ES2728955T3 - Refrigeration system - Google Patents

Abstract

A refrigeration system, comprising: a first refrigerant pass (204, 204e, 204h); a p-type silencer (20c, 20d, 20e, 20h) having a first silencer space (201c) communicating with the first coolant passage (204), a second silencer space (202c) arranged side by side with the first silencing space (201c), and a communication path (203c) extending from the lower end of the first silencing space (201c) to the lower end of the second silencing space (202c) through the exterior of the first squelch space (201c) and communicates with the second squelch space (202c); a second refrigerant passage (205, 205e, 205h) communicating with the second muffling space (202c); and a compressor (11), characterized in that the refrigeration system further comprises an outdoor unit (10), a four-way switching valve (12), an outdoor heat exchanger (13) and an indoor heat exchanger (31 ), wherein the p-type silencer (20c, 20d, 20e, 20h) is arranged between a discharge side of the compressor (11) and the four-way switching valve (12); wherein a compressor discharge path (11) is connected to the first silencing space (201c) through the first refrigerant passage (204), and a heat transfer path from the outdoor heat exchanger (13) or the Indoor heat exchanger (31) is connected to the second muffling space (202c) through the second refrigerant passage (205).

Description

DESCRIPTION

Refrigeration system

Technical field

The present invention relates to a cooling system in which a n-type silencer is used as the silencer.

Prior art

In recent years, refrigeration systems that use carbon dioxide as a refrigerant have become commodities. However, when carbon dioxide is used as a refrigerant in a refrigeration system in this manner, the problem arises that the density of the refrigerant and the speed of sound in the refrigerant become larger and the pressure pulsation inevitably increases. To counteract this problem, in recent years, several procedures have been proposed to reduce pressure pulsation in refrigeration systems (for example, see patent citation 1, patent citation 2, non-patent citation 1 and Non-patent quotation 2).

Patent Quote 1: JP-A No. 6-10875

Patent Quote 2: JP-A No. 2004-218934

Non-patent quotation 1: Sakae Yamada and Iwao Ótani, "Orifisu oyobi n-gata hairetsu kukiso ni yoru myakudo jokyo", Transactions of the Japan Society of Mechanical Engineers (Second Part), December 1968, vol. 34, No. 268, p.

2139-2145

Non-patent quotation 2: The Japan Society of Mechanical Engineers, editor, "Jirei ni manabu ryutai kanren shindo", First Edition, Gihodo Shuppan Co., Ltd., September 20, 2003, p. 190-193.

US 2002/0071774 A1 discloses a refrigeration system, comprising: a first refrigerant passage; a silencer having a first squelch space that communicates with the first coolant passage, a second squelch space arranged side by side with the first squelch space, and a communication path that extends from the first squelch space to the second mute space through the outside of the first mute space and communicating with the second mute space; and a second refrigerant passage that communicates with the second silencing space. US 2002/0071774 A1 discloses a refrigerant system according to the preamble of claim 1. Disclosure of the invention

<Technical problem>

An object of the present invention is to sufficiently reduce the pressure pulsation in a refrigeration system that employs carbon dioxide and the like as a refrigerant.

<Solution to the problem>

A cooling system according to a first aspect of the present invention is listed in claim 1. The n-type silencer has a first mute space, a second mute space and a communication path. The first silencing space communicates with the first refrigerant passage. The second mute space and the first mute space are arranged side by side. The communication path extends from the lower end of the first mute space and through the outside of the first mute space to the lower end of the second mute space and communicates with the second mute space. The second refrigerant passage communicates with the second silencing space. Note that, in this refrigeration system, the refrigerant can flow in the order of: the first refrigerant passage ^ the silencer type n ^ the second refrigerant passage, or in the order opposite: the second refrigerant passage ^ the silencer type n ^ The first coolant passage.

The type n silencer is incorporated in this cooling system. Therefore, in this refrigeration system, the pressure pulsation can be sufficiently reduced even when carbon dioxide or the like is used as a refrigerant. In addition, in this cooling system, the second mute space and the first mute space are arranged side by side, and the communication path extends from the lower end of the first mute space and outside the first space. of silencing to the lower end of the second silence space and communicates with the second silence space. Therefore, in this cooling system, the entire length of the n-type silencer can be shortened. Consequently, in this cooling system, the options for the arrangement of the n-type silencer can be extended.

A refrigeration system according to a second aspect of the present invention is the refrigeration system according to the first aspect of the present invention, in which the first refrigerant passage is inserted from the upper end of the first silencing space and extends towards the interior of the first silencing space.

