CN114991953A - V-shaped 6-cylinder engine with 95-degree included angle - Google Patents
V-shaped 6-cylinder engine with 95-degree included angle Download PDFInfo
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- CN114991953A CN114991953A CN202210551145.5A CN202210551145A CN114991953A CN 114991953 A CN114991953 A CN 114991953A CN 202210551145 A CN202210551145 A CN 202210551145A CN 114991953 A CN114991953 A CN 114991953A
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- 238000002485 combustion reaction Methods 0.000 claims description 6
- 238000010304 firing Methods 0.000 claims description 4
- 239000000463 material Substances 0.000 description 2
- 238000003672 processing method Methods 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
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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
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B75/00—Other engines
- F02B75/16—Engines characterised by number of cylinders, e.g. single-cylinder engines
- F02B75/18—Multi-cylinder engines
- F02B75/22—Multi-cylinder engines with cylinders in V, fan, or star arrangement
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- 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
- F02B75/32—Engines characterised by connections between pistons and main shafts and not specific to preceding main groups
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- 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
- F02B75/16—Engines characterised by number of cylinders, e.g. single-cylinder engines
- F02B75/18—Multi-cylinder engines
- F02B2075/1804—Number of cylinders
- F02B2075/1824—Number of cylinders six
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Supercharger (AREA)
Abstract
The invention provides a V-shaped 6-cylinder engine with an included angle of 95 degrees, and belongs to the field of engines. The problem of some enterprises select high dynamic nature to increase crankshaft journal etc. and in order to promote spare part intensity, the economic nature of sacrifice is compensated by other energy such as battery, and the engine itself has not accomplished oil consumption and power and has compromise yet is solved. The engine comprises a cylinder body and a crankshaft, wherein the right row of a V angle of the cylinder body is respectively 1 cylinder 2 cylinder 3 cylinders from front to back, the left row is respectively 4 cylinders 5 cylinders 6 cylinders from front to back, the crankshaft is arranged in the cylinder body, the V angle of the cylinder body is a, wherein the angle a is more than 90 degrees and less than 120 degrees, and the addition of the wrong turning angle of the crankshaft and the V angle of the cylinder body is equal to the conventional ignition interval angle of 120 degrees. The invention adopts the design of increasing the V angle of the crank throw of the crankshaft, reducing the angle of wrong throw, improving the strength of the crankshaft, properly reducing the shaft diameter of the connecting rod of the crankshaft, reducing the friction loss and realizing the improvement of the dynamic property and the economical efficiency of the engine.
Description
Technical Field
The invention belongs to the field of engines, and particularly relates to a V-shaped 6-cylinder engine with an included angle of 95 degrees.
Background
The V-shaped 6-cylinder gasoline engine is a classic engine type in the industry, and the conventional ignition interval angle is 120 degrees, namely the ignition interval angle of 120 degrees is obtained by dividing the rotation angle of two circles of crankshafts by the cylinder number of 6. The included angle between the axis of the left row of cylinders and the axis of the right row of cylinders of the V-shaped gasoline engine is generally called as a V angle, and the included angle between the axis of the two adjacent connecting rod journal and the connecting line of the crankshaft journal on the corresponding crankshaft becomes a crankshaft misturning angle. The common V angle is two conventional designs of 60 degrees and 90 degrees, the corresponding crank throw angles are 60 degrees and 30 degrees respectively, namely the V angle and the crank throw angle are added to obtain the firing interval angle of 120 degrees. Of course, the angle V may be designed at 180 ° or at other angles, but the sum of the corresponding crank angle degrees is 120 °.
