JP2004316626A - Tilted type engine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a tilted type engine which is miniaturized. <P>SOLUTION: In the tilted type engine with a cylinder 2 protruded upwardly in the diagonal direction from a crank case 1, a valve system cam gear 5 is engaged with a crank gear 4 from the right side in a specified observing state that the cylinder protruding direction is on the right upper side when viewed in the direction parallel to the axis 3 of a crank shaft, a governor gear 6 is disposed in a space between an engagement part of the crank gear 4 and the valve system gear 5, and the governor gear 6 is engaged with the valve system gear 5 from the left lower side. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

    The present invention relates to an inclined engine.

  Conventionally, there is an inclined engine in which a cylinder is projected obliquely upward from a crankcase, as in the present invention (see Patent Document 1).

This type of engine is useful for lowering the height and lowering the hood of the machine on which it is mounted.
In this conventional engine, a gear train is constituted by a crank gear, a valve gear cam gear, a governor gear, and a balancer gear.

JP-A-11-303941

The above prior art has the following problems.
《Problem》 The gear train is not compact.
Although the gear train is composed of the crank gear, valve gear, governor gear, and balancer gear, the gear train is not compact because the arrangement of each gear is not devised, which is one of the factors that hinder the engine from becoming compact. Has become one.

An object of the present invention is to provide an inclined engine capable of solving the above-mentioned problems.

You.

The main matters specifying the invention of claim 1 are as follows.
As shown in FIG. 1, in an inclined engine in which a cylinder (2) is projected obliquely upward from a crankcase (1),
When viewed in a direction parallel to the central axis of the crankshaft (3), in a specific observation state in which the cylinder protruding direction is the upper right, the valve gear cam gear (5) is engaged with the crank gear (4) from the right side, and the crank gear (4) is engaged. ) And a governor gear (6) arranged in a space below a meshing point of the valve gear (5), and the governor gear (6) is meshed with the valve gear (5) from the lower left thereof. Type engine.

(Invention of claim 1)
The invention of claim 1 has the following effects.
<< Effect 1 >> The gear train becomes compact.
As shown in FIG. 1, the space below the meshing point between the crank gear (4) and the valve gear cam gear (5) is effectively used as the arrangement space for the governor gear (6), and the gear train constituted by these components becomes compact. . This makes it possible to reduce the size of the engine.

(Invention of claim 2)
The invention of claim 2 has the following effect in addition to the effect of the invention of claim 1.
<< Effect 2 >> The height of the engine can be reduced.
As shown in FIG. 1, since the lower portion (2a) of the cylinder (2) is projected into the crankcase (1), the height of the engine can be reduced accordingly.

<< Effect 3 >> The cooling performance of the lower part of the cylinder is ensured.
As shown in FIG. 1, the lower part (2a) of the cylinder (2) is protruded into the crankcase (1), and the outer peripheral surface of the lower part (2a) of the cylinder (2) faces the inside of the crankcase (1). The lower part of the governor gear (6) was immersed in the oil (8) of the oil reservoir (7), and the upper part of the governor gear (6) was disposed above the oil (8) of the oil reservoir (7). The oil splashed by the rotation adheres to the outer peripheral surface of the lower portion (2a) of the cylinder (2) and cools it. For this reason, the cooling performance of the lower part (2a) of the cylinder (2) is ensured despite the lower part (2a) of the cylinder (2) protruding into the crankcase (1).

<< Effect 4 >> Oil deterioration can be suppressed.
As shown in FIG. 1, in the specific observation state, the valve cam gear (5) is arranged at the upper right of the governor gear (6), so that the valve cam gear (5) is immersed in the oil (8) of the oil reservoir (7). Or the amount of immersion is small even if immersed, so that unnecessary stirring of the oil (8) by the valve cam gear (5) can be avoided, and deterioration of the oil (8) caused by this can be suppressed. Can be.

(Invention of claim 3)
The invention of claim 3 has the following effect in addition to the effect of the invention of claim 2.
<< Effect 5 >> The cooling efficiency of the lower part of the cylinder can be increased.
As shown in FIG. 1, during the engine operation in the specific observation state, the governor gear (6) rotates counterclockwise, and the valve gear cam gear (5) rotates clockwise. The valve cam gear (5) and the outer peripheral surface of the lower part (2a) of the cylinder (2) are arranged at positions overlapping each other, and viewed in a direction perpendicular to the crankshaft center axis (3) as shown in FIG. The valve cam gear (5) is located at a position adjacent to the outer peripheral surface of the lower portion (2a) of the cylinder (2). Therefore, as shown in FIG. 8) is lifted by the governor gear (6), transferred to the valve gear cam gear (5), and smoothly supplied to the outer peripheral surface of the lower portion (2a) of the cylinder (2). Therefore, the cooling efficiency of the lower part (2a) of the cylinder (2) can be improved.