In this refrigeration system, the first refrigerant passage is inserted from the upper end of the first silencing space and extends into the first silence space. Therefore, in this refrigeration system, the oil of the refrigerating machine can be prevented from accumulating in the first silencing space when the refrigerant flows from the second silencing space to the first silencing space.

A cooling system according to a third aspect of the present invention is the cooling system according to the second aspect of the present invention, in which the second refrigerant passage is inserted from the upper end of the second silencing space and extends towards the interior of the second silencing space.

In this cooling system, the second refrigerant passage is inserted from the upper end of the second silencing space and extends into the second silence space. Therefore, in this refrigeration system, the oil of the refrigerating machine can be prevented from accumulating in the second silencing space when the refrigerant flows from the first silencing space to the second silencing space.

A cooling system according to a fourth aspect of the present invention is the cooling system according to the third aspect of the present invention, in which the first refrigerant passage extends from the upper end of the first silencing space. In addition, the second refrigerant passage extends from the upper end of the second silencing space.

In this cooling system, the first refrigerant passage extends from the upper end of the first silencing space, and the second refrigerant passage extends from the upper end of the second silencing space. Therefore, in this cooling system, a n-type silencer can be used that has a simple configuration. Therefore, in this cooling system, a reduction in manufacturing costs can be expected.

A refrigeration system according to a fifth aspect of the present invention is the refrigeration system according to the first aspect of the present invention, wherein the first refrigerant passage extends from the lower end of the first silencing space. In addition, the second refrigerant passage extends from the lower end of the second silencing space.

In this cooling system, the first refrigerant passage extends from the lower end of the first silencing space, and the second refrigerant passage extends from the lower end of the second silencing space. Therefore, in this cooling system, it is possible to prevent the oil from the refrigerating machine from accumulating in the first silencing space and in the second silencing space.

A cooling system according to a sixth aspect of the present invention is the cooling system according to any one of the previous aspects of the present invention, in which a mesh element fills the communication path.

In this cooling system, the mesh member fills the communication path. Therefore, in this cooling system, reflection waves within the communication path can be prevented.

<Effects of the invention>

In the refrigeration system according to the first aspect of the present invention, the pressure pulsation can be sufficiently reduced even when carbon dioxide or the like is used as a refrigerant. In addition, in this cooling system, the entire length of the type n silencer can be shortened. Consequently, in this cooling system, the options for the arrangement of the n-type silencer can be extended.

In the refrigeration system according to the second aspect of the present invention, it is possible to prevent the oil from the refrigerating machine from accumulating in the first silencing space when the refrigerant flows from the second silencing space to the first silencing space.

In the refrigeration system according to the third aspect of the present invention, it is possible to prevent the oil of the refrigerating machine from accumulating in the second silencing space when the refrigerant flows from the first silencing space to the second silencing space.

In the refrigeration system according to the fourth aspect of the present invention, a n-type silencer can be used that has a simple configuration. Therefore, in this cooling system, a reduction in manufacturing costs can be expected.

In the refrigeration system according to the fifth aspect of the present invention, it is possible to prevent the oil from the refrigerating machine from accumulating in the first silencing space and in the second silencing space.

In the cooling system according to the sixth aspect of the present invention, reflection waves can be prevented from arising within the communication path.

Brief description of the drawings

Figure 1 is a diagram of a refrigerant circuit of an air conditioner;

Figure 2 is a diagram in longitudinal section of a silencer of type n, which does not belong to the claimed invention, which is incorporated in the refrigerant circuit of the air conditioner of Figure 1;

Figure 3 is a diagram in longitudinal section of a silencer of type n, which does not belong to the claimed invention, which belongs to modification A;

Figure 4 is a diagram in longitudinal section of a silencer of type n, which does not belong to the claimed invention, which belongs to modification A;

Figure 5 is a diagram in longitudinal section of a silencer of type n belonging to modification B; Figure 6 is a diagram in longitudinal section of a silencer of type n belonging to modification B; Figure 7 is a diagram in longitudinal section of a silencer of type n belonging to modification B; Figure 8 is a diagram in longitudinal section of a type x silencer, which does not belong to the claimed invention, which belongs to modification C;

Figure 9 is a diagram in longitudinal section of a silencer of type n, which does not belong to the claimed invention, which belongs to modification D;

Figure 10 is a diagram in longitudinal section of a silencer of type n belonging to modification E; Figure 11 is a diagram in longitudinal section of a silencer of type n, which does not belong to the claimed invention, which belongs to modification F;

Figure 12 is a diagram in longitudinal section of a silencer of type n, which does not belong to the claimed invention, which belongs to modification F; Y

Figure 13 is a diagram in longitudinal section of a silencer of type n, which does not belong to the claimed invention, which belongs to modification G.

