JP3039884B2 - Hydraulic power unit engine - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a variable displacement axial hydraulic pump for supplying hydraulic oil to a traveling hydraulic motor in a crawler traveling device or a working vehicle for driving a traveling wheel, which comprises a traveling hydraulic motor as a traveling device. And a hydraulic power unit engine integrally comprising:

[0002]

2. Description of the Related Art Conventionally, a technique in which a variable displacement axial hydraulic pump is disposed outside a crankcase is known. For example, JP-A-62-20960, JP-A-63-305042,
Such techniques are described in JP-A-210657 and JP-B-61-23411. As shown in FIG. 24, a pump case 71 is provided on the flywheel cover 70 of the engine, a port block 72 is provided on the pump case 71, and a charge pump 73 and other operating members are provided at the tip of the port block 72. A technique provided with an oil pump 74 is also known.

[0003]

According to the present invention, a pump case 71, a port block 72, and a charge pump 73 are attached to a flywheel cover 70 by connecting the pump case 71, a port block 72, and a charge pump 73, as in a conventional hydraulic power unit engine shown in FIG. In order to solve this problem, the crankshaft of the engine was used to solve this problem, because the total length of the hydraulic power unit engine became longer and the engine room of the working vehicle such as the backhoe and front dozer became too large. The variable displacement axial hydraulic pump is arranged in parallel with the crankshaft 4 instead of extending the portion of the variable displacement axial hydraulic pump serially connected to the crankshaft 4. As a result, the variable displacement axial hydraulic pump can be housed and arranged within the length of the engine E, so that the engine room of the working vehicle equipped with the hydraulic power unit engine can be made compact.

[0004]

The problems to be solved by the present invention are as described above. Next, means for solving the problems will be described. According to the first aspect, an oil-fuel ratio of a vertical multi-cylinder engine
Built-in variable displacement axial hydraulic pump in Lupine
And a pump constituting the variable displacement axial hydraulic pump.
Pump room R, port block 1, and pump drive unit are arranged in series
And placed parallel to the lower part of the crankshaft 4
And one end of a pump shaft 2 that constitutes the pump drive unit.
Gear 13 is provided, and the pump gear 13 is
Injection pump or crankshaft 4 for driving camshaft
Mesh directly or indirectly with the upper crank gear 11,
The pump chamber R is formed integrally with the oil pan 3 .

[0005] In the second aspect, the hydraulic pressure according to the first aspect is provided.
In the power unit engine, the pump shaft 2 is bearing-supported by an oil pan cover 25 provided on the side wall of the oil pan 3 and a charge pump 9 is mounted on the oil pan cover 25.
Is provided.

According to a third aspect, the hydraulic pressure according to the first aspect is provided.
In the power unit engine, an idle gear 12 is provided between the crank gear 11 and the pump gear 13, and an idle gear shaft 14 that supports and supports the idle gear 12 is provided.
This is supported by the port block 1.

According to a fourth aspect, the hydraulic pressure according to the first aspect is provided.
In the power unit engine, the pump chamber R is isolated from the lubricating oil pool of the oil pan 3, and the volume of the lubricating oil capacity for the pump chamber R is reduced outside the mounting bolt of the oil pan 3 to the cylinder block 5. It was protruding and refilled.

[0008] In the fifth aspect, the hydraulic pressure according to the first aspect is provided.
In the power unit engine, the port block 1 is provided on one side of the pump chamber R, and the mounting surface 3 of the port block 1 is provided.
The bearing mounting seat 3i is opened on the side of the pump chamber R opposite to the port block 1,
A bearing hole 3e larger than the bearing mounting seat 3i is opened in the oil pan 3 on the side opposite to the bearing mounting seat 3i.

In claim 6, the hydraulic pressure according to claim 5 is provided.
In the power unit engine, an oil pan cover 25 is attached to the seat surface processing hole 3e, and the bearing of the pump shaft 2 is supported by the oil pan cover 25.

[0010] In claim 7, the hydraulic pressure according to claim 1 is provided.
In the power unit engine, the port block 1 is disposed inside the oil pan 3, and the main hydraulic couplings 22 and 23 project from the port block 1 to the outside of the oil pan 3,
The main hydraulic joints 22 and 23 are supported in an oil-tight state by the side opening 3h of the oil pan 3.

