CN108386290A - A kind of engine cylinder barrel structure - Google Patents
A kind of engine cylinder barrel structure Download PDFInfo
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- CN108386290A CN108386290A CN201810242751.2A CN201810242751A CN108386290A CN 108386290 A CN108386290 A CN 108386290A CN 201810242751 A CN201810242751 A CN 201810242751A CN 108386290 A CN108386290 A CN 108386290A
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- inner cylinder
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- barrel
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Classifications
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- 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
- F02F1/00—Cylinders; Cylinder heads
- F02F1/02—Cylinders; Cylinder heads having cooling means
- F02F1/10—Cylinders; Cylinder heads having cooling means for liquid cooling
-
- 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
- F02F1/00—Cylinders; Cylinder heads
- F02F1/02—Cylinders; Cylinder heads having cooling means
- F02F1/10—Cylinders; Cylinder heads having cooling means for liquid cooling
- F02F2001/104—Cylinders; Cylinder heads having cooling means for liquid cooling using an open deck, i.e. the water jacket is open at the block top face
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Cylinder Crankcases Of Internal Combustion Engines (AREA)
Abstract
The present invention provides a kind of engine cylinder barrel structures, belong to automobile technical field.It is insufficient and overheat, the problem of lower part heat dissipation is excessively and the phenomenon that be subcooled, and there are still cylinder holes thermal deformations that it solves existing cylinder barrel when in use and can exist top heat-sinking capability.This engine cylinder barrel structure includes cylinder barrel ontology, cylinder barrel ontology includes cylindrical inner cylinder and outer barrel, outer barrel is located on the outside of the inner cylinder, and the lateral wall of lower end and inner cylinder connects and inner cylinder is separated into the first inner cylinder portion and the second inner cylinder portion, the inner surface in the first inner cylinder portion is cylindrical surface, the outer surface in the first inner cylinder portion is curved outer surface, and inner surface is to increase from top to bottom with the wall thickness that outer surface is formed.This engine cylinder barrel structure can mitigate cylinder holes thermal deformation.
Description
Technical field
The invention belongs to automobile technical fields, are related to a kind of engine cylinder barrel structure.
Background technology
Available engine densification, superchargingization trend are apparent, and engine reinforcing degree also increasingly improves, to cooling requirement
Increasingly improve, need flow velocity, the flow of preferably organizing the coolant liquid of cylinder barrel outer wall, so as to alleviate bring cylinder holes thermal deformation it is big,
The problems such as hot-spot, non-uniform temperature, scuffing of cylinder bore, early combustion, engine oil consumption height and cylinder pad difficulty seal.
In view of the above problems, the unfavorable shadow that cylinder holes Zona transformans comes is reduced from the design of cylinder barrel periphery jacket structure for water
It rings, is mainly the following solution：
First, dividing water spacer device：A plastic stent is packed into water jacket, according to cylinder body water jacket upper and lower part, air inlet side
Water, flow velocity adjustment are carried out with the water demands such as near exhaust side, bridge；
Second is that water fender：It is packed into baffle in water jacket, is mounted in inlet, water ratio is divided in adjustable intake and exhaust side；Before being mounted in
Rear end, the flow direction of adjustable water, as flow main flow direction first cools down exhaust side, again cooling air inlet side；
Third, other：Such as waveform bottom water set, shallow water set, water hole, intermediate tiltedly water hole, intermediate separation trough on centre,
Primarily to improving cylinder holes thermal deformation.
There are two types of aluminium alloy cylinder water jacket is general：Enclosed water jacket, open type water jacket are opened as high-pressure casting is more and more extensive
Formula water jacket is also more and more extensive, cylinder sleeve upper deformation bigger, and existing Chinese patent literature also discloses that a kind of opened top
Formula cylinder block【Application number：CN200880008674.9】, in the cylinder block, form water jacket around cylinder and the water jacket exist
It is opened wide at cylinder block top surface:Superficial part and deep are set in the water jacket；It is arranged between the superficial part and the deep and tilts
Portion, compared with the case where this rake is not arranged, flow of cooling water is more steady, it is thus possible to it is cold further to improve cylinder
But.But the cylinder block wall thickness is equal wall thickness, and during actual product, cylinder barrel outer wall typically just combined process
The wall thickness of 0.5~1 degree of pattern draft design is not achieve the effect that loss of weight in this way, and when use can have top heat-sinking capability
It is insufficient and overheat, the problem of lower part heat dissipation is excessively and the phenomenon that be subcooled, and there are still cylinder holes thermal deformations.
