JPH11173702A - Heat transfer device of engine driving refrigerant pressure circulation type - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent the back flow of a drain exhaust passage by joining a drain exhaust passage of large number with a drain exhaust passage of small number so as to direct the drain exhaust passage of large number to a joined drain exhaust passage with respect to a line of flow for connecting the joined drain exhaust passage. SOLUTION: A piping 102 forming a second drain exhaust passage is joined is joined with a piping 103 forming a third drain exhaust passage guided from a drain separator through a confluent pipe 360. They are guided through a piping 190 forming a joined drain exhaust passage to a neutralization device. The drain exhaust passage of large number is joined with the drain exhaust passage of small number so that the drain exhaust passage of large number is directed to the joined drain exhaust passage with respect to a line of flow for connecting the joined drain exhaust passages. Accordingly, a back flow from the drain exhaust passage of small number to the drain exhaust passage of large number is prevented.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an engine-driven refrigerant pressure-feed-circulation heat transfer device in which a compressor is driven by an engine to circulate a refrigerant so as to perform a heat pump function and a refrigeration function.

[0002]

2. Description of the Related Art Such an engine-driven refrigerant pressure transfer circulation type heat transfer device is applied as an air conditioner using a gas heat pump engine as described in, for example, JP-A-7-259549. An engine room with a built-in is installed, and an air intake of an intake passage is provided in a heat exchange room in the outdoor unit or near the outer surface of the outdoor unit, and fresh air is guided to the engine through the intake passage, and exhaust gas is emitted. May be discharged from the exhaust passage to the outside.

In an exhaust passage of an engine, an exhaust gas heat exchanger, an exhaust silencer, and a drain separator are provided in this order. In the first embodiment, water vapor in the exhaust gas cools and condenses, and SO _x and NO _x in the exhaust gas are cooled. The acidic drain water that dissolves the components is sent from the exhaust gas heat exchanger to the neutralizer in the discharge passage,
It is described that the water is sent from the drain separator to the neutralizer in the discharge passage, and in the second embodiment, the drain water is
From the exhaust gas heat exchanger to the gas-liquid separator in the discharge passage, and further to the neutralizer, from the exhaust silencer to the gas-liquid separator in the discharge passage,
Further, it is described that the water is sent to a neutralizer, and then sent from a drain separator to a gas-liquid separator and a neutralizer through a discharge passage.

[0004]

However, the conventional first type
In the embodiment, since the acidic drain water in the exhaust silencer flows through the exhaust passage until reaching the drain water outlet of the drain separator, the exhaust silencer itself may be corroded.

On the other hand, in the second conventional example, the problem of the second embodiment can be solved, but the length of the discharge passage becomes longer and a gas-liquid separator is also required.

SUMMARY OF THE INVENTION The present invention has been made in view of the above point, and it is possible to reduce the price of the discharge passage, and to reduce the discharge pressure by decreasing the exhaust pressure in the order of the exhaust gas heat exchanger, the exhaust silencer, and the drain separator. An object of the present invention is to provide an engine-driven refrigerant pressure-feed circulation heat transfer device that prevents backflow in a passage.

[0007]

Means for Solving the Problems In order to solve the above problems and achieve the object, the present invention has the following constitution.

According to the first aspect of the present invention, there is provided an engine-driven refrigerant pressure-feed circulation type heat transfer apparatus in which a refrigerant is circulated by a compressor driven by an engine in the order of a compressor, a condenser, a throttle, an evaporator, and a compressor. An exhaust gas heat exchanger, an exhaust silencer, and a drain separator are provided in this order in the exhaust passage of the engine, a first drain water discharge passage in the exhaust gas heat exchanger, a second drain water discharge passage in the exhaust silencer, and the drain separator. Connected to a third drain water discharge passage, at least two of the first to third drain water discharge passages are joined together, and the combined drain water discharge passage is led to a neutralizer, and The configuration consists of a drain water discharge passage with a small number and a drain water discharge passage with a large number with respect to the streamline connecting the drain water discharge passage after the merge. Engine driving the refrigerant pumped circulating heat transfer device, characterized in that merge to direct direction. ].

According to the first aspect of the present invention, at least two of the first to third drain water discharge passages are merged with each other, so that the number of discharge passages connected to the neutralizer is reduced, and the number of discharge passages is reduced. It is possible to reduce the price. Also, the pressure at the end on the exhaust passage side of the drain water discharge passage with a small number is
The drain water discharge passage after merging from the drain water discharge passage having a higher number than the pressure at the exhaust passage side end of the drain water discharge passage having a larger number, the drain water along with the exhaust gas,
Exhaust gas containing drain water from the drain water discharge passage having a large number merges so as to be sucked out by this flow, and there is no backflow from the drain water discharge passage having a small number to the drain water discharge passage having a large number.

The invention according to claim 2 is characterized in that the cross-sectional area of the drain water discharge passage having a smaller number is smaller than the cross-sectional area of the drain water discharge passage having a larger number. Engine driven refrigerant pressure transfer circulation type heat transfer device. ].

According to the second aspect of the present invention, in addition to the first aspect, the high pressure at the exhaust passage side end of the drain water discharge passage having a small number is reduced in pressure to the junction, so that the reverse flow Is less likely to occur. Further, the exhaust gas temperature is lower in the exhaust silencer downstream of the exhaust gas heat exchanger and in the drain separator downstream of the exhaust silencer, and drain water is easily condensed. Further, even if a large amount of drain water flows into the exhaust passage of the drain water discharge passage having a small number, the passage cross-sectional area of the drain water discharge passage is large, and the drainage effect is good.

According to a third aspect of the present invention, there is provided an engine-driven refrigerant pressure-feeding and circulating heat transfer device according to the first or second aspect, wherein a throttle is provided in the middle of the drain water discharge passage having a small number. . ].

According to the third aspect of the present invention, in addition to the first or second aspect, the pressure in the vicinity of the junction of the drain water discharge passage having a small number can be more reliably reduced by the throttle, and Is less likely to occur.

According to a fourth aspect of the present invention, there is provided an engine driving refrigerant according to any one of the first to third aspects, wherein a throttle is provided near an exhaust passage of the drain water discharge passage having a small number. Pressure transfer circulation type heat transfer device. ].

According to the fourth aspect of the present invention, in addition to the first to third aspects, it becomes difficult for high-temperature exhaust gas to enter the drain water discharge passage, and the heat resistance of the drain water discharge passage constituting wall is reduced. An inexpensive drain water discharge passage can be used.

[0016]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of an engine-driven air conditioner to which an engine-driven refrigerant pressure-feed circulation heat transfer device of the present invention is applied will be described below with reference to the drawings.

FIG. 1 is a diagram showing the overall configuration of an engine-driven air conditioner.