According to an eighth aspect, the hydraulic pressure according to the first aspect is provided.
In the power unit engine, an assembling opening for assembling the variable displacement axial hydraulic pump into the pump chamber R is provided in the upper and lower portions of the oil pan 3, and a cooling and reinforcing rib is provided on a lid closing the assembling opening. 26a.

According to a ninth aspect, the hydraulic pressure according to the first aspect is provided.
In the power unit engine, the tilting swash plate 6 disposed in the pump chamber R is configured to be operated by four tilting cylinders 7, and a neutral return spring 36 is provided between the tilting cylinder 7 and the tilting piston 7a. And the tilting swash plate 6 is returned to the neutral position by the neutral return spring 36 when in the neutral position.

According to a tenth aspect, the oil according to the ninth aspect is provided.
In the pressure power unit engine, in the tilting swash plate 6 operated by the tilting cylinder 7, neutral position adjusting bolts 28 and 29 for adjusting the neutral position of the tilting swash plate 6 are supported by the port block 1 to adjust the neutral position. Bolts 28 and 29
The oil pan cover 25 can be adjusted through the seat surface processing hole 3e from which the oil pan cover 25 has been removed.

In the eleventh aspect, the oil according to the ninth aspect is provided.
In the pressure power unit engine, a servo cylinder 16 for operating the tilting swash plate 6 is supported on the side of the oil pan 3,
The Y-arm 18 is rotated by the piston 16c in the servo cylinder, and the tilt cylinder operation valves 10 provided at the tip of the Y-arm 18 are moved to the position detecting plate 1 of the tilt swash plate 6.
7

[0015] In the twelfth aspect, the oil according to the third aspect.
In the pressure power unit engine, a gear cover that covers the periphery of the idle gear 12 and the pump gear 13 is disposed so as to be immersed in lubricating oil.

[0016]

Since the present invention is constructed as described above, the following operations are performed. That is, with the rotation of the crankshaft 4 of the engine, the pump gear 13 is rotated from the crank gear 11 via the idle gear 12. Since the pump gear 13 is fixed to the pump shaft 2, the pump shaft 2 rotates, and the spline 2 a of the pump shaft 2 is engaged with the plunger case 8. I do. Nine plungers 19 are fitted into the plunger case 8, and the plunger 19 rotates while moving forward and backward with the tip of the plunger 19 abutting on the tilting swash plate 6. The hydraulic oil in the tank is discharged under pressure in the forward or reverse direction. The pressure oil is supplied from the main hydraulic couplings 22 and 23 to the hydraulic oil pipe 42.
, And is supplied to a traveling hydraulic motor of a crawler type traveling device or a wheel type traveling device portion.

[0017]

Next, embodiments of the present invention will be described. FIG. 1 is a perspective side view showing a crankshaft 4 and a variable displacement axial hydraulic pump of a hydraulic power unit engine. FIG. 2 is an overhead perspective view of the oil pan 3 and the crankshaft 4.
FIG. 4 is a side sectional view of a portion of an oil pan 3 and a variable displacement axial hydraulic pump. FIG. 4 is a plan sectional view of a portion of a plunger case 8, a port block 1, main hydraulic joints 22 and 23, and a hydraulic oil pipe 42. FIG. 6 is a front sectional view of a portion of the port block 1 and the main hydraulic couplings 22 and 23. FIG. 6 is a plan view showing a portion of the oil pan 3 and the servo cylinder 16.
7 is a side sectional view of a portion of the servo cylinder 16, FIG. 8 is a front sectional view of a portion of the pump chamber R and the servo cylinder 16,
FIG. 9 is a front sectional view of the crank gear 11, the idle gear 12, and the pump gear 13.

