JPH112464A - Refrigerant circuit structure of compression-type heating device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To effectively suppress the generation of noise at a merging part of a main flow returning to a compressor and a bypass flow by forming a hollow part being extended along a main passage at the merging connection part of the main passage and a bypass passage, and at the same time by providing a plurality of connecting holes for connecting the hollow part to the inside of the main passage. SOLUTION: At the joint between a first bypass passage 7 and a passage 4b, the tip part of the first bypass passage 7 intervenes in the inside of the passage 4b, the intervention part of the first bypass passage 7 is bent toward the lower course of the flow direction of a refrigerant and is arranged along the inner surface of the passage 4b. Then, while the tip of the first bypass passage 7 is closed, a plurality of connecting holes 16 for connecting the inside of the first bypass passage to the outside of it are formed at the side surface of a part for intervening in the passage 4b at the intervention part of the first bypass passage 7, thus emitting the refrigerant of the first bypass passage 7 from the connecting holes 16 while it is being subjected to multiple reflection inside, consuming the energy of a pressure wave, preventing the flow of a main flow from being disturbed by the bypass flow, and suppressing the generation of noise.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

TECHNICAL FIELD The present invention relates to a compressor, a condenser,
While circulating the refrigerant through a closed circuit having an expansion valve and an evaporator, a compression type heat transfer device configured to perform cooling / heating, or freezing by a heat radiation effect in the condenser or a heat absorption effect in the evaporator in the condenser. The present invention relates to a refrigerant circuit structure.

[0002]

2. Description of the Related Art Conventionally, as a compression-type heat transfer apparatus as described above, for example, a condenser and an evaporator are provided with indoor and outdoor heat exchangers, and a refrigerant including a compressor and an indoor and outdoor heat exchanger is used. BACKGROUND ART An air conditioner (air conditioner) that performs heating and cooling by circulating a refrigerant through a circuit is generally known. Recently, a plurality of indoor heat exchangers are provided in a refrigerant circuit to perform each indoor heat exchange. By operating the vessels individually,
For example, a so-called multi-type air conditioner that can air-condition a plurality of rooms with one refrigerant circuit has been proposed.

In such an air conditioner, for example, when heating is performed, a high-temperature and high-pressure gaseous refrigerant compressed by a compressor is sent to an indoor heat exchanger, where condensation heat is released. This heats the room. Then, after the refrigerant liquefied by releasing the heat of condensation is decompressed by the expansion valve,
It is sent to an outdoor heat exchanger, where it absorbs heat of vaporization and evaporates, and is sucked into the suction side of the compressor.

[0004]

However, in an air conditioner equipped with a plurality of indoor heat exchangers, the heat exchange capacity of the indoor heat exchanger varies greatly depending on the number of operating indoor heat exchangers. On the other hand, the heat exchange capacity of the outdoor heat exchanger is set during the heating operation because the heat exchange capacity of the outdoor heat exchanger is fixedly set so as to be able to cope with the case where all the indoor heat exchangers are operated. When the number of indoor heat exchangers is small, the amount of heat release of the refrigerant in the indoor heat exchanger is smaller than the amount of heat absorbed by the refrigerant in the outdoor heat exchanger. As a result of insufficient condensation, the proportion of gas-phase refrigerant in the gas-liquid mixed refrigerant passing through the expansion valve increases, and the weight of the refrigerant passing through the expansion valve decreases. The decrease in the weight of the refrigerant passing through the expansion valve further reduces the amount of heat radiated in the indoor heat exchanger, which causes a problem of lowering the heating capacity. When the weight of the refrigerant passing through the expansion valve decreases, the refrigerant stays in the non-operated indoor heat exchanger, for example, on the high pressure side between the compressor and the expansion valve, and passes through the operated indoor heat exchanger. There is a problem that the amount of refrigerant to be heated is further reduced, and the heating capacity is further reduced.

Therefore, in this type of apparatus, a bypass passage is provided to return the refrigerant discharged from the compressor to a passage on the suction side of the compressor without passing through a condenser or an evaporator. The amount of the refrigerant circulating to the indoor heat exchanger is adjusted by returning the refrigerant to the compressor via the bypass passage according to the etc., whereby the refrigerant is appropriately vaporized in the indoor heat exchanger, and To prevent stagnation,
It's actually happening.

