JP2011089525A - Accessory arrangement structure of cylinder resting internal combustion engine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an arrangement structure of an accessory, inhibiting fluctuations of driving torque of valve operating camshafts in a cylinder resting internal combustion engine having two cylinder banks. <P>SOLUTION: The cylinder resting internal combustion engine has the two cylinder banks (2L, 2R) in which a part of cylinders can rest with intake and exhaust valves (11, 21) kept closed and the remaining cylinders always operate. The accessory arrangement structure of the cylinder resting internal combustion engine includes the accessory (120) driven with rotation of the valve operating camshafts (92R, 102R) in the cylinder bank (82R) in which the resting cylinder (83R) exists. All the cylinders in one (82F) of the cylinder banks are the cylinders (83F) always operating, and the accessory (120) is provided on the valve operating camshafts (92R, 102R) of the other cylinder bank (82R) in which the resting cylinder (83R) exists. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a cylinder deactivation internal combustion engine in which two cylinder rows face each other in a V-shaped bank or are horizontally opposed so that some cylinders can be deactivated and the remaining cylinders are always operated. Concerning the arrangement structure.

Patent Document 1 discloses a structure in which a fuel pump is disposed in each valve mechanism in each cylinder row of each bank of a V-type internal combustion engine in which two cylinder rows are banked in a V-shape. The V-type internal combustion engine is provided with a DOHC type valve mechanism, and a pump cam is formed at each end of each intake camshaft disposed on the space side between the cylinder rows of each bank. Is in contact with the fuel injection pump.

JP 2007-224743 A

The fuel injection pump is a high-pressure pump that supplies fuel to a fuel injection valve that directly injects fuel into the combustion chamber of the internal combustion engine, and therefore the pump drive torque of the pump cam is large.
If the phase at which the pump driving torque becomes maximum coincides with the phase at which the valve driving torque of the intake cam that drives the intake valve coincides, the driving torque of the intake cam shaft fluctuates greatly, and the intake cam The tension of the timing belt that rotates the shaft by transmitting power between the crankshafts also varies greatly.

  Therefore, in Patent Document 1, the variation in the drive torque of the intake camshaft is set by setting the phase at which the pump drive torque is maximum and the phase at which the valve drive torque of the intake cam that drives the intake valve does not coincide with each other. Suppressed.

  However, the internal combustion engine disclosed in Patent Document 1 is a normal V-type internal combustion engine in which all cylinders are always operating cylinders, and there is no disclosure of a cylinder deactivation internal combustion engine in which some cylinders can be deactivated.

  The present invention has been made in view of such points, and an object of the present invention is to provide an auxiliary machine that can suppress fluctuations in the driving torque of the valve camshaft in a cylinder deactivation internal combustion engine having two cylinder rows. The point is to provide an arrangement structure.

  In order to achieve the above object, the invention according to claim 1 has two cylinder rows (2L, 2R), and some cylinders are deactivated by maintaining the intake and exhaust valves (11, 21) closed. In a cylinder deactivation internal combustion engine in which the remaining cylinders are always operated, an auxiliary machine (120) that is driven by the rotation of the valve camshaft (92R, 102R) of the cylinder row (82R) in which the deactivation cylinder (83R) exists is provided. , All of the cylinders in one cylinder row (82F) are always operating cylinders (83F), and the auxiliary camshafts (92R, 102R) in the cylinder row (82R) in which the other idle cylinder (83R) exists (120) is an auxiliary machine arrangement structure of a cylinder deactivation internal combustion engine.

  According to a second aspect of the present invention, in the auxiliary engine arrangement structure of the cylinder deactivation internal combustion engine according to the first aspect, the valve operating camshaft (92R, 102R) of the cylinder row (82R) in which the deactivation cylinder (83R) exists is A cam (92p) for driving the auxiliary machine (120), the number of cam peaks of the cam (92p) is equal to the number of cylinders of the normally operating cylinder (83F) of the one cylinder row (82F); It is characterized by the same number.

