JP2018128152A - Condenser - Google Patents

Abstract

PROBLEM TO BE SOLVED: To suppress noise in a condenser including a guide unit for guiding a refrigerant introduced from the outside and a heat exchange unit for introducing a refrigerant via the guide unit. SOLUTION: A guide unit 25, 27, 28 for guiding a refrigerant introduced from the outside and a heat exchange unit 19 for introducing the refrigerant via the guide unit are provided, and the guide unit is provided with a flow of the refrigerant. Provided is a condenser 3 having perforated plates 25 and 33 having facing surfaces and having a plurality of holes formed therein, and spaces R1 and R2 partitioned on the back surface side of the perforated plates 25 and 33. [Selection diagram] Fig. 4

Description

  The present invention relates to a condenser.

  The refrigerator is a heat source device that is widely used in applications such as factory air conditioning having a clean room such as an electrical and electronic related factory, and district heating and cooling. As a refrigerator, a unit is known in which constituent devices such as a centrifugal compressor, a condenser, and an evaporator are arranged in the vicinity to be integrated (see, for example, Patent Document 1).

JP 2002-327700 A

  As the efficiency of refrigerators increases, the increase in noise generated from refrigerators has become an issue. The causes of noise generated from the refrigerator are roughly classified into two types: noise caused by mechanical causes and noise caused by fluid causes.

Noise due to mechanical incentives is due to periodic fluctuations in flow rate caused by the movement of blades, the number of wings of the diffuser, etc., generated when a centrifugal compressor or a pump operates. This periodic flow rate fluctuation causes pressure pulsation, which generates noise called NZ sound.
It is known that noise generated by mechanical incentives has a characteristic and single frequency characteristic and resonates with acoustic eigenvalues such as piping inside the refrigerator to amplify the sound.

  The present invention provides a condenser capable of suppressing noise in a condenser including a guide unit that guides a refrigerant introduced from the outside and a heat exchange unit that introduces the refrigerant via the guide unit. The purpose is to do.

  According to a first aspect of the present invention, the condenser includes a guide part that guides a refrigerant introduced from the outside, and a heat exchange part into which the refrigerant is introduced via the guide part, The guide portion includes a perforated plate having a surface facing the flow of the refrigerant and having a plurality of holes formed therein, and a space defined on the back side of the perforated plate.

  According to such a configuration, noise generated in the guide unit can be reduced. That is, the excitation force can be reduced before the noise generated from the condenser reaches the resonance space provided in the subsequent stage of the condenser.

  In the condenser, the heat exchange section is a plurality of heat transfer tubes extending in a direction intersecting with the flow direction of the refrigerant, and the perforated plate moves toward the downstream side in the flow direction of the refrigerant. A first slope inclined so as to approach one end of the heat tube and an upstream end connected to the upstream end of the first slope, and the other of the heat transfer tube as it goes downstream in the flow direction of the refrigerant. And a second slope inclined so as to approach the end.

  According to such a configuration, noise can be absorbed while the refrigerant is dispersed on the heat transfer tube side.

  In the condenser, the perforated plate may include a baffle plate that is connected to the downstream side in the flow direction of the refrigerant on the first slope and the second slope and extends in the longitudinal direction of the heat transfer tube.

  According to such a structure, the back surface of a baffle plate can be utilized for noise reduction.

  According to the present invention, it is possible to reduce noise generated in the guide unit. That is, the excitation force can be reduced before the noise generated from the condenser reaches the resonance space provided in the subsequent stage of the condenser.

It is a schematic block diagram of the refrigerator of embodiment of this invention. It is sectional drawing of the condenser of embodiment of this invention. It is detail drawing of the guide part of the condenser of embodiment of this invention. FIG. 4 is a side view of the guide portion of the condenser according to the embodiment of the present invention, as viewed from the direction of the arrow IV in FIG. 3. It is sectional drawing of the downstream baffle plate of the condenser of embodiment of this invention.