(Invention of Claim 4)
The invention of claim 4 has the following effect in addition to the effect of the invention of claim 2 or 3.
<< Effect 6 >> The cooling efficiency of the lower part of the cylinder can be increased.
As shown in FIG. 1, cooling fins (9) are provided on the outer peripheral surface of the lower portion (2a) of the cylinder (2), so that the cooling fins (9) are supplied to the outer peripheral surface of the lower portion (2a) of the cylinder (2). The oil is held by the cooling fins (9) without immediately falling into the oil sump (7), where the heat in the lower part (2a) of the cylinder (2) is sufficiently absorbed. Therefore, the cooling efficiency of the lower part (2a) of the cylinder (2) can be improved.

(Invention of claim 5)
The invention of claim 5 has the following effects in addition to the effects of any of the inventions of claims 2 to 4.
<< Effect 7 >> Oil deterioration can be suppressed.
As shown in FIG. 2, the governor gear (6) is made thinner than the valve cam gear (5), so that unnecessary stirring of the oil by the governor gear (6) can be avoided. Degradation can be suppressed.

(Invention of claim 6)
The invention of claim 6 has the following effect in addition to the effect of any of the inventions of claim 1 to claim 5.
<< Effect 8 >> Oil deterioration can be suppressed.
As shown in FIG. 1, in the specific observation state, the reciprocating balancer (11) is located at the lower left of the crankshaft (10), so that the oil (8) in the oil reservoir (7) of the reciprocating balancer (11) is located. ), Or the reciprocating balancer (11) is not immersed, so that the reciprocating balancer (11) can be prevented from stirring the oil (8) more than necessary, and deterioration of the oil (8) can be prevented. Can be suppressed.

(Invention of claim 7)
The invention of claim 7 has the following effects in addition to the effects of any of the inventions of claims 1 to 6.
<< Effect 9 >> The degree of freedom in the arrangement of the reciprocating balancer is high.
As shown in FIG. 3, a part of the reciprocating balancer (11) was immersed in the oil (8) of the oil reservoir (7) so that the oil (8) was jumped up when the reciprocating balancer (11) was raised. There is no need to provide an oil depper on the connecting rod (12). For this reason, the degree of freedom of the arrangement of the reciprocating balancer (11) is high because there is no need to consider the interference with the oil depper.

(Invention of claim 8)
The invention of claim 8 has the following effect in addition to the effect of the invention of claim 7.
<< Effect 10 >> Lubricity between the large end of the connecting rod and the crankpin is high.
As shown in FIG. 3, a groove (14) is formed on the upper surface of the reciprocating balancer (11) so as to face the large end (13) of the connecting rod (12). Since the groove (14) is formed between the two, the oil (8) jumped up by the reciprocating balancer (11) is intensively supplied to the large end (13) of the connecting rod (12), Sufficient oil is supplied between the large end (13) of (12) and the crankpin (47). Therefore, lubrication between the large end portion (13) of the connecting rod (12) and the crankpin (47) is high.

(Invention of claim 9)
The invention of claim 9 has the following effect in addition to the effect of any of the inventions of claim 1 to claim 8.
<< Effect 11 >> The height of the engine can be reduced.
As shown in FIG. 1, a valve operating camshaft (15) is arranged in a space below a lower portion (2a) of a cylinder (2), and a fuel injection cam (16) is provided on the valve operating camshaft (15). In the observation state, since the fuel injection pump (17) is arranged laterally to the right of the fuel injection cam (16), the space below the lower portion (2a) of the cylinder (2) is effectively used, and the valve operating cam shaft (15) is used. ), The fuel injection cam (16) and the fuel injection pump (17) can be housed compactly. Therefore, the height of the engine can be reduced.

(Invention of claim 10)
The invention of claim 10 has the following effect in addition to the effects of any one of claims 1 to 9.
<< Effect 12 >> The height of the engine can be reduced.
As shown in FIG. 4, since the governor lever (18) is arranged in the space below the valve operating shaft (15), the governor lever (18) can be made compact by effectively utilizing the space below the lower part (2a) of the cylinder (2). Can be accommodated. Therefore, the height of the engine can be reduced.

<< Effect 13 >> Rippling of oil in the oil reservoir can be suppressed.
As shown in FIG. 4, since a part of the governor lever (18) is immersed in the oil (8) of the oil reservoir (7), the ripples of the oil (8) in the oil reservoir (7) can be suppressed.

(Invention of Claim 11)
The eleventh invention has the following effect in addition to the effect of the tenth invention.
<< Effect 14 >> Rotational hunting hardly occurs.
As shown in FIG. 5, the governor holder (21) is provided with a stopper (24) for the governor lever (18), and the stopper (24) receives the swing (18a) of the governor lever (18) in the fuel decreasing direction, whereby The upper limit of the opening angle of the governor weight (33) is specified.
When the opening angle of the governor weight (33) increases, the fluctuation of the governor force with respect to the fluctuation of the rotation speed becomes too large, and the rotation hunting easily occurs. In the present invention, however, the upper limit of the opening angle of the governor weight (33) is defined. Therefore, rotation hunting is unlikely to occur.

(Invention of Claim 12)
The invention of claim 12 has the following effect in addition to the effect of the invention of claim 11.
<< Effect 15 >> The number of parts can be reduced.
As shown in FIG. 5, the stopper pin (25) has a function of regulating the swing (18a) of the governor lever (18) and a function of fixing the pivot (22). No components are required, and the number of components can be reduced.

