US20110277718A1 - Engine including valve geometry relative to bore size - Google Patents
Engine including valve geometry relative to bore size Download PDFInfo
- Publication number
- US20110277718A1 US20110277718A1 US12/874,340 US87434010A US2011277718A1 US 20110277718 A1 US20110277718 A1 US 20110277718A1 US 87434010 A US87434010 A US 87434010A US 2011277718 A1 US2011277718 A1 US 2011277718A1
- Authority
- US
- United States
- Prior art keywords
- cylinder bore
- diameter
- defining
- intake
- exhaust
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Abandoned
Links
Images
Classifications
-
- 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
- F02B23/00—Other engines characterised by special shape or construction of combustion chambers to improve operation
- F02B23/08—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition
-
- 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
- F02F1/24—Cylinder heads
- F02F1/42—Shape or arrangement of intake or exhaust channels in cylinder heads
- F02F1/4214—Shape or arrangement of intake or exhaust channels in cylinder heads specially adapted for four or more valves per cylinder
-
- 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
Definitions
- the present disclosure relates to engine intake and exhaust valve and port geometry, and more specifically to intake and exhaust valve and port geometry defined by cylinder bore size.
- Internal combustion engines may combust a mixture of air and fuel in cylinders and thereby produce drive torque.
- Intake ports may provide air flow to the combustion chamber for combustion.
- the products of combustion may exit the combustion chamber via exhaust ports.
- An engine assembly may include an engine block defining a cylinder bore, a cylinder head coupled to the engine block, a first intake valve, a fuel injector in communication with the cylinder bore and a spark plug in communication with the cylinder bore.
- the cylinder bore may define a first diameter.
- the cylinder head may define a first intake port and a first exhaust port in communication with the cylinder bore.
- the first intake valve may be located in the first intake port and may define a second diameter at least 35 percent of the first diameter.
- the fuel injector and the spark plug may be located centrally relative to the cylinder bore.
- the first diameter may be less than 80 millimeters.
- the engine assembly may additionally include a first exhaust valve located in the first exhaust port and defining a third diameter at least 30 percent of the first diameter. More specifically, the second diameter may be at least 37 percent of the first diameter and the third diameter may be at least 32 percent of the first diameter.
- the cylinder head may additionally define a second intake port and a second exhaust port in communication with the cylinder bore.
- the first and second intake ports may be located on a first radial half of the cylinder bore and the first and second exhaust ports may be located on a second radial half of the cylinder bore opposite the first radial half.
- a first line extending radially through a center of the cylinder bore and a center of the first intake valve extends at an angle of between 40 degrees and 44 degrees relative to a line extending radially across the cylinder bore defining the first radial half and the second radial half when the first intake valve is in a seated position.
- a second line extending radially through the center of the cylinder bore and a center of the first exhaust valve extends at an angle of between 39 degrees and 43 degrees relative to the line extending radially across the cylinder bore defining the first radial half and the second radial half when the first exhaust valve is in a seated position.
- the engine assembly may include a second intake valve located in the second intake port and defining a fourth diameter at least 37 percent of the first diameter and a second exhaust valve located in the second exhaust port and defining a fifth diameter at least 32 percent of the first diameter.
- FIG. 1 is a schematic illustration of an engine assembly according to the present disclosure.
- FIG. 2 is a schematic fragmentary top plan view of the engine assembly of FIG. 1 illustrating intake and exhaust ports relative to the cylinder bore and fuel spray of the engine assembly of FIG. 1 .
- Example embodiments are provided so that this disclosure will be thorough, and will fully convey the scope to those who are skilled in the art. Numerous specific details are set forth such as examples of specific components, devices, and methods, to provide a thorough understanding of embodiments of the present disclosure. It will be apparent to those skilled in the art that specific details need not be employed, that example embodiments may be embodied in many different forms and that neither should be construed to limit the scope of the disclosure. In some example embodiments, well-known processes, well-known device structures, and well-known technologies are not described in detail.