Explanation of reference numbers

1 Air Conditioning (Cooling System) 20, 20a, 20b, 20c, 20d, 20e, 20f, 20g, 20h, 20i, 20j, 20k Silencer type n

201,201c, 201i First space of silence

202, 202c, 202i Second space of silence

203, 203a, 203b, 203c, 203f, 203g, 203i, 203j, 203k Communication path

204, 204e, 204h, 203g, 203f First refrigerant passage

205, 205e, 205h Second refrigerant step

206 Oil return hole

206k First oil drain step.

207k Second oil drain step

Examples, not belonging to the claimed invention and better way to carry out the invention

Air conditioner settings>

Figure 1 shows a general refrigerant circuit 2 of an air conditioner 1 belonging to an embodiment of the present invention.

The air conditioner 1 uses carbon dioxide as a refrigerant, is capable of cooling and heating, and is mainly configured by the refrigerant circuit 2, the fans 26 and 32, a controller 23, a high pressure pressure sensor 21, a temperature sensor 22, an intermediate pressure pressure sensor 24 and the like.

The refrigerant circuit 2 is mainly equipped with a compressor 11, a silencer of type n 20, a four-way switch valve 12, an external heat exchanger 13, a first electric expansion valve 15, a liquid receiver 16, a second electric expansion valve 17 and an internal heat exchanger 31, and the devices are, as shown in Figure 1, interconnected through refrigerant tubes.

Furthermore, in the present embodiment, the air conditioner 1 is a discrete type air conditioner and it can also be said that it is configured by: an indoor unit 30 which mainly includes the indoor heat exchanger 31 and the indoor fan 32 ; an outdoor unit 10 which mainly includes the compressor 11, the type 20 silencer, the four-way switching valve 12, the external heat exchanger 13, the first electric expansion valve 15, the liquid receiver 16, the second electric expansion valve 17, high pressure pressure sensor 21, intermediate pressure pressure sensor 24, temperature sensor 22 and controller 23; a first communication tube 41 interconnecting a coolant tube of the indoor unit 30 and a coolant tube of the outdoor unit 10; and a second communication tube 42 that interconnects a refrigerant gas tube of the indoor unit 30 and a refrigerant gas tube of the outdoor unit 10. It will be noted that the refrigerant liquid tube of the outdoor unit 10 and the first communication tube 41 are interconnected through a first shut-off valve 18 of the outdoor unit 10 and that the refrigerant gas pipe of the outdoor unit 10 and the second communication tube 42 are interconnected through a second shut-off valve 19 of the unit outside 10.

(1) Indoor unit

The indoor unit 30 mainly includes the indoor heat exchanger 31, the indoor fan 32 and the like.

The indoor heat exchanger 31 is a heat exchanger to cause heat exchange between the refrigerant and the room air which is air within an air conditioned room.

The indoor fan 32 is a fan for transporting the air from the interior of the room with air conditioning to the interior of the unit 30 and expelling the air conditioner, which is air after heat has been exchanged with the refrigerant through the heat exchanger interior 31, back inside the room with air conditioning.

In addition, because the indoor unit 30 employs this configuration, the indoor unit 30 can, during the cooling operation, generate air conditioning (cold air) causing heat exchange between the room air that has been absorbed by the fan interior 32 and the liquid refrigerant that flows through the interior heat exchanger 31 and is capable, during the heating operation, of generating air conditioning (hot air) by exchanging heat between the room air that has been absorbed by the fan interior 32 and supercritical refrigerant flowing through the interior heat exchanger 31.

(2) Outdoor unit

The outdoor unit 10 mainly includes the compressor 11, the type 20 silencer, the four-way switching valve 12, the external heat exchanger 13, the first electric expansion valve 15, the liquid receiver 16, the second valve electric expansion 17, the external fan 26, the controller 23, the high pressure pressure sensor 21, the temperature sensor 22, the intermediate pressure pressure sensor 24 and the like.

The compressor 11 is a device for aspirating low pressure refrigerant gas flowing through a suction tube, compresses the low pressure refrigerant gas to a supercritical state, and then discharges the supercritical refrigerant to a discharge tube. It will be noted that, in the present embodiment, the compressor 11 is a rotary inverter type compressor.