Invention content
The purpose of the present invention is in view of the above-mentioned problems existing in the prior art, it is proposed that a kind of engine cylinder barrel structure, it should
Engine cylinder barrel structure the technical problem to be solved is that：How cylinder holes thermal deformation is mitigated.
Object of the invention can be realized by the following technical scheme：A kind of engine cylinder barrel structure, including cylinder barrel ontology,
The cylinder barrel ontology includes cylindrical inner cylinder and outer barrel, and the outer barrel is located on the outside of the inner cylinder, and under
End connect with the lateral wall of inner cylinder and inner cylinder is separated into the first inner cylinder portion and the second inner cylinder portion, first inner cylinder
The inner surface in body portion is cylindrical surface, and the outer surface in first inner cylinder portion is curved outer surface, the inner surface and appearance
The wall thickness that face is formed is to increase from top to bottom.
This engine cylinder barrel structure will be formed between inner cylinder and outer barrel and be used by the way that inner cylinder and outer barrel is arranged
In the water jacket of injection cooling water, the top of inner cylinder is used to constitute the wall thickness of water jacket part, the i.e. wall thickness in the first inner cylinder portion
Be designed as increased wall thickness from top to bottom, and the trend that variation tendency is curvilinear motion, such design so that cooling water by
It is upper to reduce downwards, the effect of heat dissipation can be improved while mitigating cylinder barrel weight, avoid top heat-sinking capability insufficient and overheat,
Lower part heat dissipation is excessive and the phenomenon that be subcooled, and cylinder holes thermal deformation when can effectively reduce work.
In above-mentioned engine cylinder barrel structure, wall thickness that the inner surface and outer surface are formed is from top to bottom exponentially
Curve increases, and the curved outer surface in the first inner cylinder portion is formed with the increased wall thickness of the exponential curve.Using exponential curve
The wall thickness of variation forms the wall thickness in the first inner cylinder portion, the top in the first inner cylinder portion can be prevented relatively thin, and can prevent
The lower part in one inner cylinder portion is thicker, can play the effect of flash heat transfer and heat preservation.
In above-mentioned engine cylinder barrel structure, the wall thickness in second inner cylinder portion is that the first inner cylinder portion is formed most
Big wall thickness.Such design while reducing weight, and can solve the problems, such as that engine early fires.
In above-mentioned engine cylinder barrel structure, the madial wall of the inner cylinder is equipped with liner.Liner is set, can be mitigated
The thermal deformation of cylinder barrel.
In above-mentioned engine cylinder barrel structure, the liner is iron sprayed coating.Using iron sprayed coating as liner, increase
Capacity of heat transmission, while having the advantages that loss of weight, compact-sized, wear-resisting, corrosion resistant.
In above-mentioned engine cylinder barrel structure, the liner is Cast iron liner.Using Cast iron liner as liner, increase
Capacity of heat transmission, and have the advantages that simultaneously wear-resisting, corrosion resistant.