(Invention of Claim 13)
The invention of claim 13 has the following effect in addition to the effect of the invention of claim 12.
<< Effect 16 >> It is possible to easily remove the stopper pin.
As shown in FIG. 4 (A), the stopper pin hole (27) and the knock pin hole (30) overlap each other when viewed in a direction parallel to the center axis of the stopper pin hole (27). As shown in FIG. 5B and FIG. 5, the knock pin hole (30) is extended to a position reaching the insertion end of the stopper pin (25) inserted into the stopper pin hole (27). When the mechanical governor (19) is to be disassembled and repaired, the knock pin (31) is removed from the knock pin hole (30), and then a thin tool inserted through the knock pin hole (30) is used. By pushing the insertion end of the stopper pin (25), the stopper pin (25) can be easily removed.

<< Effect 17 >> Drilling is facilitated.
As shown in FIG. 4A, the stopper pin hole (27) and the knock pin hole (30) overlap each other when viewed in a direction parallel to the center axis of the stopper pin hole (27). The hole 27 and the knock pin hole 30 can be commonly aligned for drilling. In this case, drilling is facilitated.

(Invention of Claim 14)
The invention of claim 14 has the following effect in addition to the effect of any of the inventions of claim 11 to claim 13.
<< Effect 18 >> The number of parts can be reduced.
As shown in FIG. 5, the rod (34) is projected from the input block (32), a swing limiting hole (35) is opened in the governor holder (21), and the rod (34) is inserted into the swing limiting hole (35). Thus, since the swing of the input block (32) is limited, the governor holder (21) also serves as a swing limiting function of the input block (32). For this reason, it is not necessary to use a dedicated component having a swing limiting function, and the number of components can be reduced.

(Invention of claim 15)
The invention of claim 15 has the following effect in addition to the effect of the invention of claim 9.
<< Effect 19 >> A sufficient fuel capacity of the fuel tank can be secured.
As shown in FIG. 3, according to a ninth aspect, a valve operating camshaft (15) is disposed in a space below a lower portion (2a) of a cylinder (2), and a fuel injection cam (16) is mounted on the valve operating camshaft (15). ), And in the specific observation state, in addition to the fuel injection pump (17) being arranged laterally to the right of the fuel injection cam (16), as shown in FIG. ), The fuel can be supplied from the fuel tank (36) to the fuel injection pump (17) by its own weight even if the bottom of the fuel tank (36) is lowered. A sufficient fuel capacity of the tank (36) can be secured.

(Claim 16)
The invention of claim 16 has the following effect in addition to the effect of any of the inventions of claim 1 to claim 15.
<< Effect 20 >> The right and left weight balance of the engine can be secured.
As shown in FIG. 1, the starter motor (37) is arranged at the upper left of the crankcase (1) in the specific observation state where the cylinder projecting direction is the upper right, so that the weight arrangement of the cylinder (2) and the starter motor (37) is made. Thereby, the right and left weight balance of the engine can be ensured.

(Invention of claim 17)
The invention of claim 17 has the following effect in addition to the effect of any of the inventions of claim 1 to claim 16.
<< Effect 21 >> Durability of peripheral components of the sub-combustion chamber is high.
As shown in FIG. 3, since the sub-combustion chamber (48) is arranged at a position closer to a high place of the cylinder head (38), the temperature of the refrigerant such as the cooling air or the coolant rises around the sub-combustion chamber (48). However, the high-temperature refrigerant floats almost without contacting the rocker arm chamber (58) located at a position lower than the sub-combustion chamber (48). For this reason, the rocker arm (59), which is a peripheral component of the sub-combustion chamber (48), is hardly exposed to high heat, and the peripheral components of the sub-combustion chamber (48) have high durability.

(Invention of claim 18)
The invention of claim 18 has the following effect in addition to the effect of any of the inventions of claim 1 to claim 17.
<< Effect 22 >> It is possible to strongly cool a portion of a cylinder having a high heat load, which is closer to a high place.
As shown in FIG. 3, when arranging the sub-combustion chamber (48) at a position closer to a high position of the cylinder head (38), the high-periphery outer surface of the cylinder (2) faces the position closer to a high position of the cylinder block. A cooling air passage (39) was formed, and as shown in FIG. 6, the inlet (40) of the cooling air passage (39) was made to face the pressure-feeding end portion (42) of the fan case (41). The high part of the cylinder (2) having a high height can be cooled strongly.
(Invention of claim 19)
The invention of claim 19 has the following effect in addition to the effects of any one of claims 1 to 18.
<< Effect 23 >> The peripheral wall of the sub-combustion chamber having a high heat load can be cooled strongly.
As shown in FIG. 3, when arranging the sub-combustion chamber (48) at a position closer to a high place of the cylinder head (38), a cooling air passage (23) is formed beside the sub-combustion chamber (48). With the peripheral wall of the sub-combustion chamber (48) facing the air path (23), as shown in FIG. 6, the inlet (29) of the sub-combustion chamber cooling air path (23) is connected to the end of the pressure feed of the fan case (41). (42), the peripheral wall of the sub-combustion chamber (48) having a high heat load can be cooled strongly.