FIG. 10 is a side sectional view of a portion of the pump shaft 2 and the port block 1, FIG. 11 is a plan sectional view of a portion of the pivot oil passage shaft 38 of the Y-type arm 18, and FIG. 12 is a neutral position adjusting bolt 28. 29 is a cross-sectional plan view of a portion of the port block 1 and 29.
FIG. 13 shows the main hydraulic joints 22 and 23 and the hydraulic oil pipe 42.
, FIG. 14 is a partial cross-sectional view of the oil pan 3, FIG. 15 is a side cross-sectional view of the oil pan 3, and FIG.
6 is a side sectional view showing an open state of each part of the oil pan 3,
17 is a sectional view of the oil pan 3 at the pivot oil passage shaft 38, FIG. 18 is a front view of the oil pan 3, FIG. 19 is a side view of the oil pan 3 on the side of the servo cylinder 16, and FIG. FIG. 21 is a bottom view of the lower cover 26a, and FIG.
1, FIG. 22 is a side sectional view of the gear covers 40 and 41, FIG. 23 is a front view of the same, and FIG. 24 is a side view of a conventional hydraulic power unit engine.

In FIG. 1, a crankshaft 4 is disposed inside a cylinder block 5 so as to be horizontally supported and supported. At an end of the crankshaft 4, a crank gear 11 for driving a camshaft and an engine fuel injection pump is engraved. The crank gear 11 has a po
Meshes with an idle gear 12 which is supported by idle gear shaft 14 that is attached to over heat block 1. The idle gear shaft 14 meshes with the pump gear 13 on the pump shaft 2. The pump chamber R constituting the variable displacement axial hydraulic pump is formed integrally with the oil pan 3.

In FIG. 2, the configurations of the oil pan 3 and the variable displacement axial hydraulic pump are shown as a bird's-eye view. The oil pan 3 protrudes laterally beyond the position of the mounting bolt 3g to the cylinder block 5 to form a capacity increasing portion 3f. At the upper part of the pump chamber R, an assembling opening 3d for allowing the plunger case 8, the plunger 19, the tilting swash plate 6, and the like to be inserted is opened. Covered by An assembly opening 3c is also opened in the oil pan 3 below the pump chamber R, and a lid 26 with a cooling / reinforcing rib 26a is attached to this portion. An oil pan cover 25 is disposed at a portion where the pump shaft 2 protrudes toward the front side. The oil pan cover 25 supports a bearing of the pump shaft 2, and the outer surface thereof is a mounting surface of the charge pump 9. Make up. The opening on the left side of the pump chamber R is closed by a servo cylinder mounting cover 39, and the servo cylinder 16 is attached thereto.

In FIG. 3, a bearing of the pump shaft 2 is supported on an oil pan cover 25, and a charge pump 9 is further provided on the outer surface. The operating oil is pressurized by the charge pump 9 and supplied to the charge pressure oil supply joints 47 and 48 shown in FIG. 5 through pipes. Supply oil is supplied to the charge ports 1a. Pump shaft 2 bearing on port block 1
The plunger case 8 is engaged with the portion protruding into the pump chamber R via the spline 2a, and the plunger 19 is inserted into nine plunger holes of the plunger case 8. When the plunger case 8 rotates with the other end of the plunger 19 in contact with the tilting swash plate 6, the plunger 19 moves out, so that forward or backward pressure oil is supplied to the traveling hydraulic motor. Because The other end of the pump shaft 2 is supported by a bearing 27 supported on the bearing mounting seat 3i.

Assembly openings 3d and 3c are provided above and below the pump chamber R integrated with the oil pan 3, and lids 24 and 26 are respectively attached thereto. Next, in FIGS. 4, 5 and 13, the main hydraulic couplings 2 and 2
3 will be described. The variable displacement axial hydraulic pump and a port block 1 disposed within the oil pan 3, the main hydraulic couplings 22 and 23 from the interior of the oil pan 3, and to release the pressure oil to the outside of the oil pan 3
I have . A configuration for its, by the side wall portion <br/> port block 1 projects the Increment in hydraulic couplings 22 and 23, the main hydraulic
The ends of the joints 22 and 23 are supported in an oil-tight state by a lid 45, and the lid 45 is an opening formed on the side of the oil pan 3.
3h is closed .