In above-mentioned engine cylinder barrel structure, the calculation formula of first inner cylinder portion wall thickness is：
H2=λ 2*PI*D* (S/2+Lconrod-S/2*cos (a)-(Lconrod^2- (S/2*sin (a)) ^2) ^0.5) *
(CONST1*CONST2*(1+(S/2+Lconrod-S/2*cos(a)-(Lconrod^2-(S/2*sin(a))^2)^0.5)/(S/
(n-1)))(1-k)-Tcool)/(Hu*Mstroke*a/()*(m+1)*y^m*e^(-a*y^(m+1))*6*
Rotate)-λ2/λ1*H1；
Wherein, H2 is the first inner cylinder portion wall thickness, and λ 1 is the thermal coefficient of liner, and λ 2 is the thermal coefficient of cylinder barrel ontology, D
For cylinder diameter, S is piston total kilometres, and n is engine compression ratio, and Lconrod is length of connecting rod, and CONST1 is constant, and CONST2 is normal
Amount, k are adiabatic exponent, and Hu is fuel value, and Tcool is cylinder barrel outer wall coolant temperature, and Mstroke is single-stroke fuel consumption
Amount, a is crank angle；Ab is crank angle when burning starts；Crank angle when ac is fire end；M is form parameter,
Y is afterburning angle score, and e is natural constant, the thickness of H1 liners.
It can be seen that by the calculation formula, the first inner cylinder portion wall thickness is adopted apart from relevant exponential function with descent of piston
This calculation formula is taken to form the wall thickness in the first inner cylinder portion, compared to conventional cylinder barrel thickness, the first inner cylinder portion can be prevented
Top it is blocked up, can flash heat transfer, prevent malcombustion, and the lower part in the first inner cylinder portion can be prevented excessively thin, Neng Gouyou
Certain heat insulation effect increases combustion gas acting ability.
In above-mentioned engine cylinder barrel structure, the height of the outer barrel is the 30%-50% of inner cylinder height.It will be outer
The height of cylinder is set as between the 30%-50% of inner cylinder height, can effectively be reduced the dosage of cooling water, be promoted engine
Fast heat, reduces consumption of lubricating oil, effectively increases the overall performance of engine.
In above-mentioned engine cylinder barrel structure, the inner cylinder and outer barrel are coaxial.Inner cylinder and outer barrel are coaxial, carry
High internal temperature it is uniform, improve the overall performance of engine.
Compared with prior art, this engine cylinder barrel structure has the following advantages：
1, the present invention designs the wall thickness of inner cylinder according to fuel combustion thermal discharge, and such design can effectively reduce work
Cylinder holes thermal deformation when making can also prevent malcombustion；It is the design for becoming wall thickness additionally, due to inner cylinder wall thickness, is improving
Cylinder holes can effectively mitigate weight while deformation.
2, the present invention takes index wall thickness, thick compared to conventional cylinder barrel, can prevent the portion in the upper surface of first inner cylinder portion
Position it is blocked up, can flash heat transfer, prevent malcombustion, and the part below the first inner cylinder portion can be prevented excessively thin, can
There is certain heat insulation effect, increases combustion gas acting ability.
3, cylinder barrel wall thickness of the invention due to top it is relatively thin, gradually thicken from top to bottom, cylinder barrel outer diameter also can be by existing
Mold is put into operation after being repaired a die, and technique influences small.
Description of the drawings
Fig. 1 is the structural schematic diagram of the present invention.
In figure, 1, cylinder barrel ontology；2, inner cylinder；21, the first inner cylinder portion；22, the second inner cylinder portion；3, outer barrel；4、
Wall thickness；5, liner.
Specific implementation mode
Following is a specific embodiment of the present invention in conjunction with the accompanying drawings, technical scheme of the present invention will be further described,
However, the present invention is not limited to these examples.
Embodiment one：
As shown in Figure 1, this engine cylinder barrel structure includes cylinder barrel ontology 1, cylinder barrel ontology 1 includes cylindrical inner cylinder
2 and outer barrel 3, outer barrel 3 is located on 2 outside of inner cylinder, and lower end connect with the lateral wall of inner cylinder 2 and divides inner cylinder 2
It is divided into the first inner cylinder portion 21 and the second inner cylinder portion 22, the inner surface in the first inner cylinder portion 21 is cylindrical surface, the first inner cylinder
The outer surface in portion 21 is curved outer surface, and the wall thickness 4 that inner surface is formed with outer surface is to increase from top to bottom.