The engine-driven air conditioner 1 includes an outdoor air conditioning unit (hereinafter, also referred to as an outdoor unit) 2 and an indoor air conditioning unit 3 arranged in one large room R. Refrigerant pipeline 800, 801 of outdoor air conditioning unit 2
Are connected to the refrigerant pipes 810, 811 of the indoor air conditioning unit 3 via the respective joints 800a, 801a.

The indoor air-conditioning unit 3 includes an indoor heat exchanger 4 constituting a condenser during a cooling operation and a condenser during a heating operation, capillary tubes CP1 and CP2 for reducing pressure constituting a throttle, and a check valve V
1. Indoor unit 3 including strainers ST1 and ST2
a are arranged in the refrigerant pipe 820,
A plurality of refrigerant pipes are connected in parallel between the refrigerant pipes 810 and 811 via a zero. The circulating refrigerant is a capillary CP during cooling operation.
2. Pass the check valve V1 through the capillary CP1 during the heating operation. An indoor temperature sensor TH2 is disposed in the room R, and an indoor unit-side refrigerant temperature sensor TH3 is disposed between the indoor heat exchanger 4 and the strainer ST1.

The outdoor air-conditioning unit 2 is provided with an engine 5, and an output shaft of the engine 5 has an electromagnetic clutch 6a,
A pair of compressors 6 are connected via 6a.

The outlets of the pair of compressors 6 include a refrigerant line 16a, an oil separator 19a, a refrigerant line 16b, a four-way valve 15 switched to a cooling operation position, and a refrigerant line 16
c, heat exchange part 1000a of plate heat exchanger 1000,
The condenser for cooling operation is connected to the outdoor heat exchanger 11 constituting the evaporator for heating operation via the refrigerant line 16d, and the outdoor heat exchanger 11 is connected to the refrigerant line 16e and the accumulator 8.
The refrigerant pipe 811 of the indoor air conditioning unit 3 is connected to the refrigerant pipe 811 of the indoor air conditioning unit 3 via the heat exchange section 16f, the refrigerant pipe 801 and the joint 801a. The refrigerant line 800 is connected to the suction port of the compressor 6 via the four-way valve 15, the refrigerant line 16g, the accumulator 8, and the refrigerant line 16h.

In the vicinity of the outdoor heat exchanger 11, an outdoor unit-side refrigerant temperature sensor TH6 is disposed. A high-pressure side pressure sensor P1 is arranged in the refrigerant line 16b, and a low-pressure side pressure sensor P2 is arranged in the refrigerant line 16g. Packed valve PV1 is arranged in refrigerant line 800,
A packed valve PV2 and a strainer 902 are arranged in the refrigerant pipe 801.

A bypass passage 16i, in which an electromagnetic valve 90 and a strainer 91 are arranged, is connected between the refrigerant pipe 16g and the refrigerant pipe 16e. When cooling, when the load on the indoor unit 3a becomes particularly small, the solenoid valve is used. 90 is opened to allow the refrigerant to flow to the accumulator 8 bypassing the refrigerant indoor heat exchanger 4 so as to balance with the load. Note that the indoor CPU 616 described below determines that the difference between the indoor temperature and the set temperature is large during cooling, and that the difference between the set temperature and the indoor temperature is large during heating.
Information indicating that the load is large is transmitted to the outdoor CPU 615 described below.

The oil separator 19a separates the lubricating oil in the refrigerant, and the lubricating oil separated by the oil separator 19a is returned to the suction port side of the compressor 6 via the strainer 19b and the capillary tube 900.

The accumulator 8 is provided with a pair of visual refrigerant level gauges SI at upper and lower positions so that the four refrigerant liquid levels can be checked. The upper part of the accumulator 8 has a strainer 9 heated by the heater H1.
04 and a capillary tube CP11 connected to the refrigerant line 16h, and the lower portion is a strainer 905 heated by the heater H2.
And a refrigerant pipe 16h via a capillary CP12. Downstream of the heaters H1 and H2, accumulator liquid refrigerant level sensing temperature sensors TH4 and TH5 are provided for detecting the refrigerant temperature to detect the level of the liquid refrigerant in the accumulator 8.

An oil discharge passage 91 having a strainer 903 and an on-off valve 911 is provided at the bottom of the accumulator 8.
The oil discharge passage 912 is connected to the refrigerant pipe 1
6h. When the amount of oil accumulated in the lower portion of the accumulator 8 increases, the opening / closing valve 911 is opened manually or automatically so that the oil flows from the accumulator 8 toward the suction port. The refrigerant pipe 16h on the downstream side connected to the accumulator 8 has a U-shape, and upper portions of the U-shape are connected to each other by a capillary 901.

The outdoor air conditioning unit 2 is provided with a cooling water circulation system S. This cooling water circulation system S
Is provided with a cooling water pump 28e. When the cooling water pump 28e is driven, cooling water is supplied through a pipe 250 to the inlet side of the cooling water jacket 28b of the engine 5 and to the engine 5
Of the exhaust gas heat exchanger 23b provided in the exhaust pipe 23a. The outlet side of the cooling water jacket 28b is connected to the radiator 13 via a pipe 251. The cooling water whose temperature has been increased by cooling the engine 5 with the cooling water jacket 28b is cooled by the radiator 13 and is connected via a pipe 252. It is sent to the cooling water pump 28e. The radiator 13 is provided with an outdoor fan 13a for blowing air to the radiator 13.

A pipe 251 is provided at the outlet of the exhaust gas heat exchanger 23b.
Is connected. Air vent pipes 253a and 253b are connected between the pipe 251 and the water inlet 30b between the cooling water jacket 28b and the exhaust gas heat exchanger 23b, and between the downstream side of the radiator 13 and the water inlet 30b, respectively.

The cooling water reservoir tank 30a is connected to the water inlet 30b via a pipe 254, and the cooling water reservoir tank 30a is provided with a communication passage 30c with the atmosphere. In addition, the water inlet 30b is connected to the pipe 252 via the pipe 255, and the cooling water injected from the water inlet 30b is supplied to the pipe 252 and the cooling water reservoir tank 30a, and the water inlet 30b is closed. When the negative pressure of the pipe 252 increases, cooling water is supplied to the pipe 252 from the cooling water reservoir tank 30a.

A thermostat valve THST1 is disposed on the upstream side of the cooling water pump 28e of the pipe 252, and the thermostat valve THST1 is connected to the pipe 2 via a pipe 256.
53.

A thermostat valve THST2 is disposed upstream of the radiator 13 of the pipe 251. The thermostat valve THST2 is connected to the pipe 25 via a pipe 257.
2 and the heat exchange unit 257 a provided in the pipe 252 exchanges heat with the heat exchange unit 1000 a of the plate heat exchanger 1000.

