JPS61155647A - Drainage discharger of heat exchanger utilizing engine - Google Patents

Abstract

PURPOSE:To silence exhaust sound at the time of drainage by discharging condensed water in the exhaust system of a facility provided with an engine in its liquid tank to use engine exhaust heat, into a silencer with a plurality of chamber installed in the liquid tank. CONSTITUTION:An engine with its crank shaft 16 vertically positioned is installed in a liquid tank 12, and a compressor 32 is driven to operate an air conditioner, as well as a cylinder 19a, a cylinder head 19b, an exhaust pipe 20, and a muffler 22 are cooled by water in the liquid tank to acquire warm water. Exhaust condensed water inside the exhaust pipe 20 and the muffler 22 is introduced through pipes 28a, 28b to a drain muffler 30, together with a part of exhaust. In the upper chamber 61c of the drain muffler 30, exhaust including drainage is silenced after being discharged into the stored condensed water in the chamber 61c, and through a pipe 61g, the same silencing procedure is done in a lower chamber 61b. And then only exhaust gas is discharged into the liquid tank through a pipe 61h for perfect silencing.

Description

DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention is a heat exchange device using an engine, more specifically, an engine for driving a working machine is disposed in a liquid tank storing a heat transfer liquid. , rIA is applied to the drain water discharge device of a heat exchange device that heats liquid with exhaust heat from the engine.

(Prior Art and its Problems) In general, this type of heat exchange device has the advantage that it is possible to heat a heat transfer liquid (for example, water) by using the exhaust heat of the engine, and at the same time, it can cool the engine.

The present applicant has developed a prior art that facilitates the maintenance of this type of heat exchange device and has already filed an application (Japanese Patent Application No. 173801/1983, filing date: September 19, 1988).

However, in such prior art, the exhaust pipe that discharges the condensed water in the exhaust passage located below the liquid level as drain water opens directly to the outside of the liquid tank, so exhaust noise leaks from the exhaust pipe to the outside. There is a problem in that it causes noise.

Particularly when the heat exchange device is applied to an outdoor heat exchange device for air conditioning, quietness is strictly required, so it is desired to reduce exhaust noise from the exhaust pipe.

(Object of the Invention) The present invention provides a heat exchange device using an engine, in which exhaust gas A from a discharge pipe for discharging drain water from an exhaust passage.
! It is an object of the present invention to provide a drain water discharge system for a heat exchange device using an engine, which can reduce the amount of water used.

(Structure of the Invention) (1) Technical Means The present invention consists of placing an engine in a liquid tank storing heat-transferring liquid, connecting a working machine to the crankshaft of the engine, and lowering the engine body below the liquid level. In a heat exchanger using an engine, the engine is equipped with a mounting flange located above the liquid level, and the condensed water generated in the passage A is discharged to the outside of the liquid tank. A discharge pipe is provided, and a plurality of muffling chambers are formed by dividing the condensed water and exhaust gas from the discharge pipe into it, and the exhaust gas is discharged into the stored condensed water. Drain water of a heat exchange device using an engine, characterized in that a connecting pipe is provided to connect the exhaust gas and exhaust gas to flow in sequentially, and a drain water outlet for collecting condensed water is provided in a final stage muffling chamber. It is a discharge device.

(2) Function The condensed water from the discharge pipe is stored in a sound deadening chamber, and the exhaust gas is discharged into the condensed water to muffle the exhaust noise while the drain water is discharged to the outside from the outlet.

(Embodiment) In FIG. 1 showing the case where the present invention is applied to an outdoor heat exchange device for air conditioning, for example, an engine 14 is provided in a liquid tank 12 storing water 10 or other heat medium liquid. . The engine 14 is arranged with the crankshaft 16 perpendicular to the cylinder block 19 relative to the crankcase 18.
a and the cylinder radius 19b are aligned horizontally. A tubular exhaust heat exchanger 20 is provided below the cylinder head 19b, and an exhaust pipe 21a extending downward from the lower surface of the cylinder head 19b is connected to the tubular exhaust heat exchanger 20.

A hot water tank 15a is provided below the liquid tank 12, and a cooling water pump 17a, a hot water pump 17b, etc. are fixed to the front of the hot water tank 15a1 and the liquid tank 12. 17c
is a lower front cover, and the lower front cover 170 is detachable. The upper end of the lower front cover 17c is in close contact with the lower end of the separate upper front cover 17d. The upper front cover 17d is also removable.

Therefore, the external shape of the outdoor heat exchanger shown in Figure 1 is
As shown in Figures a and 1b, it has a vertically elongated box shape, and the side and rear surfaces of the liquid tank 12 and the hot water tank 15a (Figure 1) are covered with a cover 178, and a radiator is installed above the cover 17ei. 17h is exposed.

