JP3295239B2 - Engine integrated transmission - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an engine-integrated transmission that outputs engine power via a transmission mechanism. INDUSTRIAL APPLICABILITY The present invention is suitable for an engine-driven air conditioner in which a compressor is driven by engine power to perform a cooling / heating operation.

[0002]

2. Description of the Related Art An engine-driven air conditioner includes an indoor air conditioning unit and an outdoor air conditioning unit. The outdoor air conditioning unit transmits engine power to a compressor via a transmission, thereby performing a cooling and heating operation. It is configured as follows.

[0003] Conventionally, the transmission includes a belt-type transmission in which a belt is wound between a pair of pulleys mounted on a crankshaft and a transmission shaft, or a pair of transmission gears mounted on the crankshaft and the transmission shaft. Is generally adopted. In this gear type transmission, a separate transmission case is connected to an engine case, the transmission gear and the transmission shaft are rotatably housed in the transmission case, and lubrication for lubricating the meshing portion and the transmission portion thereof. It is common to have a structure in which oil is accommodated in the transmission case.

[0004]

However, in the conventional belt-type transmission, the power transmission efficiency is low, and the durability of the belt is low. In this case, there is a problem that the belt needs to be replaced periodically, and the cost for inspection and repair increases.

[0005] Further, in the above-mentioned conventional gear type transmission, although the power transmission efficiency and the durability are higher than those of the belt type, since the gear case of the transmission is separate from the engine case, both cases are separated. In addition to the increase in size in the longitudinal direction of the engine by the size of the wall and the distance between the two cases,
There is a problem that the weight increases.

[0006] The present invention has been made in view of the above-described conventional situation, and while improving power transmission efficiency and durability,
It is an object of the present invention to provide an engine-integrated transmission that can be made compact and lightweight.

[0007]

According to the present invention, a crankcase is rotatably supported by an engine case and a gear case is oil-tightly connected to an end opening of the engine case in a crankshaft direction. A third drive gear, a second drive gear, and a first drive gear are mounted on an end of the crankshaft protruding into the space, and the first and second driven gears meshing with the first and second drive gears are mounted on the end of the crankshaft. The third drive gear is engaged with an end of a camshaft disposed in an engine case-side space of the gear case and rotatably supported by the engine case and protruding from the engine case into the engine case-side space of the gear case. Fix the camshaft driven gear,
A first output shaft fixed to the first driven gear and a second output shaft fixed to the second driven gear are rotatably cantilevered by first and second bearings provided in a gear case, respectively. The outer ends of the first and second output shafts are projected from the gear case, and the gear case branches off from the oil pump to the lubricated portion of the engine in the middle of the engine lubrication system;
The first and second bearings, the first to third drive gears,
A lubricating path for supplying lubricating oil to the second driven gear and the camshaft driving gear is provided.

[0008]

According to the engine-integrated transmission according to the present invention, the end opening of the engine case is closed by the gear case and the transmission gears are disposed in the gear case.
The gear case can also be used as the side cover of the engine case, and there is no need for a case wall that separates the engine case from the gear case, such as a transmission installed separately from the conventional engine, and the dimensions between the cases. And lightening can be achieved. Further, since the gear case is oil-tightly connected to the engine case, it is possible to supply a part of the engine lubricating oil to the transmission side.

Further, in the present invention, since the output shaft fixed to the shift driven gear is cantilevered by the gear case, the length of the gear case in the axial direction can be reduced as compared with the case where the output shaft is supported at both ends, and the size can be reduced. Can be further achieved.

Further, since the engine power is transmitted to the first and second output shafts via the first and second drive gears and the first and second driven gears, the power transmission efficiency and the durability are higher than those of the belt type transmission. In addition to improving gearability, the degree of freedom in gear ratio design can be improved, and when the gear case 92a is removed, each of the gear groups is exposed, and assemblability can be improved. Further, the oil passage from the oil pump to the gear group can be shortened, so that the time required for the lubricating oil to reach can be shortened, and lubricating oil management can be simplified.

[0011]

Embodiments of the present invention will be described below with reference to the accompanying drawings. 1 to 16 are views for explaining an engine-driven air conditioner according to an embodiment of the present invention, and FIGS. 1 to 4 are diagrams of an engine-driven air conditioner to which the structure of the embodiment is applied. Front view, rear view, right side view (Fig. 2
III-III line), left side view (IV-IV line in FIG. 2), FIG. 5 is a schematic plan view of the floor of the outdoor heat exchange chamber, and FIG. 6 is a schematic sectional view of the engine room and the piping room. 8 and 9 are right side sectional views of the engine, FIGS. 10 and 11 are left side and rear views of the engine, and FIG. 12 is a view of the engine of the above embodiment. FIG. 13 is a partial plan view of the transmission, FIGS. 14 and 15 are left and right side views of the transmission, FIG. 16 is a sectional development view showing the flow of lubricating oil, and FIG. 17 is a lubrication control device. FIG.

FIG. 7 is a diagram showing the overall configuration of the apparatus of this embodiment.
, 1 is an engine-driven air conditioner, which is composed of an outdoor air conditioning unit 2 and an indoor air conditioning unit 3. The indoor air-conditioning unit 3 includes a refrigerant indoor heat exchanger 4, a decompression expansion valve 18, and a not-shown indoor heat exchange fan. The outdoor air-conditioning unit 2 includes an engine room 7 in which an engine 5, a pair of compressors 6, 6 and the like are disposed, a main accumulator 8, a sub-accumulator 9, an electrical box 50, and a pipe connecting each device. , A piping chamber 10 in which is disposed, a refrigerant outdoor upper part,
An outdoor heat exchange chamber 14 in which lower heat exchangers 11 and 12 and an engine cooling heat exchanger (hot water heat exchanger) 13 are disposed.
And

The engine 5 is a water-cooled gas-fueled engine. An intake port 21 of the engine 5 is connected to an intake pipe 21a, and the intake pipe 21a is provided with a gas mixer 21b and an air cleaner 21c. The pipe 21a penetrates through the top walls of the engine room 7 and the outdoor heat exchange chamber 14 and opens to the outside.