Preferably, inner surface and the wall thickness 4 that outer surface is formed are exponentially curve increase from top to bottom, and with this
The increased wall thickness 4 of exponential curve forms the curved outer surface in the first inner cylinder portion 21.Using the increased wall thickness of exponentially curve
It spends to form the wall thickness 4 in the first inner cylinder portion 21, the top in the first inner cylinder portion 21 can be prevented relatively thin, and can prevent in first
The lower part of barrel 21 is thicker, can play the effect of flash heat transfer and heat preservation.
Preferably, the wall thickness 4 in the second inner cylinder portion 22 is the thickest degree that the first inner cylinder portion 21 is formed.This
The design of sample while reducing weight, and can solve the problems, such as that engine early fires.
Preferably, it is arranged with liner 5 in the madial wall of inner cylinder 2, liner 5 is Cast iron liner.Cast iron is set
Cylinder sleeve increases capacity of heat transmission, and has the advantages that simultaneously wear-resisting, corrosion resistant.
Preferably, 21 wall thickness 4 of the first inner cylinder portion is with descent of piston apart from relevant function, specific calculating public affairs
Formula is as follows：
The Ideal-Gas Equation
T Vk-1=CONST1；
Wherein, T is cylinder temperature, and V is cylinder internal volume, and CONST1 is constant, and k is adiabatic exponent；
It can obtain ideally, for piston during downlink, temperature is index variation, to compensate the variation, be can be used
One index variation thickness cylinder barrel, specific calculating are as follows
L is descent of piston distance, and D is cylinder diameter, and H1 is the wall thickness 4 in the first inner cylinder portion 21, and S is piston total kilometres, and n is hair
Motivation compression ratio, Xn are descent of piston distance coefficient (Xn=L/ (S/ (n-1)))；
Then T=CONST1* (PI*D2/4*S/(n-1)+PI*D2/4*Xn*S/(n-1))(1-k)
=CONST1* (PI*D2/4*S/(n-1))(1-k)*(1+Xn)(1-k)
To a stationary engine, (PI*D2/4*S/(n-1))(1-k)For constant, it is set as CONST2
T=CONST1*CONST2* (1+Xn)(1-k)
Combustion heat release meets Weber function rule：
Dx/da=a/ (ab-ac) * (m+1) * y^m*e^ (- a*y^ (m+1))
Dx=dQ/Q
Y=(a-ac)/(ab-ac)
Q is the total amount of heat that fuel combustion is released；A is crank angle；Y is afterburning angle score；E is natural constant, about
It is 2.71828；Ab is crank angle when burning starts；Crank angle when ac is fire end；M is form parameter (burning
Qualitative index, value range is between 2.0~2.5)；A is the Vibe parameters of completely burned, a=6.9；To vibe functional integrations,
The fuel mass fraction to be burnt to a certain moment from combustion start time is obtained,
That is mass fraction burned x：
X=∫ dx/da.da
=1-e^ (- a*y^ (m+1))
=1-e^ (- a* ((a-ac)/(ab-ac)) ^ (m+1))
Namely when engine is run under certain operating mode, theoretically only piston motion position is related for mass fraction burned.
Therefore, Q=x*Hu
=(1-e^ (- a* ((a-ac)/(ab-ac)) ^ (m+1))) * Hu；
Wherein, Hu is fuel value；
Further, fuel value is fixed, then theoretically only piston motion position is related for fuel thermal discharge.
Qcl=Q*CONST3；
Qcl is to spread out of heat by cylinder body and cylinder sleeve；
CONST3 is the proportionality coefficient that cylinder body and cylinder sleeve spreads out of that heat accounts for the total thermal discharge of fuel, and usually, coolant liquid takes away heat
Amount 15~25% can be set as constant wherein spreading out of heat about 40% by cylinder body and cylinder sleeve in certain operating mode.
