JPH0874562A - Processing unit of drainage in engine exhaust gas - Google Patents

Abstract

PURPOSE: To actualize a processing unit of drainage in engine exhaust gas, being capable of extending the full length of a neutralizer, and easy to secure a setup space. CONSTITUTION: In the case of constituting a processing unit of drainage in exhaust gas of an engine equipped with a neutralizer neutralizing by means of a counteragent being built in drainage to be produced in an exhaust passage of this engine, an inlet chamber 112, where drainage is induced, and a neutralizing chamber 114 being made up so as to form four reciprocating passages in the wake of this inlet chamber 112, and filled up with the counteragent both are formed in the neutralizer.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a device for treating drain water generated in an exhaust passage of an engine, and more particularly to a structure of a neutralizer for neutralizing drain water with a neutralizing agent incorporated therein.

[0002]

2. Description of the Related Art When engine exhaust gas is cooled, acidic drain water containing oil is generated. For example, the engine-driven air conditioner has an exhaust gas heat exchanger in the exhaust passage, and the exhaust gas temperature is lowered by the heat exchange, so that the drain water is generated.

The drain water is formed by condensing condensed acid with a liquid acid formed by dissolving acidic gas in exhaust gas into condensed water or a vapor acid formed by reaction of acidic gas with water vapor. If it is drained as it is, it may corrode the drainage pipe and its surroundings. Therefore, conventionally, for example, in the engine-driven air conditioner, it is necessary to provide a drain water treatment device for reducing the acidity of the drain water and discharging the drain water, and the present applicant has proposed this.

The drain water treatment device is equipped with a neutralizer for neutralizing the drain water. This neutralizer forms a neutralization chamber that serves as a drain water flow path in the casing, connects the upstream end of the neutralization chamber and the exhaust passage with a drain water introduction passage, and connects the neutralization chamber to the downstream end of the neutralization chamber. It has a structure in which drainage passages are connected.

[0005]

By the way, in order to increase the neutralizing capacity (neutralizing capacity) in the above neutralizer, the flow path length of the neutralizing chamber is set as long as possible, and the drain water and the neutralizing agent are used. It is necessary to design so that and are in contact as long as possible. However, depending on the structure of the neutralization chamber, the total length of the neutralizer becomes long and the space for disposing the neutralizer becomes large. For example, in the engine-driven air conditioner, it is difficult to secure the space for disposing the neutralizer.

The present invention has been made in view of the above-mentioned problems of the prior art, and it is possible to improve the neutralization capacity without increasing the total length of the neutralizer, and it is easy to secure a space for the drain in the engine exhaust gas. It is intended to provide a water treatment device.

[0007]

SUMMARY OF THE INVENTION The present invention provides a drain water treatment apparatus for engine exhaust gas, comprising a neutralizer for neutralizing drain water generated in an exhaust passage of an engine with a neutralizing agent. In the neutralizer, there are formed an introducing chamber into which the drain water is introduced, and a neutralizing chamber filled with the above-mentioned neutralizing agent, which is formed so as to form a reciprocating passage of one or more reciprocating passages following the introducing chamber. It is characterized by having done.

[0008]

In the drain water treatment device according to the present invention, since the neutralization chamber is configured to form a reciprocating flow path of one or more reciprocations,
The flow path length can be increased without increasing the total length of the neutralizer.

[0009]

Embodiments of the present invention will be described below with reference to the accompanying drawings. 1 to 19 are for explaining a drain water treatment apparatus for engine exhaust gas according to an embodiment of the present invention, and FIGS. 1 to 4 are engine-driven air conditioners equipped with the drain water treatment apparatus. Front view, rear view, right side view (cross-sectional view taken along line III-III in FIG. 2), left side view (IV in FIG. 2) of the device
-IV line sectional view), FIG. 5 is a schematic plan view of the floor of the outdoor heat exchange chamber, FIG. 6 is a schematic sectional plan view of the engine room and the piping room, and FIG.
8 is a partial cross-sectional right side view of the engine, FIG. 9 is a partial cross-sectional front view, FIG. 10 is a view showing the intake and exhaust systems, and FIGS. 11 and 12 are cross-sectional front views and front views of the exhaust silencer. 15 is a sectional front view of the exhaust gas heat exchanger, FIG.
Is a schematic sectional view of the casing, FIG. 16 is a bottom plan view of the neutralizer, and FIG. 17 is a sectional view taken along line XVII-XVII of FIG.