- first, second, third, etc. may be used herein to describe various elements, components, regions, layers and/or sections, these elements, components, regions, layers and/or sections should not be limited by these terms. These terms may be only used to distinguish one element, component, region, layer or section from another region, layer or section. Terms such as “first,” “second,” and other numerical terms when used herein do not imply a sequence or order unless clearly indicated by the context. Thus, a first element, component, region, layer or section discussed below could be termed a second element, component, region, layer or section without departing from the teachings of the example embodiments.
- An engine assembly 10 is schematically illustrated in FIGS. 1 and 2 and may include an engine structure 12 , first and second intake valves 14 , 15 , first and second exhaust valves 16 , 17 , a piston 18 , a spark plug 20 and a fuel injector 22 .
- the engine structure 12 may include an engine block 24 defining a cylinder bore 28 and a cylinder head 26 coupled to the engine block 24 .
- the piston 18 may be disposed in the cylinder bore 28 .
- the engine block 24 , the cylinder head 26 and the piston 18 may cooperate to define a combustion chamber 30 .
- the first and second intake valves 14 , 15 may each extend at an intake valve angle ( ⁇ I ) relative to a sidewall of the cylinder bore 28 .
- the intake valve angle ( ⁇ I ) may be between 19 degrees and 21 degrees. In the present non-limiting example, the intake valve angle ( ⁇ I ) is approximately 20 degrees.
- the first and second exhaust valves 16 , 17 may each extend at an exhaust valve angle ( ⁇ E ) relative to the sidewall of the cylinder bore 28 .
- the exhaust valve angle ( ⁇ E ) may be between 17.5 degrees and 19.5 degrees. In the present non-limiting example, the exhaust valve angle is approximately 18.5 degrees.
- the cylinder head 26 may define intake and exhaust passages 32 , 34 in communication with the combustion chamber 30 .
- the intake passages 32 may define a first intake port 36 in communication with the cylinder bore 28 at the combustion chamber 30 and a second intake port 37 in communication with the cylinder bore 28 at the combustion chamber 30 .
- the first intake valve 14 may be located in the first intake port 36 and the second intake valve 15 may be located in the second intake port 37 .
- the exhaust passages 34 may define a first exhaust port 38 in communication with the cylinder bore 28 at the combustion chamber 30 and a second exhaust port 39 in communication with the cylinder bore 28 at the combustion chamber 30 .
- the first exhaust valve 16 may be located in the first exhaust port 38 and the second exhaust valve 17 may be located in the second exhaust port 39 . It is understood that the present teachings apply to any number of piston-cylinder arrangements and a variety of engine configurations including, but not limited to, V-engines, inline engines, and horizontally opposed engines, as well as both overhead cam and cam-in-block configurations.
- the spark plug 20 may be in communication with the cylinder bore 28 and located centrally relative to the cylinder bore 28 and the fuel injector 22 may be in communication with the cylinder bore 28 and located centrally relative to the cylinder bore 28 .
- the spark plug 20 and the fuel injector 22 may each be located in the cylinder head 26 and may be in direct communication with the combustion chamber 30 .
- the spark plug 20 and the fuel injector 22 may be centrally located in the combustion chamber 30 relative to an outer radial perimeter defined by the cylinder bore 28 , forming a central direct injection configuration.
- the spark plug 20 and the fuel injector 22 may each be radially offset from a center (C B ) of the cylinder bore 28 in directions opposite one another.
- the location and size of the first and second intake valves 14 , 15 and the first and second exhaust valves 16 , 17 may be defined as a function of the cylinder bore 28 .
- the first and second intake valves 14 , 15 and the first and second exhaust valves 16 , 17 may be disposed at an angle relative to the cylinder bore 28 .
- FIG. 2 illustrates the cross-sections of the first and second intake valves 14 , 15 and the first and second exhaust valves 16 , 17 being perpendicular to the cylinder bore 28 to better illustrate the relation between the first and second intake valves 14 , 15 and the first and second exhaust valves 16 , 17 and the cylinder bore 28 .
- a first axis (A 1 ) may extend through the center (C B ) of the cylinder bore 28 between the first intake port 36 and the second intake port 37 and between the first exhaust port 38 and the second exhaust port 39 .
