JP4085039B2 - Engine with mechanical governor - Google Patents

Description

  The present invention relates to an engine with a mechanical governor.

2. Description of the Related Art Conventionally, as an inclination engine, there is a type in which a governor holder is provided on an engine machine wall and a governor lever is pivotally supported by a pivot on the governor holder as in the present invention.
In this type of engine, when a governor lever composed of a pair of levers is attached, one of the levers receives the weight of the other lever.
The above prior art has the following problems.
<Problem> The metering accuracy of the governor is low.
When one lever is caused to receive the weight of the other lever, the movement of the one lever is deteriorated due to the weight, and the metering accuracy of the governor is low.

  This invention makes it a subject to provide the engine with a mechanical governor which can solve the said problem.

The invention specific matters of the main invention of claim 1 are as follows.
As shown in FIG. 4 (B), in the engine with a mechanical governor, the governor holder (21) is provided on the engine wall (20), and the governor lever (18) is pivotally supported by the pivot (22) on the governor holder (21).
When attaching the governor lever (18) comprising the pair of levers (18A) (18B), the governor holder (21) is provided with a pair of vertical pivot bosses (26A) (26B), and this pair of vertical pivot bosses (26A) ( 26B) is pivotally supported by a pair of levers (18A) and (18B) with a pivot shaft (22) fitted vertically, and the weight of one lever (18B) is received by the lower pivot boss (26B) and the other lever An engine with a mechanical governor, wherein the weight of (18A) is received by the upper pivot boss (26A).

(Invention of Claim 1)
The invention of claim 1 has the following effects.
<Effect 1> The metering accuracy of the governor is high.
As shown in FIG. 4B, the weight of one lever (18B) is received by the lower pivot boss (26B), and the weight of the other lever (18A) is received by the upper pivot boss (26A). . If the other lever (18A) is overlapped on one lever (18B) and the lower pivot boss (26B) receives the weight of both levers (18A) (18B), one lever ( 18B) becomes worse, and the metering accuracy of the governor is lowered. 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 metering accuracy of the governor is high.
(Invention of Claim 2)
In addition to the effect of the invention of claim 1, the invention of claim 2 has the following effect.
<Effect 2> Rotation hunting is unlikely to occur.
As shown in FIG. 5, the governor holder (21) is provided with a stopper (24) of the governor lever (18), and the stopper (24) receives the oscillation (18a) of the governor lever (18) in the fuel reduction direction. The upper limit of the opening angle of the governor weight (33) was defined.
When the opening angle of the governor weight (33) becomes large, the fluctuation of the governor force with respect to the fluctuation of the rotational speed becomes too large, and rotation hunting is likely to occur. Therefore, rotation hunting is unlikely to occur.

(Invention of Claim 3)
In addition to the effect of the invention of claim 2, the invention of claim 3 has the following effect.
<< Effect 3 >> The number of parts can be reduced.
As shown in FIG. 5, since 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), each dedicated function having each function is provided. The number of parts can be reduced without the need for parts.

(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 claim 3.
<Effect 4> The stopper pin can be easily removed.
As shown in FIG. 4 (A), the stopper pin hole (27) and the knock pin hole (30) are overlapped when viewed in a direction parallel to the central axis of the stopper pin hole (27). As shown in 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), and the knock pin hole (30) and the stopper pin hole ( 27), when the mechanical governor (19) is disassembled and repaired, the stopper pin is removed with a thin tool inserted from the knock pin hole (30) after removing the knock pin (31) from the knock pin hole (30). By pushing the insertion end of (25), the stopper pin (25) can be easily removed.
<< Effect 5 >> Drilling becomes easy.
As shown in FIG. 4A, the stopper pin hole (27) and the knock pin hole (30) are overlapped when viewed in a direction parallel to the central axis of the stopper pin hole (27). 27) and the dowel pin hole (30) can be aligned in common, and in this case, the hole processing is facilitated.

(Invention of Claim 5)
The invention of claim 5 has the following effects in addition to the effects of any one of claims 1 to 4.
<< Effect 6 >> The number of parts can be reduced.
As shown in FIG. 5, the rod (34) is projected from the input block (32), the swing limit hole (35) is opened in the governor holder (21), and the rod (34) is inserted into the swing limit hole (35). Thus, since the swing of the input block (32) is limited, the governor holder (21) also functions as the swing limit function of the input block (32). For this reason, a dedicated component having a swing limiting function is not required, and the number of components can be reduced.