FIG. 1 is a diagram showing the overall construction of the apparatus of this embodiment.
In 4, 4, 1 is an engine-driven air conditioner,
This is composed of an outdoor air conditioning unit 2 and an indoor air conditioning unit 3. The indoor air conditioning unit 3 includes an indoor heat exchanger for refrigerant 4, an expansion valve 18 for reducing pressure, and an indoor heat exchange blower fan (not shown). The outdoor air conditioning unit 2 includes an engine room 7 in which an engine 5, compressors 6, 6 and the like are arranged, a main accumulator 8, a sub accumulator 9, an electrical equipment box 50, and a pipe line connecting each device. It is provided with an installed piping chamber 10 and an outdoor heat exchange chamber 14 in which a refrigerant outdoor upper and lower heat exchangers 11, 12 and an engine cooling water heat exchanger (hot water heat exchanger) 13 are arranged. There is. As shown in FIG. 4, two upper symmetrical heat exchangers 11 are arranged in reverse, but only one is shown in FIG. 14 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 provided in the intake pipe 21a. The pipe 21a penetrates the top wall of the engine room 7 and the top wall of 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 installed in the gas line 22d.
A flow control valve 22a integrated with b, a zero governor (pressure reducing valve) 22b, and two electromagnetic valves 22c are interposed. The exhaust port of the engine 5 has an exhaust pipe 23a.
Is connected to the exhaust pipe 23a, and the exhaust gas heat exchanger 23 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 open to the outside of the heat exchange chamber 14. The mist separator 23d is shown in FIG.
As described later with reference to No. 0, it is arranged outside the top wall of the heat exchange chamber 14. Further, reference numeral 24a is an oil tank which is arranged in the piping chamber 10 and stores the lubricating oil. When the amount of the lubricating oil in the oil pan decreases, the solenoid valve 24b is opened by the lubrication control device described later, and the lubricating oil is supplied by gravity. It is supposed to be done.

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

The refrigerant line 17b from the indoor heat exchanger 4 is connected to the refrigerant line 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, 6 through the four-way valve 15, the refrigerant pipe 16d, the main accumulator 8, the refrigerant pipe 202, the sub accumulator 9, and the refrigerant pipe 201. In addition, 300 and 301 are capillaries, 210 and 210 are each a combination of a temperature detector and a capillary, and are for detecting the level of the liquid-phase refrigerant in the accumulator 8 by detecting the cooling temperature. is there. Further, 302 is an opening / closing valve, and 303 is an oil discharge passage. When the amount of oil accumulated in the lower part of the accumulator increases, the opening / closing valve is opened manually or automatically so that the oil flows from the accumulator 8 to the sub accumulator 9.

An oil separator 19a for separating lubricating oil in the refrigerant is provided between the refrigerant pipes 200 and 16a, and when the amount of 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 which opens when the above value is exceeded. The lubricating oil passes through the capillary tube 300 and is returned to the sub accumulator 9. Further, the refrigerant pipeline 16a is connected to the main accumulator 8 via an oil strainer 20a and a solenoid valve 20b which opens when the pressure in the pipeline exceeds a predetermined pressure, thereby avoiding an abnormal rise in the refrigerant pipeline pressure.

The cooling jacket 28 of the engine 5 is also provided.
Regarding the cooling of b, when the cooling water temperature is below a predetermined value, the cooling water pump 28a, the water pipe 29a, the cooling jacket 28
b, water pipe 29a ', switching valve (thermostat valve)
A cooling jacket circulation circuit (engine cooling water circulation circuit), which is one of the low-temperature circulation circuits that circulates the cooling water in the route of 28c and the water pipe 29s, is configured.

