JP2008057827A - Refrigerating cycle apparatus - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To reduce keen sounds generated in the vicinity of pipe connecting parts J1-J3 of refrigerant pipes H2, P3, P4 returning from an evaporator 50 to a compressor 10. <P>SOLUTION: A turbulence generating rugged part 65 is formed on the refrigerant flow downstream side of the pipe connecting parts J1-J3 of the refrigerant pipes H2, P3, P4 returning from the evaporator 50 to the compressor 10, and the turbulence generating rugged part 65 is composed of three or more recessed parts or projecting parts continuously arranged in the refrigerant flow direction. Thus, the turbulence generating rugged part 65 for distributing the flow of refrigerant is provided in the vicinity of upstream ends of the refrigerant pipes H2, P3, P4 generating keen sounds resonant with a standing wave, not taking measures for eliminating a step to smooth a refrigerant flow, whereby generation of keen sounds in the vicinity of the pipe connecting part can be prevented, and deterioration of keen sounds in the other pipe connecting parts can be prevented. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a refrigeration cycle apparatus, and more particularly to a pipe connection part structure that can reduce a keen sound generated in the vicinity of a pipe connection part of a refrigerant pipe returning from an evaporator to a compressor.

  Conventionally, in the refrigerant pipe of the refrigeration cycle apparatus, when the refrigerant flows, a vortex is generated due to the shape of the refrigerant flow path in the refrigerant pipe, which causes noise. In Patent Document 1 below, a multi-pass spiral groove as a swirl flow generating means is provided inside an inlet pipe of a flow distributor for diverting a refrigerant to a multi-pass type evaporator, and the constricted portion is divided by swirl flow. It eliminates the refrigerant passing noise.

  Further, in Patent Document 2 below, the flow of the refrigerant flowing into the expansion valve is disturbed by a turbulence generating portion formed in the refrigerant passage on the upstream side of the opening degree variable throttle portion. As a result, the bubbles in the gas-liquid two-phase refrigerant flow can be subdivided and made uniform without reducing the pressure of the refrigerant. In other words, the noise and discontinuous noise when the refrigerant passes through the opening degree variable throttle portion of the expansion valve are reduced.

However, these conventional techniques are for noise with a frequency not so high, such as shoe noise, which is generated by a gas-liquid two-phase refrigerant flow flowing into an expansion valve or an evaporator. On the other hand, it is known that as a refrigerant noise in the refrigeration cycle apparatus, a metallic sound in the vicinity of 5 to 7 kHz called “Kean” is generated from a pipe connection portion of the refrigerant pipe returning from the evaporator to the compressor. Conventionally, in order to suppress this noise, there is one in which the edge is eliminated as much as possible as a defective flow location causing the vortex in the connecting portion between the refrigerant pipes to have an appropriate angle taper (for example, the following patent document) 3).
JP 2000-105026 A JP 2005-226846 A Japanese Patent Laid-Open No. 7-217779

  However, in recent years, compressors with oil separators have become widespread in order to improve cooling capacity, and the amount of oil circulation in the refrigeration cycle has decreased, so that the keen sound has recurred despite the same piping shape. This is probably because oil has accumulated in the step existing in the refrigerant flow path of the pipe connection portion to smooth the shape of the flow path. Therefore, naturally, if the amount of oil circulation in the refrigeration cycle is increased, the frequency of occurrence of a keen sound is reduced, but there is a problem that the cooling capacity is lowered.

  In addition, it is known that such a keen noise will not occur if the hose or pipe as the refrigerant pipe can be formed integrally without the connection part, but it is not realistic to eliminate the pipe connection part for assembling the apparatus. Absent. By eliminating the step in the refrigerant flow path of the pipe connection part that occurs greatly, it is possible to prevent the generation of a keen sound at that part. Since a further louder keen sound is generated from the step of another pipe connection part that has not been performed, it is difficult to completely mute the sound when the step is eliminated.