(Invention of Claim 6)
The invention of claim 6 has the following effects in addition to the effects of any one of claims 1 to 5.
<< Effect 6 >> Oil deterioration can be suppressed.
As shown in FIG. 1, since the reciprocating balancer (11) is positioned at the lower left of the crankshaft (10) in the specific observation state, the oil (8) in the oil reservoir (7) of the reciprocating balancer (11) is shown. ) Or the reciprocating balancer (11) is not immersed, and the reciprocating balancer (11) can avoid stirring the oil (8) more than necessary, and the oil (8) is deteriorated. Can be suppressed.

(Invention of Claim 7)
In addition to the effect of the invention of claim 6, the invention of claim 7 has the following effect.
<Effect 7> The height of the engine can be reduced.
As shown in FIG. 1, a valve camshaft (15) is arranged in a space below a lower part (2a) of a cylinder (2), and a fuel injection cam (16) is provided on the valve camshaft (15). In the observation state, since the fuel injection pump (17) is disposed laterally on the right side of the fuel injection cam (16), the valve camshaft (15 ), The fuel injection cam (16), and the fuel injection pump (17) can be accommodated in a compact manner. For this reason, the height of the engine can be reduced.

Embodiments of the present invention will be described with reference to the drawings.
FIGS. 1-7 is a figure explaining the inclination type engine which concerns on embodiment of this invention.
In this embodiment, a single-cylinder tilt type diesel engine will be described.

The outline of this embodiment is as follows.
As shown in FIG. 3, 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. Further, the arrangement of the reciprocating balancer (11) is devised to lubricate the crankcase (1), and as shown in FIGS. 3 to 5, the fuel injection pump (17) and the governor lever (18) are arranged. As shown in FIG. 3, the fuel tank (36) is arranged to secure the fuel capacity as shown in FIG. 3, and the starter motor (37) is arranged as shown in FIG. As shown in FIG. 3, the weight balance is achieved, and the arrangement of the auxiliary combustion chamber (48) increases the durability of the peripheral parts of the auxiliary combustion chamber (48). As shown in FIG. The auxiliary combustion chamber (48) and its surroundings are cooled by (39) and 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 protruded obliquely upward from the crankcase (1), and viewed in a direction parallel to the crankshaft central axis (3). The valve gear cam (5) is meshed with the crank gear (4) from the right side, and the governor gear (6) is arranged in the space below the meshing position between the crank gear (4) and the valve gear cam gear (5). (6) is meshed with the valve cam gear (5) from the lower left.

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) protrudes into the crankcase (1), the outer peripheral surface of the lower part (2a) of the cylinder (2) faces 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 on the upper right of the governor gear (6).

  Further, as shown in FIG. 1, the governor gear (6) rotates counterclockwise and the valve cam gear (5) rotates clockwise while the engine is operating in the specific observation state. Thus, the valve cam gear (5) and the outer peripheral surface of the lower part (2a) of the cylinder (2) are arranged at positions where they overlap each other, and are orthogonal to the crankshaft center axis (3) as shown in FIG. The valve cam gear (5) is positioned adjacent to the outer peripheral surface of the lower part (2a) of the cylinder (2) when viewed in the direction. Cooling fins (9) oriented in the lateral direction are provided on the outer peripheral surface of the lower part (2a) of the cylinder (2). Further, as shown in FIG. 2, the governor gear (6) is made thinner than the valve operating cam 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 positioned at the lower left of the crankshaft (10), and a part of the reciprocating balancer (11) is placed 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, and in the specific observation state, a groove (14) is formed between the front and back walls. As shown in FIG. 1, the reciprocating balancer (11) is linked to the crankshaft (10) via the linkage arm (62), and the pivot point (63) on the crankshaft (10) side of the linkage arm (62). Is eccentric from the center axis (3) of the crankshaft. 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 raising and lowering of the piston (64). I am doing so.