Hereinafter, a refrigerator 1 according to an embodiment of the present invention will be described in detail with reference to the drawings.
As shown in FIG. 1, the refrigerator 1 of the present embodiment includes a compressor 2 that compresses a refrigerant W, a condenser 3 that condenses the refrigerant W compressed by the compressor 2 with cooling water, and a condenser 3. A first expansion valve 4 that is an expander that depressurizes the refrigerant W, and an economizer 6 (gas-liquid separator) that separates the refrigerant W from the first expansion valve 4 into a gas-liquid two-phase.

  The refrigerator 1 also includes an inflow path 8 that allows the gas phase W1 from the economizer 6 to flow into the compressor 2, a second expansion valve 5 that depressurizes the liquid phase from the economizer 6, and a second expansion. And an evaporator 7 for evaporating the refrigerant W from the valve 5.

  A hot gas bypass pipe 9 is provided between the vapor phase portion of the condenser 3 and the vapor phase portion of the evaporator 7. The hot gas bypass pipe 9 is provided with a hot gas bypass valve 10 for controlling the flow rate of the high-temperature refrigerant gas flowing through the hot gas bypass pipe 9.

The refrigerator 1 has a refrigeration cycle 11 having a pipe 12 that sequentially connects a compressor 2, a condenser 3, a first expansion valve 4, a second expansion valve 5, and an evaporator 7. Specifically, a pipe 12a that connects the compressor 2 and the condenser 3, a pipe 12b that connects the condenser 3 and the economizer 6, a pipe 12c that connects the economizer 6 and the evaporator 7, and an evaporator 7 and a pipe 12d for connecting the compressor 2 to each other.
As the refrigerant W, for example, alternative fluorocarbon R134a (hydrofluorocarbon) is used.

The compressor 2 is a centrifugal two-stage compressor, and is driven by an electric motor (not shown) whose rotational speed is controlled by an inverter that changes an input frequency from a power source.
The condenser 3 is a device that cools the refrigerant W compressed by the compressor 2 by heat exchange with cooling water or the like, and changes the state to a liquid state. For example, the condenser 3 is a shell and tube heat exchanger.

The first expansion valve 4 adiabatically expands and depressurizes the liquid refrigerant W from the condenser 3 to evaporate part of the liquid, thereby bringing the refrigerant W into a gas-liquid two-phase state.
The economizer 6 is a device that separates the refrigerant W, which is in a gas-liquid two-phase state in the first expansion valve 4, into a gas phase W1 and a liquid phase.

The inflow path 8 is a device that causes the gas phase W1 separated from the gas-liquid two-phase refrigerant W by the economizer 6 to flow into the compressor 2.
Similar to the first expansion valve 4, the second expansion valve 5 adiabatically expands and depressurizes the refrigerant W that is separated only by the economizer 6 and becomes only the liquid phase. In addition, in the refrigerator 1 of this embodiment, it is set as the structure which decompresses the refrigerant | coolant W using an expansion valve, However, It is not restricted to this, You may decompress the refrigerant | coolant W using another means.
The evaporator 7 evaporates the refrigerant W from the second expansion valve 5 by exchanging heat with water or the like to obtain a saturated vapor state.

Next, the detailed structure of the condenser 3 of this embodiment is demonstrated.
As shown in FIG. 2, the condenser 3 of the present embodiment includes a bottomed cylindrical casing 14, a first tube plate 15 and a second tube plate 16 provided inside the casing 14, and a refrigerant W. 14, an introduction pipe 12 a that is introduced into the interior of the pipe 14, a discharge pipe 12 b that discharges the refrigerant W to the outside of the casing 14, a plurality of heat transfer tubes 19 (heat exchange portions) into which cooling water is introduced, and the outside. A plurality of upstream rectifying plates 27, downstream rectifying plates 28, and baffle plates 25 (baffle plates), which are guide portions for guiding the refrigerant W, are provided. The refrigerant W is introduced into the heat transfer tube 19 through the upstream rectifying plate 27, the downstream rectifying plate 28, and the baffle plate 25 which are guide portions.

