Patent Publication Number: US-9850847-B2

Title: Piston for internal combustion engine

Description:
TECHNICAL FIELD 
     An aspect of the present invention relates to a piston for an internal combustion engine. 
     BACKGROUND ART 
     As a technical literature on a conventional piston for an internal combustion engine, Patent Literature 1 is known. This literature discloses a piston having a combustion chamber that is formed at a piston top surface and an oil gallery that is formed so as to surround the combustion chamber. 
     CITATION LIST 
     Patent Literature 
     [Patent Literature 1] Japanese Patent Application Laid Open Publication No. 2011-17263 
     SUMMARY OF INVENTION 
     Technical Problem 
     In recent years, internal combustion engines have been downsized, and high pressure injection of fuel is used to obtain sufficient output while achieving the downsizing. However, when the high pressure injection of fuel raises the combustion temperature higher, the temperature on the side of a piston top surface and the temperature on the side of a piston skirt may become significantly different, whereby deformation of the piston due to the temperature difference may occur. When a piston ring groove is deformed in the piston, the resulting malfunction of the piston ring may problematically cause seizing or reduced sealing performance. 
     In view of this, an aspect of the present invention aims to provide a piston for an internal combustion engine that makes it possible to prevent deformation of the piston due to temperature difference. 
     Solution to Problem 
     To solve the above-described problems, a piston according to an aspect of the present invention includes a combustion chamber that is formed at a piston top surface and an oil gallery that is formed so as to surround the combustion chamber. Wall thickness from a sliding side surface of the piston to the oil gallery is set greater on a piston skirt side than on a piston top surface side. 
     In the piston according to an aspect of the present invention for an internal combustion engine, the wall thickness from the sliding side surface of the piston to the oil gallery is set to be greater on the piston skirt side than on the piston top surface side. This setting makes it possible to prevent the piston skirt side in which temperature rise due to combustion is small from being excessively cooled while the piston top surface side in which temperature rise due to combustion is large can be sufficiently cooled by engine oil flowing in the oil gallery. Accordingly, the temperature difference between the piston top surface side and the piston skirt side can be reduced, whereby deformation of the piston can be prevented. 
     In the piston according to an aspect of the present invention for an internal combustion engine, the oil gallery may have an outer inclined surface that approaches closer to a piston central axis the closer it is to the piston skirt side with respect to the piston top surface side. 
     In the piston according to an aspect of the present invention for an internal combustion engine, an inner side surface of the oil gallery may be formed along a side wall of the combustion chamber. 
     In the piston according to an aspect of the present invention for an internal combustion engine, the side wall of the combustion chamber may have a lip portion that protrudes inside the combustion chamber, and the inner side surface of the oil gallery may have an inner enlarged surface that extends toward the lip portion. 
     Advantageous Effects of Invention 
     A piston according to an aspect of the present invention for an internal combustion engine makes it possible to prevent deformation of the piston due to temperature difference. 
    
    
     
       BRIEF DESCRIPTION OF DRAWINGS 
         FIG. 1  is a sectional view illustrating a piston according to a first embodiment. 
         FIG. 2  is a graph illustrating an example of temperature difference in the piston versus (B−A)/L. 
         FIG. 3  is a sectional view illustrating a piston according to a second embodiment. 
         FIG. 4  is a sectional view illustrating a piston according to a third embodiment. 
         FIG. 5  is a sectional view illustrating a piston according to a fourth embodiment. 
         FIG. 6  is a sectional view illustrating a piston according to a fifth embodiment. 
     
    
    
