• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    Rib configurations for increasing the structural efficiency of a cylinder head (20) relating to a peak combustion pressure capacity of the cylinder head (20). In addition to increasing the peak combustion pressure, the fin configurations can also improve the sealing of the cylinder head (20) and improve the durability of an associated cylinder head gasket.
    公开号:AT514866A2
    申请号:T9239/2013
    申请日:2013-06-25
    公开日:2015-04-15
    发明作者:
    申请人:Cummins Ip Inc；
    IPC主号:
    专利说明:

    CYLINDER HEAD FOR INTERNAL COMBUSTION ENGINE TECHNICAL SPECIALIST
    This disclosure relates to cylinder heads for internal combustion engines. More particularly, this disclosure relates to a cylinder head configuration with higher structural efficiency than conventional cylinder heads. The structural efficiency of a cylinder head relates to the pressure capacity of a cylinder for a given mass of the cylinder head.
    BACKGROUND
    In response to government regulations and customer expectations, the fuel efficiency of vehicles is increased. One way to increase the fuel efficiency of a vehicle is to reduce the weight of the vehicle. In internal combustion engine driven vehicles, the weight of the engine may be a substantial part of the vehicle weight. One way to reduce the weight of an internal combustion engine is thus a way to improve the fuel efficiency of an associated vehicle. Due to the size and complexity of internal combustion engines, there may still be unexpected and unanticipated opportunities to reduce the weight of such engines.
    In addition to reducing the weight, an improved combustion pressure could be implemented if a cylinder head of an internal combustion engine could be configured to increase combustion pressure capability while reducing weight. Increasing the combustion pressure results in more thorough or improved combustion of fuel, thereby reducing emissions and increasing the efficiency of the engine.
    SUMMARY
    This disclosure provides a cylinder head for an internal combustion engine. The cylinder head includes a bottom plate, a component bore, a screw boss, a valve boss, and a first rib. The component bore has a wall that extends longitudinally from the bottom plate. The screw boss extends in the longitudinal direction from the bol denplatte and is located at a position at a first radial distance from the component bore. The valve lug is at a position at a second radial distance from the component bore. The second radial distance is less than the first radial distance. The first rib extends upwardly in the longitudinal direction from the bottom plate, is connected to the screw boss at a first end, and extends to a location on an upper portion of the screw boss.
    This disclosure also provides a cylinder head for an internal combustion engine. The cylinder head includes a bottom plate, a component bore, a screw boss, a valve boss, an intake port, an exhaust port, and a first rib. The component bore has a component bore wall extending longitudinally from the bottom plate. The screw boss extends longitudinally from the bottom plate and is at a position at a first radial distance from the component bore. The valve lug is at a position at a second radial distance from the component bore. The second radial distance is less than the first radial distance. The intake passage is formed in the cylinder head, and the intake passage includes an intake passage wall. The exhaust duct is formed in the cylinder head, and the exhaust duct includes an exhaust duct wall. The first rib extends upwardly in the longitudinal direction from one of the intake passage wall and the exhaust passage passage wall, and is connected to a location on the component bore wall.
    This disclosure also provides a cylinder head for an internal combustion engine. The cylinder head includes a bottom plate, at least one intake passage, at least one exhaust passage, a component bore, a plurality of bolt bosses, a plurality of valve bosses, and a plurality of ribs. The intake passage includes an intake passage wall. The exhaust duct includes an exhaust duct wall. The component bore includes a component bore wall and a component bore center extending longitudinally from the bottom plate. Each screw boss of the plurality of bolt bosses extends longitudinally from the bottom panel and includes a screw attachment center. Each of the plurality of bolt bosses is disposed at a spaced angle about the component bore at one or more first radial distances from the component bore. Each valve lobe of the plurality of valve lobes has a valve lobe center and extends longitudinally from an intake passage or exhaust passage wall. Each of the plurality of valve lobes is disposed at a spaced angle about the component bore at one or more second radial distances, wherein the second radial distances are less than the first radial distances. The plurality of ribs extend in the longitudinal direction of at least one of the group consisting of the bottom plate, the suction channel wall and the exhaust duct wall, and the plurality of ribs are connected to at least one of the plurality of screw bosses, the plurality consists of valve lugs and the component bore wall.
    Advantages and features of the embodiments of this disclosure will become more apparent from the following detailed description of exemplary embodiments, taken in conjunction with the accompanying drawings.
