CN103635752B

CN103635752B - Outdoor machine of refrigeration device

Info

Publication number: CN103635752B
Application number: CN201280030911.8A
Authority: CN
Inventors: 冈本哲也; 古庄和宏; 杨国忠; 岩田育弘; 藤野宏和; 吉冈俊
Original assignee: Daikin Industries Ltd
Current assignee: Daikin Industries Ltd
Priority date: 2011-06-30
Filing date: 2012-06-28
Publication date: 2015-04-01
Anticipated expiration: 2032-06-28
Also published as: EP2728270A1; TR201907629T4; EP2728270B1; AU2012277182B2; US20140102131A1; JP2013015228A; JP5257491B2; CN103635752A; ES2727860T3; WO2013001816A1; EP2728270A4

Abstract

With an outdoor unit (3), first through third intermediate heat exchangers (41, 42, 43) and an outdoor heat exchanger (44) are arranged in an upright state along an intake port (123) of an outdoor casing (121), and the outdoor heat exchanger (44) is arranged above the first through third intermediate heat exchangers (41, 42, 43).

Description

The off-premises station of refrigerating plant

Technical field

The present invention relates to a kind of off-premises station of refrigerating plant, particularly relate to a kind of refrigerating plant carrying out multiple compression kind of refrigeration cycle.

Background technology

Up to now, carry out one of refrigerating plant of multiple compression kind of refrigeration cycle as utilization at the cold-producing medium of supercritical region work, exist a kind of as Patent Document 1, the aircondition that carries out two-stage compression kind of refrigeration cycle with carbon dioxide as cold-producing medium.This aircondition allows rear class side compression member suck this cold-producing medium again after cooling the cold-producing medium sprayed from the compression member of prime side with intercooler, thus reduce the temperature of the cold-producing medium from the ejection of rear class side compression member, reduce the radiation loss of outdoor heat converter.

In the aircondition shown in patent document 1, as shown in figure 20, intercooler a and heat source side heat exchanger b is incorporated in thermal source unit c.In thermal source unit c, be provided with intercooler a and heat source side heat exchanger b on its lateral surface.Further, intercooler a is arranged in the top of heat source side heat exchanger b.Heat source side fan is provided with above intercooler a.

Patent document 1: Japanese Laid-Open Patent Publication Laid-Open 2009-150641 publication

Summary of the invention

-invent technical problem to be solved-

The formation shown in above-mentioned patent document 1 be to suck from side after air blow out air upward, so-called upper blowing type thermal source unit c, as shown in figure 21, because the air velocity of top is faster than below, the heat-exchange capacity being thus arranged on the intercooler a of top is higher.For this reason, in thermal source unit c, miniaturization can be sought by intercooler a being arranged on top.

At this, the pressure of the cold-producing medium that the pressure ratio of the cold-producing medium flowed in intercooler a flows in heat source side heat exchanger b is low, and the density of the cold-producing medium that the density ratio of the cold-producing medium thus flowed in intercooler a flows in heat source side heat exchanger b is little.For this reason, if the mass flow of the cold-producing medium flowed in intercooler a and heat source side heat exchanger b is respectively roughly equal, then the volume flow of the cold-producing medium in intercooler a will be greater than the volume flow of the cold-producing medium flowed in heat source side heat exchanger b.Even if the quantity of the refrigerant path in intercooler a and heat source side heat exchanger b is roughly equal, also be greater than the refrigerant flow rates in heat source side heat exchanger b due to the flow velocity of the cold-producing medium flowed in intercooler a, the pressure loss of the cold-producing medium thus in intercooler a is greater than heat source side heat exchanger b.

Thus, as mentioned above, if make intercooler a realize miniaturization, refrigerant path quantity is reduced, the problem that the pressure loss with regard to there will be cold-producing medium in intercooler a increases.On the other hand, if suppress the pressure loss of cold-producing medium to increase and make intercooler a realize maximizing, the problem that thermal source unit c maximizes will be produced.

The present invention completes just in view of the above problems, its object is to: suppress the pressure loss of cold-producing medium in intercooler to increase, suppress the maximization of thermal source unit simultaneously.

-in order to technical solution problem technical scheme-

The present invention is configured to: be arranged in by outdoor heat exchange department 44,162 in the off-premises station of refrigerating plant than on intermediate heat exchange part 41,42,43,161 position by the top.

The invention of first aspect relates to a kind of off-premises station of refrigerating plant, and the off-premises station of this refrigerating plant comprises multi-stage compression portion 20, 150, intermediate heat exchange part 41, 42, 43, 161, outdoor heat exchange department 44, 162 and casing 121, 163, this multi-stage compression portion 20, 150 have the multiple compressing mechanisms 21 ~ 24 be one another in series, 151, 152, and senior side compressing mechanism 22, 23, 24, 152 suck rudimentary side compressing mechanism 21, 22, 23, compress after 151 cold-producing mediums sprayed, this intermediate heat exchange part 41, 42, 43, 161 are arranged on two adjacent described compressing mechanisms 21, 22, 23, 24, 151, between 152, make from rudimentary side compressing mechanism 21, 22, 23, 151 flow to senior side compressing mechanism 22, 23, 24, the cold-producing medium of 152 and outdoor air carry out heat exchange and cool this cold-producing medium, this outdoor heat exchange department 44, 162 make from highest side compressing mechanism 24, cold-producing medium and the outdoor air of 152 ejections carry out heat exchange, at this casing 121, the side of 163 is formed with the suction inlet 123 of air, 164, and at this casing 121, the upper surface of 163 is formed with the blow-off outlet 124 of air, 165, at this casing 121, described compressing mechanism 21 ~ 24 is accommodated with in 163, 151, 152, intermediate heat exchange part 41, 42, 43, 161 and outdoor heat exchange department 44, 162.Described intermediate heat exchange part 41,42,43,161 and described outdoor heat exchange department 44,162 are arranged with the state erected along the suction inlet 123,164 of described casing 121,163, and described outdoor heat exchange department 44,162 is arranged in than on described intermediate heat exchange part 41,42,43,161 position by the top.