Additionally, there is an intake silencer 17 above the combretsuna to 117.
1 is placed, and the air intake silencer 171 covers the top of the combrella room 117 to create a humbresser room! This is to prevent the noise from the 17k from leaking outside. Above the chamber 50 is a ceiling plate 660.

A primary exhaust muffler 22 which also serves as a heat exchanger is provided below the crankcase 18 (not shown in FIG. 2).
The primary iJF air silencer 22 and the tubular exhaust heat exchanger 20 are connected via a connecting pipe 21b.

A gear case 24 is provided on the lower surface of the crankcase 18, and the tubular exhaust heat exchanger 20 is fixed to the gear case 24 via a bracket 21c. gear case 2
An oil tank 26 is provided on the lower surface of the engine 4, and the primary exhaust silencer 22 is attached to an oil tank stay 27a fixed to the oil tank 26. Primary exhaust silencer 2
2 is connected to one end of a discharge via 28a for draining drain water. The other end of the discharge pipe 28a is the liquid tank 1
It is connected to a drain muffler 30, which will be described in detail later, which is fixed to the outer surface of the liquid tank 12, and is structured to discharge condensed water in the liquid tank 12 to the outside. Note that there is also a discharge pipe 28 b h< between the pipe exhaust heat exchanger 20 and the drain muffler 30.
It is provided.

The crankshaft 16 projects upward from the crankcase 18, and a flywheel 31a is fixed to the projecting end thereof. The flywheel 31a is located below the water surface 11a of the water 10.

In order to prevent water from entering the installation space 31b of the flywheel 31a, a flywheel housing 31c that surrounds the flywheel 31a from below and around it is provided at the top of the crankcase 18. Flywheel housing 31c and crankcase 18G! Equipped with bosses 31d and 31e surrounding the crankcase,
The bosses 31d and 31e are fixed in a watertight manner by bolts 31r.

The generating coil 31o is attached to the bolt 31f on the top surface of the boss 31d.
The flywheel magnet 3 surrounding the power generating coil 31Q is fixed to the lower surface of the flywheel 31a.
1h is installation. This flywheel magnet 3
1h and a power generating device including a power generating coil 31Q is for charging a starter battery, for example.

A joint 311 is fixed to the upper surface of the flywheel 31a, and the lower end of a vertical input shaft 33a of a compressor 32 (working machine) is connected to the joint 31i.

The lower surface of the mounting flange 34 is attached in close contact with the upper end of the flywheel housing 31c. The compressor 32 is fitted into the frontage of the mounting flange 34 from above in a spigot type manner and bolted to the opening of the mounting flange 34 at the lower end outer peripheral portion 33b.

An oil strainer 3 is installed on the top surface of the mounting flange 34.
6. A step motor 38 etc. are provided.

Further, the intake pipe 40 and the exhaust pipe 42 extend further upward through a support plate 44 (FIG. 1).

The intake pipe 40 is formed with a bend in the middle, and the upper part is biased closer to the flywheel housing 31C than the lower part.

A boss 31j is formed at the upper end of the flywheel housing 31c below the oil strainer 36,
There is an oil hole 3 inside the boss 31 that communicates with the oil strainer 36.
1k is perforated. The lower end of the oil hole 31 is connected to the upper end of an oil pipe 37a passing through the water 10, and the lower end of the oil pipe 37a is connected to the I! It is connected to the V case 24.

1! An r-reservoir (not shown) is built into the case 24, and oil is supplied from the oil tank 26 to the gear 1r.
The oil is sucked into the pump and passed through the oil pipe 3 to the oil strainer 36.
7a, and then returns to the gear case 24 via a return pipe (not shown) arranged parallel to the oil pipe 37a, and is then fed through a communication port (not shown) to the crankshaft 1.
6. The oil is fed under pressure to the main bearing and its basin moving parts, and after lubricating them, it is returned to the oil tank 26 again.

The step motor 38 is for controlling the angular position of the governor lever shaft of the engine 14 in response to a pulse signal from the outside. 34 extending downward toward the engine 14,
The lower end of the output shaft of the step motor 38 is connected to the end of the governor lever shaft that protrudes into the water from the crankcase 18 .

J shown in FIG.
is interposed, and the mounting flange 34 is elastically held on the support plate 44 by a vibration-proof connector 46.

The anti-vibration connector 46 is attached to the support plate 44 as shown in FIG. 2a.
A bolt 47a1 is fixed to the mounting flange 34 and passes through the mounting flange 34.A vibration isolating rubber 47b1 is inserted between the mounting flange 34 and the support plate 44 and is installed on the outer periphery of the bolt 47a. Consists of nut 47G.

The upper end of the bolt 47a extends upward through a through hole 47e of a stay 47d fixed to the support plate 44 by, for example, welding, and the through hole 478 has a larger diameter than the nut 47G.

The above vibration-proof connector 46 is attached to the mounting flange 3
For example, they are provided at 8 locations at equal intervals on the outer peripheral edge of 4. As shown in FIG. 1, a packing 47f is interposed between the mounting flange 34 and the support plate 44 further inward from the vibration-proof connector 46.
At f, there is a structure that prevents steam from escaping between the mounting flange 34 and the support plate 44.

A support &44 is fixed to the outer peripheral edge of the support plate 44 and the upper end 13b of the liquid tank 12 in an airtight state.

An intake silencer 1711, a secondary exhaust silencer 37, and a motor 51a are arranged at the intersection 50 above the compressor 32, oil strainer 36, step motor 38, etc.
1a is for rotationally driving the cooling fan 51b. The motor 51a and the cooling fan 51b are mounted on a fan mounting base 5 that forms a fan shroud that improves the circulation of cooling air.
Covered by 1C.

Upper chamber 50, compressor 32, oil strainer 36,
It is separated from the step motor etc. by the compressor attachment 17C17k, and the compressor 32 and engine 14
This prevents noise from leaking upwards.

A heat radiator 17h is provided so as to surround the side surfaces of 50 to 50. As shown in FIG. 1C, the heat radiator 17h has a substantially annular shape with a portion cut out, and the cutout portion of the heat radiator 17h is airtightly connected to a fan mounting base 51c surrounding the cooling fan 51b. . The motor 51a is supported by a stay 516 on a fan mounting base 51G. Fan mounting base 5
An upper front cover 17d is attached to the front side of 1C. The upper front cover 17d is abutted against the fan mounting base 51C to form spaces 51e and 51j inside.
In order to facilitate the assembly of the upper front cover 176, the first
An upper gap 17h shown in Figure d is provided.

The space 51j is continuous with the inner space of the lower front cover 17C (FIG. 1), and noise from the cooling water pump 17a1, feed pump 17b, etc. is transmitted to the space 51J. There is a possibility that this uM leaks from the space 51e to the outside through the gap 51h.

Therefore, as shown in FIG. 1d, the space 51e and the space 51
A rubber plate-shaped butterfly valve 51f that is bolted to the bracket 51i and in close contact with a protrusion 17f integral with the upper front cover 17d is provided between the cooling water pump 17a1.
Noise from the hot water pump 17b etc. is blocked. Space part 51
e communicates with the upper chamber 50 through a gap 51h,
When the fan 51a is operated, the space 518 has a negative pressure relative to the fan 51j. Therefore, the butterfly valve 51f has a protrusion 17
This negative pressure brings the space 51 into close contact with the space 51.
e is completely cut off. The bracket 51i is integrated with the fan mounting base 51c.

The water surface 11a of the water 10 in FIG. 1 is at the same level as the upper end of the liquid tank 12. The engine 14 is immersed in water 10 up to the vicinity of the upper end of the flywheel housing 31C, and the engine body consisting of the crankcase 18, cylinder block 19a, and cylinder head 19b is located at a relatively deep position in the liquid tank 12. 1 which also serves as a container 20 and a heat exchanger
Next, I decided to install the exhaust silencer 22 in a deep position.
The entire water 10 in the liquid tank 12 is efficiently heated by utilizing the convection phenomenon, and the dry water 11b at temperature a is always collected in the upper half of the liquid tank 12.

In order to use this hot water 11b as a heat source, the liquid tank 12
A heat exchange pipe 0 is arranged in the upper half of the pipe. The heat exchange pipe 0 extends spirally near the inner circumferential surface 13c of the liquid tank 12, and there is an empty space of ml inside the heat exchange pipe 0.
The heating medium is heated by hot water 11b. In addition, in order to efficiently heat the heat exchange pipe 0 over its entire length, the crankshaft 16 is eccentric to the center o-ok of the liquid 1ff12, and the cylinder block 1
9a and the cylinder head 19b are located relatively close to the center o-O.

Furthermore, a spacer rubber 60a is interposed between the heat exchange pipe 0 and the inner circumferential surface 13c, and the spacer rubber 60a
The heat exchange pipe 0 is elastically supported. The spacer rubber 60a is 2! near the diagonal line! ! placed in place.

When the engine 14 is made eccentric as described above, both the cylinder head 19b and the crankcase 18 are sufficiently separated from the inner circumferential surface 13c, and a sufficiently wide gap 13d is formed around the entire circumference of the engine 14. Therefore, the water 10 does not remain in a part of the gap 13d, and the hot water 11b flows uniformly through the gap 13d, so that the heat exchange pipe 0 is efficiently heated.

Next, the structure of each part will be explained in more detail.

As shown in FIG. 2b, which is an enlarged partial view of FIG. 2, the boss 31e of the crankcase 18 and the flywheel housing 3
1G bosses 31 (j) are joined to each other in a watertight state at the annular end faces. A cylindrical portion 35a is formed on the inner circumference of the boss 31e, and the cylindrical portion 35a is connected to the boss 31e through a waterproof seal 35b. An oil seal 15C is fitted to the inner circumference of the boss 31d in a spindle type manner.An oil seal 15C is provided between the upper inner circumference of the boss 31d and the crankshaft 16. A bearing 15b is provided.

As shown in FIG. 2C, the joint/11a of the intake pipe 40 is integrally provided with a cylindrical portion 41b extending upward around the intake pipe 40. As shown in FIG. A cylindrical portion 41d of a rubber seal 41G is in close contact with the outer peripheral surface of the intake pipe 40. The cylindrical portion 41d is integrally molded with the annular portion 41e and the cylindrical portion 41f.

The annular portion 41e is thin, has a curved cross section, and has high flexibility.

As shown in FIG. 2, a large number of radiation fins 19c are formed on the outer peripheral surface of the cylinder block 19a. The radiation fins 19c are spaced apart from each other, and the radiation fins 19c are spaced apart from each other.
This allows the water 10 to be efficiently heated and the engine 14 to be efficiently cooled.

As shown in FIG. 2d, a water channel 19d is provided inside the cylinder block 19a. The water channel 19d is arranged at a position corresponding to the cooling water jacket of a normal water-cooled engine, and is formed between the bottom wall of the valve arm chamber 19e and the ceiling of the combustion chamber 19f, and the upper and lower ends of the water channel 19d are open. There is.

Therefore, the water 10 in the liquid tank 12 can flow in the vertical direction through the water channel 19d, and with this structure as well, the water 10 is efficiently heated and the cylinder head 19b is efficiently cooled.

A first embodiment of the drain muffler 30 will be described with reference to FIG. In this embodiment, a drain muffler 3 is provided on the outer peripheral surface of the liquid tank 12.
This is a case where 0 is fixed.

The drain muffler 30 has a substantially cylindrical main body 61a divided by a partition wall 61b into a lower silencing chamber 61c and a lower silencing chamber 61d, and the upper silencing chamber 61c and the lower silencing chamber 61d are stacked vertically to form the upper silencing! i! The lower ends of the inlet pipes 61e and 61f are inserted and fixed in the inside of the inlet pipe 61c, and the upper ends of the inlet pipes 61e and 61f protrude to the outside. The inlet pipe 61e is connected to the discharge pipe 28a, and the inlet pipe 61f is connected to the discharge pipe 28b.

A connecting pipe 10 is provided that penetrates the partition wall 61b, and the welded portions of the partition wall 61b, the main body 61a, and the connecting pipe 1Q maintain watertightness. An outlet pipe 61h is provided at the upper part of the lower silencing chamber 61d so as to communicate with the inside thereof, and drain water is discharged to the outside from the outlet pipe 61h.

In the first embodiment described above, the mixed condensed water and exhaust gas discharged through the discharge pipes 28a and 28b flow into the upper silencing chamber 61c from the inlet pipes 61e and 61f,
Condensed water is stored in the upper silencer ff161c, exhaust gas is discharged into the water, and the exhaust noise is inquired.

The condensed water and exhaust gas from the upper muffling u61c pass through the connecting pipe 10 to the lower muffling chamber 51d1. : Inflow, condensed water is similarly stored in the lower silencing chamber 61d, exhaust gas is discharged into the water, further muffling the exhaust noise, and drain water and exhaust gas are discharged from the outlet pipe 61h to the overflow pipe 61h. Discharge outside.

Therefore, exhaust gas from the exhaust pipes 28a and 28b is submerged into the upper silencing chamber 6101 and the lower silencing chamber 61d to muffle exhaust noise, and the lower silencing chamber 61c,
Since condensed water is naturally stored in the lower silencing chamber 61d, there is no need to replenish water for submerged exhaust.

FIG. 3a shows a second embodiment of the drain muffler 30, in which a first silencing chamber 62a and a second silencing chamber 62b are arranged adjacently,
Connect pipe 2G from the first muffling chamber 62a to the second muffling chamber 6
This structure allows condensed water and exhaust gas to flow to 2b.

FIG. 3b shows a third embodiment of the drain muffler 30, in which a first silencing chamber 63a and a second silencing chamber 63b are arranged concentrically, and a connecting pipe 3c connects the first silencing chamber 63a to the second silencing chamber 63a.
It has a structure in which condensed water and exhaust gas are passed through the muffling chamber 63b and discharged to the outside from the outlet pipe 63d.

Furthermore, the drain muffler 30 is not limited to being placed outside the liquid tank 12 as described above;
Alternatively, only the drain water outlet pipe may be housed inside the liquid 112 and only the drain water outlet pipe may protrude outside the liquid 112.

An embodiment of the secondary exhaust muffler 37 will be described with reference to FIG. The secondary exhaust muffler 37 has a main body 64 having a substantially cylindrical shape.
a1 main body 64a with a plurality of silencing chambers 64b, 64c, 64d
The partition wall 64e that divides the sound deadening chambers 64b, 64c, 6
It is composed of a connecting pipe 4f, etc., which communicates with 4d.

Mute! i! 64b is provided with an inlet pipe 64g, and the inlet pipe 64Q is connected to the primary exhaust muffler 22 via a connecting pipe 42 (FIG. 2) provided in the primary exhaust muffler 22. The silencing chamber 64d has an outlet pipe 64i1.
is provided, and the outlet pipe 64h is an exhaust pipe 64n (
(Fig. 2).

The connecting pipe 4f passes through the center of the partition wall 64e and extends to the side plate 641 of the main body 64a, and the connecting pipe 4f and the side plate 64i are bolted to the bolt 64 via the end plate 64j of the connecting pipe 4f. . For example, a large number of ventilation holes 64m are formed in a portion of the connecting pipe 4f inside the silencing chamber 64b.

The connecting pipe 4f and the side plate 641 are fixed using bolts 64.
It is not limited to bolting using bolts, for example, other means such as welding may be used.

Generally, an exhaust gas outlet pipe is fixed to the side plate 64o as shown in FIG. 4C. In this method, the vibration of the side plate 640 is reduced, but the length L of the blinding device including the exhaust gas outlet pipe is
There was a drawback that l was larger than the length L2 of the silencer body.

Exhaust 8' of this invention! i ￥r'a solved the above-mentioned problem, shortened the overall length of the exhaust gas outlet pipes 64g and 64h in the direction perpendicular to the central axis of the muffler as shown in Figure 4, and shortened the side plate 64i. This reduces noise caused by vibration.

The installation structure of the secondary exhaust silencer 37 will be explained with reference to FIGS. 4a and 4b. The intake silencer 17i (Fig. 1)
A strip plate 65a is welded to the stay 658 fixed to the stay 658. The strip plate 65a is notched at a portion facing the stay 65e, and a flange 65b is formed at the end. The strip plate 65a is arranged at a location where the main body 64a vibrates the most (the axial center between the partition walls 64e or the axial center between the partition 64e and the side plate 64i).

7 bolts 65C passing through the flange 65b are provided respectively, and the bolts 65C tighten the outer peripheral surface of the main body 64a while being pulled together by a turnbuckle 65d.

In the above secondary exhaust muffler 37, the side plate 64 due to exhaust pulsation
The vibrations shown by the two-dot chain line in FIG. Reduced.

In addition, the strip plate 65a & turnbuckle 65d
Since the central portion between the partition walls 64e in the axial direction of the exhaust gas 5a is tightened, vibrations shown by the two-dot chain line in the IT48 diagram due to exhaust pulsation are also prevented. Vibration of the main body 64a can be roughly reduced by using a plurality of belt-shaped plates 65a instead of just one.

Next, a first embodiment of the intake silencer 171 is shown in FIGS.
This will be explained with reference to figure a. The intake silencer 171 is composed of an upper half body 66a1, a lower half body 66b, an element 66c, etc., and has a flat cylindrical shape and is placed on the compressor cover 17. Upper half body 66a, lower half body 6
6b is made of synthetic resin and has a substantially symmetrical shape, and the split surface 66d
are collided with. An inlet 66e is formed in the upper half body 66a, and clean air from the outside is taken in through the inlet 66e. The lower half body 66b has an intake outlet 6.
6f is formed, an intake outlet 66f is connected to the intake pipe 40, and an element 66c is housed inside.

A flange 66h is formed on the outer peripheral edge of the lower half body 66a and the lower half body 66b, and a bolt (
The upper half main body 66a and the lower half main body 66b are fixed with bolts (V (not shown)), and about four bolts are attached to the compressor chamber! 1f1
It is set to be fixed at 7k.

Further, as shown in FIG. 5b, the diameter of the intake silencer 171 is set to D.
In this case, bolts 67a are provided passing through the intake silencer 171 at, for example, three locations on a circular locus of D/4 from the center of the intake silencer 171.

A stiffener 67b is fitted around the bolt 67a, and a nut 67c holds the upper half body 66a and the lower half body 66b.
1. Tightening the stiffener 67b.

In the intake silencer 17i described above, the upper half body 68a and the lower half body 66b have a large area and are likely to cause vibration due to intake pulsation.
, tighten the stiffener 67b with the bolt 67a and nut 67c.
Since the upper half body 66 is tightened together with the
Vibration of the a1 lower half body 66t) due to intake pulsation is prevented. Moreover, the bolt 67a and the stiffener 67b are located at a position where the primary and secondary vibrations caused by the intake pulsation of the upper half body 66a and the lower half body 66b can be most effectively reduced, that is, on a circular trajectory of D/4 from the center of the intake silencer 17i. Since it is placed on top of the desk, it has an excellent vibration prevention effect.

FIG. 5C shows a second embodiment of the intake silencer 171. In FIG. 5C, the inside of the intake silencer 17i is arranged into silencing chambers 68a, 6.
It is divided into 8b and 68c by a partition wall 68dr. Partition wall 68d
A connecting pipe 8e168f penetrating through is provided.

In this embodiment, as shown in Figs. 5d and 5q, a partition wall is provided at the antinode position of both vibration modes for the vibration modes ① and ① that are present at frequencies ν1 and ν2 of the conventional vibration spectrum characteristic 67x. As a result, noise caused by vibration of the intake silencer 171 is significantly reduced.

Further, a third embodiment of the intake silencer 17i will be described with reference to FIG. 5e. This embodiment is a flat cylindrical intake silencer 1.
Partition walls 69a and 69b are arranged approximately concentrically within the interior of 71.
, 69c, 69d, and 69e are provided, each forming an opening 69f. The first connection passage 70a divided by the partition wall 69a is set to the length of the partition 1, and the partition wall 69a and the space between the first connection passage 70a and the partition wall 69a are set to the length of the first connection passage 70a. The volume of the first sound-muffling seedling 70b between 69b and 69b is set to Vl, and 1 is set to be much larger than the volume of the first connection passage 70a.

The second connection passage 70C between the partition wall 69b and the partition wall 69C is L.
The length is set to 2 (L1'>12). The volume of the second muffler 70d communicating with the second connection passage 70c is V2.
(Vl>V2). Similarly, the length of the third connection passage 70e is set to L3, and the volume of the third silencing chamber 70f is set to 3.

In the third embodiment described above, the intake from the suction port 66e is connected to the first connecting passage 70a and the second connecting passage 70c, which have different lengths.
, through the third connection passage 70e to the first silencing chamber 70b, the second silencing chamber 706, and the third silencing chamber 70f, so that intake noise of different frequencies is reduced in each passage and the silencing T,
Demonstrates a muffling effect over the entire frequency range of intake noise.

Next, a fourth embodiment will be described with reference to FIG. 5f.

In this embodiment, the position of the opening 69f is different from the case of FIG. The lengths of In are set to be different from each other. The same applies to the openings 69f of the second and subsequent partition walls 69b and the like.

In the fourth embodiment described above, the intake sound waves flowing in from the intake port 66e are branched in both left and right directions, pass through passages of different lengths, and are collected at the opening 69f, causing interference of the sound waves, which is also effective as a so-called interference type muffler. Since it has both, the effect of reducing intake noise is even greater.

Next, a fifth embodiment of the intake silencer 171 will be described with reference to FIG. 1e. In this embodiment, the intake air silencer 17'1 is installed at the top of the heat exchanger and also serves as a rain shield for the heat exchanger QN.

FIG. 6 shows details of the tubular exhaust heat exchanger 20. The tubular exhaust heat exchanger 20 is formed by spirally bending a relatively large-diameter main pipe T271a, and has a structure in which both ends of a main pipe 71a are communicated through a small-diameter bypass pipe 71b. The bypass pipe 71b passes inside the main pipe 71a.

Such a pipe-type exhaust heat exchanger 20 transfers heat to the surrounding water 1o while the high-temperature exhaust gas discharged from the engine 14 flows through the main pipe 71a, heating the water 10 and cooling the exhaust gas. be done.

Thermal energy in the exhaust gases wasted from the engine 14 is thus recovered in the water 10.

FIG. 6a is a model of the tubular exhaust heat exchanger 20, in which the length of the bypass pipe 71b is 15, and the length of the bypass pipe 71b is 15.
Let F6 be the length of the main pipe 71a short-circuited in the main pipe 7.
When the speed of sound in the C1 main pipe 71a is f and the frequency of the exhaust gas in the C1 main pipe 71a, the relationship λ=C/f (1) holds true for the wavelength λ.

At this time, in order to damp the vibrations of the exhaust gases that merge at the connection point 71c, the pressure waves traveling through the main pipe 71a and the pressure waves passing through the bypass pipe 71b interfere with each other to cancel out the vibrations. When λ/2 (2), exhaust noise is reduced.

Therefore, the frequency f1 to be attenuated is f1-c/(2(F6-15))...
- (3) Therefore, there is a similar attenuation effect even at frequencies that are integral multiples of the frequency f1.

In order to alleviate the resonance phenomenon in the portion of length F7 between the engine 14 and the connection point 71d, if the resonance frequency of the portion of length F7 is Fl, then Fl-C/(4・F7)... - 3 times, 5 times, 7 times, etc. of equations (4) and (4).

Therefore, by matching the resonance frequency F1 and the attenuation frequency f1, the resonance phenomenon in the length F7 can be alleviated.

Similarly, in order to alleviate the resonance phenomenon of the length F8 between the primary muffler 22 and the connection point 71G, if the resonance frequency is F2, then F2-C/(2・F8)... 5) and an integer multiple of equation (5).

Therefore, by matching the resonance frequency F2 and the attenuation frequency f1, the resonance phenomenon in the length 8 portion can be alleviated.

Note that when the bypass pipe 71b has a small diameter, there is an advantage that most of the exhaust gas passes through the main pipe 71al11, increasing the amount of heat energy recovered. Also, the bypass pipe 71b
When the diameter is the same as that of the main pipe 71a, the length F is compared to the length F7.
5 and the length F6, the tubular heat exchanger 2
The total length of the 0 piping becomes longer, and the amount of heat energy recovered can be increased without increasing the pressure inside the main piping of exhaust gas.

The structure of the support portion of the exhaust pipe 42 will be explained with reference to FIG. The exhaust pipe 42 passes through the hole 72a of the support plate 44,
The hole 72a has a diameter larger than the outer diameter of the exhaust pipe 42. A lower flange 72b is fixed to the outer periphery of the exhaust pipe 42, for example, by welding. A sealing member 72c is interposed between the exhaust pipe 42 and the hole 72a.

The seal member 72C is made of rubber and has a cylindrical portion 72d and an edge portion 72e that closely contacts the support plate 44. exhaust pipe 42
A threaded portion 43a is formed in the upper flange 72f, which is screwed into the threaded portion 43a, and the seal portion 4172c is tightened.

Conventionally, the exhaust pipe 42 was directly attached to the support plate 44 via the flange 72b with bolts or the like, but with this method, the exhaust pipe 42 vibrates due to the exhaust sound of the engine 14, and the exhaust pipe 42 is attached to the support plate 44 via the flange 72b. 44, the support plate 44 vibrates, and the source of vibration is the exhaust pipe 42 as shown in FIG.
In this support structure, the vibration transmitted from the exhaust pipe 42 to the support plate 44 is absorbed by the sealing member 72c, so that the noise generated by the vibration of the support plate 44 can be reduced.

7a and 7b show different embodiments, and FIG. 7a shows a spacer rubber 7 that is in close contact with the outer peripheral surface of the exhaust pipe 42.
3a and 73b elastically support the exhaust pipe 42 on the support plate 44. Also, FIG. 7b shows the mounting flange 34.
A notch 74a is formed on the outer peripheral edge of the exhaust pipe 42, and the exhaust pipe 42 is elastically supported by a spacer rubber 74b that is fitted to the outside of the support plate 44 in the notch 74a.

As described above, in the outdoor heat exchange device for air conditioning to which the present invention is applied, the exhaust heat from the engine 14 is transferred to the pipe exhaust heat exchanger 20.
．． As much as possible is recovered as water 10 by the primary exhaust muffler 22 or the like.

In addition, the exhaust noise of the engine 14 is first caused by the pipe exhaust heat exchanger 2.
After the sound is effectively muffled by the bypass pipe 71b etc. of 0, 1
The noise is muffled by the secondary muffler 22, further muffled by the secondary muffler 37, and then exhausted to the outside through the exhaust pipe 64n. The vibrations of the exhaust pipe are also blocked by the sealing member 72C, so that the exhaust noise is extremely reduced.

Next, since the intake noise is muffled by the intake silencer 17i disposed at the lower part of the air intake 50, the intake noise is also significantly reduced.

Therefore, the noise of outdoor heat exchange equipment for air conditioning, which has recently become a problem as neighborhood noise in residential areas, can be significantly reduced, and the exhaust air and intake air are separated, allowing clean air to be taken in as the intake air.

(Effects of the Invention) As explained above, the drain water discharge device of a heat exchange device using an engine according to the present invention is such that the engine is placed in a liquid tank storing a heat transfer liquid, and In a heat exchange device that uses an engine that connects a working machine and has the engine body located below the liquid level, and the engine is equipped with a mounting flange located above the liquid level, inside the exhaust passage located below the liquid level. A discharge pipe is provided to discharge the condensed water generated in the tank outside the liquid tank, and a plurality of silencing chambers are divided into which the condensed water and exhaust gas from the discharge pipe are allowed to flow in, and the exhaust gas is discharged into the stored condensed water. A connecting pipe was provided to connect the condensed water and exhaust gas to these silencing chambers in sequence, and a drain water outlet was provided to discharge the condensed water to the final silencing chamber, resulting in the following effects. can be played.

That is, the mixed condensed water and exhaust gas discharged through the discharge pipe 28a1 and the discharge pipe 28b flow into the upper silencing chamber 61c from the inlet pipes 61e and 61f, and the upper silencing chamber 61c enters the upper silencing chamber 61c. Exhaust noise can be muffled by storing condensed water in the chamber 61c and discharging the exhaust gas into the water, and the condensed water and exhaust gas from the upper muffling chamber 61c are muffled in the lower muffler'i! 61'd, condensed water is similarly stored in the lower silencing chamber 61d, and the exhaust gas is discharged into the water, further muffling the exhaust noise. can be discharged to the outside.

Therefore, the exhaust gas from the exhaust pipe 28a1 and the exhaust pipe 28b is submergedly exhausted into the upper silencing chamber 61c and the upper silencing chamber 61d, and while the exhaust noise is muffled, the exhaust gas is discharged from the exhaust pipe 61h.
Drain water can be discharged to the outside. Also, the upper silencing chamber 61
c. Since condensed water is naturally stored in the lower silencing chamber 61d, there is no need to replenish water for submerged exhaust.

(Another Embodiment) (1) The present invention is not limited to being applied to an outdoor heat exchange device for air conditioning, but can be applied to engines for other heat exchange devices.

[Brief explanation of the drawing]

FIG. 1 is an IIl1gi plane view showing the case where the present invention is applied to an outdoor heat exchange device 27 for air conditioning, FIG. , Figure 1C is the first
FIG. 1D is a vertical cross-sectional partial view showing a butterfly valve provided in the passage; FIG. 1E is a view corresponding to arrow b in FIG. 1A in the fifth embodiment of the intake silencer; Figure 2 is a partially cutaway enlarged view showing the engine part, Figure 3 is a vertical sectional view showing the first embodiment of the drain muffler, Figures 3a and 3b.
The figures are structural diagrams showing different embodiments of the drain muffler, respectively.
Figures 4 and 4C are longitudinal sectional views showing the primary exhaust silencer, Figure 4a is a front view of the secondary exhaust silencer, Figure 4b is a view taken in the direction of arrow b in Figure 4a, and Figure 5 is an intake air silencer. A plan view of the silencer, FIG. 5a is a sectional view taken along line a-C in FIG. 5, FIG. 5b is a sectional view taken along line bb in FIG. 5, and FIG. 5d is a graph showing the vibration spectrum of the upper half of the intake silencer. , Figures 5e and 5f are structural diagrams showing other embodiments of the intake silencer, Figure 5g is a diagram showing the vibration mode of the upper half of the intake silencer, and Figure 6 is a diagram showing the vibration mode of the upper half of the intake silencer. A structural diagram, FIG. 6a is a schematic diagram of FIG. 6, FIG. 7 is a vertical cross-sectional partial view showing the exhaust pipe support structure, and FIGS. 7a and 7b are structural diagrams showing different embodiments. . 10...Water, 12...Liquid tank, 14...Engine,
16... Crankshaft, 17i... Intake silencer, 17
h...Radiator, 20...Tubular exhaust heat exchanger, 22.
...Primary exhaust silencer, 28a...Exhaust pipe, 30.
...Drain muffler, 31c...Flywheel housing, 34...Mounting 7 lunge, 72c...
... Seal member patent applicant Yanmar Diesel Co., Ltd. Agent Patent attorney Tadataka Daigaru '-゛Fig. Figure r＼ Figure 7 Figure 7a

Claims (5)

[Claims] (1) Mounting in which the engine is placed in a liquid tank that stores heat-transfer liquid, a working machine is connected to the engine crankshaft, and the engine body is located below the liquid level and above the liquid level. In a heat exchange device using an engine with a flange attached to the engine, a discharge pipe is provided to discharge condensed water generated in the exhaust passage located below the liquid level to the outside of the liquid tank, and the condensed water and exhaust from the discharge pipe are A plurality of silencing chambers are divided and formed into which the condensed water flows in and exhaust gas is discharged into the stored condensed water, and a connecting pipe is connected to these silencing chambers so that the condensed water and exhaust gas sequentially flow into the silencing chambers. 1. A drain water discharge device for a heat exchange device using an engine, characterized in that a drain water outlet for discharging condensed water is provided in a final stage muffling chamber. (2) A drain water discharge device for a heat exchange device using an engine according to claim 1, wherein the plurality of silencing chambers are vertically stacked and integrally formed. (3) A drain water discharge device for a heat exchange device using an engine according to claim 1, wherein the plurality of silencing chambers are integrally formed adjacent to each other in the horizontal direction. (4) A drain water discharge device for a heat exchange device using an engine according to claim 1, wherein the plurality of silencing chambers are integrally formed concentrically. (5) A drain water discharge device for a heat exchange device using an engine according to claim 1, wherein the plurality of silencing chambers are housed in a liquid tank.