cylinder combustion room volume of compression travel 102 closer to in-cylinder combustion room volume minima, so as to
The compression ratio ε 1 of compression travel 102 is bigger.
The specific work process that Fig. 2 describes Six-stroke engine 100 according to embodiments of the present invention in detail is engaged below：
1) suction stroke 101：In suction stroke 101, inlet valve 61 is opened, and main piston 3 is by main piston top dead centre TDC1
Run to main piston lower dead center BDC1, auxiliary piston 4 runs up to operation to auxiliary piston top dead centre TDC2 directions to be stopped to auxiliary piston
Point TDC2, the volume of in-cylinder combustion room is gradually reduced, and reaches minima.
2) compression travel 102：Main piston 3 is run to main piston top dead centre TDC1, auxiliary piston 4 by main piston lower dead center BDC1
Moved to auxiliary piston lower dead center BDC2 direction from auxiliary piston top dead centre TDC2 and finally run to first position, in-cylinder combustion room
Volume starts gradually to increase from minima, and now compression ratio ε 1 is big value.
3) expansion space stroke 103：Main piston 3 is run to main piston lower dead center BDC1, auxiliary piston 4 by main piston top dead centre TDC1
Continue to be run to auxiliary piston lower dead center BDC2 direction, in-cylinder combustion room volume continues to increase.
4) stroke 104 is recompressed：Main piston 3 is run to main piston top dead centre TDC1 by main piston lower dead center BDC1, and pair is living
Plug 4 continues to run up to operation to auxiliary piston lower dead center BDC2 to auxiliary piston lower dead center BDC2 direction, and runs in auxiliary piston 4
During to auxiliary piston lower dead center BDC2, i.e., when auxiliary piston 4 is located at the second position, in-cylinder combustion room volume reaches maximum.Now compress
Than for ε 2 be minima, the ＜ ε 1 of ε 2.
5) expansion space stroke 105 again：Main piston 3 is run to main piston lower dead center BDC1 by main piston top dead centre TDC1, and pair is living
Plug 4 is run from auxiliary piston lower dead center BDC2 to auxiliary piston top dead centre TDC2 directions.Now the volume of in-cylinder combustion room starts to reduce.
6) instroke 106：Exhaust valve 62 is opened, and main piston 3 is from main piston lower dead center BDC1 to main piston top dead centre
TDC1 directions are run, and auxiliary piston 4 continues to be run to auxiliary piston top dead centre TDC2 directions, and in-cylinder combustion room volume continues to reduce.
In short, electromotor according to embodiments of the present invention, by the compression ratio for reducing recompression stroke 104, so as to drop
The compression negative work of low recompression stroke 104, makes full use of exhaust energy, by during two stage combustion, employing two kinds not
Same compression ratio, while meeting demand of two kinds of different combustion systems to compression ratio, improves engine thermal efficiency, reduces oil
Consumption, while preferably reducing control and development difficulty.
Engage Fig. 3-Fig. 6 and describe referring to Fig. 1 and specifically implemented according to one of Six-stroke engine of the present invention 100
Example.Six-stroke engine 100 includes cylinder block 1, cylinder head 2, inlet valve 61, exhaust valve 62 and auxiliary piston 4.Tool in cylinder block 1
Have in cylinder 11, cylinder 11 and be provided with main piston 3, combuster 5, cylinder are limited between cylinder head 2, cylinder block 1 and main piston 3
Auxiliary piston chamber 21 is also formed with lid 2, auxiliary piston chamber 21 is connected with combustor 5, and auxiliary piston 4 movably coordinates in auxiliary piston chamber
In 21, inlet valve 61 and exhaust valve 62 are arranged in cylinder head 2.
As shown in figure 1, auxiliary piston chamber 21 is arranged in exhaust side and auxiliary piston 4 is driven by exhaust cam shaft 7, specifically,
Crank throw 91 is provided with bent axle, main piston connecting rod 31 is provided with main piston 3, main piston connecting rod 31 is connected to drive with crank throw 91
Main piston 3 is moved in cylinder 11, and the crankshaft timing sprocket 92 of Six-stroke engine 100 passes through timing chain 90, air inlet timing
Sprocket wheel 93, exhaust timing sprockets 94 drive admission cam shaft 8 and exhaust cam shaft 7, so as to drive main piston 3 and pair to live simultaneously
Plug 4, makes the alterable compression ratio of the interior compression travel twice of a cycle of operation of Six-stroke engine 100, and without the need for arrange in addition
The driving structure of auxiliary piston 4, saves parts and arrangement space.
