JP2007002698A - 6-cylinder engine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a 6-cylinder engine, capable of compacting a body size, and restricting vibration. <P>SOLUTION: Both groups of cylinders are disposed in parallel or at a bank angle of less than 15° between the both groups. Crank pins for one crankshaft 4a corresponding to one group of cylinders are disposed at every 120° in order of first cylinder, third cylinder, and fifth cylinder in such a way that when the crank pin for the first cylinder is at the upper dead center, the crank pin for sixth cylinder on the other crankshaft 4b corresponding to the other cylinder group is at the upper dead center. Further, the crank pins for the other crankshaft are disposed at every 120° in order of sixth cylinder, fourth cylinder, and second cylinder. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a six-cylinder engine that includes two crankshafts corresponding to two banks and outputs the rotational force of both crankshafts from one output shaft.

  As a 6-cylinder engine, an in-line type, a horizontally opposed type, a V type, and the like are practically used or proposed. Further, in a 6-cylinder engine, it is common to cause each cylinder to explode at equal intervals in order to reduce vibration caused by the generation of vibration force by its components.

  An in-line type and horizontally opposed type 6-cylinder engine is advantageous in terms of vibration, but has a large engine size such as being longer in the axial direction of the crankshaft. On the other hand, the V-type 6-cylinder engine is smaller in size but inferior to the former in terms of vibration.

On the other hand, in a 2- or 4-cylinder engine, an engine having two crankshafts corresponding to two banks and configured to output the rotational force of both crankshafts from one output shaft has been proposed. (For example, refer to Patent Documents 1 to 5.)
JP-A-62-70627 JP-A-9-287476 JP-A-63-285229 JP 2003-120317 A JP 2003-83105 A Japanese Patent Laid-Open No. 54-140006

  However, in a 6-cylinder engine, an engine having two crankshafts corresponding to two banks and configured to output the rotational force of both crankshafts from one output shaft has not yet been proposed.

  The present invention has been made in view of the above-described problems, and an object of the present invention is to propose a 6-cylinder engine that can reduce the physique and suppress vibration.

  In order to achieve the above object, the six-cylinder engine according to the present invention has two cylinder groups each having three cylinders as one cylinder group, and a crankshaft so as to correspond to the two cylinder groups. A six-cylinder engine that includes two and outputs the rotational force of both crankshafts from a single output shaft, wherein both cylinder groups are arranged in parallel or have a bank angle of less than 15 °. Cylinders belonging to one cylinder group in the cylinder group in order from the end are the first cylinder, the third cylinder, the fifth cylinder, and the cylinders belonging to other cylinder groups in order from the end to the second cylinder, the fourth cylinder, and the sixth cylinder. In this case, the crankpin of one crankshaft corresponding to the one cylinder group is arranged in 120 ° increments in the order of the first cylinder, the third cylinder, and the fifth cylinder in one circumferential direction. The crank pin of the first cylinder is at the top dead center position The crankpin of the sixth cylinder of the other crankshaft corresponding to the other cylinder group is set to the top dead center position, and the crankpin of the other crankshaft is moved to the sixth circumferential direction in the sixth circumferential direction. The cylinder, the fourth cylinder, and the second cylinder are arranged in order of 120 °.

As described above, two cylinder groups having three cylinders as one cylinder group are provided, and two crankshafts are provided so as to correspond to the two cylinder groups, and the rotational force of both crankshafts is obtained from one output shaft. In a 6-cylinder engine that outputs, the distance between the plane perpendicular to the axis of the crankshaft and passing through the bore center of a cylinder belonging to one cylinder group and the plane passing through the bore center of a cylinder belonging to another cylinder group is Since it can be substantially zero or offset by an appropriate amount, the crankshaft axial direction is higher than that of other types of 6-cylinder engines such as a serial type or a V type with one crankshaft and the same bore. The length of the engine can be shortened, and the engine can be downsized.

  Then, the rotation direction of the one crankshaft and the rotation direction of the other crankshaft are the same direction, and the ignition order is the first cylinder, the second cylinder, the third cylinder, the sixth cylinder, the fifth cylinder, The order of the cylinders, or the rotation direction of the one crankshaft and the rotation direction of the other crankshaft are opposite directions, and the ignition order is the first cylinder, the fourth cylinder, the third cylinder, the sixth cylinder, The order of the fifth cylinder and the second cylinder is preferable.

  With this configuration, without adding a balance weight to the crankshaft, when the bank angle is 0 °, the perfect balance equivalent to the inline 6 cylinder and the horizontally opposed type 6 cylinder is 0 ° <bank angle < In the case of 15 °, it is possible to achieve a perfect balance equivalent to the inline 6 cylinder and the horizontally opposed 6 cylinder, and to suppress vibration. As a result, even in a 6-cylinder engine, vibration can be suppressed while reducing the physique. Note that the bearing load can be reduced by adding a balance weight.

  The six-cylinder engine according to the present invention has two cylinder groups with three cylinders as one cylinder group, two crankshafts corresponding to the two cylinder groups, A 6-cylinder engine that outputs the rotational force of a shaft from one output shaft, wherein both cylinder groups are arranged in parallel or both bank angles are smaller than 15 °, and one of the two cylinder groups is arranged. When the cylinders belonging to the cylinder group of the first cylinder, the third cylinder, the fifth cylinder, and the cylinders belonging to the other cylinder groups in order from the end to the second cylinder, the fourth cylinder, and the sixth cylinder, Crank pins of one crankshaft corresponding to one cylinder group are arranged at 120 ° in order of the first cylinder, the fifth cylinder, and the third cylinder in one circumferential direction, and the crankpin of the first cylinder When the cylinder is at the top dead center position The crank pin of the corresponding sixth crankshaft of the other crankshaft is set to the top dead center position, and the crankpin of the other crankshaft is moved to the sixth cylinder, second cylinder, It is characterized by being arranged every 120 ° in the order of four cylinders.

  Then, the rotation direction of the one crankshaft and the rotation direction of the other crankshaft are the same direction, and the ignition order is the first cylinder, the fourth cylinder, the fifth cylinder, the sixth cylinder, the third cylinder, The order of the cylinders, or the rotational direction of the one crankshaft and the rotational direction of the other crankshaft are opposite directions, and the ignition order is the first cylinder, the second cylinder, the fifth cylinder, the sixth cylinder, The order of the third cylinder and the fourth cylinder is preferable.

  Even in such a configuration, without adding a balance weight to the crankshaft, when the bank angle is 0 °, a perfect balance equivalent to that of the inline 6 cylinder and the horizontally opposed type 6 cylinder is 0 ° <bank angle <15 °. Can achieve a perfect balance equivalent to the inline 6 cylinder and the horizontally opposed 6 cylinder, and can suppress vibration. As a result, even in a 6-cylinder engine, vibration can be suppressed while reducing the physique. Note that the bearing load can be reduced by adding a balance weight.

The six-cylinder engine according to the present invention has two cylinder groups with three cylinders as one cylinder group, two crankshafts corresponding to the two cylinder groups, A 6-cylinder engine that outputs the rotational force of a shaft from one output shaft, which is arranged so that the bank angle of both cylinder groups is approximately 30 °, and belongs to one of the two cylinder groups When the cylinders belonging to the first cylinder, the third cylinder, the fifth cylinder, and the other cylinder groups in order from the end are the second cylinder, the fourth cylinder, and the sixth cylinder in order from the end, the one cylinder group Corresponding crank pins of one crankshaft are arranged every 120 ° in the order of the first cylinder, the third cylinder, and the fifth cylinder in one circumferential direction, and the crank pin of the first cylinder is located at the top dead center position. Other crankshafts corresponding to the other cylinder groups The crankpin of the sixth cylinder is at the top dead center position, and the crankpin of the other crankshaft is moved 120 ° in the order of the sixth cylinder, the fourth cylinder, and the second cylinder in the one circumferential direction. It arrange | positions for every.