In the invention of described first aspect, compress after the cold-producing medium that multi-stage compression portion 20,150 middle-and-high-ranking side compressing mechanism 22,23,24,152 suction rudimentary side compressing mechanism 21,22,23,151 sprays.Intermediate heat exchange part 41,42,43,161 is arranged between two compressing mechanisms 21,22,23,24,151,152 adjacent in multiple compressing mechanism 21 ~ 24,151,152.Further, intermediate heat exchange part 41,42,43,161 makes to flow to the cold-producing medium of senior side compressing mechanism 22,23,24,152 from rudimentary side compressing mechanism 21,22,23,151 and outdoor air carries out heat exchange and cools this cold-producing medium.Outdoor heat exchange department 44,162 makes the cold-producing medium of ejection from highest side compressing mechanism 24,152 and outdoor air carry out heat exchange.

Be formed with the suction inlet 123,164 of air in the side of casing 121,163, and be formed with the blow-off outlet 124,165 of air at the upper surface of this casing 121,163.Further, casing 121,163 by compressing mechanism 21 ~ 24,151,152, intermediate heat exchange part 41,42,43,161 and outdoor heat exchange department 44,162 be accommodated in inside.In the inside of casing 121,163, the state erected along suction inlet 123,164 is provided with outdoor heat exchange department 44,162 and intermediate heat exchange part 41,42,43,161, and outdoor heat exchange department 44,162 is arranged in than on intermediate heat exchange part 41,42,43,161 position by the top.

Flow to above casing 121,163 after the air being inhaled into casing 121,163 inside from suction inlet 123,164 carries out heat exchange intermediate heat exchange part 41,42,43,161 and outdoor heat exchange department 44,162 and be blown from blow-off outlet 124,165 again.

At this, off-premises station of the present invention is configured to suction inlet 123,164 from the side and sucks from blow-off outlet 124,165 blow out air, so-called upper blowing type upward after air, and the air velocity thus above suction inlet 123,164 is than fast below it.In intermediate heat exchange part 41,42,43,161, the pressure of the cold-producing medium that the pressure ratio of the cold-producing medium of flowing flows in outdoor heat exchange department 44,162 is low, and thus in intermediate heat exchange part 41,42,43,161, the density of the cold-producing medium of flowing is less than the density of the cold-producing medium of flowing in outdoor heat exchange department 44,162.For this reason, if in intermediate heat exchange part 41,42,43,161 and outdoor heat exchange department 44,162, the mass flow of the cold-producing medium of flowing is roughly equal respectively, then in intermediate heat exchange part 41,42,43,161, the volume flow of cold-producing medium will be greater than the volume flow of the cold-producing medium of flowing in outdoor heat exchange department 44,162.Even if the quantity of the refrigerant path in intermediate heat exchange part 41,42,43,161 and outdoor heat exchange department 44,162 is roughly equal, also be greater than the refrigerant flow rates in outdoor heat exchange department 44,162 due to the flow velocity of cold-producing medium of flowing in intermediate heat exchange part 41,42,43,161, the pressure loss of the cold-producing medium thus in intermediate heat exchange part 41,42,43,161 is greater than the pressure loss of cold-producing medium in outdoor heat exchange department 44,162.

In outdoor heat exchange department 44,162 above being arranged at air velocity in casing 121,163 and being higher, because heat exchange performance is higher, its size thus can be made to realize miniaturized.On the other hand, in the intermediate heat exchange part 41,42,43,161 being arranged at the below that air velocity is lower in casing 121,163, heat-exchange capacity is lower.For this reason, to increase heat exchange amount, intermediate heat exchange part 41,42,43,161 will than be arranged on top time large.

Therefore, off-premises station can not become maximization due to the maximization of outdoor heat exchange department 44,162 and intermediate heat exchange part 41,42,43,161.

If make intermediate heat exchange part 41,42,43,161 realize maximizing, in intermediate heat exchange part 41,42,43,161, the quantity of refrigerant path will increase.For this reason, in intermediate heat exchange part 41,42,43,161, in each bar refrigerant path, the flow velocity of cold-producing medium reduces, the pressure loss reduction of cold-producing medium when by each bar refrigerant path.Because in intermediate heat exchange part 41,42,43,161, the flow velocity of the cold-producing medium of flowing is originally higher, if thus the increase of refrigerant path quantity makes flow velocity reduce, therefore and greatly the pressure loss will reduce.

On the other hand, if outdoor heat exchange department 44,162 realizes miniaturized, in outdoor heat exchange department 44,162, the quantity of refrigerant path will reduce.If the quantity of refrigerant path reduces, in each bar refrigerant path, the flow velocity of cold-producing medium will be accelerated, the pressure loss increase of cold-producing medium when by each bar refrigerant path.

But the flow velocity of the cold-producing medium of flowing is originally lower in outdoor heat exchange department 44,162, though thus flow velocity because refrigerant path quantity reduces, some is accelerated, it is also smaller for resulting from this increase of the pressure loss.

Therefore, when being arranged on above intermediate heat exchange part 41,42,43,161 by outdoor heat exchange department 44,162, the maximization of off-premises station can be suppressed, the pressure loss of cold-producing medium in intermediate heat exchange part 41,42,43,161 can also be reduced simultaneously.

The invention of second aspect is such, in the invention of described first aspect, described multi-stage compression portion 20 has the compressing mechanism 21 ~ 24 of more than three, and highest side intermediate heat exchange part 43 is arranged in than other intermediate heat exchange part 41,42 by the top and than on described outdoor heat exchange department 44 position on the lower.

In the invention of described second aspect, multi-stage compression portion 20 has the compressing mechanism 21 ~ 24 of more than three, compresses after the cold-producing medium that senior side compressing mechanism 22,23,24 suction rudimentary side compressing mechanism 21,22,23 sprays.For this reason, be provided with multiple intermediate heat exchange part 41,42,43, highest side intermediate heat exchange part 43 is arranged on than on other intermediate heat exchange part 41,42 position by the top.Highest side intermediate heat exchange part 43 is also arranged on than on outdoor heat exchange department 44 position on the lower.