     DESCRIPTION OF EMBODIMENTS 
     Preferred embodiments of the present invention will be described hereinafter in detail with reference to the drawings. 
     First Embodiment 
     As depicted in  FIG. 1 , a piston  1  according to a first embodiment is provided to an internal combustion engine such as a diesel engine of a vehicle, and reciprocates inside a cylinder S in an extending direction of a central axis (piston central axis) C. The piston  1  is connected to a crankshaft of the internal combustion engine with a connecting rod, and the reciprocating motion energy of the piston  1  is converted to the rotational energy of the crankshaft with the connecting rod. Illustration of the connecting rod and the crankshaft is omitted herein. 
     The piston  1  includes a piston top surface  2 , a sliding side surface  3 , and a piston skirt  4 . It is assumed in the following description that, in the piston  1 , the side of the piston top surface  2  is the upper side and the side of the piston skirt  4  is the lower side. 
     The piston top surface  2  is a piston upper-end surface that forms a space E for combustion in the cylinder S. When the internal combustion engine is driving, fuel injected by a fuel injector  9  is burned in the space E, whereby the piston top surface  2  is heated to a high temperature. The piston  1  has a combustion chamber  5 . 
     The sliding side surface  3  is a piston side surface that slides over the inner side surface of the cylinder S. On the sliding side surface  3 , piston ring grooves  3   a  to  3   c  are formed into which piston rings  8 A to  8 C are fitted, respectively. 
     The first piston ring  8 A positioned closest to the side of the piston top surface  2  is arranged in the first piston ring groove  3   a . The second piston ring  8 B positioned between the first piston ring groove  3   a  and the third piston ring groove  3   c  is arranged in the second piston ring groove  3   b . The third piston ring  8 C positioned closest to the side of the piston skirt  4  is arranged in the third piston ring groove  3   c.    
     The piston skirt  4  is a skirt-like portion that is formed so as to extend downward along the sliding side surface  3 . In an inner space  7  of this piston skirt  4 , the small end of the connecting rod is arranged. 
     The combustion chamber  5  is a space that is part of the space E in which fuel mixed with air burns and is a space formed on the side of the piston  1 . The combustion chamber  5  has a bottom surface  5   a  and a side wall  5   b . The bottom surface  5   a  is formed so as to be more inclined upward in a position closer to the center (central axis C), for example. This combustion chamber  5  is a reentrant-type combustion chamber in which the side wall  5   b  is inclined toward the inside (side of the central axis C). On the upper side of the combustion chamber  5 , a lip portion Lp that is a portion of the side wall  5   b  most protruding inward is formed. Herein, the combustion chamber  5  is not limited to the reentrant-type, and may be a toroidal-type combustion chamber in which the side wall  5   b  is formed vertically along the central axis C, or may be a bathtub-type combustion chamber in which the side wall  5   b  is formed vertically and the bottom surface  5   a  is formed planarly. 
     The piston  1  also has an oil gallery  6  that is formed in a ring-shaped manner so as to surround the combustion chamber  5  (around the central axis C). The oil gallery  6  is a hollow portion that is formed inside the piston  1 , and engine oil flows therein through an oil jet hole (not depicted), thereby cooling the piston  1 . 
     The cross sectional shape of this oil gallery  6  along the central axis C (cross sectional shape depicted in  FIG. 1 ) is substantially oval. Specifically, the oil gallery  6  has an outer inclined surface  6   a , an inner enlarged surface  6   b , and an inner inclined surface  6   c.    
     The outer inclined surface  6   a  is an outer side surface (side surface away from the combustion chamber  5 ) of the oil gallery  6 . The outer inclined surface  6   a  is formed as a flat surface that approaches closer to the central axis C the closer it is to piston skirt  4  side with respect to piston top surface  2  side. In other words, the outer inclined surface  6   a  inclines away from the sliding side surface  3  toward the lower side. The outer inclined surface  6   a  is formed in the oil gallery  6  on the side of the sliding side surface  3  (away from the central axis C) of the piston  1 . Alternatively, the outer inclined surface  6   a  may be a curved surface, or may include both of a flat surface and a curved surface. 
     The inner enlarged surface  6   b  and the inner inclined surface  6   c  form an inner side surface (side surface closer to the combustion chamber  5 ) of the oil gallery  6 , and are formed along the side wall  5   b  of the combustion chamber  5 . In other words, the inner side surface of the oil gallery  6  is formed along the side wall  5   b  of the combustion chamber  5 . 
     The inner enlarged surface  6   b  is formed on the upper side of the oil gallery  6  (on the side of the piston top surface  2 ). The inner enlarged surface  6   b  is a portion of the inner side surface for enlarging the oil gallery  6  toward the side of the combustion chamber  5  (closer to the central axis C). In other words, inner enlarged surface  6   b  is formed extending toward the side of the combustion chamber  5 . Specifically, the inner enlarged surface  6   b  is formed so as to extend toward the lip portion Lp that protrudes most toward the central axis C in the side wall  5   b  of the combustion chamber  5 . The inner enlarged surface  6   b  is formed so that wall thickness between the inner side surface of the oil gallery  6  and the side wall  5   b  of the combustion chamber  5  is more uniform than the wall thickness without the inner enlarged surface  6   b . The wall thickness between the inner side surface of the oil gallery  6  and the side wall  5   b  of the combustion chamber  5  is sufficient in thickness to ensure strength. 
     The inner inclined surface  6   c  is a flat surface that is formed on the lower side (side of the piston skirt  4 ) of the inner side surface of the oil gallery  6  and is inclined substantially parallel to the outer inclined surface  6   a . The inner inclined surface  6   c  is formed being inclined along the side wall  5   b  of the combustion chamber  5 . 
     In this oil gallery  6 , assuming that the length thereof in the extending direction of the central axis C is denoted by L, and the upper effective wall thickness and the lower effective wall thickness in the wall thickness from the sliding side surface  3  of the piston  1  to the oil gallery  6  in the direction orthogonal to the central axis C are respectively denoted by A and B, the oil gallery  6  satisfies the following expressions (1) and (2). In the expression (2), H denotes the depth of the combustion chamber  5  depicted in  FIG. 1  (distance from the piston top surface  2  to the bottommost surface of the combustion chamber  5 ). 
     