  In addition, in the pipe connection part that connects the refrigerant pipes to both sides of the box-type expansion valve, the inventors arrange the refrigerant in the transmission rod that is arranged in the low-pressure side refrigerant flow path of the expansion valve and transmits the movement of the temperature sensing part. A vortex occurs on the downstream side of the flow, the periodic vortex becomes a standing wave due to the refrigerant flow velocity, propagates to the downstream side of the refrigerant flow, and the refrigerant piping downstream of the pipe connection part resonates with the standing wave. We have also found that a keen sound is generated.

  The present invention has been made paying attention to such problems existing in the prior art, and its purpose is to generate a keen sound generated in the vicinity of the pipe connection portion of the refrigerant pipe returning from the evaporator to the compressor. An object of the present invention is to provide a refrigeration cycle apparatus that can be reduced.

In order to achieve the above object, the present invention employs technical means described in claims 1 to 4. That is, in the invention according to claim 1, a compressor (10) for sucking and compressing refrigerant,
A radiator (20) for radiating high-temperature and high-pressure refrigerant discharged from the compressor (10);
Decompression expansion means (40) for decompressing and expanding the refrigerant flowing out of the radiator (20);
An evaporator (50) for evaporating the refrigerant flowing out from the decompression and expansion means (40);
In the refrigeration cycle apparatus provided with refrigerant pipes (H1, H2, P1 to 4) that connect these in an annular shape,
There is a turbulent flow generation uneven part (65) formed on the downstream side of the refrigerant flow of the pipe connection part (J1 to J3) of the refrigerant pipe (H2, P3, P4) returning from the evaporator (50) to the compressor (10). The turbulent flow generation uneven portion (65) is characterized by comprising three or more concave portions or convex portions that are continuously arranged in the refrigerant flow direction.

  According to the first aspect of the present invention, the refrigerant pipes (H2, P3, P4) generating a keen sound in resonance with the standing wave are not a measure for eliminating the step and smoothing the refrigerant flow. Providing a turbulent flow generation uneven part (65) that disturbs the refrigerant flow in the vicinity of the upstream end prevents the generation of a keen sound near the pipe connection part and prevents the deterioration of the keen sound at other pipe connection parts. be able to.

  The invention according to claim 2 is characterized in that, in the refrigeration cycle apparatus according to claim 1, the turbulent flow generation uneven part (65) is provided on the refrigerant flow upstream side of the sound generation part. According to the second aspect of the present invention, it is possible to effectively prevent the generation of a keen sound by disturbing the flow of the refrigerant upstream of the sounding portion to prevent the generation of periodic vortices. it can.

  Moreover, in invention of Claim 3, refrigeration cycle apparatus of Claim 1 or Claim 2 WHEREIN: A turbulent flow uneven | corrugated | grooved uneven | corrugated | grooved part (65) is a refrigerant | coolant flow downstream of a pipe connection part (J1-J3). It forms on the inner surface of the upstream end vicinity of the refrigerant | coolant piping (H2, P3, P4) which becomes.

  According to the third aspect of the present invention, the turbulent flow generation uneven portion that disturbs the flow of the refrigerant in the vicinity of the upstream end of the refrigerant pipe (H2, P3, P4) that generates a keen sound in resonance with the standing wave. By providing (65), it is possible to prevent the generation of a keen sound in the vicinity of the pipe connection part and to prevent the keen sound from deteriorating in other pipe connection parts.

  Moreover, in invention of Claim 4, in the refrigerating cycle apparatus of any one of Claim 1 thru | or 3, a turbulent flow generation | occurrence | production uneven | corrugated | grooved part (65) is refrigerant | coolant piping (H2, P3, P4). ) In the shape of a screw. The turbulent flow generation uneven portion (65) may be formed by cutting a screw on the inner surface of the refrigerant pipe (H2, P3, P4).