In other specific examples of the present invention, auxiliary piston chamber 21 is also disposed at air inlet side.
Further, as shown in figure 3, be provided with exhaust cam shaft 7 it is convex turn 71, as shown in figure 1, on auxiliary piston 4 arrange
There is an auxiliary piston connecting rod 41, auxiliary piston connecting rod 41 turns 71 and be connected to drive auxiliary piston 4 to move in auxiliary piston chamber 21, so as to change with convex
Become the compression ratio of Six-stroke engine 100.Wherein, the ignition order phase of the convex arranged direction and Six-stroke engine 100 for turning 71
Close.
As Figure 4-Figure 6, each two inlet valve 61 of correspondence of combustor 5 and an exhaust valve 62 and an auxiliary piston
Chamber 21.Each combustor 5 of correspondence is provided with an exhaust cam 72 and for driving exhaust valve 62 on exhaust cam shaft 7
It is individual for driving the convex of auxiliary piston 4 to turn 71, as shown in figure 3, convex, to turn 71 adjacent with corresponding exhaust cam 72.Thus, aerofluxuss are convex
The simple structure of wheel shaft 7, and compact conformation, and exhaust cam shaft 7 also synchronously drives auxiliary piston 4 while driving exhaust valve 62.
In other optional embodiments, auxiliary piston 4 can be driven by exhaust cam or admission cam, and six-stroke is sent out
Motivation 100 can also include elastic construction (not shown), and elastic construction is arranged so that auxiliary piston 4 often against cooperation in aerofluxuss
On cam or admission cam.That is, elastic construction is convex in exhaust cam or air inlet against coordinating by auxiliary piston 4 using elastic force
On wheel, move along auxiliary piston chamber 21 so as to directly drive auxiliary piston 4 by exhaust cam or admission cam.Such auxiliary piston 4
Driving structure it is simple and space availability ratio is high.It is to be appreciated that exhaust cam or admission cam here be simply positioned at
The position of the exhaust cam for being originally intended to drive exhaust valve 62, but shape and profile needed according to the movement locus of auxiliary piston 4 again
Design.That is, without the need for being changed to the integrated model of existing Six-stroke engine 100, only need to be in existing six-stroke
On the basis of electromotor 100, redesign exhaust cam or admission cam, by each combustor 5 in cylinder head 2 it is corresponding its
In an exhaust valve seat insert or inlet valve seat ring be changed to auxiliary piston chamber 21, and increase auxiliary piston 4 and elastic construction, thus
Transformation is convenient and improvement cost is low.
Present invention also offers a kind of vehicle, the vehicle includes the Six-stroke engine 100 described in above-described embodiment, from
And have the advantages that oil consumption is low, engine compression ratio is variable and engine thermal efficiency is high.
Presently preferred embodiments of the present invention is the foregoing is only, not to limit the present invention, all essences in the present invention
Within god and principle, any modification, equivalent substitution and improvements made etc. should be included within the scope of the present invention.
Claims (10)
1. a kind of Six-stroke engine (100), including cylinder block (1), cylinder head (2), inlet valve (61) and exhaust valve (62), institute
State to have in cylinder (11), the cylinder (11) in cylinder block (1) and be provided with main piston (3), the cylinder head (2) is arranged on institute
State the top of cylinder block (1), the cylinder head (2), between the cylinder block (1) and the main piston (3) limit combuster
(5), the inlet valve (61) and the exhaust valve (62) are in the cylinder head (2), it is characterised in that also include：It is secondary
Auxiliary piston chamber (21) is also formed with piston (4), the cylinder head (2), the auxiliary piston chamber (21) is with the combustor (5) even
It is logical；
The auxiliary piston (4) movably coordinates in the auxiliary piston chamber (21) along the centrage of the auxiliary piston chamber (21)；
Wherein
The main piston (3) has with main piston top dead centre (TDC1) and main piston lower dead center (BDC1), the auxiliary piston (4)
Auxiliary piston top dead centre (TDC2) and auxiliary piston lower dead center (BDC2), in main work of the main piston (3) in compression travel (102)
Beyond the Great Wall during stop (TDC1) auxiliary piston (4) in first position, in the main piston (3) in recompression stroke (104)
Main piston top dead centre (TDC1) when the auxiliary piston (4) in the second position, wherein the first position is apart from described secondary living
Beyond the Great Wall the distance of stop (TDC2) is less than distance of the second position apart from the auxiliary piston top dead centre (TDC2).