       
         
           
             
               
                 
                   [ 
                   
                     Mathematical 
                     ⁢ 
                     
                         
                     
                     ⁢ 
                     1 
                   
                   ] 
                 
               
               
                 
                     
                 
               
             
             
               
                 
                   
                     
                       B 
                       - 
                       A 
                     
                     L 
                   
                   ≥ 
                   0.05 
                 
               
               
                 
                   ( 
                   1 
                   ) 
                 
               
             
             
               
                 
                   L 
                   ≥ 
                   
                     0.65 
                     ⁢ 
                     H 
                   
                 
               
               
                 
                   ( 
                   2 
                   ) 
                 
               
             
           
         
       
     
     The upper effective wall thickness A in the present embodiment means the smallest wall thickness from the sliding side surface  3  of the piston  1  to the oil gallery  6  on the side of the piston top surface  2 . The lower effective wall thickness B in the present embodiment means the wall thickness from the sliding side surface  3  of the piston  1  to the intersection point W. In the cross section depicted in  FIG. 1 , the intersection point W denotes the point of intersection between the virtual line V 1  that passes through the lower end of the oil gallery  6  and is orthogonal to the central axis C (that is the same as lower one of the dimension lines indicated with L in  FIG. 1 ) and the extended line V 2  extending along the outer inclined surface  6   a.    
       FIG. 2  is a graph illustrating an example of temperature difference in the piston  1  versus (B−A)/L described above. The vertical axis in  FIG. 2  represents temperature difference between the vicinity of the first piston ring  8 A on the side of the piston top surface  2  and the vicinity of the third piston ring  8 C on the side of the piston skirt  4 . The horizontal axis in  FIG. 2  represents (B−A)/L. 
     As depicted in  FIG. 2 , the temperature difference in the piston  1  decreases as the value of (B−A)/L increases. In the present embodiment, to control deformation of the piston  1  due to the temperature difference at or below a reference value, (B−A)/Lq is set to be 0.05 or more. The range in which (B−A)/Lq is 0.05 or more is indicated by the arrow P.  FIG. 2  is merely one example illustrating temperature difference in the piston  1  versus (B−A)/L, and the present invention is not limited to the description above. 
     In the piston  1  for an internal combustion engine according to the above-described first embodiment, the wall thickness from the sliding side surface  3  to the oil gallery  6  is set greater on the side of the piston skirt  4  than on the side of the piston top surface  2 . This setting makes it possible to prevent the side of the piston skirt  4  in which temperature rise due to combustion is small from being excessively cooled while the side of the piston top surface  2  in which temperature rise due to combustion is large can be sufficiently cooled by oil flowing in the oil gallery  6 . Accordingly, the temperature difference between the side of the piston top surface  2  and the side of the piston skirt  4  can be reduced, whereby deformation of the piston  1  can be prevented. Thus, this piston  1  makes it possible to prevent seizing or reduced sealing performance due to malfunction of the piston rings  8 A to  8 C resulting from deformation of the piston ring grooves  3   a  to  3   c . Thus, reliability and sealing performance of the piston rings  8 A to  8 C can be improved, whereby the blowby amount can be reduced. 
     In this piston  1 , the oil gallery  6  has the outer inclined surface  6   a  that approaches closer to the central axis C the closer it is to piston skirt  4  side with respect to piston top surface  2  side. This shape of the oil gallery  6 , not the piston shape, enables the wall thickness from the sliding side surface  3  to the oil gallery  6  in the piston  1  to be set greater toward the lower side, making it possible to prevent the side of the piston skirt  4  from being excessively cooled by the oil flowing in the oil gallery  6 . 