The pressure of cold-producing medium flow in other intermediate heat exchange part 41,42 due to the pressure ratio of cold-producing medium of flowing in highest side intermediate heat exchange part 43 is high, and the density of the cold-producing medium that the density ratio of the cold-producing medium thus flowed in other intermediate heat exchange part 41,42 flows in highest side intermediate heat exchange part 43 is little.For this reason, if in other intermediate heat exchange part 41,42 and highest side intermediate heat exchange part 43, the mass flow of the cold-producing medium of flowing is roughly equal respectively, then in other intermediate heat exchange part 41,42, the volume flow of cold-producing medium will be greater than the volume flow of the cold-producing medium of flowing in highest side intermediate heat exchange part 43.Even if the quantity of the refrigerant path in other intermediate heat exchange part 41,42 and highest side intermediate heat exchange part 43 is roughly equal, also be greater than the refrigerant flow rates in highest side intermediate heat exchange part 43 due to the flow velocity of cold-producing medium of flowing in other intermediate heat exchange part 41,42, the pressure loss of the cold-producing medium thus in other intermediate heat exchange part 41,42 is greater than the pressure loss of cold-producing medium in highest side intermediate heat exchange part 43.

In senior side intermediate heat exchange part 43 above being arranged at air velocity in casing 121 and being higher, because heat exchange performance is higher, its size thus can be made to realize miniaturized.On the other hand, in other intermediate heat exchange part 41,42 being arranged at the below that in casing 121, air velocity is lower, heat-exchange capacity is lower.For this reason, to increase heat exchange amount, other intermediate heat exchange part 41,42 will than be arranged on top time large.

Therefore, off-premises station can not become maximization due to the maximization of senior side intermediate heat exchange part 43 and other intermediate heat exchange part 41,42.

If make other intermediate heat exchange part 41,42 realize maximizing, in other intermediate heat exchange part 41,42, the quantity of refrigerant path will increase.For this reason, in other intermediate heat exchange part 41,42, in each bar refrigerant path, the flow velocity of cold-producing medium reduces, the pressure loss reduction of cold-producing medium when by each bar refrigerant path.Because in other intermediate heat exchange part 41,42, the flow velocity of the cold-producing medium of flowing is originally higher, if thus the increase of refrigerant path quantity makes flow velocity reduce, therefore and greatly the pressure loss will reduce.

On the other hand, if senior side intermediate heat exchange part 43 realizes miniaturization, in senior side intermediate heat exchange part 43, the quantity of refrigerant path will reduce.If the quantity of refrigerant path reduces, in each bar refrigerant path, the flow velocity of cold-producing medium will be accelerated, the pressure loss increase of cold-producing medium when by each bar refrigerant path.

But the flow velocity of the cold-producing medium of flowing is originally lower in senior side intermediate heat exchange part 43, though thus flow velocity because refrigerant path quantity reduces, some is accelerated, it is also smaller for resulting from this increase of the pressure loss.

Therefore, when senior side intermediate heat exchange part 43 being arranged on above other intermediate heat exchange part 41,42, the maximization of off-premises station can be suppressed, the pressure loss of cold-producing medium in other intermediate heat exchange part 41,42 can also be reduced simultaneously.

The invention of the third aspect is such, in the invention of described second aspect, multiple described intermediate heat exchange part 41,42,43 is arranged to: the pressure flowing into the cold-producing medium of described intermediate heat exchange part is higher, and this intermediate heat exchange part is located in position more by the top.

In the invention of the third aspect, multiple described intermediate heat exchange part 41,42,43 is arranged to: the pressure flowing into the cold-producing medium of described intermediate heat exchange part is higher, and this intermediate heat exchange part is located in position more by the top.

In the intermediate heat exchange part 42 that flowed into refrigerant pressure is higher, the density of its cold-producing medium is greater than the refrigerant density in the lower intermediate heat exchange part 41 of flowed into refrigerant pressure.For this reason, if in low pressure side intermediate heat exchange part 41 and high pressure side intermediate heat exchange part 42, the mass flow of the cold-producing medium of flowing is roughly equal respectively, then in low pressure side intermediate heat exchange part 41, the volume flow of cold-producing medium will be greater than the volume flow of the cold-producing medium of flowing in high pressure side intermediate heat exchange part 42.Even if the quantity of the refrigerant path in low pressure side intermediate heat exchange part 41 and high pressure side intermediate heat exchange part 42 is roughly equal, also be greater than the refrigerant flow rates in high pressure side intermediate heat exchange part 42 due to the flow velocity of cold-producing medium of flowing in low pressure side intermediate heat exchange part 41, the pressure loss of the cold-producing medium thus in low pressure side intermediate heat exchange part 41 is greater than the pressure loss of cold-producing medium in high pressure side intermediate heat exchange part 42.

In high pressure side intermediate heat exchange part 42 above being arranged at air velocity in casing 121 and being higher, because heat exchange performance is higher, its size thus can be made to realize miniaturized.On the other hand, in the low pressure side intermediate heat exchange part 41 being arranged at the below that in casing 121, air velocity is lower, heat-exchange capacity is lower.For this reason, to increase heat exchange amount, low pressure side intermediate heat exchange part 41 will than be arranged on top time large.

Therefore, off-premises station can not become maximization due to the maximization of high pressure side intermediate heat exchange part 42 and low pressure side intermediate heat exchange part 41.

If make low pressure side intermediate heat exchange part 41 realize maximizing, in low pressure side intermediate heat exchange part 41, the quantity of refrigerant path will increase.For this reason, in low pressure side intermediate heat exchange part 41, in each bar refrigerant path, the flow velocity of cold-producing medium reduces, the pressure loss reduction of cold-producing medium when by each bar refrigerant path.Because in low pressure side intermediate heat exchange part 41, the flow velocity of the cold-producing medium of flowing is originally higher, if thus the increase of refrigerant path quantity makes flow velocity reduce, therefore and greatly the pressure loss will reduce.

On the other hand, if high pressure side intermediate heat exchange part 42 realizes miniaturization, in high pressure side intermediate heat exchange part 42, the quantity of refrigerant path will reduce.If the quantity of refrigerant path reduces, in each bar refrigerant path, the flow velocity of cold-producing medium will be accelerated, the pressure loss increase of cold-producing medium when by each bar refrigerant path.

But the flow velocity of the cold-producing medium of flowing is originally lower in high pressure side intermediate heat exchange part 42, though thus flow velocity because refrigerant path quantity reduces, some is accelerated, it is also smaller for resulting from this increase of the pressure loss.

Therefore, when high pressure side intermediate heat exchange part 42 being arranged on above low pressure side intermediate heat exchange part 41, the maximization of off-premises station can be suppressed, the pressure loss of cold-producing medium in low pressure side intermediate heat exchange part 41 can also be reduced simultaneously.