The gas mixer 21b is connected to a supply pipe from an external gas fuel source in the terminal chamber 22 by a gas pipe 22d. A gas mixer 21 is connected to the gas line 22d.
b, a flow control valve 22a, a zero governor (reducing valve) 22b, and two solenoid valves 22c are interposed. The exhaust port of the engine 5 has an exhaust pipe 23a.
Is connected to the exhaust pipe 23a.
b, an exhaust silencer 23c and a mist separator 23d are interposed, and the exhaust pipe 23a is opened outside the heat exchange chamber 14.

A transmission 92,
The compressors 6, 6 are connected via clutches 6a, 6a. The outlet of the compressor 6 is connected to refrigerant lines 200 and 16.
a, the outdoor outdoor upper and lower heat exchangers 1 for the refrigerant via the four-way valve 15 and the refrigerant pipe 16b switched to the cooling operation position.
The two heat exchangers 11 and 12 are connected to the refrigerant pipe 16c, the heat exchanger in the main accumulator 8, and the refrigerant pipe 101 from the indoor heat exchanger 4 for refrigerant in the terminal chamber 22 via the refrigerant pipe 101. Is connected to the refrigerant line 17a by a joint 101a. Reference numeral 102 denotes a dryer, and reference numeral 103 denotes a filter that bypasses the dryer.

The refrigerant line 17b from the indoor heat exchanger 4 is connected to the refrigerant line 100 from the outdoor unit in the terminal room 22 by a joint 100a.
The refrigerant line 100 is connected to the suction ports of the compressors 6 and 6 via a four-way valve 15, a refrigerant line 16d, a main accumulator 8, a refrigerant line 202, a sub-accumulator 9, and a refrigerant line 201. In addition, 300 and 301 are capillary tubes, 210 and 210 are each a combination of a temperature detector and a capillary tube, and are for detecting the cooling temperature to detect the level of the liquid-phase refrigerant in the accumulator 8. is there. Reference numeral 302 denotes an open / close valve, and 303 denotes an oil discharge passage. When the amount of oil accumulated in the lower part of the accumulator increases, the open / close valve is opened manually or automatically so that oil flows from the main accumulator 8 to the sub accumulator 9.

An oil separator 19a for separating the lubricating oil in the refrigerant is interposed between the refrigerant pipes 200 and 16a. When the amount of the lubricating oil separated by the separator 19a exceeds a predetermined value. , Oil strainer 19b,
It is returned to the main accumulator 8 via the solenoid valve 19c that opens when the predetermined value is exceeded. The lubricating oil is also returned to the sub accumulator 9. In addition, the refrigerant pipe 16a
Is connected to the main accumulator 8 via an oil strainer 20a and a solenoid valve 20b which opens when the pipe pressure is equal to or higher than a predetermined pressure, thereby avoiding an abnormal rise in refrigerant pipe pressure.

The cooling jacket 28 of the engine 5
b, when the cooling water temperature is equal to or lower than a predetermined value, the cooling water pump 28a, the water pipe 29a, and the cooling jacket 28
b, water line 29a ', switching valve (thermostat valve)
A cooling jacket circulating circuit (engine cooling water circulating circuit), which is one of low-temperature circulating circuits for circulating cooling water through the path of 28c and the water pipe line 29s, is configured.

When the cooling water temperature exceeds a predetermined value,
Cooling water pump 28e, water line 29e, exhaust gas heat exchanger 23b, water line 29e ', cooling water pump 28a, water line 29a, cooling jacket 28b, water line 29a', switching valve 28c, water line 29b, three-way valve 28d. , Water pipe 2
9c, heat exchanger 13 for cooling water, water pipes 29d, 29p,
A high-temperature circulation circuit that circulates cooling water through the path of the cooling water pump 28e is configured. The switching valve 28
When c is switched to the low temperature circulation position, the cooling water from the cooling water pump 28e flows in the direction of the water pipe 29b through the bypass passage 29r. That is, an exhaust gas heat exchanger circulation circuit, which is another low temperature circulation circuit, is configured. As a result, the exhaust heat of the exhaust gas heat exchanger 23b is discarded by the cooling water heat exchanger 13 through the three-way valve 28d, or is supplied to the refrigerant by the heater 29g of the main accumulator 8. As a result, the exhaust heat can be used even during warm-up at the time of start-up, which is particularly effective when a rapid rise of heating is required or when the water temperature does not easily rise.

In the above-mentioned cooling system, reference numeral 30a denotes a cooling water reservoir tank, which comprises a water pipe 30c, an inlet 30
b, it is connected to the cooling water heat exchanger 13. When the three-way valve 28d is switched, the engine cooling water is supplied to the heater 29g in the main accumulator 8 through the water pipe 29d, thereby supplying heat to the refrigerant. Reference numeral 90 denotes a solenoid valve, and 89 denotes an oil strainer. When the load on the indoor unit 4 during cooling becomes particularly small, the solenoid valve 90 opens to allow the refrigerant to bypass the indoor unit 4 and flow to the main accumulator 8. And try to balance.

Next, a specific structure of the outdoor air conditioning unit 2 will be described with reference to FIGS. The casing 31 of the outdoor air-conditioning unit 2 has a floor plate 3 on a pair of bases 32.
3 is placed and fixed, and columns 34 are erected at the four corners,
The upper ends of the four pillars 34 are connected by one ceiling beam (not shown) on the right and left sides, respectively, and the front and rear ends of the floor plate 33 are bent to form floor beams 33a. The entire left and right side surfaces of the casing 31 are covered with left and right plates 37c and 37d, and the ceiling surface is a ceiling plate 37e.
Covered with. The lower portions of the front and rear sides of the casing 31 are covered with front and rear plates 37a and 37b. The front, rear, left and right plates 37a to 37d are detachable to ensure maintainability of each device.

The upper portions of the front and rear side plates 37a and 37b on the front and rear sides of the casing 31 are provided with openings for introducing outside air. Wire meshes 38a and 38b functioning as filters are provided in the respective openings. 36b are detachably mounted on the upper and lower sides of each of them. A discharge opening 37f for discharging the introduced outside air upward is formed in the ceiling plate 37e, and the outside air is passed through the wire mesh 3 to the discharge opening 37f.
An outdoor heat exchange blower fan 44 for sucking air from the portions 8a and 38b into the outdoor heat exchange chamber 14 and discharging the air above the heat exchange chamber 14 is provided. Reference numeral 38c denotes a wire net standing upright around the discharge opening 37f.