Then, dQcl/dt=dQcl/da*da/dt
=dQcl/da*6*Rotate
=Hu*Mstroke*dx/da*6*Rotate
=Hu*a/ (ab-a-
c)*(m+1)*y^m*e^(-a*y^(m+1))*6*Rotate；
Wherein, Rotate is engine speed, and Mstroke is single-stroke fuel consumption；
Wherein, piston displacement formula is：
L=S/2+Lconrod-S/2*cos (a)-(Lconrod^2- (S/2*sin (a)) ^2) ^0.5；Lconrod is to connect
Bar is long；
It is obtained according to heat transfer formula：
Usually, there is a fixed proportion relationship by iron cylinder sleeve and the heat conducted by aluminium cylinder barrel, be set as equal herein,
λ 1* (T-Tmid)/H1*PI*D*L=λ 2* (Tmid-Tcool)/H2*PI*D*L
Then, Tmid=(λ 1*T/H1+ λ 2*Tcool/H2)/(λ 1/H1+ λ 2/H2)
Heat transfer formula is reused, and ignores the influence of cylinder dig pass heat,
DQcl/dt=λ 2* (Tmid-Tcool)/H2*PI*D*L；
Wherein, λ 1 is the thermal coefficient of liner 5；λ 2 is 1 thermal coefficient of cylinder barrel ontology；H1 is the thickness of liner 5；H2 is interior
21 wall thickness 4 of the first inner cylinder portion of cylinder 2；Tmid is outer wall of cylinder jachet temperature；Tcool is cylinder barrel outer wall coolant temperature, and PI is
Pi；
Tmid substitution above formulas are had,
DQcl/dt=λ 2* (Tmid-Tcool)/H2*PI*D*L
=λ 2* ((λ 1*T/H1+ λ 2*Tcool/H2)/(λ 1/H1+ λ 2/H2)-Tcool)/H2*PI*D*L；
Then H2=λ 2*PI*D*L* (T-Tcool)/2/ λ 1*H1 of (dQcl/dt)-λ
=λ 2*PI*D*L* (T-Tcool)/2/ λ 1*H1 of (dQcl/dt)-λ
=λ 2*PI*D*
(S/2+Lconrod-S/2*cos(a)-(Lconrod^2-(S/2*sin(a))^2)^0.5)*(CONST1*
CONST2*(1+Xn)(1-k)-Tcool)/(Hu*a/(ab-a-c)*(m+1)*y^m*e^(-a*y^(m+1))*6*Rotate)-λ2/
λ 1*H1=λ 2*PI*D*
(S/2+Lconrod-S/2*cos(a)-(Lconrod^2-(S/2*sin(a))^2)^0.5)*(CONST1*
CONST2*
(1+(S/2+Lconrod-S/2*cos(a)-(Lconrod^2-(S/2*sin(a))^2)^0.5)/(S/(n-1))
)(1-k)-Tcool)/(Hu*Mstroke*a/(ab-ac)*(m+1)*y^m*e^(-a*y^(m+1))*6*Rotate)-λ2/λ1*
H1；
As can be seen from the above equation, 4 cylinder sleeve H1 of widely used equal wall thickness is constant, generally 2mm-3mm, if ignored
Lower part coolant temperature Tcool differences, H2 are the first inner cylinders of the exponential function that piston displacement is independent variable namely inner cylinder 2
The thickness in body portion 21 is the exponential function of amount of piston displacement.
In actual design process, heat liberation rate, heat release rate generally reaches maximum in the crank angle degrees of 10 crank angle degrees~20, at this time cylinder
The heat of body water jacket conduction is concentrated mainly on upper area, this just needs the wall thickness 4 in the first inner cylinder portion 21 of inner cylinder 2 to fit
It spends thinning to radiate as early as possible.Heat liberation rate, heat release rate gradually declines after 20 crank angle degrees, at this time the first inner cylinder portion 21 of inner cylinder 2
Wall thickness 4 can increase, to prevent be subcooled so that fuel economy is bad.When corner reaches 90 crank angle degrees, Ke Yikao
Limitation cylinder barrel largest outside diameter value or shallow water set method are considered to design 1 structure of cylinder barrel ontology.Conventional cylinder barrel thickness 4 is generally taken single
Draft angle realizes that top is thin, and lower part is thick.This engine cylinder barrel structure takes index wall thickness 4, compares conventional cylinder barrel thickness 4, both
Top can be prevented blocked up, can flash heat transfer, prevent malcombustion, and lower part can be prevented excessively thin, can there is certain heat preservation effect
Fruit increases combustion gas acting ability.