The invention of fourth aspect is such, in described first to the third aspect either side invention in, described intermediate heat exchange part 41,42,43,161 comprises many flat tubes 231 and multiple fin 235,235, this many flat tubes 231 side is arranged above and below opposite to each other and is formed with many fluid passages 232 extended along pipe range direction in inside, the plurality of fin 235,235 will be divided into air and flows through many ventilation path between adjacent described flat tube 231.

In the invention of described fourth aspect, flat tube 231 and fin 235,235 are respectively provided with multiple.Fin 235,235 is provided with between the flat tube 231 be arranged above and below.In intermediate heat exchange part 41,42,43,161, air passes through between the flat tube 231 be arranged above and below, and the fluid flowed in this air and fluid passage 232 in flat tube 231 carries out heat exchange.

In intermediate heat exchange part 41,42,43,161, because flowing resistance reduces, the flow velocity of thus flowed air is accelerated.Also because the heat transfer area of cold-producing medium increases by flat tube 231, therefore the heat exchange performance of cold-producing medium is improved.For this reason, the COP (coefficient of performance) of refrigerating plant improves.Because the caliber of flat tube 231 is less than existing heat-transfer pipe, so velocity in pipes increases.For this reason, increased by the pressure loss of the cold-producing medium of fluid passage 232.

But in the intermediate heat exchange part 41,42,43,161 being arranged at the below that air velocity is lower in casing 121,163, heat-exchange capacity is lower.For this reason, to increase heat exchange amount, intermediate heat exchange part 41,42,43,161 will than be arranged on top time large.If intermediate heat exchange part increases, in intermediate heat exchange part 41,42,43,161, the quantity of fluid passage 232 will increase, thus in intermediate heat transformation component 41,42,43,161, in each bar fluid passage 232, the flow velocity of cold-producing medium reduces, the pressure loss reduction of cold-producing medium when by each bar fluid passage 232.

Therefore, even if the increase causing refrigerant pressure loss to increase due to the caliber path using flat tube 231 to cause also is smaller.

The invention of the 5th aspect is such, in the invention of described fourth aspect, described outdoor heat exchange department 44,162 comprises many flat tubes 231 and multiple fin 235,235, this many flat tubes 231 side is arranged above and below opposite to each other and is formed with many fluid passages 232 extended along pipe range direction in inside, the plurality of fin 235,235 will be divided into air and flows through many ventilation path between adjacent described flat tube 231.

In invention in the described 5th, flat tube 231 and fin 235,235 are respectively provided with multiple.Fin 235,235 is provided with between the flat tube 231 be arranged above and below.In outdoor heat exchange department 44,162, air passes through between the flat tube 231 be arranged above and below, and the fluid flowed in this air and fluid passage 232 in flat tube 231 carries out heat exchange.

In outdoor heat exchange department 44,162, because flowing resistance reduces, the flow velocity of thus flowed air is accelerated.Also because the heat transfer area of cold-producing medium increases by flat tube 231, therefore the heat exchange performance of cold-producing medium is improved.For this reason, the COP (coefficient of performance) of refrigerating plant improves.Because the caliber of flat tube 231 is less than existing heat-transfer pipe, so velocity in pipes increases.For this reason, increased by the pressure loss of the cold-producing medium of fluid passage 232.

But the flow velocity of the cold-producing medium of flowing is originally lower in outdoor heat exchange department 44,162, even if thus make flow velocity because adopting flat tube 231 to make caliber realize path, some is accelerated, and it is also smaller for resulting from this increase of the pressure loss.

-invention effect-

According to the invention of described first aspect, because outdoor heat exchange department 44,162 is arranged on the top that in casing 121,163, air velocity is higher, so the heat exchange performance of outdoor heat exchange department 44,162 can be improved.Also because outdoor heat exchange department 44,162 lower for refrigerant flow rates is arranged on the top that in casing 121,163, air velocity is higher, so refrigerant pressure loss can not be made with increasing to realize the miniaturization of outdoor heat exchange department 44,162.

On the other hand, increase the quantity of refrigerant path by intermediate heat exchange part 41,42,43,161 being arranged on below that in casing 121,163, air velocity is lower, thus can reliably prevent the pressure loss of cold-producing medium in intermediate heat exchange part 41,42,43,161 from increasing.

As mentioned above, miniaturization is realized by the outdoor heat exchange department 44,162 of more difficult for the pressure loss of cold-producing medium increase being arranged on top, thus the size of off-premises station can be suppressed to increase, the pressure loss of cold-producing medium in intermediate heat exchange part 41,42,43,161 can also be suppressed simultaneously.

According to the invention of described second aspect, because highest side intermediate heat exchange part 43 is arranged on the top that in casing 121, air velocity is higher, so the heat exchange performance of highest side intermediate heat exchange part 43 can be improved.Also because highest side intermediate heat exchange part 43 slower for refrigerant flow rates is arranged on the top that in casing 121, air velocity is higher, so refrigerant pressure loss can not be made with increasing to realize the miniaturization of highest side intermediate heat exchange part 43.

On the other hand, by by refrigerant flow rates faster other intermediate heat exchange part 41,42 be arranged on the quantity that below that in casing 121, air velocity is lower increases refrigerant path, thus can reliably prevent the pressure loss of cold-producing medium in other intermediate heat exchange part 41,42 from increasing.

As mentioned above, miniaturization is realized by the highest side intermediate heat exchange part 43 of more difficult for the pressure loss of cold-producing medium increase being arranged on top, thus the size of off-premises station can be suppressed to increase, the pressure loss of cold-producing medium in other intermediate heat exchange part 41,42 can also be suppressed simultaneously.

According to the invention of the described third aspect, because high pressure side intermediate heat exchange part 42 is arranged on the top that in casing 121, air velocity is higher, so the heat exchange performance of high pressure side intermediate heat exchange part 42 can be improved.Also because high pressure side intermediate heat exchange part 42 slower for refrigerant flow rates is arranged on the top that in casing 121, air velocity is higher, so refrigerant pressure loss can not be made with increasing to realize the miniaturization of high pressure side intermediate heat exchange part 42.

On the other hand, by by refrigerant flow rates faster low pressure side intermediate heat exchange part 41 be arranged on the quantity that below that in casing 121, air velocity is lower increases refrigerant path, thus can reliably prevent the pressure loss of cold-producing medium in low pressure side intermediate heat exchange part 41 from increasing.