With the continuous tightening of national oil consumption regulations, the heat efficiency of an engine needs to be improved through technical means, the oil consumption is reduced, the friction work generated by a friction pair is reduced by adopting a method of reducing the shaft diameter of a crankshaft connecting rod, and the strength of the crankshaft is reduced by adopting the measures under the condition of not changing the material, the overlapping coefficient and the processing method of the crankshaft. At present, the design of the V-type 6-cylinder gasoline engine in the industry does not break the rule, so in order to meet the continuously upgraded oil consumption regulation, part of enterprises select to reduce the dynamic property to ensure the oil consumption, namely, the small crankshaft journal and the relatively low dynamic property are kept to ensure the strength. Some enterprises select high dynamic performance, increase crankshaft journals and the like to improve the strength of parts, the sacrificed economy is compensated by other energy sources such as batteries, and the engine does not have the oil consumption and the power.
Disclosure of Invention
In view of the above, the present invention is directed to a V-type 6 cylinder 95 ° angle engine to solve the above mentioned problems in the background art, which reduces the strength of the crankshaft due to the reduction of the shaft diameter of the crankshaft connecting rod, and reduces the dynamic performance of the engine.
In order to achieve the purpose, the invention adopts the following technical scheme: a V-shaped 6-cylinder 95-degree included angle engine comprises a cylinder body and a crankshaft, wherein the right row of a V angle of the cylinder body is respectively 1 cylinder 2 cylinder 3 cylinder from front to back, the left row is respectively 4 cylinders 5 cylinders 6 cylinder from front to back,
the crankshaft is arranged in the cylinder body, the V angle of the cylinder body is a, wherein the angle a is more than 90 degrees and less than 120 degrees, and the sum of the misturning angle of the crankshaft and the V angle of the cylinder body is equal to the conventional ignition interval angle of 120 degrees.
Furthermore, the V angle of the cylinder body is 95 degrees, and the angle of the crank shaft in a wrong turning way is 25 degrees.
Furthermore, the ignition sequence of the V-shaped 6-cylinder 95-degree included angle engine is 1 cylinder-4 cylinder-3 cylinder-6 cylinder-2 cylinder-5 cylinder.
Further, the firing interval angle is 120 °.
Furthermore, the cylinder body is externally connected with a right row of air inlet manifold, a right row of air throttle, a right row of supercharger, a right row of exhaust pipe, a left row of air inlet manifold, a left row of air throttle, a left row of supercharger and a left row of exhaust pipe, wherein the right row of air inlet manifold, the right row of air throttle, the right row of supercharger and the right row of exhaust pipe are positioned on the right side of the cylinder body, the left row of air inlet manifold, the left row of air throttle, the left row of supercharger and the left row of exhaust pipe are positioned on the left side of the cylinder body, the left row of exhaust pipe is installed on the left row of supercharger, and the right row of exhaust pipe is installed on the right row of supercharger.
Furthermore, the right row of the intake manifold and the left row of the intake manifold are symmetrically arranged in two rows.
Furthermore, the right row of throttle valves and the left row of throttle valves are symmetrically arranged in two rows.
Furthermore, the right row of superchargers and the left row of superchargers are symmetrically arranged in two rows.
Furthermore, the right exhaust pipe row and the left exhaust pipe row are symmetrically arranged in two rows.
Furthermore, when the engine works, the supercharger pressurizes the sucked air, the air flows through the throttle valve and the intake manifold and then enters the cylinder body, the exhaust gas generated by the full mixing and combustion with the gasoline flows through the supercharger through the exhaust pipe, the power of the compressed air is brought to the supercharger, and the power generated by the combustion is transmitted to the automobile wheels through the crankshaft to drive the automobile to run.
Compared with the prior art, the V-shaped 6-cylinder engine with the included angle of 95 degrees has the beneficial effects that:
(1) the design of increasing the V angle of the crank throw of the crankshaft, reducing the wrong throw angle, improving the strength of the crankshaft, properly reducing the shaft diameter of the connecting rod of the crankshaft, reducing the friction loss and realizing the improvement of the dynamic property and the economical efficiency of the engine is adopted.
(2) The crank throw structure reduces the angle of the crank throw, increases the overlapping coefficient between the shaft diameters of two connecting rods on the same crank throw, and improves the strength of the crank throw.