  Then, the rotation direction of the one crankshaft and the rotation direction of the other crankshaft are the same direction, and the ignition order is the first cylinder, the second cylinder, the third cylinder, the sixth cylinder, the fifth cylinder, The order of the cylinders, or the rotation direction of the one crankshaft and the rotation direction of the other crankshaft are opposite directions, and the ignition order is the first cylinder, the fourth cylinder, the third cylinder, the sixth cylinder, The order of the fifth cylinder and the second cylinder is preferable.

  The six-cylinder engine according to the present invention has two cylinder groups with three cylinders as one cylinder group, two crankshafts corresponding to the two cylinder groups, A 6-cylinder engine that outputs the rotational force of a shaft from one output shaft, which is arranged so that the bank angle of both cylinder groups is approximately 30 °, and belongs to one of the two cylinder groups When the cylinders belonging to the first cylinder, the third cylinder, the fifth cylinder, and the other cylinder groups in order from the end are the second cylinder, the fourth cylinder, and the sixth cylinder in order from the end, the one cylinder group A corresponding crank pin of one crankshaft is arranged in the order of the first cylinder, the fifth cylinder, and the third cylinder in one circumferential direction every 120 °, and the crank pin of the first cylinder is located at the top dead center position. Other crankshafts corresponding to the other cylinder groups The crankpin of the sixth cylinder is at the top dead center position, and the crankpin of the other crankshaft is moved 120 ° in the order of the sixth cylinder, the second cylinder, and the fourth cylinder in the one circumferential direction. It arrange | positions for every.

  Then, the rotation direction of the one crankshaft and the rotation direction of the other crankshaft are the same direction, and the ignition order is the first cylinder, the fourth cylinder, the fifth cylinder, the sixth cylinder, the third cylinder, The order of the cylinders, or the rotational direction of the one crankshaft and the rotational direction of the other crankshaft are opposite directions, and the ignition order is the first cylinder, the second cylinder, the fifth cylinder, the sixth cylinder, The order of the third cylinder and the fourth cylinder is preferable.

  In the above-described 6-cylinder engine arranged so that the bank angle of both cylinder groups is approximately 30 °, when the rotation direction of the one crankshaft and the rotation direction of the other crankshaft are the same direction, When the weight of the reciprocating motion part is Wrec, the weight of the rotational motion part is Wrot, and the crank radius is R, the balance moment in each cylinder is (Wrot + 1/2 × Wrec) × R. It is preferable to provide a balance weight.

  As a result, a residual moment equivalent to that of a general V-type 6-cylinder engine having a bank angle of 60 ° can be obtained, and vibration can be suppressed. Thereby, also in a 6-cylinder engine, a physique can be made small and a vibration can be suppressed.

  Alternatively, it is preferable to provide balance weights on both crankshafts so that Wrot × R. Thereby, the remaining pitch moment can be made zero. In addition, although the yaw moment remains, it can be made smaller than a general V-type 6-cylinder engine with a bank angle of 90 °. Can be suppressed.

  Further, in the above-described 6-cylinder engine arranged so that the bank angle of both the cylinder groups is approximately 30 °, when the rotation direction of the one crankshaft and the rotation direction of the other crankshaft are reversed, Provide balance weights on both crankshafts so that the balance moment in each cylinder is Wrot × R, where Wrec is the weight of the reciprocating part of the cylinder, Wrot is the weight of the rotary part and R is the crank radius. Is preferred.

  Thereby, the remaining pitch moment can be made zero. In addition, although the yaw moment remains, it can be made smaller than a general V-type 6-cylinder engine with a bank angle of 90 °. Can be suppressed.

  The six-cylinder engine according to the present invention has two cylinder groups with three cylinders as one cylinder group, two crankshafts corresponding to the two cylinder groups, A 6-cylinder engine that outputs the rotational force of a shaft from one output shaft, which is arranged so that the bank angle of both cylinder groups is approximately 60 °, and belongs to one of the two cylinder groups When the cylinders belonging to the first cylinder, the third cylinder, the fifth cylinder, and the other cylinder groups in order from the end are the second cylinder, the fourth cylinder, and the sixth cylinder in order from the end, the one cylinder group Corresponding crank pins of one crankshaft are arranged every 120 ° in the order of the first cylinder, the third cylinder, and the fifth cylinder in one circumferential direction, and the crank pin of the first cylinder is located at the top dead center position. Other crankshafts corresponding to the other cylinder groups The crank pin of the fourth cylinder is set to the top dead center position, and the crank pin of the other crank shaft is further rotated 120 ° in the order of the fourth cylinder, the sixth cylinder, and the second cylinder in the one circumferential direction. It arrange | positions for every.

  The rotation direction of the one crankshaft and the rotation direction of the other crankshaft are the same direction, and the ignition order is the first cylinder, the second cylinder, the third cylinder, the fourth cylinder, the fifth cylinder, The order of the cylinders is preferable.

  Also, there are two cylinder groups with three cylinders as one cylinder group, two crankshafts are provided to correspond to the two cylinder groups, and the rotational force of both crankshafts is output from one output shaft A six-cylinder engine is arranged so that the bank angle of both cylinder groups is approximately 60 °, and the cylinders belonging to one of the two cylinder groups are arranged in order from the end, the first cylinder, the third cylinder When the cylinders belonging to the fifth cylinder and other cylinder groups are the second cylinder, the fourth cylinder, and the sixth cylinder in order from the end, the crankpin of one crankshaft corresponding to the one cylinder group is The first cylinder, the fifth cylinder, and the third cylinder are arranged in order of 120 ° in the circumferential direction of the cylinder, and the other cylinder group corresponds to the other cylinder group when the crank pin of the first cylinder is at the top dead center position. The crankpin of the sixth cylinder of the crankshaft is at the top dead center position So as to further the crank pin of the other crankshaft, sixth cylinder in the one circumferential direction, the fourth cylinder, characterized in that arranged in the order of the second cylinder for each 120 °.

  The rotation direction of the one crankshaft and the rotation direction of the other crankshaft are the same direction, and the ignition order is the first cylinder, the second cylinder, the fifth cylinder, the sixth cylinder, the third cylinder, The order of the cylinders is preferable.

  Further, in the above-described 6-cylinder engine arranged so that the bank angle of both the cylinder groups is approximately 60 °, the weight of the reciprocating motion portion in each cylinder is Wrec, the weight of the rotational motion portion is Wrot, and the crank radius is R. In this case, it is preferable to provide balance weights on both crankshafts so that the balance moment in each cylinder is (Wrot + 1/2 × Wrec) × R.

  As a result, the residual unbalance moment is mainly only the secondary vibration force, and can be set to a vibration level equivalent to that of a general V-type 6-cylinder engine having a bank angle of 60 °. As a result, even in a 6-cylinder engine, the size can be reduced and vibration can be suppressed.

  The six-cylinder engine according to the present invention has two cylinder groups with three cylinders as one cylinder group, two crankshafts corresponding to the two cylinder groups, A 6-cylinder engine that outputs the rotational force of a shaft from one output shaft, which is arranged so that the bank angle of both cylinder groups is approximately 120 °, and belongs to one of the two cylinder groups When the cylinders belonging to the first cylinder, the third cylinder, the fifth cylinder, and the other cylinder groups in order from the end are the second cylinder, the fourth cylinder, and the sixth cylinder in order from the end, the one cylinder group Corresponding crank pins of one crankshaft are arranged every 120 ° in the order of the first cylinder, the third cylinder, and the fifth cylinder in one circumferential direction, and the crank pin of the first cylinder is located at the top dead center position. Other crankshafts corresponding to the other cylinder groups The crank pin of the second cylinder of the second cylinder is set to the top dead center position, and the crank pins of the other crank shafts are arranged in the order of the second cylinder, the sixth cylinder, and the fourth cylinder in the one circumferential direction. It is arranged at every degree.

  The rotation direction of the one crankshaft and the rotation direction of the other crankshaft are the same direction, and the ignition order is the first cylinder, the fourth cylinder, the third cylinder, the second cylinder, the fifth cylinder, The order of the cylinders is preferable.