The main hydraulic joints 22 and 23 are composed of two pipes which have a high pressure when moving forward and a high pressure when moving backward. An O-ring is interposed on the outer periphery of the main hydraulic joints 22 and 23, and the space between the main hydraulic joints 22 and 23 and the lid 45 are oil-tight.
Then, it is sandwiched between front and rear portions of the main hydraulic joints 22 and 23 outside the lid 45 by split fasteners 44 and 43, and the split fasteners 44 and 43 are formed by grooves 2 of the main hydraulic joints 22 and 23.
2a is engaged to prevent slippage. The split body 44.4
The joint body 20 is provided outside the joint 3, and the joint body 20 is fixed to the split clamps 44 and 43 by bolts 46. The hydraulic oil pipe 42 projects from the joint body 20. The joint body 20 is paired with the lower part 21. Split body 44
Reference numeral 43 integrates the two main hydraulic joints 22 and 23 and fixes the joint bodies 20 and 21 to the outside thereof.

As shown in FIGS. 4 and 5, tilting cylinders 7 are arranged at four positions, up, down, left and right, of a wall constituting the pump chamber R of the oil pan 3. The tilt cylinders 7 move in and out of the two left and right cylinders, respectively, to tilt the tilt swash plate 6. As shown in FIG. 5, charge pressure oil supply joints 47 and 48 are arranged on the side surface, and pressure oil from the charge pump 9 is supplied to the port block 1 via a pipe. FIG. 6 discloses a planar state of the oil pan 3. The servo cylinder 16 is attached to a servo cylinder mounting lid 39, and the line filter 15 is similarly attached to the servo cylinder mounting lid 39.

A tilting swash plate 6 is inserted vertically into a pump chamber R integrally formed with the oil pan 3.
The tilting swash plate 6 tilts left and right forward and backward. A position detection plate 17 protrudes from the tilting swash plate 6,
The Y-shaped arm 1 is held so as to sandwich the position detecting plate 17 from front and rear.
The tilt cylinder operation valves 10 fixed to 8 are in contact with each other. The operator rotates the operation lever of the operation operation column, thereby electrically switching the servo cylinder 16 in some cases, hydraulic pressure in some cases, and automatic hydraulic pressure in engine rotation detection in some cases. It is.

Instead of the servo cylinder pistons 16a and 16b directly operating the tilting swash plate 6, first, the pistons 16a and 16b of the servo cylinder 16 use the pistons 16a and 16b of FIG.
As shown in FIG. 8 , the servo cylinder 16
The upper arm of the Y-type arm 18 between the stones 16a and 16b.
When the tip of the arm 18a is engaged, the upper arm 18a of the Y-shaped arm 18 is rotated, and the tilt cylinder operation valves 10 at the lower end of the Y-shaped arm 18 move back and forth, the position detecting plate 17 Does not move in the original position, the tilt cylinder operation valves 10 are switched, and pressurized oil is supplied to the tilt cylinder 7. Only when the pressure oil is supplied to the tilt cylinder 7 does the tilt piston 7a in the tilt cylinder 7 move in and out, the tilt swash plate 6 rotates, and the position detecting plate 17 moves. When the position detecting plate 17 moves to a desired position, both the tilt cylinder operation valves 10 return to the neutral position, the ingress and egress of the tilt cylinder 7 stop, and the position of the tilt swash plate 6 is determined. Because

Then, as shown in FIG.
Is pivotally fitted between the wall of the pump chamber R and the wall of the servo cylinder mounting cover 39, and the pump chamber R is The oil passage in the wall of R communicates with the oil passage, and the oil passage further communicates with the tilting cylinder operation valve 10 at the tip of the Y-shaped arm 18 through an oil passage formed inside the Y-shaped arm 18. -ing The pressure oil after control is supplied to the four tilt cylinders 7 through the oil passage in the Y-shaped arm 18, the oil passage in the pivot oil passage shaft 38, and the oil passage in the wall of the pump chamber R. It is done. The oil passage in the wall of the pump chamber R is disclosed as a sectional view in FIGS. 8, 11 and 14.