    BRIEF DESCRIPTION OF THE DRAWING FIG. 1 is a sectional view of a part of a conventional internal combustion engine. FIG. 2 is a sectional view of a conventional cylinder head of the internal combustion engine of FIG. 1. FIG. 3 is a sectional view of a cylinder head according to a first embodiment of the present disclosure taken along line 3-3 in FIG. 5. FIG. 4 is a perspective view of the cylinder head of FIG. 3, with certain parts removed. FIG. 5 is a plan view of the cylinder head of FIG. 4. FIG. 6 is a perspective view of a cylinder head according to a second embodiment of the present disclosure. FIG. 7 is a plan view of the cylinder head of FIG. 6th FIG. 8 is a perspective view of a cylinder head according to a third embodiment of the present disclosure. FIG. 9 is a plan view of the cylinder head of FIG. 8. FIG. 10 is a perspective view of a cylinder head according to a fourth embodiment of the present disclosure. FIG. 11 is a plan view of the cylinder head of FIG. 10. FIG. 12 is a perspective view of a cylinder head according to a fifth embodiment of the present disclosure. FIG. 13 is a plan view of the cylinder head of FIG. 12. FIG. 14 is a perspective view of a cylinder head according to a sixth embodiment of the present disclosure. FIG. 15 is a plan view of the cylinder head of FIG. 14th
    DETAILED DESCRIPTION
    In FIG. 1 and 2 is a portion of a conventional internal combustion engine, shown in cross-sectional view and generally designated 10. The engine 10 includes a machine body or block 12, a small portion of which is shown, and at least one combustion chamber 14. Of course, the engine 10 may also include a plurality of combustion chambers, e.g. Four, six or eight, which may be arranged in a row or in a "V" configuration. Each combustion chamber 14 is formed at one end of a cylinder cavity 16, which may be formed directly in the engine body 12.
    The cylinder cavity 16 may be configured to receive a removable cylinder insert 18. The engine 10 also includes a cylinder head 20 that is attached to the engine body 12 to close the cylinder cavity 16. As will be seen in the following description, an improved cylinder head configuration is described which increases the strength of the cylinder head of an engine and in particular increases the peak combustion pressure (PCP) bearing capacity of the cylinder head of a machine.
    The engine 10 further includes a piston 22 positioned for reciprocation in each cylinder liner 18 associated with each combustion chamber 14. The piston 22 may be any type of piston as long as it includes the features identified below that are required to accomplish the present disclosure. For example, the piston 22 may be an articulated piston or a piston in one piece.
    An upper surface 24 of the piston 22 cooperates with the cylinder head 20 and the portion of the cylinder liner 18 extending between the cylinder head 20 and the piston 22 to define the combustion chamber 14. Although not specifically illustrated, the piston 22 is connected to a crankshaft of the engine 10 via a connecting rod 26 which causes the piston 22 to reciprocate along a straight path in the cylinder liner 18 as the crankshaft of the engine rotates rotates. FIG. FIG. 1 illustrates a piston 22 in a top dead center (TDC) position that is achieved when the crankshaft is positioned to move the piston 22 to the farthest position from the axis of rotation of the crankshaft. Conventionally, the piston 22 moves from the TDC position to a bottom dead center (TDC) position as it advances through the suction and piston strokes. For the purpose of this disclosure, the words "outside " and "outside" the direction away from the engine's crankshaft, and the words "inside " and "within" correspond to the direction toward the crankshaft of the engine or to the UT position of the piston 22.
    The engine 10 of the present disclosure may be a compression-ignition (diesel) four-stroke engine in which the fuel is injected directly into each combustion chamber 14. An intake passage 28 formed in the cylinder head 20 directs intake air through a pair of intake poppet valves 30 positioned in the cylinder head 20, only one of which is shown in FIG. 1, selectively into the combustion chamber 14. Similarly, an exhaust duct 32 formed in the cylinder head 20 deflects exhaust gases through a pair of exhaust poppet valves 34 positioned in the cylinder head 20, only one of which is shown in FIG. The opening and closing of the valves 30 and 34 may be accomplished by a mechanical cam or hydraulic actuation system (not shown) or other motive system in carefully controlled timing with the reciprocation of the piston 22 respectively.
    At the uppermost position shown in FIG. 1, the piston 22 has just completed the compression stroke to the top where the charge air that can enter the combustion chamber 14 from the intake ports 28 is compressed causing its temperature to be raised above the ignition temperature of the combustion engine.
    Stoffs of the machine rises. This position is usually considered to be the zero position at which the 720 degree turn begins, which is required for four complete strokes of the piston 22. The amount of charge air caused to enter the combustion chamber 14 and the other combustion chambers of the engine 10 may be increased by providing a pressure increase in the intake manifold (not shown) of the engine 10. This pressure increase can z. Example, by a turbocharger (not shown) are provided with a compressor which is driven by a turbine which is powered by the exhaust air of the engine 10 or by the crankshaft (not shown) of the machine 10 is driven.