  Also, there are two cylinder groups with three cylinders as one cylinder group, two crankshafts are provided to correspond to the two cylinder groups, and the rotational force of both crankshafts is output from one output shaft A six-cylinder engine is arranged so that the bank angle of both cylinder groups is approximately 120 °, and the cylinders belonging to one of the two cylinder groups are arranged in order from the end, the first cylinder, the third cylinder When the cylinders belonging to the fifth cylinder and other cylinder groups are the second cylinder, the fourth cylinder, and the sixth cylinder in order from the end, the crankpin of one crankshaft corresponding to the one cylinder group is The first cylinder, the fifth cylinder, and the third cylinder are arranged in order of 120 ° in the circumferential direction of the cylinder, and the other cylinder group corresponds to the other cylinder group when the crank pin of the first cylinder is at the top dead center position. Crankshaft of the 4th cylinder of the crankshaft of the top dead center As a further crank pin of the other crankshaft, the fourth cylinder in the one circumferential direction, the sixth cylinder, characterized in that arranged in the order of the second cylinder for each 120 °.

  The rotation direction of the one crankshaft and the rotation direction of the other crankshaft are the same direction, and the ignition order is the first cylinder, the second cylinder, the fifth cylinder, the fourth cylinder, the third cylinder, The order of the cylinders is preferable.

  Further, in the above-described 6-cylinder engine arranged so that the bank angle of both cylinder groups is approximately 120 °, the weight of the reciprocating motion portion in each cylinder is Wrec, the weight of the rotational motion portion is Wrot, and the crank radius is R. In this case, it is preferable to provide balance weights on both crankshafts so that the balance moment in each cylinder is (Wrot + 1/2 × Wrec) × R.

  As a result, the residual unbalance moment is mainly only the secondary vibration force, and can be set to a vibration level equivalent to that of a general V-type 6-cylinder engine having a bank angle of 60 °. As a result, even in a 6-cylinder engine, the size can be reduced and vibration can be suppressed.

The six-cylinder engine according to the present invention has two cylinder groups with three cylinders as one cylinder group, two crankshafts corresponding to the two cylinder groups, A 6-cylinder engine that outputs the rotational force of a shaft from one output shaft, which is arranged so that the bank angle of both cylinder groups is approximately 50 °, and belongs to one of the two cylinder groups When the cylinders belonging to the first cylinder, the third cylinder, the fifth cylinder, and the other cylinder groups in order from the end are the second cylinder, the fourth cylinder, and the sixth cylinder in order from the end, the one cylinder group Corresponding crank pins of one crankshaft are arranged every 120 ° in the order of the first cylinder, the third cylinder, and the fifth cylinder in one circumferential direction, and the crank pin of the first cylinder is located at the top dead center position. Other crankshafts corresponding to the other cylinder groups The crank pin of the fourth cylinder is set to the top dead center position, and the crank pin of the other crank shaft is further rotated 120 ° in the order of the fourth cylinder, the sixth cylinder, and the second cylinder in the one circumferential direction. It arrange | positions for every.

  The rotation direction of the one crankshaft and the rotation direction of the other crankshaft are the same direction, and the ignition order is the first cylinder, the second cylinder, the third cylinder, the fourth cylinder, the fifth cylinder, The order of the cylinders is preferable.

  Also, there are two cylinder groups with three cylinders as one cylinder group, two crankshafts are provided to correspond to the two cylinder groups, and the rotational force of both crankshafts is output from one output shaft A six-cylinder engine is arranged so that the bank angle of both cylinder groups is approximately 50 °, and the cylinders belonging to one of the two cylinder groups are arranged in order from the end, the first cylinder, the third cylinder When the cylinders belonging to the fifth cylinder and other cylinder groups are the second cylinder, the fourth cylinder, and the sixth cylinder in order from the end, the crankpin of one crankshaft corresponding to the one cylinder group is The first cylinder, the fifth cylinder, and the third cylinder are arranged in order of 120 ° in the circumferential direction of the cylinder, and the other cylinder group corresponds to the other cylinder group when the crank pin of the first cylinder is at the top dead center position. The crankpin of the second cylinder of the crankshaft is at the top dead center position So as to further the crank pin of the other crankshaft, the second cylinder to said one circumferential direction, the fourth cylinder, characterized in that arranged on each 120 ° in the order of the sixth cylinder.

  The rotation direction of the one crankshaft and the rotation direction of the other crankshaft are the same direction, and the ignition order is the first cylinder, the second cylinder, the fifth cylinder, the sixth cylinder, the third cylinder, The order of the cylinders is preferable.

  Further, in the above-described 6-cylinder engine arranged so that the bank angle of both cylinder groups is approximately 120 °, the weight of the reciprocating motion portion in each cylinder is Wrec, the weight of the rotational motion portion is Wrot, and the crank radius is R. In this case, it is preferable to provide balance weights on both crankshafts so that the balance moment in each cylinder is (Wrot + 1/2 × Wrec) × R.

  As a result, the residual unbalance moment is mainly only the secondary vibration force, and can be a vibration level equal to or lower than that of a general V-type 6-cylinder engine having a bank angle of 90 °. As a result, even in a 6-cylinder engine, the size can be reduced and vibration can be suppressed.

  As described above, according to the present invention, it is possible to realize a 6-cylinder engine that can reduce the size and suppress vibration.

  The best mode for carrying out the present invention will be exemplarily described in detail below based on the following embodiments with reference to the drawings.

FIG. 1 shows a schematic configuration of an engine 1 according to a first embodiment, where (a) is a longitudinal sectional view of the engine and (b) is a top view of (a).

  The engine 1 is a six-cylinder engine, and is an engine divided into two cylinder groups, with three cylinders out of the six cylinders 2 as one cylinder group. Two crankshafts are provided to correspond to each cylinder group, and the rotational force of these two crankshafts is output from one output shaft.

  In FIG. 1B, the front side when the engine 1 is mounted on a vehicle is the upper side, and the rear side is the lower side. When the engine 1 is viewed from the rear side, a cylinder group arranged on the right side is called a right bank 3a, and a cylinder group arranged on the left side is called a left bank 3b. The crankshaft corresponding to the right bank 3a is referred to as 4a, and the crankshaft corresponding to the left bank 3b is referred to as 4b.

  Further, the numbers of the respective cylinders are assigned to the first cylinder (# 1), the third cylinder (# 3), the fifth cylinder (# 5) from the front side of the right bank 3a, and the second cylinder (from the front side of the left bank 3b). # 2), the fourth cylinder (# 4), and the sixth cylinder (# 6).

  The engine 1 is a so-called zero bank angle engine in which both banks 3a and 3b are provided in parallel as shown in FIG. 1, and the angle formed by the bore centers of both cylinders is substantially zero.

  The plane perpendicular to the axis of the crankshaft 4a and passing through the # 1 bore center is parallel to the plane perpendicular to the axis of the crankshaft 4b and passing through the # 2 bore center. Is configured to be substantially zero. Alternatively, an appropriate amount may be offset. As a result, the length in the axial direction of the crankshaft can be made shorter than that of other types of 6-cylinder engines such as a serial type or a V type with one crankshaft and the same bore, and the engine can be downsized. be able to.

  The output shaft 5 is rotatably supported between the pair of crankshafts 4a and 4b, and the driven gear 51 provided on the output shaft 5 is a drive gear 41a provided on the shaft ends of the pair of crankshafts 4a and 4b. , 41b. One-way clutches (not shown) are provided between the crankshafts 4a and 4b and the drive gears 41a and 41b.

  Normally, when the engine 1 operates, both the crankshafts 4a and 4b rotate in the clockwise direction when viewed from the front side (counterclockwise direction as viewed from the rear side as shown in FIG. 1A). It has become. Each one-way clutch is engaged, and the rotation of the drive gears 41a and 41b is transmitted to the driven gear 51. The output shaft 5 integrated with the driven gear 51 is rotated counterclockwise (when viewed from the rear side, FIG. Rotate clockwise as shown in a). As described above, in the engine 1 according to this embodiment, the crankshafts 4 a and 4 b rotate in the same direction, and these rotational forces are output from one output shaft 5.