The interior of the casing 31 is defined by the partition plate 39 into the outdoor heat exchange chamber 14, the engine room 7, and the piping room 10. The partition plate 39 is a central partition constituting the ceiling of the engine room 7. Plate 40 and engine room side partition plate 41
a, 41b, and piping room side partition plates 42a, 42b constituting the ceiling of the piping room 10. The engine room side partition plates 41a and 41b and the piping room side partition plate 42
a and 42b are detachable upward. At the time of removal, the front and rear side plates 37a and 37b are also removed, so that
The engine room 7 is open at the ceiling, front and both corners, and the piping room 10 is open at the ceiling, rear and both corners, so that the maintenance work of the equipment in each room is easy.

Further, at the boundary between the center partition plate 40 and the pipe chamber side partition plates 42a and 42b and on the upper outside side (upper side of the pipe chamber 10) of the rear middle plate 44a constituting the rear wall of the engine room 7. The gutter 48 (drain passage) is disposed so as to be disassembled from the center and the pipe chamber side partition plates 40, 42a and 42b, that is, exchangeable with a new one. The gutter 48 is a groove extending in the longitudinal direction of the outdoor air-conditioning unit 2 (horizontal direction in FIG. 2), that is, in the direction of the surface where the heat exchanger is disposed, and becomes lower toward the right side (right side in FIGS. 2 and 5). It is inclined.
The high end 48b located at the highest point of the gutter 48 can be exposed to the outside by removing the right side plate 37d or by providing an opening (cleaning hole).

A tubular downspout (drainage pipe) 43 can be disassembled at the lower end 48a located at the lowest point of the horizontal gutter 48.
And it is connected interchangeably with a new one. The downspout 43 extends downward at a corner formed by the inner surface of the left side plate 37c and the outer surface of the rear middle plate 44a of the engine room 7, and a drain port 43a opening at the lower end thereof is located below the floor plate 33. And facing outward.

The engine room side partition plates 41a and 41b, the piping room side partition plates 42a and 42b, and the center partition plate 40
Are inclined so as to become lower toward the above-mentioned gutter 48 side.
Therefore, rainwater or the like that has entered the outdoor heat exchanger 14 is immediately collected by the horizontal gutter 48 and discharged to the outside through the vertical gutter 43. Also, due to the above inclination, the engine room side partition plates 41a, 4
1b and the position of the outer ends of the piping chamber side partition plates 42a and 42b are increased, and the opening for inspecting and maintaining the inside by removing the front and rear plates 37a and 37b is increased.

The central partition plate 40 has two vent holes 40b for ventilating air so as to open into the outdoor heat exchange chamber 14. The outlet 40b is provided with a sound absorbing box 40c having a sponge-like sound absorbing sheet adhered to the inside thereof.
Surrounded by Opening 4 of this silencing box 40c
0d is located above the above-mentioned gutter 48, and is located downstream of the gutter 48 with respect to the discharge port 40b.
This prevents rainwater or the like entering the outdoor heat exchange 14 or rainwater or the like flowing in the gutter 48 from entering the engine room 7 from the discharge port 40b.

The side wall of the engine room 7 is connected to the front side plate 37a,
The left wall 37c, the rear middle plate 44a, and the right middle plate 44b, the top wall is composed of the engine room side partition plates 41a, 41b, and the center partition plate 40, and the bottom wall is the floor plate 3
3 is provided with a bottom plate 45 arranged at an interval. The upper and lower end surfaces of the rear middle plate 44a and the right middle plate 44b are air-tightly connected to the partition plate 39 and the floor plate 33, and thus the engine room 7 is configured to have a soundproof structure.

The space between the bottom plate 45 and the floor plate 33 is a box-shaped air introduction chamber 46, and the bottom plate 45 has a large number of outlets 45 a for blowing ventilation air into the engine room 7. It is arranged and formed almost evenly across. Further, two engine room air inlets 46a that open into the piping chamber 10 are formed on the right middle plate 44b side of the air introduction chamber 46, and a ventilation fan 47 is disposed in each of the air inlets 46a. ing.

On the inner surface side of the rear side plate 37b in the piping chamber 10, there are provided an electrical box 50 in which various control devices and the like are accommodated and arranged, and a terminal room 22 for connection to external piping. An air inlet 50a is formed on the bottom surface of the electrical component box 50, and a discharge port 50b is formed on the upper side surface. A gap serving as an air passage is opened between the bottom surface and the floor plate 33. The outside air is supplied to the floor plate 33 by the piping room 10.
A piping chamber air inlet 33b for introducing the air into the inside is formed, and a part of the introduced outside air is supplied to the air inlet 50a.
Is introduced into the electrical box 50 for ventilation, and then discharged from the discharge port 50b.

The refrigerant outdoor upper heat exchangers 11 and 11 are provided on the upper front and rear sides of the outdoor heat exchange chamber 14, the refrigerant outdoor lower heat exchanger 12 is provided on the lower rear side, and the front heat exchanger 12 is provided on the front side. The heat exchangers 13 for engine cooling water are respectively arranged at the lower part. The outdoor upper heat exchangers 11, 11 are arranged vertically and along the wire meshes 38a, 38b. The lower outdoor heat exchanger 12 and the cooling water heat exchanger 13 are arranged so as to be inclined so that the lower part thereof is located on the inner side, and a rubber hose 13c is provided at the upper right side of the cooling water heat exchanger 13. Is provided with the above-mentioned water inlet 30b.

The lower end of the cooling water heat exchanger 13 extends beyond the engine room side partition plates 41a and 41b and the center partition plate 40.
And the muffling box 40c. Further, the lower end of the refrigerant outdoor lower heat exchanger 12 is located at a lower corner portion of the center partition plate 40 and the sound deadening box 40c from the piping room side partition plates 42a and 42b further beyond the horizontal gutter 48.

Here, the pipes 29c, 29d, 16b, 16c, and 30 connecting the cooling water heat exchanger 13, the refrigerant heat exchangers 11, 12 and the respective devices in the piping chamber 10 are connected.
The pipe bundle P is arranged on the right side plate 37d side of the piping chamber 10 and at the center in the front-rear direction.
Penetrates the inside of one sealing pad 49 disposed at the right end of the pipe bundle, and thus a plurality of tube bundles P are sealed by one pad. In this sealing pad 49, each notch 4 connecting each pipe hole and the side end of the left side plate 37c direction.
9a, which allows fitting after removing the right plate 37d after piping.