    The engine 10 also includes a fuel injector 36 that is securely mounted in a central bore, component bore, or bore 38 of the fuel injector formed in the cylinder head 20 to inject a very high pressure fuel into the combustion chamber 14 when the piston 22 approaches the OT position or moves away from it. In other configurations, the central bore 38 may include a spark plug or other igniter instead of the fuel injector 36, which would then be positioned elsewhere in the cylinder head 20. The injector 36 includes an injector assembly 40 at the inner end. The injector 36 includes a plurality of injection ports 42 formed in the lower end of the nozzle assembly 40 to allow high pressure fuel out of a nozzle valve cavity of the injector 36 under very high pressure to flow into the combustion chamber 14 so that thorough mixing of the fuel with the high temperature compressed charge air in the combustion chamber 14 is initiated. It should be understood that the injector 36 may be any type of injector capable of injecting high pressure fuel into a combustion chamber 14 through a plurality of injection ports in the manner described below. For example, the injector 36 may be a closed nozzle injector or an open nozzle injector. Further, the injector 36 may include a mechanically actuated pressure member housed in the body of the injector to produce high pressure upon forward thrust of the pad assembly. Alternatively, the injector 36 may receive high pressure fuel from an upstream high pressure source, e.g. As a Pumplini-en nozzle system with one or more high-pressure pumps and / or a high pressure accumulator and / or a fuel rail. The injector 36 may include an electronically actuated injection control valve that supplies high pressure fuel to the nozzle valve assembly to open the injector assembly 40 or controls the discharge of high pressure fuel from the nozzle valve cavity to provide a pressure imbalance for a nozzle valve member of the injector assembly 40 produce. The pressure imbalance thereby causes the nozzle valve element to open and close to initiate an injection process. For example, the nozzle valve member may be a conventional spring-loaded, closed-nozzle valve member actuated by fuel pressure as disclosed in U.S. Patent No. 5,326,034, the entire contents of which are incorporated herein by reference. Injector 36 may be in the form of the injector disclosed in U.S. Patent No. 5,819,704, the entire contents of which are incorporated herein by reference.
    With reference to FIG. 2, a conventional cylinder head 20 includes a top plate 60, a center plate 62 and a bottom plate 64. The top plate 60, center plate 62 and bottom plate 64 cooperate with other features of the cylinder head 20 to form an upper coolant gallery 66 and a lower coolant gallery 68 , The upper coolant gallery 66 and the lower coolant gallery 68 contain a flowing cooling fluid for removing heat generated in the combustion chamber 14. A plurality of bores 70 formed in the cylinder head 20 receive bolts (not shown) to fix the cylinder head 20 to the engine body 12. A side wall portion 72 connects a bottom plate portion 64 to a center plate portion 62 and top plate portion 60 and forms part of the upper coolant gallery 66 and the lower coolant gallery 68. The injector or central bore 38 may have a wall portion 74 of an injector, component, or central bore ,
    In FIG. 3-5, a cylinder head 120a according to a first embodiment of the present disclosure is shown. As shown in FIG. 3, the cylinder head 120a includes a forehead, bottom or bottom plate 164a, a middle or middle plate 162, and a top or top plate 160. A side wall portion 172 connects the bottom plate 164a to the center plate 162 and the top Plate 160. As will be explained in more detail below, top plate 160, center plate 162, and side wall portion 172 are not directly related to the improvements of the present disclosure and have been shown in FIGS. 4-15, which describe embodiments of the present disclosure, are removed for the sake of clarity. Face plate 164a, center plate 162, top plate 160, side wall portion 172, and a central bore wall 174a cooperate to form an upper coolant gallery 166 and a lower coolant gallery 168.
    As best in FIG. 4 and 5, the cylinder head 120a further includes a plurality of longitudinally extending bolt bosses 44a extending from the bottom plate 164a of the cylinder head 120a. The screw bosses 44 are disposed at spaced angles about a central bore 38a and may be symmetrically disposed about the central bore 38a. The central bore 38a may include a fuel injector, a spark plug or other ignition device. Each screw boss 44a may be at approximately the same first radial distance from the central bore 38a, or each screw boss 44a may be at a different radial distance from the central bore 38a. The central bore 38a is thus positioned in a central or central area with respect to the screw bosses 44a, but this position may be uncentered or offset with respect to the midpoint of the pattern defined by the bosses 44a. Each screw boss 44a includes a bore 70 that receives a mounting bolt (not shown) for securing the cylinder head 120a to the machine body 12. The cylinder head 120a also includes a plurality of valve bosses 48a angularly arranged in a row about the central bore 38a. Like the screw bosses 44a, the valve bosses 48a may be symmetrically disposed about the central bore 38a. Each valve lug 48a includes a valve bore 50a. Each valve bore 50a adopts an intake poppet valve 30 or an exhaust poppet valve 34 for the
    Reciprocating motion in each valve bore 50a. Each valve lug 48a is at a second radial distance from the central bore 38a, which is less than all radial distances to each screw lug 44a. Each valve lug 48a may be at approximately the same radial distance from the central bore 38a or each lobe may be at a different second radial distance from the central bore 38a. Thus, central bore 38a is in the region bounded by the pattern formed by valve bosses 48a, but central bore 38a may be uncentered or offset relative to the midpoint of the pattern formed by valve bosses 48a. A cut extending longitudinally through the bottom plate 164a containing the central axis of the central bore 38a and extending radially outwardly from the central bore 38a to intersect the central axis of a valve lug 48a then extends radially outward by a screw boss 44a. The cut may include a single plane or include a plurality of planes as indicated by line 3-3 in FIG. 5 shown. For example, as shown in FIG. 3, shown along such a cut, each valve lug 48a is positioned radially between a central bore 38a and a screw boss 44a. Each screw boss 44a is consequently radially further from the central bore 38a than the respective valve boss 48a.