When the engine is cold, the thermostat valve T
While HST1 makes the pipe 251 communicate with the pipe 256,
By shutting off the upstream and downstream portions of the thermostat valve THST1 of the pipe 252 and driving the cooling water pump 28e, the cooling water is supplied to the pipe 250, the cooling water jacket 28b, the exhaust gas heat exchanger 23b, the pipes 251 and 256, and the thermostat. Circulating from the valve THST1 to the cooling water pump 28e.

At the time of engine warm-up when the cooling water temperature exceeds the first predetermined value, the thermostat valve THST1 closes the space between the pipe 256 and the pipe 252, while the thermostat valve THST of the pipe 252 connects between the upstream and the downstream of the thermostat valve THST1. Communication. The thermostat valve THST2 has the cooling water temperature of the first
If the second predetermined value is larger than the second predetermined value, the upstream part of the pipe 251 is communicated with the pipe 257 while
51, shuts off the upstream and downstream portions of the thermostat valve THST2, and drives the cooling water pump 28e to supply cooling water to the pipe 250, the cooling water jacket 28b, the exhaust gas heat exchanger 23b, the pipe 251, the pipe 257, and the plate. The water is circulated from the heat exchange section 257a of the heat exchanger 1000 and the pipe 252 to the cooling water pump 28e. This allows the low-pressure refrigerant to recover the engine waste heat via the heat exchange unit 1000a during the heating operation, thereby increasing the heating capacity.

A water-cooled gas fuel engine is used as the engine 5, and an intake port of the engine 5 has an intake pipe 21a.
The mixer 21b and the air cleaner 21c are connected through the air conditioner, and the intake pipe 21a penetrates the upper part of the outdoor air-conditioning unit 2 and opens to the outside through the air intake 21a2. A chamber 21d is provided at the opening of the intake pipe 21a, and by providing a chamber 21d for reducing pressure fluctuations in the intake passage, the effect of strong and weak wind can be reduced.

The mixer 21b is connected to a gas fuel source by a fuel line 22. The fuel line 22 has a flow control valve 22a for varying the air-fuel ratio A / F of the air-fuel mixture supplied to the combustion chamber.
Zero governor (pressure reducing valve) that reduces fuel pressure to almost atmospheric pressure
22b and two solenoid valves 22c are provided. The zero governor (pressure reducing valve) 22b is connected to the chamber 21d via a pipe 22d, and the outside air pressure is taken into the zero governor (pressure reducing valve) 22b from the air intake 21d1 of the chamber 21d via the pipe 22d.

The exhaust port of the engine 5 is connected to an exhaust gas heat exchanger 23b and an exhaust silencer 23c via an exhaust pipe 23a, and the exhaust pipe 23a is connected to the outdoor air conditioning unit 2 via a drain separator 23d. It is open at the top.

When the exhaust gas passes through the exhaust pipe 23a and flows through the exhaust gas heat exchanger 23b and the exhaust silencer 23c, the exhaust gas is cooled, and the steam in the exhaust gas is condensed to generate drain water having an acidic content. Also in the drain separator 23d, in order to prevent the emission of the acidic gas, the water vapor in the exhaust gas is condensed to dissolve the SO _X or NO _X gas to generate drain water having an acidic component.

The drain water flows through a pipe 101 forming a first drain water discharge passage, a pipe 102 forming a second drain water discharge passage, and a pipe 103 forming a third drain water discharge passage. Led to the neutralizer 104,
The drain water is neutralized by the neutralizer 104 and drained through a pipe 105. In this embodiment, the pipe 102 forming the second drain water discharge path and the pipe 103 forming the third drain water discharge path are merged, and the pipe 102 forming the merged drain water discharge path is connected. Neutralizer 10
Leading to 4. By generating the drain water in this way, the exhaust gas can be purified, and the acidic drain water can be neutralized and purified by the neutralizer 104 and drained.

The blow-by gas containing oil mist from the cylinder head of the engine 5 is sent to the engine oil separator 23e,
Then, the breather gas is supplied through the line 108 to the air cleaner 2.
1c, the oil communicates with the oil pan of the engine 5 via the oil return passage 106.

The outdoor air-conditioning unit 2 is provided with an outside air temperature sensor TH1 and an engine coolant temperature sensor TH7.

FIG. 2 is a control circuit diagram of the engine-driven air conditioner. The engine-driven air conditioner 1 includes a control device, a sensor group, and an actuator group in each of the outdoor air conditioning unit 2 and the plurality of indoor units 3a. The outdoor CPU 615 of the outdoor air-conditioning unit 2 and the indoor CPU 616 of the plurality of indoor units 3a transmit and receive information via the data bus 620 and are controlled. The memory 617 is connected to the outdoor CPU 615 and stores, for example, various control information.

The outdoor CPU 615 controls the throttle valve opening control actuator 311, the two electromagnetic clutches 6a, the starting motor 238 of the engine 5, the driving actuator 235 of the outdoor fan 13a, the driving actuator 261 of the cooling water pump 28e, and the bypass passage 16i. The drive actuator 301 of the solenoid valve 90 that opens and closes, and other actuator groups 640, for example, the fuel gas flow control valve 22a,
It controls the four-way valve 15, the electromagnetic valve 22c, etc., and controls the engine rotation sensor 310, the high pressure side pressure sensor P1, the low pressure side pressure sensor P2, the refrigerant temperature sensors TH4 to TH6, the engine coolant temperature sensor TH7, and other sensor groups, for example. The detection data of the outside air temperature sensor TH1 and the like are taken in.

The indoor CPU 616 includes the blower fan 240
a, control of the indoor louver motor 240b, the indoor unit side refrigerant liquid temperature sensor TH3, the indoor remote control operation section 570a, the indoor temperature sensor TH2, and the like, or capture of detection data.

Next, a specific arrangement structure of the outdoor air conditioning unit 2 will be described in detail with reference to FIGS. FIG.
FIG. 4 is a schematic configuration diagram of the outdoor air conditioning unit, FIG. 4 is a schematic cross-sectional view of an engine room and a piping room of the outdoor air conditioning unit, and FIG. 5 is a diagram illustrating a connection portion between the outdoor air conditioning unit and the outside.

The casing 31 of the outdoor air-conditioning unit 2
A floor plate 33 is provided on the base member 32, and pillars 34 are erected at four corners of the floor plate 33, the upper ends of the four pillars 34 are covered with a ceiling plate 35, and the left and right sides are left and right side plates 37c. , 3
7d, and the front and rear side plates 37a, 37b
The front, rear, left, and right plates 37a to 37d are detachable to ensure the maintainability of each device.