As mentioned above, miniaturization is realized by the high pressure side intermediate heat exchange part 42 of more difficult for the pressure loss of cold-producing medium increase being arranged on top, thus the size of off-premises station can be suppressed to increase, the pressure loss of cold-producing medium in low pressure side intermediate heat exchange part 41 can also be suppressed simultaneously.

According to the invention of described fourth aspect, because include the many flat tubes 231 and multiple fin 235,235 that are formed with many fluid passages 232, so can flowing resistance be reduced.For this reason, the air velocity flowed in ventilation path increases.Also because the heat transfer area of cold-producing medium increases by flat tube 231, thus the heat exchange performance of cold-producing medium is improved.For this reason, the COP (coefficient of performance) of refrigerating plant can be improved.

According to the invention of described 5th aspect, because include the many flat tubes 231 and multiple fin 235,235 that are formed with many fluid passages 232, so can flowing resistance be reduced.For this reason, the air velocity flowed in ventilation path increases.Also because the heat transfer area of cold-producing medium increases by flat tube 231, thus the heat exchange performance of cold-producing medium is improved.For this reason, the COP (coefficient of performance) of refrigerating plant can be improved.

Accompanying drawing explanation

Fig. 1 is the piping diagram of the cooling operation of the refrigerant loop represented involved by first embodiment of the invention.

Fig. 2 is the enthalpy-entropy diagram of the refrigerant loop involved by first embodiment of the invention.

Fig. 3 is the figure of the outdoor unit represented involved by first embodiment of the invention.

Fig. 4 is the schematic top plan view of the outdoor unit involved by first embodiment of the invention.

Fig. 5 is the sectional view at V-V line place in Fig. 4.

Fig. 6 is the figure representing air velocity distribution situation in the outdoor machine shell involved by first embodiment of the invention.

Fig. 7 is the piping diagram heating running of the refrigerant loop represented involved by first embodiment of the invention.

Fig. 8 is the piping diagram of the cooling operation of the refrigerant loop represented involved by second embodiment of the invention.

Fig. 9 is the enthalpy-entropy diagram of the refrigerant loop involved by second embodiment of the invention.

Figure 10 is the piping diagram of the cooling operation of the refrigerant loop represented involved by third embodiment of the invention.

Figure 11 is the enthalpy-entropy diagram of the refrigerant loop involved by third embodiment of the invention.

Figure 12 is the figure of the outdoor unit represented involved by third embodiment of the invention.

Figure 13 is the piping diagram heating running of the refrigerant loop represented involved by third embodiment of the invention.

Figure 14 is the schematic diagram of the outdoor unit involved by variation representing third embodiment of the invention.

Figure 15 is the enlarged drawing of flat tube in the heat exchanger involved by variation of third embodiment of the invention and fin.

Figure 16 is the schematic diagram of the outdoor unit represented involved by other embodiment.

Figure 17 is the enlarged drawing of flat tube in the heat exchanger involved by other embodiment and fin.

Figure 18 is the schematic diagram of the structure of the outdoor unit represented involved by reference example, and (A) represents the layout example of outdoor heat exchanger group, and (B) represents the wind speed profile situation corresponding with outdoor heat exchanger group.

Figure 19 is the sectional view of the outdoor heat exchanger group involved by reference example.

Figure 20 is the figure of the outdoor unit represented involved by existing example.

Figure 21 is the schematic diagram of the structure of the outdoor unit represented involved by existing example, and (A) represents the layout example of outdoor heat exchanger group, and (B) represents the wind speed profile situation corresponding with outdoor heat exchanger group.

Detailed description of the invention

Below, with reference to the accompanying drawings embodiments of the present invention are described in detail.

First embodiment > of < invention

-refrigerant loop of aircondition-

As shown in Figure 1, the aircondition 1 involved by the first embodiment of the present invention is described.This aircondition 1 comprises the refrigerant loop 10 being configured to reversibly switch flow of refrigerant, and is configured to carry out cold and hot switching.This aircondition 1 comprises setting outdoor unit 3 without and the indoor units 2 be arranged within doors.The refrigerant loop 10 of above-mentioned aircondition 1 is that the indoor loop 12 that the outdoor loop 11 that has of outdoor unit 3 and indoor units 2 have is formed by connecting by gas side connecting pipe 13 and hydraulic fluid side connecting pipe 14.Carbon dioxide has been enclosed (hereinafter referred to as cold-producing medium in this refrigerant loop 10.), and be configured to: this cold-producing medium is circulated in refrigerant loop 10, thus can multiple compression supercritical refrigeration cycle be carried out.

The outdoor loop > of <

As shown in Figure 1, in described outdoor loop 11, be connected with four-stage compressor 20, outdoor heat exchanger group 40, the first to the four four-way change-over valve 93,94,95,96, the first to the three supercooling heat exchanger 100,101,102, the first to the five expansion valve 80 ~ 84, decompressor 87 and gas-liquid separator 88.Described outdoor heat exchanger group 40 comprises the first to the three intermediate heat exchanger 41,42,43 and outdoor heat converter 44.

In addition, described outdoor heat converter 44 forms outdoor heat exchange department involved in the present invention, and the first to the three intermediate heat exchanger 41,42,43 forms intermediate heat exchange part involved in the present invention.First and second intermediate heat exchangers 41,42 form other intermediate heat exchange part involved in the present invention, and the 3rd intermediate heat exchanger 43 forms highest side intermediate heat exchange part involved in the present invention.

Except above-mentioned inscape, be also connected with four gs-oil separators 89,90,91,92, current divider 18, capillary 15, bridge circuit 17 and check-valves CV1 ~ CV13.

In first embodiment of the invention, by switching the first to the four four-way change-over valve 93,94,95,96, thus the running of described refrigerant loop 10 is switched to cooling operation or heats running.

Described four-stage compressor 20 comprises the first to the four compression unit 21,22,23,24, forms multi-stage compression portion involved in the present invention.Be connected with the first to the four bleed pipe 25,26,27,28 in the ejection side of the first to the four compression unit 21,22,23,24, be connected with the first to the four suction line 29,30,31,32 in the suction side of the first to the four compression unit 21,22,23,24.In each compression unit 21,22,23,24, till the gaseous refrigerant sucked is compressed to authorized pressure, then this cold-producing medium is sprayed from each bleed pipe 25,26,27,28 by each suction line 29,30,31,32.