When the cooling water temperature exceeds a predetermined value,
Cooling water pump 28e, water conduit 29e, exhaust gas heat exchanger 23b, water conduit 29e 'Cooling water pump 28a, water conduit 2
9a, cooling jacket 28b, water conduit 29a ', switching valve 28c, water conduit 29b, three-way valve 28d, water conduit 29
c, a heat exchanger 13 for cooling water, water pipes 29d and 29p, and a cooling water pump 28e constitute a high temperature circulation circuit for circulating the cooling water. 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 pipeline 29b through the bypass passage 29r. That is, another exhaust gas heat exchanger circulation circuit, which is a low temperature circulation circuit, is configured. As a result, the exhaust heat of the exhaust gas heat exchanger 23b passes through the three-way valve 28d and is discarded by the cooling water heat exchanger 13, or is given to the refrigerant by the heater 29g of the 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 it is necessary to quickly start the heating.

In the above cooling system, 30a is a reservoir tank for cooling water, which is a water conduit 30c and an inlet 30.
It is connected to the heat exchanger 13 for cooling water via b. As will be described later, an inlet independent of the inlet 30b is arranged above the cooling water reservoir tank, and the inlet 30b is provided with one of the switching valves 28c.
Two ports are also connected. The port is always in communication with the cooling water jacket 28b via a throttle, which allows air to escape from the cooling jacket circulation circuit.
Further, when the three-way valve 28d is switched, the engine cooling water is supplied to the main accumulator 8 by the water pipe 29d.
It is supplied to the internal heater 29g, which supplies 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 is particularly small, the electromagnetic valve 90 opens to allow the refrigerant to bypass the indoor unit 4 and flow 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. In the casing 31 of the outdoor air conditioning unit 2, a floor plate 33 is placed and fixed on a pair of bases 32, and pillars 34 are provided upright at four corners, and the upper ends of the four pillars 34 are on the right side surface and the left side. The ceiling beams are connected to each other by one 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 faces are left and the right side plates 37c and 37d. It has a structure in which it is covered with a plate 37e. The ceiling plate 37e is formed with a connecting portion with each side plate or each pillar 34 by bending the front, rear, left, and right ends.
Further, as shown in FIG. 15, the front side surface is provided with the left and right front side plates 37a and 37a whose upper ends are respectively bent and attached to the bent engine room side partition plates 41a and 41b.
It is concluded by. Similarly, the rear side surfaces are bent left and right rear side plates 37b, 37b when viewed from the front side with the upper ends bent, respectively.
Is installed. The front and rear side plates 37a and 37b cover lower portions of the front and rear side faces of the casing 31, and the left and right side plates 37c and 37d cover the entire left and right side faces of the casing 31. And before and after these,
The left and right side plates 37a to 37d are detachable so as to ensure maintainability of each device.

The front side plate 37a and the rear side plate 37b on the front and rear side surfaces of the casing 31 are provided with outside air introduction openings, and wire meshes 38a, 38b functioning as filters are provided in the respective horizontal frames 36a, 36b. 36b are detachably attached to the top and bottom of each. A discharge opening 37f for discharging the introduced outside air upward is formed in the top plate 37e, and the outside air is discharged through the discharge opening 37f.
An outdoor heat exchange blower fan 44 is provided which sucks air from the portions 8a and 38b into the outdoor heat exchange chamber 14 and discharges it above the outdoor heat exchange chamber 14. Reference numeral 38c is 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 room 10, and the central partition plate 40 and the engine room which constitute the ceiling of the engine room 7. It is composed of side partition plates 41a and 41b and piping chamber side partition plates 42a and 42b that constitute the ceiling of the piping chamber 10. The engine room side partition plates 41a and 41b and the piping room side partition plates 42a and 42b are detachable upward.
At the time of removal, the front and rear side plates 37a, 37b are also removed, the engine room 7 is open at the ceiling side, the front side, and both corners, and the piping room 10 is at the ceiling side, rear side, and both corners. The parts are open, making it easy to perform maintenance work on equipment in each room.

Further, at the boundary between the central partition plate 40 and the piping chamber side partition plates 42a and 42b, and outside the rear middle plate 44a which constitutes the rear side wall of the engine room 7, the upper part on the piping chamber 10 side.
A gutter 48 (drainage passage) is disposed at the center of the gutter 48 and the partition walls 40, 42a, 42b on the piping chamber side so as to be disassembled, that is, replaceable with a new one. The gutter 48 is a groove-like member extending in the longitudinal direction of the outdoor air-conditioning unit 2 (left-right direction in FIG. 2), that is, in the direction of the arrangement surface of the heat exchanger, and becomes lower toward the right side (right side in FIGS. 2 and 5). It is inclined.
The high end portion 48b located at the highest position of the gutter 48 can be exposed to the outside by removing the right side plate 37d or providing an opening (cleaning hole). The center partition plate 40 may cover the gutter 48 with a V-shape, and a plurality of rainwater dropping holes may be provided in the V-shaped bottom above the gutter 48.