However, while the refrigerant (by-pass flow) returned through the bypass passage is a high-pressure refrigerant, the refrigerant (main flow) returned to the compressor through the indoor heat exchanger has a low pressure, so that the refrigerant is compressed. If the bypass passage is connected directly to the passage (main passage) on the suction side of the machine, the bypass flow collides with the main flow at the junction of the bypass flow and the main flow and disturbs the main flow. There is a problem of generating noise.

SUMMARY OF THE INVENTION The present invention has been made to solve the above-mentioned problems. In a compression heat transfer device such as a multi-type air conditioner as described above, a refrigerant discharged from a compressor is provided as necessary. The compressor and the evaporator can be bypassed to ensure the proper circulation of the refrigerant in the refrigerant circuit, while effectively reducing the noise generation at the junction of the main flow and the bypass flow returning to the compressor. It is an object of the present invention to provide a refrigerant circuit structure of a compression heat transfer device that can be suppressed.

[0008]

In order to solve the above-mentioned problems, a refrigerant circuit structure of a compression type heat transfer device according to the present invention is configured to compress a refrigerant discharged from a compressor through a condenser, an expansion valve and an evaporator. A main passage configured to return to the compressor, and a bypass passage branching from the high pressure side of the main passage and returning a part of the refrigerant discharged from the compressor to the main passage on the low pressure side without passing through the condenser or the like. In the compression type heat transfer device provided with: a hollow portion extending along the main passage is formed at the junction of the main passage and the bypass passage, and a plurality of the hollow passages communicate with the inside of the main passage. And the refrigerant passing through the bypass passage is guided to the hollow portion (claim 1).

According to this structure, the refrigerant in the bypass passage is multiple-reflected in the hollow portion, and is discharged into the main passage through the communication hole while the energy of the pressure wave of the refrigerant is consumed. Therefore, the flow velocity of the bypass flow at the time of merging is suppressed. Also, a large number of minute vortices generated when the refrigerant is jetted into the main passage through the communication hole interfere with each other by interfering with the vortex of the refrigerant flowing through the main passage, thereby canceling the energy of the pressure wave of the refrigerant after jetting. Is further consumed. Therefore, by these respective actions, the bypass flow and the main flow merge without disturbing the flow of the main flow, and the generation of noise due to collision of the two flows at the merging portion is effectively suppressed.

In this refrigerant circuit structure, the hollow portion is constituted by the bypass passage by interposing a tip portion of the bypass passage inside the main passage and closing the tip portion. If a plurality of holes are provided as the communication holes (claim 2), the circuit structure can be obtained relatively easily.

At this time, if a bulging portion bulging laterally is formed on the inner wall of the main passage, and the bypass passage is arranged in the bulging portion (claim 3), it is more effective. The bypass flow and the main flow can be combined without disturbing the flow of the main flow.

Further, in the refrigerant circuit structure of the first aspect,
While forming multiple hollow portions as the hollow portions, the inner and outer hollow portions are communicated with each other by a plurality of internal communication holes, and after the refrigerant sequentially passes through each hollow portion, it enters the main passage through the communication holes. If the refrigerant passing through the bypass passage is introduced into the hollow portion so as to be introduced (Claim 4), the refrigerant in the bypass passage is jetted into the main passage while being sequentially multiple-reflected in each hollow portion. Therefore, the energy of the pressure wave of the refrigerant can be effectively consumed.
Therefore, it is possible to more effectively suppress the flow velocity of the refrigerant at the time of merging.

In this case, the tip portion of the bypass passage is interposed in a single hollow portion, and the tip portion is closed to form a plurality of hollow portions. If the holes are provided (claim 5), the refrigerant circuit of claim 4 can be manufactured relatively easily.

Further, the refrigerant circuit structure of the compression heat transfer device according to the present invention includes: a main passage configured to return the refrigerant discharged from the compressor to the compressor through a condenser, an expansion valve, and an evaporator; A compression-type heat transfer device comprising a bypass passage that branches off from the high pressure side of the main passage and returns a part of the refrigerant discharged from the compressor to the main passage on the low pressure side without passing through the condenser or the like. A plurality of holes for allowing the bypass passage to intervene in the inside of the main passage so as to close the tip thereof, and for ejecting the refrigerant in the bypass passage in a direction parallel to the flow direction of the refrigerant in the main passage to the intervening portion of the bypass passage. (Claim 6).