First valve port of described first four-way change-over valve 93 is connected with the first bleed pipe 25 of the first compression unit 21, second valve port of this first four-way change-over valve 93 is connected with the end side of collecting fitting 67,3rd valve port of this first four-way change-over valve 93 is connected with the end side of the first intermediate heat exchanger 41, and the 4th valve port of this first four-way change-over valve 93 is connected with the second suction line 30 of the second compression unit 22.This first four-way change-over valve 93 to be communicated with the 3rd valve port and the first state (by the state shown in solid line in Fig. 1) of being communicated with the 4th valve port of the second valve port and the first valve port to be communicated with the 4th valve port and to switch between the second state (by the state shown in dotted line in Fig. 1) of being communicated with the 3rd valve port of the second valve port at the first valve port.

First valve port of described second four-way change-over valve 94 is connected with the second bleed pipe 26 of the second compression unit 22, second valve port of this second four-way change-over valve 94 is connected to the midway of collecting fitting 67,3rd valve port of this second four-way change-over valve 94 is connected with the end side of the second intermediate heat exchanger 42, and the 4th valve port of this second four-way change-over valve 94 is connected with the 3rd suction line 31 of the 3rd compression unit 23.This second four-way change-over valve 94 to be communicated with the 3rd valve port and the first state (by the state shown in solid line in Fig. 1) of being communicated with the 4th valve port of the second valve port and the first valve port to be communicated with the 4th valve port and to switch between the second state (by the state shown in dotted line in Fig. 1) of being communicated with the 3rd valve port of the second valve port at the first valve port.

First valve port of described 3rd four-way change-over valve 95 is connected with the 3rd bleed pipe 27 of the 3rd compression unit 23, second valve port of the 3rd four-way change-over valve 95 is connected to the midway of collecting fitting 67,3rd valve port of the 3rd four-way change-over valve 95 is connected with the end side of the 3rd intermediate heat exchanger 43, and the 4th valve port of the 3rd four-way change-over valve 95 is connected with the 4th suction line 32 of the 4th compression unit 24.3rd four-way change-over valve 95 to be communicated with the 3rd valve port and the first state (by the state shown in solid line in Fig. 1) of being communicated with the 4th valve port of the second valve port and the first valve port to be communicated with the 4th valve port and to switch between the second state (by the state shown in dotted line in Fig. 1) of being communicated with the 3rd valve port of the second valve port at the first valve port.

First valve port of described 4th four-way change-over valve 96 is connected with the 4th bleed pipe 28 of the 4th compression unit 24, second valve port of the 4th four-way change-over valve 96 is connected with the end side of tube connector 66,3rd valve port of the 4th four-way change-over valve 96 is connected with the end side of outdoor heat converter 44, and the 4th valve port of the 4th four-way change-over valve 96 is connected with gas side connecting pipe 13.4th four-way change-over valve 96 to be communicated with the 3rd valve port and the first state (by the state shown in solid line in Fig. 1) of being communicated with the 4th valve port of the second valve port and the first valve port to be communicated with the 4th valve port and to switch between the second state (by the state shown in dotted line in Fig. 1) of being communicated with the 3rd valve port of the second valve port at the first valve port.

At this, be connected with check-valves CV1, CV2, CV3 in the midway of the second to the four suction line 30,31,32.Each check-valves CV1, CV2, CV3 allow cold-producing medium to circulate from the first to the three four-way change-over valve 93,94,95 towards described four-stage compressor 20, and stop cold-producing medium to circulate in the opposite direction.

Gs-oil separator 89,90,91,92 is connected in the midway of the first to the four bleed pipe 25,26,27,28.This gs-oil separator 89,90,91,92 is used for the lubricating oil be included in the cold-producing medium flowing through this bleed pipe 25,26,27,28 to separate from this cold-producing medium.On this gs-oil separator 89,90,91,92, be connected with the oily effuser 16,16,16,16 that the lubricating oil that makes to separate in this gs-oil separator 89,90,91,92 flows out towards this gs-oil separator 89,90,91,92 outside.

Specifically, the oily effuser 16 of the first gs-oil separator 89 corresponding to described first bleed pipe 25 is connected with described second suction line 30.The oily effuser 16 of the second gs-oil separator 90 corresponding to described second bleed pipe 26 is connected with described 3rd suction line 31.The oily effuser 16 of the 3rd gs-oil separator 91 corresponding to described 3rd bleed pipe 27 is connected with described 4th suction line 32.The oily effuser 16 of the 4th gs-oil separator 92 corresponding to described 4th bleed pipe 28 is connected with described first suction line 29.In addition, capillary 15 is connected in the midway of each oily effuser 16,16,16,16.

Described the first to the three intermediate heat exchanger 41,42,43 and outdoor heat converter 44 are configured to Gilled heat exchanger.Near these heat exchangers 41,42,43,44, be provided with outdoor fan 122, and these heat exchangers 41,42,43,44 are configured to: between the outdoor air sent here by this outdoor fan 122 and the cold-producing medium flowed in the heat-transfer pipe 52 of each heat exchanger 41,42,43,44, carry out heat exchange.In addition, the concrete structure of each heat exchanger 41,42,43,44 refers to hereinafter described.

At this, one end of described first intermediate heat exchanger 41 is connected with the 3rd valve port of described first four-way change-over valve 93, one end of described second intermediate heat exchanger 42 is connected with the 3rd valve port of described second four-way change-over valve 94, one end of described 3rd intermediate heat exchanger 43 is connected with the 3rd valve port of described 3rd four-way change-over valve 95, and one end of described outdoor heat converter 44 is connected with the 3rd valve port of described 4th four-way change-over valve 96.On the other hand, the other end of the described the first to the three intermediate heat exchanger 41,42,43 is connected with the first to the three refrigerant tubing 70,71,72, and the other end of outdoor heat converter 44 is connected with the 4th refrigerant tubing 73.

After the other end branch of described 4th refrigerant tubing 73, an arm is connected with described bridge circuit 17 and another arm is connected with the 4th flow export P4 of described current divider 18.In addition, between the branch and the 4th flow export P4 of described current divider of described 4th refrigerant tubing 73, check-valves CV7 and capillary 15 is provided with.This check-valves CV7 allows cold-producing medium from described current divider 18 towards the circulation of the branch of described 4th refrigerant tubing 73, and stops cold-producing medium to circulate in the opposite direction.

