JP4312695B2 - Engine-driven air conditioner for lubricating oil supply - Google Patents

Description

  The present invention relates to an engine-driven air conditioner for lubricating oil supply in which lubricating oil is replenished according to the amount of lubricating oil consumed.

  A four-cycle engine lubrication device, for example, stores lubricating oil in an oil pan, pumps the lubricating oil by an oil pump, and supplies oil to lubricated parts such as a crankshaft journal part, a camshaft journal part, and a valve mechanism. Is configured to do. In the case where this type of lubricating device is provided, in order to continuously operate the engine for a long time, it is necessary to replenish the oil pan with an amount of lubricating oil corresponding to the amount of consumption of the lubricating oil.

  As a lubricating oil supply device for an engine that replenishes lubricating oil according to such lubricating oil consumption, conventionally, for example, as disclosed in JP-A-3-246310, the engine operating time is integrated. In some cases, lubricating oil is supplied to the oil pan every time the accumulated operation time reaches a reference time.

  By the way, in the case of the above-described conventional device in which the lubricating oil is simply replenished in accordance with the engine operating time, if there is an abnormality in the oil level sensor or the like, the amount of lubricating oil corresponding to the amount of lubricating oil consumption is reliably replenished. I can't do it.

  The present invention has been made in view of the above-described conventional situation, and it is an object of the present invention to provide a lubricating oil supply engine-driven air conditioner capable of detecting an abnormality in an oil level sensor or the like. It is said.

The present invention, the cumulative value of the engine rotational speed to open the replenishing oil valve during supplementation during engine stop after exceeding the predetermined value, the oil level is at the upper limit and the replenishment oil valve closing the lubricating oil supply for driving the engine a formula air conditioner, when the oil level has passed the time more defined until the upper limit is to notice that servicing is required, close the replenishing oil valve, reset the data The feature is that the operation is terminated.

  According to the present invention, the replenishment of the lubricating oil is started and the replenishment is stopped when the oil level reaches the upper limit. Even before the signal indicating that the oil level has reached the upper limit, the replenishment is stopped even if the specified time has elapsed since the start of the lubrication oil replenishment. It will be announced that it is necessary.

  As described above, according to the present invention, the replenishment is stopped when the oil level reaches the upper limit, and the replenishment is also stopped when a time longer than the specified time has elapsed since the start of the lubricating oil replenishment. Since the advance notice of the need for inspection and maintenance is provided, it is possible to detect any abnormality in the oil level sensor or the like.

  Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.

  1 to 36 are for explaining an engine-driven air conditioner according to an embodiment of the present invention. FIGS. 1 to 4 are a front view, a rear view and a right side view of the apparatus (of FIG. 2). III-III cross-sectional view), left side view (IV-IV cross-sectional view of FIG. 2), FIG. 5 is a schematic plan view of the floor of the outdoor heat exchange chamber, and FIG. 6 is a schematic cross-sectional plan view of the engine room and the piping chamber. 7, FIG. 7 and FIG. 8 are partially sectional right side views of the engine, FIG. 9 is a partially sectional front view, FIG. 10 is a diagram showing the flow of lubricating oil, FIG. 11 is a diagram showing an oil separation chamber, and FIG. FIG. 13 is a cross-sectional front view showing an air cleaner and intake pipe connection procedure, FIGS. 14 to 17 are diagrams for explaining various piping systems, and FIGS. 18 to 30 are diagrams showing respective main parts. 31 to 34 are general configuration diagrams, FIG. 35 is a flowchart, and FIG. 36 is a schematic view of a water supply port portion.

  In FIG. 31 which shows the whole structure of a present Example apparatus with a diagram, 1 is an engine drive type air conditioner, and this is comprised by the outdoor air conditioning unit 2 and the indoor air conditioning unit 3. In FIG. The indoor air conditioning unit 3 includes a refrigerant indoor heat exchanger 4, an expansion valve 18 for decompression, and a blower fan for indoor heat exchange (not shown). The outdoor air conditioning unit 2 includes an engine room 7 in which an engine 5, a compressor 6, 6 and the like are arranged, a main accumulator 8, a sub accumulator 9, an electrical box 50, and pipes for connecting the devices to each other. A piping chamber 10 provided; and an outdoor heat exchange chamber 14 in which an upper and lower heat exchangers 11 and 12 for refrigerant, an engine cooling water heat exchanger (hot water heat exchanger) 13 and the like are disposed. Yes. As can be seen in FIG. 4, the upper heat exchanger 11 has two symmetrical ones arranged upside down, but in FIG. 31, only one is shown for convenience.

  The engine 5 is a water-cooled gas fuel engine. An intake pipe 21a is connected to an intake port of the engine 5, and a gas mixer 21b and an air cleaner 21c are interposed in the intake pipe 21a. It penetrates the ceiling wall of the engine room 7 and the ceiling wall of the outdoor heat exchange chamber 14 and opens to the outside. The intake pipe 21a may be opened in the engine room 7 as will be described later.

  The gas mixer 21b is connected to a supply pipe from an external gas fuel source in the terminal chamber 22 through a gas pipe line 22d. A flow rate control valve 22a, a zero governor (pressure reducing valve) 22b, and two electromagnetic valves 22c integrated with the gas mixer 21b are interposed in the gas pipe line 22d. An exhaust pipe 23a is connected to the exhaust port of the engine 5, and an exhaust gas heat exchanger 23b, an exhaust silencer 23c, and a mist separator 23d are interposed in the exhaust pipe 23a. It opens to the outside of the chamber 14. The mist separator 23d may be disposed outside the top wall of the heat exchange chamber 14, as will be described later with reference to FIG. Reference numeral 24a denotes an oil tank for storing lubricating oil. When the amount of lubricating oil in the oil pan decreases, the electromagnetic valve 24b is opened by a lubrication control device described later, and the lubricating oil is supplied by gravity.

  The compressors 6 and 6 are connected to the output shaft of the engine 5 via clutches 6a and 6a. The discharge port of the compressor 6 is connected to the refrigerant outdoor upper and lower heat exchangers 11 and 12 through the refrigerant pipes 200 and 16a, the four-way valve 15 switched to the cooling operation position, and the refrigerant pipe 16b. The two heat exchangers 11 and 12 are connected to the refrigerant pipe 17a from the refrigerant indoor heat exchanger 4 in the terminal chamber 22 via the refrigerant pipe 16c, the heat exchanger in the main accumulator 8, and the refrigerant pipe 101. 101a is connected. In addition, 102 is a dryer, 103 is a filter which bypasses this.

  The refrigerant pipe 17b from the indoor heat exchanger 4 is connected to the refrigerant pipe 100 from the outdoor unit in the terminal chamber 22 by a joint 100a. The refrigerant pipe 100 is connected to the suction ports of the compressors 6 and 6 through the four-way valve 15, the refrigerant pipe 16 d, the main accumulator 8, the refrigerant pipe 202, the sub accumulator 9, and the refrigerant pipe 201. Reference numerals 300 and 301 are capillaries, and 210 and 210 are combinations of temperature detectors and capillaries, respectively, for detecting the level of the liquid-phase refrigerant in the accumulator 8 by detecting the cooling temperature. is there. Reference numeral 302 denotes an on-off valve, and 303 denotes an oil discharge passage. When the amount of oil accumulated in the lower part of the accumulator increases, the on-off valve is opened manually or automatically so that oil flows from the 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, the oil strainer 19b, is returned to the main accumulator 8 through the electromagnetic valve 19c that opens when the predetermined value is exceeded. The lubricating oil is also returned to the sub accumulator 9. The refrigerant pipe line 16a is connected to the main accumulator 8 through an oil strainer 20a and an electromagnetic valve 20b that opens when the pipe pressure is equal to or higher than a predetermined pressure, thereby avoiding an abnormal rise in refrigerant pipe pressure.

  Further, regarding the cooling of the cooling jacket 28b of the engine 5, when the cooling water temperature is below a predetermined value, the cooling water pump 28a, the water pipe 29a, the cooling jacket 28b, the water pipe 29a ', the switching valve (thermostat valve) 28c, the water pipe A cooling jacket circulation circuit (engine cooling water circulation circuit), which is one of the low-temperature circulation circuits for circulating the cooling water through the 29 s path, is configured.

  When the cooling water temperature exceeds a predetermined value, the cooling water pump 28e, the water pipe 29e, the exhaust gas heat exchanger 23b, the water pipe 29e 'the cooling water pump 28a, the water pipe 29a, the cooling jacket 28b, and the water pipe 29a'. , A switching circuit 28c, a water pipe 29b, a three-way valve 28d, a water pipe 29c, a cooling water heat exchanger 13, water pipes 29d, 29p, and a cooling water pump 28e are circulated at high temperature. ing. When the switching valve 28c 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. Thereby, the exhaust heat of the exhaust gas heat exchanger 23b passes through the three-way valve 28d and is discarded in the heat exchanger 13 for cooling water, or is given to the refrigerant by the heater 29g of the accumulator 8. This makes it possible to use exhaust heat even during warming up at the time of start-up, and is effective particularly when quick rise of heating is required.