    From the bottom plate 164a, a plurality of suction passages 28a and a plurality of exhaust passages 32a extend. Each intake port 28a opens in the bottom plate 164a and extends away from the bottom plate 164a, bending to extend between a first pair of bolt bosses 44a. Each intake passage 28a thus forms an angle for the intake air flow, which angle may be approximately 90 degrees. The intake ports 28a are connected to an intake manifold of the engine (not shown). The exhaust ducts 32a also open in the bottom plate 164a and initially extend in a direction away from the bottom plate 164a, which may be parallel to the intake ducts 28a. The exhaust ducts 32a may then curve to extend between another or second pair of bolt bosses 44a in a direction generally opposite that in which the intake ducts 28a extend between the first pair of bolt bosses 44a. Each exhaust duct 32a forms an angle for the exhaust air flow, which angle may be approximately 90 degrees. The exhaust ducts 32a are connected to an exhaust manifold of the engine (not shown).
    A wall or rib 52 extends upwardly in the longitudinal direction or away from an upper wall portion 84a of a wall portion 84 of each intake duct 28a. The wall or rib 52 is connected to and extends upwardly along an inner boss portion 54 of a screw boss 44a to a boss portion or location 56 proximate an upper surface 45a of the screw boss 44a. In one embodiment, rib 52 extends to a location on screw boss 44a at least 50% of the distance from bottom plate 164a to top surface 45a. Preferably, rib 52 extends to a location on screw boss 44a at least 75% of the distance from bottom plate 164a to top surface 45a. The connection of rib 52 and lug 44a is at a first side or first end of rib 52. Wall or rib 52 also extends and connects to an inner lug portion 58 of a valve lug 48a at the base of each valve lug 48a. The connection of rib 52 and valve lug 48a is at a second end or a second side of rib 52. A valve lug 48a also extends from each wall portion 84 of each suction passage 28a. The rib 52 may extend upwardly along the valve lug 48a, but to allow adequate cooling fluid flow through the cylinder head 120a, the rib 52 preferably extends less than 50% of the distance from the base of the valve lobe 48a to the top of the valve lug 48a. Each rib 52 may also extend longitudinally from a bottom plate portion 59 of bottom plate 164a at some locations, as best shown in FIG. 5 can be seen. The extension of the ribs 52 from the bottom plate 164a is possible because the wall parts 84 and, as described below, a plurality of wall parts 85 of the exhaust air ducts 32a extend from the bottom plate 164a. However, the wall portions 84 and wall portions 85 may not extend all the way from the bottom panel 164a, at which ribs 52 may be positioned between each screw boss 44a and each valve boss 48a, leaving locations for the ribs 52 to extend from the bottom panel 164a stay.
    A wall or rib 52 also extends upwardly in the longitudinal direction from an upper wall portion 85a of a wall portion 85 of each exhaust duct 32a. Each wall or rib 52 is connected to and extends upwardly along an inner boss portion 54 of a screw boss 44a to a boss portion or location 56 proximate an upper surface 45a of the screw boss 44a. The connection of rib 52 and screw boss 44a is at a first side or first end of rib 52. In one embodiment, rib 52 extends to a location on screw boss 44a at least 50% of the distance from bottom plate 164a to top surface 45a. Preferably, rib 52 extends to a location on screw boss 44a at least 75% of the distance from bottom plate 164a to top surface 45a. The wall or rib 52 also extends and is connected to an inner boss portion 58 of a valve lug 48a at the base of each valve lug 48a. The connection of rib 52 and valve lug 48a is at a second end or side of the rib 52. A valve lug 48a also extends from each wall portion 85 of each exhaust duct 32a. The rib 52 may extend upwardly along the valve lug 48a, but to allow adequate cooling fluid flow through the cylinder head 120a, the rib 52 should extend less than 50% of the distance from the base of the valve lug 48a to the top of the valve lug 48a. Each rib 52 may also extend longitudinally away from a bottom plate portion 59 of bottom plate 164a at some locations, as best shown in FIG. 5 can be seen. The extension of the ribs 52 from the bottom plate 164a is possible because the wall parts 85 also extend from the bottom plate 164a, but can not extend all the way from the bottom plate 164a where ribs 52 are positioned between each screw boss 44a and each valve boss 48a may be so that locations for the ribs 52 remain for extending from the bottom plate 164a.
    Each rib 52 terminates in an upper or upper edge 53a. The upper or upper edge 53a may appear generally flat or as a straight line when viewed from one side of the rib 52, or normal to the longitudinal extent of the rib 52 extending from the bottom plate 164a. The upper or
    However, upper edge 53a may also form a slightly convex shape.