  FIG. 2 is a schematic view of the crankshafts 4a and 4b according to the present embodiment, and is a perspective view of the crankshaft as viewed from the front side.

  As shown in FIG. 2, the crankshaft 4a cranks the # 1 first crankpin P1, the # 3 third crankpin P3, and the # 5 fifth crankpin P5 in this order in the clockwise direction. They are arranged every 120 °.

As shown in FIG. 2, the crankshaft 4b has a sixth crankpin P6 # 6 arranged in the same direction as the first crankpin P1 # 1, that is, the first crankpin P1 # 1 is dead. The sixth crankpin P6 of # 6 is at the top dead center position when it is at the point position, and the sixth crankpin P6 of # 6, the fourth crankpin P4 of # 4, the second of the second crankpin # 2 are set in the clockwise direction. The crank pins P2 are arranged in this order at every crank angle of 120 °.

  In such a configuration, ignition (explosion) is performed in the order of # 1, # 2, # 3, # 6, # 5, and # 4, and equidistant ignition (explosion) is performed every crank angle of 120 °.

  By adopting such a crankpin arrangement and firing order, in-line 6 cylinders, horizontally opposed without adding a balance moment Wc × Rc to the crankshaft, which is obtained by multiplying the crank weight weight Wc by the crank weight center of gravity distance Rc. A perfect balance equivalent to that of the type 6 cylinder can be achieved, and vibration can be suppressed. As a result, even in a 6-cylinder engine, vibration can be suppressed while reducing the physique. Note that the bearing load can be reduced by adding a balance weight.

  Alternatively, as shown in FIG. 3, which is a view from the front side, the crankshaft 4a is arranged in the clockwise direction in the # 1st first crankpin P1, the # 5 fifth crankpin P5, and the # 3 third crank. The pins P3 are arranged in this order at every crank angle of 120 °. On the other hand, the crankshaft 4b has the sixth crankpin P6 of # 6 arranged in the same direction as the first crankpin P1 of # 1, and the sixth crankpin P6 of # 6 and the second crank of # 2 in the clockwise direction. The fourth crank pins P4 of the pins P2 and # 4 may be arranged in this order at every crank angle of 120 °.

  In such a configuration, ignition (explosion) is performed in the order of # 1, # 4, # 5, # 6, # 3, and # 2, and equidistant ignition (explosion) is performed every crank angle of 120 °.

  Then, by adopting such a crankpin arrangement and ignition order, the balance moment Wc × Rc is not added to the crankshaft in the same manner as the crankpin arrangement and ignition order shown in FIG. 2 described above. A perfect balance equivalent to 6 cylinders and horizontally opposed 6 cylinders can be achieved, and vibration can be suppressed. As a result, even in a 6-cylinder engine, vibration can be suppressed while reducing the physique. Note that the bearing load can be reduced by adding a balance weight.

  The method of transmitting the rotational force of the crankshafts 4a and 4b to the output shaft 5, that is, the connecting method thereof is not limited to the method described above. For example, as shown in FIG. 4, a driven gear 51 provided on the output shaft 5 and a drive gear 41a of the crankshaft 4a are meshed to transmit the rotational force of the crankshaft 4a to the output shaft 5, and Sprockets may be provided on the crankshaft 4b, and the rotational force of the crankshaft 4b may be transmitted to the output shaft 5 by the chain 6 or the like.

  In such a case, normally, when the engine 1 is operated, the crankshaft 4a rotates in the clockwise direction when viewed from the front side (counterclockwise direction as viewed from the rear side) as shown in FIG. The output shaft 5 rotates in the counterclockwise direction (when viewed from the rear side, the clockwise direction as shown in FIG. 4). That is, the crankshafts 4a and 4b rotate in the opposite direction.

  In such a configuration, as shown in FIG. 5, the crankshaft 4 a has the first crankpin P1 of # 1, the third crankpin P3 of # 3, and the fifth crankpin P5 of # 5 in the clockwise direction. In this order, the crank angle is arranged every 120 °. On the other hand, the crankshaft 4b has the first crankpin P1 # 1 and the sixth crankpin P6 # 6 arranged in the same direction, and the sixth crankpin P6 # 6 and the fourth crankpin # 4 in the clockwise direction. The second crankpins P2 of the crankpins P4 and # 2 are arranged in this order at every crank angle of 120 °.

Then, ignition (explosion) is performed in the order of # 1, # 4, # 3, # 6, # 5, and # 2, and a crank angle of 1
Perform an equally spaced ignition (explosion) every 20 °. Thus, in the same manner as described in the section of the configuration in which the crankshafts 4a and 4b rotate in the same direction, the in-line 6 cylinders, the horizontally opposed 6 cylinders, Equivalent perfect balance can be achieved and vibration can be suppressed. Moreover, bearing load can also be relieved by adding a balance weight.

  Alternatively, as shown in FIG. 3, which is a view from the front side, the crankshaft 4a is arranged in the clockwise direction in the # 1st first crankpin P1, the # 5 fifth crankpin P5, and the # 3 third crank. The pins P3 are arranged in this order at every crank angle of 120 °. On the other hand, in the crankshaft 4b, the # 1 first crankpin P1 and the # 6 sixth crankpin P6 are arranged in the same direction, and the # 6 sixth crankpin P6 and # 2 second are arranged in the clockwise direction. The fourth crank pins P4 of the crank pins P2, # 4 are arranged in this order at every crank angle of 120 °.

  In such a configuration, ignition (explosion) is performed in the order of # 1 → # 2 → # 5 → # 6 → # 3 → # 4, and equidistant ignition (explosion) is performed every crank angle of 120 °. Thus, similarly, a perfect balance equivalent to that of the inline 6 cylinder and the horizontally opposed type 6 cylinder can be achieved without adding a balance moment Wc × Rc to the crankshaft, and vibration can be suppressed. Moreover, bearing load can also be relieved by adding a balance weight.

  The above has described an engine having a bank angle (cylinder pinching angle) of zero in which both banks 3a and 3b of the engine 1 are provided in parallel. The order is preferred.

  With such a configuration, it is difficult to achieve perfect balance like a bank angle of zero, but even if a balance moment Wc × Rc is not added to the crankshaft, it is equivalent to an inline 6 cylinder and a horizontally opposed 6 cylinder. A perfect balance can be achieved, and good engine vibration can be realized. In the range of 0 ° <bank angle <15 °, the residual moment increases as the bank angle increases, but the size is sufficiently small and it is not necessary to mount a balancer shaft.

  As shown in FIG. 6, the engine 1 according to the present embodiment has a so-called bank angle of 30 ° in which the angle (cylinder pinching angle) formed by the bore centers of the cylinders of both banks 3a and 3b is approximately 30 °.

  In the configuration in which the crankshafts 4a and 4b rotate in the same direction as described in the first embodiment, as shown in FIG. 7 which is a view seen from the front side, the crankshaft 4a is rotated in the # 1 direction in the clockwise direction. The first crankpin P1, the third crankpin P3 of # 3, and the fifth crankpin P5 of # 5 are arranged in this order every 120 ° crank angle.

  On the other hand, the crankshaft 4b has the bank angle (cylinder pinching) in the clockwise direction (inclination direction of the bank 3b with respect to the bank 3a) with respect to the # 1 first crankpin P1 with respect to the # 6 sixth crankpin P6. Tilt 30 degrees the same as the angle. In other words, when the # 1 first crank pin P1 is at the top dead center position, the # 6 sixth crank pin P6 is at the top dead center position. Then, the sixth crankpin P6 of # 6, the fourth crankpin P4 of # 4, and the second crankpin P2 of # 2 are arranged in this order at every crank angle of 120 ° in the clockwise direction.