- a second axis (A 2 ) may extend through the center (C B ) of the cylinder bore 28 perpendicular to the first axis (A 1 ).
- the first and second intake ports 36 , 37 and the first and second intake valves 14 , 15 may be symmetric about the first axis (A 1 ).
- the first and second exhaust ports 38 , 39 and the first and second exhaust valves 16 , 17 may be symmetric about the first axis (A 1 ).
- first intake valve 14 the first intake port 36 , the first exhaust valve 16 , and the first exhaust port 38 will be discussed with the understanding that the description applies equally to the second intake valve 15 , the second intake port 37 , the second exhaust valve 17 and the second exhaust port 39 .
- the first and second intake valves 14 , 15 and the first and second intake ports 36 , 37 may be located on a first radial half of the cylinder bore 28 .
- the first and second exhaust valves 16 , 17 and the first and second exhaust ports 38 , 39 may be located on a second radial half of the cylinder bore 28 opposite the first radial half.
- the spark plug 20 and the fuel injector 22 may be located between the first and second radial halves.
- the second axis (A 2 ) may define a line extending radially across the cylinder bore 28 and defining the first radial half and the second radial half.
- the cylinder bore 28 may define a first diameter (D B ), the first intake valve 14 may define a second diameter (D I1 ) and the first exhaust valve 16 may define a third diameter (D E1 ).
- the spark plug 20 and the fuel injector 22 may be located centrally (radially) within the first intake port 36 and the first exhaust port 38 .
- the first diameter (D B ) of the cylinder bore 28 may be less than 80 millimeters, and more specifically less than 75 millimeters. In the present non-limiting example, the first diameter is approximately 74 millimeters.
- the second diameter (D I1 ) may be at least 35 percent of the first diameter (D B ) and the third diameter (D E1 ) may be at least 30 percent of the first diameter (D B ). More specifically, the second diameter (D I1 ) may be at least 37 percent of the first diameter (D B ) and the third diameter (D E1 ) may be at least 32 percent of the first diameter (D B ).
- the second intake valve 15 may be similar to the first intake valve 14 and the second exhaust valve 17 may be similar to the first exhaust valve 16 . Therefore, the second intake valve 15 may define a fourth diameter (D I2 ) at least 35 percent of the first diameter (D B ) and the second exhaust valve 17 may define a fifth diameter (D E2 ) at least 30 percent of the first diameter (D B ). More specifically, the fourth diameter (D I2 ) may be at least 37 percent of the first diameter (D B ) and the fifth diameter (D E2 ) may be at least 32 percent of the first diameter (D B ).
- the second and fourth diameters (D I1 , D I2 ) are approximately 38 percent of the first diameter (D B ), and the third and fifth diameters (D E1 ,D E2 ) are approximately 32 percent of the first diameter (D B ).
- the location of the center of the first intake valve 14 and the center of the first exhaust valve 16 may each be defined as a function of the cylinder bore 28 as well.
- a first line (L I ) extending radially through the center (C B ) of the cylinder bore 28 and the center (C I ) of the first intake valve 14 may extend at a first angle ( ⁇ I ) relative to the second axis (A 2 ) when the first intake valve 14 is in a seated position (closed position).
- a second line (L E ) extending radially through the center (C B ) of the cylinder bore 28 and the center (C E ) of the first exhaust valve 16 may extend at a second angle ( ⁇ E ) relative to the second axis (A 2 ) when the first exhaust valve 16 is in a seated position (closed position).
- the first angle ( ⁇ I ) may be between 40 degrees and 44 degrees and the second angle ( ⁇ E ) may be between 39 degrees and 43 degrees.
- the first intake valve 14 and the first exhaust valve 16 may be located such that the first angle ( ⁇ E ) is approximately 42 degrees and the second angle ( ⁇ E ) is approximately 41 degrees.
- a first radial distance (D LI ) defined along the first line (L I ) between the center (C B ) of the cylinder bore 28 and a radially innermost portion of the first intake valve 14 may be less than 25 millimeters when the first intake valve 14 is in the seated position.