  The casing 14 includes a cylindrical casing body 22 and a pair of lid portions 23 provided at one end and the other end in the longitudinal direction L of the casing body 22. The first tube sheet 15 is a plate-like member provided on one end side of the casing 14. The main surface of the first tube sheet 15 is parallel to the main surface of the lid portion 23. The space on the one end side of the first tube sheet 15 is a first header inner space S1.

The second tube sheet 16 is a plate-like member provided on the other end side of the casing 14. The main surface of the second tube sheet 16 is parallel to the main surface of the lid portion 23. The space on the other end side than the second tube sheet 16 is a second header inner space S2.
The first tube plate 15 and the second tube plate 16 are formed with a plurality of through holes 24 through which the heat transfer tubes 19 are inserted. A space surrounded by the casing 14, the first tube plate 15, and the second tube plate 16 is a casing internal space S3.

  The plurality of heat transfer tubes 19 extend in the longitudinal direction L of the casing 14 in the casing inner space S3. The plurality of heat transfer tubes 19 are positioned at predetermined positions by being inserted into the plurality of through holes 24 formed in the first tube plate 15 and the second tube plate 16.

  The introduction pipe 12a is a pipe for introducing the refrigerant W into the casing inner space S3. The introduction pipe 12 a is formed at the approximate center in the longitudinal direction L of the casing 14. The central axis of the introduction pipe 12 a is substantially orthogonal to the central axis A of the casing 14. That is, the flow direction of the refrigerant W introduced into the casing inner space S <b> 3 via the introduction pipe 12 a is substantially orthogonal to the extending direction of the heat transfer tube 19.

  The discharge pipe 12b is a pipe 12 for discharging the refrigerant W from the casing inner space S3. The discharge pipe 12b is formed at the approximate center in the longitudinal direction L of the casing 14 and on the opposite side of the introduction pipe 12a. The central axis of the discharge pipe 12 b is substantially orthogonal to the central axis A of the casing 14.

  The baffle plate 25 is a guide portion that uniformly distributes the introduced refrigerant W into the condenser 3 body. The upstream rectifying plate 27 and the downstream rectifying plate 28 are guide portions that rectify the introduced refrigerant W and the refrigerant W that has collided with the baffle plate 25.

  As shown in FIG. 3, the baffle plate 25 is a plate-like member, and is provided at a position where the refrigerant W introduced from the introduction pipe 12a collides. The baffle plate 25 is disposed between the introduction pipe 12 a and the plurality of heat transfer tubes 19 so that the main surface of the baffle plate 25 is parallel to the central axis A of the casing 14.

  As shown in FIG. 4, the baffle plate 25 is disposed so as to be inclined with respect to the flow direction of the refrigerant W (the central axis of the introduction pipe 12a). The baffle plate 25 may be arranged such that the main surface of the baffle plate 25 is orthogonal to the flow direction of the refrigerant W.

  The plurality of upstream rectifying plates 27 and the downstream rectifying plates 28 are arranged on the upstream side of the baffle plate 25. The plurality of upstream rectifying plates 27 are arranged on the upstream side of the downstream rectifying plate 28.

The upstream rectifying plate 27 guides the refrigerant W flowing so as to be orthogonal to the central axis A of the casing 14 along the central axis A of the casing 14. The upstream rectifying plate 27 includes an upstream inclined portion 30 that is inclined so as to approach the end of the casing 14 toward the baffle plate 25, and an upstream rectifying plate main body portion 31 that is formed along the central axis A of the casing 14. ,have.
The condenser 3 of the present embodiment has four upstream rectifying plates 27. Hereinafter, of the four upstream rectifying plates 27, the two upstream rectifying plates 27 arranged on the upstream side are referred to as first upstream rectifying plates 27a, and the two upstream rectifying plates arranged on the downstream side of the first upstream rectifying plate 27 are referred to as “first upstream rectifying plates 27a”. The plate 27 is referred to as a second upstream rectifying plate 27b.