    It is less preferred that the upper or upper edge 53a forms a concave shape since such a shape is less suitable for loads transmitted from the bottom plate 164a, the walls 84 and the walls 85 to the screw bosses 44a. Unless otherwise noted, the shape of the ribs in the following embodiments should be similar to the shape of the ribs 52.
    The peak cylinder pressure capacity (PCP) of a conventional cylinder head similar to the cylinder head 20, which can be defined as the pressure applied to a cylinder head by an associated combustion chamber, was measured at 193 bar. The configuration of the first embodiment of the present disclosure achieves a peak cylinder pressure of 240 bar. The material of the conventional cylinder head 20 and the cylinder head 120a of the first embodiment, which achieves the aforementioned PCP, is gray iron. The dimensions that may be associated with the cylinder head 120a are as follows: a thickness of the bottom plate or end plate 164a of 17 millimeters; a thickness of the center plate 162 of 5 millimeters; a thickness of the top plate 160 of 15 millimeters; a distance from the center of the center plate 162 in the longitudinal direction to the center of the bottom plate 164a of 27.5 millimeters; a thickness of a side wall portion 172 of 13 millimeters and a minimum thickness of a wall 174 a of the central bore of 10 millimeters. The thickness of each rib 52 should be sufficient for casting. For example, the thickness of the ribs 52 may be in the range of 3 millimeters to 10 millimeters, for example 5 millimeters thick. The fins 52 may be thicker if desired, but should be configured to avoid interference with the function of the upper coolant gallery 166. The ribs 52 should be limited to the minimum thickness required to withstand the PCP formed; otherwise, more material than needed is used for the cylinder head 120a and becomes heavier than required. All of the aforementioned features that have a joint or joint should include a radius at the joint. The radius of the joint should be as large as possible. For example, an advantageous radius may be about 6 millimeters. Of course, such connecting or articulating radii could be much larger depending on the space available.
    The essential advantage of the ribs 52 is that they allow for removal of 75% of the material in the region of the upper water jacket or the upper coolant gallery 166, while maintaining or even increasing the PCP of the cylinder head 120a. This benefit is provided by limiting or decreasing the material not related to the strength of the cylinder head 120a while adding material to the locations and configurations described above. The ability to remove material by appropriately placing the ribs 52 while increasing the PCP was an unexpected result. In the first embodiment of the present disclosure, the result of adding the ribs 52 in conjunction with the above dimensions resulted in an increase of the structural efficiency of the cylinder head 120a over a conventional cylinder head by 15%, the structural efficiency being the stiffness to mass ratio is defined. As described above, the ribs 52 allow removal of material from the cylinder head 120a while increasing the PCP of the cylinder head 120a, resulting in improved structural efficiency. The structural rigidity of the cylinder head 120a, which is defined as the ability to resist deformation when a load is applied, has been increased by 32% over a conventional cylinder head. Changing the various dimensions given above in combination with the ribs 52 would result in improvements in PCP and structural efficiency that differ from the example just given.
    A second embodiment of a cylinder head of the present disclosure, indicated generally by 120b, is shown in FIG. 6 and 7 are shown. Features having the same number as in the previous embodiments, or features having the same number as in the previous embodiments and an appended letter, e.g. 44a, 44b, are similar to the previous embodiments and are described in this embodiment only to the extent necessary for clarity.
    The cylinder head 120b has a plurality of ribs 152 extending longitudinally from a face or bottom plate 164b on a bottom plate member 78 to mate with a central portion 76 of a central bore wall 174b, at an angle to the face plate 164b is formed. The part 78 is located on the bottom plate 164b between a wall portion 88 of a suction channel 28b and a wall portion 89 of an exhaust duct 32b. A portion of the ribs 152 may be connected or attached to an upper wall portion 88a of the wall portion 88 or an upper wall portion 89a of the wall portion 89 or both, depending on the location of an edge of the wall 88 where the wall 88 extends from the floor panel 164b , and the location of an edge of the wall 89 where the wall 89 extends from the bottom plate 164b. The ribs 152 provide additional PCP bearing capacity when used with the ribs 52. The ribs 152 may be used by themselves but with a lower PCP load than the ribs 52.
    A third embodiment of a cylinder head of the present disclosure, indicated generally by 120c, is shown in FIG. 8 and 9 are shown. Features having the same number as in the previous embodiments, or features having the same number as in the previous embodiments and an appended letter, e.g. 44a, 44b, are similar to the previous embodiments and are described in this embodiment only to the extent necessary for clarity.