(Invention of claim 20)
The invention of claim 20 has the following effect in addition to the effect of the invention of claim 18 or 19.
<< Effect 24 >> The blowing loss to the end of the pressure feeding of the fan case is reduced.
As shown in FIG. 6, since the starter gear (43) is arranged at a position (58) deviating from the pressure feed path (57) from the pressure feed start end (56) to the pressure feed end (42) of the fan case (41), It is not necessary to form a bulge for accommodating the starter gear (43) in the path (57), and the loss of blowing air to the pressure-feeding end portion (42) of the fan case (41) is reduced.
(Invention of claim 21)
The invention of claim 21 has the following effect in addition to the effects of any one of claims 1 to 20.
<< Effect 25 >> The degree of freedom in the arrangement of the oil pump is high.
As shown in FIG. 7, when the oil pump (45) is arranged near the work implement mounting portion (44) of the engine machine wall (20) in the specific observation posture, as shown in FIG. Since the pump case (46) of (45) protrudes inside the engine machine wall (20), there is no need to consider interference with the work machine mounting part (44). High degree.
(Invention of claim 22)
The invention of claim 22 has the following effect in addition to the effects of any one of claims 10 to 14.
<< Effect 26 >> The governing accuracy of the governor is high.
As shown in FIG. 4B, the weight of one lever (18B) was received by the lower pivot boss (26B), and the weight of the other lever (18A) was received by the upper pivot boss (26A). . If the other lever (18A) is overlaid on one lever (18B) and the lower pivot boss (26B) receives the weight of both levers (18A) (18B), one lever (18B) 18B), and the governor dosing accuracy is reduced. On the other hand, in the present invention, one lever (18B) does not receive the weight of the other lever (18A), the movement is smooth, and the governing accuracy of the governor is high.

An embodiment of the present invention will be described with reference to the drawings.
FIG. 1 to FIG. 7 are diagrams illustrating an inclined engine according to an embodiment of the present invention.
This embodiment will be described using a single-cylinder inclined diesel engine.

The outline of this embodiment is as follows.
As shown in FIG. 1, the feature of this embodiment is to reduce the size of the engine and cool the oil in the lower part (2a) of the cylinder (2) by devising the gear arrangement of the gear train, as shown in FIG. In addition, the arrangement of the reciprocating balancer (11) improves the lubrication in the crankcase (1), and as shown in FIGS. 3 to 5, the arrangement of the fuel injection pump (17) and the governor lever (18). The size of the engine is reduced, and as shown in FIG. 3, the fuel capacity is secured by disposing the fuel tank (36). As shown in FIG. The weight balance is achieved, and as shown in FIG. 3, the arrangement of the sub-combustion chamber (48) increases the durability of the peripheral parts of the sub-combustion chamber (48), and as shown in FIG. (39) cools the sub-combustion chamber (48) and its surroundings, and is shown in FIG. Sea urchin, the arrangement of the oil pump (45), lies in increasing the degree of freedom in arrangement.

The gear arrangement of the engine gear train is as follows.
As shown in FIG. 1, the cylinder (2) is projected obliquely upward from the crankcase (1), viewed in a direction parallel to the crankshaft center axis (3), and in a specific observation state in which the cylinder projection direction is upper right. , The valve gear cam gear (5) is engaged with the crank gear (4) from the right side, and the governor gear (6) is arranged in a space below the meshing point of the crank gear (4) and the valve gear cam gear (5). (6) is engaged with the valve cam gear (5) from the lower left thereof.

The oil cooling structure of the lower part (2a) of the cylinder (2) is as follows.
As shown in FIG. 1, the lower part (2a) of the cylinder (2) is protruded into the crankcase (1), and the outer peripheral surface of the lower part (2a) of the cylinder (2) faces the inside of the crankcase (1). The lower part of the governor gear (6) is immersed in the oil (8) of the oil sump (7), and the upper part of the governor gear (6) is arranged above the oil (8) of the oil sump (7). The valve cam gear (5) is arranged at the upper right of the governor gear (6).

  As shown in FIG. 1, in the specific observation state, the governor gear (6) rotates counterclockwise while the engine is operating, and the valve gear cam gear (5) rotates clockwise in the specific observation state. The valve cam gear (5) and the outer peripheral surface of the lower portion (2a) of the cylinder (2) are arranged at positions overlapping each other, and are orthogonal to the crankshaft center axis (3) as shown in FIG. When viewed from the direction, the valve gear cam gear (5) is located at a position adjacent to the outer peripheral surface of the lower portion (2a) of the cylinder (2). Cooling fins (9) are provided on the outer peripheral surface of the lower part (2a) of the cylinder (2) in a lateral direction. As shown in FIG. 2, the governor gear (6) is thinner than the valve gear (5).