  According to the fourth aspect of the present invention, the turbulent flow generation uneven portion (65) can be easily formed, and the cost for preventing the keen noise can be suppressed. In addition, the code | symbol in the parenthesis as described in a claim and said each means is an example which shows a corresponding relationship with the specific means as described in embodiment mentioned later.

  Hereinafter, a first embodiment of the present invention will be described in detail with reference to FIGS. First, FIG. 1 is a perspective view showing a configuration of a refrigeration cycle apparatus 1 according to an embodiment of the present invention, and FIG. 2 is a front view of an evaporator 50 and pipe connecting portions J1 and J2. 3 is a cross-sectional view showing the structure of the pipe connection portion J1 in one embodiment of the present invention, FIG. 4 is a cross-sectional view showing the structure of the pipe connection portion J2 in one embodiment of the present invention, and FIG. It is sectional drawing which shows the structure of the piping connection part J3 in one Embodiment.

  In the present embodiment, an example in which the present invention is applied to a refrigeration cycle apparatus as a vehicle cooler will be described. The vehicle cooler includes a blower (not shown) for sending cooling air into the passenger compartment and a duct (not shown) that forms a passage for the cooling air, and the cooling heat for cooling the air flowing in the duct is contained in the duct. An evaporator 50 described later is provided as an exchanger.

  Next, the components of the refrigeration cycle apparatus 1 will be described along the refrigerant flow. First, the compressor 10 obtains power from a vehicle travel engine (not shown) and sucks and compresses the refrigerant. Note that the compressor 10 is a well-known compressor and will not be described in detail because the structure is not limited. In the present embodiment, the compressor 10 includes an oil separator (not shown), and the amount of oil circulation in the refrigeration cycle. Is less. Further, the compressor 10 may be an electric one.

  Then, the high-pressure refrigerant discharged from the compressor 10 is supplied to the condenser (radiator referred to in the present invention) 20 through the flexible refrigerant hose H1. The condenser 20 cools the high-pressure refrigerant by exchanging heat between the cooling wind and high-pressure refrigerant discharged from the compressor 10 using wind received from the front during vehicle travel or wind sent from a cooling fan (not shown) as cooling air. It is a high-pressure side heat exchanger that is allowed to condense.

  In addition, since the condenser 20 is also a well-known thing and does not ask | require a structure in this embodiment, detailed description is abbreviate | omitted. In addition, the condenser 20 of the present embodiment gas-liquid separates the refrigerant flowing in from the condenser 20 and causes only the liquid refrigerant to flow out, and stores the surplus refrigerant in the refrigeration cycle as liquid refrigerant, and the receiver 30. A supercooler that further cools the liquid refrigerant that has flowed out further by exchanging heat with the outside air is integrally configured.

  The condensed refrigerant flowing out of the condenser 20 flows into the first inflow port 411 of the expansion valve (decompression expansion means in the present invention) 40 through the aluminum refrigerant pipe P1 (see FIG. 4). In addition, the expansion valve 40 in this embodiment is comprised with the known box type expansion valve 40 which has a temperature sensing part in a refrigerant | coolant flow path, as shown in FIG. The expansion valve 40 decompresses and expands the high-pressure refrigerant in an enthalpy manner, and controls the pressure of the high-pressure refrigerant based on the refrigerant temperature on the refrigerant outlet side of the evaporator 50. The detailed structure will be described later.

  The high-pressure refrigerant that has flowed into the first inflow port 411 is depressurized by a later-described valve portion in the first refrigerant passage, flows out from the first outflow port 412, passes through the aluminum refrigerant pipe P <b> 2, and enters the evaporator 50. Supplied. The evaporator 50 is a low-pressure side heat exchanger that evaporates the low-pressure refrigerant by exchanging heat between the decompressed low-pressure refrigerant and the air blown into the passenger compartment.

