JPS61155650A - Intake silencer of engine for heat exchanger - Google Patents

Abstract

PURPOSE:To prevent vibration sound from being made by a silencer by forming a thin cylindrical shaped intake silencer of a facility with an engine set in liquid tank to used engine exhaust heat, and by arranging dividing, supporters partition the inside, to the parts tend to vibrate. 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 conditioners and others, as well as a cylinder 19a, a cylinder head 19b, an exhaust pipe 20, and a muffler 22 are cooled by water of the liquid tank 12 to acquire warm water. An intake silencer 17i is shaped as a thin cylinder, made up of an upper round board 66a, and a lower round board 66b. An intake port 66e is installed at the upper round board 66a, and an exhaust port 66f at the lower round board 66b. Supporters partitioning the silencer 17i into a plurality of chambers are integrated together with upper and lower mating faces. These dividers are installed to the weakest part of the intake silencer shaped as a thin disk, in order to prevent vibration of the silencer.

Description

Detailed Description of the Invention (Field of Industrial Application) The present invention relates to an intake silencer for an engine for a heat exchange device, more specifically, an engine for driving a working machine is placed in a liquid tank storing a heat transfer liquid. 1. An intake silencer installed in the engine of a heat exchange device that heats liquid with exhaust heat from the engine. :1
31f.

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

Is the applicant responsible for the maintenance and maintenance of this type of heat exchange equipment?
We have developed a prior art to make the lJs, and have already filed an application (Patent Application No. 173801/1982, filing date: 1982).
September 19th).

However, in this prior art, there is a problem in that the intake silencer, which has a relatively wide area and a flat shape, generates vibrations due to intake pulsation, which causes intake U noise.

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 desired to reduce the intake noise from the intake silencer.

(Object of the Invention) An object of the present invention is to provide an intake silencer for an engine for a heat exchange device that can reduce intake noise caused by intake pulsation from an intake silencer in an engine for a heat exchange device.

(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 an engine for a heat exchange device in which the engine is provided with a mounting 7 flange located above the liquid level, the thin cylindrical silencer body communicated with the intake passage of the engine is used. This is an intake silencer for an engine for a heat exchange system, characterized in that a partition plate is installed to divide the inside of the silencer at a portion where the amplitude of vibration due to intake air becomes large, and also serves as reinforcement for the silencer main body.

(2) Function By using the partition plate as a stiffener, vibrations of the muffler body due to intake pulsation, which cause intake noise, are prevented.

(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 head 19b are aligned horizontally. A tubular exhaust heat exchanger 2S20 is provided below the cylinder head t9b, 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 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, it has a vertically long box shape, and the side and rear surfaces of the liquid tank 12 and the hot water tank 15a (FIG. 1) are covered with a cover 178, and above the cover 1Le is a heat radiation 1 !17h is exposed.

Additionally, an intake silencer 17 is provided above the compressor attachment 17.
i is placed, and the intake silencer 171 covers the top of the compressor chamber 117! This is to prevent noise from the 117k from leaking outside. Above the chamber 50 is a ceiling plate 66g.

As shown in FIG. 2, a primary exhaust noise 322 that also serves as a heat exchanger WI4 is provided below the crankcase 18, and the primary exhaust silencer 22 and the pipe exhaust heat exchanger 20 are connected to a connecting pipe. 21b.

A gear case 24 is provided on the lower surface of the crankcase 18, which includes a pipe exhaust heat exchanger 2 OL & bracket 21.
It is fixed to the gear case 24 via G. An oil tank 26 is provided on the lower surface of the gear case 24, and the primary exhaust silencer 22 is attached to an oil tank stay 27a fixed to the oil tank 26. At the bottom of the primary exhaust silencer 22 is a discharge pipe 28 for draining drain water.
One end of a is connected. The other end of the discharge pipe 28a 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 configured to discharge condensed water in the liquid tank 12 to the outside. In addition, the pipe exhaust heat exchanger 2
A discharge pipe 28b is also provided between the drain muffler 30 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 31G that surrounds the flywheel 31a from below and around it is provided at the top of the crankcase 18.