The interior of the casing 31 is divided into an engine room 7 and a piping room 10 by a partition wall 44a. In the engine room 7, an inspection device T used for maintenance and inspection of the outdoor air-conditioning unit 2 is disposed so as to face the front side plate 37a.
Operation can be easily performed by removing 7a. In the engine room 7, an engine 5 and a compressor 6 integrated in the longitudinal direction are arranged. Since the volume of the engine room 7 is reduced by the division and the internal temperature easily rises,
A ventilation inlet 46a in which a ventilation fan 47 is arranged and a ventilation outlet to the heat exchanger room 14 are arranged.

An air cleaner 21c is disposed above the compressor 6, and the exhaust silencer 23c and the engine oil separator 23 are arranged in a position parallel to the air cleaner 21c.
e are arranged side by side up and down. Air cleaner 21c
Pipe 21a connected to the upstream side of the air cleaner 21 passes through the ceiling plate 35 through a chamber 21d disposed in the upper part of the heat exchanger room 9 and near the ceiling plate 35, and the air intake 21a2 is opened to the outside. The mixer 21b connected downstream of the mixer 21c is connected to the intake port 5a of the engine 5. The exhaust gas heat exchanger 23b is fixedly arranged on the engine 5 from the front side of the engine 5, and an exhaust outlet 23b1 is arranged on the compressor side in the longitudinal direction of the exhaust gas heat exchanger 23b. The exhaust pipe 23a from the exhaust outlet 23b1 passes through the top plate 44b of the engine room 7 from the exhaust silencer 23с arranged in the space above the compressor 6 and below the engine separator 23, passes through the heat exchanger room 9, and passes through the ceiling plate. Exhaust outlet 23d through a drain separator 23d provided through
1 to the outside.

A mixer 21b having a built-in throttle is arranged beside the cylinder head 5b, and the mixer 21b and the air cleaner 21c are connected by an intake pipe 21a1. The compressor 6 is disposed on an extension of the crankshaft of the engine 5 and is located at a position lower than the entire cylinder head 5a of the engine 5, so that the upper space of the compressor 6 can be effectively used, and the air cleaner 21c and the exhaust Silencer 23c
And the engine oil separator 23e are arranged vertically, whereby the engine room 7 can be made smaller. Further, an exhaust pipe 23a1 between the exhaust gas heat exchanger 23b and the exhaust silencer 23c.
Can be shortened, and the workability of attaching and detaching the exhaust pipe 23a1 is improved.

In the engine room 7 at a position other than above the engine 5, an air cleaner 21c, an exhaust silencer 23c and an engine oil separator 23e are arranged in a space above the compressor 6 connected to the engine 5, and the compressor 6
The exhaust gas heat exchanger 23b is disposed at a position higher than the neutralizer 104, and the air cleaner 21c, the exhaust silencer 23c, and the drain separator 23d are disposed at a higher position. As a result, the height of the engine room 7 can be reduced. Also,
The condensed water in the exhaust gas heat exchanger 23b and the exhaust silencer 23c can be reliably guided to the neutralizer 104, and the condensed water in the drain separator 23d can be reliably guided to the neutralizer 104. The drain water is neutralized by the neutralizer 104 and drained from a pipe 105 penetrating the floor plate 33.

The exhaust silencer 23c, the drain separator 23d, and the neutralizer 104 are disposed on the right side of the outdoor air conditioning unit 2 and the drain port of the exhaust gas heat exchanger 23b is disposed on the right side. , 10
2,103 is short and drain water does not stay.

Further, the engine oil separator 23e is disposed by utilizing the space above the exhaust silencer 23c, and is located above the engine 5, so that the oil separated from the breather gas can be reliably used by utilizing the head difference. The oil can be led to the oil pan of the engine 5. In addition, since the amount of oil remaining in the oil separator 23e can be reduced, the function of the oil separator 23e for separating oil from breather gas can be enhanced.

On the inner surface side of the rear plate 37b in the piping chamber 10,
An electrical box 50 in which various control devices and the like are accommodated and a terminal room 699 are provided. The floor plate 33 is provided with a piping chamber air intake 33b for introducing outside air into the piping chamber 10, and outside air is introduced into the piping chamber 10 through the air intake 33b. There is no floor plate 33 below the terminal room 699, and there is no ceiling. The terminal chamber 699 is a communication passage connecting the piping chamber 10 and the outside of the casing 31. Further, the terminal chamber 699 is opened to the rear outside with the rear side plate 37b removed. Joints 800a, 801a of refrigerant pipes 800, 801 and joint 802a of pipe 22d
Are located in the terminal chamber 699 and are respectively connected to external piping introduced from below the terminal chamber 699. A power supply cord 953 connected to an external power supply and having a plug at the end is also provided in the terminal room 6.
Pass 99.

A pressure reducing diaphragm shown in FIG. 7 is built in the zero governor 22b, and a piping 22d as an atmospheric pressure introducing pipe for introducing atmospheric pressure from the air intake port 21d1 to one atmospheric pressure chamber of the diaphragm is also connected to the terminal chamber 699. It is arranged to pass. As shown in FIG. 5, a breaker 950, a power line terminal block 951 and a communication line terminal block 952 are provided on the surface of the electrical box 50, and a power cord 953 is connected to the power line terminal block 951. .

Next, the exhaust gas heat exchanger 23b will be described. The exhaust gas heat exchanger 23b is configured as shown in FIG. The exhaust gas heat exchanger 23b is mounted on the exhaust side of the engine 5, and the engine 5 and the exhaust gas heat exchanger
3b is integrated.

The exhaust gas heat exchanger 23b has an upstream heat exchange section 1210 consisting of an expansion chamber having a large exhaust passage cross-sectional area and having irregularities on the wall, and a downstream heat exchange section having a non-circular screw pipe in the exhaust passage. A part 1211 is provided.

The upstream heat exchange section 1210 is
In FIG. 7, a U-shaped exhaust expansion chamber 1212 is formed. On the wall surface of the exhaust expansion chamber 1212, irregularities are formed by fins 1213 and projections 1214. This exhaust expansion chamber 12
12 has a partition wall 1207d from one side 1207c.
Extend in proximity to the other side 1207e, this side 12
The upper expansion chamber 1212a and the lower expansion chamber 12
12b is formed.

The upper expansion chamber 121 of the upstream heat exchange section 1210
An upper cooling water jacket 1215a is formed around the periphery of the partition wall 12a.
07d. Further, a lower cooling water jacket 1215b is formed around the lower expansion chamber 1212b, and the cooling water entering from the cooling water inlet 1226 is supplied to the downstream heat exchange unit 112.
After flowing to the right inside 211, it enters the lower cooling water jacket 1215b through the communication port 1227, flows to the left through the lower cooling water jacket 1215b, and then flows to the upper cooling water jacket 1215b.
a, flows to the right through the upper cooling water jacket 1215a, is discharged from a cooling water outlet 1215c formed at the upper right end of the casing 1207, and flows through the cooling water pipe 1029e2.
to go into.