  In such a configuration, ignition (explosion) is performed in the order of # 1 → # 2 → # 3 → # 6 → # 5 → # 4, and equidistant ignition (explosion) is performed every crank angle of 120 °.

In the configuration in which the crank pin arrangement and the firing order are adopted, the balance moment Wc × Rc of the crankshaft is determined as follows.

  Here, as shown in FIG. 8, the weight of the reciprocating portion (piston, piston pin, connecting rod small end, etc.) is Wrec, the weight of the rotating portion (crank pin, connecting rod large end, etc.) is Wrot, crank radius Is R.

  Then, the balance moment Wc × Rc = (Wrot + ½ × Wrec) × R. Thereby, the remaining moment can be made equivalent to that of a general V-type 6-cylinder engine having a bank angle of 60 °, and vibration of the engine 1 can be suppressed. Thereby, also in a 6-cylinder engine, a physique can be made small and a vibration can be suppressed.

  Alternatively, the balance moment Wc × Rc = Wrot × R. Thereby, the remaining pitch moment can be made zero. In addition, although the yaw moment remains, it can be made smaller than a general V-type 6-cylinder engine with a bank angle of 90 °. Vibration can be suppressed.

  Alternatively, as shown in FIG. 9 as viewed from the front side, the crankshaft 4a is arranged in the clockwise direction in the # 1st first crankpin P1, the # 5 fifth crankpin P5, and the # 3 third crank. The pins P3 are arranged in this order at every crank angle of 120 °.

  On the other hand, the direction of the # 6 sixth crankpin P6 of the crankshaft 4b is the same as the configuration of FIG. 7, and the sixth crankpin P6 of # 6 and the second crankpin P2, # 4 of # 2 are rotated in the clockwise direction. The fourth crank pins P4 are arranged in this order at every crank angle of 120 °.

  In this configuration, ignition (explosion) is performed in the order of # 1, # 4, # 5, # 6, # 3, and # 2, and equidistant ignition (explosion) is performed every crank angle of 120 °.

  Even in the configuration in which the crank pin arrangement and the firing order are adopted, the balance moment Wc × Rc of the crankshaft is set to Wc × Rc = (Wrot + 1/2 × Wrec) × R, so that a general bank angle of 60 ° V A residual moment equivalent to that of the type 6-cylinder engine can be obtained, and vibration of the engine 1 can be suppressed.

  Alternatively, the remaining pitch moment can be made zero by setting the balance moment Wc × Rc = Wrot × R. In addition, although the yaw moment remains, it can be made smaller than a general V-type 6-cylinder engine with a bank angle of 90 °. Vibration can be suppressed.

  Further, in the configuration in which the crankshafts 4a and 4b described in the first embodiment rotate in the reverse direction at a bank angle of 30 °, the same crankpin arrangement as in FIG. 7 is used, and then # 1 → # 4 → # 3 → Ignite (explode) in the order of # 6 → # 5 → # 2, and perform equidistant ignition (explosion) every 120 ° of crank angle.

  Alternatively, with the same crank pin arrangement as in FIG. 9, ignition (explosion) is performed in the order of # 1 → # 2 → # 5 → # 6 → # 3 → # 4. Explosion).

In each of these two types of configurations of the crankpin arrangement and the firing order, the balance moment of the crankshaft is Wc × Rc = Wrot × R. Thereby, the remaining pitch moment can be made zero. In addition, although the yaw moment remains, it can be made smaller than a general V-type 6-cylinder engine with a bank angle of 90 °. Vibration can be suppressed.

  As shown in FIG. 10, the engine 1 according to the present embodiment has a so-called bank angle of 60 ° in which the angle (cylinder pinching angle) formed by the bore centers of the cylinders of both banks 3a and 3b is approximately 60 °.

  In the configuration in which the crankshafts 4a and 4b rotate in the same direction as described in the first embodiment, as shown in FIG. 11, which is a view seen from the front side, the crankshaft 4a is rotated in the # 1 direction in the clockwise direction. The first crankpin P1, the third crankpin P3 of # 3, and the fifth crankpin P5 of # 5 are arranged in this order every 120 ° crank angle.

  On the other hand, the crankshaft 4b has a bank angle (cylinder pinching) in which the direction of the # 4 fourth crank pin P4 is clockwise (inclination direction of the bank 3b with respect to the bank 3a) with respect to the # 1 first crank pin P1. Tilt the same 60 °. In other words, when the # 1 first crank pin P1 is at the top dead center position, the # 4 fourth crank pin P4 is at the top dead center position. Then, the fourth crankpin P4 of # 4, the sixth crankpin P6 of # 6, and the second crankpin P2 of # 2 are arranged in this order at every crank angle of 120 ° in the clockwise direction.

  In such a configuration, ignition (explosion) is performed in the order of # 1, # 2, # 3, # 4, # 5, and # 6, and equidistant ignition (explosion) is performed every 120 ° of crank angle.

  In the configuration in which the arrangement of the crankpins and the ignition order are used, the balance moment of the crankshaft is Wc × Rc = (Wrot + 1/2 × Wrec) × R. As a result, the residual unbalance moment is mainly only the secondary vibration force, and can be set to a vibration level equivalent to that of a general V-type 6-cylinder engine having a bank angle of 60 °. Thereby, also in a 6-cylinder engine, a physique can be made small and a vibration can be suppressed.

  Alternatively, as shown in FIG. 12, which is a view from the front side, the crankshaft 4a is arranged in the clockwise direction in the # 1st first crankpin P1, the # 5 fifth crankpin P5, and the # 3 third crank. The pins P3 are arranged in this order at every crank angle of 120 °.

  On the other hand, the direction of the sixth crankpin P6 of # 6 of the crankshaft 4b is set to the bank angle (cylinder clamping angle) in the clockwise direction (inclination direction of the bank 3b with respect to the bank 3a) with respect to the first crankpin P1 of # 1. Tilt the same 60 °. In other words, when the # 1 first crank pin P1 is at the top dead center position, the # 6 sixth crank pin P6 is at the top dead center position. Then, the sixth crankpin P6 of # 6, the fourth crankpin P4 of # 4, and the second crankpin P2 of # 2 are arranged in this order at every crank angle of 120 ° in the clockwise direction.

  In such a configuration, ignition (explosion) is performed in the order of # 1, # 2, # 5, # 6, # 3, and # 4, and equidistant ignition (explosion) is performed every 120 ° of crank angle.

  In the configuration in which the crankpins are arranged and the firing order is set, the balance moment of the crankshaft is Wc × Rc = (Wrot + 1/2 × Wrec) × R. As a result, the residual unbalance moment is mainly only the secondary vibration force, and can be set to a vibration level equivalent to that of a general V-type 6-cylinder engine having a bank angle of 60 °. Thereby, also in a 6-cylinder engine, a physique can be made small and a vibration can be suppressed.

  As shown in FIG. 13, the engine 1 according to the present embodiment has a so-called bank angle of 120 ° in which the angle (cylinder pinching angle) formed by the bore centers of the cylinders of both banks 3 a and 3 b is approximately 120 °.

  In the configuration in which the crankshafts 4a and 4b rotate in the same direction described in the first embodiment, as shown in FIG. 14 as viewed from the front side, the crankshaft 4a is rotated in the # 1 direction in the clockwise direction. The first crankpin P1, the third crankpin P3 of # 3, and the fifth crankpin P5 of # 5 are arranged in this order every 120 ° crank angle.

  On the other hand, the crankshaft 4b has the # 4 fourth crankpin P4 oriented in the same direction as the # 1 first crankpin P1, and the # 2 second crankpin P2 is connected to the # 1 first crankpin. The bank is inclined 120 ° in the clockwise direction (inclination direction of the bank 3b with respect to the bank 3a) with the bank angle (cylinder clamping angle). In other words, when the # 1 first crank pin P1 is at the top dead center position, the # 2 second crank pin P2 is at the top dead center position. Then, the fourth crankpin P4 of # 4, the second crankpin P2 of # 2, and the sixth crankpin P6 of # 6 are arranged in this order at every crank angle of 120 ° in the clockwise direction.