FIG. 9 shows the positional relationship among the crankshaft 4, the idle gear shaft 14, and the pump shaft 2. FIG. 10 shows a state in which an idle gear shaft 14 that supports the idle gear 12 is supported by the port block 1. In FIG. 11, the shape of the tilt cylinder 7 and the pump chamber R reaching the tilt cylinder 7 are shown.
And an oil passage drilled inside the pivot oil passage shaft 38 are disclosed. The pivot oil passage shaft 38 is formed as a swivel joint, and communicates with the oil passage of the Y-shaped arm 18.

FIG. 12 shows the structure of the neutral position adjusting bolts 28 and 29 for adjusting the neutral position of the tilting swash plate 6. When the variable displacement axial hydraulic pump is in the neutral state, all the pressure oil to the tilt cylinder 7 is released to the drain circuit.
As a result, the left and right sides of the tilting swash plate 6 are pushed with substantially the same load and return to the neutral position. If the neutral position is shifted,
They move forward or backward at the position where they should stop. Therefore, in a state where the pressure oil has been drained from the tilting cylinder 7, the neutral determination piston 3 that operates at the neutral position
The neutral determination pistons 34 and 35 are constantly pressed by the biasing springs 37. The biasing spring 3
7 and 37 spring chambers 30 and 33
The neutral position of the tilting swash plate 6 is determined by changing the pressing amount according to 8.29.

Since the neutral position adjusting bolts 28 and 29 are provided with the driver engaging grooves by removing the cap nuts 31 and 32, they can be adjusted by inserting a driver. In FIG. 12, when the tilting cylinder 7 and the tilting piston 7a and the tilting piston 7a
A neutral return spring 36 that neutralizes the tilting swash plate 6 when all the tilting pistons 7a press it is provided.

FIG. 14 shows a plan view of the oil pan 3. A drilling oil passage for supplying pressure oil after control to the tilt cylinder 7 from the portion of the Y-shaped arm 18 and the tilt cylinder operation valves 10 and 10 is provided on a wall constituting the pump chamber R. Also, the mounting bolt position of the oil pan 3 is 3g.
A capacity increasing portion 3f is provided outside the opening, and an opening 3h is provided in the capacity increasing portion 3f. In addition, a seat surface machining hole 3e is provided on the rear surface side of the oil pan 3 so that a bearing mounting seat 3i in which the bearing 27 for bearing the pump shaft 2 in the pump chamber R is fitted can be machined (FIGS. 3 and 15). ) .

FIGS. 15 and 16 show sectional views of a part of the pump chamber R integrated with the oil pan 3. Reference numeral 3b denotes a passage hole of the main hydraulic couplings 22 and 23 which receives the pressure oil from the variable displacement axial hydraulic pump. 17 and 18 are a front sectional view and a front view of the oil pan 3. The seat surface processing hole 3e is largely open for processing the attachment surface 3j for fixing the port block 1. In order to machine the bearing mounting seat 3i, a seating hole 3e on the rear surface is formed.
Is also large.

As shown in FIGS. 17 and 19, a shaft hole 3k into which the pivot oil passage shaft 38 is fitted is provided. It is configured such that pressure oil is passed from the oil passage in the shaft hole 3k to the oil passage in the pivot oil passage shaft 38. FIG. 20 shows the assembly opening 3c.
The lid 26 is formed by forming a cooling and reinforcing rib 26a for reinforcing the strength of the portion of the pump chamber R and for releasing the light heat generated inside the pump chamber R. Provided.

In FIGS. 22 and 23, the pump gear 1
Gear covers 40 and 41 for covering the outer periphery of the idle gear 12 and the idle gear 12 so that the gear does not entrain the lubricating oil inside the oil pan 3 are shown.
Since the idle gear 12 and the pump gear 13 are immersed in the lubricating oil of the oil pan 3, if they are rotated freely, a large flow of the lubricating oil is generated, and the power loss and heat loss increase. is there. In the present invention, the idle gear 12 and the pump gear 13 are covered with the gear covers 40 and 41, and only the lubricating oil inside the cover is moved together with the gears. FIG. 21 shows a gear cover 40 around the idle gear 12 and the pump gear 13.
It is a front view in the state where 41 was attached.