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

The configuration of the governor holder (21) for supporting the governor lever (18) is as follows.
As shown in FIG. 5, in arranging the mechanical governor (19), the governor holder (21) is attached to the engine machine wall (20), and the governor lever (18) is pivotally supported by the pivot (22) on the governor holder (21). The governor holder (21) is provided with a stopper (24) for the governor lever (18), and the stopper (24) receives the swing (18a) in the fuel decreasing direction of the governor lever (18), 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 the front wall of the crankcase (1). A stopper pin (25) is used as the stopper (24), and the pivot (22) is fitted into the pivot boss (26) of the governor holder (21), and the stopper pin hole (27) is formed in the pivot boss (26). A stopper pin (25) is inserted in series along the radial direction of the stopper pin hole (27) and the pivot (22), and the pivot (22) is inserted into the pivot boss (26) with the stopper pin (25). The governor lever (18) is received by the protruding 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 seating portion (28), and the seating portion (28) attaches the governor holder (21) to the engine machine wall (20). 28), a knock pin hole (30) is formed, and the position of the governor holder (21) with respect to the engine machine wall (20) by the knock pin (31) driven into the knock pin hole (30) is shown in FIG. As seen in the direction parallel to the central axis of the stopper pin hole (27), the stopper pin hole (27) and the knock pin hole (30) are overlapped with each other, and FIGS. ), The knock pin hole (30) and the stopper pin hole (27) are extended to the position where the stopper pin (25) inserted into the stopper pin hole (27) reaches the insertion end. And communicate with each other.

  As shown in FIG. 5 (B), the input block (32) is swingably attached to the swing end of the governor lever (18), and the governor lever (18) is connected from the governor weight (33) through the input block (32). When transmitting the governor force to the swing end of the rod, the rod (34) protrudes from the input block (32), the swing limit hole (35) is opened in the governor holder (21), and the swing limit hole (35) By inserting the rod (34) into the shaft, the swing of the input block (32) is limited. 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 shaft (32a) is provided at the pivot end of the governor lever (18), and the pivot block (32a) pivotally supports the input block (32). The governor gear (6) is provided with a pivot (33c), and the pivot (33c) pivotally supports the governor weight (33). The governor weight (33) is provided with a pivot (33d), and the output block (33b) is swingably attached to the pivot (33d). A pressure receiving bearing (33a) for receiving the governor force generated by the governor weight (33) is attached to the input block (32). The output block (33b) is brought into contact with the pressure receiving bearing (33a). When the swing of the input block (32) is not limited, the input block (32) is largely inclined when the governor is assembled, and the output block (33b) of the governor weight (33) and the pressure receiving bearing (33a) are in contact with each other. When the engine is stopped, the input block (32) is greatly inclined, and 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 maintained. 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 disposed above the crankcase (1), and the starter motor (37) is disposed at the upper left of the crankcase (1) in the specific observation state.

The arrangement of the auxiliary combustion chamber (48) and the configuration of the cooling air passages (39), (23) are as follows.
As shown in FIG. 3, the auxiliary combustion chamber (48) is arranged near the high part of the cylinder head (38), and the outer peripheral surface of the high part of the cylinder (2) faces the high part of the cylinder (2). As shown in FIG. 6, an inlet (40) of the cylinder high-position cooling air passage (39) is connected to the pressure-feed end portion (40) of the fan case (41). 42). Further, as shown in FIG. 3, a sub-combustion chamber cooling air passage (23) is formed on the side of the sub-combustion chamber (48) so that the peripheral wall of the sub-combustion chamber (48) faces, and as shown in FIG. The inlet (29) of the sub-combustion chamber cooling air passage (23) faces the pumping end (42) of the fan case (41). Further, the starter gear (43) is arranged at a position (58) deviated from the pressure feed path (57) from the pressure feed start end portion (56) to the pressure feed end portion (42) of the fan case (41). The arrow (60) in FIG. 6 shows the rotation direction of the cooling fan (61) attached to the crankshaft (10). The pressure feed start end portion (56) of the fan case (41) is formed at a closing point where the gap between the peripheral side surface of the fan case (41) and the cooling fan (61) becomes narrow, and the pressure feed end portion (42) is formed at the closing point. Is formed at a position where the gap between the peripheral side surface of the fan case (41) and the cooling fan (61) becomes wide.

The arrangement and configuration of the oil pump (45) are as follows.
As shown in FIG. 7, when the oil pump (45) is disposed near the work machine mounting portion (44) of the engine machine wall (20) in the specific observation state, as shown in FIG. 45) is protruded inside the engine machine wall (20). A rotor (50) is accommodated in the pump case (46), 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) in which the pump case (46) is formed is a back cover that covers the back opening of the crankcase (1).