The engine 5 according to the present embodiment is a water-cooled parallel four-cylinder OHV engine, as shown in FIGS. In the engine 5, an oil pan 5b is bolted and fixed to the lower mating surface of the cylinder block 5a, the cylinder head 5c is fastened to the upper mating surface with a head bolt, and a head cover 5d is attached to the cylinder head 5c.
It is of a structure covered with. The cylinder block 5a
The piston 5e slidably inserted into the cylinder bore of the connecting rod body 5f and the connecting rod cap 5
f 'is connected to the crankshaft 5g, and a valve train 5h is provided on the cylinder head 5c. The valve train 5h connects the intake valve 5i and the exhaust valve 5i 'to the crankshaft 5 via a rocker arm 5j and a push rod 5k.
It is configured to be opened and closed by a cam shaft 51 arranged near g. Reference numeral 200 denotes two connecting bolts for connecting the connecting rod body 5f and the connecting rod cap 5f 'with the crankshaft 5g interposed therebetween.

In the engine 5, the cylinder block 5a has a one-block structure in which four cylinders are integrated, while the cylinder head 5c
Has a structure in which two cylinder bores are divided into one, that is, two sets.
Two sets of d are also provided. And each of the above head covers 5
Each of d has a breather chamber (see FIG. 10).

As shown in FIG. 11, a flywheel 91 is connected to the right end of the crankshaft 5g when viewed from the back of the engine 5, and the ring gear 91a is disposed on the back of the engine. The output gear of the starter motor 91b can be meshed. A gear type transmission 92 is connected to the left end of the crankshaft 5g, and the compressors 6, 6 are connected to the transmission 92 via the clutches 6a, 6a. As described above, in this embodiment, since the gear type transmission 92 is provided, there is no problem that the belt needs to be periodically replaced in the case of the belt type transmission.

The transmission 92 has a structure in which a mating surface a2 of a gear case 92a is oil-tightly and integrally connected to a mating surface a1 on the side opposite to the flywheel of the cylinder block 5a and oil pan 5b constituting an engine case. (See FIG. 11). The gear case 92a functions as a side cover of the engine case, and as shown in FIG. 14 (a view of the transmission 92 from the left) when viewed from the mating surface a2 side, in the crankshaft direction. It looks like a generally square dish. In FIG. 14, the gears are removed. The gear case 92a has a pair of P
TO shafts (output shafts) 92b, 92b are arranged in parallel with the crankshaft 5g. The two PTO shafts 92b are rotatably cantilevered by bosses 92c formed on the bottom wall 92d of the gear case 92a, and the outer ends of the PTO shafts 92b are located outside the bottom wall 92d (FIG. 16). Project to the right)
An oil seal 92 is provided between the projection and the boss 92c.
e sealed.

First and second driven gears 93a, 93b are mounted on inner end portions of the PTO shafts 92b, 92b located on the engine case side, respectively. The driven gears 93a and 93b are fastened to the PTO shaft 92b by bolts 93c and fixed by being prevented from rotating by knock pins 93d. The knock pins 93d are pressed by washers 93c 'of the bolts 93c and are prevented from coming off.

The bottom wall 92 of each PTO shaft 92b
As shown in FIG. 15, substantially rectangular connection plates 95a and 95b are fastened and fixed to the outer end protruding from d by three bolts 95e. Rubber bushes 95f are provided on both outer edges of the connection plates 95a and 95b.
Are arranged two by two, and each rubber bush 95f is inserted and connected to the tip of a bolt 95c fixed to the flange 6c. Bolts 95c, 95c
Share one nut 95d, and the flange 6c is fixed to the clutch 6a of the compressor 6. Thus, one nut 95d is connected to a pair of bolts 95.
The number of parts of the nut is reduced by sharing the nut with the nuts c and 95c, and co-rotation during attachment and detachment is prevented to improve workability.

In the gear case 92a, the crankshaft 5 is provided.
The g output portion 5g 'protrudes, and the first to third drive gears 94a to 94c are coupled to the output portion 5g'.
The third drive gear 94c is a cam gear 5l of the cam shaft 5l.
′, The first and second drive gears 94a and 94b are in mesh with the first and second driven gears 93a and 93b, respectively. A gear 61d of an oil pump 61, which will be described later, meshes with the cam gear 51 '. Here, the first drive gear 94a, the driven gear 93a, and the second drive gear 9
4b and the driven gear 93b have different gear ratios, so that each of the compressors 6, 6 has a different speed ratio.
Is driven. With this configuration, it is possible to arrange compressors having different performances, and to drive one or the other or both of the compressors in accordance with the load of cooling and heating, thereby enabling three types of refrigerant compression. It is possible to impart characteristics. Therefore, the degree of freedom of the gear ratio design and the ease of assembly can be improved.

The engine 5 of this embodiment has its crankshaft 5g oriented parallel to the front side plate 37a of the engine room 7,
Further, the cylinder shaft is arranged in a forwardly inclined state with an inclined axis X inclined such that the upper part of the cylinder axis is closer to the front side plate 37a. Due to this forward inclined arrangement, the lower mating surface orthogonal to the cylinder axis (X) of the cylinder block 5a is inclined such that the farther part from the front side plate 37a is located higher (see FIG. 8). On the other hand, the oil pan 5b attached to the inclined mating surface is formed so as to bulge downward so that its bottom wall 5b 'is substantially parallel to the floor plate 45.

Two sets of engine mounting support brackets 81 and 82 are provided at both ends of the engine 5 in the crankshaft direction. As shown in FIG. 11, when viewed from the back of the engine, two sets of support brackets 81, 81 'on the right side are at the right end of the oil pan 5b, and two sets of support brackets 82, 82' on the left side are the transmission. 92
Is disposed below the gear case 92a. When viewed in the crankshaft direction, the support brackets 81 ', 8
2 'is disposed at a position close to the front side plate 37a, and the support brackets 81 and 82 are disposed at positions far from the front side plate 37a (see FIG. 10). Each of the support brackets 81, 81 ', 82, 82' has basically the same structure.
The structure is such that a common base plate 81c and a bracket plate 81a at each position are bolted and fixed between the base plate 81c and the bracket plate 81a at each position for each 1 'or 82, 82'. The base plate 81c is fixed to the floor plate 45. Each of the bracket plates 81a on the transmission 92 side is fixed to the gear case 92a with bolts.
On the other hand, the bracket plate 81a on the oil pan end side and on the front side plate 37a side is fixed to a boss 5a 'formed near the lower mating surface of the cylinder block 5a by bolts, and is further disposed on the side far from the front side plate 37a. The bracket plate 81a of the provided support bracket 81 is bolted and fixed to a corner between the bottom wall and the vertical wall of the oil pan 5b.