  In such a configuration, ignition (explosion) is performed in the order of # 1, # 4, # 3, # 2, # 5, and # 6, and equidistant ignition (explosion) is performed every 120 ° of crank angle.

  In the configuration in which the arrangement of the crankpins and the ignition order are used, the balance moment of the crankshaft is Wc × Rc = (Wrot + 1/2 × Wrec) × R. As a result, the residual unbalance moment is mainly only the secondary vibration force, and can be set to a vibration level equivalent to that of a general V-type 6-cylinder engine having a bank angle of 60 °. As a result, even in a 6-cylinder engine, the size can be reduced and vibration can be suppressed.

  Alternatively, as shown in FIG. 15 as viewed from the front side, the crankshaft 4a is arranged in the clockwise direction in the # 1st first crankpin P1, the # 5 fifth crankpin P5, and the # 3 third crank. The pins P3 are arranged in this order at every crank angle of 120 °.

  On the other hand, the crankshaft 4b has the # 2 second crankpin P2 arranged in the same direction as the # 1 first crankpin P1, and the # 4 fourth crankpin P4 is oriented so that the # 1 first crankpin The bank is inclined 120 ° in the clockwise direction (inclination direction of the bank 3b with respect to the bank 3a) with the bank angle (cylinder clamping angle). In other words, when the # 1 first crank pin P1 is at the top dead center position, the # 4 fourth crank pin P4 is at the top dead center position. Then, the second crankpin # 2 of # 2, the fourth crankpin P4 of # 4, and the sixth crankpin P6 of # 6 are arranged in this order at every crank angle of 120 ° in the clockwise direction.

  In such a configuration, ignition (explosion) is performed in the order of # 1, # 2, # 5, # 4, # 3, and # 6, and equidistant ignition (explosion) is performed every 120 ° of crank angle.

  Even in the configuration in which the crankpins are arranged and in the ignition order, the balance moment of the crankshaft is Wc × Rc = (Wrot + 1/2 × Wrec) × R. As a result, the residual unbalance moment is mainly only the secondary vibration force, and can be set to a vibration level equivalent to that of a general V-type 6-cylinder engine having a bank angle of 60 °. As a result, even in a 6-cylinder engine, the size can be reduced and vibration can be suppressed.

  As shown in FIG. 16, the engine 1 according to the present embodiment has a so-called bank angle of 50 °, in which the angle (cylinder pinching angle) formed by the bore centers of the cylinders of both banks 3a and 3b is approximately 50 °.

  In the configuration in which the crankshafts 4a and 4b described in the first embodiment rotate in the same direction, as shown in FIG. 17 which is a view seen from the front side, the crankshaft 4a is rotated in the # 1 direction in the clockwise direction. The first crankpin P1, the third crankpin P3 of # 3, and the fifth crankpin P5 of # 5 are arranged in this order every 120 ° crank angle.

  On the other hand, the crankshaft 4b has a bank angle (cylinder pinching angle) in the clockwise direction (inclination direction of the bank 3b with respect to the bank 3a) with respect to the # 1 first crankpin P1. Tilt the same 50 °. In other words, when the # 1 first crank pin P1 is at the top dead center position, the # 4 fourth crank pin P4 is at the top dead center position. Then, the fourth crankpin P4 of # 4, the sixth crankpin P6 of # 6, and the second crankpin P2 of # 2 are arranged in this order at every crank angle of 120 ° in the clockwise direction.

  In such a configuration, ignition (explosion) is performed in the order of # 1, # 2, # 3, # 4, # 5, and # 6, and equidistant ignition (explosion) is performed every 120 ° of crank angle.

  In the configuration in which the arrangement of the crankpins and the ignition order are used, the balance moment of the crankshaft is Wc × Rc = (Wrot + 1/2 × Wrec) × R. As a result, the remaining unbalance moment is mainly only the secondary vibration force, and can be set to a vibration level equivalent to that of a general V-type 6-cylinder engine having a bank angle of 90 °. As a result, even in a 6-cylinder engine, the size can be reduced and vibration can be suppressed.

  Alternatively, as shown in FIG. 18 as viewed from the front side, the crankshaft 4a is arranged in the clockwise direction in the # 1st first crankpin P1, the # 5 fifth crankpin P5, and the # 3 third crank. The pins P3 are arranged in this order at every crank angle of 120 °.

  On the other hand, the crankshaft 4b has a bank angle (cylinder pinching angle) in the clockwise direction (inclination direction of the bank 3b with respect to the bank 3a) with respect to the # 1 first crankpin P1 in the direction of the # 2 second crankpin P2. Tilt the same 50 °. In other words, when the # 1 first crank pin P1 is at the top dead center position, the # 2 second crank pin P2 is at the top dead center position. Then, the second crankpin # 2 of # 2, the fourth crankpin P4 of # 4, and the sixth crankpin P6 of # 6 are arranged in this order at every crank angle of 120 ° in the clockwise direction.

  In such a configuration, ignition (explosion) is performed in the order of # 1, # 2, # 5, # 6, # 3, and # 4, and equidistant ignition (explosion) is performed every 120 ° of crank angle.

  In the configuration in which the arrangement of the crankpins and the ignition order are used, the balance moment of the crankshaft is Wc × Rc = (Wrot + 1/2 × Wrec) × R. As a result, the remaining unbalance moment is mainly only the secondary vibration force, and can be set to a vibration level equivalent to that of a general V-type 6-cylinder engine having a bank angle of 90 °. As a result, even in a 6-cylinder engine, the size can be reduced and vibration can be suppressed.

1 is a diagram illustrating a schematic configuration of an engine according to Embodiment 1. FIG. It is a perspective view which shows arrangement | positioning of the crankpin of the crankshaft of the engine which concerns on Example 1. FIG. It is a figure which shows other arrangement | positioning of the crankpin of the crankshaft of the engine which concerns on Example 1. FIG. It is a figure which shows the outline of the other structure of the engine which concerns on Example 1. FIG. It is a figure which shows arrangement | positioning of the crankpin in the other structure of the engine which concerns on Example 1. FIG. FIG. 3 is a diagram illustrating a schematic configuration of an engine according to a second embodiment. It is a figure which shows arrangement | positioning of the crankpin of the crankshaft of the engine which concerns on Example 2. FIG. It is a schematic diagram of a crankshaft, a connecting rod, a piston, etc. used when considering the vibration balance of the engine. It is a figure which shows other arrangement | positioning of the crankpin of the crankshaft of the engine which concerns on Example 2. FIG. FIG. 6 is a diagram illustrating a schematic configuration of an engine according to a third embodiment. It is a figure which shows arrangement | positioning of the crankpin of the crankshaft of the engine which concerns on Example 3. FIG. FIG. 10 is a view showing another arrangement of crank pins of a crankshaft of an engine according to a third embodiment. FIG. 10 is a diagram illustrating a schematic configuration of an engine according to a fourth embodiment. It is a figure which shows arrangement | positioning of the crankpin of the crankshaft of the engine which concerns on Example 4. FIG. FIG. 10 is a diagram illustrating another arrangement of crank pins of a crankshaft of an engine according to a fourth embodiment. FIG. 10 is a diagram illustrating a schematic configuration of an engine according to a fifth embodiment. It is a figure which shows arrangement | positioning of the crankpin of the crankshaft of the engine which concerns on Example 5. FIG. FIG. 10 is a view showing another arrangement of crank pins of a crankshaft of an engine according to a fifth embodiment.