The upstream heat exchange section 1210 is
A connection part (not shown) is formed at 07, and this connection part can be directly connected to the exhaust side of the engine 5. Engine 5
Exhaust gas from the exhaust side of the upper exhaust expansion chamber 12 through exhaust gas inlets 1216 formed at four places of the casing 1207.
The exhaust gas is introduced into the lower exhaust expansion chamber 121a.
2b, and further guided to the downstream heat exchange unit 1211.

The high-temperature, high-pressure exhaust gas generated by the combustion of the air-fuel mixture in the combustion chamber of the engine 5 is introduced into the upstream heat exchange section 1210 of the exhaust gas heat exchanger 23b, where the cooling water and Heat is exchanged between the two to be cooled.

The exhaust expansion chamber 1212 of the upstream heat exchange section 1210 reduces the exhaust resistance of the exhaust gas from the exhaust side of the engine 5, thereby improving the exhaust efficiency and also reducing the exhaust pressure and improving the noise reduction effect. I do. Moreover,
Irregularities are formed by fins 1213 and protrusions 1214 on the wall surface of the exhaust expansion chamber 1212 of the upstream side heat exchange section 1210, and the irregularities increase the surface area, so that high heat exchange efficiency can be obtained.

The exhaust gas passage of the downstream heat exchange section 1211 is constituted by a screw pipe 1220 having a non-circular cross section. A closing plate 1221 is provided at one end of the plurality of screw pipes 1220, and a gasket 1222 is provided at the other end.
Are provided, and a guide plate 1223 is provided at an intermediate portion to form a pipe unit 1224. The screw pipe 1220 has a cruciform cross section, and four projections 1220 a radially protruding from the outer periphery thereof form a spiral along the outer periphery of the screw pipe 1220 in the length direction.

The pipe unit 1224 is
07, a cooling water inlet 1226 is formed below the cooling water chamber 1225, and a communication port 1227 is formed above the cooling water chamber 1225. Cooling water from the engine 5 flows from the cooling water inlet 1226 to the cooling water chamber 122.
5 and circulates through the cooling water chamber 1225 to be supplied from the cooling water outlet 1227 to the lower cooling water passage 1215b of the upstream heat exchange unit 1210.

The closing plate 1 of the pipe unit 1224
221 is sealed by an O-ring 1228, and the cover 1230 is further secured by bolts 1231 via a gasket 1229.
At the lower portion of the side portion 1207e of the casing 1207. Collective exhaust chamber 1232 with cover 1230
Is formed, and the exhaust gas outlet 1 is provided at the center of the cover 1230.
233 are provided, and a drain water outlet 1234 is provided below the cover 1230. A first drain water discharge passage described below is connected to the drain water outlet 1234.

On the other side of the pipe unit 1224, a gasket 1222 is fastened to the lower part of the side portion 1207 c of the casing 1207 with a bolt 1235.
2, the cover 1236 is fastened and fixed to the side 1207c of the casing 1207 with bolts 1237. A communication collective exhaust chamber 1238 is formed by the cover 1236, and exhaust gas is introduced into the communication collective exhaust chamber 1238 from the lower expansion chamber 1212 b of the upstream heat exchange unit 1210. This exhaust gas is guided from the communicating collective exhaust chamber 1238 to the collective exhaust chamber 1232 through the screw pipe 1220 of the pipe unit 1224, and the collective exhaust chamber 123
2 is exhausted from an exhaust gas outlet 1233.

As described above, since the exhaust passage of the downstream heat exchange section 1211 is constituted by the screw pipe 1220, the exhaust gas flows in the screw pipe 1220 as a swirling flow, and the exhaust gas is exhausted by the turbulence effect of the exhaust gas. The heat transfer coefficient of the gas to the cooling water is increased, and high heat exchange efficiency is obtained.

In the exhaust gas heat exchanger 23b, the upstream heat exchange unit 1210 and the downstream heat exchange unit 1211
The exhaust gas exchanges heat with the cooling water to effectively recover the heat of the exhaust gas. At the same time, the temperature and pressure of the exhaust gas are reduced to reduce the exhaust noise. Then, water vapor in the exhaust gas is condensed, and at the same time, NO _X and SO _X are dissolved to become acidic drain water, which flows out from the drain water outlet 1234 to the first drain water discharge passage.

Next, the exhaust silencer 23c will be described with reference to FIG. 7A is a cross-sectional view in which a part of the exhaust silencer is broken, FIG. 7B is a cross-sectional view taken along the line bb of FIG. 7A, and FIG. 7C is an opening for drain water introduction. FIG.

The exhaust silencer 23c is provided with an exhaust introduction part 351 at the lower end of the cylindrical housing 300, and a part 351a of the exhaust introduction part 351 is connected to the cylindrical housing 300.
To prevent the drain water from flowing backward from the exhaust introduction section 351. An exhaust outlet 352 is provided at the upper end of the cylindrical housing 300.
2 protrudes into the cylindrical housing 300.

The cylindrical housing 300 has three partition walls 3
10, 311 and 312 are provided, and the first expansion chamber 31 is provided.
3, a second expansion chamber 314, a third expansion chamber 315, and a fourth expansion chamber 316 are formed. A communication pipe 320 is provided on the upper side of the center partition wall 311, and the communication pipes 321 and 32 are provided on the lower side of the respective partition walls 310 and 312 on both sides.
2 is provided, and the communication pipe 321 on the introduction side is located at a position close to the exhaust introduction section 351, and the communication pipe 3
Reference numeral 22 is located away from the exhaust outlet 352. Exhaust gas is introduced from the exhaust introduction section 301 into the first expansion chamber 313 and expanded, and the communication pipe 321 causes the second expansion chamber 31 to expand.
4 and expands from the communication pipe 320 to the third expansion chamber 3.
15, expands, flows from the communication pipe 322 to the fourth expansion chamber 316, expands, thereby silencing, and exhaust gas is discharged from the exhaust outlet 352. Further, in each of the expansion chambers 313, 314, 315, and 316, the temperature of the exhaust gas decreases due to the expansion of the exhaust gas, and water vapor in the exhaust gas condenses to generate drain water.

Drain water holes 340, 341 and 342 are formed below the partition walls 310, 311 and 312, respectively, so that the drain water flows into the respective drain water holes 340 and 34.
1, 342 are connected to the fourth expansion chamber 316 and are connected to a lower portion of the fourth expansion chamber 316 to form a second drain water discharge passage attached to the drain water discharge section 343. It is discharged to the pipe 102.