On the outer surface of the bottom wall 5b 'of the oil pan 5b, a number of fins 75 extending in the crankshaft direction are provided.
Are integrally formed. The fins 75 improve the rigidity of the oil pan 5b and improve the cooling efficiency. That is, the cooling air introduced by the ventilation fan 47 is supplied into the engine room 7 through the air introduction chamber 46, and the heat exchange between the cooling air and the fins 75 cools the lubricating oil in the oil pan 5b. (Fig. 1
reference). As a result, a special device for cooling the lubricating oil can be dispensed with, and the installation of the device can be simplified.

Further, the crankshaft 5 of the oil pan 5b
A bearing portion 77 is formed at a portion facing each journal portion of g. The bearing portion 77 is formed by bulging a part of the bottom wall portion of the oil pan 5b toward the opening of the mating surface thereof. The bearing portion 77 and the bearing portion 5a 'of the cylinder block 5a 5g of the crankshaft
Is supported. By forming the bearing portion 77, the rigidity and strength of the oil pan itself are improved, so that the rigidity and strength of the entire engine can be improved, thereby contributing to reduction of vibration and noise.

Two sets of inspection windows 78 are formed in the cylinder block skirt portion of the engine 5.
8 is provided with a cover member 78a for detachably closing the opening thereof by means of a mounting bolt. Each inspection window 78
Is formed at a boundary between adjacent cylinders and at a position facing a bearing portion of the crankshaft 65 and a connecting portion between the crankshaft 65 and the large end of the connecting rod. That is, the connecting rod body 5f
Bolts 2 for fastening the connecting rod cap 5f 'to the
Inspection window 7 so that an extension of the line connecting 00 and 200 can pass through inspection window 78 as crankshaft 5g rotates.
8, and the size of the inspection window 78 is
The connecting rod body 5f, the connecting rod cap 5f ', and the piston 5e are large enough to pass through. The inspection window 78 is located above the upper limit oil level of the lubricating oil in the oil pan 5b, below the inclined axis X, and substantially opposite to the front plate 37a.

Next, the intake and exhaust systems of the engine 5 will be described. Each intake port 5p of the engine 5 is led out above the cylinder shaft. An intake manifold 73 'connected to each intake port 5p extends toward the right side plate 37d in the direction of the crankshaft 5g. The gas mixer 21b is connected to the air cleaner 21c disposed above the compressor 6 in the engine room 7 via an intake hose 21a '. This air cleaner 2
Reference numeral 1c denotes a combination of an intake silencer section and an air cleaner section, and a lid section (not shown) of the air cleaner 21c faces the front side plate 37a, so that maintenance such as element cleaning and replacement can be easily performed. It has become.

The four exhaust ports 5q of the engine 5 are led out below the cylinder shaft.
The exhaust gas heat exchanger 23b is connected directly to the external connection port, i.e., without interposing an exhaust pipe. As shown in FIG. 8, the exhaust gas heat exchanger 23b has a structure in which an inner fin type heat exchange unit 73 located on the upper side and a screw type heat exchange unit 74 located on the lower side are integrated. It is set longer than the interval between the exhaust ports 5q, 5q at both ends.

The inner fin type heat exchange section 73 is formed by utilizing an exhaust passage, and is formed by bending an upper section and a lower section so as to form a substantially U-shape in order to secure a necessary heat exchange area. It has a structure in which it is molded, its outer surface is surrounded by a cooling jacket 73a, and a number of fins 73b protrude from its inner surface. Each exhaust port 5q communicates with the inside of the upper stage, and the water pipe 29e 'is connected to a cooling water outlet of the cooling jacket 73a.

The screw type heat exchange section 74 has a cooling jacket (casing) 74a formed in a cylindrical shape.
A number of helical screw pipes 74b are disposed in the jacket 74a, and the upstream end of the pipe 74b is connected to an upstream chamber into which exhaust gas passing through the inner fin heat exchanger 73 is introduced, and the downstream end is connected to an exhaust pipe. This is a structure connected to the exhaust silencer 23c via 23a '. The exhaust silencer 23c is disposed above the compressor 6 in the engine room 7 and adjacent to the air cleaner 21c.

The compressor 6 on the floor plate 45 of the engine room 7
At a lower position, a neutralizer 82 for neutralizing condensed water containing acidic gas in the exhaust gas is disposed. The exhaust gas heat exchanger 23b, the exhaust silencer 23c, and the mist separator 83 are connected to the neutralizer 82 via respective drain hoses (see FIG. 1).

Next, a cooling system of the engine 5 of the embodiment will be described. In the cooling jacket circulation circuit, which is one of the low-temperature circulation circuits, a cooling water pump 28a and a water pipe 29 are provided.
a through the cooling jacket 28b of the outer peripheral portion of the wet liner 500a and the cooling jacket 28b of the cylinder head 5c shown in FIG. 8, and further, a circuit of a water pipe 29a ', a switching valve 28c, water pipes 29s and 29t, and a cooling water pump 28a. The cooling water circulates.

In the exhaust gas heat exchanger circulation circuit, which is one of the low temperature circulation circuits, a cooling water pump 28e, a water pipe 29e, an exhaust gas heat exchanger 23b, a water pipe 29e ',
A bypass pipe 29 for bypassing the switching valve 28c;
The cooling water circulates in the circuit of the water pipe 29b, the three-way valve 28d, the water pipe 29c, the cooling water heat exchanger 13, the water pipes 29d and 29p, and the cooling water pump 28e. At high temperatures, the cooling water pump 28e and the cooling water pump 2
Since the cooling water 8a is connected in series, the cooling water also circulates in the high temperature circulation circuit. That is, the three-way valve 28d
From the cooling water heat exchanger 13 or the heat exchanging portion 29g of the main accumulator 8 to return to the cooling water pump 28e via the water pipe 29p.