  The downstream rectifying plate 28 has a main portion 32 along the flow direction of the refrigerant W introduced from the introduction pipe 12a, and a downstream inclined portion 33 connected to the downstream end of the main portion 32. The downstream inclined portion 33 is inclined so as to approach the end portion of the casing 14 toward the baffle plate 25. Specifically, the downstream inclined portion 33 includes a first inclined surface 33a inclined so as to approach one end of the heat transfer tube 19 toward the downstream side in the flow direction of the refrigerant W, and an upstream end portion of the first inclined surface 33a. A second inclined surface 33b that is connected to the upstream end portion and is inclined so as to approach the other end of the heat transfer tube 19 toward the downstream side in the flow direction of the refrigerant W. The downstream end of the downstream inclined portion 33 is connected to the baffle plate 25.

  As shown in FIG.4 and FIG.5, the 1st slope 33a and the 2nd slope 33b of the downstream baffle plate 28 of this embodiment are perforated plates. That is, a plurality of holes 36 are formed in the first slope 33a and the second slope 33b. The holes 36 are regularly arranged on the first slope 33a and the second slope 33b. Punching metal can be used as the first slope 33a and the second slope 33b.

  The 1st slope 33a and the 2nd slope 33b can be formed from metals, such as SUS304, for example. The shape of the hole 36 is not limited to a circular shape, and may be a rectangular shape or a slit shape. The material of the plate portion is not limited to metal, and may be a plastic such as polyacetal resin, for example.

A first wall portion 37 having a main surface intersecting with the first slope 33a and the second slope 33b is provided at the ends of the first slope 33a and the second slope 33b. Edges of the first slope 33 a and the second slope 33 b opposite to the intersecting ridge line 38 are connected by a second wall 39.
A first space R <b> 1 that functions as a partitioned resonator is formed on the back side of the first slope 33 a and the second slope 33 b (downstream in the flow direction of the refrigerant W). The first space R1 is a space formed by the first slope 33a, the second slope 33b, the first wall portion 37, the second wall portion 39, and the baffle plate 25. The first space R1 and the casing inner space S3 communicate with each other only by the hole 36 formed in the first inclined surface 33a and the second inclined surface 33b.

As shown in FIGS. 3 and 4, the baffle plate 25 of the present embodiment is a porous plate similar to the first inclined surface 33 a and the second inclined surface 33 b. That is, the baffle plate 25 is formed with a plurality of holes 36.
A partitioned second space R2 is formed on the back surface side of the baffle plate 25 (downstream in the flow direction of the refrigerant W). The second space R <b> 2 is a space formed by the baffle plate 25, the four side wall portions 42, and the rear wall portion 43.

The rear wall portion 43 is a plate-like member that is disposed in parallel to the baffle plate 25 on the back surface side (downstream side in the flow direction of the refrigerant W) of the baffle plate 25. The baffle plate 25 and the rear wall portion 43 have substantially the same shape.
The side wall portion 42 is a plate-like member that connects the four edge portions of the baffle plate 25 and the four edge portions of the rear wall portion 43. The second space R2 and the casing inner space S3 communicate with each other only by a hole 36 formed in the baffle plate 25.

  The hole 36 of the baffle plate 25 is formed only on the surface exposed to the casing inner space S3. That is, the hole 36 of the baffle plate 25 is not formed on the surface facing the first space R1.

In the condenser 3 of the present embodiment, the first inclined surface 33a, the second inclined surface 33b, and the baffle plate 25, which are perforated plates, and the spaces R1 and R2 that are partitioned on the back surface side thereof are noise having a single frequency. It functions as an acoustic device that can ensure a high sound absorption rate.
The resonance frequency of the acoustic device can be adjusted by the volume of the spaces R1 and R2, (distance L between the baffle plate 25 and the rear wall portion 43), the diameter φ of the hole 36, and the aperture ratio σ of the porous plate.