2. Six-stroke engine (100) according to claim 1, it is characterised in that the second position is described secondary living
Plug (4) moves to the position of the auxiliary piston lower dead center (BDC2).
3. Six-stroke engine (100) according to claim 1, it is characterised in that the first position is positioned at described
Auxiliary piston top dead centre (TDC2) is to the optional position in the auxiliary piston lower dead center (BDC2).
4. Six-stroke engine (100) according to claim 3, it is characterised in that the first position is apart from the pair
The distance of piston top dead center (TDC2) is less than distance of the first position apart from the auxiliary piston lower dead center (BDC2).
5. Six-stroke engine (100) according to claim 1, it is characterised in that the auxiliary piston chamber (21) is arranged in
Air inlet side or exhaust side.
6. Six-stroke engine (100) according to claim 5, it is characterised in that the auxiliary piston chamber (21) is arranged in
The exhaust side, and the auxiliary piston (4) is by exhaust cam shaft (7) driving.
7. Six-stroke engine (100) according to claim 6, it is characterised in that arrange on the exhaust cam shaft (7)
Have it is convex turn (71), be provided with auxiliary piston connecting rod (41) on the auxiliary piston (4), the auxiliary piston connecting rod (41) convex is turned with described
(71) it is connected.
8. Six-stroke engine (100) according to claim 7, it is characterised in that each described combustor (5) correspondence two
The individual inlet valve (61) and an exhaust valve (62) and an auxiliary piston chamber (21)；
Each described combustor (5) of correspondence is provided with one for driving the exhaust valve (62) on the exhaust cam shaft (7)
Exhaust cam (72) and one be used for drive the convex of the auxiliary piston (4) to turn (71), convex turn (71) are with corresponding institute
State exhaust cam (72) to adjoin.
9. Six-stroke engine (100) according to claim 5, it is characterised in that the auxiliary piston (4) is by exhaust cam
(72) or admission cam drive；And
The Six-stroke engine (100) also includes：Elastic construction, the elastic construction is arranged so that the auxiliary piston (4)
Often against cooperation on the exhaust cam (72) or admission cam.
10. a kind of vehicle, it is characterised in that include the Six-stroke engine according to any one of claim 1-9
(100)。
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410596398.XA CN104533612B (en) | 2014-10-29 | 2014-10-29 | Six-stroke engine and vehicle having same |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410596398.XA CN104533612B (en) | 2014-10-29 | 2014-10-29 | Six-stroke engine and vehicle having same |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104533612A CN104533612A (en) | 2015-04-22 |
| CN104533612B true CN104533612B (en) | 2017-04-19 |
Family
ID=52849205
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410596398.XA Active CN104533612B (en) | 2014-10-29 | 2014-10-29 | Six-stroke engine and vehicle having same |
Country Status (1)
| Country | Link |
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| CN (1) | CN104533612B (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111811447B (en) * | 2020-06-11 | 2021-03-23 | 广汽本田汽车有限公司 | Engine piston top dead center measuring system and method |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CH668291A5 (en) * | 1986-06-25 | 1988-12-15 | Roger Bajulaz | INTERNAL COMBUSTION ENGINE. |
| CN1138907C (en) * | 2000-12-05 | 2004-02-18 | 贾平安 | 6-stroke IC engine |
| CN202073637U (en) * | 2010-11-10 | 2011-12-14 | 彭建成 | Six-stroke engine |
| CN102022188A (en) * | 2010-12-31 | 2011-04-20 | 陈伟明 | Six-stroke engine |
| CN202250389U (en) * | 2011-08-19 | 2012-05-30 | 牛耕 | Straight-line or V-line six-cylinder six-stroke engine |
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2014
- 2014-10-29 CN CN201410596398.XA patent/CN104533612B/en active Active
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