(3) The invention properly reduces the shaft diameter of the crankshaft connecting rod, reduces the friction work between the crankshaft and the connecting rod, reduces the energy loss and increases the heat efficiency of the engine.
(4) The invention adopts a conventional ignition interval angle of 120 degrees, namely when a crankshaft rotates for two cycles by 720 degrees, the engine can ignite according to the sequence of 1 cylinder-4 cylinders-3 cylinders-6 cylinders-2 cylinders-5 cylinders-1 cylinders, the ignition interval of each cylinder is 120 degrees, and uniform ignition is realized.
(5) The technology can be applied to other double-arrangement gasoline engines such as V-shaped 8 cylinders, V-shaped 12 cylinders and the like in the same way, and the design generalization rate is higher.
(6) Under the condition of not changing the shaft diameter, materials and processing method of the connecting rods of the crankshaft, after the crankshaft is designed in a wrong way, the angle of the wrong corner of the crankshaft is reduced from 30 degrees to 25 degrees, namely the angle V is reduced from 30 degrees to 25 degrees, the contact area between the shaft diameters of the two connecting rods on the same crank throw of the crankshaft is increased, the overlapping coefficient of the shaft diameters of the left and right connecting rods of the crankshaft is increased, the strength of the crankshaft is increased, and the dynamic property of an engine is increased; at the moment, the shaft diameter of the crankshaft connecting rod is properly reduced, the friction between the shaft diameter of the crankshaft connecting rod and the connecting rod can be reduced, and the purpose of reducing oil consumption is achieved.
Drawings
The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate an embodiment of the invention and, together with the description, serve to explain the invention and not to limit the invention. In the drawings:
FIG. 1 is a front view of a V-type 6 cylinder 95 ° angle engine according to the present invention;
FIG. 2 is a perspective view of a V-shaped 6 cylinder 95 degree angle engine according to the present invention;
FIG. 3 is a front view of a crankshaft of the present invention;
FIG. 4 is a cross-sectional view of the crankshaft A-A shown in FIG. 3 according to the present invention.
In the figure: 1-cylinder block, 2-crankshaft, 3-right row of intake manifold, 4-right row of throttle valve, 5-right row of supercharger, 6-left row of intake manifold, 7-left row of throttle valve and 8-left row of exhaust pipe.
Detailed Description
The technical solution in the embodiments of the present invention will be clearly and completely explained below with reference to the drawings in the embodiments of the present invention. It should be noted that, in the present invention, the embodiments and features of the embodiments may be combined with each other without conflict, and the described embodiments are only a part of the embodiments of the present invention, not all of the embodiments.
First embodiment, referring to fig. 1 to 4 to explain the present embodiment, a V-shaped 6-cylinder 95 ° angle engine includes a cylinder block 1 and a crankshaft 2, the right row of the V angle of the cylinder block 1 is 1 cylinder 2, 3 cylinders from front to back, the left row is 4 cylinders 5, 6 cylinders from front to back,
the crankshaft 2 is arranged in the cylinder body 1, the V angle of the cylinder body 1 is a, wherein 90 degrees is larger than a and smaller than 120 degrees, and the sum of the misturning angle of the crankshaft 2 and the V angle of the cylinder body 1 is equal to the conventional ignition spacing angle of 120 degrees.
The key feature of the present invention is as shown in fig. 1, the V angle of the cylinder 1 is 95 °, the angle of the crankshaft 2 is 25 °, that is, the sum of the two is 120 ° of the conventional ignition interval angle.
Along with the reduction of the wrong turning angle of the crankshaft 2 to 25 degrees, the contact area of the shaft diameters of two adjacent connecting rods of the crankshaft 2 is increased, the strength and the safety coefficient of the crankshaft are increased, the pressure born by the crankshaft 2 is higher, and the dynamic property of the engine is improved; when the diameter of the shaft diameter of the connecting rod of the crankshaft is reduced, the contact area between the shaft diameters of the connecting rods is reduced, so that the diameter of the shaft diameter of the connecting rods is properly reduced, the contact area between the shaft diameters of the two connecting rods is larger than that of the unchanged crankshaft, the strength of the crankshaft can be increased, the friction force is reduced, and the dynamic property and the economical efficiency of the engine are improved.