That's it. The flywheel housing 31c and the crankcase 18 have bosses 31d, 3 surrounding the crankshaft 16.
1e, and the bosses 31d and 31e are fixed by bolts 31f in a watertight state.

The generator coil 31G is attached to the bolt 31f on the top surface of the boss 31d.
The flywheel magnet 3 surrounding the power generating coil 31g 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 31i is fixed to the upper surface of the flywheel 31a, and the joint 31i includes: l pump presser 32 (work machine)
The lower ends of vertical input shafts 33a are connected to each other.

The lower surface of the mounting 7 flange 34 is attached in close contact with the upper end of the flywheel housing 31c. The compressor 32 is fitted into the opening of the mounting 7 flange 34 from above in a spigot type manner and bolted to 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.

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

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,
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 oil pipe 37a passing through the water 10, and the lower end of the oil pipe 37a is connected to the gear case 24.

A gear pump (not shown) is built in the gear 11 case 24, and oil is sucked from the oil tank 26 to the VP pump and sent to the oil strainer 36 through the oil pipe 37.
a, and then returns to the gear case 24 via a return pipe (not shown) arranged parallel to the A-Ile pipe 37a, and then returns to the gear case 24 from a communication port (U not shown) to the crankshaft 16.
, the main bearings, and other moving parts, and after passing through them, it is returned to the oil tank 26 again.

The step motor 38 receives a pulse signal from the outside and changes the angular position of the governor lever shaft of the engine 14.
Although not shown, the vertical output shaft of the step motor 38 extends downward toward the engine 14 through a hole in the mounting flange 34, and connects to the crankcase of the governor lever shaft. The lower end of the output shaft of the step motor 38 is connected to the end protruding into the water from the step motor 18 .

As shown in FIG. 1, a vibration-proof connector 46 is interposed between the lower surface of the outer peripheral edge of the mounting 7 flange 34 and the support plate 44, and the vibration-proof connector 46 connects the mounting 7 flange 34 to the support plate 44. It is designed to be held elastically.

For anti-vibration connector No. 46, attach support plate 4 as shown in Figure 2a.
A bolt 47a is fixed to the bolt 47a and passes through the mounting 7 flange 34.A vibration isolating rubber 47b is interposed between the mounting 7 flange 34 and the support plate 44 and installed on the outer periphery of the bolt 47a. It consists of a nut 47G that is tightened to 34. 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 47e has a larger diameter than the nut 47c.

The above vibration-proof connector 46 is attached to the mounting flange 3
They are provided at, for example, eight locations at equal intervals on the outer edge of R8. As shown in FIG.
As shown in y, a packing 47f is interposed, and the structure is such that the packing 47f prevents steam from escaping between the mounting flange 34 and the support plate 44.

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

Compressor 32, oil strainer 36, step motor 9
In the chamber 50 above 381, an intake f4B2S1711 secondary exhaust muffler 37 and a motor 51a are arranged, and the motor 51a is for rotating the cooling fan 51b. Motor 51a1 cold part? The fan 51b is covered with a fan mounting base 51c that forms a fan shroud that improves the circulation of cooling air.

Upper chamber 50, compressor 32, oil strainer 36,
What is a step motor, etc.? Compressor 7 lid 17j, 17k
Compressor 32 and engine 1
The noise from No. 4 does not leak upward.

A radiator 17h is installed so as to surround the side surface of the chamber 50. As shown in Fig. 1c, the radiator 17hG is formed into a substantially annular shape with a part cut out, and the notch part of the radiator 17h is a fan mounting base 51 that recesses the cold JI door 51b.
It is hermetically connected to c. The motor 51a is supported by a stay 51d on a fan mounting stand 51C. An upper front cover 17d is attached to the front side of the fan mounting base 51c. The upper front cover 17d is abutted against the fan mounting base 51C to form spaces 51e and 51j inside, and an upper gap 17h shown in FIG. 1d is provided to facilitate assembly of the upper front cover 176. ing.