Next, the lubrication system of the engine 5 of this embodiment will be described. This lubrication system is shown in FIGS.
Is shown in FIG. 16 shows a partial cross-sectional view of the transmission along a horizontal plane, which is integrated with a partial cross-sectional view of the cylinder portion. In the lubrication system, the lubricating oil in the oil pan 5b is sucked up by the oil pump 61 through the oil strainer 61b, and is pumped through the oil filter 62 to the main gallery 63 arranged at the center of the cam shaft. The first and second engine lubrication systems A and B to be distributed to and supplied to the lubricated parts, and the shift from the oil filter 62 into the transmission 92 (middle gear case m), which is distributed and supplied to the lubricated parts in various places. And a gear lubrication system C. Reference numeral 61a denotes a relief valve for maintaining the discharge pressure of the oil pump 61 at a predetermined value or less, and 62a is built in the oil filter 62 so as to bypass the lubricating oil when the passage pressure of the filter 62 becomes equal to or more than a predetermined value. The relief valve 63a is an oil passage connecting the oil filter 62 with the main gallery 63 and the oil passage 96 of the gear case 92a.

The first engine lubrication system A supplies oil from the main gallery 63 to the journal 64 of the camshaft 51, the journal 65 of the crankshaft 5g, and the large end 66 of the connecting rod 5f, and thereafter returns to the oil pan 5b. It is configured as follows. The second engine lubrication system B is configured to supply oil from the main gallery 63 to the respective valve trains 5h of the respective cylinder heads 5c, and thereafter return to the oil pan 5b.

In the lubrication system B, the oil passage 5 from the main gallery 63 to the tappet chamber of the tappet 5j is provided.
Only two sets of t are provided, left and right, and a throttle 5u is provided on at least one side to adjust the flow rate of the left and right oil passages 5t. A breather chamber 5m formed in each of the head covers 5d is connected to an oil separator portion 76 from a breather outlet 5n through a breather passage 69, and lubricating oil separated by the separator 76 is supplied from a return hose 80 to an oil pan. 5b.

In the transmission gear lubrication system C, a part of the lubricating oil from the oil passage 63a on the upstream side of the main gallery 63 passes through the oil passage 96 of the gear case 92a, and from each P
The bearing 67 of the TO shaft 92b and the gears 93a, 93b,
The lubricating oil is supplied to the meshing portions 68 of the gears 94a to 94c, and thereafter, the lubricating oil dropped to the bottom of the gear case 92a is returned to the oil pan 5b. Abrasion powder that is likely to be generated at each gear meshing portion 68 is washed away by the oil that is forcibly circulated, and accumulates in the oil pan 5b or is captured by the oil filter 62.

Here, in the transmission gear lubrication system C, since the lubricating oil on the engine side is shared, there is a possibility that the time for the lubricating oil to reach the transmission particularly when the engine is started may be long. Therefore, in this embodiment, the oil pump 61 is arranged near the joint surface of the gear case 92a of the oil pan 5b, and the oil passage 63a to each part of the engine is arranged near the gear case 92a of the cylinder block 5a.
An oil passage to the transmission was formed to extend from the oil passage 63a to the oil passage 96 of the gear case 92a. As a result, the length of the oil passage from the oil pump 61 to various parts of the transmission is reduced, and the time required for the lubricating oil to reach the transmission can be reduced. In addition, it is because lubricating oil is shared,
The oil pump 61, the oil strainer 61b, the oil tank 24a, and the like can be used in common, so that it is not necessary to independently check the lubricating oil, and the management of the replenishing lubricating oil is smaller than when two lubricating oils are used. Is also easy.

The oil pan 5b has an oil hose 2
An oil tank 24 that is separate from the engine 5 and higher than the oil level of the oil pan 5b via the oil tanks 4c and 24d.
a is connected to the oil hoses 24c and 24d.
A solenoid valve 24b is interposed midway. When the solenoid valve 24b is opened, lubricating oil is supplied into the oil pan 5b by its own weight.

The oil tank 24a is provided between the right middle plate 44b of the engine room 7 and the right plate 37b of the casing 31, that is, in the piping room 10 having a lower bottom than the engine room 7, and has a replenishing port 24e.
Are arranged so as to face the front side plate 37a side. As shown in FIG. 3, the oil tank 24a has an L-shaped notch formed in a lower portion thereof, and the reserve tank 30a is disposed in the notch.
As a result, both large tanks 24a and 30 are placed in a narrow space.
a is arranged without difficulty. Also, by removing the front side plate 37a, the supply ports 24e, 30d of the tanks 24a, 30a face outward, so that oil supply and cooling water supply can be performed simultaneously and easily. Also,
The oil tank 24a and the reserve tank 30a are made narrower than the opening of the system so that replacement from the front side is possible.

The solenoid valve 24b is fixed via a bracket near the left support bracket 81 on the upper surface of the floor plate 45 and near the lubricating oil inlet 5r to the oil pan 5b. The solenoid valve 24b and the inlet 5r are connected by a flexible oil hose 24c, and the solenoid valve 24b and the oil tank 24a are connected by an oil hose 24d.

The oil pump 61 includes an oil pan 5b
And the vicinity of the boundary of the skirt portion of the cylinder block 5a,
In addition, it is disposed below the tilt axis X. The oil filter 62 is detachably attached to a bracket 5v detachably attached to the outer surface of the skirt portion of the cylinder block 5a below the inclined axis X.
As a result, the oil filter 62 is located below the exhaust gas heat exchanger 23b and the front side plate 37a
When it is removed, it faces the outside, and can be removed from the outside. The oil filter bracket 5
Since there is v, even if the attachment / detachment bracket of the oil filter 62 is damaged, only the bracket 5v needs to be replaced.

The oil filter 62 is located below the discharge port 61a of the oil pump 61 and the inlet of the oil passage 63a to the engine side. Does not come off even when the oil pump 61 is stopped for a long time. Also, by appropriately setting the shape of the bracket 5v, the mounting position and mounting direction of the oil filter 62, the height relationship with the pump outlet and the lubricating oil level can be freely set, thereby improving workability such as oil replacement and maintenance. It is possible to cope with the downsizing of the engine 5.