  The evaporator 50 is a well-known heat exchanger and may have any structure, but in the present embodiment, as shown in FIG. 2, tubes 51 and fins 52 are alternately stacked to form a heat exchange unit, A lower tank 53 for distributing the refrigerant to the tubes 51 is provided on the lower side, and an upper tank 54 for collecting the heat-exchanged refrigerant is provided on the upper side. A refrigerant introduction pipe 55 extends from the lower tank 53, and a refrigerant outlet pipe 56 extends from the upper tank 54, and a block joint 57 is brazed and joined to the distal ends of these pipes 55, 56.

  The evaporator 50 is housed in a duct (not shown) mounted in the passenger compartment, and is arranged so that the entire amount of cooling air sent by the blower passes through the heat exchange unit. The evaporator 50 evaporates the refrigerant decompressed and expanded by the expansion valve 40, and cools and dehumidifies the cooling air blown into the vehicle interior by the evaporation heat of the refrigerant.

  The low-pressure refrigerant evaporated in the evaporator 50 flows into the second inflow port 413 of the expansion valve 40 through the aluminum refrigerant pipe P3, passes through the second refrigerant passage communicating with the temperature sensing unit, and the second outflow port 414. (See FIG. 4). The refrigerant that has passed through the expansion valve 40 is drawn into the compressor 10 through the aluminum refrigerant pipe P4 and the flexible refrigerant hose H2.

  In this embodiment, as shown in FIGS. 1 and 2, block joints 61 and 62 are brazed and joined to both ends of the refrigerant pipes P2 and P3 to form a pipe assembly 60, and one end of the refrigerant pipes P1 and P4. A pipe assembly 70 is configured by brazing the block joint 71. Further, a pipe connection portion J3 shown in FIG. 5 is configured between the refrigerant pipe P4 and the refrigerant hose H2.

  Next, a specific structure of the pipe connecting portions J1 to J3 will be described with reference to FIGS. First, the pipe connection part J1 shown in FIG. 3 is a connection part between the block joint 57 of the evaporator 50 and the block joint 61 on one end side of the pipe assembly 60. Pipe connection holes 571 and 572 are formed on the side opposite to the block joint 57, and the leading ends of the refrigerant introduction and lead-out pipes 55 and 56 are inserted into the pipe connection holes 571 and 572 for brazing. . Further, fitting convex portions 573 and 574 are formed on the connection side surface, and O-rings 58 and 59 for sealing are fitted.

  The block joint 61 also has pipe connection holes 611 and 612 formed on the side opposite to the connection side, and is inserted by brazing and joining the leading ends on one end side of the refrigerant pipes P2 and P3. Further, fitting concave portions 613 and 614 are formed on the connection side surface, and fitting convex portions 573 and 574 of the block joint 57 are inserted and fitted. The block joints 57 and 61 are connected and sealed by fastening with through bolts (not shown).

  4 is a connection portion in which the expansion valve 40 is configured between the block joint 62 on the other end side of the pipe assembly 60 and the block joint 71 on the one end side of the pipe assembly 70. Pipe connection holes 621 and 622 are formed on the side opposite to the block joint 62, and the other ends of the refrigerant pipes P2 and P3 are inserted and brazed and joined. Further, fitting convex portions 623 and 624 are formed on the connection side surface, and O-rings 63 and 64 for sealing are fitted.

  The block joint 71 also has pipe connection holes 711 and 712 formed on the non-connection side surface, and is inserted by brazing and joining one end of the refrigerant pipes P1 and P4. Further, fitting convex portions 713 and 714 are formed on the connection side surface, and O-rings 72 and 73 for sealing are fitted.

  Next, the structure of the expansion valve 40 will be described. The expansion valve 40 of the present embodiment is of a so-called box type. The expansion valve 40 includes an expansion valve block B, a heat transfer part 41, a transmission rod 42, an element part 43, a ball valve 44, and the like. The valve block B is made of, for example, aluminum and is provided in a substantially rectangular parallelepiped shape, and includes a first refrigerant passage and a second refrigerant passage.