The V angle of the cylinder body 1 is 95 degrees, the right row is respectively 1 cylinder 2 cylinder 3 cylinders from front to back, and the left row is respectively 4 cylinders 5 cylinders 6 cylinders from front to back, so that the cylinder body accords with the conventional classical design.
The V angle of the cylinder block 1 can be other angles greater than 90 °, the final choice depending on the structural arrangement and the safety factor of the crankshaft 2.
The crank shaft 2 disclosed by the invention has the wrong turning angle of 25 degrees, and the design can effectively improve the strength of the crank shaft under the condition that the journal of the connecting rod of the crank shaft is not enlarged, namely, the friction work is reduced and the safety coefficient is improved.
As shown in FIG. 2, the engine mainly comprises a cylinder body 1, a crankshaft 2, a right row of intake manifolds 3, a right row of throttle valves 4, a right row of superchargers 5, a right row of exhaust pipes, a left row of intake manifolds 6, a left row of throttle valves 7 and a left row of supercharger exhaust pipes 8, wherein the crankshaft 2 is arranged in the cylinder body 1, and the intake manifolds, the throttle valves, the superchargers, the exhaust pipes and the like are connected to the outside of the cylinder body 1.
The cylinder body 1 external connection has the right side to be listed as air intake manifold 3, the right side is listed as air throttle 4, the right side is listed as booster 5, the right side is listed as the blast pipe, the left side is listed as air intake manifold 6, the left side is listed as air throttle 7, the left side is listed as booster and left side is listed as blast pipe 8, wherein the right side is listed as air intake manifold 3, the right side is listed as air throttle 4, the right side is listed as booster 5 and the right side is listed as blast pipe and is located cylinder body 1 right side, the left side is listed as air intake manifold 6, the left side is listed as air throttle 7, the left side is listed as booster and the left side is listed as blast pipe 8 and is located cylinder body 1 left side, install left side on the left side and be listed as blast pipe 8 on the booster, install right side and be listed as the blast pipe on the booster 5.
Wherein the right row of intake manifolds 3 and the left row of intake manifolds 6 are arranged in a double-row symmetrical manner. The right row of throttle valves 4 and the left row of throttle valves 7 are symmetrically arranged in two rows. The right-row supercharger 5 and the left-row supercharger are symmetrically arranged in two rows, and the right-row exhaust pipe and the left-row exhaust pipe 8 are symmetrically arranged in two rows.
When the engine works, the supercharger pressurizes the sucked air, the air flows through the throttle valve and the intake manifold and then enters the cylinder body 1, the exhaust gas generated by the full mixing and combustion with gasoline flows through the supercharger through the exhaust pipe, the power of the compressed air is brought to the supercharger, and the power generated by the combustion is transmitted to the automobile wheels through the crankshaft to drive the automobile to run. The ignition sequence of the gasoline engine is 1 cylinder-4 cylinders-3 cylinders-6 cylinders-2 cylinders-5 cylinders.
The intake manifold, the throttle valve, the supercharger, the exhaust pipe and the like are all designed in a double-row symmetrical arrangement mode, so that independent closed-loop control can be realized on the left row and the right row of the engine by using a left controller and a right controller based on crankshaft signals, and uniform ignition of each cylinder is realized.
Fig. 3 shows the structure of the crankshaft 2, and fig. 4 shows a schematic view of a cross section a-a of the crankshaft 2, wherein the hatched area is the overlapping area of the shaft diameters of two adjacent crankshaft connecting rods, and the area is increased along with the decrease of the V angle, so that the strength of the crankshaft of the engine is increased, the safety factor of the crankshaft is increased, and the dynamic property of the engine is improved. According to the principle, the shaft diameter is properly reduced, namely the friction work can be reduced, the economy of the engine is improved, finally, the shadow area shown in figure 4 is increased, the shaft diameter of the crankshaft connecting rod is reduced, and the power economy of the engine is improved.