The arrangement of the reciprocating balancer (11) is as follows.
As shown in FIG. 3, in the specific observation state, the reciprocating balancer (11) is located at the lower left of the crankshaft (10), and a part of the reciprocating balancer (11) is oiled in the oil reservoir (7). (8) so that the oil (8) jumps up when the reciprocating balancer (11) is raised, and a groove facing the large end (13) of the connecting rod (12) is formed on the upper surface of the reciprocating balancer (11). (14) is formed so that a groove (14) is formed between the front and back walls in the specific observation state. As shown in FIG. 1, the reciprocating balancer (11) is operatively connected to the crankshaft (10) through an interlocking arm (62), and a pivot point (63) of the interlocking arm (62) on the crankshaft (10) side. Are eccentric from the crankshaft center axis (3). As shown in FIG. 3, the reciprocating balancer (11) descends when the piston (64) rises, rises when the piston (64) descends, and cancels the reciprocating vibration generated by the elevation of the piston (64). Like that.

The arrangement of the fuel injection pump (17) and the governor lever (18) are as follows.
As shown in FIG. 3, a valve operating camshaft (15) is arranged in a space below a lower portion (2a) of the cylinder (2), and a fuel injection cam (16) is provided on the valve operating camshaft (15). In the observation state, the fuel injection pump (17) is arranged laterally on the right side of the fuel injection cam (16). Further, as shown in FIG. 4, a governor lever (18) is arranged in a space below the valve cam shaft (16), and a part of the governor lever (18) is immersed in the oil (8) of the oil reservoir (7). I have.

The configuration of the governor holder (21) that supports the governor lever (18) is as follows.
As shown in FIG. 5, in disposing the mechanical governor (19), the governor holder (21) is attached to the engine machine wall (20), and the governor lever (18) is pivotally supported on the governor holder (21) by the pivot (22). The governor holder (21) is provided with a stopper (24) for the governor lever (18), and the stopper (24) receives the swing (18a) of the governor lever (18) in the fuel decreasing direction, thereby opening the governor weight (33). Specifies the upper limit of the angle. The engine machine wall (20) to which the governor holder (21) is attached is a front wall of the crankcase (1). Using a stopper pin (25) as the stopper (24), the pivot (22) is fitted inside the pivot boss (26) of the governor holder (21), and a stopper pin hole (27) is formed in the pivot boss (26). Open the stopper pin (25) in series along the radial direction of the stopper pin hole (27) and the pivot (22), and use the stopper pin (25) to connect the pivot (22) to the pivot boss (26). The governor lever (18) is received by the projecting portion of the stopper pin (25) from the pivot boss (26).

The mounting structure of the governor holder (21) is as follows.
As shown in FIG. 5 (A), the governor holder (21) is provided with a seat (28), and the governor holder (21) is attached to the engine machine wall (20) with the seat (28). A knock pin hole (30) is made in the knock pin hole (30), and when the governor holder (21) is positioned with respect to the engine machine wall (20) by the knock pin (31) driven into the knock pin hole (30), it is shown in FIG. 4B and 5A, the stopper pin hole 27 and the knock pin hole 30 overlap each other when viewed in a direction parallel to the center axis of the stopper pin hole 27. ), The knock pin hole (30) is extended to a position reaching the insertion end of the stopper pin (25) inserted into the stopper pin hole (27), and the knock pin hole (30) and the stopper pin hole (27) are extended. And the communication.

  As shown in FIG. 5 (B), the input block (32) is swingably attached to the swinging end of the governor lever (18), and the governor lever (18) is moved from the governor weight (33) via the input block (32). In transmitting the governor force to the swing end of the rod, the rod (34) is projected from the input block (32), and a swing limiting hole (35) is opened in the governor holder (21). The rocking of the input block (32) is restricted by inserting the rod (34) into the shaft. The input block (32) is for smoothly transmitting the governor force generated by the governor weight (33) to the swinging end of the governor lever (18). A pivot (32a) is provided at the swing end of the governor lever (18), and the input block (32) is pivotally supported by the pivot (32a). A pivot (33c) is provided on the governor gear (6), and the governor weight (33) is pivotally supported by the pivot (33c). A pivot (33d) is provided on the governor weight (33), and the output block (33b) is swingably mounted on the pivot (33d). The input block (32) is provided with a pressure receiving bearing (33a) for receiving a governor force generated by the governor weight (33). The output block (33b) is in contact with the pressure receiving bearing (33a). When the swing of the input block (32) is not restricted, the input block (32) is greatly inclined when the governor is assembled, and the contact between the output block (33b) of the governor weight (33) and the pressure receiving bearing (33a) is made. Or when the engine is stopped, the input block (32) is greatly inclined, the contact between the output block (33b) of the governor weight (33) and the pressure receiving bearing (33a) is released, and the original contact state is restored. Since recovery may not be possible, it is necessary to limit the swing of the input block (32).

The arrangement of the fuel tank (36) and the starter motor (37) is as follows.
As shown in FIG. 3, the fuel tank (36) is arranged above the crankcase (1), and in the specific observation state, the starter motor (37) is arranged on the upper left of the crankcase (1).