    The cylinder head 120c has a plurality of ribs 252 extending in the longitudinal direction from an upper wall part 86a of a wall part 86 of an intake duct 28c or an upper wall part 87b of a wall part 87 of an exhaust duct 32c. The ribs 252 are connected to and extend longitudinally upwardly along a wall 174c of a central bore at a first end of the ribs 252 and are connected to and extend longitudinally upwardly along a boss portion 80 of a valve boss 48c a second end of the ribs 252. The attachment portion 80 is positioned on a side of the valve lug 48c which faces the wall 174c of the central bore. Each rib 252 extends to a point on the wall 174c of the central bore that is as far away from the bottom plate 164c in the longitudinal direction as possible while maintaining adequate cooling fluid flow through the cylinder head 120c. In one embodiment, each rib 252 extends to a point along the central bore wall 174c at least 50% of the distance from the bottom plate 164c to an upper surface 175 of the central bore wall 174c. Each rib 252 also extends to a point on the valve lug 48c that is as far away from the bottom plate 164c in the longitudinal direction as possible while maintaining adequate cooling fluid flow through the cylinder head 120c. In one embodiment, each rib 252 extends to a point along the valve lug 48c which is less in the longitudinal direction than the distance that the rib 252 extends along the wall 174c of the central bore.
    An upper edge 252a of the rib 252 forms an angle to the face plate 164c, with the connection of the upper edge 252a to the wall 174c of the central bore being farther from the bottom plate 164c in the longitudinal direction than the joining of the upper edge 252a to the wall portion 80 of FIG Valve attachment 48c.
    The upper edge 252a thus extends longitudinally downwardly toward the bottom panel 164c as the upper edge 252a extends from the central bore wall 174c to the valve boss 48c. The ribs 252 provide additional PCP bearing capability for the cylinder head 120c when used in conjunction with the ribs 52. The ribs 252 may also be used in conjunction with the ribs 152. While the ribs 252 may be used by themselves, the improvement in PCP is much less than the improvement in the PCP provided by the ribs 52 or the ribs 152, so that the ribs 252 are more effective when used with one or more other ribs, which are described in the other embodiments of this disclosure.
    A fourth embodiment of a cylinder head of the present disclosure, indicated generally by 120d, is shown in FIG. 10 and 11 are shown. Features having the same number as in the previous embodiments, or features having the same number as in the previous embodiments and an appended letter, e.g. 44a, 44b, are similar to the previous embodiments and are described in this embodiment only to the extent necessary for clarity.
    The cylinder head 120d has a plurality of ribs 352, each of which extends upwardly in the longitudinal direction from a bottom plate 164d and at a first end or a first side and a second end or a second
    Side of the ribs 352 is connected to facing wall parts of a pair of screw lugs 44d, wherein the screw lugs 44d are connected to the bottom plate 164d. An upper edge 352a of each rib 352 is connected to the screw boss 44d at a location in the longitudinal direction as far as possible from the bottom plate 164d while providing adequate cooling fluid flow through the cylinder head 120d. The upper edge 352a of each rib 352 extends at an angle from each screw boss 44d to the bottom plate 164d, at one location on each screw boss 44d at greater than 50% of the length in the longitudinal direction from the bottom plate 164d to an upper surface 91 of each screw boss 44d when viewed in a direction normal to the rib 352, a "V" shape is formed.
    A rib 352 extends in the longitudinal direction at least partially upwardly from one or more wall portions 92 of one or more intake passages 28d. At the point where this rib 352 is connected to the wall parts 92, the rib 352 is integrated or rounded into the wall part 92 of a respective intake duct 28d. A portion of the rib 352 may extend into an intake passage 28d to impart additional structural load to the rib 352. The extent to which the rib 352 extends into the intake ports 28d, however, must not interfere with adequate intake air flow through the intake ports 28d. A rib 352 extends in the longitudinal direction at least partially upwardly from one or more wall portions 93 of one or more exhaust ducts 32d. At the point where this rib 352 is connected to the wall parts 93, the rib 352 is integrated or rounded into the wall part 93 of a respective exhaust duct 32d to give the rib 352 additional structural load capacity. A portion of the rib 352 may extend into an exhaust duct 32d to provide additional structural support to the rib 352. However, the extent to which the rib 352 extends into the exhaust ducts 32d must not disturb an adequate exhaust air flow through the exhaust ducts 32d.
    The ribs 352 provide improved sealing of the cylinder head 120d with a machine body by increasing the robustness of the cylinder head 120d. The increased robustness of the cylinder head 120d improves the sealing effectiveness of a sealing mechanism located between the cylinder head 120d and an associated engine body. This sealing mechanism may include a head gasket located between the cylinder head 120d and the associated engine body. The ribs 352 can also improve the durability of an associated head gasket since bending of the head gasket along the seal joint is reduced by the presence of the ribs 352. The ribs 352 may be used with one or more of the previously described embodiments. By using the ribs 352 in combination with one or more ribs of the previously described embodiments, the sealing of the cylinder head 120d relative to an associated machine can be further improved.
    A fifth embodiment of a cylinder head of the present disclosure, indicated generally by 120e, is shown in FIG. 12 and 13 are shown. Features having the same number as in the previous embodiments, or features having the same number as in the previous embodiments and an appended letter, e.g. 44a, 44b, are similar to the previous embodiments and are described in this embodiment only to the extent necessary for clarity.