  In the cooling system, reference numeral 30a denotes a cooling water reservoir tank, which is connected to the cooling water heat exchanger 13 through a water pipe 30c and an inlet 30b. As will be described later, an inlet independent of the inlet 30b is disposed in the upper part of the cooling water reservoir tank, and one port of the switching valve 28c is also connected to the inlet 30b. Yes. The port is always in communication with the cooling water jacket 28b through a throttle, thereby enabling air to be vented from the cooling jacket circulation circuit. 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 conduit 29d, thereby supplying heat to the refrigerant. 90 is an electromagnetic valve, and 89 is an oil strainer. When the load on the indoor unit 4 during cooling becomes particularly small, the electromagnetic valve 90 opens, and the refrigerant flows around the indoor unit 4 to the accumulator 8 to balance the load. I try to take it.

  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 mounts and fixes a floor plate 33 on a pair of bases 32, and supports columns 34 at four corners, with the upper ends of the four columns 34 on the right side and the left side. On the surface, each is connected by a ceiling beam (not shown), and the front and rear ends of the floor plate 33 are bent to form a floor beam 33a. The left and right side surfaces are left, and the right side plates 37c and 37d are used. Each of the structures is covered with a plate 37e. The ceiling plate 37e is formed with a connecting portion with each side plate or with each column 34 by bending the front, rear, left and right end portions. Further, as shown in FIG. 34, left and right front plates 37 a and 37 a whose upper ends are bent are respectively fastened to the front side surfaces by folding screws 35 on bent engine room side partition plates 41 a and 41 b. Similarly, the left and right rear plates 37b and 37b are attached to the pipe chamber side partition plates 42a and 42b, which are bent at the rear side, as viewed from the front with the upper ends bent. The front and rear plates 37a and 37b cover the lower portions of the front and rear sides of the casing 31, and the left and right plates 37c and 37d cover the entire left and right sides of the casing 31. These front, rear, left and right side plates 37a to 37d are detachable in order to ensure maintainability of each device.

  Further, the upper portions of the front and rear side plates 37a and 37b of the casing 31 are openings for introducing outside air, and wire meshes 38a and 38b functioning as filters are respectively formed in the horizontal frames 36a and 36b. Removably attached to the top and bottom of the. The top plate 37e is formed with a discharge opening 37f for discharging the introduced outside air upward. The discharge opening 37f allows the outside air to enter the outdoor heat exchange chamber 14 from the metal meshes 38a and 38b. An outdoor heat exchange blower fan 44 that is sucked and discharged above the outdoor heat exchange chamber 14 is disposed. Reference numeral 38c denotes a wire mesh erected around the discharge opening 37f.

  The partition plate 39 is for defining the outdoor heat exchange chamber 14, the engine room 7, and the piping chamber 10. The central partition plate 40 that forms the ceiling of the engine room 7, and the engine room side partition plate 41a and 41b, and the piping chamber side partition plates 42a and 42b which comprise the ceiling of the piping chamber 10 are comprised. The engine room side partition plates 41a and 41b and the piping chamber side partition plates 42a and 42b are detachable upward. At the time of removal, the front and rear plates 37a and 37b are also removed, the engine room 7 is opened at the ceiling, the front, and both corners, and the piping chamber 10 is at the ceiling, the rear, and both corners. The part is opened, and the maintenance work of the equipment in each room is easy.

  In addition, a horizontal rod 48 (on the upper side on the side of the piping chamber 10) is formed at the boundary between the central partition plate 40 and the piping chamber side partition plates 42 a and 42 b and on the outer upper side (upper side of the piping chamber 10) of the rear middle plate 44 a constituting the rear side wall of the engine room 7. A drainage passage) is disposed so as to be disassembled from the center and piping chamber side partition plates 40, 42a and 42b, that is, exchangeable with a new one. The horizontal gutter 48 is a groove extending in the longitudinal direction of the outdoor air conditioning unit 2 (left and right direction in FIG. 2), that is, in the direction of the arrangement surface of the heat exchanger. It is inclined. The high end portion 48b located at the highest position of the horizontal bar 48 can be exposed to the outside by removing the right side plate 37d or by providing an opening (cleaning hole). The central partition plate 40 may cover the horizontal rod 48 with a V shape, and a plurality of rainwater dropping holes may be provided on the V-shaped bottom above the horizontal rod 48.

  A cylindrical vertical gutter (drainage pipe) 43 is detachably connected to the lower end portion 48a located at the lowest position of the horizontal gutter 48. The vertical shaft 43 extends downward in a corner portion formed by the inner surface of the left side plate 37 c and the outer surface of the rear middle plate 44 a of the engine room 10, and a drain port 43 a opened at the lower end thereof is positioned below the floor plate 33. And facing outwards. The vertical rod 43 can be replaced with a new one by removing the left side plate 37c.

  The engine room side partition plates 41a and 41b, the piping chamber side partition plates 42a and 42b, and the central partition plate 40 are inclined so as to become lower toward the side rail 48 side. For this reason, rainwater or the like that has entered the outdoor heat exchange chamber 14 is immediately collected by the horizontal gutter 48 and discharged to the outside through the vertical gutter 43. Further, the inclination increases the positions of the outer end portions of the engine room side partition plates 41a and 41b and the piping chamber side partition plates 42a and 42b, and the opening when the front and rear side plates 37a and 37b are removed to inspect and maintain the interior. Is getting bigger.

  The central partition plate 40 is formed with ventilation air discharge ports 40 b at two locations so as to open into the outdoor heat exchange chamber 14. The discharge port 40b is surrounded by a silence box 40c. Further, the opening 40d of the silencing box 40c is located above the reed 48 and is located downstream of the reed 48 with respect to the discharge port 40b. This prevents rainwater or the like that has entered the outdoor heat exchange chamber 14 or rainwater or the like flowing in the side wall 48 from entering the engine room 7 from the discharge port 40b. A sponge-like sound absorbing sheet is attached to the inside of the sound deadening box 40c.

  The engine room 7 has side walls composed of the front side plate 37a, left side plate 37c, rear middle plate 44a, and right middle plate 44b, and the top wall is composed of the engine room side partition plates 41a and 41b and the central partition plate 40. In addition, the bottom wall is composed of a bottom plate 45 disposed with a space between the bottom plate 33 and the floor plate 33. The upper and lower end surfaces of the rear middle plate 44a and the right middle plate 44b are airtightly connected to the partition plate 39 and the floor plate 33, and thus the engine room 7 is configured as a soundproof structure.

  The space between the bottom plate 45 and the floor plate 33 is a box-like 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 over the entire surface. Almost evenly arranged. Further, two engine room air intakes 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 intakes 46a. ing. Here, the drainage port 43a of the vertical shaft 43 is provided on the opposite side of the engine room air intake 46a, that is, at a position sufficiently separated from the air intake 46a.

  On the inner surface side of the rear plate 37b in the piping chamber 10, there are disposed an electrical box 50 in which various control devices and the like are accommodated and a terminal chamber 22 for connection with external piping. An air intake port 50 a is formed on the bottom surface of the electrical box 50, and a discharge port 50 b is formed on the upper side surface. A gap serving as an air passage is formed between the bottom surface and the floor plate 33. The floor plate 33 is formed with a piping chamber air inlet 33b for introducing outside air into the piping chamber 10, and the outside air is introduced into the piping chamber 10 through the air inlet 33b. Further, a part of the introduced outside air is introduced into the electrical box 50 from the air intake port 50 a and discharged from the discharge port 50 b to ventilate the box 50. In addition, the drainage port 43a of the vertical shaft 43 is located at a position away from the piping chamber air intake port 33b and below the air intake port 33b.

  There is no floor plate 33 below the terminal chamber 22 and there is no ceiling. The terminal chamber 22 is a communication path that connects the piping chamber 10 and the outside of the casing 31. Further, the terminal chamber 22 is opened to the rear and outside with the rear side plate 37b removed. The joints 100a and 101a of the refrigerant pipes 100 and 1001 and the joint of the gas pipe 22d are located in the terminal chamber 22 and are connected to external pipes introduced from below the terminal chamber 22, respectively. A power cord 600 or the like connected to an external power source is also extended to the outside from below the terminal chamber 22. Since the external piping is routed toward the lower side of the terminal chamber 22, the outer size of the casing 31 becomes compact, and the piping chamber 22 also serves as a piping chamber air intake.

  The refrigerant outdoor upper heat exchangers 11, 11 are located at the front and rear upper portions of the outdoor heat exchange chamber 14, the refrigerant outdoor lower heat exchanger 12 is located at the rear lower portion, and the engine is located at the front lower portion. Cooling water heat exchangers 13 are respectively provided. Here, the upper heat exchangers 11 and 11 are arranged in the vertical direction and along the wire nets 38a and 38b, whereas the lower outdoor heat exchanger 12 and the cooling water heat exchanger 13 are The lower portion is disposed so as to be located on the inner side, and the cooling water heat exchanger 13 is provided with the above-described water injection port 30b at the upper right end portion thereof.