The arrangement of the sub-combustion chamber (48) and the configuration of the cooling air passages (39) and (23) are as follows.
As shown in FIG. 3, a sub-combustion chamber (48) is disposed at a position closer to a high position of a cylinder head (38), and a cylinder having a high position outer peripheral surface of the cylinder (2) faces a position closer to a high position of a cylinder block. A cooling air passage (39) closer to the high place is formed, and as shown in FIG. 6, the inlet (40) of the cooling air passage (39) closer to the cylinder higher position is connected to the pressure feed terminal (42) of the fan case (41). It is facing. Further, as shown in FIG. 3, a sub-combustion chamber cooling air passage (23) having a peripheral wall of the sub-combustion chamber (48) facing the side of the sub-combustion chamber (48) is formed. As shown in FIG. The inlet (29) of the sub-combustion chamber cooling air passage (23) faces the pressure-feeding end portion (42) of the fan case (41). Further, a starter gear (43) is arranged at a position (58) deviating from a pressure feed path (57) from a pressure feed start end (56) to a pressure feed end (42) of the fan case (41). The arrow (60) in FIG. 6 indicates the rotation direction of the cooling fan (61) attached to the crankshaft (10). The pumping start end (56) of the fan case (41) is formed at a cut-off point where the gap between the peripheral side surface of the fan case (41) and the cooling fan (61) is narrowed, and the pumping end portion (42) is formed at the cut-off point. Is formed at a position where the gap between the peripheral side surface of the fan case (41) and the cooling fan (61) is widened.

The arrangement and configuration of the oil pump (45) are as follows.
As shown in FIG. 7, in the specific observation state, when the oil pump (45) is arranged near the work implement mounting portion (44) of the engine machine wall (20), as shown in FIG. The pump case (46) of 45) protrudes inside the engine machine wall (20). The pump case (46) houses a rotor (50), and the rotor (50) is driven by a rotor shaft (51). The rotor shaft (51) is interlocked with the crankshaft (10) via the governor gear (6). The engine machine wall (20) on which the pump case (46) is formed is a back cover that covers the back opening of the crankcase (1).

The configuration of a modified example of the oil pump (45) is as follows.
An oil pump (45) shown in FIG. 8 is provided with a suction passage (52) and a discharge passage (53) in an engine machine wall (20), and a pump case is provided on the engine machine wall (20) via a spacer (49). The rotor (50) is accommodated in the pump case (46), and the rotor (50) is interlocked with the rotor shaft (51). The spacer (49) has a suction port (54) and a discharge port (55). When the rotor (50) is rotated counterclockwise as shown in FIG. 8C, and when the rotor (50) is rotated clockwise as shown in FIG. ) Is installed upside down so that the same parts can be used for both rotations.

The mounting structure of the governor lever (8) to the governor holder (21) is as follows.
As shown in FIG. 5, when attaching a governor lever (18) composed of a pair of levers (18A) (18B), a governor holder (21) is attached to an engine machine wall (20), and shown in FIGS. 4 (A) and 4 (B). Thus, a pair of upper and lower pivot bosses (26A) and (26B) is provided on the governor holder (21), and a pair of upper and lower pivot bosses (26A) and (26B) is fitted with a pair of upper and lower pivots (22). Of the lever (18A) (18B), the weight of one lever (18B) is received by the lower pivot boss (26B), and the weight of the other lever (18A) is absorbed by the upper pivot boss (26A). It is received at.
As shown in FIG. 4B, the pair of levers (18A) and (18B) is a bent product obtained by bending a sheet metal into a groove shape in cross section. By placing the lower plate of one lever (18B) on the upper surface of the lower pivot boss (26B), the weight of this one lever (18B) is received by the lower pivot boss (26B). By placing the upper plate of the other lever (18A) on the upper surface of the upper pivot boss (26A), the weight of the other lever (18A) is received by the upper pivot boss (26A).
The upper plate of one lever (18B) is brought into contact with the lower surface of the upper pivot boss (26A) to prevent the one lever (18B) from shifting upward. The lower plate of the other lever (18A) is brought into contact with the lower surface of the lower pivot boss (26B) to prevent the other lever (18A) from shifting upward.
The pair of levers (18A) and (18B) can be prevented from falling off in the vertical direction only by supporting the governor holder (21) with the pivot (22) without using a circlip or the like.
As shown in FIG. 5, one lever (18B) is a governor force input lever which receives a governor force input from a governor weight (33) via an input block (32). A fuel metering rack (69) of the fuel injection pump (17) is interlocked to the governor force input lever (18B). The other lever (18A) is a spring force input lever interlockingly connected to a speed control lever (65) via a governor spring (66). The fuel limiter (67) faces the spring force input lever (18A) from the fuel increasing side, and a torque increasing device (68) is provided between the spring force input lever (18A) and the governor force input lever (18B). ) Is placed.
According to this governor, during the partial load operation, the pair of levers (18A) and (18B) swings inseparably and integrally to meter the fuel metering rack (69). The input lever (18A) comes into contact with the fuel restrictor (67), and during overload operation, the spring force input lever (18A) is received by the fuel restrictor (67) and the governor force and the torque-up force are reduced. Due to the unbalance force, only the governor force input lever (18B) swings to adjust the fuel metering rack (69), thereby suppressing engine stall.