Explanation of symbols

1 Engine 2 Cylinder 3a Right bank 3b Left bank 4a, 4b Crankshaft 5 Output shaft 6 Chain

Claims (25)

6 cylinders that have 2 cylinder groups with 3 cylinders as 1 cylinder group, 2 crankshafts corresponding to 2 cylinder groups, and output torque of both crankshafts from 1 output shaft An engine,
Both cylinder groups are arranged in parallel or the bank angle of both is smaller than 15 °,
Cylinders belonging to one of the two cylinder groups in order from the end to the first cylinder, third cylinder, fifth cylinder, cylinders belonging to the other cylinder groups in order from the end to the second cylinder, fourth cylinder, In the case of the sixth cylinder, the crank pins of one crankshaft corresponding to the one cylinder group are arranged at 120 ° intervals in the order of the first cylinder, the third cylinder, and the fifth cylinder in one circumferential direction. In addition, when the crank pin of the first cylinder is at the top dead center position, the crank pin of the sixth cylinder of the other crank shaft corresponding to the other cylinder group is at the top dead center position. 6. A six-cylinder engine, wherein crankshaft crankpins are arranged in the order of the sixth cylinder, the fourth cylinder, and the second cylinder in the one circumferential direction in every 120 degrees.   The rotation direction of the one crankshaft and the rotation direction of the other crankshaft are the same direction, and the ignition order is the first cylinder, the second cylinder, the third cylinder, the sixth cylinder, the fifth cylinder, and the fourth cylinder. Or the rotation direction of the one crankshaft and the rotation direction of the other crankshaft are opposite directions, and the ignition sequence is the first cylinder, the fourth cylinder, the third cylinder, the sixth cylinder, The six-cylinder engine according to claim 1, wherein the cylinder is in the order of the second cylinder. 6 cylinders that have 2 cylinder groups with 3 cylinders as 1 cylinder group, 2 crankshafts corresponding to 2 cylinder groups, and output torque of both crankshafts from 1 output shaft An engine,
Both cylinder groups are arranged in parallel or the bank angle of both is smaller than 15 °,
Cylinders belonging to one of the two cylinder groups in order from the end to the first cylinder, third cylinder, fifth cylinder, cylinders belonging to the other cylinder groups in order from the end to the second cylinder, fourth cylinder, In the case of the sixth cylinder, the crank pins of one crankshaft corresponding to the one cylinder group are arranged at 120 ° intervals in the order of the first cylinder, the fifth cylinder, and the third cylinder in one circumferential direction. In addition, when the crank pin of the first cylinder is at the top dead center position, the crank pin of the sixth cylinder of the other crank shaft corresponding to the other cylinder group is at the top dead center position. 6. A six-cylinder engine, wherein crankshaft crankpins are arranged every 120 degrees in the order of the sixth cylinder, the second cylinder, and the fourth cylinder in the one circumferential direction.   The rotation direction of the one crankshaft and the rotation direction of the other crankshaft are the same direction, and the ignition order is the first cylinder, the fourth cylinder, the fifth cylinder, the sixth cylinder, the third cylinder, and the second cylinder. Or the rotation direction of the one crankshaft and the rotation direction of the other crankshaft are opposite directions, and the ignition sequence is the first cylinder, the second cylinder, the fifth cylinder, the sixth cylinder, The six-cylinder engine according to claim 3, wherein the order is cylinder, fourth cylinder. 6 cylinders that have 2 cylinder groups with 3 cylinders as 1 cylinder group, 2 crankshafts corresponding to 2 cylinder groups, and output torque of both crankshafts from 1 output shaft An engine,
Arranged so that the bank angle of both cylinder groups is approximately 30 °,
Cylinders belonging to one of the two cylinder groups in order from the end to the first cylinder, third cylinder, fifth cylinder, cylinders belonging to the other cylinder groups in order from the end to the second cylinder, fourth cylinder, In the case of the sixth cylinder, the crank pins of one crankshaft corresponding to the one cylinder group are arranged at 120 ° intervals in the order of the first cylinder, the third cylinder, and the fifth cylinder in one circumferential direction. In addition, when the crank pin of the first cylinder is at the top dead center position, the crank pin of the sixth cylinder of the other crank shaft corresponding to the other cylinder group is at the top dead center position. 6. A six-cylinder engine, wherein crankshaft crankpins are arranged in the order of the sixth cylinder, the fourth cylinder, and the second cylinder in the one circumferential direction in every 120 degrees.   The rotation direction of the one crankshaft and the rotation direction of the other crankshaft are the same direction, and the ignition order is the first cylinder, the second cylinder, the third cylinder, the sixth cylinder, the fifth cylinder, and the fourth cylinder. Or the rotation direction of the one crankshaft and the rotation direction of the other crankshaft are opposite directions, and the ignition sequence is the first cylinder, the fourth cylinder, the third cylinder, the sixth cylinder, 6. A six-cylinder engine according to claim 5, wherein the cylinder is in the order of the second cylinder. 6 cylinders that have 2 cylinder groups with 3 cylinders as 1 cylinder group, 2 crankshafts corresponding to 2 cylinder groups, and output torque of both crankshafts from 1 output shaft An engine,
Arranged so that the bank angle of both cylinder groups is approximately 30 °,
Cylinders belonging to one of the two cylinder groups in order from the end to the first cylinder, third cylinder, fifth cylinder, cylinders belonging to the other cylinder groups in order from the end to the second cylinder, fourth cylinder, In the case of the sixth cylinder, the crank pins of one crankshaft corresponding to the one cylinder group are arranged at 120 ° intervals in the order of the first cylinder, the fifth cylinder, and the third cylinder in one circumferential direction. In addition, when the crank pin of the first cylinder is at the top dead center position, the crank pin of the sixth cylinder of the other crank shaft corresponding to the other cylinder group is at the top dead center position. 6. A six-cylinder engine, wherein crankshaft crankpins are arranged every 120 degrees in the order of the sixth cylinder, the second cylinder, and the fourth cylinder in the one circumferential direction.   The rotation direction of the one crankshaft and the rotation direction of the other crankshaft are the same direction, and the ignition order is the first cylinder, the fourth cylinder, the fifth cylinder, the sixth cylinder, the third cylinder, and the second cylinder. Or the rotation direction of the one crankshaft and the rotation direction of the other crankshaft are opposite directions, and the ignition sequence is the first cylinder, the second cylinder, the fifth cylinder, the sixth cylinder, The six-cylinder engine according to claim 7, wherein the cylinder is in the order of the fourth cylinder. When the rotation direction of the one crankshaft and the rotation direction of the other crankshaft are the same direction,
When the weight of the reciprocating motion part in each cylinder is Wrec, the weight of the rotational motion part is Wrot, and the crank radius is R,
The six-cylinder engine according to claim 6 or 8, wherein balance weights are provided on both crankshafts so that a balance moment in each cylinder is (Wrot + 1/2 × Wrec) × R or Wrot × R. . When the rotation direction of the one crankshaft and the rotation direction of the other crankshaft are opposite directions,
When the weight of the reciprocating motion part in each cylinder is Wrec, the weight of the rotational motion part is Wrot, and the crank radius is R,
The six-cylinder engine according to claim 6 or 8, wherein balance weights are provided on both crankshafts so that a balance moment in each cylinder is Wrot × R. 6 cylinders that have 2 cylinder groups with 3 cylinders as 1 cylinder group, 2 crankshafts corresponding to 2 cylinder groups, and output torque of both crankshafts from 1 output shaft An engine,
Arranged so that the bank angle of both cylinder groups is approximately 60 °,
Cylinders belonging to one of the two cylinder groups in order from the end to the first cylinder, third cylinder, fifth cylinder, cylinders belonging to the other cylinder groups in order from the end to the second cylinder, fourth cylinder, In the case of the sixth cylinder, the crank pins of one crankshaft corresponding to the one cylinder group are arranged at 120 ° intervals in the order of the first cylinder, the third cylinder, and the fifth cylinder in one circumferential direction. In addition, when the crankpin of the first cylinder is at the top dead center position, the crankpin of the fourth cylinder of the other crankshaft corresponding to the other cylinder group is at the top dead center position. 6. A six-cylinder engine, wherein crankshaft crankpins are arranged every 120 degrees in the order of the fourth cylinder, the sixth cylinder, and the second cylinder in the one circumferential direction.   The rotation direction of the one crankshaft and the rotation direction of the other crankshaft are the same direction, and the ignition order is the first cylinder, the second cylinder, the third cylinder, the fourth cylinder, the fifth cylinder, and the sixth cylinder. The six-cylinder engine according to claim 11, wherein the six-cylinder engine is in order. 6 cylinders that have 2 cylinder groups with 3 cylinders as 1 cylinder group, 2 crankshafts corresponding to 2 cylinder groups, and output torque of both crankshafts from 1 output shaft An engine,