The key points and points to be protected of the invention are:
1. the V angle of the cylinder 1 is 95 °, the angle of the crankshaft 2 is 25 °, i.e. the sum of the angles equals a conventional firing interval angle of 120 °.
2. The left and right banks of cylinders are supplied with air by separate throttles and exhaust by separate superchargers, and the two banks can be controlled separately without mutual influence.
3. The whole ignition sequence is 1 cylinder-4 cylinder-3 cylinder-6 cylinder-2 cylinder-5 cylinder-1 cylinder, and the whole ignition interval angle is 120 degrees, 120 degrees and 120 degrees, namely the interval is 120 degrees.
The embodiments of the invention disclosed above are intended merely to aid in the explanation of the invention. The examples are not intended to be exhaustive or to limit the invention to the precise forms disclosed. Many modifications and variations are possible in light of the above teaching. The embodiments were chosen and described in order to best explain the principles of the invention and the practical application, to thereby enable others skilled in the art to best utilize the invention.
Claims (10)
1. The utility model provides a V type 6 jar 95 contained angles engines which characterized in that: comprises a cylinder body (1) and a crankshaft (2), wherein the right row of a V angle of the cylinder body (1) is respectively provided with 1 cylinder, 2 cylinders and 3 cylinders from front to back, the left row is respectively provided with 4 cylinders, 5 cylinders and 6 cylinders from front to back,
the crankshaft (2) is arranged in the cylinder body (1), the V angle of the cylinder body (1) is a, wherein the angle a is more than 90 degrees and less than 120 degrees, and the sum of the misturning angle of the crankshaft (2) and the V angle of the cylinder body (1) is equal to the conventional ignition interval angle of 120 degrees.
2. The V-type 6 cylinder 95 ° angle engine of claim 1, wherein: the V angle of the cylinder body (1) is 95 degrees, and the angle of the crank shaft (2) in a wrong turning way is 25 degrees.
3. The V-type 6 cylinder 95 ° angle engine of claim 1, wherein: the ignition sequence of the V-shaped 6-cylinder 95-degree included angle engine is 1 cylinder-4 cylinders-3 cylinders-6 cylinders-2 cylinders-5 cylinders.
4. The V-type 6 cylinder 95 ° angle engine of claim 4, wherein: the firing interval angle is 120 °.
5. The V-type 6 cylinder 95 ° angle engine of claim 1, wherein: cylinder body (1) outside still is connected with the right side and is listed as air intake manifold (3), the right side is listed as choke valve (4), the right side is listed as booster (5), the right side is listed as blast pipe, the left side is listed as air intake manifold (6), the left side is listed as choke valve (7), the left side is listed as booster and left side is listed as blast pipe (8), wherein the right side is listed as air intake manifold (3), the right side is listed as choke valve (4), the right side is listed as booster (5) and the right side is listed as blast pipe and is located cylinder body (1) right side, the left side is listed as air intake manifold (6), the left side is listed as choke valve (7), the left side is listed as booster and the left side is listed as blast pipe (8) and is located cylinder body (1) left side, install the right side on the booster (5) and is listed as blast pipe.
6. The V-type 6 cylinder 95 ° angle engine of claim 5, wherein: wherein the right row of intake manifolds (3) and the left row of intake manifolds (6) are arranged in a double-row symmetrical manner.
7. The V-type 6 cylinder 95 ° angle engine of claim 6, wherein: the right row of throttle valves (4) and the left row of throttle valves (7) are symmetrically arranged in two rows.
8. The V-type 6 cylinder 95 ° angle engine of claim 7, wherein: the right row of superchargers (5) and the left row of superchargers are symmetrically arranged in two rows.
9. The V-type 6 cylinder 95 ° angle engine of claim 8, wherein: the right exhaust pipe and the left exhaust pipe (8) are symmetrically arranged in two rows.