After the other end branch of described 3rd refrigerant tubing 72, an arm is connected to the midway (between check-valves CV3 with the 4th compression unit 24) of described 4th suction line 32 and another arm is connected with the 3rd flow export P3 of described current divider 18.In addition, between the branch and the 3rd flow export P3 of described current divider 18 of described 3rd refrigerant tubing 72, check-valves CV6 and capillary 15 is provided with.This check-valves CV6 allows cold-producing medium from described current divider 18 towards the circulation of the branch of described 3rd refrigerant tubing 72, and stops cold-producing medium to circulate in the opposite direction.Check-valves CV10 is provided with between the branch and the connecting portion of described 4th suction line 32 of described 3rd refrigerant tubing 72.This check-valves CV10 allows cold-producing medium to circulate from the branch of described 3rd refrigerant tubing 72 towards the connecting portion of described 4th suction line 32, and stops cold-producing medium to circulate in the opposite direction.

After the other end branch of described second refrigerant pipeline 71, an arm is connected to the midway (between check-valves CV2 with the 3rd compression unit 23) of described 3rd suction line 31 and another arm exports P2 with the second of described current divider 18 is connected.Export between P2 at the branch of described second refrigerant pipeline 71 and the second of described current divider 18 and be provided with check-valves CV5 and capillary 15.This check-valves CV5 allows cold-producing medium from described current divider 18 towards the circulation of the branch of described second refrigerant pipeline 71, and stops cold-producing medium to circulate in the opposite direction.Check-valves CV9 is provided with between the branch and the connecting portion of described 3rd suction line 31 of described second refrigerant pipeline 71.This check-valves CV9 allows cold-producing medium to circulate from the branch of described second refrigerant pipeline 71 towards the connecting portion of described 3rd suction line 31, and stops cold-producing medium to circulate in the opposite direction.

After the other end branch of described first refrigerant tubing 70, an arm is connected to the midway (between check-valves CV1 with the second compression unit 22) of described second suction line 30 and another arm is connected with the first-class outlet P1 of described current divider 18.Check-valves CV4 and capillary 15 is provided with between the branch and the first-class outlet P1 of described current divider 18 of described first refrigerant tubing 70.This check-valves CV4 allows cold-producing medium from described current divider 18 towards the circulation of the branch of described first refrigerant tubing 70, and stops cold-producing medium to circulate in the opposite direction.Check-valves CV8 is provided with between the branch and the connecting portion of described second suction line 30 of described first refrigerant tubing 70.This check-valves CV8 allows cold-producing medium to circulate from the branch of described first refrigerant tubing 70 towards the connecting portion of described second suction line 30, and stops cold-producing medium to circulate in the opposite direction.

Described bridge circuit 17 is loops check-valves CV11, CV12, CV13 and the 5th expansion valve 84 bridge-type coupled together.In bridge circuit 17, the link of the inflow side and another side of the 5th expansion valve 84 that are positioned at check-valves CV13 is connected with the first effuser 61, and the link of the outflow side and the inflow side of check-valves CV12 that are positioned at check-valves CV13 is connected with hydraulic fluid side connecting pipe 14.In addition, on refrigerant tubing hydraulic fluid side connecting pipe 14 and the first indoor heat converter 110 coupled together, the first indoor expansion valve 85 that aperture is variable is provided with.On refrigerant tubing hydraulic fluid side connecting pipe 14 and the second indoor heat converter 111 coupled together, be provided with the second indoor expansion valve 86 that aperture is variable.The link of the outflow side and the outflow side of check-valves CV11 that are positioned at check-valves CV12 is connected with inflow pipe 60.Be connected with current divider 18 in the end side of the 5th expansion valve 84, the inflow end of check-valves CV11 is connected with the 4th refrigerant tubing 73.

The first supercooling heat exchanger 100, second supercooling heat exchanger 101, decompressor 87, gas-liquid separator 88 and the 3rd supercooling heat exchanger 102 is connected with in turn in the midway of described inflow pipe 60.

Described first supercooling heat exchanger 100 comprises high-pressure side stream 100a and low-pressure side stream 100b.First supercooling heat exchanger 100 is configured to: make to carry out heat exchange between the cold-producing medium that flows in high-pressure side stream 100a and low-pressure side stream 100b, make the cold-producing medium flowing through high-pressure side stream 100a by supercooling.

Be connected with inflow pipe 60 at the inflow end of described high-pressure side stream 100a, be connected with the first branched pipe 62 using as supercooling path at the inflow end of low-pressure side stream 100b.This first branched pipe 62 is provided with supercooling the second expansion valve 81.This second expansion valve 81 is made up of aperture adjustable electron expansion valve.One end of ascending pipe 106 is connected with the outflow end of low-pressure side stream 100b.

One end of described ascending pipe 106 is connected with the low-pressure side stream 100b of the first supercooling heat exchanger 100, and the other end is connected with second refrigerant pipeline 71.In addition, the other end of ascending pipe 106 is connected with the outflow side of the check-valves CV9 on second refrigerant pipeline 71.

Described second supercooling heat exchanger 101 comprises high-pressure side stream 101a and low-pressure side stream 101b.Second supercooling heat exchanger 101 is configured to: make to carry out heat exchange between the cold-producing medium that flows in high-pressure side stream 101a and low-pressure side stream 101b, make the cold-producing medium flowing through high-pressure side stream 101a by supercooling.

Inflow pipe 60 is connected with at the inflow end of described high-pressure side stream 101a.Another side of tube connector 66 is connected with the inflow end of low-pressure side stream 101b, and the first suction line 29 is connected with the outflow end of this low-pressure side stream 101b.

The end side of described tube connector 66 is connected with the second valve port of the 4th four-way change-over valve 96, and another side of this tube connector 66 is connected with the inflow end of the low-pressure side stream 101b of the second supercooling heat exchanger 101.The other end of collecting fitting 67 is connected to the midway of tube connector 66.

The end side of described collecting fitting 67 is connected with the second valve port of the first four-way change-over valve 93, and another side of this collecting fitting 67 is connected to the midway of tube connector 66.The pipeline be communicated with the second valve port of the second four-way change-over valve 94 and the pipeline be communicated with the second valve port of the 3rd four-way change-over valve 95 is also connected with in the midway of collecting fitting 67.