[0015] According to this structure, the refrigerant in the bypass passage is multiple-reflected in the hollow portion, whereby the energy of the pressure wave of the refrigerant is exhausted into the main passage through the communication hole while the energy of the refrigerant is consumed. Is effectively suppressed. In addition, since the refrigerant in the bypass passage is ejected in parallel with the flow direction of the refrigerant in the main passage, the main flow is hardly disturbed when the refrigerant is ejected from the bypass passage. Therefore, by these actions, the bypass flow and the main flow can be combined without disturbing the flow of the main flow.

[0016]

Embodiments of the present invention will be described with reference to the drawings.

FIG. 1 is a circuit diagram showing an air conditioner using a compression heat transfer device according to the present invention. In this figure, only the main part of the air conditioner is shown. In the following description, the term "passage" means a pipe.

An air conditioner 1 (hereinafter abbreviated as an air conditioner 1) shown in FIG. 1 includes a compressor 2 driven by an engine (not shown) and a refrigerant such as Freon compressed and discharged by the compressor 2. And a circulating refrigerant circuit 3.

The refrigerant circuit 3 includes a condenser, an expansion valve,
And a closed circuit for circulating the refrigerant discharged from the compressor 2 back to the compressor 2 through the condenser, the expansion valve, and the evaporator.

In this embodiment, a plurality of indoor heat exchangers 1
0, the expansion valve 11 attached thereto and the outdoor heat exchanger 12 are incorporated in the refrigerant circuit 3 and the four-way valve 5 for switching the refrigerant circulation direction is provided. Is a condenser, the outdoor heat exchanger 12 is an evaporator, and at the time of cooling, the indoor heat exchanger 10 is an evaporator,
The outdoor heat exchanger 12 is configured to be a condenser.

More specifically, a passage 4a extends from the discharge side of the compressor 2 and is connected to the first port 5a of the four-way valve 5. In the four-way valve 5, a passage 4b extends from the fourth port 5d.
Is introduced to the suction side of the compressor 2 via the accumulator 6.

Between the passages 4a and 4b, there is provided a first bypass passage 7 which branches off from the middle thereof and is connected to the passage 4b on the upstream side of the accumulator 6. The first bypass passage 7 is used for adjusting a flow rate. The first bypass valve 8 is connected.

In the four-way valve 5, a passage 4c extends from the second port 5b, and the passage 4c leads to each indoor heat exchanger 10.

As shown in the figure, the indoor heat exchangers 10 are arranged in parallel with each other, and the input / output part on one side (the left side in the figure) is connected to the passage 4c and the other side ( The input / output portions (on the right side in the figure) are connected to the passages 4d via the expansion valves 11, respectively. The passage 4 d is connected to the third port 5 c of the four-way valve 5 via the outdoor heat exchanger 12.

In the passage 4d, a second bypass passage 13 branched from the passage 4d is provided upstream of the outdoor heat exchanger 12, and the bypass passage 13 is connected to the passage 4b.
The second bypass passage 13 is connected to a second bypass valve 14 for adjusting the flow rate.

Incidentally, in the refrigerant circuit 3, as a characteristic point of the present invention, a connection portion (a portion indicated by a symbol T in the drawing) between the first bypass passage 7 and the passage 4b has a structure as shown in FIG. I have.

That is, in this portion, the leading end of the first bypass passage 7 is interposed inside the passage 4b as shown in the drawing, and the intervening portion of the first bypass passage 7 is directed in the flow direction of the refrigerant (arrow in the drawing). ) Is bent toward the downstream side and disposed along the inner surface of the passage 4b.

The front end of the first bypass passage 7 is closed, while the side of the intervening portion of the first bypass passage 7 which intervenes in the passage 4b is provided with the second bypass passage 7 as shown in FIG. A large number of communication holes 16 communicating between the inside and the outside of the 1 bypass passage 7 are formed.
The refrigerant in the bypass passage 7 is introduced into the passage 4b.

Next, the operation and effect of the air conditioner 1 will be described.

When a heating operation is performed in the air conditioner 1, the compressor 2 is operated according to the driving of the engine.
The high-temperature and high-pressure gaseous refrigerant is discharged to the passage 4a and sent to the first port 5a of the four-way valve 5. At this time, when all the indoor heat exchangers 10 are operating, the first and second bypass valves 8 and 14 are all in the fully closed state. The case where some of the indoor heat exchangers 10 are operated will be described later in detail.