  The first refrigerant passage includes the inflow port 411 connected to the refrigerant pipe P1 from the condenser 20, the outflow port 412 connected to the refrigerant pipe P2 to the evaporator 50, and the inflow port 411 side and the outflow port 412 side. And a conical sheet surface is provided on the inlet side (inflow port 411 side) of the communication hole. The second refrigerant passage includes an inflow port 413 connected to the refrigerant pipe P3 from the outlet side of the evaporator 50, an outflow port 414 connected to the refrigerant pipe P4 to the compressor 10, and an inflow port 413 and an outflow port 414. It has a communication path that communicates with the heat transfer section 41.

  The element portion 43 includes a diaphragm 431 made of a flexible thin metal plate, a receiving portion 432 for sandwiching the diaphragm 431, and a lid portion 433, and is screwed to the upper portion of the valve block B via a packing 49a. Is done. The receiving portion 432 and the lid portion 433 are joined by, for example, TIG welding, and the diaphragm chamber 431 and the lid portion 433 form a diaphragm chamber 45.

  The diaphragm chamber 45 is filled with a different kind of saturated gas from the refrigerant gas used in the refrigeration cycle. The lid 433 is provided with a hole for allowing saturated gas to enter the diaphragm chamber 45, and after being filled with the saturated gas, it is airtightly closed by a plug 45a. Further, each component (diaphragm 431, receiving portion 432, lid portion 433 and plug 45a) constituting the element portion 43 is formed using the same metal material (for example, stainless steel).

  The heat transfer part 41 is formed in a columnar shape using a metal material (for example, aluminum or brass) having high thermal conductivity. The cylindrical upper surface is in close contact with the lower surface of the diaphragm 431 by receiving an urging force described later from below, and the temperature change of the refrigerant flowing in the second refrigerant passage (the vapor phase refrigerant evaporated in the evaporator 50) is changed. While transmitting to the diaphragm 433, the transmission rod 42 is contact | abutting to the cylindrical lower surface, and the displacement of the diaphragm 431 cooperates with the transmission rod 42 and is transmitted to the ball valve 44.

  The transmission rod 42 is disposed below the heat transfer section 41 and is slidably held by the valve block B. The upper end portion abuts on the lower surface of the heat transfer section 41, passes through the communication passage of the second refrigerant passage in the vertical direction, is inserted into the communication hole of the first refrigerant passage, and the lower end portion is a conical sheet surface. The ball valve 44 is pressed against the upper surface of the ball valve 44. Further, with respect to the transmission rod 42 that is slidably inserted in the vertical direction, the valve block B portion between the first refrigerant passage and the second refrigerant passage is provided with a seal portion by an O-ring 49b. Yes.

  As shown in FIG. 4, the ball valve 44 is disposed on the inlet side of the communication hole, is held between the transmission rod 42 and the valve receiving member 46, and closes the communication hole by sitting on the seat surface. The communication hole can be opened by detaching (lifting) from the surface. This ball valve 44 is shown in FIG. 4 via a force that pushes the diaphragm 431 downward (pressure in the diaphragm chamber 45 -pressure of refrigerant vapor acting on the lower side of the diaphragm 431) and a valve receiving member 46. 4 is stationary at a position where the load of the spring 47 biased upward is balanced.

  The spring 47 is disposed between an adjusting screw 48 attached to the lower end of the valve block B and a valve receiving member 46, and the ball valve 44 is moved upward in FIG. To the direction). The adjusting screw 48 adjusts the valve opening pressure of the ball valve 44 (the load of the spring 47 that urges the ball valve 44), and is screwed to the lower end of the valve block B via an O-ring 49c. These block joints 62 and 71 and the expansion valve 40 are connected and sealed by being fastened from both sides with through bolts (not shown).