Further, 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 gutter 43 extends downward at a corner portion 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 10, and has a drain port 43a opening at the lower end thereof.
Is located below the floor plate 33 and faces outward. The vertical gutter 43 can be replaced with a new one by removing the left side plate 37c.

The engine room side partition plates 41a, 41b,
Piping room side partition plates 42a, 42b and central partition plate 40
Is inclined so that it becomes lower toward the gutter 48 side.
Therefore, rainwater and the like that have entered the outdoor heat exchange chamber 14 are immediately collected in the lateral gutter 48 and are discharged to the outside through the vertical gutter 43. Further, due to the inclination, the engine room side partition plates 41a, 4
1b and the outer ends of the piping chamber side partition plates 42a, 42b are higher, and the openings for inspecting and maintaining the inside by removing the front and rear side plates 37a, 37b are large.

Further, the central partition plate 40 is formed with two ventilation air discharge ports 40b at two locations so as to open into the outdoor heat exchange chamber 14. The discharge port 40b is surrounded by a muffling box 40c. Also this silence box 4
The opening 40d of 0c is located above the gutter 48, and is located downstream of the gutter 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 that flows in the gutter 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 side wall of the engine room 7 has the front side plate 37a,
It is composed of a left side plate 37c, a rear middle plate 44a, a right middle plate 44b, a ceiling wall is composed of the engine room side partition plates 41a, 41b, and a central partition plate 40, and a bottom wall is formed between the floor plate 33 and It is composed of bottom plates 45 arranged at intervals. 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 has 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
Is a jet port 45a that blows out ventilation air into the engine room 7.
Are arranged and formed substantially evenly over the entire surface. In addition, the piping chamber 10 is provided on the right middle plate 44b side of the air introducing chamber 46.
Two engine room air intake ports 46a that open inside are formed, and a ventilation fan 47 is disposed in each of the air intake ports 46a. Here, the drain 43a of the vertical gutter 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 side plate 37b in the piping chamber 10, there are provided an electrical equipment box 50 accommodating and arranging various control devices and the like, and a terminal chamber 22 for connecting to external piping. An air intake port 50a is formed on the bottom surface of the electrical equipment box 50, and an exhaust port 50b is formed on the upper side surface, and a gap serving as an air passage is formed between the bottom surface and the floor plate 33. A piping chamber air intake 33b for introducing outside air into the piping chamber 10 is formed on the floor plate 33, and the outside air is introduced into the piping chamber 10 through the air intake 33b. Further, part of the introduced outside air is introduced into the electrical equipment box 50 through the air intake port 50a and discharged through the exhaust port 50b to ventilate the inside of the box 50. The drain 43a of the vertical gutter 43 is located away from the air inlet 33b of the piping chamber and below the air inlet 33b.

A floor plate 33 is provided below the terminal chamber 22.
There is also no ceiling. The terminal chamber 22 is a communication passage that connects the piping chamber 10 and the outside of the casing 31. Further, the terminal chamber 22 is opened to the rear outside with the rear side plate 37b removed. Each joint 100a of the refrigerant pipes 100, 1001
The joints of 101a and the gas pipe line 22d are located in the terminal chamber 22, and are connected to external pipes introduced from below the terminal chamber 22, respectively. Power cord 6 connected to an external power source
00 and the like are also extended to the outside from below the terminal chamber 22. Since the external pipes are routed downwardly of the terminal chamber 22, the outer size of the casing 31 becomes compact, and the pipe chamber 22 also serves as the air inlet of the pipe chamber.