    The cylinder head 120e has ribs 452. A pair of ribs 452 extend longitudinally away from a bottom plate 164e, a wall portion 94 of an aspiration channel 28e, and / or a wall portion 95 of an exhaust channel 32e, depending upon the position of the pair of ribs 452. For example, a pair of ribs 452 extend longitudinally away from the bottom plate 164e and from an upper wall portion 94a of the wall portion 94, connect to a screw boss 44e, and extend to an upper inner portion 82 of the screw boss 44e. In another example, a pair of ribs 452 may extend longitudinally away from the bottom plate 164e and from an upper wall portion 95b of the wall portion 95, connect to the screw boss 44e, and extend to the upper inner portion 82 of the screw boss 44e. In one embodiment, a rib 452 extends to a location on the screw boss 44e at least 50% of the distance from the bottom plate 164e to the top surface 91. Preferably, the rib 452 extends to a location on the screw boss 44e at least 75% of the distance from the bottom plate Each pair of ribs 452 forms a "V" shape when viewed from a direction generally normal to the plane of bottom plate 164e. Each of the pair of ribs 452 lie on either side of a plane 96 that extends normal to and through the bottom plate 164e, through the center of a component or central bore 38e, and through the center of a screw boss 44e. A plane 97 that extends normal to the bottom plate 164e through the midpoint of two valve lugs 48e and does not intersect the central bore 38e extends through a rib 452 of two different pairs of fins. The angle of the "V" may be in the range of 20 degrees to 60 degrees, but more preferably in the range of 30 degrees to 50 degrees, and most preferably in the range of 35 degrees to 45 degrees.
    When the ribs 452 intersect the upper wall part 94a of the wall part 94 of the suction channels 28e and the upper wall part 95b of the wall part 95 of the exhaust ducts 32e, the ribs 452 become the wall parts 94a of the wall parts 94 of the suction channels 28e and the wall parts 95b of the wall parts 95 of the exhaust ducts 32e integrated or rounded. The ribs 452 may extend into the intake ports 28e and the exhaust ports 32e to increase the robustness of the cylinder head 120e. However, the ribs 452 should not interfere with the function of the intake ports 28e and the exhaust ports 32e. The improvement of the PCP by the ribs 452 is comparable to the PCP improvement by the ribs 52. As with the previous embodiments, the ribs 452 may be used in conjunction with the previously described embodiments to enhance the PCP of the cylinder head 120e.
    A sixth embodiment of a cylinder head of the present disclosure, indicated generally by 120f, is shown in FIG. 14 and 15 are shown. Features having the same number as in the previous embodiments, or features having the same number as in the previous embodiments and an appended letter, e.g. 44a, 44b, are similar to the previous embodiments and are described in this embodiment only to the extent necessary for clarity.
    The cylinder head 120f has ribs of all the above-described embodiments, and the numbering of the ribs of the above-described embodiments is maintained for the sake of simplicity and clarity, although the use of all the ribs of the previous embodiments may have slight modifications of the ribs of the foregoing embodiments, to make it possible to place some ribs next to each other. The use of all embodiments enables the largest possible PCP. However, the use of all of the ribs can result in a massive restriction of the upper gallery of coolant and the lower gallery of coolant, which should be considered regardless of which combination of previously described embodiments is used. While various embodiments of the disclosure have been shown and described, it is to be understood that these embodiments are not limited thereto. The embodiments may be changed, modified and further applied by those skilled in the art. Accordingly, these embodiments are not limited to the details shown and described above, but include all such changes and modifications.
    权利要求:
    Claims (20)
    [1]
    Claims 1. A cylinder head for an internal combustion engine, the cylinder head comprising: a bottom plate; a component bore having a wall extending longitudinally from the bottom plate; a screw boss extending in the longitudinal direction from the bottom plate and positioned at a first radial distance from the component bore; a valve lug positioned at a second radial distance from the component bore, the second radial distance being less than the first radial distance; and a first rib that extends upwardly in the longitudinal direction from the bottom plate, connects to the screw boss at a first rib end, and extends to a location on an upper part of the screw boss.
    [2]
    2. A cylinder head according to claim 1, wherein the first rib extends in the longitudinal direction of the bottom plate upwardly to connect at a second end of the first rib with a location on a lower part of the valve lug.
    [3]
    3. The cylinder head of claim 1, further comprising an intake passage having an intake passage wall, and an exhaust passage having an exhaust passage passage wall, the first rib extending upward from one of the intake passage wall and the exhaust passage passage wall.
    [4]
    4. The cylinder head according to claim 1, further comprising a second rib extending upwardly in the longitudinal direction from the bottom plate to connect with a location on an upper part of the screw boss.
    [5]
    5. The cylinder head of claim 1, further comprising a pair of bolt bosses positioned at a spaced angle about the component bore with at least one of the bolt bosses positioned at the first radial distance and a third rib connecting the pair of bolt bosses.
    [6]
    A cylinder head according to claim 5, wherein the third rib is in the form of a "V " when considered normal to the third rib, the bottom of the "V " positioned closer to the bottom plate than the top of the "V".