     As depicted in  FIG. 1 , in the piston  1 , the distance H L  from the piston top surface  2  to the lower end of the oil gallery  6  is longer than the distance Hr from the piston top surface  2  to the second piston ring groove  3   b  (i.e., to the second piston ring  8 B). Specifically, the oil gallery  6  is formed so as to extend perpendicularly from the upper side of the first piston ring groove  3   a  to the vicinity of the third piston ring groove  3   c  beyond the second piston ring groove  3   b . This makes it possible to suitably obtain the cooling effect of the oil flowing in the oil gallery  6  even in the second piston ring groove  3   b  and the third piston ring groove  3   c.    
     Furthermore, in this piston  1 , the inner enlarged surface  6   b  that extends toward the lip portion Lp at the combustion chamber  5  is formed in the oil gallery  6 , whereby the lip portion Lp at the combustion chamber  5  can be suitably cooled. Specifically, in the reentrant-type combustion chamber  5 , flows of air and fuel mixed with the air are suitably tuned by providing the lip portion Lp, whereby the combustion efficiency in the combustion chamber  5  can be increased. However, the lip portion Lp most protruding in the side wall  5   b  of the combustion chamber  5  is likely to be affected by heat concentration. In the piston  1  according to the present embodiment, the oil gallery  6  has the inner enlarged surface  6   b  that is recessed toward the lip portion Lp. Accordingly, the lip portion Lp can be suitably cooled by the oil flowing in the oil gallery  6 . 
     Furthermore, in this piston  1 , because the inner side surface (the inner enlarged surface  6   b  and the inner inclined surface  6   c ) of the oil gallery  6  is formed along the side wall  5   b  of the combustion chamber  5 , the wall thickness of the piston  1  between the side wall  5   b  of the combustion chamber  5  and the inner side surface of the oil gallery  6  can be made more uniform. This makes it possible to prevent temperature distribution in the side wall  5   b  from becoming non-uniform by cooling with oil as contrasted with when the wall thickness between the inner side surface of the oil gallery  6  and the side wall  5   b  of the combustion chamber  5  is not uniform. Thus, in this piston  1 , it is possible to prevent deformation of the piston  1  due to temperature difference that is caused by non-uniform temperature distribution in the piston  1  resulting from non-uniform air temperature distribution in the combustion chamber  5  originating from non-uniform temperature distribution in the side wall  5   b . It is also possible to prevent reduction of combustion efficiency in the combustion chamber  5 . 
     Second to Fourth Embodiments 
     The following describes second to fourth embodiments with reference to  FIG. 3  to  FIG. 5 . Pistons  10 ,  20 , and  30  according to the second to the fourth embodiments are different only in shape of oil galleries from the piston  1  according to the first embodiment. Hereinafter, the same reference numerals are given to the same or equivalent components in the respective drawings, and repetitive description will not be made. 
     The oil gallery  11  of the piston  10  according to the second embodiment depicted in  FIG. 3  has an oval cross sectional shape (cross sectional shape along the central axis C). The oil gallery  11  has an outer inclined surface  11   a  in the same manner as the first embodiment, but does not have a portion like the inner enlarged surface  6   b . The inner side surface of the oil gallery  11  is an inclined surface along the outer inclined surface  11   a.    
     The oil gallery  11  satisfies the above-described expressions (1) and (2), also in terms of the length L in the extending direction of the central axis C, and the upper effective wall thickness A and the lower effective wall thickness B in the wall thickness from the sliding side surface  3  of the piston  1  to the oil gallery  11 , in the same manner as the first embodiment. 