The four-way valve 5 is in a state where the first port 5a and the second port 5b communicate with each other and the third port 5c and the fourth port 5d communicate with each other during heating (the state shown in the drawing). Therefore, the refrigerant discharged from the compressor 2 to the passage 4a is sent to the passage 4c via the four-way valve 5. Then, the heat reaches the indoor heat exchangers 10, where the heat of condensation is released to liquefy. That is, at this time, each indoor heat exchanger 1
The room is heated by the condensation heat released at zero.

The refrigerant liquefied by releasing the heat of condensation is decompressed by the expansion valve 11 and then sent to the passage 4d to reach the outdoor heat exchanger 38a, where it is vaporized by absorbing the heat of evaporation from the outside air. Thereafter, it is sent to the four-way valve 5.

In the four-way valve 5, as described above, the third port 5c
Is communicated with the fourth port 5d, the refrigerant reaches the accumulator 6 via the four-way valve 5 and the passage 4b, where the refrigerant is separated into a gas component and a liquid component, and only the gaseous refrigerant passes through the passage. It is sent to the compressor 2 through 4b. Thus,
Thereafter, similarly, the refrigerant is circulated in the refrigerant circuit 3 to perform the heating operation.

On the other hand, in the cooling operation, the first port 5a and the third port 5c of the four-way valve 33 in the refrigerant circuit 3,
The port 5b communicates with the fourth port 5d.
Therefore, the refrigerant discharged from the compressor 20 first passes through the passage 4a, the four-way valve 5, and the passage 4d to reach the outdoor heat exchanger 12, where it is cooled and condensed by outside air to become a high-pressure liquid refrigerant, and each expansion. It is sent to the valve 11.

The refrigerant sent to each expansion valve 11 is decompressed here and sent to each indoor heat exchanger 10, where it absorbs latent heat of evaporation from indoor air and evaporates (vaporizes). In other words, the cooling of the room is performed by the refrigerant absorbing the latent heat of evaporation in the room.

The vaporized refrigerant passes through the passage 4c, the four-way valve 5 and the passage 4b and reaches the accumulator 6, where the refrigerant is separated into a gas and a liquid. Sent to Thus, hereafter, similarly,
The cooling operation is performed by circulating the refrigerant through the refrigerant circuit 30.

By the way, in the above-mentioned air conditioner 1, during the heating operation and when some of the indoor heat exchangers 10 among the indoor heat exchangers 10 are operated, the first bypass valve 8 Is opened and a part of the refrigerant flowing through the passage 4a is introduced into the passage 4b via the first bypass passage 7, whereby a part of the refrigerant discharged from the compressor 2 is
And it is returned to the compressor 2 without passing through the outdoor heat exchanger 12 and the like. Further, the second bypass valve 14 is opened and a part of the passage 4d is introduced into the passage 4b via the second bypass passage 13, whereby a part of the refrigerant after releasing the condensation heat is removed from the outdoor heat exchanger 12 Without passing through the passage 4b.
Is returned to. At this time, for example, the opening degrees of the first and second bypass valves 8 and 14 are adjusted according to the number of operations of the indoor heat exchanger 10.

That is, when only some of the indoor heat exchangers 10 are operated during the heating operation, the fans of the other indoor heat exchangers are stopped, and the expansion valve 11 is fully closed. The amount of heat dissipated in the indoor heat exchanger 10 is smaller than the amount of heat absorbed in the outdoor heat exchanger 12, and the balance of heat transfer of the refrigerant is often lost. When the balance is lost, the proportion of the gas-phase refrigerant in the gas-liquid mixed refrigerant passing through the expansion valve 11 connected to the operated indoor heat exchanger 10 increases, and the weight of the refrigerant passing through the expansion valve 11 decreases. Accordingly, the amount of the refrigerant passing through the operated indoor heat exchanger 10 also decreases, and the heating capacity decreases. Therefore, in such an operation state, a part of the refrigerant flowing through the passage 4a is
The refrigerant is returned to the compressor 2 via the bypass passage 7, whereby an appropriate amount of refrigerant according to the number of operating indoor heat exchangers 10 is sent to the indoor heat exchanger 10. This allows
The refrigerant on the high pressure side is bypassed from the expansion valve 11 to the low pressure side reaching the compressor 2 via the outdoor heat exchanger 12, and the refrigerant temperature on the low pressure side is increased. As a result, the amount of heat absorbed by the outdoor heat exchanger 12 is reduced, the refrigerant flowing from the compressor 2 to the operating indoor heat exchanger 10 is radiated and liquefied, and the amount of refrigerant passing through the expansion valve 11 is increased. That is, the operating indoor heat exchanger 1
On the contrary, the amount of refrigerant flowing to zero increases, and the heating capacity is improved.