The space 51j is continuous with the inner space of the lower front cover 17c (FIG. 1), and noise from the cold N1 water pump 17a, hot water pump 17b, etc. is transmitted to the space 51j.

This noise may leak 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 511 and closely contacts the projection 17f that is integral with the upper front cover 176 is provided between the cooling water pumps 17a and 17j.
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 51e becomes negative and positive with respect to 51j. Therefore, the butterfly valve 51f has a protrusion 17
f due to this negative pressure, and the space 51j and the space 51
e is completely cut off. The bracket 511 is integrated with the fan mounting base 51G.

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 31G, and the engine body consisting of the crankcase 18, cylinder block 19a, and cylinder head 19b is located relatively deep in the liquid tank 12, and the engine body is located in a relatively deep position in the liquid tank 12. 1 that also serves as a heat exchanger
By installing the next exhaust silencer 2s22 in a deep position,
The entire water 10 in the liquid tank 12 is efficiently heated by utilizing the convection phenomenon, and the high-temperature hot water 11b 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 unit. The heat exchange pipe 0 spirally extends near the inner circumferential surface 13c of the liquid tank 12, and a heat medium for an air conditioner flows inside the heat exchange pipe 0 to be heated with 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 0-0 of the liquid tank 12, and the cylinder block 19a and cylinder head 19b are relatively close to the center 0-0. in position.

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

When the engine 14 is eccentrically set as described above, both the cylinder head 19b and the crankcase 18 are sufficiently separated from the inner peripheral surface 13c, and a sufficiently wide gap 13 (j) is formed around the entire circumference of the engine 14. Therefore, the gap 13d
The water 10 does not stay in a part of the gap 13d, and the hot water 11b flows uniformly throughout 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
The bosses 31d of 1c are joined to each other in a watertight state at the annular end faces. Also, &! on the inner periphery of the boss 31e! A cylindrical portion 35a is formed, and the cylindrical portion 35a is fitted into the inner periphery of the boss 31e through a waterproof seal 35b. 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, a joint 41a of the intake pipe 40 is integrally provided with a planar 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 41C and the cylindrical portion 41f. The annular portion /11e is thin, has a curved cross section, and has high flexibility.

As shown in FIG. 2, a large number of radiation fins 19G 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 19G
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 19 (l) is provided inside the cylinder block 19a. The upper and lower ends of the water channel 19d are open.

Therefore, the water 10 in the liquid tank 12 can flow in the vertical direction through the water channel 19d, and this structure also allows the water 10 to be efficiently heated and the cylinder head 19b to be 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 61a into an upper silencing chamber 61C and a lower silencing chamber 61d by a partition 161b, stacking the upper silencing chamber 610 and the lower silencing chamber 6M in the vertical direction, and forming an upper silencing chamber. Inlet pipe 61 in 61C
e. Insert and secure the lower end of 61f, and inlet pipe 61
e, the upper end of 61f protrudes to the outside. The inlet pipe 61e is connected to the discharge pipe 28a, and the inlet pipe 61e is connected to the inlet pipe 61e.
1f is connected to the discharge pipe 28b.

A connecting pipe 1g is provided to allow ventilation through the partition wall 61b, and the welded portions of the partition wall 61b, the main body 61a, and the connecting pipe 1g maintain watertightness. of the lower silencing chamber 61d,
An outlet pipe 61h is provided in the upper part to communicate with the inside, 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 128a and 28b flow into the upper silencing chamber 61c from the inlet pipes 61e and 61f,
Condensed water is stored in the upper muffling chamber 61C, exhaust gas is discharged into the water, and exhaust noise is muffled.

Condensed water and exhaust gas from the upper muffling chamber 61c pass through the connecting pipe 1g to the lower muffling VI9!61d1. : Similarly, condensed water is stored in the lower silencing W61d and the exhaust gas is discharged into the water, further muffling the exhaust noise, and overflowing drain water and exhaust gas are discharged to the outside from the outlet pipe 61h.