- a second radial distance (D LE ) defined along the second line (L E ) between the center (C B ) of the cylinder bore 28 and a radially innermost portion of the first exhaust valve 16 may be less than 27 millimeters when the first exhaust valve 16 is in the seated position.
- the first radial distance (D LI ) is approximately 23 millimeters and the second radial distance (D LE ) is approximately 26 millimeters.
Abstract
Description
- This application claims the benefit of U.S. Provisional Application No. 61/345,369, filed on May 17, 2010. The entire disclosure of the above application is incorporated herein by reference.
- The present disclosure relates to engine intake and exhaust valve and port geometry, and more specifically to intake and exhaust valve and port geometry defined by cylinder bore size.
- This section provides background information related to the present disclosure which is not necessarily prior art.
- Internal combustion engines may combust a mixture of air and fuel in cylinders and thereby produce drive torque. Intake ports may provide air flow to the combustion chamber for combustion. The products of combustion may exit the combustion chamber via exhaust ports. As engines become increasing smaller, accommodating appropriate valve and port sizes becomes more difficult.
- An engine assembly may include an engine block defining a cylinder bore, a cylinder head coupled to the engine block, a first intake valve, a fuel injector in communication with the cylinder bore and a spark plug in communication with the cylinder bore. The cylinder bore may define a first diameter. The cylinder head may define a first intake port and a first exhaust port in communication with the cylinder bore. The first intake valve may be located in the first intake port and may define a second diameter at least 35 percent of the first diameter. The fuel injector and the spark plug may be located centrally relative to the cylinder bore.
- The first diameter may be less than 80 millimeters. The engine assembly may additionally include a first exhaust valve located in the first exhaust port and defining a third diameter at least 30 percent of the first diameter. More specifically, the second diameter may be at least 37 percent of the first diameter and the third diameter may be at least 32 percent of the first diameter.
- The cylinder head may additionally define a second intake port and a second exhaust port in communication with the cylinder bore. The first and second intake ports may be located on a first radial half of the cylinder bore and the first and second exhaust ports may be located on a second radial half of the cylinder bore opposite the first radial half.
- A first line extending radially through a center of the cylinder bore and a center of the first intake valve extends at an angle of between 40 degrees and 44 degrees relative to a line extending radially across the cylinder bore defining the first radial half and the second radial half when the first intake valve is in a seated position. A second line extending radially through the center of the cylinder bore and a center of the first exhaust valve extends at an angle of between 39 degrees and 43 degrees relative to the line extending radially across the cylinder bore defining the first radial half and the second radial half when the first exhaust valve is in a seated position.
- The engine assembly may include a second intake valve located in the second intake port and defining a fourth diameter at least 37 percent of the first diameter and a second exhaust valve located in the second exhaust port and defining a fifth diameter at least 32 percent of the first diameter.
- Further areas of applicability will become apparent from the description provided herein. The description and specific examples in this summary are intended for purposes of illustration only and are not intended to limit the scope of the present disclosure.
- The drawings described herein are for illustrative purposes only and are not intended to limit the scope of the present disclosure in any way.
-
FIG. 1 is a schematic illustration of an engine assembly according to the present disclosure; and -
FIG. 2 is a schematic fragmentary top plan view of the engine assembly ofFIG. 1 illustrating intake and exhaust ports relative to the cylinder bore and fuel spray of the engine assembly ofFIG. 1 . - Corresponding reference numerals indicate corresponding parts throughout the several views of the drawings.
- Examples of the present disclosure will now be described more fully with reference to the accompanying drawings. The following description is merely exemplary in nature and is not intended to limit the present disclosure, application, or uses.
- Example embodiments are provided so that this disclosure will be thorough, and will fully convey the scope to those who are skilled in the art. Numerous specific details are set forth such as examples of specific components, devices, and methods, to provide a thorough understanding of embodiments of the present disclosure. It will be apparent to those skilled in the art that specific details need not be employed, that example embodiments may be embodied in many different forms and that neither should be construed to limit the scope of the disclosure. In some example embodiments, well-known processes, well-known device structures, and well-known technologies are not described in detail.