     The second embodiment is the same as the first embodiment also in that the distance H L  from the piston top surface  2  to the lower end of the oil gallery  11  is longer than the distance Hr from the piston top surface  2  to the second piston ring groove  3   b  (i.e., to second piston ring  8 B). The third and the fourth embodiments are also the same as the first embodiment in that the length L in the extending direction of the central axis C, the upper effective wall thickness A, and the lower effective wall thickness B satisfy the above-described expressions (1) and (2) and in that the distance H L  is longer than the distance Hr. 
     The following describes the piston  20  according to the third embodiment depicted in  FIG. 4 . As depicted in  FIG. 4 , an oil gallery  21  of the piston  20  according to the third embodiment has a cross sectional shape (cross sectional shape along the central axis C) in which the lower side of an oval extending in the extending direction of the central axis C bends slightly toward the central axis C. 
     This oil gallery  21  also has an outer vertical surface  21   a  on the upper side and an outer inclined surface  21   b  on the lower side. The outer vertical surface  21   a  and the outer inclined surface  21   b  form the outer side surface of the oil gallery  21 . The outer vertical surface  21   a  and the outer inclined surface  21   b  are formed in the oil gallery  21  on the side of the sliding side surface  3  (away from the central axis C). The outer vertical surface  21   a  is a flat surface that extends in the extending direction of the central axis C, and the outer inclined surface  21   b  is a flat surface that inclines closer to the central axis C toward the lower side. Alternatively, the outer vertical surface  21   a  and the outer inclined surface  21   b  may be curved surfaces, or may include a flat surface and a curved surface. The oil gallery  21  also has an inner vertical surface  21   c  on the upper side and an inner inclined surface  21   d  on the lower side. The inner vertical surface  21   c  and the inner inclined surface  21   d  form the inner side surface of the oil gallery  21 . 
     The following describes the piston  30  according to the fourth embodiment depicted in  FIG. 5 . As depicted in  FIG. 5 , an oil gallery  31  of the piston  30  according to the fourth embodiment has a cross sectional shape (cross sectional shape along the central axis C) in which the upper side of an oval extending in the extending direction of the central axis C bends slightly toward the side of the sliding side surface  3  (away from the central axis C). 
     This oil gallery  31  also has an outer inclined surface  31   a  on the upper side and an outer vertical surface  31   b  on the lower side. The outer inclined surface  31   a  and the outer vertical surface  31   b  are formed in the oil gallery  31  on the side of the sliding side surface  3  (away from the central axis C). The outer inclined surface  31   a  is a flat surface inclines closer to the central axis C toward the lower side, and the outer vertical surface  31   b  is a flat surface that extends in the extending direction of the central axis C. Alternatively, the outer inclined surface  31   a  and the outer vertical surface  31   b  may be curved surfaces, or may include a flat surface and a curved surface. 
     In the above-described pistons  10 ,  20 , and  30  according to the second to the fourth embodiments, the wall thicknesses from the sliding side surface  3  to the oil galleries  11 ,  21 , and  31  are also set greater on the side of the piston skirt  4  than on the side of the piston top surface  2 . Thus, the same effect as in the piston  1  according to the first embodiment can be obtained. 
     Fifth Embodiment 
     The following describes a fifth embodiment with reference to  FIG. 6 . A piston  40  according to the fifth embodiment is different only in shape of the combustion chamber from the piston  20  according to the third embodiment. 
     The combustion chamber  41  of the piston  40  according to the fifth embodiment depicted in  FIG. 6  is what is called a bathtub-type combustion chamber. The combustion chamber  41  has a bottom surface (bottom surface substantially parallel to the piston top surface  2 )  41   a  orthogonal to the central axis C and a side wall (side wall substantially orthogonal to the piston top surface  2 )  41   b  extending along the central axis C. Alternatively, the bottom surface  41   a  may be formed so as to be more inclined upward in a position closer to the center (central axis C), for example. In this combustion chamber  41 , the upper end of the opening of the combustion chamber  41  formed at the piston top surface  2  corresponds to the lip portion Lp. 