Therefore, the exhaust gas from the exhaust pipes 28a and 28b is submerged into the upper silencing chamber 961c and the lower silencing chamber 61d to muffle exhaust noise, and the upper 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 silencing chamber 62a to the second silencing 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 outlet pipe 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;
The secondary exhaust muffler 37 may be housed in the liquid tank 12 and only the drain water outlet pipe may protrude outside the liquid tank 12; an embodiment of the secondary exhaust muffler 37 will be described with reference to FIG. The secondary exhaust muffler 37 includes a main body 64a having a substantially cylindrical shape, and a plurality of muffler chambers 64 that connect the main body 64a to a plurality of muffler chambers 64.
The interval to divide into b, 64c, and 64d! ! 64e, a connecting pipe 4f that communicates the silencing units 64b, 64c, and 64d;
It is composed of etc.

An inlet pipe 64C] is provided to the muffler 64b, and the inlet pipe 64a is connected to the C1st exhaust muffler 22 through a connecting pipe 42 (FIG. 2) provided in the primary exhaust muffler 22.
It is connected to the. There is an outlet pipe 64h in the extinguisher chamber 64d.
is provided, and the outlet pipe 64h is an exhaust pipe 64n (
(Fig. 2).

The connecting pipe 4f extends through the center of the partition wall 64e 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 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, a 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 of the muffler including the exhaust gas vent pipe is
There was a drawback that l was larger than the silencer main body length L2.

The exhaust silencer of the present invention solves the above-mentioned problems, shortens the overall length of the exhaust gas outlet pipes 64a and 64h in the direction perpendicular to the central axis of the silencer as shown in FIG. This is to reduce 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 B17i (Fig. 1)
A strip plate 65a is welded to the stay 65e fixed to the stay 65e. The strip plate 65a is notched at a portion facing the stay 65e, and seven flange 65b are formed at the end. The belt-shaped plate 65a is located at a location where the vibration of the main body 64a is greatest (the axial center of the partition wall 64etFl or the partition W!64).
e 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. is reduced.

In addition, the strip plate 65a has a turnbuckle 65dr and the strip plate 65
Since the center part between the distance 164e in the axial direction of a is tightened, the two points 11J in the first IQ diagram, which also occur in the exhaust pulsation,
The aWl-shaped plate 55a4 and 111 prevent the vibration indicated by I.
The vibration of the main body 64a is further reduced by using a plurality of parts instead of just one part.

Next, a W11 embodiment of the intake silencer 17i will be described with reference to FIGS. 5 and 5a. 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 placed above the compressor chamber 1117. The upper half body 66a1 and the lower half body 66b are made of synthetic resin and have a substantially symmetrical shape.
6dT:Iii combined. An inlet 66e is formed in the upper half body 66a, and clean air from the outside is taken in through the inlet 66e. An intake outlet 66f is formed in the lower half body 66b, and the intake outlet 66f is connected to the intake pipe 40, and an element 66C is housed inside.

Seven flange 66h is formed on the outer peripheral edge of the upper half body 66a 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 bolts of approximately 4 g are connected to the compressor chamber, f! 1
It is set to be fixed at 7k.

Further, as shown in FIG. 5b, the diameter of the intake silencer 17i is set to D.
Then, 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 17i.

A stiffener 67b is fitted around the bolt 67a, and a nut 67c connects the lower half body 66a1 to the lower half body 66b.
, the stiffener 67b is tightened.

In the intake silencer 17i described above, the area is large and vibrations are likely to occur due to intake pulsation.
, tighten the stiffener 67b with bolt 67a1 and nut 67G.
Since the upper half body 66 is tightened together with the
a. Vibration of the lower half body 66b due to intake pulsation is prevented. Moreover, the bolt 67a and the stiffener 67b are caused by the primary and secondary i
Since it is arranged on a circular locus of D/4 from the center of the intake silencer 17i, which is the position where vibration can be most effectively reduced, 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 171 is shown in silencing chambers 68a and 6.
It is divided into 8b and 68G with an interval of V 68 d'c. Connection vias 168e and 68f are provided that penetrate the partition wall 68d.