[0035]

As described above, the present invention is constructed as described above.
It has the following effects. Since the variable displacement type axial hydraulic pump is disposed parallel to the crankshaft 4 without protruding from the engine as a hydraulic power unit engine, the overall length can be shortened and the hydraulic power unit can be made compact. is there. Also, since the variable displacement axial hydraulic pump is housed inside the oil pan 3, noise generated by the pump can be confined inside the oil pan 3. Further, since the variable displacement axial hydraulic pump and the engine are matched from the beginning, there is no need to assemble both at the site. In addition, since the crank gear 11 for driving the fuel pump or the camshaft on the crankshaft 4 which is always required in the engine can be used as it is and used as a gear for driving the pump shaft 2, a new gear can be used. It is no longer necessary to provide a gear for taking out power to the variable displacement axial hydraulic pump. Further, since the oil pan 3 and the pump chamber R are integrated, the cost can be reduced, and the pump chamber R
The stiffness was improved and the durability was improved.

According to the second aspect, the charge pump 9 can be disposed below the crankshaft 4 without providing a charge pump on the extension of the crankshaft as in the prior art. Therefore, a compact arrangement can be achieved. Further, a circuit for replenishing the pressure oil to the port block 1 disposed inside the oil pan 3 could be simply configured.

Since the oil pan of the conventional engine is replaced with the oil pan 3 of the present invention, the portion of the idle gear 12 together with the idle gear shaft 14 is provided in the port block 1. , Can be integrally supported together with the variable displacement axial hydraulic pump, and a hydraulic power unit engine can be configured by merely replacing the oil pan 3.

The pump chamber R is constructed as in claim 4.
When the pump chamber R is shielded from the lubricating oil pool inside the oil pan 3, the amount of lubricating oil is reduced. However, by providing the capacity increasing portion 3f, Therefore, a desired amount of lubricating oil could be secured.

According to the fifth aspect of the present invention, the portion of the pump chamber R integrated with the oil pan 3 and the portion of the bearing mounting seat 3 i where the port block 1 is attached and the bearing 27 is disposed are connected to the oil pan 3. Because it can be processed from the outside, it was possible to improve productivity in casting and machining.

The pump shaft 2 is constructed as in claim 6.
Thus, the bearing support of the variable displacement type axial hydraulic pump can be made strong, and the durability of the variable displacement axial hydraulic pump can be improved and the vibration noise can be reduced.

According to the seventh aspect of the present invention, a portion for extracting pressure oil from the plunger case 8 and the charge pump 9 disposed inside the oil pan 3 to an external traveling motor is provided.
The main hydraulic joints 22 and 23, the split clamps 44 and 43, and the joint body 20 can be easily configured with improved oil tightness.

The arrangement of the pump chamber R inside the oil pan 3 makes it difficult to dissipate the heat generated in the pump chamber R. It can be eliminated by the reinforcing ribs 26a, and the lid 26 can be reinforced by the cooling and reinforcing ribs 26a, and the parts where the strength of the oil pan 3 has become weak due to the assembly openings 3d and 3c can be reinforced. It was done.

Since the pressure oil in the tilting cylinder 7 is drained, the tilting swash plate 6 returns to the neutral position by the neutral return spring 36 in the tilting cylinder 7. When the operator sets the operating tool to the neutral position, the tilting swash plate 6 is automatically returned to the neutral position by the neutral return spring 36, and the operator sets the neutral position while considering the position of the operating tool with his / her feet or hands. There was no need to seek out.

According to the tenth aspect, when the operating lever is returned to the neutral position, and when the tilting swash plate 6 slightly deviates from the neutral position, a stronger spring force than the neutral return spring 36 is provided. Since the tilting swash plate 6 is biased to the neutral position by the neutral determination pistons 34 and 35 biased by the biasing springs 37 and 37, the tilting swash plate 6 is completely maintained at the neutral position, and the traveling of the vehicle body is performed. It can be blocked.