- When an element or layer is referred to as being “on,” “engaged to,” “connected to” or “coupled to” another element or layer, it may be directly on, engaged, connected or coupled to the other element or layer, or intervening elements or layers may be present. In contrast, when an element is referred to as being “directly on,” “directly engaged to,” “directly connected to” or “directly coupled to” another element or layer, there may be no intervening elements or layers present. Other words used to describe the relationship between elements should be interpreted in a like fashion (e.g., “between” versus “directly between,” “adjacent” versus “directly adjacent,” etc.). As used herein, the term “and/or” includes any and all combinations of one or more of the associated listed items.
- Although the terms first, second, third, etc. may be used herein to describe various elements, components, regions, layers and/or sections, these elements, components, regions, layers and/or sections should not be limited by these terms. These terms may be only used to distinguish one element, component, region, layer or section from another region, layer or section. Terms such as “first,” “second,” and other numerical terms when used herein do not imply a sequence or order unless clearly indicated by the context. Thus, a first element, component, region, layer or section discussed below could be termed a second element, component, region, layer or section without departing from the teachings of the example embodiments.
- An
engine assembly 10 is schematically illustrated inFIGS. 1 and 2 and may include anengine structure 12, first andsecond intake valves second exhaust valves piston 18, aspark plug 20 and afuel injector 22. Theengine structure 12 may include anengine block 24 defining acylinder bore 28 and acylinder head 26 coupled to theengine block 24. Thepiston 18 may be disposed in thecylinder bore 28. Theengine block 24, thecylinder head 26 and thepiston 18 may cooperate to define acombustion chamber 30. - The first and
second intake valves cylinder bore 28. The intake valve angle (αI) may be between 19 degrees and 21 degrees. In the present non-limiting example, the intake valve angle (αI) is approximately 20 degrees. The first andsecond exhaust valves cylinder bore 28. The exhaust valve angle (αE) may be between 17.5 degrees and 19.5 degrees. In the present non-limiting example, the exhaust valve angle is approximately 18.5 degrees. - The
cylinder head 26 may define intake andexhaust passages combustion chamber 30. In the present non-limiting example, theintake passages 32 may define afirst intake port 36 in communication with the cylinder bore 28 at thecombustion chamber 30 and asecond intake port 37 in communication with the cylinder bore 28 at thecombustion chamber 30. Thefirst intake valve 14 may be located in thefirst intake port 36 and thesecond intake valve 15 may be located in thesecond intake port 37. - The
exhaust passages 34 may define afirst exhaust port 38 in communication with thecylinder bore 28 at thecombustion chamber 30 and asecond exhaust port 39 in communication with the cylinder bore 28 at thecombustion chamber 30. Thefirst exhaust valve 16 may be located in thefirst exhaust port 38 and thesecond exhaust valve 17 may be located in thesecond exhaust port 39. It is understood that the present teachings apply to any number of piston-cylinder arrangements and a variety of engine configurations including, but not limited to, V-engines, inline engines, and horizontally opposed engines, as well as both overhead cam and cam-in-block configurations. - The
spark plug 20 may be in communication with thecylinder bore 28 and located centrally relative to thecylinder bore 28 and thefuel injector 22 may be in communication with thecylinder bore 28 and located centrally relative to thecylinder bore 28. Thespark plug 20 and thefuel injector 22 may each be located in thecylinder head 26 and may be in direct communication with thecombustion chamber 30. In the present non-limiting example, thespark plug 20 and thefuel injector 22 may be centrally located in thecombustion chamber 30 relative to an outer radial perimeter defined by the cylinder bore 28, forming a central direct injection configuration. Thespark plug 20 and thefuel injector 22 may each be radially offset from a center (CB) of the cylinder bore 28 in directions opposite one another. - With reference to
FIG. 2 , the location and size of the first andsecond intake valves second exhaust valves FIG. 1 and as discussed above, the first andsecond intake valves second exhaust valves FIG. 2 illustrates the cross-sections of the first andsecond intake valves second exhaust valves second intake valves second exhaust valves - A first axis (A1) may extend through the center (CB) of the cylinder bore 28 between the