However, when the number of operating indoor heat exchangers 10 is particularly small, the heat radiation capacity is reduced.
Since the heat absorption capacity of the outdoor heat exchanger 12 remains large, simply adjusting the amount of refrigerant passing through the first bypass passage 7 as described above causes the indoor heat being operated due to the temperature drop due to the pressure drop on the high pressure side. As the heat radiating ability of the exchanger 10 decreases, the pressure difference before and after the expansion valve 11 decreases, and the weight of the refrigerant passing through the expansion valve 11 decreases, and as a result, the refrigerant passes through the indoor heat exchanger 10 that is being operated. The amount of the refrigerant decreases, and the improvement of the heating capacity reaches a limit, and conversely, decreases. And there is a possibility that the compressor 2 may be overheated due to the temperature rise on the low pressure side due to the bypass. Therefore, when a part of the refrigerant is returned to the compressor 2 through the first bypass passage 7 as described above, the relatively low-temperature refrigerant after releasing the heat of condensation in the indoor heat exchanger 10 is converted into the outdoor heat. By returning the refrigerant to the compressor 2 via the second bypass passage 13 without passing through the exchanger 12, the temperature of the refrigerant sucked into the compressor 2 is reduced, thereby maintaining the imbalance in heat transfer of the refrigerant. ing.

When the refrigerant is bypassed through the first bypass passage 7 as described above, the high-pressure refrigerant discharged from the compressor 2 is supplied to the relatively low-pressure refrigerant in the passage 4b, that is, the expansion valve 11 The refrigerant (bypass flow) in the first bypass passage 7 collides with the refrigerant (main flow) in the passage 4b and disturbs the flow of the main flow. There is a concern that noise may be generated.

However, in the refrigerant circuit 3 of the air conditioner 1, the first bypass passage 7 having a closed end is interposed in the passage 4b as described above, and the communication hole 16 formed in the side surface of the first bypass passage 7 is formed. Since the bypass flow is introduced into the passage 4b through the passage, the generation of the noise as described above is effectively suppressed.

That is, in the first bypass passage 7,
Since the tip is closed, the refrigerant in the first bypass passage 7 that has reached the junction with the passage 4b is jetted into the passage 4b through the communication hole 16 while being multiply reflected therein. At this time, the refrigerant is multiple-reflected in the first bypass passage 7, so that the energy of the pressure wave of the refrigerant is remarkably consumed. (Reduction of flow velocity). Therefore, the bypass flow does not violently collide with the main flow and disturb the main flow.

Further, when the refrigerant is jetted into the passage 4b through the plurality of communication holes 16, a large number of minute vortices generated at the time of jetting interfere with each other by interfering with the vortex of the refrigerant flowing through the passage 4b. (Interaction of eddy currents). Therefore, the energy of the pressure wave of the refrigerant after the ejection is further consumed, and as a result, disturbance of the main flow due to collision between the bypass flow and the main flow is further suppressed.

Therefore, while the high-pressure refrigerant is bypassed through the first bypass passage 7 and introduced into the passage 4b, both of the above-described functions of reducing the flow velocity and interfering with the vortex flow are exhibited. As a result, the bypass flow and the main flow merge without disturbing the flow of the main flow, and the generation of noise due to collision of the two flows at the junction is effectively suppressed.

FIG. 3 shows a case where the structure of the above embodiment is adopted as a structure of a connecting portion between the first bypass passage 7 and the passage 4b, and a general connecting structure in a conventional refrigerant circuit of this kind, for example, simply Pass the end of the first bypass passage 7 to the passage 4
b shows data obtained by detecting noise at each specific frequency when the two paths are connected to each other in a substantially T-shape by being connected to the side wall portion of FIG. , And the solid line indicates data according to the conventional structure). From this data, according to the structure of the above-described embodiment, noise generation,
Specifically, it can be considered that the generation of noise in a frequency region exceeding 1.6 K (Hz) in the audible frequency region is effectively suppressed.