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 attached at the antinode position of both vibration modes. As a result, the noise U caused by the 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, a gap ff169a that partitions the inside of the flat cylindrical intake silencer 17i into substantially concentric circles;
6'9b, 69c, 69d, and 691Ei are provided, and an opening 69f is formed in each. The first connection passage 70a divided by the partition wall 69a is set to have a length of Ll, and the volume of the first silencing chamber 70b between the partition wall 69a and the partition wall 69b is
1, and 1 is set to be much larger than the volume of the first connection passage 70a.

Separation! The second connection passage 70C between the partition wall 169b and the partition wall 69G is set to have a quality of L2 (Ll>L2). The volume of the second silencing chamber 70d communicating with the second connection passage 70c is V2
(Vl>V2>.Similarly, the length of the third connection passage 70e is L3, and the third silencing!i!70f
The volume of 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 70G, which have different lengths.
, through the third connection passage 70e to the first silencing chamber 70b1 and the second silencing chamber 70b1! ! 70d, flows into the third sound chamber 70f, so
It reduces intake noise of different frequencies in each passage and silencing chamber, and exhibits a silencing 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 opening 69f of the partition wall 69bW of the second and subsequent layers.

In the fourth embodiment described above, the intake sound waves flowing in from the intake port 666 are branched in both left and right directions, pass through paths of different lengths, and gather at the opening 69f, causing interference of the sound waves and producing the effect of a so-called interference type muffler. Because it has both, the effect of reducing intake noise is even greater.

Next, a fifth embodiment of the intake silencer 17i will be described with reference to FIG. 1e. In this embodiment, the intake og device 17i is installed at the top of the heat exchange device and also serves as a rain shield for the heat exchange device.

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 connected through a small-diameter bypass pipe 71b. The bypass pipe 71b passes inside the main pipe 71a.

Such a pipe-type exhaust heat exchanger 320 transfers heat to the surrounding water 10 while the high-temperature exhaust gas discharged from the engine 14 flows through the main pipe 71a, heats the water 10, and cools the exhaust gas. cooled down.

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.
The length of the main pipe 71a short-circuited is 16, and the main pipe 7
When the sound speed in C1 main pipe 71a is f and the frequency of exhaust gas in C1 main pipe 71a, the wavelength λ is λ-c/f (1).

At this time, in order to damp the vibrations of the exhaust gases that merge at the connection point 71c, the n force waves traveling through the main pipe 71a and the force waves passing through the bypass pipe 71b interfere with each other so as to further cancel out the vibrations. Therefore, when F6-15-λ/2 (2), the exhaust noise is reduced.

Therefore, the frequency f1 to be attenuated is f1-c/(2(F6-F5)) (3), and a frequency that is an integral multiple of the frequency f1 has a similar attenuation effect.

To alleviate the resonance phenomenon at the length F7 between the engine 14 and the connection point 71d, the resonance frequency at the length F7 is expressed as Fl-C/(4・F7)... ...3 times, 5 times, 7 times, etc. of equations (4) and (4).

Therefore, by matching the resonance frequency 1=1 and the attenuation frequency f1, the resonance phenomenon at the length F7 can be alleviated.

Similarly, in order to alleviate the resonance phenomenon in the portion of the circle 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 at the length 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 F5 compared to the length F7.
By increasing the length 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 gas 41142 passes through the hole 72a of the support plate 44, and 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 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 tightly contacts the support plate 44. exhaust pipe 42
A threaded portion 43a is formed in the upper portion 43a, and the seal 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 flange 72b, but with this method, the exhaust pipe 42 vibrates due to the exhaust sound of the engine 14, and the The vibration was transmitted to the support plate 44, and the support plate 44 became a vibration source, but the exhaust pipe 42 as shown in FIG.
Support l#! In this structure, vibration transmitted from the exhaust pipe 42 to the support plate 44 is absorbed by the seal member 72c, so the support plate 4
Noise caused by the vibrations in step 4 can be reduced.