first intake port 36 and thesecond intake port 37 and between thefirst exhaust port 38 and thesecond exhaust port 39. A second axis (A2) may extend through the center (CB) of the cylinder bore 28 perpendicular to the first axis (A1). The first andsecond intake ports second intake valves second exhaust ports second exhaust valves first intake valve 14, thefirst intake port 36, thefirst exhaust valve 16, and thefirst exhaust port 38 will be discussed with the understanding that the description applies equally to thesecond intake valve 15, thesecond intake port 37, thesecond exhaust valve 17 and thesecond exhaust port 39. - The first and
second intake valves second intake ports second exhaust valves second exhaust ports spark plug 20 and thefuel injector 22 may be located between the first and second radial halves. The second axis (A2) may define a line extending radially across the cylinder bore 28 and defining the first radial half and the second radial half. - The cylinder bore 28 may define a first diameter (DB), the
first intake valve 14 may define a second diameter (DI1) and thefirst exhaust valve 16 may define a third diameter (DE1). Thespark plug 20 and thefuel injector 22 may be located centrally (radially) within thefirst intake port 36 and thefirst exhaust port 38. The first diameter (DB) of the cylinder bore 28 may be less than 80 millimeters, and more specifically less than 75 millimeters. In the present non-limiting example, the first diameter is approximately 74 millimeters. - By way of non-limiting example, the second diameter (DI1) may be at least 35 percent of the first diameter (DB) and the third diameter (DE1) may be at least 30 percent of the first diameter (DB). More specifically, the second diameter (DI1) may be at least 37 percent of the first diameter (DB) and the third diameter (DE1) may be at least 32 percent of the first diameter (DB).
- As discussed above, the
second intake valve 15 may be similar to thefirst intake valve 14 and thesecond exhaust valve 17 may be similar to thefirst exhaust valve 16. Therefore, thesecond intake valve 15 may define a fourth diameter (DI2) at least 35 percent of the first diameter (DB) and thesecond exhaust valve 17 may define a fifth diameter (DE2) at least 30 percent of the first diameter (DB). More specifically, the fourth diameter (DI2) may be at least 37 percent of the first diameter (DB) and the fifth diameter (DE2) may be at least 32 percent of the first diameter (DB). In the present non-limiting example, the second and fourth diameters (DI1, DI2) are approximately 38 percent of the first diameter (DB), and the third and fifth diameters (DE1,DE2) are approximately 32 percent of the first diameter (DB). - The location of the center of the
first intake valve 14 and the center of thefirst exhaust valve 16 may each be defined as a function of the cylinder bore 28 as well. A first line (LI) extending radially through the center (CB) of the cylinder bore 28 and the center (CI) of thefirst intake valve 14 may extend at a first angle (θI) relative to the second axis (A2) when thefirst intake valve 14 is in a seated position (closed position). A second line (LE) extending radially through the center (CB) of the cylinder bore 28 and the center (CE) of thefirst exhaust valve 16 may extend at a second angle (θE) relative to the second axis (A2) when thefirst exhaust valve 16 is in a seated position (closed position). By way of non-limiting example, the first angle (θI) may be between 40 degrees and 44 degrees and the second angle (θE) may be between 39 degrees and 43 degrees. In the present non-limiting example, thefirst intake valve 14 and thefirst exhaust valve 16 may be located such that the first angle (θE) is approximately 42 degrees and the second angle (θE) is approximately 41 degrees. - A first radial distance (DLI) defined along the first line (LI) between the center (CB) of the cylinder bore 28 and a radially innermost portion of the
first intake valve 14 may be less than 25 millimeters when thefirst intake valve 14 is in the seated position. A second radial distance (DLE) defined along the second line (LE) between the center (CB) of the cylinder bore 28 and a radially innermost portion of thefirst exhaust valve 16 may be less than 27 millimeters when thefirst exhaust valve 16 is in the seated position. In the present non-limiting example, the first radial distance (DLI) is approximately 23 millimeters and the second radial distance (DLE) is approximately 26 millimeters.