According to a third aspect of the present invention, in the auxiliary engine arrangement structure of the cylinder deactivation internal combustion engine according to the first or second aspect, the fuel injection valve (110) for directly injecting fuel into the combustion chamber of the internal combustion engine is provided,
The auxiliary machine (120) is a fuel that is driven by bringing a pump operating part into contact with a pump cam (92p) formed on the valve camshaft (92R, 102R) and pumps fuel to the fuel injection valve (110) side. It is an injection pump (120).

  According to a fourth aspect of the present invention, in the auxiliary cylinder arrangement structure of the cylinder deactivation internal combustion engine according to the third aspect, the cylinder row (82R) in which the other deactivation cylinder (83R) exists is composed of all deactivation cylinders (83R). The intake / exhaust valves (91, 101) of the valve operating camshafts (92F, 102F) of the cylinder row (82F) in which the one continuously operating cylinder (83F) exists during the idle operation in which the deactivated cylinder (83R) is deactivated. The maximum or minimum phase of the combined valve driving torque (Tv) obtained by combining the valve operating torques of the operating cams that operate and the maximum or minimum phase of the pump driving torque (Tp) of the pump cam (92p), The pump cam (92p) is set in phase so as not to coincide.

  According to a fifth aspect of the present invention, in the auxiliary engine arrangement structure of the cylinder deactivation internal combustion engine according to the third aspect, the cylinder row (82R) in which the other deactivation cylinder (83R) exists is composed of all deactivation cylinders (83R). The intake / exhaust valves (91, 101) of the valve operating camshafts (92F, 102F) of the cylinder row (82F) in which the one continuously operating cylinder (83F) exists during the idle operation in which the deactivated cylinder (83R) is deactivated. The maximum or minimum phase of the combined valve driving torque (Tv) obtained by combining the valve operating torques of the operating cams that operate and the phase where the pump driving torque (Tp) of the pump cam (92p) is minimum or maximum, The pump cam (92p) is set in phase so as to match.

  According to the auxiliary engine arrangement structure of the cylinder deactivation internal combustion engine according to claim 1, all of the cylinders in one cylinder row (82F) are always active cylinders (83F), and the cylinder row in which the other deactivation cylinder (83R) exists. (82R) The valve drive camshaft (92R, 102R) is equipped with an auxiliary device, so the other auxiliary drive torque (Tp) is effective against the valve drive torque (Tv) of one cylinder row (82F). It is possible to suppress the maximum torque of the combined drive torque (T) to be small, and it is possible to reduce the load on the valve power transmission member by suppressing fluctuations in the drive torque.

  According to the auxiliary engine arrangement structure of the cylinder deactivation internal combustion engine according to claim 2, the number of cam ridges of the cam (92p) is the same as the number of normally operating cylinders (83F) of one cylinder row (82F). Therefore, fluctuations in the drive torque can be suppressed by setting the phase so that the other accessory drive torque (Tp) cancels out the valve drive torque (Tv) of the one cylinder row (82F).

  According to the auxiliary arrangement structure of the cylinder deactivation internal combustion engine according to claim 3, the fuel injection valve (110) for directly injecting the fuel into the combustion chamber of the internal combustion engine is provided, and the auxiliary machine (120) includes the valve operating camshaft (92R , 102R) is a fuel injection pump (120) that is driven by contacting a pump operating part to a pump cam (92p) formed on the fuel injection valve (110) side. The pump drive torque of the fuel injection pump (120) that supplies high-pressure fuel to the fuel injection valve (110) of the jet is relatively large, but the combined drive torque of the valve drive torque (Tv) and the accessory drive torque (Tp) The maximum torque of (T) can be effectively reduced, and fluctuations in drive torque can be suppressed.