10. The V-type 6 cylinder 95 ° angle engine according to any one of claims 5 to 9, wherein: when the engine works, the supercharger pressurizes the sucked air, the air flows through the throttle valve and the intake manifold and then enters the cylinder body (1), the exhaust gas generated by full mixing and combustion with gasoline flows through the supercharger through the exhaust pipe, the power of compressed air is brought to the supercharger, and the power generated by combustion is transmitted to the automobile wheels through the crankshaft to drive the automobile to run.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210551145.5A CN114991953A (en) | 2022-05-20 | 2022-05-20 | V-shaped 6-cylinder engine with 95-degree included angle |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210551145.5A CN114991953A (en) | 2022-05-20 | 2022-05-20 | V-shaped 6-cylinder engine with 95-degree included angle |
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| CN114991953A true CN114991953A (en) | 2022-09-02 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202210551145.5A Pending CN114991953A (en) | 2022-05-20 | 2022-05-20 | V-shaped 6-cylinder engine with 95-degree included angle |
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Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH07180562A (en) * | 1993-12-24 | 1995-07-18 | Hino Motors Ltd | V-type engine with turbosupercharger |
| CN101149003A (en) * | 2006-09-21 | 2008-03-26 | 本田技研工业株式会社 | Multicylinder internal combustion engine |
| CN101328834A (en) * | 2008-07-17 | 2008-12-24 | 无锡开普动力有限公司 | V type engine |
| CN102182555A (en) * | 2010-01-15 | 2011-09-14 | 通用汽车环球科技运作有限责任公司 | Internal combustion engine |
| CN102278196A (en) * | 2010-06-11 | 2011-12-14 | Dr.Ing.h.c.F.保时捷股份公司 | Internal combustion engine |
| CN204099395U (en) * | 2014-07-22 | 2015-01-14 | 北京北内柴油机有限责任公司 | Six cylinder ductile iron crankshafts |
| CN105370452A (en) * | 2014-08-12 | 2016-03-02 | 福特环球技术公司 | Systems and methods for a modified cylinder firing interval in a dedicated egr engine |
| CN113586233A (en) * | 2021-09-15 | 2021-11-02 | 重庆磐谷动力技术有限公司 | V-shaped high-pressure common rail engine |
-
2022
- 2022-05-20 CN CN202210551145.5A patent/CN114991953A/en active Pending
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH07180562A (en) * | 1993-12-24 | 1995-07-18 | Hino Motors Ltd | V-type engine with turbosupercharger |
| CN101149003A (en) * | 2006-09-21 | 2008-03-26 | 本田技研工业株式会社 | Multicylinder internal combustion engine |
| CN101328834A (en) * | 2008-07-17 | 2008-12-24 | 无锡开普动力有限公司 | V type engine |
| CN102182555A (en) * | 2010-01-15 | 2011-09-14 | 通用汽车环球科技运作有限责任公司 | Internal combustion engine |
| CN102278196A (en) * | 2010-06-11 | 2011-12-14 | Dr.Ing.h.c.F.保时捷股份公司 | Internal combustion engine |
| CN204099395U (en) * | 2014-07-22 | 2015-01-14 | 北京北内柴油机有限责任公司 | Six cylinder ductile iron crankshafts |
| CN105370452A (en) * | 2014-08-12 | 2016-03-02 | 福特环球技术公司 | Systems and methods for a modified cylinder firing interval in a dedicated egr engine |
| CN113586233A (en) * | 2021-09-15 | 2021-11-02 | 重庆磐谷动力技术有限公司 | V-shaped high-pressure common rail engine |
Non-Patent Citations (2)
| Title |
|---|
| 郭建等: ""某V型6缸柴油机错拐曲轴设计"", 《内燃机与配件》, no. 8, pages 1 - 3 * |
| 郭建等: "某V型6缸柴油机错拐曲轴设计", 内燃机与配件, 31 December 2011 (2011-12-31), pages 1 - 3 * |
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