Figures 7a and 7b show different embodiments, respectively.
In FIG. 7a, the exhaust pipe 42 is elastically supported on the support plate 44 by spacer rubbers 73a and 73b that are in close contact with the outer peripheral surface of the exhaust pipe 42. In FIG. Figure 7b also shows mounting 7 lunge 3.
A notch 74a is formed in the outer peripheral edge of the support plate 4, 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 exchanger for air conditioning to which the present invention is applied, the exhaust heat from the engine 14 is transferred to the pipe-type exhaust heat exchanger F! As much water as possible is recovered in the water 10 by the A unit 20 and the primary exhaust sonicator 22W.

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 located at the lower part of the chamber 50, the intake noise is also extremely reduced.

Therefore, the noise of outdoor heat exchange equipment for air conditioning, which has recently become a problem as neighborhood noise in residential areas, is 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 intake silencer for an engine for a heat exchange device according to the present invention includes an engine placed in a liquid tank storing a heat transfer liquid, and a working machine attached to the engine crankshaft. In an engine for a heat exchange device in which the engine body is located below the '/II surface and the engine is provided with a mounting flange located above the liquid level, a thin cylindrical tube connected to the intake passage of the engine is used. Install the silencer body
(2) A partition plate (stiffener) that divides the interior of the silencer is provided at a portion of the silencer body where the amplitude of vibration due to intake air increases, and this also serves to reinforce the silencer body, so the following effects can be achieved.

That is, the upper half body 66a and the lower half body 66b, which have a large area and are likely to cause vibration due to intake pulsation, are replaced by the bolts 67a.
, the nut 67c sandwiches the stiffener -67b and is tightened together, so the upper main body 66a and the lower main body 6
Vibration caused by the intake pulsation of the intake air filter 6b can be prevented, and intake noise from the intake silencer 17i, which also serves as the upper cover of the entire device, can be significantly reduced. Moreover, the bolt 67a is primarily caused by the intake pulsation of the upper half body 66a and the lower half body 66b.
Since the secondary tIjx ribs are arranged on the circular locus of D/4 from the position where the secondary tIjx rib can be most effectively reduced, that is, the center of the intake noise silencing 1ls17i, the vibration prevention effect is excellent.

(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 intake heater.

(2) The present invention can also be applied to an exhaust muffler.