Silencer 20 type n is, as shown in Figure 1, disposed between the discharge side of compressor 11 and four-way switching valve 12. Silencer 20 type n is, as in the example shown in Figure 2, configured by a first mute space 201, a second mute space 202 and a communication path 203 which allows the first mute space 201 and the second mute space 202 to communicate. It will be noted that, in the conditioner of air 1, a discharge path of the compressor 11 is connected to the first silencing space 201 through a first refrigerant passage 204 and that a heat transfer path of the external heat exchanger 13 or the internal heat exchanger 31 is connected to the second silencing space 202 through a second refrigerant passage 205. In other words, the refrigerant always flows in the order of: the first silencing space 201 ^ the communication path 203 ^ the second silencing space 202. The first silencing space 201 is a substantially cylindrical space, with the refrigerant passage 204 which is connected to its upper end in the axial direction and the communication path 203 is connected to its lower end in the axial direction. The second silencing space 202 is a substantially cylindrical space, with the communication path 203 connected to its upper end in the axial direction and the refrigerant passage 205 connected to the lower end thereof in the axial direction. Communication path 203 is a substantially cylindrical passage whose radius is smaller than the radius of the first squelch space 201 and the second squelch space 202, and the first squelch space 201 and the second squelch space 202 are connected to both sides of the communication path 203. It will be noted that, in the silencer 20 of type n, the axes of the first silencing space 201, the second silencing space 202 and the communication path 203 overlap. In addition, the length of communication path 203 is longer than S1 / 2 (1 / V1 + 1 / V2) (c / nNmin) 2 and shorter than c / 2ft. Here, S1 is the cross-sectional area of communication path 203, V1 is the volume of the first silencing space 201, V2 is the volume of the second silencing space 202, c is the speed of sound in carbon dioxide ( when the pressure is 10 MPa, the density is 221.6 kg / m3 and the speed of sound becomes 252 m / sec), n is pi, Nmin is the minimum number of rotations of compressor 11, and ft is a target Highest frequency reduction. It will be noted that, in the air conditioner 1, the silencer of type n 20 is housed in the outdoor unit 10, so that the first silencing space 201 and the second silencing space 202 are arranged one above the other along of the vertical direction.

The four-way switching valve 12 is a valve for changing the flow direction of the refrigerant in correspondence with each operation and is capable, during the cooling operation, of interconnecting the discharge side of the compressor 11 and a high temperature side of the external heat exchanger 13 and also interconnecting the suction side of the compressor 11 and a gas side of the internal heat exchanger 31 and is capable, during the heating operation, of interconnecting the discharge side of the compressor 11 and the second valve of closure 19 and also interconnect the suction side of the compressor 11 and a gas side of the external heat exchanger 13.

The external heat exchanger 13 may, during the cooling operation, use air outside the room with air conditioning as a heat source to cool the supercritical high-pressure refrigerant that has been discharged from the compressor 11 and is capable, during the operation of heating, to evaporate the liquid refrigerant returning from the indoor heat exchanger 31.

The first electric expansion valve 15 is for depressurizing the supercritical refrigerant (during the cooling operation) that flows outward from the low temperature side of the external heat exchanger 13 or the liquid refrigerant (during the heating operation) that flows to through the liquid receiver 16.

The liquid receiver 16 is for storing the excess refrigerant according to the mode of operation and the charge of the air conditioner.

The second electric expansion valve 17 is for depressurizing the liquid refrigerant (during the cooling operation) that flows through the liquid receiver 16 or the supercritical refrigerant (during the heating operation) leaving a low temperature side of the exchanger of internal heat 31.

The outside fan 26 is a fan to bring the outside air into the unit 10 and discharge the air after the air has exchanged heat with the refrigerant through the outside heat exchanger 13.

The high pressure sensor 21 is arranged on the discharge side of the compressor 11.

The temperature sensor 22 is arranged on the side of the external heat exchanger of the first electric expansion valve 15.

The intermediate pressure pressure sensor 24 is disposed between the first electric expansion valve 15 and the liquid receiver 16.

The controller 23 is communally connected to the high pressure pressure sensor 21, the temperature sensor 22, the intermediate pressure pressure sensor 24, the first electric expansion valve 15, the second electric expansion valve 17 and the like, and controls the openings of the first electric expansion valve 15 and the second electric expansion valve 17 based on the temperature information sent from the temperature sensor 22, the high pressure pressure information sent from the pressure sensor 21 High pressure and intermediate pressure pressure information sent from intermediate pressure pressure sensor 24.

air conditioner operation>

The operation of the air conditioner 1 will be described using Figure 1. The air conditioner 1 is, as mentioned above, capable of performing a cooling and heating operation.