Arranged so that the bank angle of both cylinder groups is approximately 60 °,
Cylinders belonging to one of the two cylinder groups in order from the end to the first cylinder, third cylinder, fifth cylinder, cylinders belonging to the other cylinder groups in order from the end to the second cylinder, fourth cylinder, In the case of the sixth cylinder, the crank pins of one crankshaft corresponding to the one cylinder group are arranged at 120 ° intervals in the order of the first cylinder, the fifth cylinder, and the third cylinder in one circumferential direction. In addition, when the crank pin of the first cylinder is at the top dead center position, the crank pin of the sixth cylinder of the other crank shaft corresponding to the other cylinder group is at the top dead center position. 6. A six-cylinder engine, wherein crankshaft crankpins are arranged in the order of the sixth cylinder, the fourth cylinder, and the second cylinder in the one circumferential direction in every 120 degrees.   The rotation direction of the one crankshaft and the rotation direction of the other crankshaft are the same direction, and the ignition order is the first cylinder, the second cylinder, the fifth cylinder, the sixth cylinder, the third cylinder, and the fourth cylinder. The six-cylinder engine according to claim 13, wherein the six-cylinder engine is in order. When the weight of the reciprocating motion part in each cylinder is Wrec, the weight of the rotational motion part is Wrot, and the crank radius is R,
The six-cylinder engine according to claim 12 or 14, wherein balance weights are provided on both crankshafts so that a balance moment in each cylinder is (Wrot + 1/2 x Wrec) x R. 6 cylinders that have 2 cylinder groups with 3 cylinders as 1 cylinder group, 2 crankshafts corresponding to 2 cylinder groups, and output torque of both crankshafts from 1 output shaft An engine,
Arrange so that the bank angle of both cylinder groups is approximately 120 °,
Cylinders belonging to one of the two cylinder groups in order from the end to the first cylinder, third cylinder, fifth cylinder, cylinders belonging to the other cylinder groups in order from the end to the second cylinder, fourth cylinder, In the case of the sixth cylinder, the crank pins of one crankshaft corresponding to the one cylinder group are arranged at 120 ° intervals in the order of the first cylinder, the third cylinder, and the fifth cylinder in one circumferential direction. In addition, when the crankpin of the first cylinder is at the top dead center position, the crankpin of the second cylinder of the other crankshaft corresponding to the other cylinder group is at the top dead center position. 6. A six-cylinder engine, wherein crankshaft crankpins are arranged at intervals of 120 degrees in the order of the second cylinder, the sixth cylinder, and the fourth cylinder in the one circumferential direction.   The rotation direction of the one crankshaft and the rotation direction of the other crankshaft are the same direction, and the ignition order is the first cylinder, the fourth cylinder, the third cylinder, the second cylinder, the fifth cylinder, and the sixth cylinder. The six-cylinder engine according to claim 16, wherein the six-cylinder engine is in order. 6 cylinders that have 2 cylinder groups with 3 cylinders as 1 cylinder group, 2 crankshafts corresponding to 2 cylinder groups, and output torque of both crankshafts from 1 output shaft An engine,
Arrange so that the bank angle of both cylinder groups is approximately 120 °,
Cylinders belonging to one of the two cylinder groups in order from the end to the first cylinder, third cylinder, fifth cylinder, cylinders belonging to the other cylinder groups in order from the end to the second cylinder, fourth cylinder, In the case of the sixth cylinder, the crank pins of one crankshaft corresponding to the one cylinder group are arranged at 120 ° intervals in the order of the first cylinder, the fifth cylinder, and the third cylinder in one circumferential direction. In addition, when the crankpin of the first cylinder is at the top dead center position, the crankpin of the fourth cylinder of the other crankshaft corresponding to the other cylinder group is at the top dead center position. 6. A six-cylinder engine characterized in that crankshaft crank pins are arranged in 120 ° increments in the order of the fourth cylinder, the sixth cylinder, and the second cylinder in the one circumferential direction.   The rotation direction of the one crankshaft and the rotation direction of the other crankshaft are the same direction, and the ignition order is the first cylinder, the second cylinder, the fifth cylinder, the fourth cylinder, the third cylinder, and the sixth cylinder. The six-cylinder engine according to claim 18, wherein the six-cylinder engine is in order. When the weight of the reciprocating motion part in each cylinder is Wrec, the weight of the rotational motion part is Wrot, and the crank radius is R,
20. The six-cylinder engine according to claim 17, wherein balance weights are provided on both crankshafts so that a balance moment in each cylinder is (Wrot + ½ × Wrec) × R. 6 cylinders that have 2 cylinder groups with 3 cylinders as 1 cylinder group, 2 crankshafts corresponding to 2 cylinder groups, and output torque of both crankshafts from 1 output shaft An engine,
Arrange so that the bank angle of both cylinder groups is about 50 °,
Cylinders belonging to one of the two cylinder groups in order from the end to the first cylinder, third cylinder, fifth cylinder, cylinders belonging to the other cylinder groups in order from the end to the second cylinder, fourth cylinder, In the case of the sixth cylinder, the crank pins of one crankshaft corresponding to the one cylinder group are arranged at 120 ° intervals in the order of the first cylinder, the third cylinder, and the fifth cylinder in one circumferential direction. In addition, when the crankpin of the first cylinder is at the top dead center position, the crankpin of the fourth cylinder of the other crankshaft corresponding to the other cylinder group is at the top dead center position. 6. A six-cylinder engine, wherein crankshaft crankpins are arranged every 120 degrees in the order of the fourth cylinder, the sixth cylinder, and the second cylinder in the one circumferential direction.   The rotation direction of the one crankshaft and the rotation direction of the other crankshaft are the same direction, and the ignition order is the first cylinder, the second cylinder, the third cylinder, the fourth cylinder, the fifth cylinder, and the sixth cylinder. The six-cylinder engine according to claim 21, wherein the six-cylinder engine is in order. 6 cylinders that have 2 cylinder groups with 3 cylinders as 1 cylinder group, 2 crankshafts corresponding to 2 cylinder groups, and output torque of both crankshafts from 1 output shaft An engine,
Arrange so that the bank angle of both cylinder groups is about 50 °,
Cylinders belonging to one of the two cylinder groups in order from the end to the first cylinder, third cylinder, fifth cylinder, cylinders belonging to the other cylinder groups in order from the end to the second cylinder, fourth cylinder, In the case of the sixth cylinder, the crank pins of one crankshaft corresponding to the one cylinder group are arranged in 120 ° increments in the order of the first cylinder, the fifth cylinder, and the third cylinder in one circumferential direction. In addition, when the crankpin of the first cylinder is at the top dead center position, the crankpin of the second cylinder of the other crankshaft corresponding to the other cylinder group is at the top dead center position. 6. A six-cylinder engine, wherein crankshaft crankpins are arranged at 120 ° intervals in the order of the second cylinder, the fourth cylinder, and the sixth cylinder in the one circumferential direction.   The rotation direction of the one crankshaft and the rotation direction of the other crankshaft are the same direction, and the ignition order is the first cylinder, the second cylinder, the fifth cylinder, the sixth cylinder, the third cylinder, and the fourth cylinder. The six-cylinder engine according to claim 23, wherein the six-cylinder engine is in order. When the weight of the reciprocating motion part in each cylinder is Wrec, the weight of the rotational motion part is Wrot, and the crank radius is R,
25. The six-cylinder engine according to claim 22, wherein balance weights are provided on both crankshafts so that a balance moment in each cylinder is (Wrot + 1/2 × Wrec) × R.

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