Inside the outdoor heat exchange chamber 14, the upper outdoor heat exchangers 11, 11 for the refrigerant are provided at the upper portions on the front and rear sides, the lower outdoor heat exchanger 12 for the refrigerant is provided at the lower rear portion, and the lower front portion is also provided. The heat exchanger 13 for engine cooling water is arranged in each of the above. Here, the upper heat exchangers 11 and 11 are arranged vertically and along the wire nets 38a and 38b, while the lower outdoor heat exchanger 12 and the cooling water heat exchanger 13 are arranged. The cooling water heat exchanger 13 is inclined so that the lower part thereof is located inward, and the above-described water injection port 30b is provided at the upper right end portion of the cooling water heat exchanger 13.

The engine 5 of this embodiment is a water-cooled parallel four-cylinder OHV engine, and the crankshaft 5 is provided in the engine room 10.
g is oriented in parallel with the front plate 37a of the engine room, and the cylinder axis is inclined forward so as to be closer to the front plate 37a. It is fixed on the floor plate 45 via the engine mount 81.

In the engine 5 of this embodiment, as shown in FIGS. 7 to 9, the oil pan 5 is provided on the lower mating surface of the cylinder block 5a.
b is bolted and fixed, the cylinder head 5c is fastened to the upper mating surface with head bolts, and the cylinder head 5c is covered with a head cover 5d. A piston 5e 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 provided on the cylinder head 5c. The valve operating system 5h includes the intake valve 5
i, the exhaust valve 5i 'is configured to be opened and closed by a cam shaft 5l arranged in the vicinity of the crank shaft 5g via a rocker arm 5j and a push rod 5k.

In the engine 5 of this embodiment, the cylinder block 5a is formed by integrating four cylinders.
In contrast to the block structure, the cylinder head 5c has a structure in which one of the two cylinder bores is divided into two sets, that is, two sets of head covers 5d are provided correspondingly. A breather chamber 5m is formed in each of the head covers 5d.

The four exhaust ports 5q of the engine 5 are led out to the lower side of the tilt axis X, and the exhaust gas heat exchanger 23b is directly connected to the external connection ports of these exhaust ports 5q, that is, the exhaust pipe is interposed. Connected without letting.
As shown in FIGS. 7 and 13, this heat exchanger 23b has a structure in which an inner fin type heat exchange section 73 located on the upper side and a screw type heat exchange section 74 located on the lower side are integrated, It is set longer than the interval between the exhaust ports 5q at the both ends.

The inner fin type heat exchange section 73 is formed by utilizing the exhaust passage, and the upper step section and the lower step section are bent so as to have a substantially U shape in order to secure a necessary heat exchange area. It has a structure in which it is molded, the outer surface is surrounded by a cooling jacket 73a, and a large number of fins 73b are projectingly formed on the inner surface. The exhaust ports 5q communicate with each other in the upper portion, and the cooling jacket 73
The water pipe line 29e 'is connected to the cooling water outlet 73c of a.

In the screw type heat exchange section 74, the cooling jacket (casing) 74a is formed into a cylindrical shape,
A large number of spiral screw pipes 74b are arranged in the jacket 74a, the upstream end of the pipes 74b is placed in the upstream chamber 74c into which the exhaust gas passing through the inner fin type heat exchange section 73 is introduced, and the downstream end is placed in the downstream side. The structure is such that each of the chambers 74d is opened. The downstream end of the screw pipe 74b is slidable with respect to the downstream chamber 74d side end of the cooling jacket 74a so as to absorb the amount of thermal expansion.

A cooling water inlet 7 for introducing cooling water into the jacket 74a is provided below the cooling jacket 74a.
4e is formed, and the water conduit 29e is connected to the cooling water inlet 74e. Note that, in FIG. 13, the flow direction of the exhaust gas is indicated by a dashed arrow, and the flow direction of the cooling water is indicated by a solid arrow. Further, 74h is a drain water outlet for guiding condensed water generated by cooling the water vapor contained in the exhaust gas to the neutralizer 82 described later.

The exhaust gas outlet 74g of the screw type heat exchange section 74 is connected to the exhaust silencer 23c via an exhaust pipe 23a '. This exhaust silencer 23c
Is arranged above the compressor 6 in the engine room 7 and adjacent to the air cleaner 21c.
As shown in FIG. 5, the silencer portion 75 and the oil separator portion 76 are integrally formed.