According to the eleventh aspect, the servo cylinder 16 for operating the tilt swash plate 6 is supported on the side of the oil pan 3,
The Y-type arm 18 is rotated by the servo cylinder pistons 16a and 16b, and the tilting cylinder operation valves 10 and 10 provided at the end of the Y-type arm 18 contact the position detecting plate 17 of the tilting swash plate 6. Therefore, the operator merely generates a signal for operating the servo cylinder pistons 16a and 16b, and the Y-arm 18 is rotated by the servo cylinder 16, and the tilt cylinder operating valve 10 at the tip of the Y-arm 18
When the lever 10 is brought into contact with the position detecting plate 17, the pressure oil is switched and the tilting cylinder 7 is moved in and out, so that the lever operating force of the operator may be small, and if the lever is set to the neutral position, the automatic operation is performed. Tilting cylinder operation valve 10
The tilt swash plate 6 converges to the neutral position by the tilt cylinder 10 and the tilt cylinder 7.

In a configuration in which the pump gear 13 and the idle gear 12 are arranged inside the oil pan 3, the gear cover that covers the periphery of the idle gear 12 and the pump gear 13 is immersed in the lubricating oil. With the arrangement, the idle gear 12 and the pump gear 13 are less likely to circulate the lubricating oil, and the temperature rise of the lubricating oil and the power loss for moving the lubricating oil are reduced.

[Brief description of the drawings]

FIG. 1 shows a crankshaft 4 of a hydraulic power unit engine
FIG. 1 is a perspective side view showing a variable displacement axial hydraulic pump.

FIG. 2 is an overhead perspective view of an oil pan 3 and a crankshaft 4;

FIG. 3 is a side sectional view of a part of an oil pan 3 and a variable displacement axial hydraulic pump.

FIG. 4 is a plan sectional view of a portion of a plunger case 8, a port block 1, main hydraulic couplings 22 and 23, and a hydraulic oil pipe 42.

FIG. 5: Port block 1 and main hydraulic couplings 22 and 23
FIG.

FIG. 6 is a plan view showing parts of an oil pan 3 and a servo cylinder 16;

FIG. 7 is a side sectional view of a portion of the servo cylinder 16;

FIG. 8 is a front sectional view of a portion including a pump chamber R and a servo cylinder 16;

FIG. 9 is a front sectional view of a portion of a crank gear 11, an idle gear 12, and a pump gear 13.

FIG. 10 is a side sectional view of a portion of the pump shaft 2 and the port block 1.

11 is a plan sectional view of a portion of a pivot oil passage shaft 38 of the Y-type arm 18. FIG.

FIG. 12 is a plan sectional view of the neutral position adjusting bolts 28 and 29 and the port block 1;

FIG. 13: Main hydraulic couplings 22 and 23 and hydraulic oil pipe 4
2 is a plan cross-sectional view of a fixed portion of FIG.

FIG. 14 is a partial cross-sectional plan view of the oil pan 3;

FIG. 15 is a side sectional view of the oil pan 3.

FIG. 16 is a side sectional view showing an open state of each part of the oil pan 3;

FIG. 17 shows an oil pan 3 at a pivot oil passage shaft 38.
FIG.

18 is a front view of the oil pan 3. FIG.

FIG. 19 is a side view of the oil pan 3 on the side of the servo cylinder 16;

FIG. 20 is a bottom view of the lower cover 26a.

FIG. 21 is a front view of the gear covers 40 and 41;

FIG. 22 is a side sectional view of the gear covers 40 and 41.

FIG. 23 is a front view of the same.

FIG. 24 is a side view of a conventional hydraulic power unit engine.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Port block 2 Pump shaft 3 Oil pan 4 Crank shaft 5 Cylinder block 6 Tilting swash plate 7 Tilting cylinder 8 Plunger case 9 Charge pump 10 Tilting cylinder operation valve 11 Crank gear 12 Idle gear 13 Pump gear 14 Idle gear shaft 16 Servo cylinder 17 Position detection plate 18 Y-shaped arm 22 Main hydraulic joint 38 Pivot oil path shaft

──────────────────────────────────────────────────続 き Continued on the front page (58) Field surveyed (Int. Cl. ⁷ , DB name) F02B 63/06 B60K 17/10 F01M 11/00 F02B 67/04

Claims (12)