The configuration of the modified example of the oil pump (45) is as follows.
The oil pump (45) shown in FIG. 8 is provided with a suction passage (52) and a discharge passage (53) in the engine machine wall (20), and a pump case is provided on the engine machine wall (20) via a spacer (49). (46) is attached, the rotor (50) is accommodated in the pump case (46), and this rotor (50) is interlocked by the rotor shaft (51). The spacer (49) includes a suction port (54) and a discharge port (55). When the rotor (50) is rotated counterclockwise as shown in FIG. 8 (C) and when the rotor (50) is rotated clockwise as shown in FIG. 8 (D), the spacer (49 ) Can be used for both rotations with the same parts.

The attachment structure of the governor lever (8) to the governor holder (21) is as follows.
As shown in FIG. 5, in attaching the governor lever (18) composed of a pair of levers (18A) and (18B), the governor holder (21) is attached to the engine machine wall (20) and shown in FIGS. 4 (A) and (B). As described above, the governor holder (21) is provided with a pair of vertical pivot bosses (26A) (26B), and a pair of pivots (22) with upper and lower portions fitted into the pair of vertical pivot bosses (26A) (26B). The lever (18A) (18B) is pivoted, the weight of one lever (18B) is received by the lower pivot boss (26B), and the weight of the other lever (18A) is pivoted by the upper pivot boss (26A). I take it in.
As shown in FIG. 4 (B), the pair of levers (18A) (18B) is a bent product obtained by bending a sheet metal into a cross-sectional groove shape. By placing the lower plate of one lever (18B) on the upper surface of the lower pivot boss (26B), the weight of the 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).
By causing the upper plate of one lever (18B) to come into contact with the lower surface of the upper pivot boss (26A), upward displacement of the one lever (18B) is prevented. By causing the lower plate of the other lever (18A) to contact the lower surface of the lower pivot boss (26B), the other lever (18A) is prevented from shifting upward.
The pair of levers (18A) and (18B) can be prevented from coming 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 that receives the governor force input from the governor weight (33) via the input block (32). A fuel metering rack (69) of the fuel injection pump (17) is linked to the governor force input lever (18B). The other lever (18A) is a spring force input lever linked to the governing lever (65) via a governor spring (66). The spring force input lever (18A) is exposed to the fuel limiter (67) from the fuel increase side, and between the spring force input lever (18A) and the governor force input lever (18B), a torque increase device (68 ).
According to this governor, at the time of partial load operation, the pair of levers (18A) (18B) swings in an integral manner to meter the fuel metering rack (69), and at rated load operation, the spring force When the input lever (18A) is in contact with the fuel limiter (67) and overloaded, the spring force input lever (18A) is received by the fuel limiter (67) and the governor force and torque-up force are reduced. Due to the unbalanced force, only the governor force input lever (18B) swings, and the fuel metering rack (69) is metered to suppress the engine stall.

It is the rear view which removed the back cover of the inclination type engine which concerns on embodiment of this invention. It is the II-II sectional view taken on the line of FIG. It is a vertical rear view of the engine of FIG. 4A is an enlarged rear view of the governor lever of the engine of FIG. 1 and its surroundings, and FIG. 4B is a sectional view taken along line BB of FIG. 4A. 5A is a view in the direction of the arrow V in FIG. 4A, and FIG. 5B is a transverse 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. It is a rear view of the engine of FIG. FIG. 8A is a cross-sectional plan view, FIG. 8B is a cross-sectional view taken along line BB of FIG. 8A, and FIG. 8C is a counterclockwise rotation of the rotor. FIG. 8B is a cross-sectional view taken along the line CC in FIG. 8B, and FIG. 8D is a view corresponding to FIG.