The silencer portion 75 is of a vertically divided two-part type, and has a structure in which the interior is divided into a large number of expansion chambers 75a and the expansion chambers 75a are connected to each other by reduction pipes 75b. Exhaust gas inlet 75c of this silencer 75
Is connected to the exhaust pipe 23a ', and the exhaust gas outlet 75d is connected to the exhaust pipe 23a.

The compressor 6 on the floor plate 45 of the engine room 7
A neutralizer 82 for neutralizing the condensed water containing the acidic gas in the exhaust gas is arranged at the lower position. As shown in FIGS. 16 and 17, the neutralizer 82 is composed of a lower case 111 having a rectangular shape in plan view with an upper end opened, and an upper lid 110 detachably attached to the opening.

In the lower case 111, as shown in FIG. 16, an introducing chamber 112 into which the drain water is introduced,
A neutralization chamber 114 formed following the introduction chamber 112 and filled with a neutralizing agent 113, and a discharge chamber 116 formed subsequent to the downstream end of the neutralization chamber 114 are formed.

The introduction chamber 112 has connection ports 112a, 1
12b are formed so as to communicate with each other. A drain water passage 115 is connected to the connection port 112a, and the drain water passage 115 is connected to the drain port 74h of the exhaust gas heat exchanger 23b and the exhaust silencer 2 by branch passages 84a and 84b.
It is connected to the drain port 75c 'of 3c. Further, the exhaust gas return passage 8 is provided at the connection port 112b of the introduction chamber 112.
4c are connected, and the passage 84c is connected to the mist separator 23d.

In the discharge chamber 116, the first and second drain ports 1
16a and 116b are formed, and first and second drainage passages 117 and 118 are connected to the first and second drainage openings 116a and 116b, respectively. The first and second drainage passages 117 and 118 are made of rubber hoses, and extend one end upward from the drainage port and then bend downward so that the water surface in the water neutralizer 82 is A or B. The traps 117a and 118a are maintained at the height. The water surface in the neutralizer 82 is normally held at the water surface A determined by the trap 117a, and is held at the water surface B if the first drainage passage 117 is clogged and cannot be drained. Further, the water surface in the neutralizer 82 becomes slightly lower than A due to the gas pressure from the connection ports 112a and 112b, but this gas pressure prevents the water surface from becoming lower than the discharge port 116b.

Further, the connection port 112 of the introduction chamber 112
The a and 112b are provided slightly above the water surface A, so that a function of separating gas and liquid is obtained.

The lower case 111 has an outer peripheral wall 111a.
The inside of the introduction chamber 1 is defined by the interior wall 111b or 111c.
12, a neutralization chamber 114, and a discharge chamber 116 are defined, and a communication port 111c is formed in a wall portion of the neutralization chamber 114 and the introduction chamber 112 or the drainage chamber 116, and the communication port 111c is formed in the communication port 111c. A punching metal 119 having a large number of holes formed in the plate is arranged. Further, the outer peripheral wall 1
A rubber O-ring 120 is arranged on the upper end surface of 11a, and a ridge 110a formed on the outer periphery of the upper lid 110 abuts on the O-ring 120 to form a seal therebetween. The ridge 110a fits into the accommodation groove of the O-ring 120 and also functions to prevent displacement.

The neutralization chamber 114 has a reciprocating flow path of two reciprocations by three partition walls 111b. The introduction chamber 112 communicates with the upstream end of the flow path and the discharge chamber 116 has the downstream end.
Are in communication. Further, each of the image walls 111 forming the flow path
The upper end surface of b is located higher than the water surface A, and is in contact with a ridge 110b formed on the upper lid 110 so as to face the wall 111b. As a result, even if the water surface becomes B, the drain water will not cross over the wall 111b and short-circuit. The amount of short circuit is small and the top lid 110
Neutralization can be sufficiently performed without attaching the ridge 110b.