  According to the above-described embodiment, the guide portion (downstream rectifying plate 28, baffle plate 25) includes the perforated plate and the spaces R1 and R2 that are defined on the back surface side of the perforated plate. Noise can be reduced. That is, the noise can be reduced before the noise generated from the condenser 3 resonates with the space in the pipe 12 between the condenser 3 and the evaporator 7. In other words, the excitation force can be reduced before the noise generated from the condenser 3 reaches the resonance space provided in the subsequent stage of the condenser 3.

Further, the downstream inclined portion 33 (the first inclined surface 33a and the second inclined surface 33b) of the downstream rectifying plate 28 is a perforated plate, and the first space R1 is formed on the back surface side, so that the refrigerant W is moved to the heat transfer tube 19 side. Noise can be absorbed while being dispersed.
Further, the baffle plate 25 is a perforated plate, and the second space R2 is formed on the back side, so that the back side of the baffle plate 25 can be used for noise reduction.

Moreover, since the guide part diverts the conventional structure, it can be realized in a small remodeling range. Thereby, the guide part which enables noise reduction can be formed at low cost.
Moreover, the resonance frequency as an acoustic device can be adjusted by adjusting the volumes of the spaces R1 and R2, the diameter φ of the hole 36, and the aperture ratio σ of the porous plate.
Further, since the porous plate has a surface facing the flow of the refrigerant W, the refrigerant W directly collides with the porous plate. Thereby, the acoustic resistance (sound absorption performance) by the flow of the refrigerant W can be increased.

The embodiment of the present invention has been described in detail with reference to the drawings. However, the specific configuration is not limited to this embodiment, and includes design changes and the like within a scope not departing from the gist of the present invention. .
In the above-described embodiment, the diameter of the hole 36 formed in the plate portion is the same. However, the diameter is not limited to this, and the diameter of the hole 36 may be different.

1 Refrigerator 2 Compressor 3 Condenser 4 First expansion valve (expander)
5 Second expansion valve (expander)
6 Economizer 7 Evaporator 8 Inlet 9 Hot Gas Bypass Pipe 10 Hot Gas Bypass Valve 11 Refrigeration Cycle 12 Piping 14 Casing 15 First Tube Plate 16 Second Tube Plate 19 Heat Transfer Tube (Heat Exchanger)
22 Casing body 23 Lid part 24 Through hole 25 Baffle plate (guide part, perforated plate)
27 Upstream rectifier (guide)
28 Downstream rectifier (guide)
30 Upstream inclined portion 31 Upstream rectifying plate main body portion 32 Main portion 33 Downstream inclined portion 33a First inclined surface (perforated plate)
33b Second slope (perforated plate)
36 hole portion 37 first wall portion 38 intersecting ridge line 39 second wall portion 42 side wall portion 43 rear wall portion L longitudinal direction R1 first space R2 second space S1 first header inner space S2 second header inner space S3 casing inner space W refrigerant

Claims (3)

A guide for guiding refrigerant introduced from the outside;
A heat exchange part into which the refrigerant is introduced via the guide part,
The guide part is
A perforated plate having a surface facing the flow of the refrigerant and having a plurality of holes formed therein;
A condenser having a compartment formed on the back side of the perforated plate. The heat exchange part is a plurality of heat transfer tubes extending in a direction intersecting the flow direction of the refrigerant,
The perforated plate has a first inclined surface that is inclined so as to approach one end of the heat transfer tube as it goes downstream in the flow direction of the refrigerant, and an upstream end is connected to an upstream end of the first inclined surface. The condenser according to claim 1, further comprising a second inclined surface that inclines so as to approach the other end of the heat transfer tube toward the downstream side in the refrigerant flow direction.   3. The condenser according to claim 2, wherein the perforated plate includes a baffle plate that is connected to the downstream side in the flow direction of the refrigerant on the first slope and the second slope and extends in a longitudinal direction of the heat transfer tube.

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