(1) Cooling operation

During the cooling operation, the four-way switching valve 12 is in the state indicated by the continuous lines in Figure 1, that is, a state where the discharge side of the compressor 11 is connected to the high temperature side of the exchanger of external heat 13 and where the suction side of the compressor 11 is connected to the second shut-off valve 19. Furthermore, at this time, the first shut-off valve 18 and the second shut-off valve 19 open.

When the compressor 11 starts in this state of the refrigerant circuit 2, the refrigerant gas is aspirated to the compressor 11, a supercritical state is compressed, then sent to the external heat exchanger 13 through the four-way switching valve 12, and it cools in the external heat exchanger 13. It will be noted that, at this time, the silencer 20 of type n dampens the pressure pulse of the refrigerant.

Then, the supercritical refrigerant that has cooled is sent to the first electric expansion valve 15. Then, the supercritical refrigerant that has been sent to the first electric expansion valve 15 is depressurized to a saturated state and then sent to the second electric expansion valve 17 through the liquid receiver 16. The refrigerant in the saturated state that has been sent to the second electric expansion valve 17 is depressurized, converted into a cooling liquid, then supplied to the indoor heat exchanger 31 a through the first shut-off valve 18, the room air cools, evaporates and becomes refrigerant gas.

Next, the refrigerant gas is returned to the compressor 11 through the second shut-off valve 19 and the four-way switching valve 12. In this way, the cooling operation is performed.

(2) Heating operation

During the heating operation, the four-way switching valve 12 is in the state indicated by the broken lines in Figure 1, that is, a state where the discharge side of the compressor 11 is connected to the second shut-off valve 19 and where the suction side of the compressor 11 is connected to the gas side of the external heat exchanger 13. In addition, at this time, the first shut-off valve 18 and the second shut-off valve 19 open.

When the compressor 11 is started in this state of the refrigerant circuit 2, the refrigerant gas is aspirated to the compressor 11, compressed to a supercritical state and then supplied to the internal heat exchanger 31 through the switching valve of four ways 12 and the second shut-off valve 19. It will be noted that, at this time, the pressure pulse of the refrigerant is damped by the silencer 20 of type n.

The supercritical refrigerant then heats the room air in the indoor heat exchanger 31 and cools. The supercritical refrigerant that has cooled is sent to the second electric expansion valve 17 through the first shut-off valve 18. The supercritical refrigerant that has been sent to the second electric expansion valve 17 is depressurized to a saturated state and subsequently sent to the first electric expansion valve 15 through the liquid receiver 16. The refrigerant in the saturated state that has been sent to the first electric expansion valve 15 is depressurized, converted into a cooling liquid, then sent to the exchanger of external heat 13, evaporates in the external heat exchanger 13 and becomes refrigerant gas. Next, the refrigerant gas is returned to the compressor 11 through the four-way switching valve 12. In this way, the heating operation is performed.

Features of the air conditioner>

(1) In the air conditioner 1, the type 20 silencer is connected to the discharge pipe of the compressor 11. For this reason, in the air conditioner 1, the pressure pulsation can be reduced sufficiently.

(2) In the air conditioner 1, the silencer of type n 20 is housed in the outdoor unit 10 so that the first silencing space 201 and the second silencing space 202 are arranged one above the other along the vertical direction For this reason, in the air conditioner 1, it is possible to prevent the refrigerating machine oil from accumulating in the silencer 20 type n.3

(3) In silencer 20 type n, the length of the communication path is longer than S1 / 2 (1N-I 1N2) (c / nNmin) 2 and shorter than c / 2ft. For this reason, in the air conditioner 1, the cut-off frequency of the silencer 20 type n can be equal to or less than the minimum number of rotations of the compression mechanism, and a frequency less than the highest target reduction frequency. Ft can be reduced.

<Modifications>

(A) In the air conditioner 1, the n-type silencer 20 which includes the communication path 203 extending along the axial direction of the first silencing space 201 from the lower end of the first silencing space 201 was used and is connected to the upper end of the second silencing space 202, but instead of the silencer of type n 20, a silencer of type n 20a can also be employed such as the example shown in Figure 3. In the silencer 20a type n, a communication path 203a that extends along the axial direction of the first silencing space 201 from the lower end of the first silencing space 201 penetrates the upper end of the second silencing space 202 and is inserted into the second silencing space 202. When the n-type silencer is used 20a, only the communication path can be extended without changing the size of the entire silencer type n. In a type n silencer, the longer the communication path, the greater the effect of reducing the pressure pulse. In other words, the pressure pulsation reduction effect can be made larger without changing the size of the entire type n silencer.