FIG. 2 is a rear view of the inclined engine according to the embodiment of the present invention, with a rear cover removed. FIG. 2 is a sectional view taken along line II-II of FIG. 1. FIG. 2 is a longitudinal rear view of the engine of FIG. 1. FIG. 4A is an enlarged rear view of the governor lever of the engine of FIG. 1 and the periphery thereof, and FIG. 5A is a view in the direction of arrow V in FIG. 4A, and FIG. 5B is a cross-sectional bottom view of the governor. FIG. 6A is a front view of the engine with the fan case removed, and FIG. 6B is a front view of the fan case. FIG. 2 is a rear view of the engine of FIG. 1. 8 (A) is a cross-sectional plan view, FIG. 8 (B) is a cross-sectional view taken along line BB of FIG. 8 (A), and FIG. 8 (C) is a case where the rotor rotates counterclockwise. 8B is a sectional view taken along the line CC of FIG. 8B, and FIG. 8D is a view corresponding to FIG. 8C in the case of clockwise rotation.

Explanation of reference numerals

(1) Crank case, (2) Cylinder, (3) Crank shaft center axis, (4) Crank gear, (5) Valve cam gear, (6) Governor gear, (7) Oil reservoir, (8) oil, (9) cooling fin, (10) crankshaft, (11) reciprocating balancer, (12) connecting rod, (13) large end, (14) groove, (15) ): Valve operating cam shaft, (16): fuel injection cam, (17): fuel injection pump, (18): governor lever, (18A): spring force input lever, (18B): governor force input lever, (19) ... mechanical governor, (20) engine wall, (21) governor holder, (22) pivot, (23) auxiliary combustion chamber cooling air path, (24) stopper, (25) stopper pin, (26) ) ... pivot boss, (26A) ... upper pivot boss, (26B) ... lower pivot boss, (27) ... stopper pin hole, (28) ... seat, (29) ... auxiliary combustion Inlet of cooling air path (30): knock pin hole, (31): knock pin, (32): input block, (33): governor weight, (34): rod, (35): swing restriction hole, (36) ... Fuel tank, (37) ... Starter motor, (38) ... Cylinder head, (39) ... Cylinder high place cooling air path, (40) ... Cylinder high place cooling air path entrance, (41) ... Fan case , (42): end of pressure feeding, (43): starter gear, (44): mounting part of working machine, (45): oil pump, (46): pump case, (47): crank pin, (48): auxiliary Combustion chamber, (56) ... start end of pumping, (57) ... pumping path.

Claims (22)