    [7]
    7. The cylinder head of claim 1, further comprising a plurality of bolt bosses and a plurality of ribs, wherein the plurality of ribs connect each bolt boss of the plurality of bolt bosses to two other bolt bosses.
    [8]
    8. Cylinder head according to claim 1, wherein the peak pressure capacity of the cylinder head is 240 bar.
    [9]
    9. Cylinder head according to claim 1, wherein the first rib extends over at least 50% of the distance from the bottom plate to an upper surface of the screw lug.
    [10]
    10. Cylinder head according to claim 9, wherein the first rib extends over at least 75% of the distance from the bottom plate to the upper surface of the screw lug.
    [11]
    11. A cylinder head for an internal combustion engine, the cylinder head comprising: a bottom plate; a component bore having a component bore wall extending longitudinally from the bottom plate; a screw boss extending in the longitudinal direction from the bottom plate and positioned at a first radial distance from the component bore; a valve lug positioned at a second radial distance from the component bore, the second radial distance being less than the first radial distance; an intake passage formed in the cylinder head, the intake passage including an intake passage wall; an exhaust duct formed in the cylinder head, the exhaust duct containing an exhaust duct wall; and a first rib that extends upwardly in the longitudinal direction from one of the intake passage wall and the exhaust passage passage wall to communicate with a location on the component bore wall.
    [12]
    12. The cylinder head of claim 11, wherein the first rib extends longitudinally from one of the intake passage wall and the exhaust passageway wall to communicate with a location at a lower portion of the valve boss.
    [13]
    13. The cylinder head of claim 11, further comprising a second rib extending upwardly from one of the intake passage wall and the exhaust passageway wall for communicating with a location on an upper portion of the screw boss and a location on a lower portion of the valve boss connect.
    [14]
    14. Cylinder head according to claim 13, wherein the peak pressure capacity of the cylinder head is 240 bar.
    [15]
    15. The cylinder head according to claim 11, further comprising a plurality of screw bosses and a plurality of ribs, each of the plurality of ribs extending in the longitudinal direction of at least one of the bottom plate, the suction channel wall, and the exhaust duct wall to communicate with two of the plurality to connect screw approaches.
    [16]
    16. A cylinder head for an internal combustion engine, the cylinder head comprising: a bottom plate; at least one intake passage including an intake passage wall; at least one exhaust duct containing an exhaust duct wall; a component bore including a component bore wall and a component bore center extending in the longitudinal direction from the bottom plate; a plurality of screw lugs, each screw lug including a helical lug center extending longitudinally from the bottom plate, each of the plurality of lug extensions positioned at a spaced angle about the component bore at one or more first radial distances from the component bore; a plurality of valve lobes, each valve lug having a valve lobe center and extending longitudinally from an intake passage wall or exhaust passage wall, each of the plurality of valve lobes being positioned at a spaced angle about the component bore, at one or more second radial distances, wherein the second radial distances are less than the first radial distances; and a plurality of ribs extending in the longitudinal direction of at least one of the group consisting of the bottom plate, the suction channel wall, and the exhaust duct wall, the plurality of ribs being connected to at least one of the plurality of screw bosses; consists of the plurality of valve lugs and the component bore wall connects.
    [17]
    17. The cylinder head according to claim 16, wherein the plurality of ribs extend upward in the longitudinal direction from the bottom plate so as to connect with an upper part of the component bore.
    [18]
    18. Cylinder head according to claim 16, wherein each screw lug is connected by ribs with two other screw lugs.
    [19]
    19. Cylinder head according to claim 16, wherein the peak pressure capacity of the cylinder head is 240 bar.
    [20]
    20. A cylinder head according to claim 16, including a pair of ribs extending in the longitudinal direction of at least one of the group consisting of the bottom plate, the intake duct wall and the exhaust duct wall to connect to one of the plurality of bolt bosses, each one Ridge of the pair of ribs is positioned on each side of a plane which extends normal to the bottom plate and from the center of the component bore to the screw attachment center of the one of the plurality of screw lugs.
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    同族专利:
    公开号 | 公开日
    CN107917011A|2018-04-17|
    CN104884778B|2017-12-05|
    US9470177B2|2016-10-18|
    CN104884778A|2015-09-02|
    AT514866B1|2016-07-15|
    CN107917011B|2020-10-30|
    AT514866A5|2015-07-15|
    US8950374B2|2015-02-10|
    WO2014004547A1|2014-01-03|
    BR112014032328B1|2022-01-25|
    US20130340703A1|2013-12-26|
    BR112014032328A2|2017-06-27|
    US20150167581A1|2015-06-18|
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    法律状态:
    优先权:
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    US13/531,932|US8950374B2|2012-06-25|2012-06-25|Cylinder head for internal combustion engine|
    PCT/US2013/047672|WO2014004547A1|2012-06-25|2013-06-25|Cylinder head for internal combustion engine|
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