The cylindrical housing 30 below the expansion chamber 316
A circular opening is opened at 0, and a pipe-shaped drain discharge portion 343 having a flange in contact with the periphery of the opening is connected to the cylindrical housing 300 by welding. A half of the circular opening is covered with a partition wall 312, and a communication part between the expansion chamber 316 and the drain discharge part 343 has a semicircular drain water introduction opening 33.
It becomes 0. In this way, the drain water introduction opening 330 is made smaller than the inner cross section of the drain discharge part 343 to have a function of restricting. Also, a semicircular drain water introduction opening 330 is provided.
The communication pipe 322 is further protruded into the expansion chamber 31 to prevent the exhaust gas passing through the communication pipe 322 from directly flowing into the drain water introduction opening 330. Thereby, it is possible to prevent the pressure in the drain discharge section 343 from becoming abnormally high.

FIG. 8 is a detailed view of the junction of the drain water discharge passage. Piping 102 constituting second drain water discharge passage
And a pipe 103 forming a third drain water discharge passage led from the drain separator 23d, via a merge pipe 360, and a neutralizer 104 via a pipe 190 forming the merged drain water discharge path. Leading to. Piping 1
02, the pipe 103 and the pipe 190 are rubber pipes. With respect to the bent streamline from the pipe 103 forming the second drain water discharge passage to the pipe 190 forming the drain water discharge path after merging, the pipe 103 forming the third drain water discharge path is joined after the merging. In the direction of the drain water discharge passage.

Piping 1 constituting second drain water discharge passage
A throttle 361 is provided at 02, and the passage cross-sectional area of the pipe 102 forming the second drain water discharge passage is set smaller than the passage cross-sectional area of the pipe 103 forming the third drain water discharge passage. . As a result, the pressure on the inlet side of the pipe 103 becomes higher than that on the inlet side of the pipe 103.
Can be made close to the pressure on the merging side of the pipe 103. In this way, in addition to the shape of the merging portion that makes it difficult for the flow from the merging side end of the pipe 102 to the merging side end of the pipe 103 to occur, the pipe resistance is used. It is possible to prevent the flow of 103 to the merging side end.

In this embodiment, the pipe 102 forming the second drain water discharge passage and the pipe 103 forming the third drain water discharge passage are joined.
Pipes 102, 102, 1 constituting a drain water discharge passage of
03 are joined to each other, and a pipe 190 forming the combined drain water discharge passage is guided to the neutralizer 104. The configuration of the merge portion is a drain water discharge passage having a small number and a drain water after the merge. The drain water discharge passage having a larger number with respect to the flow line connecting the discharge passages may be joined so as to point in the direction of the drain water discharge passage after the merge.

As described above, since at least two of the first to third drain water discharge passages merge with each other, the neutralizer 1
It is possible to reduce the number of discharge passages connected to the discharge passage 04 and reduce the price of the discharge passages. In addition, the pressure at the end of the drain water discharge passage having the smaller number on the exhaust passage side is higher than the pressure at the end of the drain water discharge passage having the larger number on the exhaust passage side. The exhaust gas including drain water from the drain water discharge passage having a larger number merges so that the drain water flows together with the exhaust gas and is sucked into this flow, and the drain water having a higher number flows from the drain water discharge passage having a smaller number. There is no backflow to the discharge passage.

In this embodiment, the cross-sectional area of the pipe 102 forming the second drain water discharge passage is set smaller than the cross-sectional area of the pipe 103 forming the third drain water discharge passage. However, the cross-sectional area of the drain water discharge passage having the smaller number among the pipes 102, 102, 103 constituting the first to third drain water discharge passages is smaller than the passage cross-sectional area of the drain water discharge passage having the higher number. .

As described above, the high pressure at the exhaust passage side end of the drain water discharge passage having a small number is reduced by reducing the cross-sectional area of the passage to the junction, thereby increasing the passage resistance and decreasing the pressure. Hateful. Further, the exhaust gas temperature is lower in the exhaust silencer 23c downstream of the exhaust gas heat exchanger 23b and in the drain separator 23d downstream of the exhaust silencer 23c, and drain water is easily condensed.

The phrase that the cross-sectional area of the drain water discharge passage having a smaller number is smaller than the cross-sectional area of the drain water discharge passage having a larger number means that the cross-sectional area of the drain water discharge passage having a larger number is smaller than that of the drain water having a smaller number. It is agreed that the cross-sectional area of the water discharge passage is larger than that of the water discharge passage, so that a large amount of drain water that is easily condensed and is easily guided to the junction. The pipe 190 constituting the drain water discharge passage after the merger is closer to or equal to the passage cross-sectional area of the drain water discharge passage having a larger number than the passage cross-sectional area of the drain water discharge passage having a smaller number, and furthermore, the drain having a larger drain number By making the passage cross-sectional area larger than the water discharge passage, the water can be guided to the neutralizer 104 more easily after the merging.

Further, in this embodiment, the throttle 102 is provided in the pipe 102 forming the second drain water discharge passage, but the pipes forming the first to third drain water discharge passages to be joined. A throttle 361 may be provided in the middle of the drain water discharge passage having a smaller number among 102, 102 and 103. Alternatively, all of the first to third drain water discharge passages may be joined.

As described above, the pressure in the vicinity of the junction of the drain water discharge passage having a small number can be more reliably reduced by the throttle 361, and the backflow is less likely to occur.

Further, in this embodiment, the throttle 361 is provided in the pipe 102 forming the second drain water discharge passage, but the pipe 102 forming the first to third drain water discharge passages is By providing a throttle near the exhaust passage of the drain water discharge passage having a small number of 102 and 103, it becomes difficult for high-temperature exhaust gas to enter the drain water discharge passage, and the heat resistance of the drain water discharge passage constituting wall is reduced. And an inexpensive drain water discharge passage is sufficient.

Alternatively, two of the first to third drain water discharge passages may be merged, and then the remaining drain water discharge passages may be merged downstream of the two. Each junction is configured in the same manner as described above. That is, with respect to the first and second merged ones, the merged one may be configured as a drain water discharge passage having a smaller number than the third drain water discharge passage, and the structure of the downstream merging portion may be configured. In addition, for the second and third merged portions, the merged one may be configured as a drain water discharge passage having a number larger than that of the first drain water discharge passage to form the structure of the downstream merge portion. Further, for the first and third merged ones, the merged one may be configured as a drain water discharge passage having a number larger than that of the second drain water discharge passage to form the structure of the downstream merging portion. Further, all of the first to third drain water discharge passages may be joined at one place. Also in this case, with respect to the streamline from the first drain water discharge passage to the drain water discharge passage after merging, both the second and third drain water discharge passages are directed to the drain water discharge passage after merging. So that both the third drain water discharge passage and the drain water discharge passage after the merge are directed to the streamline from the second drain water discharge passage to the drain water discharge passage after the merge. It is good to join A throttle is provided in the middle of the first and second drain water discharge passages, and the throttle in the middle of the first drain water discharge passage has a smaller passage cross-sectional area than the middle of the second drain water discharge passage. It is good to make it smaller.