Claims (20)
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US12/874,340 US20110277718A1 (en) | 2010-05-17 | 2010-09-02 | Engine including valve geometry relative to bore size |
DE102010044546A DE102010044546A1 (en) | 2010-05-17 | 2010-09-07 | Motor with hole size valve geometry |
CN2010105203714A CN102251843A (en) | 2010-05-17 | 2010-09-14 | Engine including valve geometry relative to bore size |
BRPI1003614-8A BRPI1003614A2 (en) | 2010-05-17 | 2010-09-30 | motor assembly |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US34536910P | 2010-05-17 | 2010-05-17 | |
US12/874,340 US20110277718A1 (en) | 2010-05-17 | 2010-09-02 | Engine including valve geometry relative to bore size |
Publications (1)
Publication Number | Publication Date |
---|---|
US20110277718A1 true US20110277718A1 (en) | 2011-11-17 |
Family
ID=44910609
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US12/874,340 Abandoned US20110277718A1 (en) | 2010-05-17 | 2010-09-02 | Engine including valve geometry relative to bore size |
Country Status (4)
Country | Link |
---|---|
US (1) | US20110277718A1 (en) |
CN (1) | CN102251843A (en) |
BR (1) | BRPI1003614A2 (en) |
DE (1) | DE102010044546A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20190186409A1 (en) * | 2017-12-19 | 2019-06-20 | Ge Jenbacher Gmbh & Co Og | Cylinder head for one internal combustion engine |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN103670773A (en) * | 2012-09-18 | 2014-03-26 | 广西玉柴机器股份有限公司 | Four-valve gas engine |
CN112648099B (en) * | 2019-10-11 | 2022-07-22 | 广州汽车集团股份有限公司 | Cylinder head assembly and engine comprising same |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6276330B1 (en) * | 2000-02-23 | 2001-08-21 | Ford Global Technologies, Inc. | Air/fuel induction system for developing swirl motion of an air/fuel mixture |
US6799550B2 (en) * | 2001-12-14 | 2004-10-05 | Ford Global Technologies, Llc | Spark-ignition engine having direct fuel injection |
US6945212B2 (en) * | 2004-02-10 | 2005-09-20 | Nissan Motor Co., Ltd. | Combustion chamber structure for internal combustion engine |
US20080022967A1 (en) * | 2005-01-06 | 2008-01-31 | Dai Tanaka | Direct-Injection Spark-Ignition Internal Combustion Engine |
US7849683B2 (en) * | 2006-01-13 | 2010-12-14 | Honda Motor Co., Ltd | Multiple-cylinder internal combustion engine having cylinder head provided with centralized exhaust passageway |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3145696A (en) * | 1962-08-31 | 1964-08-25 | White Motor Co | Internal combustion engine |
SE401239B (en) * | 1972-05-10 | 1978-04-24 | List Hans | INJECTION TYPE COMBUSTION ENGINE |
DE4141063C2 (en) * | 1991-12-13 | 1994-06-23 | Michael Liewehr | Cylinder head for internal combustion engines |
DE19704965A1 (en) * | 1997-02-10 | 1998-08-13 | Audi Ag | Diesel internal combustion engine |
DE10035239B4 (en) * | 2000-07-20 | 2011-04-21 | Daimler Ag | Internal combustion engine |
CN2546631Y (en) * | 2002-06-18 | 2003-04-23 | 上汽集团奇瑞汽车有限公司 | Vehicle engine |
-
2010
- 2010-09-02 US US12/874,340 patent/US20110277718A1/en not_active Abandoned
- 2010-09-07 DE DE102010044546A patent/DE102010044546A1/en not_active Withdrawn
- 2010-09-14 CN CN2010105203714A patent/CN102251843A/en active Pending
- 2010-09-30 BR BRPI1003614-8A patent/BRPI1003614A2/en not_active IP Right Cessation
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6276330B1 (en) * | 2000-02-23 | 2001-08-21 | Ford Global Technologies, Inc. | Air/fuel induction system for developing swirl motion of an air/fuel mixture |
US6799550B2 (en) * | 2001-12-14 | 2004-10-05 | Ford Global Technologies, Llc | Spark-ignition engine having direct fuel injection |