It can be seen that by the calculation formula, the wall thickness 4 in the first inner cylinder portion 21 is with descent of piston apart from relevant index letter
Number takes this calculation formula to form the wall thickness 4 in the first inner cylinder portion 21, compares conventional cylinder barrel thickness 4, can prevent first
The top in inner cylinder portion 21 is blocked up, can flash heat transfer, prevent malcombustion, and the lower part in the first inner cylinder portion 21 can be prevented
It is excessively thin, there can be certain heat insulation effect, increase combustion gas acting ability.
Preferably, the height of outer barrel 3 is the 30%-50% of 2 height of inner cylinder.The height of outer barrel 3 is set
It is set between the 30%-50% of 2 height of inner cylinder, can effectively reduce the dosage of cooling water, promote engine hot soon, reduce
Consumption of lubricating oil effectively increases the overall performance of engine.
Preferably, inner cylinder 2 and outer barrel 3 are coaxial.Inner cylinder 2 and outer barrel 3 are coaxial, improve internal temperature
It is uniform, improve the overall performance of engine.
Embodiment two：
Technical solution in the present embodiment and the technical solution in embodiment one are essentially identical, the difference is that：Liner 5
For iron sprayed coating.Thickness is 0.1mm-0.2mm, using iron sprayed coating as liner 5, increases capacity of heat transmission, has simultaneously
Loss of weight, compact-sized, wear-resisting, corrosion resistant advantage.
Specific embodiment described herein is only an example for the spirit of the invention.Technology belonging to the present invention is led
The technical staff in domain can make various modifications or additions to the described embodiments or replace by a similar method
In generation, however, it does not deviate from the spirit of the invention or beyond the scope of the appended claims.
Claims (9)
1. a kind of engine cylinder barrel structure, including cylinder barrel ontology (1), the cylinder barrel ontology (1) includes cylindrical inner cylinder
(2) and outer barrel (3), the outer barrel (3) are located on the inner cylinder (2) outside, and the lateral wall of lower end and inner cylinder (2)
It connects and inner cylinder (2) is separated into the first inner cylinder portion (21) and the second inner cylinder portion (22), first inner cylinder portion
(21) inner surface is cylindrical surface, which is characterized in that the outer surface in first inner cylinder portion (21) is curved outer surface, institute
It is to increase from top to bottom to state the wall thickness (4) that inner surface is formed with outer surface.
2. engine cylinder barrel structure according to claim 1, which is characterized in that the wall that the inner surface is formed with outer surface
Thick (4) are that exponentially curve increases from top to bottom, and forms the first inner cylinder portion (21) with the increased wall thickness of the exponential curve (4)
Curved outer surface.
3. engine cylinder barrel structure according to claim 1 or 2, which is characterized in that second inner cylinder portion (22) wall
The numerical values recited of thick (4) is the thickest degree that the first inner cylinder portion (21) is formed.
4. engine cylinder barrel structure according to claim 1 or 2, which is characterized in that the madial wall of the inner cylinder (2) is set
There is liner (5).
5. engine cylinder barrel structure according to claim 4, which is characterized in that the liner (5) is iron sprayed coating.
6. engine cylinder barrel structure according to claim 4, which is characterized in that the liner (5) be Cast iron liner.