It should be noted that the above data is stored in a passage 4 of φ17 (mm).
The first bypass passage 7 of φ5 (mm) is interposed with respect to the refrigerant b. The refrigerant (main stream) flowing at a pressure of approximately 0.5 MPa in the passage 4 b has a pressure of approximately 2 MPa ( This is data when the bypass flow is merged through the first bypass passage 7.

As described above, according to the air conditioner 1, when part of the indoor heat exchanger 10 is operated, a part of the refrigerant discharged from the compressor 2 passes through the first bypass passage 7. By returning the refrigerant to the compressor 2 through the refrigerant circuit, it is possible to prevent the refrigerant from staying in the refrigerant circuit, while effectively suppressing the generation of noise at the junction of the first bypass passage 7 and the passage 4b. . Therefore, it is possible to provide a quieter air conditioner as compared with a conventional air conditioner of this type.

Incidentally, the connection structure between the first bypass passage 7 and the passage 4b is one embodiment of the refrigerant circuit structure of the present invention, and the specific structure thereof does not depart from the gist of the present invention. It can be changed appropriately within a range not to be performed.

For example, FIGS. 4A to 4G and FIG.
(A) to (c) each show another embodiment of the connection structure, and these structures may be adopted.

First, FIG. 4A shows a structure in which the first bypass passage 7 interposed in the passage 4b is appropriately inclined with respect to the passage 4b in the structure shown in FIG.

FIG. 4B shows a branch structure at the end of the first bypass passage 7, in which each of the branch passages 7a and 7b is interposed in the passage 4b, and the flow direction of the refrigerant along the inner surface of the passage 4b. It is a structure arranged side by side. In this case, the distal end of the first bypass passage 7 may be branched into three or more. Further, as shown in the figure, in addition to arranging the branch passages 7a and 7b in the flow direction of the refrigerant, they may be arranged in the circumferential direction of the passage 4b.

FIG. 4C shows a structure in which a silencer is provided in the first bypass passage 7 in the structure shown in FIG. More specifically, a portion of the first bypass passage 7 slightly upstream of an intervening portion of the first bypass passage 7 in the passage 4b is disposed in the closed chamber 21, and a large number of communication holes 20 are formed in this portion. According to this structure, the energy of the pressure wave of the refrigerant flowing in the first bypass passage 7 is consumed by the resonance of the pressure wave before the refrigerant reaches the tip end portion of the first bypass passage 7, so that the flow velocity at the junction is Is more effectively exerted.

FIG. 4D shows a structure in which a bulging portion 18 bulging laterally is formed inside the passage 4b, and the tip of the first bypass passage 7 is arranged in the bulging portion 18. . According to such a structure, the bypass flow and the main flow can be merged more effectively without disturbing the flow of the main flow.

FIG. 4 (e) shows a state in which the first
FIG. 4F shows a structure in which the diameter of the distal end portion of the bypass passage 7 is gradually increased toward the downstream side in the flow direction of the refrigerant. In FIG. 4F, the diameter of the distal end portion is gradually reduced toward the downstream side in the flow direction of the refrigerant. Structure.

FIG. 4 (g) shows a first bypass passage 7 which is formed by extending a tip portion of the first bypass passage 7 into a U-shape by extending in a direction substantially perpendicular to the flow direction of the refrigerant inside the passage 4b. The communication hole 16 is formed such that the refrigerant in the passage 7 is jetted in a direction parallel to the flow direction of the refrigerant in the passage 4b.

FIG. 5A shows a hollow portion 22 communicating with the passage 4b through a large number of communication holes 24 formed in the partition wall 23.
Is provided integrally on the side of the passage 4b, and the bypass flow through the first bypass passage 7 is introduced into the hollow portion 22. In this structure, the tip of the first bypass passage 7 is simply connected to the side wall forming the hollow portion 22. Also according to this structure, the refrigerant introduced into the hollow portion 22 from the first bypass passage 7 is jetted into the passage 4b through the communication hole 24 while being multiply reflected inside the hollow portion 22. As with the structure shown, the effect of reducing the flow velocity and the effect of interfering with the vortex flow are exhibited. Therefore, the bypass flow and the main flow can be combined without disturbing the flow of the main flow. In addition, in the case of this structure, as shown in FIG. 5, in addition to forming the hollow portion 22 in a part of the circumferential direction of the passage 4b, as shown in FIG. The hollow portion 22 may be formed.