  Here, as shown in FIGS. 3, 19, and 23, the water injection port 30b is connected to the upper end of the head pipe of the cooling water heat exchanger 13 disposed obliquely upward via a rubber hose 13c. A water supply tube 60, a cap 61 that opens and closes an opening 60 a of the water supply tube 60, and a pressure valve 62 disposed in the cap 61 are provided. In front of the opening 60a, a right end portion of the horizontal frame 36a constituting the side wall of the casing 31 of the outdoor air conditioning unit 2 and an opening provided in the column 34 and a lid member 63 capable of opening and closing the opening are disposed. . The pressure valve 62 opens and closes a valve seat port 60b formed in the intermediate portion of the water supply cylinder 60 with the valve body 62b. The valve body 62b is urged in the closing direction by a spring 62a. ing.

  The pressure valve 62 defines the maximum internal pressure of both circulation circuits of the cooling water. That is, when the internal pressure of the circulation circuit exceeds the valve opening pressure, the pressure valve 62 opens, and the remaining air, water vapor or hot water is guided to the cooling water reservoir tank 30a, and the circuit components are protected even if abnormal water vapor pressure occurs. It is possible.

  62c is a pressure valve that opens when the pressure difference between the outside and the inside of the circulation circuit exceeds a predetermined value and allows the flow from the outside to the inside. When the engine is stopped, the cooling water temperature falls, the water vapor in the circulation circuit condenses, the internal pressure falls below atmospheric pressure, and the pressure difference between the outside and the inside increases, the pressure valve 62c opens, and the cooling water reservoir tank The water inside is pushed up by atmospheric pressure and replenished into the circulation circuit.

  If the cap 61 is removed for checking the cooling water, the airtightness due to the seal 61a is lost, and the water in the conduit 30c returns to the reservoir tank 30a, and the water level drops. The water level gradually rises by repeated evaporation of water in the circuit due to engine operation, movement of water vapor through the pressure valve 62 to the reservoir tank 30a, and water level rise corresponding to the amount of water vapor moved by engine stop. However, although the circulation circuit can be replenished, there is a possibility that the amount of cooling water is insufficient until then. However, in this embodiment, since the water injection port 30b is arranged at the end of the engine cooling water heat exchanger 13 arranged in the low place, the position of the water supply tube 60 becomes low, and the water level rises so fast that the amount of cooling water is reduced. It is hard to run out. Accordingly, heat exchange in the accumulator 8 or the cooling water heat exchanger 13 can be sufficiently performed. This is because the time until replenishment can be shortened even if the generated vapor pressure decreases due to heat exchange. The lower end portion of the cooling water heat exchanger 13 is located on the upper corner portion of the central partition plate 40 and the silencer box 40c beyond the engine room side partition plates 41a and 41b. Moreover, the lower end part of the refrigerant | coolant outdoor lower heat exchanger 12 is located on the lower corner part of the center partition plate 40 and the silencing box 40c beyond the horizontal wall 48 from the piping chamber side partition plates 42a and 42b.

  Here, the pipes 29 c, 29 d, 16 b, 16 c, and 30 c connected to the cooling water heat exchanger 13, the refrigerant heat exchangers 11, 12 and the devices in the pipe chamber 10 are on the right side of the pipe chamber 10. The tube bundle P is arranged on the side of the plate 37d and at the center in the front-rear direction, and this tube bundle P penetrates through one sealing pad 49 disposed at the right end portion of the central partition plate 40. P is sealed by one pad. The sealing pad 49 has notches 49a that connect the respective duct holes and the end portions on the left side plate 37c side. Thus, after the piping is completed, the sealing pad 49 can be fitted into the piping from the right side with the right side plate 37d removed. The periphery of the sealing pad 49 forms a sealed state with the central partition plate 40 and the right side plate 37d, thereby partitioning the piping chamber 10 and the heat exchange chamber 14. The pipes connected to the heat exchangers 11 to 13 are routed obliquely along the oblique arrangement of the lower heat exchangers 12 and 13.

  The engine 5 of this embodiment is a water-cooled parallel 4-cylinder OHV engine, and in the engine room 10, the crankshaft 5 g is oriented parallel to the front plate 37 a of the engine room, and the cylinder shaft is closer to the front plate 37 a as the upper part is located. It is arranged in a forward inclined state with an inclination axis X inclined so as to be fixed to the floor plate 45 through an engine mount 81 made of an elastic body arranged at four corners.

  As shown in FIGS. 7 to 9, the engine 5 of this embodiment has an oil pan 5b bolted and fixed to the lower joint surface of the cylinder block 5a, and a cylinder head 5c fastened to the upper joint surface with a head bolt. The head 5c is covered with a head cover 5d. A piston 5e that is slidably inserted in the cylinder bore of the cylinder block 5a is connected to a crankshaft 5g by a connecting rod 5f, and a valve train 5h is disposed in the cylinder head 5c. The valve train 5h is configured to open and close an intake valve 5i and an exhaust valve 5i 'with a camshaft 5l disposed in the vicinity of the crankshaft 5g via a rocker arm 5j and a push rod 5k.

  In the engine 5 of the present embodiment, the cylinder block 5a has a one-block structure in which four cylinders are integrated, whereas the cylinder head 5c is divided into one for two cylinder bores, that is, two sets. Corresponding to this, two sets of head covers 5d are also provided. A breather chamber 5m is formed in each of the head covers 5d.

  Next, the intake / exhaust system, the lubrication system, and the cooling system in the engine 5 of this embodiment will be described. Each intake port 5p of the engine 5 is led to the upper side of the inclined axis X, and an intake manifold 73 'connected to each intake port 5p extends toward the right side plate 37d in the direction of the crankshaft 5g. Is connected to a gas mixer 21b, which is connected to the air cleaner 21c disposed above the compressor 6 in the engine room 10 by an intake hose 21a '.

  As shown in FIGS. 24 and 25, the air cleaner 21c is a combination of an intake silencer portion 77 and an air cleaner portion 78, and a central portion is integrally formed. The intake pipe 21a is connected to the air inlet 77a of the intake silencer section 77, and the intake hose 21a 'is connected to the air outlet 77b. The air cleaner portion 78 has a structure in which an element 78b is inserted and disposed in a casing 78a. The upstream side of the silencer portion 77 communicates with the inside of the element 78b, and the downstream side communicates with the outside.

  The casing 78a has an opening 78c for inserting and removing an element, and a lid 78d is detachably attached to the opening 78c. The air cleaner 21c is disposed so that the lid 78d faces the front side plate 37a. Thus, by removing the front side plate 37a, it is possible to easily perform maintenance such as cleaning and replacement of the elements of the air cleaner 21c.

  Further, fresh air introduced from the hole inlet 77a enters the expansion chamber 77d and is bent in the direction along the outer periphery of the element 78b by the guide blade 78e from the communication hole 77e between the intake silencer 77 and the air cleaner 78. Guided to section 78. The fresh air that has passed through the element 78b returns to the air cleaner section 78 and reaches the air outlet 77b through the expansion chamber 77f. The expansion chambers 77d and 77f are silenced, and the wide surface of the element 78b can contribute to dust removal by the guide vanes.

  The air inlet 77a of the air cleaner 21c and the intake pipe 21a are connected by the structure shown in FIG. Note that FIG. 13 shows both the intake system connection structure and the exhaust system connection structure in one figure. The numbers without parentheses indicate the intake system connection structure, and the numbers with parentheses indicate the exhaust system connection structure. It is for showing each. An opening 40e having a diameter larger than that of the air inlet 77a is formed in the central partition plate 40 constituting the wall of the engine room 7 and the outdoor heat exchange chamber 14, and the opening 40e is fitted and fitted to the air inlet 77a. A body-made seal member 77d is fitted and inserted. At this time, the air cleaner 21c is fixed to a bracket (not shown) provided on the central partition plate 40 by bolting or the like so that the seal member 77d is pressed against the lower surface of the central partition plate 40 by the air cleaner 21c. Then, the lower end of the intake pipe 21a is fitted and mounted on the upward projecting portion of the air inlet 77a and fixed by a fixing band 77e.

  The four exhaust ports 5q of the engine 5 are led out below the inclined axis X, and the exhaust gas heat exchanger 23b is directly connected to the external connection ports of these exhaust ports 5q, that is, without interposing the exhaust pipe. It is connected. As shown in FIGS. 7 and 30, the heat exchanger 23 b has a structure in which an inner fin type heat exchanging portion 73 located on the upper side and a screw type heat exchanging portion 74 located on the lower side are integrated. It is set longer than the interval between the exhaust ports 5q and 5q at both ends.