In addition, a silencer 20b of type n can also be used such as the example shown in Figure 4.

In the n-type muffler 20b, a communication path 203b extends along the axis of the first mute space 201 from inside the first mute space 201 and through the lower end of the first mute space 201 outwards, and then penetrates the upper end of the second silencing space 202 and extends into the second silencing space 202. Furthermore, in the silencer of type n 20b, an oil return hole 206 is disposed in the end portion bottom of the communication path 203b within the first squelch space 201. When the silencer of type n 20b is used, the oil of the refrigerating machine can be prevented from accumulating in the silencer of type n, and only the communication path It can be extended a lot without resizing the entire type n silencer. In a type n silencer, the longer the communication path, the greater the effect of reducing the pressure pulse. In other words, oil from the refrigerating machine can be prevented from accumulating in the type n silencer, and the effect of reducing the pressure pulse can be made larger without resizing the entire type n silencer.

(B) In the air conditioner 1, the type 20 silencer 20 was used, the example, where the axes of the first silencing space 201, the second silencing space 202 and the communication path 203 overlap in a straight line and in looking in the vertical direction, but instead of the silencer of type n 20, according to the invention, a silencer of type n 20c, such as the embodiment shown in Figure 5. In the silencer 20c type n, a first silencing space 201c and a second silencing space 202c are arranged side by side, and the axes of both silencing spaces 201c and 202c are along the vertical direction but are not superimposed in a straight line. In addition, in the silencer 20c type n, a communication path 203c is U-shaped and extends from the lower end of the first silencing space 201c to the lower end of the second silencing space 202c. When the silencer type n 20c is used, the entire length of the silencer type n can be shortened. Accordingly, the options for the arrangement of the n-type silencer in the outdoor unit 10 can be extended.

In addition, a silencer 20d of type n can also be used such as the embodiment shown in Figure 6.

The type n 20d silencer is one where a mesh member 207 fills the communication path 203c of the type n silencer 20c shown in Figure 5. When the type 20d silencer is used, reflection waves can be prevented from arising within communication path 203c.

In addition, a silencer 20e type n can also be used such as the embodiment shown in Figure 7.

The silencer of type n 20e is one where a first refrigerant passage 204e and a second refrigerant passage 205e are inserted inside the first silencing space 201c and the second silencing space 202c of the silencer type n 20c shown in Figure 5. When silencer 20e type n is used, it can be ensured that the oil of the refrigerating machine does not accumulate in the first silencer space 201c and in the second silencer space 202c.

(C) In air conditioner 1, silencer 20 type n was used where the axes of the first silencing space 201, the second silencing space 202 and the communication path 203 overlap in a straight line and facing the direction vertical, but instead of the silencer of type n 20, a silencer of type n 20f can also be used such as the example shown in Figure 8. In the silencer of type n 20f, a first silencer space 201c and a second space of Silence 202c are arranged side by side, and the axes of both silence spaces 201c and 202c are in the vertical direction but are not superimposed in a straight line. Furthermore, in the silencer 20f type n, a communication path 203f is U-shaped, penetrates the upper end of the first silencing space 201c from inside the first silencing space 201c, extends to the upper end of the second space of Silence 202c penetrates the upper end of the second silence space 202c and extends into the second silence space 202c. When the silencer of type n 20f is used, the entire length of the silencer of type n can be shortened, the oil of the refrigerating machine can be prevented from accumulating in the first silencing space 201c and the second silencing space 202c, and Only the communication path can be extended for a long time without changing the size of the entire type n silencer. Consequently, the options for the provision of % type silencer in the outdoor unit 10 can be extended, the oil of the refrigerating machine can be prevented from accumulating in the first silencing space 201c and the second silencing space 202c, and the pressure pulsation reduction effect can get bigger without changing the size of the entire% muffler.