  According to the auxiliary cylinder arrangement structure of the cylinder deactivation internal combustion engine according to claim 4, during the cylinder deactivation operation in which the deactivation cylinder (83R) is deactivation, the valve train of the cylinder row (82F) in which one continuously operating cylinder (83F) exists The maximum or minimum phase of the combined valve drive torque (Tv) that combines the valve operating torque of the operating cam that operates the intake and exhaust valves (91, 101) of the camshaft (92F, 102F), and the pump drive of the pump cam (92p) The pump cam (92p) is phase-set so that the maximum or minimum phase of the torque (Tp) does not match, so the combined drive torque (Tv) and pump drive torque (Tp) combined drive torque ( The maximum torque of T) can be reduced, and fluctuations in drive torque can be suppressed.

  According to the auxiliary cylinder arrangement structure of the cylinder deactivation internal combustion engine according to claim 5, during the cylinder deactivation operation in which the deactivation cylinder (83R) is deactivation, the valve train of the cylinder row (82F) in which one of the normally operating cylinders (83F) is present The maximum or minimum phase of the combined valve drive torque (Tv) that combines the valve operating torque of the operating cam that operates the intake and exhaust valves (91, 101) of the camshaft (92F, 102F), and the pump drive of the pump cam (92p) Since the pump cam (92p) is set in phase so that the minimum or maximum phase of the torque (Tp) matches, the combined drive torque of the combined valve drive torque (Tv) and the pump drive torque (Tp) The maximum torque is suppressed as small as possible, and fluctuations in drive torque can be suppressed.

1 is a partial left side view of a water-cooled four-stroke V-type six-cylinder internal combustion engine according to an embodiment of the present invention. It is the same top view. It is a block diagram of the intake cam shaft and the exhaust cam shaft of the valve mechanism. It is a figure which shows the torque fluctuation | variation which synthesize | combined the drive torque of the intake / exhaust valve-operating camshaft of a right side cylinder row | line | column and a left side cylinder row | line | column in a idle cylinder driving state.

Hereinafter, an embodiment according to the present invention will be described with reference to FIGS.
The V-type cylinder deactivation internal combustion engine according to the present embodiment is an on-vehicle water-cooled four-stroke V-type six-cylinder internal combustion engine E2, which is mounted on the vehicle with the crankshaft 81 directed in the left-right direction of the vehicle body, The front cylinder row 82F and the rear cylinder row 82R are banked in a V shape (see FIG. 1).

In the front cylinder row 82F and the rear cylinder row 82R, three cylinders 83F and 83R are arranged in series, respectively, and the position of the front cylinder row 82F is slightly shifted to the right from the rear cylinder row 82R. (See FIG. 2).

  Cylinder heads 84F and 84R are overlapped on the front and rear cylinders 83F and 83R, respectively, and fastened together, and the head covers 85F and 85R are covered on the cylinder heads 84F and 84R, respectively. The cylinder head 84F and the head cover 85F and the cylinder 83R, the cylinder head 84R and the head cover 85R of the rear bank protrude in a V shape.

  Connecting rods 87F, 87R are interposed between pistons 86F, 86R reciprocating in the cylinder bores of cylinders 83F, 83R and crankshaft 81 to form a piston / crank mechanism, and pistons 86F, 86R of cylinder heads 84F, 84R are configured. Open to the combustion chambers 88, 88 facing the top of the engine, intake ports 89, 89 extend toward the space between the front and rear cylinder rows 82F, 82R (inside the bank), and the exhaust ports 90, 90 are front and rear cylinders. It extends toward the opposite side (outside the bank) of the space between the rows 82F and 82R.

The cylinder heads 84F and 84R are each provided with a so-called DOHC type valve mechanism having intake cam shafts 92F and 92R and exhaust cam shafts 102F and 102R in parallel with the crankshaft 81, respectively. 92R is disposed inside the bank, and the exhaust camshafts 102F and 102R are disposed outside the bank.

Between the intake valve 91 that opens and closes the opening of the intake port 89 to the combustion chamber 88 and the intake cam shafts 92F and 92R, the intake valve that converts the rotational motion of the intake cam shafts 92F and 92R into the open and close motion of the intake valve 91 Drive devices 93F and 93R are interposed.
Further, between the exhaust valve 101 that opens and closes the opening of the exhaust port 90 to the combustion chamber 88 and the exhaust cam shafts 102F and 102R, the rotational motion of the exhaust cam shafts 102F and 102R is converted into the opening and closing motion of the exhaust valve 101. Exhaust valve driving devices 103F and 103R are interposed.