  The inner fin type heat exchanging portion 73 is formed using an exhaust passage, and an upper step portion and a lower step portion are bent and formed so as to have a substantially U shape in order to secure a necessary heat exchange area, The outer surface is surrounded by a cooling jacket 73a, and a large number of fins 73b are formed to protrude from the inner surface. The exhaust ports 5q communicate with the upper stage portion, and the water pipe 29e 'is connected to the cooling water outlet 73c of the cooling jacket 73a.

  Further, the screw type heat exchanging portion 74 has a cooling jacket (casing) 74a formed in a cylindrical shape, a number of helical screw pipes 74b disposed in the jacket 74a, and the upstream end of the pipe 74b connected to the inner fin. In this structure, the upstream end of the upstream chamber 74c into which the exhaust gas that has passed through the mold heat exchange section 73 is introduced is opened to the downstream chamber 74d. The downstream end portion of the screw pipe 74b is slidable with respect to the downstream chamber 74d side end portion of the cooling jacket 74a so as to absorb the amount of thermal expansion.

  A cooling water inlet 74e for introducing cooling water into the jacket 74a is formed below the cooling jacket 74a, and the water pipe 29e is connected to the cooling water inlet 74e. In FIG. 30, the flow direction of the exhaust gas is indicated by a broken line arrow, and the flow direction of the cooling water is indicated by a solid line arrow.

  An exhaust gas outlet 74g of the screw heat exchanger 74 is connected to the exhaust silencer 23c through an exhaust pipe 23a '. 74 h is a drain water outlet for guiding condensed water generated by cooling the water vapor contained in the exhaust gas to the neutralizer 82. The exhaust silencer 23c is disposed above the compressor 6 in the engine room 7 and adjacent to the air cleaner 21c. As shown in FIGS. 28 and 29, the exhaust silencer 23 c has a structure in which an oil separator portion 76 is integrally formed with a silencer portion 75.

  The silencer portion 75 is of a vertically divided type, and has a structure in which the inside is defined by a number of expansion chambers 75a and the expansion chambers 75a communicate with each other through a reduction tube 75b. The exhaust pipe 23a 'is connected to the exhaust gas inlet 75c of the silencer portion 75, and the exhaust pipe 23a is connected to the exhaust gas outlet 75d.

  The connection structure between the exhaust pipe (23a) and the exhaust gas outlet (75d) is the same as the air inlet 77a and the intake pipe 21a of the air cleaner 21c shown in FIG. That is, as shown by the reference numerals in FIG. 13, the seal member (75e) fitted to the exhaust gas outlet (75d) is pressed against the lower surface of the central partition plate 40 by the exhaust silencer (75), and the exhaust gas The exhaust pipe (23a) is connected and fixed to the protruding portion in the outdoor heat exchange chamber 14 at the outlet (75d). Needless to say, the sealing member must be made of a material having heat resistance according to the exhaust gas temperature. In addition, (40f) shows an opening larger in diameter than the exhaust gas outlet (75d), and (75f) shows a fixed band.

  The oil separator portion 76 has a structure in which an independent chamber 76a is integrally formed at the lower portion of the silencer portion 75 and on the front plate 37a side portion, and an element 76b is inserted and disposed in the chamber portion 76a. The illustrated upper side wall 76c and right side wall 76d of the chamber 76a are in common with the bottom wall of the silencer portion 76. An opening 76e for inserting and removing the element 76b is formed on the front plate 37a side of the chamber 76a. A lid 76f is detachably attached to the opening 76e. The lid 76f faces the outside of the casing 31 when the front plate 37a is removed.

  A breather hose 69 is connected to the breather air inlet 76g of the oil separator section 76, and a breather air outlet 76h provided on the left side of the oil separator section is connected to the breather air inlet 77c of the silencer 77 of the air cleaner 21c by the hose 79. It is connected. The breather hose 69 includes branch hoses 69a and 69b connected to the connection port 5n of the breather chamber 5m of each head cover 5d, a merge hose 69c that merges just above the breather chamber on the side close to the oil separator portion 76, The connecting hose 69e is connected to the T-shaped tube 69d and the breather portion inlet 76g. The lubricating oil separated by the oil separator 76 flows down through the walls of the connecting hose 69e and the T-shaped tube 69d, and is connected below the oil surface in the oil pan of the T-shaped tube 69d and the oil pan 5b. The oil is recovered from the oil recovery hose 80 in the oil pan 5b. Further, the connection port of the hose 80 to the oil pan is located above the drain plug 5v ′, thereby allowing the oil in the hose 80 to be drained by lifting the hose 80. The bottom wall of the oil separator portion is gently inclined from the back toward the front toward the breather portion inlet 76g to facilitate the discharge of the separated oil.

  A neutralizer 82 for neutralizing condensed water containing acid gas in the exhaust gas is disposed below the compressor 6 on the floor plate 45 of the engine room 7. A drain port 74h of the exhaust gas heat exchanger 23b, a drain port 75c 'of the exhaust silencer 23c, and a drain port 83a of the mist separator 83 are connected to the neutralizer 82 by drain hoses 84a, 84b, and 84c, respectively. Has been.

  As shown in FIGS. 32, 8 and 10, the lubrication system of the engine 5 of the present embodiment sucks up the lubricating oil in the oil pan 5b through the oil screen 61b by the oil pump 61 and passes through the oil filter 62. Then, it is configured to be pressure-fed to a main gallery 63 disposed at the center of the camshaft, and from there to be distributed and supplied to lubricated parts at various locations. 61a is a relief valve for maintaining the discharge pressure of the oil pump 61 below a predetermined value, 62a is a relief valve built in the oil filter 62, and bypasses the lubricating oil when the passing pressure of the oil filter 62 exceeds a predetermined value. A valve 63 a is an oil passage connecting the main gallery 63 and the oil filter 62.

  The lubrication system includes a first lubrication system A that supplies oil from the main gallery 63 to the journal 64 of the camshaft 5l, the journal 65 of the crankshaft 5g, and the large end 66 of the convolution 5f, and returns to the oil pan 5b. A second lubrication system B that supplies oil from the gallery 63 to each valve train 5h of each cylinder head 5c and returns to the oil pan 5b, and an output take-out shaft (PTO shaft) disposed in the middle gear case m from the oil filter 62b. ) Bearing 67 and a gear 68, and a third lubricating system C that returns the lubricating oil dropped to the bottom of the gear case m into the oil pan 5b.

  Here, in the lubrication system B, the oil passage 5t from the main gallery 63 to the tappet chamber in which the tappet 5j is arranged is provided in the same number as the number of cylinder heads 5c. In the present embodiment, only two sets of left and right are provided. The minimum quantity required. Further, at least one of the two oil passages 5t is provided with a throttle 5u, thereby adjusting the flow rate of the left and right oil passages. In this lubricating system B, the lubricating oil that has lubricated the valve operating system 5h returns to the oil pan 5b through the arrangement hole 5s of the push rod 5k. In the engine 5 of this embodiment, the engine tilt axis X is Since the arrangement hole 5s is arranged on the lower side, the lubricating oil is returned smoothly.

  Further, as described above, the breather chamber 5m formed in each head cover 5d is connected to the oil separator portion 76 from the breather outlet 5n via the breather passage 69, and the lubricating oil separated by the oil separator portion 76 is connected. The oil is returned to the oil pan 5b through the oil return hose 80. The oil return hose 80 extends downward along the right middle plate 44b of the engine chamber 7, extends to the center of the engine chamber along the bottom plate 45, and is connected to the vicinity of a mounting portion of an oil filter 62 (described later) of the oil pan 5b. . This avoids an increase in the arrangement space of the oil return hose 80 in the engine room 7 and troubles such as engine inspection and maintenance. Note that the air (breather air) from which the lubricating oil is separated by the oil separator portion 76 is supplied by the breather hose 79 to the air cleaner 21c disposed adjacent to the synthesizer portion 76, and both are disposed adjacent to each other. 79 is short.

  Furthermore, the oil tank 24a is connected to the oil pan 5b via oil hoses 24c and 24d, which is separate from the engine 5 and disposed higher than the oil level of the oil pan 5b. An electromagnetic valve 24b is interposed in the middle of the hose. When the electromagnetic valve 24b is opened, the lubricating oil is supplied into the oil pan 5b by its own weight.

  The oil tank 24a is disposed between the right middle plate 44b of the engine chamber 7 and the right side plate 37d of the case sink 31, that is, in the piping chamber 10 lower than the engine chamber 7, so that the supply port 24e faces the front plate 37a. Is arranged. A cap provided with a breather passage with a check valve that guides the atmosphere as the oil is consumed is detachably attached to the supply port 24e. Further, as shown in FIG. 3, the oil tank 24a has a L-shaped notch formed in the lower portion thereof, and the reserve tank 30a is disposed in the notch. Accordingly, the relatively large oil tank 24a and the reserve tank 30a are arranged without difficulty in a narrow space. A breather passage 30e that allows air to enter and exit and a replenishment port 30d to which a cap can be attached and detached are provided at the top of the reserve tank 30a. Further, by removing the front side plate 37a, the replenishing ports 24e and 30d of both tanks 24a and 30a face outward, so that lubricating oil replenishment, cooling water replenishment and the like can be performed simultaneously and easily.