Next, the operation and effect of this embodiment will be described. During the cooling operation, the four-way valve 15 is switched to the outdoor heat exchanger side shown in FIG. The refrigerant gas that has been compressed by the compressors 6 and 6 and has become high temperature and high pressure
a, the refrigerant is supplied to the outdoor heat exchangers 11 and 12 for the refrigerant via the four-way valve 15 and the refrigerant pipe 16b, where it is cooled and liquefied by outside air. The liquefied high-pressure refrigerant liquid is supplied to the refrigerant line 1
The pressure is reduced by the expansion valve 18 of the refrigerant pipe 17a through the main accumulator 8 by 6c. The decompressed low-pressure refrigerant liquid evaporates by removing heat from the indoor air in the indoor heat exchanger 4, and the evaporated heat causes a cooling effect to cool the room. The evaporated refrigerant gas passes from the refrigerant line 17b, passes through the four-way valve 15, the refrigerant line 16d, returns to the compressor 6 through the main accumulator 8, the sub-accumulator 9, and the same cycle is repeated.

During the heating operation, the four-way valve 15 is switched to the indoor heat exchanger side, and the high-temperature, high-pressure refrigerant gas from the compressors 6, 6 is passed through the refrigerant pipes 16a, 17b. , Where it is cooled and liquefied by the room air, and the condensing heat in this case warms the room air to obtain a heating effect. The liquefied refrigerant liquid is decompressed by the expansion valve 18. The decompressed low-pressure refrigerant liquid evaporates by removing the heat of the outside air in the outdoor heat exchangers 11 and 12 and evaporates, and the main accumulator 8 and the sub accumulator 9
, And the same cycle is repeated.

The heat exchange in the outdoor heat exchange chamber 14 is performed as follows. The outdoor heat exchange blower fan 44
, The outside air is sucked into the outdoor heat exchange chamber 14 from the wire meshes 38a and 38b and discharged upward from the opening 37f of the ceiling. In this case, as shown in FIG. 2, air flows in a substantially horizontal direction in the upper part of the outdoor heat exchange chamber 14 because it is close to the blower fan 44. Since the upper heat exchanger 11 is arranged vertically, air passing through the upper heat exchanger 11 flows in a direction substantially perpendicular to the upper heat exchanger 11 as shown by an arrow a. Therefore, the air flow rate can be made uniform over substantially the entire surface, and the heat exchange rate can be improved.

On the other hand, in the lower part of the outdoor heat exchange chamber 14, air flows obliquely upward because it is far from the blower fan 44.
On the other hand, since the lower heat exchangers 12 and 13 are inclined so that the lower ends are located inside, they flow in a direction substantially perpendicular to the lower heat exchangers 12 and 13. Also in this case, the heat exchange rate can be improved as described above.

According to the present embodiment, since the engine 5 is inclined forward with the inclination axis X such that the upper part of the engine 5 is closer to the front side plate 37a, the engine 5 is inspected by removing the front side plate 37a. Lubricating the capped lubrication port 5x provided on the cylinder head cover 5d,
Most operations required for adjusting tappet clearance and maintaining the engine, such as waste oil from the oil drain 5u of the oil pan 5b, inspection of the oil level gauge 5z, etc., can be easily performed from the front, and the engine is oriented vertically. The maintainability can be improved as compared with the case.

Since the engine 5 has been inclined forward,
The portion of the cylinder block far from the front side plate 37a is located at a high place. Therefore, when the conventional structure for supporting the cylinder block is adopted in the engine mount, the support bracket at the far portion becomes long.
In the present embodiment, the bracket plate 81a is fixed to the lower portion of the oil pan 5b by bolts for the support bracket 81 of the oil pan 5b far from the front side plate 37a. The bracket can be shortened, and as a result, it is not necessary to use a support bracket having high rigidity and strength or separately add a reinforcing member, and it is possible to avoid an increase in weight and an increase in cost. Further, when supporting the above-mentioned on pan 5b, the bracket plate 81a of the support bracket 81 is used.
Is supported by a highly rigid portion such as a corner between a vertical wall and a bottom wall at the end of the oil pan 5b, so that the oil pan 5b can be prevented from being deformed without requiring special reinforcement. The bearing portion 77 is formed integrally with the oil pan 5b of the present embodiment, and the rigidity of the oil pan itself is increased. From this point, it is possible to avoid troubles caused by supporting the oil pan itself. Further, the cylinder block is supported at a portion near the front side plate 37a side, but since the cylinder block position is low at this portion, the support bracket does not become long. Furthermore, since the transmission 92 supports the gear case 92a coupled to the engine 5, it is possible to prevent the engine weight and external force from excessively acting on the oil pan 5b.

In this embodiment, since the inspection window 78 is formed in the skirt portion of the cylinder block 5a of the engine 5, it is easy to inspect the condition of the bearing of the crankshaft 65, the large end of the connecting rod 5f, and the like. be able to. Also,
Since the inspection window 78 is formed between the adjacent cylinders, the connecting rod connecting portions of both cylinders can be inspected from one opening, and only a minimum inspection window is required.

When the crankshaft 65 is rotated,
The extension of the line connecting the heads of the connecting bolts 200, 200 is
The inspection window 78 matches the inspection window 78, and the size of the inspection window 78 is large enough to allow the connecting rod 5f, the connecting rod cap 5f 'and the piston 5e to pass therethrough. 5e, connecting rod 5f, connecting rod cap 5f ', etc. can be replaced.

Further, since the inspection window 78 is provided above the upper limit oil level of the lubricating oil, it is not necessary to once remove the lubricating oil from the oil pan 5b and to remove the oil pan 5b. It can be done in a short time.
Further, since the inspection window 78 faces the front side plate 37a, the work can be easily performed from the front outside of the apparatus by removing the front side plate 37a. That is, inspection work,
The operation of replacing the lubricating oil and the like can be performed without removing the engine 5 from the inside of the casing 31.

In the engine 5 of this embodiment, the lubricating oil from the oil pump 61 is distributed and supplied to each lubricated portion of the engine system via the main gallery 63.
B and a transmission gear lubrication system for distributing and supplying the lubricating oil from the oil pump 61 from an upstream side of the main gallery to each lubricated portion of each gear system via an oil passage 96 formed in a gear case 92a of the transmission 92. C, the lubricated parts of the engine and the transmission can be reliably lubricated.