(D) In the air conditioner 1, silencer 20 type% was used where the axes of the first silencing space 201, the second silencing space 202 and the communication path 203 overlap in a straight line and facing the direction vertical, but instead of the% 20 type silencer, a% 20g type silencer can also be used as the example shown in Figure 9. In the% 20g type silencer, a first silence space 201c and a second space of Silence 202c are arranged side by side, and the axes of both silence spaces 201c and 202c are along the vertical direction but are not superimposed in a straight line. In addition, in the% 20g type silencer, a communication path 203g is S-shaped and extends from the lower end of the first silencing space 201c to the upper end of the second silencing space 202c. When the% 20g type silencer is used, refrigeration machine oil can be prevented from accumulating in the% type silencer, the entire length of the% type silencer can be shortened and the communication path can be lengthened without changing The size of the entire silencer type%. In a% type silencer, the longer the communication path, the greater the effect of reducing the pressure pulse. In other words, it is possible to prevent the oil of the refrigerating machine from accumulating in the% type silencer, the options for the arrangement of the% type silencer in the outdoor unit 10 can be extended, and the effect of reducing the pulsation of Pressure can be made larger without changing the size of the entire silencer type%. It will be noted that the communication path 203g extending from the lower end of the first mute space 201c can also penetrate the upper end of the second mute space 202c and extend into the second mute space 202c.

(E) In the air conditioner 1, silencer 20 type% was used where the axes of the first silencing space 201, the second silencing space 202 and the communication path 203 are superimposed in a straight line and facing the vertical direction . but instead of the% 20 type silencer, a% 20h type silencer can also be used such as the embodiment shown in Figure 10. In the% 20h silencer, a first mute space 201c and a second mute space 202c are arranged side by side, and the axes of both silencing spaces 201c and 202c are along the vertical direction but are not superimposed in a straight line. In addition, in the silencer 20h type%, a first refrigerant passage 204h is connected to the lower end of the first silencing space 201c, and a second refrigerant passage 205h is connected to the lower end of the second silencing space 202c. Furthermore, in the silencer 20h type%, a communication path 203c is U-shaped and extends from the lower end of the first silencing space 201c to the lower end of the second silencing space 202c. When the% 20h type silencer is used, refrigeration machine oil can be prevented from accumulating in the% type silencer, and the entire length of the% type silencer can be shortened. Accordingly, it is possible to prevent the oil from the refrigerating machine from accumulating in the% type silencer, and the options for the arrangement of the% type silencer in the outdoor unit 10 can be extended.

(F) In the air conditioner 1, silencer 20 type% was used where the axes of the first silencing space 201, the second silencing space 202 and the communication path 203 overlap in a straight line and facing the direction vertical, but instead of the% 20 type silencer, a% 20i type silencer can also be used, such as an example shown in Figure 11. The% 20 type silencer is housed in the outdoor unit 10, so that the axes of a first squelch space 201i and a second squelch space 202i overlap in a straight line and face the horizontal direction. In addition, in the silencer 20i type%, a first refrigerant passage 204 is connected to the lower part of the outer end of the first silencing space 201i, and a second refrigerant passage 205 is connected to the lowest part of the external end of the second mute space 202i. In addition, in the silencer 20i type%, a communication path 203i interconnects the lower part of the inner end of the first mute space 201i and the lower part of the inner end of the second mute space 202i. When the% 20i type silencer is used, it is possible to prevent the refrigerating machine oil from accumulating in the% type silencer.

In addition, a silencer 20j of type% can also be used as an example shown in Figure 12. In the silencer 20j type%, a communication path 203j penetrates the lower part of the inner end of the first silencer space 201i and the lower part of the inner end of the second mute space 202i and extends into the second mute space 202i from the inside of the first mute space 201i. When the% 20j silencer is used, refrigeration machine oil can be prevented from accumulating in the% silencer, and the communication path can be made longer without changing the size of the entire% silencer. In a% type silencer, the longer the communication path, the greater the effect of reducing the pressure pulse. In other words, it is possible to prevent the oil from the refrigerating machine from accumulating in the% type silencer, and the effect of reducing the pressure pulse can be made larger without changing the size of the entire% type silencer.

(G) In the air conditioner 1, silencer 20 type% was used where the axes of the first silencing space 201, the second silencing space 202 and the communication path 203 overlap in a straight line and facing the direction vertical, but instead of the% 20 type silencer, a% 20k type silencer can also be used, such as the embodiment shown in Figure 13. The% 20k type silencer is housed in the outdoor unit 10, so that the axes of a first silencing space 201i, a second silencing space 202i and a communication path 203k overlap in a straight line and are oriented in a horizontal direction. In addition, in the silencer 20k type%, a first oil drain passage 206k extends from the lower end of the first silencing space 201i, and a second oil drain passage 207k extends from the lower end of the second silence space 202i. It will be noted that the first oil drain passage 206k and the second oil drain passage 207k are joined midway and connected to the suction tube of the compressor 11 through a capillary. When the% 20k type silencer is used, the refrigerant machine oil can be prevented from accumulating in the% type silencer. It will be noted that the communication path 203k can also penetrate the center of the inner end of the first mute space 201i and the center of the second mute space 202i and extend into the second mute space 202i from inside the first space of 201i silencing.