Next, the neutralizer 104 will be described in detail with reference to FIGS. 9 and 10. FIG. 9 is a front view of the neutralizer, FIG.
0 is a development view of the neutralizer along the line XX in FIG.

The neutralizer 104 has an exhaust gas heat exchanger 23b
101 forming a first drain water passage connected to
And a pipe 190 forming a drain water discharge passage which is a combination of the pipe 102 forming the second drain water discharge passage and the pipe 103 forming the third drain water discharge passage.

The case 494 of the neutralizer 104 has a lid 495
A partition wall 494a extending from one side wall to the center is formed in the case 494, and a punching metal 496, 497 having a large number of small holes is formed inside the case wall 494a. Compartment 49
8b, a compartment 498c on the drain water outlet side is provided. A neutralizing agent 499 is provided in the compartment 498a.

The case 494 has entrances 491a and 491b.
Are formed, and a pipe 101 forming a first drain water passage and a pipe 190 forming a merged drain water discharge path are connected to the inlets 491a and 491b.
A throttle 490 is provided at the connection portion 1, and drain water and exhaust gas from these flow into the compartment 498 b. Thereby, after the high pressure drain water and exhaust gas from the exhaust gas heat exchanger 23b are reduced in pressure by passing through the restrictor 490, they can be guided to the compartment 498b on the drain water inlet side. Can be smoothly guided to the compartment 498b on the drain water inlet side.
Outlets 492a and 492b are formed in the case 494, and pipes 105 and 1 are connected to the outlets 492a and 492b.
05 is connected, and drain water is discharged from the compartment 498c via the pipes 105, 105.

FIG. 11 is a schematic configuration diagram of another embodiment of the outdoor air conditioning unit. Water-cooled 4 as engine 701
A cycle engine is used, and a cylinder block 701 is used.
is mounted on a crankcase 701b, and a cylinder head 701c is mounted on a cylinder block 701a. An intake manifold 701d and an exhaust manifold 701e are formed in the cylinder head 701c. A piston 706 is provided in the cylinder block 701a, and the piston 706 is connected to a crankshaft 703 via a connecting rod 707. Cylinder head 70
1c, a water jacket 708 is formed, and the water jacket 708 has a cooling water circuit 73 of the cooling water circulation system S.
6a is connected.

An opening 701d of the intake manifold 701d and the exhaust manifold 701e that opens to the combustion chamber 799.
1, 701e1 is provided with an intake valve 715 and an exhaust valve 716. The intake valve 715 and the exhaust valve 716 are provided with rocker arms 713, 714 and push rods 790, 79.
1 is provided so as to be opened and closed at a predetermined timing. A spark plug 724 is provided on the cylinder head 701c.
Are provided so as to face the combustion chamber 799, and the ignition plug 72
4 is connected to an ignition coil 725, and the ignition control circuit 726 generates a high voltage to the ignition coil 725 to spark the spark plug 724. The ignition control circuit 726 is controlled by the outdoor unit CPU 733. The outdoor unit CPU 733 includes a crank angle sensor 709.
The detection information is input from the engine speed sensor 710.

The driving gears G1 and G3 are provided on the crankshaft 703.
And power from the crankshaft 703 is transmitted from the driven gears G2 and G4 to the compressors 702A and 702B via the electromagnetic clutches 705A and 705B. Compressor 7
A refrigerant circuit 702 is connected to 02A and 702B to send refrigerant from a high pressure side and return to a low pressure side. The electromagnetic clutches 705A and 705B are controlled by the outdoor unit CPU 733.

The exhaust manifold 701e has an exhaust passage 7
The exhaust passage 712 is provided with an exhaust gas heat exchanger 727 and an exhaust silencer 766. The exhaust gas heat exchanger 727 exchanges heat with the cooling water circuit 736a.

The intake manifold 701d has an intake passage 7
11, an air cleaner 717 is connected to the intake passage 711, and a filter 7 is connected to the air cleaner 717.
17a is provided. A chamber 718 is provided at the tip of the intake passage 711, and the chamber 718 has an air intake port 718 a disposed in the heat exchanger chamber 9.
Is provided.

A throttle valve 734 is provided in the intake passage 711.
The throttle valve 734 is driven by a stepping motor 735, and the stepping motor 735 is controlled by the outdoor unit CPU 733, and the larger the load, the larger the throttle valve opening. In the intake passage 711, a fuel injection valve 789 is disposed downstream of the throttle valve 734. A flow control valve 723 is provided in a fuel passage 720 connected to the fuel injection valve 789, and the flow control valve 723 is connected to the outdoor unit C.
It is controlled by the PU 733.

Further, the flow control valve 7 is provided in the fuel passage 720.
A pressure reducing valve 72 for reducing pressure to a predetermined injection pressure upstream of 23
2, and two solenoid valves 721 are provided.
Is controlled by the outdoor unit CPU 733. Pressure reducing valve 722
Is connected to the chamber 718 via a pipe 740.
Inside the chamber 718, a wind pressure inlet 740 of the pipe 740 is provided.
a is opened, and outside air is taken into the pressure reducing valve 722 from the wind pressure inlet 740a via the pipe 740. This pressure reducing valve 7
22 has the same structure as the zero governor 22b of FIG.
The resilience of the resilience means 231 is increased, and
2 can be adjusted to a predetermined injection pressure higher than the atmospheric pressure.

Further, a pipe constituting a first drain water discharge passage in the exhaust gas heat exchanger 727, a pipe constituting a second drain water discharge passage in the exhaust silencer 766, and a third drain water discharge passage in the drain separator. The constituent pipes are connected, at least two of the first to third drain water discharge passages are merged with each other, and the merged drain water discharge passage is guided to the neutralizer. The drain water discharge passage having a larger number with respect to the stream line connecting the drain water discharge passage and the drain water discharge passage after merging is merged so as to be directed in the direction of the drain water discharge passage after merging. 10 to FIG. Further, the passage cross-sectional area of the drain water discharge passage having a large number is made larger than the passage cross-sectional area of the drain water discharge passage having a small number, and a throttle is provided in the middle of the drain water discharge passage having a small number. The provision of a throttle near the exhaust passage of the small drain water discharge passage is the same as in the embodiment of FIGS.