In this case, the oil pump 61 is disposed in the vicinity of the joint surface of the gear case 92a of the engine case (oil pan 5b), and the oil passage to the transmission is formed from the portion of the cylinder block 5a near the gear case 92a side to the gear case 92a. The transmission 92
The oil passage length to the lubricated part can be shortened, and sufficient lubricating oil can be immediately supplied to the transmission, especially when the engine is started,
As a result, the durability of the transmission can be improved.

Further, since the lubricating oil is distributed to the engine system and the transmission gear system on the upstream side of the main gallery 63, the pressure of the lubrication oil to the transmission gear system can be ensured. The time required for the lubricating oil to reach each lubricated portion of the transmission gear system can be shortened, lubrication can be smoothly performed at the time of starting the engine, and the durability of the transmission 92 can be improved.

Further, in this embodiment, a gear case 92a is oil-tightly connected to the end openings of the cylinder block 5a and the oil pan 5b constituting the engine case of the engine 5, and the inside of the space of the gear case 92a on the engine case side. Gears 93a, 93b, 94a-94c can be used also as a side cover of the engine, and a case that separates the engine case and the gear case such as a transmission device provided separately from the conventional engine. The wall can be dispensed with, the transmission 92 can be arranged without increasing the overall length of the engine, and the size can be reduced.

In this embodiment, since the PTO shaft 92b is cantilevered by the bottom wall 92d of the gear case 92a, the transmission 92 can be made compact from this point, and the gear case 92a can be easily removed from the engine case together with the transmission gears. Can be removed to improve inspection and maintenance. Furthermore, in the present embodiment, the transmission 92 and the compressor 6
In connection with the compressor, a structure is employed in which the bolt 95c of the flange 6c on the compressor 6 side is inserted into the rubber bush 95f on the transmission 92, so that connection and removal of the compressor are easy and vibration due to torque fluctuation and the like is reduced. Can be absorbed.

Further, in this embodiment, the oil filter 62
Is located below the discharge port 61a of the oil pump 61 and below the oil passage 63a at the engine-side inlet.
The lubricating oil can always be stored in the oil filter 62, and does not come off even when the oil pump 61 is stopped for a long time. Therefore, when the engine 5 is restarted after being stopped for a long period of time, it is not necessary to fill the oil filter 62 with the lubricating oil, and the lubrication system can be started up accordingly.

Further, since the oil filter 62 is fixed to the engine 5 via the bracket 5v, the height relationship with the pump discharge port 61a, the oil level and the like can be set freely, and the oil filter 62 can be freely mounted in the mounting direction. The degree is high, and the layout can be improved.

[0079]

According to the engine-integrated transmission according to the present invention, the gear case is oil-tightly connected to the end opening of the engine case in the crankshaft direction, and the driven case meshes with the drive gear of the crankshaft in the gear case. Since the gears are arranged and the output shaft of the driven gear is rotatably supported by the gear case in a cantilever manner, while improving power transmission efficiency and durability,
This has the effect of reducing the size and weight of the entire engine. Further, the degree of freedom in gear ratio design can be improved, the assemblability of each gear group can be improved, the arrival time of lubricating oil can be shortened, and lubricating oil management can be simplified.

[Brief description of the drawings]

FIG. 1 is a partial cross-sectional front view of an air conditioner to which an engine-integrated transmission according to one embodiment of the present invention is applied.

FIG. 2 is a partial cross-sectional rear view of the apparatus of the embodiment.

FIG. 3 is a partial cross-sectional right side view of the apparatus of the embodiment (II in FIG. 2).
(I-III line sectional view).

FIG. 4 is a left side view (IV in FIG. 2) of a partial cross section of the apparatus of the embodiment.
-IV line sectional view).

FIG. 5 is a plan view showing a floor member portion of an outdoor heat exchange chamber of the apparatus of the embodiment.

FIG. 6 is a cross-sectional plan view showing an engine room and a piping room of the apparatus of the embodiment.

FIG. 7 is a system diagram showing an entire configuration of the apparatus in the embodiment.

FIG. 8 is a partial sectional side view of the engine of the embodiment.

FIG. 9 is a schematic diagram showing a lubrication system of the engine of the embodiment.

FIG. 10 is a left side view of the engine of the embodiment.

FIG. 11 is a rear view of the engine of the embodiment.

FIG. 12 is a schematic front view of the engine of the embodiment.

FIG. 13 is a partially sectional plan view showing a transmission of the engine of the embodiment.

FIG. 14 is a right side view showing the transmission of the engine in the embodiment.

FIG. 15 is a left side view showing the transmission of the engine in the embodiment.

FIG. 16 is a sectional view showing a lubricating device for the engine of the embodiment.

FIG. 17 is a system diagram showing a lubricating oil system of the apparatus of the embodiment.

[Explanation of symbols]

Reference Signs List 5 engine 5a cylinder block (engine case) 5b oil pan (engine case) 5g crankshaft 92 transmission 92a gear case 92b PTO shaft (output shaft) 93a, 93b driven gear 94a, 94b drive gear

Continuation of the front page (58) Field surveyed (Int.Cl. ⁷ , DB name) F02B 61/06 F01M 1/12 F02B 63/06 F02B 67/04

Claims (1)

(57) [Claims] An engine case rotatably supports a crankshaft , and a crankshaft direction of the engine case.
A gear case is oil-tightly connected to the end opening, and the gear case is
End of the crankshaft protruding into the space on the engine case side
3rd driving gear, 2nd driving gear, 1st driving gear
And the first and second driven teeth meshing with the first and second drive gears
Place the car in the space on the engine case side of the gear case
The engine is rotatably supported by the engine case.
From the inside of the case to the engine case side of the gear case
The third drive gear meshes with the end of the camshaft protruding into the space.
And fixed to the above-mentioned first driven gear
The first output shaft and the second output shaft fixed to the second driven gear.
The first and second bearings are provided on a gear case, respectively.
The cantilever is supported rotatably by bearings, and the first and
2 Make the outer end of the output shaft protrude from the gear case,
Engine from the oil pump to the lubricated part of the engine.
Branch from the middle of the lubrication system,
The first to third drive gears, the first and second driven gears, the cam
An engine-integrated transmission , wherein a lubrication path for supplying lubricating oil to a shaft drive gear is provided .