  The electromagnetic valve 24b is fixed via a support bracket in the vicinity of the left engine mount 81 on the upper surface of the floor plate 45 and in the vicinity of 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 also connected by a flexible oil hose 24d. The lubricating oil inlet 5r is positioned higher than the oil level in the oil pan, thereby preventing the dirty oil in the oil pan 5b from flowing back to the electromagnetic valve 24b.

  Here, in this embodiment, an oil supply amount control device for automatically supplying the amount of lubricating oil corresponding to the amount of lubricating oil consumption to the oil pan 5b is provided. As shown in FIG. 32, the oil supply amount control device includes an engine speed detection sensor 91a, an oil level detection sensor 91b for detecting the lubricating oil level in the oil pan 5b, a load detection sensor 91c, and each sensor. And an ECU 92 for controlling the opening / closing timing of the electromagnetic valve 24b as a fueling means. Specifically, one or a plurality of sensors that detect the throttle opening, the fuel supply amount, and the boost pressure are employed as the load detection sensor 91c.

  The ECU 92 stores the engine speed integration means 92a that integrates the engine speed from the engine speed detection sensor 91a while correcting the engine speed according to the detected load from the load detection sensor 91c, and the accumulated total engine speed. It functions as a memory 92b and a refueling control means 92c that opens the solenoid valve 24b when the accumulated total engine speed reaches the reference accumulated speed.

  As shown in FIGS. 7 and 8, the oil pump 61 is disposed in the vicinity of the boundary between the oil pan 5b and the skirt portion of the cylinder block 5a and in the lower part of the tilt axis X. The oil filter 62 is detachably attached to an oil filter bracket 5v attached to the lower portion of the inclined axis X on the outer surface of the skirt portion of the cylinder block 5a. As a result, the oil filter 62 is positioned below the exhaust gas heat exchanger 23b and faces outward when the front plate 37a is removed, and can be detached from the outside. Further, since the oil filter bracket 5v is provided, only the oil filter bracket 5v may be replaced even if the attachment / detachment portion of the oil filter 62 is damaged.

  The oil filter 62 is located below the discharge port 61a of the oil pump 61 and the engine side inlet 63a. Therefore, the lubricating oil accumulated in the oil filter 62 has stopped the oil pump 61 for a long time. Even if it does not come out. Therefore, at the time of re-operation after the engine has been stopped for a long time, the start-up of the lubrication system is accelerated by the amount of time required for the lubricating oil to accumulate in the oil filter. Since the oil filter bracket 5v is interposed between the oil filter 62 and the engine, the height relationship with the pump discharge port 61a, the oil level and the like can be freely set, and the mounting direction of the oil filter 62 The degree of freedom for is high.

  A specific arrangement structure of the cooling system of the engine of this embodiment will be described. In the cooling jacket circulation circuit, which is one of the low-temperature circulation circuits, as shown by solid arrows in FIGS. 15 and 16, the cooling jacket 28b on the outer periphery of the wet liner 500a in FIG. The coolant passes through the cooling jacket 28b of the cylinder head and further circulates in the circuit of the water pipe 29a ', the switching valve 28c, the water pipes 29s and 29t, and the cooling water pump 28a.

  In this case, as shown in FIGS. 15 and 16, the cooling water pump 28a is disposed at the lowest position, the switching valve 28c is disposed at the highest position, and each component between the pump 28a and the switching valve 28c, The part to be cooled is disposed so as to be positioned higher in the downstream side. The switching valve 28c and the water injection port 30b of the cooling water heat exchanger 13 are connected by the bypass hose A described above. Therefore, the air in the cooling water in the low-temperature circulation circuit gathers at the switching valve 28c both when the pump 28a is operating and when the operation is stopped, and then rises to the water inlet 30b through the bypass hose A, It will accumulate here.

  In the exhaust gas heat exchanger circulation circuit, which is one of the low temperature circulation circuits, as shown by the dashed line arrows in FIGS. 15 and 16, the cooling water pump 28e, the water pipe 29e, the exhaust gas heat exchanger 23b, and the water pipe Cooling water in the circuit of the passage 29e ', the bypass pipe 29r that bypasses the switching valve 28c, 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. Circulates. When the temperature is high, the cooling water pump 28e and the cooling water pump 28a are connected in series, so that the water also circulates in the high temperature circulation circuit. That is, the cooling water pump 28e, the water pipe 29e, the exhaust gas heat exchanger 23b, the water pipe 29e ', the water pipe 29t, the cooling water pump 28a, the water pipe 29a, the cooling jacket 28b, the water pipe 29a', the switching valve 28c, and the water pipe 29b. , A three-way valve 28d, branches from here, and returns to the cooling water pump 28e via the water conduit 29p from the cooling water heat exchanger 13 or the heat exchanging portion 29g of the accumulator 8.

  In the exhaust gas heat exchanger circulation circuit at a low temperature, the cooling water pump 28e is arranged at the lowest position, and the cooling water heat exchanger 13 is arranged at the highest position, and between the pump 28e and the heat exchanger 13 is arranged. These parts and the part to be cooled are arranged so as to be located at a higher position on the downstream side. Therefore, the air in the cooling water rises to the heat exchanger 13 and accumulates in the water inlet 30b during both operation and stop of the pump.

  In addition, when the three-way valve 28d is set to a halfway opening degree, the water pipes 29b, 29c, and 29f communicate with each other in the three-way valve 28d when the three-way valve 28d is set to a halfway opening degree. Since it will be in a state, air will flow backward through the water pipe 29f, and will accumulate in the water inlet 30b from the heat exchanger 13 for cooling water. That is, the air can be vented more reliably by setting the three-way valve 28d to a halfway opening degree while the pump is stopped. Further, a part of the water conduit 29b is positioned downward as it moves away from the switching valve 28c. The air in this part is released by the air rising to the switching valve 28c part while the pump is stopped, and then collecting in the water injection port 30b through the bypass hose A.

  Furthermore, the return water system from the heat exchanging portion 29g of the accumulator 8 joins the water pipe 29f 'as the first return path in the middle of the water pipe 29d as the second return path from the water injection port 30b. It is configured. In this case, the water pipe 29f 'extends obliquely upward so that the merging portion is located at a high place. Therefore, when the pump is stopped, the air in the return water system rises through the water pipes 29f 'and 29d and accumulates in the water inlet 30b.

  Next, the function and effect of the apparatus 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 to a high temperature and a high pressure is supplied to the refrigerant outdoor heat exchangers 11 and 12 via the refrigerant pipe 16a, the four-way valve 15, and the refrigerant pipe 16b. It is cooled by outside air and liquefied. The liquefied high-pressure refrigerant liquid passes through the main accumulator 8 through the refrigerant line 16c and is decompressed by the expansion valve 18 in the refrigerant line 17a. The decompressed low-pressure refrigerant liquid takes heat from the indoor air in the indoor heat exchanger 4 and evaporates, and this evaporating heat produces a cooling effect to cool the room. The evaporated refrigerant gas passes from the refrigerant pipe 17b through the four-way valve 15 and the refrigerant pipe 16d, returns to the compressor 6 through the main accumulator 8 and 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 and high-pressure refrigerant gas from the compressors 6 and 6 is supplied to the indoor heat exchanger 4 via the refrigerant pipes 16a and 17b. Here, it is cooled and liquefied by room air, and the room air is warmed by the condensation heat in this case, and a heating effect is obtained. The liquefied refrigerant liquid is decompressed by the expansion valve 18. The decompressed low-pressure refrigerant liquid is evaporated by taking the heat of the outside air in the outdoor heat exchangers 11 and 12, and returns to the compressor 6 via the main accumulator 8 and the sub-accumulator 9, and the same cycle is repeated. .

  Heat exchange in the outdoor heat exchange chamber 14 is performed as follows. By the rotation of the outdoor heat exchange blower fan 44, the outside air is sucked into the outdoor heat exchange chamber 14 from the wire nets 38a and 38b and discharged upward from the ceiling opening 37f. In this case, as shown in FIG. 2, in the upper part of the outdoor heat exchange chamber 14, air flows in a substantially horizontal direction because it is close to the blower fan 44. Since the upper heat exchanger 11 is arranged vertically, the air passing through the upper heat exchanger 11 flows in a direction substantially perpendicular to the upper heat exchanger 11 as indicated by an arrow a.

  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 thereof are located on the inner side, the air passing through the lower heat exchangers 12 and 13 is exchanged with the lower heat exchanger as indicated by an arrow b. It flows in a direction substantially perpendicular to the vessels 12 and 13.