FIG. 5C shows the structure shown in FIG.
This is a structure obtained by combining the structure shown in FIG. That is, the distal end portion of the first bypass passage 7 is interposed in the hollow portion 22, and the communication hole 16 is formed in the intervening portion. According to this structure, first, the first bypass passage 7
The effect of reducing the flow velocity is exhibited by the above, and the effect of reducing the flow velocity is further exhibited by the hollow portion 22. That is, the effect of reducing the flow velocity is doubled. Therefore, the bypass flow and the main flow can be combined more effectively without disturbing the flow of the main flow.

Although not shown, as a modification of FIG. 5C, for example, a hollow portion is formed outside the hollow portion 22 via a side wall, and the insides thereof are connected to each other through a communication hole. A double hollow portion may be formed so as to communicate, and the bypass flow by the first bypass passage 7 may be introduced into the outermost hollow portion. With such a structure, FIG.
As in the case of the structure (c), the effect of reducing the flow velocity is doubled. In this case, for example, when the pressure difference between the bypass flow and the main flow is large, the hollow portion may be formed in three or more layers to more effectively reduce the flow velocity.

In the description of the above embodiment, the shape of the communication hole 16 formed in the first bypass passage 7 is not particularly mentioned, but the communication hole 16 may be any one of a circle, an ellipse, and a slit. It may be. The communication hole 16 has a hole diameter that is constant in the hole axis direction.
The hole diameter may change in the hole axis direction, such as a tapered shape or a stepped shape. Further, the communication holes 16 having the same shape
In addition to forming the communication holes, communication holes 16 having different shapes may be mixed. In short, the communication hole 16 may be formed so that the disturbance of the refrigerant flow at the junction can be effectively suppressed. In the first bypass passage 7, a portion where the communication hole 16 is formed may be covered with a porous member such as a wire mesh to suppress the flow velocity of the bypass flow at the time of merging.

In the above embodiment, the air conditioner 1 has been described as an example of the compression type heat transfer device. However, the application of the present invention is not limited to the air conditioner 1, and of course, the amount of heat absorbed by the evaporator is smaller than Since the operation may be performed in a state where the amount of heat released from the condenser is small, the present invention is also applicable to other compression heat transfer devices such as a refrigerator.

[0061]

As described above, the present invention provides a main passage for circulating the refrigerant and a bypass for returning a part of the refrigerant discharged from the compressor to the main passage on the low pressure side without passing through a condenser or the like. In a compression type heat transfer device having a passage, a hollow portion extending along the main passage is formed, and a plurality of communication holes communicating the hollow portion and the inside of the main passage are provided. By introducing the refrigerant into the hollow part, the refrigerant is jetted into the main passage through the communication hole while making multiple reflections in the hollow part, so that the bypass flow and the main flow merge effectively without disturbing the flow of the main flow I can do it. Therefore, it is possible to effectively suppress the generation of noise due to the collision of the two flows at the junction.

In particular, in this refrigerant circuit structure, the hollow portion is constituted by the bypass passage by interposing a tip portion of the bypass passage inside the main passage and closing the tip end. By providing a plurality of holes as the communication holes on the side surface, the circuit structure as described above can be obtained relatively easily. On this occasion,
By forming a swelling portion swelling laterally on the inner wall of the main passage and arranging the bypass passage in the swelling portion, the bypass flow and the main flow can be more effectively disturbed without disturbing the flow of the main flow. And can be merged.

In the refrigerant circuit structure, a plurality of hollow portions are formed as the hollow portions, and the inner and outer hollow portions are communicated with each other through a plurality of internal communication holes. If the refrigerant in the bypass passage is introduced into the hollow portion so as to be introduced into the main passage through the communication hole, the refrigerant in the bypass passage is sequentially multiple-reflected in each hollow portion. Since the refrigerant is jetted into the passage, the energy of the pressure wave of the refrigerant can be effectively consumed. Therefore, it is possible to more effectively suppress the flow velocity of the refrigerant at the time of merging. In this case, the distal end portion of the bypass passage is interposed in the single hollow portion, and the distal end is closed to form a multiple hollow portion, and a plurality of holes are provided on the side surface of the bypass passage as the internal communication holes. If provided, the refrigerant circuit as described above can be manufactured relatively easily.