US6945212B2 (en) * | 2004-02-10 | 2005-09-20 | Nissan Motor Co., Ltd. | Combustion chamber structure for internal combustion engine |
US20080022967A1 (en) * | 2005-01-06 | 2008-01-31 | Dai Tanaka | Direct-Injection Spark-Ignition Internal Combustion Engine |
US7849683B2 (en) * | 2006-01-13 | 2010-12-14 | Honda Motor Co., Ltd | Multiple-cylinder internal combustion engine having cylinder head provided with centralized exhaust passageway |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20190186409A1 (en) * | 2017-12-19 | 2019-06-20 | Ge Jenbacher Gmbh & Co Og | Cylinder head for one internal combustion engine |
EP3502450A1 (en) * | 2017-12-19 | 2019-06-26 | Innio Jenbacher GmbH & Co OG | Cylinder head for one internal combustion engine |
Also Published As
Publication number | Publication date |
---|---|
BRPI1003614A2 (en) | 2013-01-29 |
DE102010044546A1 (en) | 2011-11-17 |
CN102251843A (en) | 2011-11-23 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US8763570B2 (en) | Engine assembly including multiple bore center pitch dimensions | |
US8468998B2 (en) | Engine having fuel injection induced combustion chamber mixing | |
US9593640B2 (en) | Engine assembly including cylinder head cooling | |
US20130319381A1 (en) | Engine including venturi in intake air flow path for exhaust gas recirculation supply | |
US9038592B2 (en) | Cylinder head comprising a shroud | |
US20120006287A1 (en) | Engine assembly with integrated exhaust manifold | |
US20110277718A1 (en) | Engine including valve geometry relative to bore size | |
US20140150759A1 (en) | Engine Including External EGR System | |
US8544436B2 (en) | Engine assembly including camshaft with multimode lobe | |
US20120031355A1 (en) | Engine including partial integrated intake manifold | |
US20120097138A1 (en) | Engine assembly including rotary engine providing exhaust gas recirculation to primary engine | |
US8887680B2 (en) | Engine assembly including modified camshaft arrangement | |
US9032921B2 (en) | Engine assembly including variable valve lift arrangement | |
US8534251B2 (en) | Engine assembly with camshaft housing | |
US8651075B2 (en) | Engine assembly including camshaft with independent cam phasing | |
US10082100B2 (en) | Cylinder head and engine block configuration | |
US20120125282A1 (en) | Engine assembly including combustion chambers with different port arrangements | |
US20110277727A1 (en) | Engine including fuel injector spray pattern | |
US7571708B2 (en) | Spark ignited direct injection targeting for improved combustion | |
US9097204B2 (en) | Cylinder head configuration for internal combustion engine | |
US10100776B2 (en) | Preformed article for cylinder head, cylinder head, and method for manufacturing cylinder head | |
US7565893B2 (en) | Spark ignited direct injection flow geometry for improved combustion | |
US8616173B2 (en) | Engine assembly including modified intake port arrangement | |
FI130147B (en) | Internal combustion engine | |
US20180058390A1 (en) | Three cylinder head for a dedicated egr internal combustion engine including two ports |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: GM GLOBAL TECHNOLOGY OPERATIONS, INC., MICHIGAN Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:HALSALL, SCOTT;LUCHANSKY, KEVIN M.;BAKER, RODNEY E.;REEL/FRAME:024930/0602 Effective date: 20100901 |
|
AS | Assignment |
Owner name: WILMINGTON TRUST COMPANY, DELAWARE Free format text: SECURITY AGREEMENT;ASSIGNOR:GM GLOBAL TECHNOLOGY OPERATIONS, INC.;REEL/FRAME:025324/0658 Effective date: 20101027 |
|
AS | Assignment |
Owner name: GM GLOBAL TECHNOLOGY OPERATIONS LLC, MICHIGAN Free format text: CHANGE OF NAME;ASSIGNOR:GM GLOBAL TECHNOLOGY OPERATIONS, INC.;REEL/FRAME:025781/0333 Effective date: 20101202 |
|
STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |