JPS61155649A - Supporting structure of exhaust pipe of heat exchanger utilizing engine - Google Patents

Abstract

PURPOSE:To eliminate vibration sound to be made at a supporting section by applying supporting boards with a elastic seal to fix a part of the wall with ports where an exhaust pipe projects from a liquid tank of a facility with an engine in its liquid tank to use engine exhaust heat. 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 and others, as well as a cylinder 19a, a cylinder head 19b, an exhaust pipe 20, a muffler 22 are cooled by water in the liquid tank 12 to acquire warm water. After passing through the exhaust pipe 20 and the muffle 22, exhaust penetrates a wall 44 through a pipe 42 to enter an exhaust silencer 37. An elastic seal 72c is inserted into a port 72a of the wall 44 penetrated by a pipe 42, and is pinched vertically by supporting boards 72b, 72f. The upper supporting board 72f is screwed by a screw 43a installed on the outer peripery of the exhaust pipe, and firmly fixes the elastic seal 72. This elastic seal 72c prevents vibrations from a seal in the liquid tank and the exhaust pipe from being transmitted outside.

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 arranged in a liquid tank storing a liquid for a heat transfer, This relates to a support structure for an exhaust pipe in a heat exchanger that heats a liquid using exhaust heat from an engine.

(Prior Art and Problems Therewith) 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 heat exchanged by the engine, and at the same time, it can cool the engine.

The applicant has developed a prior art that makes the maintenance of this type of heat exchange equipment easier and has already filed an application (Patent Application No. 173801, filed in 1982).
(Monday 19th).

However, in such prior art, the exhaust pipe from the engine located below the liquid level is attached to the support plate through seven lunges, and vibrations of the exhaust pipe are transmitted to the entire heat exchange device via the support plate. There is a problem that it causes vibration.

In particular, when the heat exchange device is applied to an outdoor heat exchange device for air conditioning, quietness is strictly required, so it is required to insulate vibrations transmitted from the exhaust pipe from the support plate.

(Object of the Invention) The present invention provides an exhaust pipe of a heat exchange device using an engine that can insulate vibrations from an exhaust passage from a support plate and reduce noise generated from vibrations of the support plate. Its purpose is to provide a supporting structure.

(Structure of the Invention) (1) Technical Means The present invention stores a liquid for heat transfer, arranges an engine in the liquid tank, connects an engine to the crankshaft of the engine, and connects the engine body to the liquid tank. In a heat exchange device using an engine in which the engine is provided with a mounting flange positioned below the liquid level and above the liquid level, exhaust gas is guided from the exhaust passage located below the liquid level above the mounting flange. The exhaust pipe is provided so as to pass through the support plate that supports the mounting flange via the anti-vibration connector, and a sealing member made of an elastic material is provided between the support plate and the exhaust pipe to absorb vibrations of the exhaust pipe from the support plate. This is a support structure for an exhaust pipe of a heat exchange device using an engine, and is characterized by being insulated from the exhaust pipe.

(2) The vibration of the exhaust pipe vibrating due to the working exhaust gas is absorbed by the sealing member, and the vibration of the exhaust pipe is insulated from the support plate.

(Example) In FIG. 1 showing an application of the present invention to an outdoor heat exchange device for air conditioning, for example, an engine 14 is installed in a liquid tank 12 storing water 10 or other heat medium liquid. be. The engine 14 is arranged with the crankshaft 16 perpendicular to the cylinder block 19 relative to the crankcase 18.
a and the cylinder head 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 installed below the liquid tank 12, and a cooling water pump 17a1, a hot water pump 17b, etc. are fixed to the front of the hot water tank 15a and the liquid 1112. 1
70 is a lower front cover, and the lower front cover 17G 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 FIGS. a and 1b, the liquid tank 12 and hot water tank 15a (FIG. 1) have a vertical box shape, and the side and rear surfaces of the liquid tank 12 and hot water tank 15a (FIG. 1) are covered with a cover 178, and above the cover 178 is a radiator. 17h is exposed.

Additionally, an intake silencer 17 is provided above the compressor chamber 117.
i, and the upper surface of the compressor fitting 17 is covered with an intake silencer 171 to prevent noise from the compressor chamber 1117k from leaking to the outside. Above the chamber 50 is a ceiling plate 66o.

As shown in FIG. 2, a primary exhaust quencher [322] which also serves as a heat exchanger is provided below the crankcase 18.
The next exhaust silencing 422 and the pipe exhaust heat exchanger 20 are connected to the connecting pipe 21
connected via b.

A gear V case 24 is provided on the lower surface of the crankcase 18, and a tube type IT aging heat exchanger 20 has a bracket 21c.
It is fixed to the V-case 24 via. An oil tank 26 is provided on the lower surface of the air tank 24, and the primary exhaust quencher 22 is attached to an oil tank stay 27a fixed to the oil tank 26. Primary exhaust silencing 7
! There is a discharge pipe 2 at the bottom of A22 to drain the drain water.
One end of 8a is connected. The other end of the discharge pipe 28a is connected to a drain muffler 30 fixed to the outer surface of the liquid tank 12, which will be described in detail later, and is configured to discharge condensed water in the liquid tank 12 to the outside. Note that a discharge pipe 28b is also provided between the tubular exhaust heat exchanger 20 and the drain muffler 30.

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 the flywheel 31a is provided at the upper part of the crankcase 18. The flywheel housing 31G and the crankcase 18 are provided with bosses 31d and 31e surrounding the crankshaft 16, and the boss 3
1d and 31e are fixed by bolts 31f in a watertight state.

The generating coil 31g is attached to the bolt 31f on the top surface of the boss 31d.
The lower surface of the flywheel 31a has a flywheel magnet 3 surrounding the power generating coil 31g.
1h is A-1. This power generating device consisting of the flywheel magnet 31h and the power generating coil 319 is for charging a starter battery, for example.

A joint 31i 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 311.

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 bent part in the middle, and the upper part is closer to the flywheel housing 31C than the lower part.
;I'm listening.

A boss 31j is formed at the upper end of the flywheel housing 31G below the oil strainer 36,
An oil hole 3 communicating with the oil strainer 36 is provided inside the boss 31j.
1k is perforated. The lower end of the oil hole 31 is connected to the upper end of an A-il pipe 37a passing through the water 10, and the lower end of the oil vibe 37a is connected to the GiV case 24.

A gear pump (not shown) is built in the gear case 24, and oil is sucked into the gear pump from the oil tank 26 and sent to the oil strainer 36 through an oil vibrator 37a.
Afterwards, it returns to the gill case 24 via a return vibrator (not shown) arranged in parallel with the oil vibrator 37a, and is then pumped through a communication port (not shown) to the crankshaft 16,
The oil is fed under pressure to the main bearing and its basin moving parts, and after lubricating them, returns 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, and is not shown in the figure. [The straight output shaft of the step motor 38 extends downward toward the engine 14 through a hole in the mounting flange 34,
At the end of the governor lever shaft that protrudes into the water from the crankcase 18.

The lower end of the output shaft of the step motor 38 is connected.

As shown in FIG. 1, a vibration-proof connector 46 is interposed between the lower surface of the outer peripheral edge of the mounting flange 34 and the support plate 44, and the vibration-proof connector 46 connects the mounting flange 34 to the support plate 44 elastically. It is designed to be held at

The anti-vibration connector 46 is attached to the support plate 44 as shown in FIG. 2a.
Is it fixed to and mounting flange? 34, a vibration-proof rubber 47b interposed between the mounting flange 34 and the support plate 44 and numbered on the outer periphery of the pole 1-4711, and a nut 47c for tightening the bolt/17a to the mounting flange 34. has been done. The upper end of the bolt 47a extends upward through a through hole 47e of a stay 476 fixed to the support plate 44 by, for example, welding, and the through hole 47e has a larger diameter than the nut 47G.

The above vibration-proof connector 46 is attached to the mounting flange 3
For example, 5QGJ at 8 locations at equal intervals on the outer periphery of 4.
It is being As shown in FIG. 1, a packing 47f is interposed between the mounting flange 34 and the support plate 44, which are further inward from the vibration-proof connector 46. It has a structure that prevents steam from escaping.

The support plate 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.

In the chamber 50 above the compressor 32, oil strainer 36, step motor 38, etc., an intake silencer 171, a secondary exhaust silencer 37, and a t-tube 51a are arranged.
1a is for rotationally driving the cooling fan 2b 51b. The motor 51a1 and the cooling fan 51b are mounted on a fan mounting base 5 that forms a fan shroud that distributes the cooling air in nine directions.
Covered by 1c.

Upper chamber 50, compressor 32, oil strainer 36,
Step motor etc. are compressor mating 17j, 17k
Compressor 2 and engine 1
This prevents the JJ sound from 4 from leaking to the E direction.

A radiator 17h is provided so as to surround the side surface of the chamber 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 connected in an airtight manner to the fan mounting base 5ic surrounding the cooling fan 51b. . The motor 51a is supported by a fan mount 51c by a stay 51d. Fan mounting base 5
An upper front cover 176 is provided with a mounting number on 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, and 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 170 (FIG. 1), and noise from the cooling water pump 17a, the heat pump 17b, etc. is transmitted to the space 51j. There is a possibility that this noise may leak from the space 51e to the outside through the gap 1!151h.

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 511 and in close contact with a protrusion 17f that is integral with the upper front cover 176 is provided between the cooling water pumps 17a1 and 17a1.
Noise from the feed pump 17b etc. is blocked. Space part 51
e is above through the gap 51h! ! 50, and when the fan 51a is operated, the space 51e becomes a negative pressure with respect to the space 51j. Therefore, the butterfly valve 51f has a protrusion 1
7f due to this negative pressure, and the space 51j and the space 5
1e 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 height as the vicinity of 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 knob 19a, and cylinder head 19b is located at a relatively deep position in the liquid tank 12, and is a pipe type engine. By installing the exhaust heat exchanger 20 and the primary exhaust silencer 22 that also serves as a heat exchanger at a deep position, the entire water 10 in the liquid tank 12 is efficiently heated using convection phenomenon, and the liquid tank 12 The high temperature hot water 11b is always collected in the upper half of the tank.

In order to use this hot water 11b as a heat source, the liquid tank 1
A heat exchange vibro 0 is arranged in the upper half of the 2.

The heat exchange vibro 0 extends spirally near the inner circumferential surface 13G of the liquid tank 12, and is configured to flow a heat medium for an air conditioner inside the heat exchange vibro 0 and heat it with dry water 11b. In addition, in order to efficiently heat the heat exchanger vibro 0 over its entire length, the crankshaft 16 is located at the center of the liquid W112.
It is eccentric with respect to O, and the cylinder block 19a and cylinder head 19b are located relatively close to the center O-O.

Furthermore, a spacer rubber 60a is interposed between the heat exchange vibro 0 and the inner circumferential surface 13C, and the spacer rubber 60a
The heat exchanger vibro 0 is elastically supported. The spacer rubber 60a is arranged at two diagonally adjacent locations.

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 gap 13d of sufficient width is formed around the engine 14. Therefore, the water 10 does not accumulate in a part of the gap 13d, and the wet water 11b flows uniformly throughout the gap 13d, so that the heat exchange vibro 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
The bosses 31d of 1C are joined to each other in a watertight state at the annular end faces. Also, the μ cylindrical portion 3 is provided on the inner circumference of the boss 31e.
5a is formed, and the cylindrical portion 35a is fitted into the inner periphery of the boss 31e via a waterproof seal 35b in a locking type manner.

An oil seal 15c is provided between the upper inner periphery of the boss 31d and the crankshaft 16. Furthermore, a bearing 15b is provided between the upper inner periphery of the boss 31d and the crankshaft 16.

As shown in FIG. 2C, the joint 41a of the intake pipe 40 is integrally provided with a cylindrical &S/11b extending upward around the intake @40. A rubber seal 41G is attached to the outer peripheral surface of the intake pipe 40.
The cylindrical portion 41d of is in close contact. The cylindrical portion 41d is integrally molded with the annular portion 41e and the cylindrical portion 41f. The annular portion 410 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 19dta 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 vertically 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 is formed by dividing a substantially cylindrical main body 618 into an upper silencing chamber 61c and a lower silencing chamber 61d by a partition wall 61b, stacking the upper silencing chamber 61c and the lower silencing chamber 61d in the vertical direction, and forming an upper silencing chamber 161C. Entrance vibrator 6 inside
Insert and secure the lower ends of 1e and 61f, and inlet vibrator 6
The upper ends of 1e and 61f protrude to the outside. The inlet pipe 161G is connected to the discharge pipe 28a, and the inlet pipe 161G is connected to the inlet pipe 161G.
61f is a pipe to which the discharge pipe 28b is connected.

A connecting vibro 1Q is provided that penetrates the partition wall 61b, and the welded portions of the partition wall 61b, the main body 61a, and the connecting vibro 161g maintain watertightness. (2) An outlet vibrator 61h is provided at the upper part of the silencing chamber 61d so as to communicate with the inside, and drain water is discharged to the outside from the outlet vibrator 61h.

In the first embodiment described above, the mixed condensed water and exhaust gas discharged through the dry mountain pipes 128a and 28b flow into the upper silencing chamber 61c from the inlet vibes 61e and 61f,
Condensed water is stored in the upper muffling chamber 61C and the exhaust gas is discharged into the water to muffle the R air noise 8.

Condensed water and exhaust gas from the upper silencing chamber 61c pass through the connecting vibro 1g to the lower silencing chamber 61d1. : flows in, condensed water is similarly stored in the lower silencing chamber 61d, exhaust gas is discharged into the water, and -J! ! In addition to muffling the air noise, overflowing drain water and exhaust gas are discharged from the outlet vibrator 61h to the outside.

Therefore, the exhaust gas from the exhaust vibrator 28a and the exhaust vibrator 28b is submerged into the upper silencing chamber 61'C and the F section silencing chamber 61d to muffle the exhaust noise, and the upper silencing chamber 61G
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 adjacent to each other, and condensation is condensed from the first silencing chamber 62a to the second silencing chamber 62b by a connecting vibro 2c. This structure allows water and exhaust gas to circulate.

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 condensation is condensed from the first silencing chamber 63a to the second silencing chamber 63b by a connecting pipe 163G. It has a structure in which water and exhaust gas are circulated and discharged to the outside from the exit vibe 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 vibrator may be housed inside the liquid W112 and only the drain water outlet vibrator may be made to protrude outside the liquid W112.

An embodiment of the secondary exhaust muffler 37 will be described with reference to FIG. The secondary exhaust silencer 337 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 vibro 4f that communicates with the 4d.

An inlet vibrator 6/IQ is installed in the muffling chamber 64b. The exit vibrator 64t' is connected to the silencing chamber 64d.
l Provided with an exit! Vibro 4h has exhaust pipe 64n
(Fig. 2).

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

The connecting vibro 4f and the side plate 64i 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 640 as shown in FIG. 4C. In this method, the vibration of the side plate 640 is reduced, but the silencer length L including the gate gas outlet pipe is
There was a drawback that l was larger than the length L2 of the silencer body.

The exhaust silencer of the present invention solves the above-mentioned problems, shortens the overall length of the exhaust gas outlet pipe 649.64h in the direction perpendicular to the central axis of the silencer by 1' as shown in Fig. 4, and
This is to reduce noise caused by the fi movement of the side plate 641.

The installation structure of the secondary exhaust silencer 37 will be explained with reference to FIGS. 4a and 4b. The intake silencer 171 (Fig. 1)
A strip plate 65a is welded to the stay 65e fixed to the stay 65e. The strip plate 65a is cut out at the portion facing the stay 65e, and seven flange 65b is formed at the end. , the belt-shaped plate 65a is located at the point where the vibration of the main body 64a is greatest (the axial center between the partitions W!64e or the partition wall 64).
e and the axial center of the side plate 641@).

Bolts 65G passing through the flange 65b are provided, 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 vibration shown by the two-dot chain line in FIG. 4 of i is prevented by the side plate 64i and the connecting vibro 4f being fixed to the bolts 64, and the noise generated from the main body of the secondary exhaust silencer 37 is reduced. be done.

Further, the belt-shaped plate 65a is attached to the turnbuckle 65d.
Distance in the axial direction of a! 164e, the vibration shown by the two-dot chain line in FIG. 4a due to exhaust pulsation is also prevented. Vibration of the main body 64a is further reduced by using a plurality of belt-like plates 65a instead of just one.

Next, a first embodiment of the intake silencer 17i is shown in FIGS.
Explanation will be given with reference to figure a. The intake silencer 171 is composed of an upper half body 66a, a lower half body 66b, an element 66c, etc., and has a flat cylindrical shape that is placed on the compressor cross section 11u17. The upper half body 66a1 and the lower half body 66b are made of synthetic resin and have a substantially symmetrical shape.
It is abutted at 6d. An inlet 66 is provided in the upper half body 66a.
e is formed, and clean air from the outside is sucked in through the suction port 66e. An intake outlet 66f is formed in the lower half body 66b, and the intake outlet 66f is connected to the intake pipe 4.
0, and an element 66c is housed inside.

A flange 66h is formed on the outer peripheral edge of the upper half body 66a1 and the lower half body 66b, and a bolt (
(not shown) to fix the upper half main body 66a and the lower half main body 66b, and approximately four bolts are attached to the compressor 17k.
It is designed to be fixed to

Further, as shown in FIG. 5b, the diameter of the intake silencer 171 is set to D.
Then, for example, ports t・67a are located at three locations on a circular locus of D/4 from the center of the intake silencer 171.
It is installed through 1.

A stiffener 67b is fitted around the bolt 67a, and a nut 67c holds the lower half body 66a and the lower half body 66b.
, Stiffener 67b@tightened.

In the intake silencer 17i described above, the area is large and vibrations are likely to occur due to intake pulsation.
, bolt 67a, tt drawer c and stiffener 67b.
Since the upper half body 66 is tightened together with the
Vibration of the a1 lower half body 66b due to intake pulsation is prevented. Moreover, the bolt 67a and stiffener 67b are primary and secondary due to the intake pulsation of the upper half body 66a5 and the lower half body 66b!
Since it is arranged on a circular locus of D/4 from the center of the intake silencer 17i, the vibration prevention effect is excellent.

FIG. 5C shows a second embodiment of the intake silencer 17i. In FIG. 5C, the interior of the intake silencer 17i is a silencing chamber 68a16.
The partition wall 68d1' is divided into 8b and 68c. Partition wall 68
Connecting vibrators 8e and 68f passing through d are provided.

In this embodiment, as shown in Fig. 5d and Fig. 5Q, for the vibration modes ■ and ■ at frequencies ν1 and ν2 of the conventional vibration spectrum characteristic 67x, a partition wall is provided at the antinode position of both vibration modes. As a result, noise caused by vibration of the intake silencer 17i is significantly reduced.

Further, a third embodiment of the intake silencer 171 will be described with reference to FIG. 5e. In this embodiment, partition walls 69a and 69 partition the inside of the flat cylindrical intake silencer 17i into substantially concentric circles.
b, 69c, 169d, and 69e are provided4), and an opening 69 is provided in each.
f. The first connection passage 708 divided by the partition wall 69a is set to have a length of 1, and the volume of the first silencing passage 70b between the partition wall 69a and the partition wall 69b is set to vl, where vl is the first connection passage. It is set to be much larger than the volume of 70a.

The second connection passage 70C between the partition wall 69b and the partition v69c is L.
The length is set to 2 (Ll>12). The volume of the second muffler 770d communicating with the second connection passage 70G is V2
(Vl>V2). Similarly, the length of the third connection passage 70e is 1L3r, and the third connection passage 70f has a length of 1L3r.
i! The F product is set to v3.

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.
1 through the third connection passage 70e, the first W4 sound 170b,
Since it flows into the second muffler palm 70d1 and the third muffler 70f,
Each passage and silencing tape reduce intake noise of different frequencies, demonstrating a silencing effect over the entire frequency range of intake noise.
Ru.

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. are set to different lengths of in. The same applies to the surrounding openings 69'' of the second and subsequent partition walls 69b.

In the fourth embodiment described above, the intake sound waves that flowed in from the intake port 66e are branched in both left and right directions, pass through passages of different lengths, and come together at 4 days 69f, resulting in sound wave interference and an effect as a so-called interference type muffler. Since it also has the following properties, the effect of reducing intake noise is even greater.

Next, a fifth embodiment of the intake silencer 3171 will be described with reference to FIG. 1e. In this embodiment, the intake air muffler 17i is installed at the top of the heat exchanger and also serves as the top of the heat exchanger.

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 71a, and has a structure in which both ends of the main pipe 71a are communicated through a small-diameter bypass @71b. The bypass pipe 71b passes inside the main pipe 71a.

Such a tubular exhaust heat exchanger 20 connects the engine 14 to the
While the high temperature exhaust gas discharged from 71 flows through the main pipe 71a, heat is transferred to the surrounding water 10, thereby heating the water 10 and cooling the exhaust gas.

Therefore, the thermal energy in the exhaust gas that is completely discarded from the engine 14 is recovered into the water 10.

Fig. 6a is a diagram of the tubular exhaust heat exchanger 2i120 made into a model, with the length of the bypass pipe 71b being F5, and the length of the bypass pipe 7
The main pipe 71a17) short-circuited at 1b has a quality of 16,
If the sound velocity in the main pipe 71a is C1, and the frequency of the exhaust gas in the l-pipe 71a is r, then the relationship of wave [(λ is λ-C/f) (1) holds true.

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. F5-λ/2 (2) Exhaust noise is reduced.

Therefore, the frequency f1 to be attenuated is fl-c/(2([6-15))...(3),
There is a similar attenuation effect at frequencies that are integral multiples of the frequency f1.

In order to alleviate the resonance phenomenon at the length F7 between the engine 14 and the connection point 71d, if the resonance frequency at the length F7 is Fl, then Fl-c/(4.7)... ...(4) and 3 times, 5 times, 7 times, etc. of equation (4).

Therefore, by matching the resonance frequency F1 and the attenuation frequency f1, the resonance phenomenon in the area 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 71c, 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 area F8 can be alleviated.

Note that when the bypass pipe 71b has a small diameter, there is an advantage that most of the exhaust gas flows through the main pipe 71a, increasing the amount of heat energy recovered. Also, the bypass pipe 71b is made to have the same diameter as the main pipe 71a, and the length is 55 compared to the length F7.
By changing the design and the design F6, the tubular heat exchanger 20
The total length of the piping becomes longer, and the amount of heat energy recovered can be increased without increasing the pressure inside the main piping for 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 7 flange 72b is fixed to the outer periphery of the exhaust pipe 42 by, for example, welding. A seal portion 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 portion 43a, and the sealing member 72c is tightened by the upper 7 flange 72f which is screwed into the threaded portion 43a.

Conventionally, the exhaust pipe 42 was directly attached to the support plate 44 with bolts or the like via the 7 langes 72b, 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 via the 7 langes 72b to It is transmitted to the support plate 44, and the support plate 44 @
The exhaust pipe 42, as shown in Fig. 7, was a source of vibration.
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 bone support the exhaust pipe 42 on the support plate 44. Also, FIG. 7b shows the mounting flange 34.
A notch 74a is formed in the outer peripheral edge of the support plate 44, and the exhaust pipe 42 is elastically supported by a spacer rubber 74b that is fitted into the notch 74a from the outside of the support plate 44.

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.
．． The primary exhaust silencer 22 or the like collects as much water as possible to 1°.

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, and then 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, the intake noise is muffled by the intake silencer 17i located at the bottom of the chamber 50, so the intake A! & will also be extremely small.

Therefore, the noise caused by outdoor heat exchangers for air conditioning, which has recently become a problem as neighborhood noise in residential areas, etc., can be significantly reduced, and the exhaust air and intake air are separated so that clean air is taken in as the intake air.

(Effects of the Invention) As explained above, in the support structure of the exhaust pipe of the heat exchange device using the engine according to the present invention, the engine is disposed in the liquid tank storing the liquid for heat transfer, and the exhaust pipe is attached to the crankshaft of the engine. 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 provided with a mounting flange located above the liquid level, from the exhaust passage located below the liquid level. An exhaust pipe that guides exhaust air above the mounting flange is provided by penetrating the support plate that supports the mounting flange via a vibration-proof connector, and a seal member made of an elastic material is installed between the support plate and the exhaust pipe. Since the vibration of the exhaust pipe is insulated from the support plate, the following effects can be achieved.

? However, the exhaust pipe 42 is connected to the flange 72b as before.
The seal member 72c can absorb vibrations transmitted from the exhaust gas @42 to the support plate 44, compared to the case where the support plate 44 is directly attached to the support plate with bolts or the like. Therefore, the vibration of the support plate 44 is eliminated, and the noise caused by this i-motion can be reduced.

(Another Embodiment) (1) The present invention is not limited to being applied to an outdoor heat exchange device for air conditioning, but can also be applied to an engine exhaust pipe.

[Brief explanation of the drawing]

FIG. 1 is a longitudinal sectional view showing the case where the present invention is applied to an outdoor heat exchange device for air conditioning, FIG.
Figure b is a cross-sectional view of Figure 1a, and Figure 1C is a view of C- in Figure 1b.
1D is a vertical sectional view without showing the butterfly valve provided in the passage, FIG. 1E is a view corresponding to arrow B of FIG. 1A in the fifth embodiment of the intake silencer, and FIG. FIG. 3 is a longitudinal sectional view showing a first embodiment of the drain muffler, and FIGS. 3a and 3b each show another embodiment of the drain muffler. iSchematic diagram,
Figures 4 and 4C are longitudinal cross-sectional views showing the primary exhaust silencer, Figure 4a is a front view of the secondary exhaust silencer, Figure 4b is a view taken from arrow b in Figure 4a, and Figure 5G. , Plan view of L intake silencer, No. 5a
The figure is a cross-sectional view taken along line a''-a in Figure 5, and figure 5b is a cross-sectional view taken along line b--in Figure 5.
Figures 5e and 5f are graphs showing the vibration spectrum of the upper half of the intake silencer, respectively.
Figure 5g is a diagram showing the vibration mode of the upper half of the intake silencer; Figure 6 is a diagram showing the structure of a tubular heat exchanger; Figure 6a is a diagram showing the vibration mode of the upper half of the intake silencer; FIG. 7 is a partial longitudinal cross-sectional view showing a support structure for an exhaust pipe, and FIGS. 7a and 7b are structural diagrams showing different embodiments, respectively. 10・
...Water, 12...Liquid tank, 14...Engine, 16.
... Crankshaft, 17i... Intake worn out n, 17h...
・Radiator, 20...tubular exhaust heat exchanger, 22...1
Next exhaust silencer, 28a...Kareyama vibe, 30...Drain muffler, 31c...Flywheel housing, 34...Mounting flange, 72c...Sealing member Patent applicant Yanmar Diesel Co., Ltd. agent Patent attorney 1]"';□°15°Figure 26Figure 3Figure 4cFigure 4bFigure 4 To-21bFigure 4a 66f Vt l/2 Enrenshiki-Figure 7bFigure 7Figure 7 (Figure 1 Procedural Amendment S (Method) 1. Indication of Case 1981 Patent Application No. 281089 2, Title of Invention Support for Exhaust Pipe of Heat Exchange Device Using Engine tI8 Construction 3, Person Making Amendment Case and Relationship Patent applicant address: 1-32 Chayamachi, Kita-ku, Osaka Name (678) No. 9 No. 4 Chiyoda Building East Building 101!!i (No. 530) 5, Date of amendment order (
Shipping date) April 3081, 1985, the (Brief explanation of the drawings) column of the specification store is corrected as shown in 1+1J below. 1i1 top view showing the case where it is applied to a replacement device, Fig. 1a.
Figure 1d is a partial longitudinal cross-sectional view of the butterfly valve installed in the passage, and Figure 1e is a cross-sectional view taken along the line C-C of Figure 1a, showing the fifth embodiment of the intake silencer. Fig. 2 is a partially cutaway enlarged view of the engine, Fig. 2a is an enlarged sectional view of the anti-vibration connector, Fig. 2b is an enlarged partial view of the main part of Fig. 2, Fig. 2C The figure is an enlarged cross-sectional view of the intake pipe, Figure 2d is an enlarged cross-sectional view showing the water passage of the cylinder block, Figure 3 is a vertical cross-sectional view of the first embodiment of the drain muffler, Figures 3a and 3b are Figure 3b is a structural schematic diagram showing another embodiment of the large drain muffler, Figures 4 and 4C are I sectional views showing the primary exhaust silencer, and Figure 4a is a front view of the secondary exhaust silencer.
Fig. 4b (see arrow b in Fig. 4a, Fig. 5 is a plan view of the air intake and sleeper, Fig. 5a is a sectional view taken along line a-C in Fig. 5, Fig. 5b is
The figure is a sectional view taken along line b-b in Figure 5, Figure I'I5d is a graph showing the vibration spectrum of the upper half of the intake silencer, and Figures 5C, 5e, and 5f are different implementations of the intake silencer. A schematic structural diagram showing an example, Figure 5g is a diagram that does not show the vibration mode of the upper half of the intake silencer, and Figure 6 is a schematic diagram of the IM structure of a tubular heat exchanger.
The figure is a schematic diagram of FIG. 6, the seventh factor is a longitudinal cross-sectional partial view showing the support structure of the male trachea, and FIGS. 7a and 7b are structural diagrams each not 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 vibe, 30.
...Drain muffler, 31c...Flywheel housing, 34...Mounting flange, 72G...
・More than sealing material

Claims (4)

[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, an exhaust pipe that guides exhaust air above the mounting flange from an exhaust passage placed below the liquid level is supported by the mounting flange via a vibration-proof connector. A heat exchange device using an engine, characterized in that a support plate is provided through the support plate, and a sealing member made of an elastic material is provided between the support plate and the exhaust pipe to insulate vibrations of the exhaust pipe from the support plate. Exhaust pipe support structure. (2) The support structure for an exhaust pipe of a heat exchange device using an engine according to claim 1, wherein the sealing member is fixed to the exhaust pipe by a flange. (3) The support structure for an exhaust pipe of a heat exchange device using an engine according to claim 1, wherein the sealing member is a spacer made of an elastic material. (4) A support structure for an exhaust pipe of a heat exchange device using an engine according to claim 1, wherein a notch is formed in the outer peripheral edge of the support plate, and a sealing member is attached to the notch.