  As described above, in the present embodiment, the upper heat exchanger 11 is arranged vertically and the lower heat exchangers 12 and 13 are inclined, so that the air flow is substantially the same as the heat exchanger in any heat exchanger. By flowing vertically, the air flow rate can be substantially uniform over substantially the entire surface of each of the heat exchangers 11 to 13, and the heat exchange efficiency can be improved. Incidentally, when the lower heat exchangers 12 and 13 are arranged vertically, the air passage of the heat exchanger is inclined with respect to the air flow direction, so that the resistance increases and the amount of air decreases.

  Further, since the lower heat exchangers 12 and 13 are arranged to be inclined inward, in the case of the same heat exchange area, the heat exchanger arrangement surface of the outdoor heat exchange chamber 14 may be narrower than arranged in the vertical direction. The increase in the size of the outdoor air conditioning unit 2 can be suppressed, and the problems of increased weight and increased layout space can be avoided.

  Moreover, in the water injection operation | work of engine cooling water, the cover 63 is opened and the cap 61 of the water injection port 30b is removed. Then, water is poured from the rear surface of the air conditioning unit 2 into the opening 60a. In this case, since the water injection port 30b is provided at the upper end portion of the head pipe 13c of the cooling water heat exchanger 13 which is disposed below and inclined, the height position thereof is provided, for example, on the top wall. Compared to the conventional example, it is lower and the injection of cooling water is easier. Further, since the water injection opening 60a is opened obliquely upward, water injection is easy from this point.

  Then, after cooling water is extracted from the cooling water circuit for engine inspection and cooling system inspection, when cooling water is injected again, air in the cooling system is vented as follows. First, in the low-temperature circulation circuit, the switching valve 28c positioned on the downstream side of the pump 28a is positioned at the highest position, and the switching valve 28c is connected to the water injection port 30a positioned at the highest position of the entire cooling system by the bypass hose A. Therefore, the air in the circuit is accumulated in the water injection port 30d from the switching valve 28c both when the pump is operating and when it is stopped, and the cap 61 can be loosened to release the air. Further, in the exhaust gas heat exchanger circulation circuit, the water pipes from the pump 28e to the heat exchanger 13 and the part to be cooled are located higher in the downstream, so that the air is in the water pipe 29e and the exhaust gas heat exchanger 23b. , Water pipes 29e ', 29r, 29b, three-way valve 28d, and water pipe 29c, can be collected in the water inlet 30b of the heat exchanger 13 and extracted outside.

  The air supply from the three-way valve 28d to the heat exchanger 29g of the accumulator 8 is vented so that when the three-way valve 28d is set to a halfway opening, the water pipes 29b, 29c, 29f communicate with each other in the three-way valve 28d. As a result, the air flows backward through the water conduit 29f and accumulates from the cooling water heat exchanger 13 to the water inlet 30b. Further, since a part of the water pipe 29b is located lower as it is farther from the switching valve 28c, the air vent of this part rises to the switching valve 28c part while the pump is stopped, and from here the bypass hose A passes through the above note. This is done by accumulating in the water inlet 30b. In the drainage system from the heat exchanging portion 29g, it similarly accumulates in the water injection port 30b through the water pipes 29f 'and 29d, and can be extracted outside.

  Further, in this embodiment, the lower heat exchangers 12 and 13 are inclined and the lower end portions are arranged on the central partition plate 40, so that the piping chamber side partition plates are not moved without moving the lower heat exchangers 12 and 13. 42a and 42b and the engine room side partition plates 41a and 41b can be attached and detached, and particularly when the front and rear side plates 37a and 37b are removed from the front and the rear, the work for inspecting the engine, pipes and the like from above is easy. In particular, when the front and rear plates 37a and 37b are removed together with the partition plate, the engine can be inspected from the upper, front, and diagonal directions, and the pipes and the like can be inspected from the upper rear and the diagonal directions. Work is easy.

  Here, when the refrigerant outdoor heat exchanger is used as an evaporator (during heating), water vapor in the atmosphere condenses on the surface of the heat exchanger, but the lower heat exchangers 12 and 13 are inclined as described above. However, since the lower end of the heat exchanger 12 is disposed so as to exceed the side wall 48, most of the condensed water flows along the inclined surface of the heat exchanger 12 in the side wall 48 or a position close to the side wall 48. Fall into. Accordingly, the corrosion of these partition plates can be suppressed by the amount of less condensed water adhering to the engine room side partition plates 41a and 41b and the piping chamber side partition plates 42a and 42b.

  Furthermore, in the inclined arrangement of the heat exchangers 12 and 13, the ventilation outlet 40 b of the engine room 7 is located between the lower ends of the heat exchangers 12 and 13. High air does not pass through the heat exchanger, and adverse effects on the heat exchange efficiency can be avoided.

  Moreover, drainage of rainwater and the like is performed as follows. When rainwater or the like that has entered the outdoor heat exchange chamber 14 from the wire nets 38a and 38b falls on the partition plate 39, it flows into the horizontal wall 48 from the partition plate 39, passes through the vertical wall 43, and passes through the drain port 43a. Drained below the floor plate 36 of the air conditioning unit 2.

  In this case, since the center, engine room side, and piping chamber side partition plates constituting the partition plate 39 are inclined so that the side wall 48 side is lowered, the rain water or the like is allowed to flow into the side wall 48 in a short time. Can do. Thus, since rainwater etc. are drained in a short time without staying on the partition plate 39 which comprises the floor member of the outdoor heat exchange chamber 14, the corrosion resistance of these floor members can be improved.

  Further, since the partition plates 39 constituting the ceilings of the engine room 7 and the piping chamber 10 are disposed in an inclined manner, the outside height of the chambers 7 and 10 can be increased, and accordingly the front side plate 37a and the rear side plate 37b are removed. The opening can be enlarged and maintainability can be improved.

  In addition, the horizontal rod 48 and the vertical rod 43 are arranged outside the engine room 10 and drained below the engine room, so that rainwater or the like can enter the engine room even if these holes are pierced. Absent. Therefore, rainwater or the like does not reach the high-temperature engine or the like, and the heat shock resistance and corrosion resistance of the engine or the like can be improved. Further, since the drainage port 43a of the vertical shaft 43 is positioned on the opposite side of the air intake port 36a of the engine room 7, rainwater or the like does not enter the engine room 7, and water drops are sucked into the engine. Engine failure can be prevented. Since the position of the drain outlet 43a is located below the piping chamber air intake port 33b and is separated, rainwater or the like does not enter the piping chamber 10. Note that the air intake port 36a of the engine room 7 is separated from the piping chamber air intake port 33b, and the air intake port 36a of the engine room 7 is further away from the drainage port 43a.

  And if the said horizontal gutter 48 and the vertical gutter 43 are made of a synthetic resin, the corrosion resistance can be improved as much and the other floor member can be exchanged as a separate part, so that the durability as a whole can be improved. When replacing the vertical rod 43, it is possible to remove the right side plate 37d, and the operation is easy. Furthermore, since the left end portion 48b located on the upstream side of the horizontal bar 48 can be exposed outwardly, cleaning from the outside is possible. Cleaning can be performed more efficiently by removing the right side plate 37c.

  The ventilation of the piping chamber 10 and the engine room 7 is performed as follows. The outside air is introduced into the piping chamber 10 from the piping chamber air intake port 33 b of the floor plate 33 and the terminal chamber 22 by the rotation of the ventilation fan 47. At this time, since a part of the introduced air ventilates the electrical equipment box 50, the electrical equipment can be cooled. The air introduced into the piping chamber 10 is pushed into the air introduction chamber 46 formed between the bottom plate 45 and the floor plate 33 of the engine chamber 7 by the ventilation fan 47, and enters the engine chamber 7 from the jet port 45a. Erupts throughout. At this time, the cooling water pump 28e disposed in front of the ventilation fan 47 is cooled. Further, the jet outlet 45 a is opened below the oil pan 5 b and the oil filter 62. An opening is also formed near the engine mount 81, and the engine mount 81 including the oil pan 5b, the oil filter 62, and the rubber portion is effectively cooled. The end of the air introduction chamber 46 opens into the engine chamber 7, where a cooling water pump 28a is arranged and cooled. In particular, both the cooling water pumps 28a and 28e are electric pumps and generate heat, and cooling with a ventilation flow is effective in ensuring the durability of the bearing portion and the seal portion. The blown air is exhausted into the outdoor heat exchange chamber 14 from the exhaust port 40b formed in the ceiling wall through the muffler box 40c while ventilating the engine room 7. In this case, the air introduction chamber 46 has a box shape extending over the entire bottom surface of the engine room 7, and a large number of jets 45a are formed in the bottom plate 45. Can be performed reliably.