The intake valve driving devices 93F and 93R and the exhaust valve driving devices 103F and 103R are all provided with a valve lift amount changing mechanism for changing the valve lift amount according to the operating state of the internal combustion engine. There are two types: a drive device with a pause mechanism that can be paused by keeping 101 closed, and a drive device without it.
A cylinder having a drive device with a deactivation mechanism is a deactivation cylinder, and a cylinder having a drive device without a deactivation mechanism is a normally operating cylinder.

In the V-type six-cylinder internal combustion engine E2, three cylinders in the front cylinder row 82F are always operating cylinders, and three cylinders in the rear cylinder row 82R are idle cylinders (see FIG. 2).
In FIG. 2, broken cylinder hatches are applied to the idle cylinders in the rear cylinder row 82R.

  Accordingly, the three-cylinder intake valve driving device 93F and the exhaust valve driving device 103F in the front cylinder row 82F are not provided with a deactivation mechanism and are always driven intake valve driving devices, and the intake air of the three cylinders in the rear cylinder row 82R. The valve driving device 93R and the exhaust valve driving device 103R are provided with a pause mechanism.

In the V-type six-cylinder internal combustion engine E 2, a fuel injection valve 110 that directly injects fuel into the combustion chamber 88 is inserted in the center of the ceiling surface of the combustion chamber 88.
Although not shown, the spark plug is also inserted into the ceiling surface of the combustion chamber 88.

  FIG. 3 is a configuration diagram of intake camshafts 92F and 92R and exhaust camshafts 102F and 102R of the valve operating mechanism. Referring to FIG. 3, driven pulleys 115F and 115F are disposed at the left ends of intake camshafts 92F and 92R. 115R is fitted, and driven pulleys 116F and 116R are fitted to the left ends of the exhaust camshafts 102F and 102R.

An endless timing belt 117 is wound around a driving pulley 114 and driven pulleys 115F, 115R, 116F, and 116R that are fitted to the crankshaft 81, and the rotation of the crankshaft 1 is taken into the intake cam via the timing belt 117. It is transmitted to the shafts 92F and 92R and the exhaust cam shafts 102F and 102R.
The intake camshafts 92F and 92R and the exhaust camshafts 102F and 102R are transmitted at half the rotational speed of the crankshaft 81.

  Referring to FIG. 3, the three cylinders in the front cylinder row 82F are always operating cylinders, and the portions corresponding to the cylinders of the intake camshaft 92F and the exhaust camshaft 102F have large displacement intake air with a high cam peak at the center. Cams 92b and 102b are formed, and small displacement intake cams 92s, 92s, 102s and 102s with low cam peaks are formed adjacent to both sides thereof.

  Three cylinders in the rear cylinder row 82R are deactivated cylinders, and large displacement intake cams 92b and 102b with high cam peaks are formed in the center at portions corresponding to the cylinders of the intake cam shaft 92R and the exhaust cam shaft 102R. The cams 92d, 92d, 102d and 102d are formed adjacent to both sides to form a cam surface of a basic circle having no cam crest, and further adjacent to the outside of the cams 92d, 92d, 102d and 102d. Accordingly, small displacement intake cams 92s, 92s, 102s, and 102s with low cam peaks are formed.

A pump cam 92p is formed in the vicinity of the right end portion of the intake camshaft 92R in the rear cylinder row 82R including the deactivated cylinder.
A fuel injection pump 120 is disposed above the pump cam 92p. The fuel injection pump 120 is driven by the rotation of the pump cam 92p with the pump lifter protruding downward contacting the cam surface of the pump cam 92p.