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 have a high temperature and a high pressure is supplied to the refrigerant outdoor heat exchangers 11 and 12 through the refrigerant pipe 16a, the four-way valve 15 and the refrigerant pipe 16b. It is cooled by the outside air and liquefied. The liquefied high-pressure refrigerant liquid passes through the main accumulator 8 by the refrigerant pipe 16c and is decompressed by the expansion valve 18 of the refrigerant pipe 17a. The decompressed low-pressure refrigerant liquid takes heat from the indoor air in the indoor heat exchanger 4 and evaporates, and the evaporation heat causes a cooling effect to cool the room. The evaporated refrigerant gas is the refrigerant pipeline 17
From b, passing through the four-way valve 15 and the refrigerant pipe line 16d, passing through the main accumulator 8 and the sub accumulator 9 and returning to the compressor 6, 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 transferred to the indoor heat exchanger 4 via the refrigerant pipes 16a, 17b. It is supplied, where it is cooled by the indoor air and liquefied, and the condensation heat in this case warms the indoor air, and a heating effect is obtained. The liquefied refrigerant liquid is decompressed by the expansion valve 18. The depressurized low-pressure refrigerant liquid evaporates by removing heat from the outside air in the outdoor heat exchangers 11 and 12, 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. Blower fan 44 for outdoor heat exchange
By the rotation, the outside air is sucked into the outdoor heat exchange chamber 14 through the wire nets 38a and 38b, and is discharged upward through the opening 37f in the ceiling. In this case, as shown in FIG. 2, in the upper part of the outdoor heat exchange chamber 14, since it is close to the blower fan 44, air flows in in a substantially horizontal direction. And the upper heat exchanger 1
Since 1 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, since it is far from the blower fan 44, air flows in obliquely upward.
On the other hand, since the lower heat exchangers 12 and 13 are arranged so as to be inclined so that the lower ends thereof are located inside, the air passing through the lower heat exchangers 12 and 13 is, as indicated by the arrow b, the lower heat exchangers. It flows in a direction substantially perpendicular to the vessels 12, 13.

The drain water generated in the exhaust gas heat exchanger 23b and the exhaust silencer 23c passes through the drain water passages 84a, 84b to 115, while the drain water generated in the mist separator 23d passes through the drain water passage. 84c, is introduced into the introduction chamber 112 of the neutralizer 82,
The neutralization chamber 11 passes through the small holes of the punching metal 119.
It flows into 4. Then, it is neutralized by the neutralizing agent 113, and is usually discharged from the drainage chamber 116 to the first drainage channel 11
It is discharged through 7 to the outside.

Further, the exhaust gas flowing into the introduction chamber 112 together with the drain water is discharged to the outside from the mist separator 23d through the exhaust gas return passage 84c. In this case, since the connection ports 112a and 112b are located above the water surface A, gas-liquid separation is reliably performed.
Further, the exhaust gas pressure in the portion of the mist separator 23d connected to the exhaust gas return passage 84c is the same as the drain water passage 1
Since it is lower than the exhaust gas pressure in the exhaust heat exchanger 23b to which 15 is connected, the gas separated in the neutralizer 82 is discharged from the mist separator 23d without any trouble.

As described above, in the present embodiment, since the interior of the neutralization chamber 114 is constituted by the four partition walls 111b to make a reciprocating flow path of two reciprocations, the flow path length, that is, the total length of the neutralizer 82, that is, The contact distance between the neutralizing agent and the drain water and the time can be lengthened, and the neutralizing ability can be improved. As a result, it is easy to secure an arrangement space in the engine-driven air conditioner.

Further, in this embodiment, both the drain water passage 115 and the exhaust gas return passage 84c are connected to the upper side by the water surface A, and the return passage 84c is connected to a portion where the exhaust gas pressure is low. The gas introduced into the washer can be reliably separated, and the separated gas can be reliably discharged.

Furthermore, in this embodiment, the two traps 117a, 1 are provided by the first and second drainage passages 117, 118.
Since 18a is formed, even if the first drainage passage 117 is clogged, drainage is possible from the second drainage passage 118.

When the side of the first trap 117a is clogged, the water surface A rises to B, which has the effect of further improving the neutralization performance. Further, the connection ports 112a and 112b at the same height position are below the water surface B,
Exhaust gas is neutralized by the effect of the head difference due to the difference in position.
2 can be stopped from entering. Even if the exhaust gas pressure overcomes this water head difference and the exhaust gas enters the neutralizer 82, the positions of the connection ports 112a and 112b are considerably higher than the second drain port 116b. Will not be discharged to. When the acidic gas component in the exhaust gas does not dissolve in water and passes through the neutralizer 82 without being neutralized and dissolves in the drain water in the drainage passage 117 or 118, it dissolves concrete or the like around the outlet in the long term. This is not the case, though. If the connection port 112b is located above the water surface B, the amount of retention can be reduced even if the exhaust gas enters the neutralizer 82.