  Further, since the ventilation air intake 46a to the engine room 7 is opened in the piping chamber 10, the noise in the engine room 7 leaks into the piping chamber 10 but does not leak directly to the outside. Since the volume of 10 is large, the above-described noise attenuation function can be obtained, and as a result, noise can be reduced. Further, since the jet port 45a formed in the bottom plate 45 of the engine room 7 is opened in the box-shaped air introduction chamber 46, the air introduction chamber 46 also provides a damping function, and noise is reduced from this point as well. it can. Moreover, although the rainwater splashed enters the piping chamber 10 from the air intake 36 a to the piping chamber 10, it does not enter the engine room 7.

  Here, the main and sub accumulators 8 and 9 disposed in the piping chamber 10 store liquid phase refrigerant, and a cooling function by this refrigerant is obtained. In this embodiment, since each of the accumulators is disposed between the air intake port 33b to the piping chamber 10 and the air intake port 46a to the engine chamber 7, the outside air is cooled in the piping chamber 10 before the engine. It will be introduced into the chamber 7. Therefore, since the inside of the engine room 7 is ventilated by air having a relatively low temperature, it is cooled more reliably. Further, looking at the refrigerant, energy is given by the heat of the air in the piping chamber 10, and the thermal efficiency is improved.

  In the above ventilation, the air outlet 45a to the engine room 7 and the discharge port 40b from the engine room 7 are provided at positions separated from each other, and the engine 5 is disposed between them. Air having a relatively low temperature is surely hit. From this point, the cooling performance of the engine 5 is improved.

  Further, a discharge port 40b for discharging air from the engine room 7 is surrounded by a silencer box 40c, and an opening 40d of the silencer box 40c is provided at a position away from each pipe line passing through the pad 49 portion of the partition plate 39, and in the opposite direction. The exhaust air from the engine room does not heat the pipes, which is advantageous in terms of the corrosion resistance of the pipes and adversely affects the heat exchange effect of the heat exchanger. There is nothing.

  Further, since the silencing box 40c and the discharge port 40b are positioned higher than the side pad 48, it is possible to prevent water flowing through the side pad 48 from entering the engine room 7 through the opening 40d of the silencing box 40c.

  Further, in the present embodiment, the front plate 37a constituting the engine room 7 is detachable, and the oil filter 62 is disposed at a portion facing the front plate 37a of the engine 5, so that the oil filter 62 can be easily attached and detached. . In particular, as in this embodiment, when the engine room 7 and the piping chamber 10 are arranged to overlap each other in order to suppress the lateral width of the outdoor unit, it is extremely difficult to attach and detach the oil filter from the piping chamber 10 side. In addition, the arrangement structure of the present embodiment has a great effect when the engine room 7 and the piping room 10 are arranged so as to overlap each other.

  Further, since the exhaust gas heat exchanger 23b is disposed below the tilt axis X of the engine 5 and the oil filter 62 is disposed below it, the lubricating oil leaks when the oil filter is attached or removed or due to deterioration of the gasket or the like. However, the lubricant does not touch the hot exhaust passage.

  When lubricating oil is supplied to the oil pan 5b from a separate oil tank, the solenoid valve 24b is disposed at a lower position than the connection port 5r to the oil pan 5b. Therefore, after the solenoid valve 24b is closed, the solenoid valve 24b It is possible to prevent the lubricating oil on the downstream side from flowing into the oil pan 5b and to improve the responsiveness associated with opening and closing of the electromagnetic valve.

  Further, since the electromagnetic valve 24b is fixed on the floor plate 45 so as to be disposed at a low place, the oil hose 24d can be routed over the floor plate 45, and thereby, particularly during inspection and maintenance such as element replacement of the oil filter 62, The oil hose 24d does not become an obstacle when the exhaust gas heat exchanger 23b is attached or detached, and workability can be ensured.

  Further, since the electromagnetic valve 24b and the connection port 5r of the oil pan 5b are connected by the flexible oil hose 24c, it is possible to avoid the engine vibration being directly transmitted to the electromagnetic valve 24b. In this case, since the oil hose 24c is made relatively short by arranging the electromagnetic valve 24b in the vicinity of the connection port 5r, the vibration of the flexible oil hose 24c due to engine vibration can be reduced. The lifetime of 24c can be secured.

  Here, the supply amount control of the lubricating oil to the oil pan 5b is performed as shown in FIG. When the engine starts operation, the detected engine speed is corrected to a smaller engine speed for a smaller load according to the detected load, and corrected to a larger engine speed for a larger load and accumulated, and the engine stops. It continues until it does (steps S1-S3). When the engine is stopped, when the oil level is not lower than the lower limit and not higher than the upper limit, it is determined whether or not the cumulative value of the engine speed exceeds a preset reference cumulative number (steps S3 to S6). In this case, the electromagnetic valve 24b is opened, and when the oil level reaches the upper limit, the electromagnetic valve 24b is closed, the data is reset, and the operation is terminated (steps S7 to S10).

  When the solenoid valve is open, it is monitored whether or not the specified time has elapsed until the oil level reaches the upper limit. If the specified time has elapsed, the upper limit oil level sensor is monitored. The solenoid valve 24b, the oil tank 24a, the hoses 24c and 24d on the way, etc. are determined to be abnormal, a notice is displayed that inspection and maintenance are necessary (steps S11 and 12), and the process proceeds to step S9. In step S4, if the oil level is below the lower limit, the flow proceeds to step S7 and lubricating oil is supplied immediately. If the cumulative engine speed does not exceed the reference value in step S6, the cumulative speed is stored. Then, the operation is terminated, and at the next engine operation, the stored engine speed is further accumulated.

  Although it is considered that the amount of consumption of lubricating oil due to rising oil depends on the total engine speed, in this embodiment, the engine speed is accumulated and the lubricating oil is supplied when the speed reaches the reference value. Therefore, the lubrication state can be stabilized for a long time, and the durability of the engine can be improved.

  In this case, it is considered that as the engine load increases, the combustion pressure increases, the amount of breather gas from the crank chamber increases, and the amount of lubricating oil consumption increases. In this embodiment, the engine speed increases as the engine load increases. Therefore, the amount of lubricating oil corresponding to the actual amount of lubricating oil consumed in consideration of the amount of oil discharged to the atmosphere as oil mist from the crank chamber can be supplied with high accuracy. In addition, when accumulating the engine speed, the engine speed is corrected and accumulated according to the magnitude of the load. However, this is not always necessary, and it is accumulated without modification. Lubricating oil may be supplied when the value reaches the reference value. Even in this case, it is possible to supply the lubricating oil in accordance with the consumption amount of the lubricating oil.

  In the engine 5 of this embodiment, since the cylinder heads 5c are divided into two sets for four cylinders, that is, the cylinder heads are divided into a plurality of parts, each cylinder head 5c can be reduced in size, and the mold structure in casting is Simplified and easy to handle in machining and the like.

  Also, the cylinder head is at the top, and breather gas with high temperature is likely to enter. In this embodiment, since the breather chamber 5m is provided in the cylinder head 5c, the oil separation property can be improved because the breather chamber 5m is far from the crank chamber. In addition, since the breather chambers are provided in both of the two cylinder heads 5c, 5c, the breather function can be maintained even if one of the cylinder heads is clogged.

  Further, since the breather chamber 5m is formed in each cylinder head 5c and this is connected to the external oil separator section 76, the burden on the oil separator section 76 is reduced by the amount that the breather function on the engine side can be obtained. The function of the oil separator 76 can be maintained for a long time. In addition, when connecting each breather chamber to the oil separator portion 76 with the breather hose 69, both branch hoses are joined and the joining passage is connected to the oil separator 76 portion. The hose length can be shortened.

  In configuring the oil separator portion 76, the oil separator portion 76 is integrated with the exhaust silencer portion 75, so that the number of parts can be reduced and the size can be reduced, and condensation can be prevented by using heat of the exhaust gas. The deterioration of the separated lubricating oil due to mayonnaise sludge generation can be prevented. In this case, since the ceiling wall 76c and the right wall 76d of the oil separator section 76 are shared with the wall of the exhaust silencer section 75, the exhaust heat utilization efficiency can be improved.

  Further, since the lid 76f of the oil separator portion 76 is disposed at a position facing the outside when the front side plate 37a is removed, the serviceability of the oil separator portion 76 can be improved. In disposing the exhaust gas heat exchanger 23b, the front plate 37a facing the heat exchanger 23b can be attached and detached, so that the inspection and maintenance of the heat exchanger 23b is easy. Since the heat exchanger 23b is composed of the inner fin type heat exchanger 73 and the screw type heat exchanger 74 integrated with the inner fin type heat exchanger 73, the entire exhaust gas heat exchanger 23b is secured while ensuring a necessary heat exchange area. Can be miniaturized.

  Further, the inner fin type heat exchanger 73 has a structure in which fins 73b project from an exhaust passage that guides exhaust gas to the screw type heat exchanger 74, and is directly connected to the exhaust port 5q. The exhaust passage that guides the exhaust gas can also function as a heat exchanger, and the ability to exchange heat with the exhaust gas can be enhanced while effectively using the space. In this case, the heat transfer area is increased by the fins 73b, the flow becomes turbulent, and the heat exchange efficiency is improved. Incidentally, for example, when the partition method is used, the flow resistance becomes large, the flow is stagnation, and the heat exchange efficiency is low. Moreover, since the length of the helical screw pipe 74b of the screw type heat exchanger 74 is longer than the length between the exhaust ports 5q at both ends, a sufficient heat exchange area can be obtained.