[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 view taken from arrow b in Figure 1a, and Figure 1C is a view taken from C- in Figure 1b.
1D is a longitudinal sectional partial view showing a butterfly valve provided in the passage, and FIG. 1E is a view corresponding to arrow b in FIG. Fig. 2 is a partially cutaway enlarged view showing the engine part, Fig. 3 is a longitudinal section showing the first embodiment of the drain muffler, Figs. 3a and 3b are structures showing other embodiments of the drain muffler, respectively. Schematic diagrams, FIGS. 4 and 4C show the primary exhaust silencer. FIG. 4A is a front view of the secondary exhaust silencer, FIG. Figure 5 is a plan view of the intake air temperature N21, Figure 5a is a sectional view taken along line a-C in Figure 5, Figure 5b is a sectional view taken along line bb in Figure 5, and Figure 5d is a vibration of the upper half of the intake silencer. Graphs showing spectra, Figures 5e and 5f are structural diagrams showing other embodiments of the intake silencer, Figure 5Q is a diagram showing the vibration mode of the upper half of the intake silencer, and Figure 6 is a pipe type A schematic diagram of the structure of the heat exchanger, FIG. 6a is a schematic diagram of FIG. 6, FIG. 7 is a longitudinal section 91M showing the support structure of the exhaust pipe, and FIGS. 7a and 7b are structural diagrams each showing different embodiments. It is. 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 Oshiki:: ” ':, +MFigure 2cFigure 3Figure 4cFigure 4bFigure 4T-21b =349-Figure 5c 1 I VI VI Dinner Table - Figure 7b Figure 7 7?L Procedure Amendment 2j (Method) May 15, 1985 To the Director General of the Patent Office Manabu Shiga 1. Indication of the case 1988 Special Permission Request No. 281090 Bow 2, Name of Invention Engine Intake Silencer for Heat Exchange Device 3, Relationship to the Amendment Case Patent Applicant Address 1-32 Chayamachi, Kita-ku, Osaka Name (678) Yanma・-Di-Zel Co., Ltd. Representative Right Representative Director Atsushi Yamaoka 4, Agent Address 10th Floor, East Building, Chiyoda Building, 2-9-4 Higashitenma, Kita-ku, Osaka (Building 530) 5. Date of Amendment Order ( Shipping date) April 30, 1985
Day 6, Ml″′″+7) 74 IQ +lI m1l
1. Amend the "Brief Description of Drawings" column of the specification as stated in F. Note 4: Brief description of the drawings FIG. 1 is a vertical gfT view showing the case where the present invention is applied to an empty pot heat exchanger for air conditioning, FIG. 1a is a view taken in the direction of arrow a in FIG. 1,
Figure 1b is a view taken in the direction of arrow b in Figure 1a, Figure 1C is a sectional view taken along line C-C in Figure 1b, Figure 1d is a vertical ll1i & 1 partial view showing the butterfly valve provided in the passage, and Figure 1e is an intake A view corresponding to arrow b in Fig. 1a in 1J of the fifth embodiment of the silencer, 2nd
The figure is a partially cutaway enlarged view that does not show the engine part, Figure 2a is an enlarged sectional view showing the vibration-proof connector, and Figure 2b is 3 in Figure 2.
Figure 2C is an enlarged cross-sectional view of part 1fI1 showing the joint of the intake pipe, Figure 2d is an enlarged cross-sectional view of the cylinder block without showing the waterway, and Figure 3 shows the first actual example of the drain muffler. The longitudinal cross-sectional view shown, FIG. 3a, and FIG.
The figure is a longitudinal sectional view showing the primary exhaust silencer, Figure 4a is a front view of the secondary exhaust silencer, and Figure 4b is the arrow b in Figure 4a. N cause,
Fig. 5 is a plan view of the intake silencer, and Fig. 5a is a-a of Fig. 5.
Alli side view, Figure 5b is a bb cross-sectional view of Figure 5, Figure 5
Figure d is a graph showing the vibration spectrum of the upper half of the intake silencer, Figures 5c, 5e, and 5r are structural diagrams showing other embodiments of the intake silencer, and Figure 5Q is the vibration spectrum on the upper half of the intake silencer. Figure 6 is a schematic diagram of the structure of the tubular heat exchanger; Figure 6a is a schematic diagram of Figure 6; Figure 7 is a vertical cross-sectional partial diagram showing the support structure of the exhaust pipe; 7a and 7b are structural diagrams without 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, 3o.
...Drain muffler, 31G...I wheel housing, 34...Mounting 7 lunge, 72c...
・More than sealing material

Claims (3)

[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 an engine for a heat exchange device in which a flange is provided on the engine, a thin cylindrical muffler body is provided that communicates with the intake passage of the engine, and the inside of the muffler is located at a portion of the muffler body where the amplitude of vibration due to intake air becomes large. An intake silencer for an engine for a heat exchange device, characterized in that a dividing plate is provided and the silencer body is also reinforced. (2) The heat exchange device according to claim 1, wherein the space within the muffler main body is divided into a plurality of parts, and adjacent divided muffler chambers are communicated with each other by connecting pipes of different lengths. Engine intake silencer. (3) The intake silencer for an engine for a heat exchange device according to claim 1, wherein the silencer main body is arranged to cover an upper part of the heat exchange device and also serves as a rain cover for the heat exchange device.