  A pipe connection portion J3 shown in FIG. 5 is a connection portion between the refrigerant pipe P4 from the expansion valve 40 and the refrigerant hose H2 to the compressor 10. A fitting female part 74 is formed at the other end of the refrigerant pipe P4, and a male screw joint 75 is inserted outside the fitting female part 74. Further, a fitting male part 91 is formed on the end fitting of the refrigerant hose H2, and a sealing O-ring 92 is fitted on the fitting male part 91 and on the outside of the fitting male part 91. The female screw joint 93 is inserted. Then, the fitting male part 91 is inserted and fitted into the fitting female part 74, and the male screw joint 75 and the female screw joint 93 are fastened to establish connection and seal.

  Next, the main part of the invention in this embodiment will be described. In the present embodiment, the inner surface of the refrigerant pipes H2, P3, P4 near the upstream end of the refrigerant pipes H2, P3, P4 on the downstream side of the refrigerant pipes H2, P3, P4 of the refrigerant pipes H2, P3, P4 returning from the evaporator 50 to the compressor 10 is disturbed. The flow generation uneven part 65 is formed (see FIGS. 3 to 5). In the present embodiment, the turbulent flow generation uneven portion 65 is formed by cutting screws on the inner surfaces of the refrigerant pipes H2, P3, and P4. However, the present invention is not limited to this. For example, each uneven portion is formed in the circumferential direction. It may not be continuous or may not be a spiral like a screw.

  According to this, by providing the turbulent flow generation portion 65 whose shape is not uniform in the flow path direction on the downstream side of the refrigerant flow in the step in the direction in which the inner diameter is reduced in the refrigerant flow path of the pipe connection portion, It is possible to suppress the sound generation at a specific frequency by disturbing the periodicity of the keen sound that causes such a change in tube diameter. Note that the sound generation parts in the present embodiment are the refrigerant pipes H2, P3, and P4 on the downstream side of the refrigerant flow that resonates with the standing wave. In this manner, the formation of the turbulent flow generation uneven portion 65 on the inner surfaces of the refrigerant pipes H2, P3, and P4 can easily prevent the generation of a keen sound.

  FIG. 6 is a graph showing a noise generation state in an embodiment to which the present invention is applied, and FIG. 7 is a graph showing a noise generation state before the present invention is applied. In the graph of FIG. 7, a peak of 78 dBA keen sound appears at 6.47 kHz as shown by the dashed ellipse. In the graph of FIG. 6, the peak of the keen sound is applied by applying the present invention. You can see that it disappears.

  Next, features and effects of this embodiment will be described. First, it has a turbulent flow generation uneven part (65) formed on the downstream side of the refrigerant flow of the pipe connection parts J1 to J3 of the refrigerant pipes H2, P3, and P4 returning from the evaporator 50 to the compressor 10, The part (65) is composed of three or more continuously arranged concave parts or convex parts in the refrigerant flow direction.

  According to this, the flow of the refrigerant is disturbed in the vicinity of the upstream ends of the refrigerant pipes H2, P3, and P4 that generate a keen sound in resonance with the standing wave, not a measure for eliminating the step and smoothing the refrigerant flow. By providing the turbulent flow generation uneven part 65, it is possible to prevent the generation of a keen sound in the vicinity of the pipe connection part and to prevent the keen sound from deteriorating in other pipe connection parts.

  Moreover, the turbulent flow generation uneven part 65 is provided on the refrigerant flow upstream side of the sound generation part. According to this, it is possible to effectively prevent the generation of a keen sound by disturbing the flow of the refrigerant upstream of the sound generation unit and preventing the generation of periodic vortices.

  Moreover, the turbulent flow generation uneven part 65 is formed on the inner surface in the vicinity of the upstream ends of the refrigerant pipes H2, P3, and P4 that are on the downstream side of the refrigerant flow of the pipe connecting parts J1 to J3. According to this, by providing the turbulent flow generation uneven portion 65 that disturbs the flow of the refrigerant in the vicinity of the upstream ends of the refrigerant pipes H2, P3, and P4 that generate a keen sound in resonance with the standing wave, the pipe connection It is possible to prevent the generation of a keen sound in the vicinity of the part and the deterioration of the keen sound at other pipe connection parts.