7. engine cylinder barrel structure according to claim 4, which is characterized in that first inner cylinder portion (21) wall thickness
(4) calculation formula is：
H2=λ 2*PI*D* (S/2+Lconrod-S/2*cos (a)-(Lconrod^2- (S/2*sin (a)) ^2) ^0.5) *
(CONST1*CONST2*(1+(S/2+Lconrod-S/2*cos(a)-(Lconrod^2-(S/2*sin(a))^2)^0.5)/(S/
(n-1)))(1-k)-Tcool)/(Hu*Mstroke*a/(ab-ac)*(m+1)*y^m*e^(-a*y^(m+1))*6*Rotate)-λ
2/λ1*H1；
Wherein, H2 is first inner cylinder portion (21) wall thickness (4), and λ 1 is the thermal coefficient of liner (5), and λ 2 is that cylinder barrel ontology (1) is led
Hot coefficient, D are cylinder diameter, and S is piston total kilometres, and n is engine compression ratio, and Lconrod is length of connecting rod, and CONST1 is constant,
CONST2 is constant, and k is adiabatic exponent, and Hu is fuel value, and Tcool is cylinder barrel outer wall coolant temperature, and Mstroke is one-shot
Journey fuel consumption, a are crank angle；Ab is crank angle when burning starts；Crank angle when ac is fire end；m
For form parameter, y is afterburning angle score, and e is natural constant, and H1 is the thickness of liner (5).
8. engine cylinder barrel structure according to claim 1 or 2, which is characterized in that the height of the outer barrel (3) is interior
The 30%-50% of cylinder (2) height.
9. engine cylinder barrel structure according to claim 1 or 2, which is characterized in that the inner cylinder (2) and outer barrel
(3) coaxial.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810242751.2A CN108386290A (en) | 2018-03-23 | 2018-03-23 | A kind of engine cylinder barrel structure |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810242751.2A CN108386290A (en) | 2018-03-23 | 2018-03-23 | A kind of engine cylinder barrel structure |
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| CN108386290A true CN108386290A (en) | 2018-08-10 |
Family
ID=63067149
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| DE3447579A1 (en) * | 1984-01-23 | 1985-07-25 | Steyr-Daimler-Puch Ag, Wien | Cast cylinder for two-stroke internal combustion engines |
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| CN201474784U (en) * | 2009-08-31 | 2010-05-19 | 上海通用汽车有限公司 | Engine cylinder body |
| CN202266341U (en) * | 2011-09-20 | 2012-06-06 | 广州汽车集团股份有限公司 | Automobile engine cylinder body |
| CN103511112A (en) * | 2012-06-20 | 2014-01-15 | 通用电气公司 | Variable thickness coating for cylinder liner |
| CN104806370A (en) * | 2014-01-27 | 2015-07-29 | 内山工业株式会社 | Water jacket spacer |
-
2018
- 2018-03-23 CN CN201810242751.2A patent/CN108386290A/en active Pending
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3447579A1 (en) * | 1984-01-23 | 1985-07-25 | Steyr-Daimler-Puch Ag, Wien | Cast cylinder for two-stroke internal combustion engines |
| CN2630507Y (en) * | 2002-06-18 | 2004-08-04 | 上汽集团奇瑞汽车有限公司 | Automobile engine body |
| US20050028758A1 (en) * | 2002-09-16 | 2005-02-10 | Perkins Engines Company Limited | Cylinder block for an internal combustion engine having a locally thickened end wall |
| JP2005201085A (en) * | 2004-01-13 | 2005-07-28 | Toyota Motor Corp | Cylinder block and engine |
| CN101578444A (en) * | 2007-02-22 | 2009-11-11 | 丰田自动车株式会社 | Working method and working jig for cylinder block, and cylinder block |
| CN201474784U (en) * | 2009-08-31 | 2010-05-19 | 上海通用汽车有限公司 | Engine cylinder body |
| CN202266341U (en) * | 2011-09-20 | 2012-06-06 | 广州汽车集团股份有限公司 | Automobile engine cylinder body |
| CN103511112A (en) * | 2012-06-20 | 2014-01-15 | 通用电气公司 | Variable thickness coating for cylinder liner |
| CN104806370A (en) * | 2014-01-27 | 2015-07-29 | 内山工业株式会社 | Water jacket spacer |
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Application publication date: 20180810 |
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| RJ01 | Rejection of invention patent application after publication |