18 and 19 are views for explaining the second embodiment of the present invention. FIG. 18 is a plan view of the neutralizer, and FIG.
9 is a sectional view taken along line XIX-XIX in FIG. The neutralizer 50 of this embodiment includes a lower case 94 and an upper lid 95 detachably attached to the upper end opening of the lower case 94. The drain water passage 92 is connected to one connection port 94a formed so as to communicate with the introduction chamber 98b of the lower case 94.
The exhaust gas return passage 93 is connected to the connection port 94c formed in the No. Further, one drainage passage 69 is connected to the discharge port 94b formed to communicate with the discharge chamber 98c, and a trap 69c is formed. Further, the neutralization chamber 99 is formed in one reciprocating flow path by one picture wall 94a.
6 is filled. In addition, 97 is the punching metal 1 which connects the neutralization chamber 99 and the introduction chamber 98b or the discharge chamber 98c.
00 is a gasket for sealing between the upper lid 95 and the lower case 94.

In the present embodiment, since the neutralization chamber 99 is formed in one reciprocating flow path, the flow path length can be made approximately twice the length of the neutralizer 50, and the size of the neutralizer 50 can be increased. The neutralization ability can be improved without. Also in this embodiment, gas-liquid separation is possible, and the separated gas is surely discharged.

[0059]

According to the drain water treatment apparatus for engine exhaust gas according to the present invention, the neutralization chamber is configured to form a reciprocating flow path of one or more reciprocations, so that the total length of the neutralizer is increased. There is an effect that the flow path length can be lengthened to secure the neutralizing ability, and the arrangement space can be easily secured.

[Brief description of drawings]

FIG. 1 is a front view of an engine-driven air conditioner according to an embodiment of the present invention.

FIG. 2 is a rear view of the apparatus according to the embodiment.

FIG. 3 is a right side view of the apparatus according to the embodiment.

FIG. 4 is a left side view of the apparatus of the above embodiment.

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

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

FIG. 7 is a partial cross-sectional side view of the engine of the above embodiment.

FIG. 8 is a schematic diagram showing a lubricating system of the engine of the embodiment.

FIG. 9 is a partially sectional front view of the engine of the above embodiment.

FIG. 10 is a piping diagram of the intake and exhaust systems of the apparatus of the above embodiment.

FIG. 11 is a partial cross-sectional side view of the exhaust silencer of the apparatus of the above embodiment.

FIG. 12 is a front view of an exhaust silencer of the apparatus of the above embodiment.

FIG. 13 is a cross-sectional front view of the exhaust gas heat exchanger of the apparatus of the above embodiment.

FIG. 14 is a system diagram showing the overall configuration of the apparatus of the above embodiment.

FIG. 15 is a schematic cross-sectional view of a casing of the apparatus of the above-mentioned embodiment.

FIG. 16 is a bottom plan view of the neutralizer of the apparatus of the above embodiment.

17 is a sectional view taken along line XVII-XVII in FIG.

FIG. 18 is a plan view of a neutralizer according to a modified example of the apparatus of the above embodiment.

19 is a sectional view taken along line XIX-XIX in FIG.

[Explanation of symbols]

 5 Engine 23a Exhaust passage (Exhaust pipe) 82 Neutralizer 112 Introduction chamber 113 Neutralizer 114 Neutralization chamber 115 Drain water passage 117,118 First and second drainage passages (drainage passage)

Claims (1)

[Claims] 1. A drain water treatment apparatus for engine exhaust gas, comprising a neutralizer for neutralizing a drain water produced in an exhaust passage of an engine with a neutralizer contained therein, wherein the drain is provided in the neutralizer. An engine exhaust comprising an introduction chamber into which water is introduced and a neutralization chamber filled with the above-mentioned neutralizing agent, which is formed so as to form a reciprocating flow path of one or more reciprocations subsequent to the introduction chamber. Drain water treatment device in gas.