  Moreover, the turbulent flow generation uneven part 65 is formed in a screw shape on the inner surfaces of the refrigerant pipes H2, P3, and P4. The turbulent flow generation uneven portion 65 may be formed by cutting screws on the inner surfaces of the refrigerant pipes H2, P3, and P4. According to this, the turbulent flow generation uneven part 65 can be easily formed, and the cost for preventing a keen sound can be suppressed.

(Other embodiments)
In the above-described embodiment, an example in which the present invention is applied to a vehicle air conditioner has been shown. However, the present invention is not limited to the above-described embodiment, and may be applied to other devices as long as a refrigeration cycle is used. You may do it. Further, in the above-described embodiment, the pipe assemblies 60 and 70 are configured by integrating the pipes in both directions by the block joint, but a configuration in which the pipes in the respective directions are separated may be employed.

  Moreover, in the above-mentioned embodiment, although joining of piping and a block joint is brazing, it may be caulking joining. In the above-described embodiment, the subcritical pressure cycle in which the refrigerant is condensed in the radiator is used. However, in the radiator, a supercritical pressure cycle in which the refrigerant is not condensed may be used. An exchanger may be configured.

1 is a perspective view showing a configuration of a refrigeration cycle apparatus 1 according to an embodiment of the present invention. It is a front view of the evaporator 50 and the piping connection parts J1 and J2. It is sectional drawing which shows the structure of the piping connection part J1 in one Embodiment of this invention. It is sectional drawing which shows the structure of the piping connection part J2 in one Embodiment of this invention. It is sectional drawing which shows the structure of the piping connection part J3 in one Embodiment of this invention. It is a graph which shows the generation situation of noise in the embodiment to which the present invention is applied. It is a graph which shows the generation condition of noise before applying the present invention.

Explanation of symbols

10 ... Compressor 20 ... Condenser (radiator)
40. Expansion valve (decompression expansion means)
50 ... Evaporator 65 ... Turbulent flow uneven part H1, H2 ... Refrigerant hose (refrigerant piping)
P1-4 ... Refrigerant pipe (refrigerant piping)
J1-J3 ... Piping connection

Claims (4)

A compressor (10) for sucking and compressing refrigerant;
A radiator (20) for radiating high-temperature and high-pressure refrigerant discharged from the compressor (10);
Decompression expansion means (40) for decompressing and expanding the refrigerant flowing out of the radiator (20);
An evaporator (50) for evaporating the refrigerant flowing out of the decompression and expansion means (40);
In the refrigeration cycle apparatus provided with refrigerant pipes (H1, H2, P1 to 4) that connect these in an annular shape,
The turbulent flow generation uneven part (65) formed on the downstream side of the refrigerant flow of the pipe connection part (J1 to J3) of the refrigerant pipe (H2, P3, P4) returning from the evaporator (50) to the compressor (10). The refrigeration cycle apparatus is characterized in that the turbulent flow generating uneven part (65) is composed of three or more continuously arranged concave parts or convex parts in the refrigerant flow direction.   The refrigeration cycle apparatus according to claim 1, wherein the turbulent flow generation uneven portion (65) is provided on the refrigerant flow upstream side of the sound generation portion.   The said turbulent flow generation | occurrence | production uneven | corrugated | grooved part (65) is formed in the inner surface of the upstream end vicinity of the said refrigerant | coolant piping (H2, P3, P4) used as the refrigerant | coolant flow downstream of the said piping connection part (J1-J3). The refrigeration cycle apparatus according to claim 1 or 2, characterized by the above.   The said turbulent flow generation | occurrence | production uneven | corrugated | grooved part (65) is formed in the inner surface of the said refrigerant | coolant piping (H2, P3, P4) in the shape of a screw, In any one of Claims 1 thru | or 3 characterized by the above-mentioned. The refrigeration cycle apparatus described.

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