     In this piston  40 , the inner vertical surface  21   c  of the oil gallery  21  is formed along the side wall  41   b  of the combustion chamber  41 . Furthermore, the inner inclined surface  21   d  of the oil gallery  21  is inclined along a connection portion between the bottom surface  41   a  and the side wall  41   b  of the combustion chamber  41 . 
     As the inner vertical surface  21   c  of the oil gallery  21  is formed along the side wall  41   b  of the combustion chamber  41  also in the above-described piston  40  according to the fifth embodiment, the wall thickness of the piston  40  between the side wall  41   b  of the combustion chamber  41  and the inner side surface of the oil gallery  21  can be made more uniform. It is thus possible to avoid non-uniformity in the temperature distribution in the side wall  41   b  due to cooling of the oil, in comparison to when the thickness between the inner side wall of oil gallery  21  and the side wall  41   b  of the combustion chamber  41  is not uniform. Therefore, from this piston  40 , in addition to making it possible to prevent the deformation of the piston  40  from the temperature difference, as caused by the temperature distribution of air in the combustion chamber  41  becoming non-uniform due to the temperature distribution in the side wall  41   b  becoming non-uniform, along with non-uniformity also in the temperature distribution of the piston  40 , it is also possible to prevent the reduction of combustion efficiency in the combustion chamber  41 . 
     Hereinbefore, preferred embodiments of the present invention have been described, but the present invention is not limited to the above-described embodiments. 
     For example, an aspect of the present invention may be applied to pistons for gasoline engines instead of the above-described pistons exclusively for diesel engines. Furthermore, the shapes of the oil galleries are not limited to those described above, and any shape may be used as long as the wall thickness from the sliding side surface of the piston to the oil gallery may be set greater on the side of the piston skirt than on the side of the piston top surface. 
     Furthermore, the oil galleries do not have to extend to below the position of the second piston ring groove, and the lower ends of the oil galleries may be positioned above the second piston ring groove. Furthermore, the outer inclined surfaces of the oil galleries do not have to be inclined smoothly, and may have steps, for example. Furthermore, in the first embodiment, if deformation of the piston  1  due to temperature difference does not occur that is caused by non-uniform temperature distribution in the piston  1  resulting from non-uniform temperature distribution in the side wall  5   b , the inner enlarged surface  6   b  may be formed so that the wall thickness between the inner side surface of the oil gallery  6  and the side wall  5   b  of the combustion chamber  5  is not completely uniform but more uniform than the wall thickness without the inner enlarged surface  6   b.    
     INDUSTRIAL APPLICABILITY 
     According to an aspect of the present invention, a piston for an internal combustion engine can be provided that makes it possible to prevent deformation of the piston due to temperature difference. 
     REFERENCE SIGNS LIST 
       1  . . . piston,  2  . . . piston top surface,  3  . . . sliding side surface,  3   a  . . . first piston ring groove,  3   b  . . . second piston ring groove,  3   c  . . . third piston ring groove,  4  . . . piston skirt,  5 ,  41  . . . combustion chamber,  5   a ,  41   a  . . . bottom surface,  5   b ,  41   b  . . . side wall,  6   a  . . . outer inclined surface,  6   b  . . . inner enlarged surface,  6   c  . . . inner inclined surface,  7  . . . inner space,  8 A . . . piston ring,  8 B . . . piston ring,  8 C . . . piston ring,  9  . . . fuel injector,  1 ,  10 ,  20 ,  30 ,  40  . . . piston,  6 ,  11 ,  21 ,  31  . . . oil gallery,  11   a ,  21   b ,  31   a  . . . outer inclined surface,  21   a ,  31   b  . . . outer vertical surface,  21   c  . . . inner vertical surface,  21   d  . . . inner inclined surface, A . . . upper effective wall thickness, B . . . lower effective wall thickness, C . . . central axis (piston central axis), E . . . space, S . . . cylinder, V 1  . . . virtual line, V 2  . . . extended line, W . . . intersection point.