The pump cam 92p has a substantially equilateral triangle shape with a cam surface having three cam peaks.
Since intake camshaft 92R makes one rotation with respect to two rotations of crankshaft 81, pump cam 92p reciprocates the pump lifter of fuel injection pump 120 three times during that time.
The fuel injection pump 120 supplies fuel to the fuel injection valves 110 of the respective cylinders before and after the fuel injection pressure is controlled by the fuel spill, similarly to the fuel injection pumps 70L and 70R of the above embodiment.

The V-type six-cylinder internal combustion engine E2 is in a pause operation state in which all three cylinders in the front cylinder row 82F of the front bank are in operation and all three cylinders in the rear cylinder row 82R in the rear bank are in a pause operation.
FIG. 4 shows the combined valve drive torque Tv (broken line) of the intake camshaft 92F and the exhaust camshaft 102F of the front cylinder row 82F that is valve-driven in the idle operation state, and the pump cam 92p of the intake camshaft 92R of the rear cylinder row 82R. The fluctuation of the pump driving torque Tp (dotted line) of the fuel injection pump 120 and the combined driving torque T (solid line) of the valve driving torque Tv and the pump driving torque Tp is shown.

A combined drive torque T obtained by combining the drive torques of all the valve drive camshafts corresponds to the drive torque of the crankshaft 81 driven via the timing belt 117.
As shown in FIG. 4, during the cylinder resting operation, the pump driving torque Tp fluctuates to the negative side at a phase where the valve driving torque Tv fluctuates to the positive side, and the pump driving torque at a phase where the valve driving torque Tv fluctuates to the negative side Tp varies to the positive side and varies to the opposite side.

  The phase in which the valve driving torque Tv indicates the maximum torque value (about 15 N · m) and the phase in which the pump driving torque Tp indicates the minimum torque value (about −2.5 N · m) are substantially coincident with each other, and the valve driving torque Tv is The phase showing the minimum torque value (about -15 N · m) and the phase where the pump driving torque Tp shows the maximum torque value (about 2.5 N · m) are almost the same.

  Therefore, the valve driving torque Tv of the front cylinder row 82F with only the normally operating cylinder and the pump driving torque Tp of the rear cylinder row 82R of the deactivated cylinder are effectively changed in a direction to cancel each other, and the valve driving torque Tv As shown by the solid line in FIG. 4, the maximum torque of the combined drive torque T obtained by combining the pump drive torque Tp and the pump drive torque Tp is kept as small as possible.

The pump drive torque Tp of the fuel injection pump 120 that supplies high pressure fuel to the direct injection fuel injection valve 110 that requires high pressure injection is relatively large, and the combined drive torque T of the valve drive torque Tv and the pump drive torque Tp is The maximum torque can be effectively reduced, and fluctuations in the drive torque can be suppressed to reduce the load on the timing belt 117.

  In the above embodiment, the fuel injection pump 120 is provided on the intake camshaft 92R of the rear bank including the idle cylinder of the V-type six-cylinder internal combustion engine E2, but the fuel injection pump is provided on the exhaust camshaft 102R of the rear bank. Also good.

  In the above two embodiments, the pump cam is formed on the valve camshaft and the fuel injection pump is driven. In addition, an auxiliary machine such as a water pump is driven or the valve camshaft is driven. The present invention can also be applied to a case in which a gear is formed and an auxiliary machine is driven through gear engagement.

  When the phases of the multiple operating cams that operate the intake and exhaust valves are not evenly spaced, the maximum or minimum phase of the valve driving torque of the operating cam and the minimum or maximum phase of the pump driving torque of the pump cam In some cases, it may be difficult to set the phase of the pump cam so that the values substantially match.

In such a case, the phase of the pump cam may be set so that the phase at which the valve driving torque of the operating cam is maximum or minimum does not match the phase at which the pump driving torque of the pump cam is maximum or minimum. preferable.
In this case, it is more preferable to set such that the maximum or minimum phase of the valve driving torque of the operating cam does not match the maximum or minimum phase of the pump driving torque of the pump cam.

  In general, the absolute value of the positive torque is greater than the absolute value of the negative torque, so the phase of the maximum valve drive torque of the operating cam and the phase of the maximum pump drive torque of the pump cam match. It is desirable to prioritize such settings.