In the inclined engine in which the cylinder (2) is projected obliquely upward from the crankcase (1),
When viewed in a direction parallel to the central axis of the crankshaft (3), in a specific observation state in which the cylinder protruding direction is the upper right, the valve gear cam gear (5) is engaged with the crank gear (4) from the right side, and the crank gear (4) is engaged. ) And a governor gear (6) arranged in a space below a meshing point of the valve gear (5), and the governor gear (6) is meshed with the valve gear (5) from the lower left thereof. Type engine. The inclined engine according to claim 1,
The lower part (2a) of the cylinder (2) projects into the crankcase (1), the outer peripheral surface of the lower part (2a) of the cylinder (2) faces the inside of the crankcase (1), and the lower part of the governor gear (6) Immerse in the oil (8) of the oil reservoir (7), arrange the upper part of the governor gear (6) above the oil (8) of the oil reservoir (7), and in the specific observation state, the upper right of the governor gear (6) A tilted engine, wherein a valve gear cam gear (5) is disposed on the engine. The inclined engine according to claim 2,
In the specific observation state, during the operation of the engine, the governor gear (6) rotates counterclockwise, and the valve gear cam gear (5) rotates clockwise. In the specific observation state, the valve gear cam gear (5) rotates. When the outer peripheral surface of the lower portion (2a) of the cylinder (2) overlaps with the outer peripheral surface of the cylinder (2) and is viewed in a direction orthogonal to the crankshaft center axis (3), the valve gear cam gear (5) is Characterized in that it is located adjacent to the outer peripheral surface of the lower part (2a) of the engine. In the inclined engine according to claim 2 or 3,
A tilt type engine, characterized in that cooling fins (9) oriented in the lateral direction are provided on the outer peripheral surface of a lower part (2a) of a cylinder (2). In the inclined engine according to any one of claims 2 to 4,
An inclined engine wherein the governor gear (6) has a smaller thickness than the valve gear (5). The inclined engine according to any one of claims 1 to 5,
The reciprocating balancer (11) is located at the lower left of the crankshaft (10) in the specific observation state. In the inclined engine according to any one of claims 1 to 6,
A part of the reciprocating balancer (11) is immersed in the oil (8) of the oil reservoir (7), and the oil (8) is jumped up when the reciprocating balancer (11) is raised. Type engine. The inclined engine according to claim 7,
A groove (14) facing the large end (13) of the connecting rod (12) is formed on the upper surface of the reciprocating balancer (11), and the groove (14) is formed between the front and back walls in the specific observation state. An inclined engine, characterized in that it is formed. The inclined engine according to any one of claims 1 to 8,
When applied to diesel engines,
A valve operating camshaft (15) is arranged in a space below a lower portion (2a) of the cylinder (2), and a fuel injection cam (16) is provided on the valve operating camshaft (15). An inclined engine, wherein a fuel injection pump (17) is arranged laterally on the right side of (16). The inclined engine according to any one of claims 1 to 9,
An inclined engine, wherein a governor lever (18) is arranged in a space below a valve operating cam shaft (15), and a part of the governor lever (18) is immersed in oil (8) of an oil reservoir (7). . The inclined engine according to claim 10,
In arranging the mechanical governor (19), a governor holder (21) is provided on the engine machine wall (20), the governor lever (18) is pivotally supported on the governor holder (21) by a pivot (22), and the governor lever (21) is mounted on the governor holder (21). The stopper (24) of (18) is provided, and the stopper (24) receives the swing (18a) of the governor lever (18) in the fuel decreasing direction, thereby defining the upper limit of the opening angle of the governor weight (33). A tilt type engine characterized by the above-mentioned. The inclined engine according to claim 11,
Using a stopper pin (25) as the stopper (24), the pivot (22) is fitted inside the pivot boss (26) of the governor holder (21), and a stopper pin hole (27) is formed in the pivot boss (26). Open the stopper pin (25) in series along the radial direction of the stopper pin hole (27) and the pivot (22), and use the stopper pin (25) to connect the pivot (22) to the pivot boss (26). And a governor lever (18) is received by a projecting portion of the stopper pin (25) from the pivot boss (26). The inclined engine according to claim 12,
A seat (28) is provided on the governor holder (21), and the governor holder (21) is attached to the engine wall (20) with the seat (28), and a knock pin hole (30) is formed in the seat (28). When positioning the governor holder (21) with respect to the engine wall (20) with the knock pin (31) driven into the knock pin hole (30),
When viewed in a direction parallel to the center axis of the stopper pin hole (27), the stopper pin hole (27) and the knock pin hole (30) overlap each other, and the stopper pin (25) inserted into the stopper pin hole (27) is inserted. ), Wherein the knock pin hole (30) is extended to a position where the knock pin hole (30) extends to the insertion end of the inclined engine, and the knock pin hole (30) communicates with the stopper pin hole (27). The inclined engine according to any one of claims 11 to 13,
The input block (32) is swingably attached to the swinging end of the governor lever (18), and governor force is transmitted from the governor weight (33) to the swinging end of the governor lever (18) via the input block (32). In doing so
A rod (34) is protruded from the input block (32), a swing limiting hole (35) is opened in the governor holder (21), and the rod (34) is inserted into the swing limiting hole (35). (32) An inclined engine in which swinging is restricted. The inclined engine according to claim 9,
An inclined engine, wherein a fuel tank (36) is disposed above the crankcase (1). The inclined engine according to any one of claims 1 to 15,
In the specific observation state, a starter motor (37) is disposed at the upper left of the crankcase (1). The inclined engine according to any one of claims 1 to 16,
An inclined engine, wherein a sub-combustion chamber (48) is arranged at a portion of the cylinder head (38) closer to a high place. The inclined engine according to any one of claims 1 to 17,
In arranging the sub-combustion chamber (48) at a position closer to the height of the cylinder head (38),
A cooling air path (39) facing the high-level outer surface of the cylinder (2) is formed in a portion closer to a high place of the cylinder block, and an inlet (40) of the cooling air path (39) is connected to a fan case (41). Characterized in that the engine faces the pressure feeding end portion (42). The inclined engine according to any one of claims 1 to 18,
In arranging the sub-combustion chamber (48) at a position closer to the height of the cylinder head (38),
A cooling air passage (23) is formed beside the sub-combustion chamber (48), a peripheral wall of the sub-combustion chamber (48) faces the cooling air passage (23), and an inlet (29) of the cooling air passage (23) is formed. ) Is directed to the terminal end (42) of the fan case (41). In the inclined engine according to claim 18 or 19,
An inclined engine, wherein a starter gear (43) is arranged at a position (58) deviating from a pressure feed path (57) from a pressure feed start end (56) to a pressure feed end (42) of the fan case (41). . The inclined engine according to any one of claims 1 to 20,
In the specific observation state, when disposing the oil pump (45) near the work implement mounting portion (44) of the engine machine wall (20),
An inclined type engine, wherein a pump case (46) of an oil pump (45) is projected inside an engine machine wall (20). The inclined engine according to any one of claims 10 to 14,
In mounting a governor lever (18) consisting of a pair of levers (18A) (18B), a governor holder (21) is provided on the engine machine wall (20), and a pair of vertical pivot bosses (26A) (26B) is provided on the governor holder (21). ), And a pair of levers (18A) and (18B) are pivotally supported by a pivot (22) whose upper and lower portions are fitted inside the pair of vertical pivot bosses (26A) and (26B). An inclined engine wherein the weight is received by a lower pivot boss (26B) and the weight of the other lever (18A) is received by an upper pivot boss (26A).

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