  Further, since the exhaust port 5q is disposed below the tilt axis X of the engine 5 and the exhaust gas heat exchanger 23b is disposed below the exhaust port 5q, the condensed water generated in the heat exchanger 23b can enter the engine. Can be reliably prevented. That is, the water cooled by the accumulator 8 is introduced into the exhaust gas heat exchanger 23b, but the temperature in the accumulator 8 is about 0 ° C. Therefore, condensed water is generated in the exhaust gas heat exchanger 23b. easy. The condensed water may enter the engine due to exhaust pulsation. In this embodiment, the intrusion can be avoided because the screw heat exchanger 74 of the exhaust gas heat exchanger 23b is disposed below the exhaust port 58.

  Since the exhaust gas heat exchanger 23b is disposed at a lower position than the cooling water heat exchanger 13, the cooling water heated by the exhaust gas heat exchanger 23b is smoothly transferred to the cooling water heat exchanger 13 by natural convection during the cooling operation. Flowing into.

  Since the exhaust silencer portion 75 is disposed above the exhaust gas heat exchanger 23b and the neutralizer 82 is disposed below the heat exchanger 23, the exhaust silencer portion 75 and the exhaust gas heat exchanger 23b are disposed. The condensed water from can be reliably guided to the neutralizer 82.

  Further, when arranging the intake pipe 21a and the exhaust pipe 23a, the air cleaner 21c and the air inlet 77a and the exhaust gas outlet 75d of the exhaust silencer 23c are projected into the outdoor heat exchange chamber 14, and the seal member 77d is formed by the air cleaner 21c and the exhaust silencer 23c. , 75d are pressed against the central partition plate 40, the number of parts can be reduced, and the number of assembly steps can be reduced accordingly.

  In the above embodiment, when water is poured, as shown in FIG. 36, the opening / closing window 63 facing the water filling port 30b may be opened. As can be seen from the above, the water injection port 30b is arranged at the front right end, and both the water injection to the replenishment port 30d of the reserve tank 30a with the front side plate 37a removed can be easily performed. As described above, by removing the front side plate 37a, the oil filter 62 is replaced, the element 78b of the air cleaner 21c is replaced, the element 76b of the oil separator 76 is replaced, the oil is added to the oil tank 24a, and the engine 5 is inclined. Inspection of spark plug 5w facing forward, lubrication to capped lubrication port 5x provided on cylinder head cover 5d, waste oil due to oil drain 5u position of oil pan 5b being forward, inspection of oil level gauge 5z, etc. The work required for the maintenance of the engine 5 can be almost entirely performed from the front, and the maintainability is good.

  Moreover, although the said Example demonstrated the case where the heat exchanger 13 for engine cooling water was arrange | positioned below the heat exchanger 11 for refrigerant | coolants, this invention is the heat exchanger 13 for engine cooling water on the upper side. The present invention can also be applied to the case where the refrigerant heat exchanger 11 is disposed on the lower side. In this case, a water injection port may be provided in the upper engine cooling water heat exchanger. Further, although the water injection port 30b is attached to the engine cooling water heat exchanger 13, the water injection port may be attached separately from the heat exchanger 13, and in this case, The degree of freedom of the position of the water inlet can be improved. In any case, the water inlet is opened obliquely upward toward the inner surface of the side wall of the air conditioning unit.

  Here, in the above embodiment, the intake pipe 21 a is opened outside the ceiling of the outdoor heat exchange chamber 14. However, the intake pipe 21 a may be opened inside the engine room 7. If it does in this way, the air with comparatively low temperature in the said piping chamber 10 will be supplied in an engine, and filling efficiency will improve. Further, when the engine 5 is taken out from the engine room 7 for inspection and maintenance, the engine 5 can be taken out without removing the intake pipe, so that the inspection and maintenance performance is improved accordingly.

  Further, since the air cleaner 21c and the exhaust silencer 23c are arranged by effectively using the upper space of the compressor 6 arranged on the right side of the engine, and the gas mixer 21b is arranged on the right side of the engine 5, the intake hoses 21a ′, The piping length of 79 is shortened. In addition, the pipes 69, 80, 23a'84a, 84b, 84c, a part of the flow rate adjusting valve 22a, the electromagnetic valve 24b, and the oil level gauge 5z are disposed in front of the obstacle, so the front plate 37a is removed. The inspection work becomes easier. Further, the neutralized air 82 is arranged by effectively using the lower space of the compressor 6.

  Since all the piping 30c, 29c, 29d, 16b, and 16c of the piping chamber 10 and the heat exchange chamber 14 are concentrated on the right side where the accumulator 8 is disposed, piping work is easy. Further, the sealing pad 49 can be easily attached to and removed from the through portion of the central partition plate 40c.

  Since the oil tank 24a and the reserve tank 30 are arranged in the vicinity of the piping chamber 10 and further in the accumulator 8, there is a cooling effect.

  Since the main journal bearing 65 of the crankshaft 5g is disposed at the joint fastening portion between the cylinder block 5a and the oil pan 5b, the bearing cap is unnecessary. In addition, since the oil pan 5b is formed with a recess toward the coupling portion, the rigidity and strength of the oil pan 5b are increased.

  The cylinder block 5a is made of an aluminum alloy die-cast, and a steel wet liner 500a is inserted. Three O-rings 500b for water sealing are arranged below the wet liner 500a. With this structure, the engine 5 can be measured and improved in workability.

FIG. 1 is a partial cross-sectional front view of an engine-driven air conditioner according to an embodiment of the present invention. It is a partial cross section rear view of the said embodiment apparatus. It is a partial cross section right side view (III-III line sectional view of Drawing 2) of the above-mentioned embodiment device. It is a partial cross section left side view (IV-IV line sectional view of Drawing 2) of the above-mentioned embodiment device. It is a top view of the floor member part of the outdoor heat exchange chamber of the said embodiment apparatus. It is a section top view of the engine room and piping room of the above-mentioned embodiment device. It is a partial cross section side view of the embodiment engine. It is a schematic diagram which shows the lubrication system of the said embodiment engine. It is a partial cross section front view of the said embodiment engine. It is a figure which shows the flow of the lubricating oil of the said embodiment engine. It is a figure which shows the oil separation chamber of the said embodiment engine. It is an intake and exhaust system piping diagram of the above-mentioned embodiment device. It is a sectional front view showing the air cleaner and intake pipe connection point of the above-mentioned embodiment device. It is a piping diagram of the lubricating oil supply system of the said embodiment apparatus. It is a front piping figure of the cooling system of the above-mentioned embodiment device. It is a plane piping figure of the cooling system of the above-mentioned embodiment device. It is a right side piping diagram of the cooling system of the above-mentioned embodiment device. It is a top view of the pad of the above-mentioned embodiment device. It is a cross-sectional right view of the water inlet of the said embodiment apparatus. It is a rear view of the electrical equipment box of the said embodiment apparatus. It is a section side view of the electrical equipment box of the above-mentioned embodiment device. It is a right view of the engine room of the said embodiment apparatus. It is a right view of the water inlet part of the said embodiment apparatus. It is a side view of the air cleaner of the said embodiment apparatus. It is a front view of the air cleaner of the said embodiment apparatus. It is a cross-sectional top view of the air cleaner of the said embodiment apparatus. It is a section front view of the air cleaner of the above-mentioned embodiment device. It is a partial cross section side view of the exhaust silencer of the above-mentioned embodiment device. It is a front view of the exhaust silencer of the above-mentioned embodiment device. It is a section front view of the exhaust gas heat exchanger of the above-mentioned embodiment device. It is a systematic diagram which shows the whole structure of the said embodiment apparatus. It is a systematic diagram which shows the lubricating oil system of the said embodiment apparatus. It is a block block diagram of the lubricating oil amount control apparatus of the said embodiment apparatus. It is a cross-sectional schematic diagram of the casing of the said Example apparatus. It is a flowchart figure which shows the lubricating oil amount control of the said Example apparatus. It is a schematic diagram which shows the example which provided the opening-and-closing window in the water supply port in the said Example apparatus.

Explanation of symbols

5 Engine 24b Solenoid valve (fuel supply means)

Claims (1)

Cumulative value of the engine speed to open the replenishing oil valve during supplementation during engine stop after exceeding a predetermined value, for the supply and oil level is at the upper limit oil valve in the lubricating oil supply for an engine-driven air conditioning system closes the there, when the oil level has passed the time more defined until the upper limit is to notice that servicing is required, the replenishment oil valve closes and terminates the operation by resetting the data An engine-driven air conditioner for supplying lubricating oil, characterized in that it is configured as described above.

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