E2 ... V-type 6-cylinder internal combustion engine, 81 ... Crankshaft, 82L ... Left cylinder row, 82R ... Right cylinder row, 83L, 83R ... Cylinder, 84L, 84R ... Cylinder head, 85L, 85R ... Head cover, 86L, 86R ... Piston , 88 ... Combustion chamber, 89 ... Intake port, 90 ... Exhaust port,
91 ... Intake valve, 92L, 92R ... Intake cam shaft, 92b, 102b ... Large displacement intake cam, 92d, 92d, 102d, 102d ... Pause cam, 92s, 92s, 102s, 102s ... Small displacement intake cam, 92p ... Pump cam , 93F, 93R ... intake valve driving device, 101 ... exhaust valve, 102F, 102R ... exhaust camshaft, 103F, 103R ... exhaust valve driving device,
110 ... Fuel injection valve, 115F, 115R, 116F, 116R ... Driven pulley, 117 ... Timing belt, 120 ... Fuel injection pump.

Claims (5)

In a cylinder deactivation internal combustion engine that has two cylinder rows (2L, 2R), some cylinders can be deactivated by maintaining the intake and exhaust valves (11, 21) closed, and the remaining cylinders are always in operation.
An auxiliary machine (120) that is driven by the rotation of the valve camshaft (92R, 102R) of the cylinder row (82R) in which the idle cylinder (83R) exists,
All of the cylinders in one cylinder row (82F) are always operating cylinders (83F), and the auxiliary machine (92R, 102R) is connected to the valve drive camshaft (92R, 102R) of the cylinder row (82R) in which the other idle cylinder (83R) exists. 120) An auxiliary machine arrangement structure of a cylinder deactivation internal combustion engine characterized by comprising The valve train cam shaft (92R, 102R) of the cylinder row (82R) in which the idle cylinder (83R) exists has a cam (92p) for driving the auxiliary machine (120),
The number of cam peaks of the cam (92p) is the same as the number of cylinders of the normally operating cylinder (83F) of the one cylinder row (82F). Machine layout structure. A fuel injection valve (110) for directly injecting fuel into the combustion chamber of the internal combustion engine,
The auxiliary machine (120) is a fuel that is driven by bringing a pump operating part into contact with a pump cam (92p) formed on the valve camshaft (92R, 102R) and pumps fuel to the fuel injection valve (110) side. The auxiliary machine arrangement structure of a cylinder deactivation internal combustion engine according to claim 1 or 2, wherein the auxiliary pump arrangement is an injection pump (120). The cylinder row (82R) in which the other idle cylinder (83R) exists is composed of all idle cylinders (83R),
During idle cylinder operation when the idle cylinder (83R) is deactivated, the intake / exhaust valves (91, 101) of the valve drive camshafts (92F, 102F) of the cylinder row (82F) in which the one continuously operating cylinder (83F) exists are operated. The maximum or minimum phase of the combined valve drive torque (Tv) combined with the valve operation torque of the operating cam that does not match the maximum or minimum phase of the pump drive torque (Tp) of the pump cam (92p). As described above, the auxiliary cam arrangement of the cylinder deactivation internal combustion engine according to claim 3, wherein the phase of the pump cam (92p) is set. The cylinder row (82R) in which the other idle cylinder (83R) exists is composed of all idle cylinders (83R),
During idle cylinder operation when the idle cylinder (83R) is deactivated, the intake / exhaust valves (91, 101) of the valve drive camshafts (92F, 102F) of the cylinder row (82F) in which the one continuously operating cylinder (83F) exists are operated. The maximum or minimum phase of the combined valve drive torque (Tv), which combines the valve operation torques of the operating cams, matches the minimum or maximum phase of the pump drive torque (Tp) of the pump cam (92p). As described above, the auxiliary cam arrangement of the cylinder deactivation internal combustion engine according to claim 3, wherein the phase of the pump cam (92p) is set.

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