Explanation of symbols

(1) ... Crankcase, (2) ... Cylinder, (3) ... Crankshaft center axis, (4) ... Crank gear, (5) ... Valve cam gear, (6) ... Governor gear, (7) ... Oil sump, (8) ... Oil, (9) ... Cooling fin, (10) ... Crankshaft, (11) ... Reciprocating balancer, (12) ... Connecting rod, (13) ... Large end, (14) ... Groove, (15 ) ... Valve camshaft, (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 machine wall, (21) ... governor holder, (22) ... pivot, (23) ... subcombustion chamber cooling air passage, (24) ... stopper, (25) ... stopper pin, (26 ) ... Pivot boss, (26A) ... Upper pivot boss, (26B) ... Lower pivot boss, (27) ... Stopper pin hole, (28) ... Sitting part, (29) ... Sub-combustion Cooling air passage inlet (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) ... Cooling air passage near the cylinder height, (40) ... Entrance to the cooling air passage near the cylinder height, (41) ... Fan case , (42) ... pressure-feed end, (43) ... starter gear, (44) ... work implement mounting part, (45) ... oil pump, (46) ... pump case, (47) ... crankpin, (48) ... sub Combustion chamber, (56) ... pressure feed start end, (57) ... pressure feed path.

Claims (7)

In an engine with a mechanical governor in which a governor holder (21) is provided on an engine machine wall (20) and a governor lever (18) is pivotally supported by a pivot (22) on the governor holder (21).
When attaching the governor lever (18) comprising the pair of levers (18A) (18B), the governor holder (21) is provided with a pair of vertical pivot bosses (26A) (26B), and this pair of vertical pivot bosses (26A) ( 26B), a pair of levers (18A) (18B) is pivotally supported by a pivot (22) in which upper and lower portions are fitted, and the weight of one lever (18B) is received by a lower pivot boss (26B). An engine with a mechanical governor, wherein the weight of the lever (18A) is received by the upper pivot boss (26A). The engine with a mechanical governor according to claim 1,
The governor holder (21) is provided with a stopper (24) of the governor lever (18), and the stopper (24) receives the swing (18a) of the governor lever (18) in the fuel reduction direction, thereby opening the governor weight (33). An engine with a mechanical governor characterized by defining an upper limit of the angle. The engine with a mechanical governor according to claim 2,
A stopper pin (25) is used as the stopper (24), and the pivot (22) is fitted into the pivot boss (26) of the governor holder (21), and the stopper pin hole (27) is formed in the pivot boss (26). A stopper pin (25) is inserted in series along the radial direction of the stopper pin hole (27) and the pivot (22), and the pivot (22) is inserted into the pivot boss (26) with the stopper pin (25). An engine with a mechanical governor characterized in that the governor lever (18) is received by the protruding portion of the stopper pin (25) from the pivot boss (26). The engine with a mechanical governor according to claim 2 or claim 3,
A seating portion (28) is provided in the governor holder (21), and the governor holder (21) is attached to the engine machine wall (20) by the seating portion (28), and a knock pin hole (30) is formed in the seating portion (28). In positioning the governor holder (21) with respect to the engine machine wall (20) with the knock pin (31) driven into the knock pin hole (30),
When viewed in a direction parallel to the central axis of the stopper pin hole (27), the stopper pin hole (27) and the knock pin hole (30) are overlapped with each other and inserted into the stopper pin hole (27) (25 The engine with a mechanical governor is characterized in that the knock pin hole (30) is extended to a position reaching the insertion end of), and the knock pin hole (30) and the stopper pin hole (27) are communicated. The engine with a mechanical governor according to any one of claims 1 to 4,
The input block (32) is swingably attached to the swing end of the governor lever (18), and the governor force is transmitted from the governor weight (33) to the swing end of the governor lever (18) through the input block (32). In doing so,
The rod (34) protrudes from the input block (32), the swing limit hole (35) is opened in the governor holder (21), and the rod (34) is inserted into the swing limit hole (35). An engine with a mechanical governor, characterized in that the swinging of (32) is limited. The engine with a mechanical governor according to any one of claims 1 to 5,
When applied to an inclined engine in which the cylinder (2) protrudes obliquely upward from the crankcase (1),
The reciprocating balancer (11) is positioned at the lower left of the crankshaft (10) in a specific observation state with the cylinder protruding direction at the upper right when viewed in a direction parallel to the crankshaft central axis (3). Features an engine with mechanical governor. The engine with a mechanical governor according to claim 6,
A valve drive cam shaft (15) is disposed in a lower space (2a) of the cylinder (2), and a fuel injection cam (16) is provided on the valve drive cam shaft (15). An engine with a mechanical governor, characterized in that a fuel injection pump (17) is disposed sideways on the right side of (16).

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