(57) [Claims] 1. An oil pan of a vertical multi-cylinder engine,
Built-in variable displacement type axial hydraulic pump,
Room R / port that constitutes the type axial hydraulic pump
Block 1-With the pump drives arranged in series,
The pump is driven in parallel with the lower part of the rank shaft 4.
A pump gear 13 is provided at one end of a pump shaft 2 constituting a part.
The pump gear 13 is connected to an engine fuel injection pump or
Crank gear on crankshaft 4 for driving camshaft
11 directly or indirectly, and the pump chamber R is
A hydraulic power unit engine characterized by being integrally formed with the oil pan 3 . 2. A hydraulic power unit engine according to claim 1.
, Wherein the pump shaft 2 is supported by bearings on an oil pan cover 25 provided on the side wall of the oil pan 3 and a mounting seat for the charge pump 9 is provided on the oil pan cover 25. 3. The hydraulic power unit engine according to claim 1,
, An idle gear 12 is interposed between the crank gear 11 and the pump gear 13, and an idle gear shaft 14 that supports and supports the idle gear 12 is connected to the port block 1.
A hydraulic power unit engine characterized by being supported by a hydraulic power unit. 4. The hydraulic power unit engine according to claim 1,
In this case, the pump chamber R is isolated from the lubricating oil pool of the oil pan 3 and the volume of the lubricating oil for the pump chamber R, which decreases, is protruded outside of the mounting bolt of the oil pan 3 to the cylinder block 5. A hydraulic power unit engine characterized by replenishment. 5. The hydraulic power unit engine according to claim 1,
, A port block 1 is attached to one side of the pump chamber R, a seating hole 3a for machining an attachment surface 3j of the port block 1 is opened, and a bearing is provided on the side of the pump chamber R opposite to the port block 1. A hydraulic power unit engine characterized in that the mounting seat (3i) is opened, and a seating hole (3e) larger than the bearing mounting seat (3i) is opened in the oil pan (3) opposite to the bearing mounting seat (3i). 6. The hydraulic power unit engine according to claim 5,
In, the seat surface machining holes 3e, annexed to the oil pan cover 25, a hydraulic power unit engine, characterized in that the supporting bearings of the pump shaft 2 to the oil pan cover 25. 7. The hydraulic power unit engine according to claim 1,
In the above, the port block 1 is disposed inside the oil pan 3 and the main hydraulic couplings 22 and 2 are connected from the port block 1.
A hydraulic power unit engine characterized in that the main hydraulic couplings (22, 23) are supported in an oil-tight state by projecting the oil hydraulic pump (3) outward from the oil pan (3) and opening (3h) on the side of the oil pan (3). 8. A hydraulic power unit engine according to claim 1,
In the above, an assembly opening for assembling the variable displacement axial hydraulic pump into the pump chamber R is provided in the upper and lower portions of the oil pan 3, and a cooling and reinforcing rib 26a is provided on a lid closing the assembly opening. A hydraulic power unit engine characterized by being provided. 9. The hydraulic power unit engine according to claim 1, wherein the tilting swash plate disposed in the pump chamber is configured to be operated by four tilting cylinders. A hydraulic power unit engine characterized in that a neutral return spring 36 is interposed between the rotary piston 7a and the tilting swash plate 6 is returned to the neutral position by the neutral return spring 36 when in neutral. 10. The hydraulic power unit according to claim 9.
In the tilting swash plate 6 operated by the tilting cylinder 7, neutral position adjusting bolts 28 and 29 for adjusting the neutral position of the tilting swash plate 6 are supported on the port block 1, and the neutral position adjusting bolt 28・ 29, oil pan cover 2
5. A hydraulic power unit engine characterized in that it can be adjusted from a seat surface processing hole 3e from which the seat 5 is removed. 11. The hydraulic power unit according to claim 9.
In Seki, servo cylinder 16 for operating the tilting swash plate 6
Is supported on the side of the oil pan 3, and the Y-type arm 18 is rotated by the piston 16c in the servo cylinder.
The tilt cylinder operation valve 10 provided at the tip of the mold arm 18
A hydraulic power unit engine characterized in that 10 is in contact with a position detecting plate 17 of the tilting swash plate 6. 12. The hydraulic power unit according to claim 3.
1. A hydraulic power unit engine according to claim 1, wherein a gear cover that covers the periphery of the idle gear 12 and the pump gear 13 is disposed so as to be immersed in lubricating oil.