The present invention also relates to a main passage configured to return a refrigerant discharged from a compressor to a compressor via a condenser, an expansion valve and an evaporator, and a part of the refrigerant discharged from the compressor. And a bypass passage for returning the air to the main passage on the suction side of the compressor without passing through a condenser or the like. At the same time, a plurality of holes for ejecting the refrigerant in the bypass passage in a direction parallel to the flow direction of the refrigerant in the main passage are formed in the intervening portion of the bypass passage. Since the refrigerant is ejected in a direction parallel to the flow of the refrigerant, the bypass flow and the main flow can be effectively combined without disturbing the flow of the main flow. Therefore, it is possible to effectively suppress the generation of noise due to the collision of the two flows at the junction.

[Brief description of the drawings]

FIG. 1 is a refrigerant circuit diagram of an air conditioner to which the present invention is applied.

FIG. 2 is a schematic cross-sectional view showing a structure of a connection portion between a bypass passage and a main passage (a passage structure at a junction of a bypass flow and a main flow).

FIG. 3 is a graph (graph) showing noise level detection results obtained by a conventional connection structure and a connection structure of the present application.

FIGS. 4A to 4G are schematic cross-sectional views showing another structure of a connection portion between the bypass passage and the main passage.

FIGS. 5A to 5C are schematic cross-sectional views showing another structure of a connection portion between the bypass passage and the main passage.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Air conditioner (air conditioner) 2 Compressor 3 Refrigerant circuit 4a-4d Passage 5 Four-way valve 5a 1st port 5b 2nd port 5c 3rd port 5d 4th port 6 Accumulator 7 1st bypass passage 8 1st bypass valve 10 Indoor heat exchanger 11 Expansion valve 12 Outdoor heat exchanger 13 Second bypass passage 14 Second bypass valve 16 Communication hole

Claims (6)

[Claims] 1. A main passage configured to return a refrigerant discharged from a compressor to a compressor via a condenser, an expansion valve, and an evaporator, a branch from a high pressure side of the main passage, and discharge from the compressor. And a bypass passage for returning a part of the refrigerant to the main passage on the low pressure side without passing through the condenser or the like. In addition to forming a hollow portion extending along the passage, a plurality of communication holes communicating the hollow portion and the inside of the main passage are provided, and refrigerant passing through the bypass passage is guided to the hollow portion. Refrigerant circuit structure of compression heat transfer device. 2. The hollow portion is constituted by the bypass passage by interposing a distal end portion of the bypass passage inside the main passage and closing the distal end thereof, and the communication hole is formed in a side surface of the bypass passage as the communication hole. The refrigerant circuit structure of a compression heat transfer device according to claim 1, wherein a plurality of holes are provided. 3. The compression heat transfer according to claim 2, wherein a bulging portion bulging laterally is formed on an inner wall of the main passage, and the bypass passage is arranged in the bulging portion. The refrigerant circuit structure of the device. 4. A plurality of hollow portions are formed as the hollow portions, and the inner and outer hollow portions are communicated with each other by a plurality of internal communication holes. After the refrigerant sequentially passes through each hollow portion, the refrigerant passes through the communication holes. 2. The refrigerant circuit structure of the compression heat transfer device according to claim 1, wherein the refrigerant passing through the bypass passage is introduced into the hollow portion so as to be introduced into the main passage. 5. A double hollow portion is formed by interposing a distal end portion of the bypass passage in a single hollow portion and closing the distal end thereof, and a plurality of internal communication holes are provided on side surfaces of the bypass passage. The refrigerant circuit structure of the compression heat transfer device according to claim 4, wherein the holes are provided. 6. A main passage configured to return the refrigerant discharged from the compressor to the compressor via a condenser, an expansion valve, and an evaporator, a branch from a high pressure side of the main passage, and discharge from the compressor. And a bypass passage that returns a part of the refrigerant to be returned to the main passage on the low pressure side without passing through the condenser or the like. And a plurality of holes for discharging the refrigerant in the bypass passage in a direction parallel to the flow direction of the refrigerant in the main passage are formed in the intervening portion of the bypass passage. Refrigerant circuit structure.