The pressure detecting means 7 is located near the open end of the intake passage 711, that is, near the air intake port 718a.
19 may be provided and this air pressure information may be sent to the outdoor CPU 733. When the pressure value becomes large, the outdoor CPU 733 controls the stepping motor 735 to operate the throttle valve 734 to make a correction so that the throttle opening is reduced. Alternatively, the opening degree of the flow control valve 723 may be increased, or the valve opening period of the fuel injection valve 789 may be lengthened. The pressure detecting means 719 includes an intake passage 711
May be provided on the way.

As described above, when the pressure value becomes large, the throttle opening is corrected to be small to prevent an increase in the air amount, there is no need to adjust the fuel amount, and there is no change in the air-fuel ratio A / F. Even when wind acts on the intake air intake port, the engine can be prevented from being stopped.

Further, in synchronization with the control of the rotation speed of the outdoor fan 13a of the outdoor CPU 733 by the load, when the rotation speed increases or when the detection pressure of the pressure detecting means 719 increases, the outdoor CPU 733 controls the flow control valve 723. The control may be performed such that the opening degree is increased or the fuel injection period of the fuel injection valve 789 is lengthened. Further, instead of the pressure reducing valve 722, a variable throttle, a fuel pressure sensor disposed in a fuel storage chamber provided downstream of the variable throttle, and an outdoor CPU 73
3, a pressure reducing device may be configured. Feedback control is performed on the opening degree of the variable throttle that reduces the fuel pressure when fuel passes so that the fuel pressure sensor becomes the target pressure.
The target pressure is increased when the rotation speed of the outdoor fan 13a increases or when the pressure detected by the pressure detecting means 719 increases.

Thus, even if dynamic pressure acts on the air intake port 718a of the intake passage 711, the air-fuel ratio A / F of the air-fuel mixture supplied to the engine 701 can be maintained in the combustible range, and the engine 701 is stopped. Can be prevented.

Further, when fuel is directly injected from the fuel injection valve 789 into the combustion chamber 799, the same throttle valve opening control, opening control of the flow control valve 723, fuel injection period control, By performing one or a combination of the injection pressure controls, the air-fuel ratio A / F of the air-fuel mixture formed in the engine 701 even when a dynamic pressure acts on the air intake 718a of the intake passage 711.
Can be kept in the flammable region, and the engine 701 can be prevented from being stopped.

[0100]

As described above, according to the first aspect of the present invention, the first drain water discharge passage is provided in the exhaust gas heat exchanger, the second drain water discharge passage is provided in the exhaust silencer, and the third drain water is provided in the drain separator. Since the discharge passages are connected and at least two of the first to third drain water discharge passages are joined together, the number of discharge passages connected to the neutralizer is reduced, and the price of the discharge passages can be reduced. It is. In addition, the pressure at the end of the drain water discharge passage having the smaller number on the exhaust passage side is higher than the pressure at the end of the drain water discharge passage having the larger number on the exhaust passage side. The exhaust gas including drain water from the drain water discharge passage having a larger number merges so that the drain water flows together with the exhaust gas and is sucked into this flow, and the drain water having a higher number flows from the drain water discharge passage having a smaller number. There is no backflow to the discharge passage.

According to the second aspect of the present invention, in addition to the first aspect, the cross-sectional area of the drain water discharge passage having a large number is made larger than the cross-sectional area of the drain water discharge passage having a small number. Since the high pressure at the end of the water discharge passage on the exhaust passage side is reduced in pressure to the junction,
The backflow hardly occurs. Further, the exhaust gas temperature is lower in the exhaust silencer downstream of the exhaust gas heat exchanger and in the drain separator downstream of the exhaust silencer, and drain water is easily condensed. Further, even if a large amount of drain water flows into the exhaust passage of the drain water discharge passage having a small number, the passage cross-sectional area of the drain water discharge passage is large, and the drainage effect is good.

According to the third aspect of the present invention, in addition to the first or second aspect, the pressure in the vicinity of the junction of the drain water discharge passage having a small number can be reduced more reliably by the throttle, and the backflow hardly occurs. .

According to the fourth aspect of the present invention, in addition to the first to third aspects, high-temperature exhaust gas is less likely to enter the drain water discharge passage, and the heat resistance of the drain water discharge passage constituting wall is reduced. It is possible to use an inexpensive drain water discharge passage.

[Brief description of the drawings]

FIG. 1 is a diagram showing an overall configuration of an engine-driven air conditioner.

FIG. 2 is a control circuit diagram of the engine-driven air conditioner.

FIG. 3 is a schematic configuration diagram of an outdoor air conditioning unit.

FIG. 4 is a schematic cross-sectional plan view of an engine room and a piping room of the outdoor air conditioning unit.

FIG. 5 is a diagram showing a connection portion between the outdoor air conditioning unit and the outside.

FIG. 6 is a sectional view of an exhaust gas heat exchanger.

FIG. 7 is a diagram showing an exhaust silencer.

FIG. 8 is a detailed view of a junction of a drain water discharge passage.

FIG. 9 is a front view of the neutralizer.

FIG. 10 is a development view of the neutralizer along the line XX in FIG. 9;

FIG. 11 is a schematic configuration diagram of a liquid according to another embodiment of the outdoor air conditioning unit.

[Explanation of symbols]

 2 Outdoor air-conditioning unit 5 Engine 6 Compressor 23a Exhaust passage 23b Exhaust gas heat exchanger 23c Exhaust silencer 23d Drain separator 101 Piping constituting first drain water discharge passage 102 Piping constituting second drain water discharge passage 103 Third Constituting the drain water discharge passage of the tank 104 Neutralizer

Claims (4)

[Claims] 1. An engine-driven refrigerant pressure-feed circulation type heat transfer device in which a refrigerant is circulated by a compressor driven by an engine in the order of a compressor, a condenser, a throttle, an evaporator, and a compressor. A heat exchanger, an exhaust silencer, and a drain separator are provided in this order, a first drain water discharge passage in the exhaust gas heat exchanger, a second drain water discharge passage in the exhaust silencer, and a third drain water discharge in the drain separator. Connecting the at least two of the first through third drain water discharge passages to each other; guiding the combined drain water discharge passage to a neutralizer; A water discharge passage,
An engine-driven refrigerant pumping / circulating heat characterized in that a drain water discharge passage having a larger number with respect to a stream line connecting the drain water discharge passage after merging merges in a direction of the drain water discharge passage after merging. Moving equipment. 2. The engine-driven refrigerant pressure-feed circulation heat system according to claim 1, wherein the cross-sectional area of the drain water discharge passage having the smaller number is smaller than the cross-sectional area of the drain water discharge passage having the larger number. Moving equipment. 3. The heat transfer device according to claim 1, wherein a throttle is provided in the middle of the drain water discharge passage having a small number. 4. The heat transfer device according to claim 1, wherein a throttle is provided near an exhaust passage of the drain water discharge passage having a small number.