(H) In the air conditioner 1, the% 20 silencer was connected to the discharge tube of the compressor 11, but instead, the% 20 silencer can also be connected to the discharge tube and the tube compressor suction 11.

(I) In the air conditioner 1, although it was not touched, when the containers such as an oil separator, an accumulator and a liquid receiver are present in the refrigerant circuit 2, the spaces within them can also be used as the first mute space or second mute space. In this way, the refrigerant circuit 2 can be simplified.

(J) In the air conditioner 1, the% 20 silencer was used in which the two silencing spaces 201 and 202 are present, but instead, a% type silencer can also be used where three or more Silence spaces are present. In this way, an even greater pressure pulsation reduction effect can be expected.

(K) In the air conditioner 1, an inverter rotary type compressor was used, but instead, a constant speed rotary compressor can also be used.

(L) In air conditioner 1, carbon dioxide was used as a refrigerant, but instead, a refrigerant such as r 22 or R410A can also be used. Incidentally, when the pressure is 1.5 MPa, the density becomes 56.4 kg / m3 and the speed of sound becomes 169 m / sec. In addition, when the pressure is 2.4 MPa, the density becomes 83.3 kg / m3 and the speed of sound becomes 174 m / sec.

(M) In the% type silencer 20, the shape of the first silencing space 201 was cylindrical, but in the present invention, the shape of the first silencing space 201 is not particularly limited and can also be a cuboid or a regular hexahedron. , for example.

(N) In the% 20 silencer, the shape of the second silencing space 202 was cylindrical, but in the present invention, the shape of the second silencing space 202 is not particularly limited and can also be a cuboid or a regular hexahedron. , for example.

(O) In silencer 20 type%, the first silencing space 201 and the second silencing space 202 were configured to have the same shape and volume, but in the present invention, the shapes and volumes of the first space of silencing 201 and the second silencing space 202 may also be different.

(P) In the% 20 silencer, the shape of the communication path 203 was cylindrical, but in the present invention, the shape of the communication path 203 is not particularly limited and can also be a cuboid, for example.

Industrial applicability

The refrigeration system according to the present invention has the characteristic that it can sufficiently reduce the pressure pulsation even when carbon dioxide or the like is used as a refrigerant, whereby the refrigeration system is suitable for a refrigeration system employing carbon dioxide. carbon or similar as a refrigerant.

Claims (6)

1. A cooling system, comprising: a first refrigerant passage (204, 204e, 204h); a type n silencer (20c, 20d, 20e, 20h) that has a first silencing space (201c) communicating with the first refrigerant passage (204), a second silencing space (202c) arranged side by side with the first silencing space (201c), and a communication path (203c) extending from the lower end of the first silencing space (201c) to the lower end of the second mute space (202c) through the outside of the first mute space (201c) and communicates with the second mute space (202c); a second refrigerant passage (205, 205e, 205h) that communicates with the second silencing space (202c); Y a compressor (11), characterized in that the cooling system further comprises an outdoor unit (10), a four-way switching valve (12), an external heat exchanger (13) and an internal heat exchanger (31), wherein the n-type silencer (20c, 20d, 20e, 20h) is disposed between a discharge side of the compressor (11) and the four-way switching valve (12); wherein a discharge path of the compressor (11) is connected to the first silencing space (201c) through the first refrigerant passage (204), and a heat transfer path of the external heat exchanger (13) or the Internal heat exchanger (31) is connected to the second silencing space (202c) through the second refrigerant passage (205). 2. The cooling system according to claim 1, wherein The first refrigerant passage (204e) is inserted from the upper end of the first silencing space and extends into the first silencing space. 3. The cooling system according to claim 1 or claim 2, wherein The second refrigerant passage (205e) is inserted from the upper end of the second silencing space and extends into the second silencing space. 4. The cooling system according to claim 1, wherein the first refrigerant passage (204) extends from the upper end of the first silencing space (201c), and the second refrigerant passage (205) extends from the upper end of the second silencing space (202c). 5. The cooling system according to claim 1, wherein the first refrigerant passage (204h) extends from the lower end of the first silencing space, and the second refrigerant passage (205h) extends from the lower end of the second silencing space. 6. The cooling system according to any one of claims 1 to 5, wherein a mesh member (207) fills the communication path (203c).