Described decompressor 87 comprises and is formed as the columnar decompressor casing of lengthwise, and between the second supercooling heat exchanger 101 be arranged on inflow pipe 60 and gas-liquid separator 88.Be provided with in the inside of decompressor casing and make cold-producing medium expand and produce the expansion mechanism of power.Decompressor 87 forms so-called rotary displacement fluid mechanism.Decompressor 87 is configured to: the cold-producing medium flowed into is expanded, and is again sent towards inflow pipe 60 by the cold-producing medium after expanding.

Described inflow pipe 60 is provided with the shunt valve 64 walking around described decompressor 87.The end side of shunt valve 64 is connected with the inflow side of decompressor 87, and another side of this shunt valve 64 is connected with the outflow side of decompressor 87, thus walks around decompressor 87.This shunt valve 64 is provided with the first expansion valve 80.This first expansion valve 80 is made up of aperture adjustable electron expansion valve.

Described gas-liquid separator 88 is made up of the cylindric closed container of lengthwise.On gas-liquid separator 88, be connected with inflow pipe 60, first effuser 61 and the second effuser 65.Inflow pipe 60 is uncovered towards the top of gas-liquid separator 88 inner space.First effuser 61 is uncovered towards the below of gas-liquid separator 88 inner space.Second effuser 65 is uncovered towards the top of gas-liquid separator 88 inner space.In gas-liquid separator 88, the cold-producing medium flowed into from inflow pipe 60 is separated into saturated liquid and saturated gas, and saturated liquid flows out from the first effuser 61, and saturated gas flows out from the second effuser 65.

The end side of described second effuser 65 is connected with gas-liquid separator 88, and another side of this second effuser 65 is connected to the midway of return duct 68.This second effuser 65 is provided with the 4th expansion valve 83.4th expansion valve 83 is made up of aperture adjustable electron expansion valve.

3rd supercooling heat exchanger 102 is connected to the midway of described first effuser 61.3rd supercooling heat exchanger 102 comprises high-pressure side stream 102a and low-pressure side stream 102b.3rd supercooling heat exchanger 102 is configured to: make to carry out heat exchange between the cold-producing medium that flows in high-pressure side stream 102a and low-pressure side stream 102b, make the cold-producing medium flowing through high-pressure side stream 102a by supercooling.

The inflow end of described high-pressure side stream 102a is connected with the outflow side of gas-liquid separator 88, and the outflow end of this high-pressure side stream 102a is connected with bridge circuit 17.Be connected with the second branched pipe 63 using as supercooling path at the inflow end of low-pressure side stream 102b, the outflow end of low-pressure side stream 102b is connected with another side of return duct 68.

The end side of described second branched pipe 63 is connected between gas-liquid separator 88 on the first effuser 61 and the 3rd supercooling heat exchanger 102, and another side of this second branched pipe 63 is connected with the inflow end of the low-pressure side stream 102b of the 3rd supercooling heat exchanger 102.This second branched pipe 63 is provided with the 3rd expansion valve 82.3rd expansion valve 82 is made up of aperture adjustable electron expansion valve.

One end of described return duct 68 is connected with the other end of tube connector 66, and the other end of this return duct 68 is connected with the outflow end of the low-pressure side stream 102b of the 3rd supercooling heat exchanger 102, and the second effuser 65 is connected to the midway of this return duct 68.

The indoor loop > of <

In indoor loop 12, the first indoor expansion valve 85 and the first indoor heat converter 110 is disposed with from its liquid side towards gas side, and be also disposed with the second indoor expansion valve 86 and the second indoor heat converter 111 from its liquid side towards gas side, this first indoor expansion valve 85 and the first indoor heat converter 110, be connected in parallel to each other with the second indoor expansion valve 86 and the second indoor heat converter 111.Each indoor expansion valve 85,86 is made up of aperture adjustable electron expansion valve.Each indoor heat converter 110,111 is made up of tubes provided with cross ribs plate heat exchanger.Near each indoor heat converter 110,111, be respectively arranged with indoor fan room air being sent to each indoor heat converter 110,111, but this and not shown come.Further, in each indoor heat converter 110,111, between cold-producing medium and room air, heat exchange is carried out.

The structure > of the outdoor unit of <

As shown in Fig. 3 to Fig. 5, outdoor unit 3 comprises outdoor machine shell 121, and this outdoor machine shell 121 forms casing involved in the present invention.Outdoor machine shell 121 is formed as the casing of the rectangular shape of lengthwise, is formed with the suction inlet 123 of air in the below in this outdoor machine shell 121 front, and is formed with the blow-off outlet 124 of air at the upper surface of this outdoor machine shell 121.In addition, this suction inlet 123 forms suction inlet involved in the present invention.Outdoor heat converter 44, first intermediate heat exchanger 41, second intermediate heat exchanger 42, the 3rd intermediate heat exchanger 43 and the outdoor fan 122 that form outdoor heat exchanger group 40 is provided with in the inside of outdoor machine shell 121.Each heat exchanger 41,42,43,44 is formed as approximate mouth " U " font towards a left side when overlooking, and erectly arranges along suction inlet 123.

Described outdoor fan 122 is used to the fan air be drawn in outdoor machine shell 121 being sent to each heat exchanger 41,42,43,44, and is configured to so-called Sirocco fan.Outdoor fan 122 is arranged in the top of each heat exchanger 41,42,43,44 in outdoor machine shell 121.Further, this air after the air making to suck from suction inlet 123 is by each heat exchanger 41,42,43,44, then blows out from blow-off outlet 124 by outdoor fan 122 towards the outside.

As shown in Figure 5, in the inside of outdoor machine shell 121, pile up successively from downside towards upside and be provided with the first intermediate heat exchanger 41, second intermediate heat exchanger 42, the 3rd intermediate heat exchanger 43 and outdoor heat converter 44.In addition, also can be arranged to: turned upside down in the position of the first intermediate heat exchanger 41 and the second intermediate heat exchanger 42.

Described first intermediate heat exchanger 41 is made up of so-called tubes provided with cross ribs plate heat exchanger.First intermediate heat exchanger 41 comprises: multiple heat transfer tube group 50 and the thermofin 51 respectively with many heat-transfer pipes 52 and Duo Gen U-shaped pipe.

Described multiple heat transfer tube group 50 is arranged in order setting by seven heat transfer tube group about 50 and forms.In each heat transfer tube group 50, many heat-transfer pipes 52 (being the six roots of sensation in Figure 5) along air flow direction up and down each one two ground be set altogether be arranged to three row, the first pipe row 53 are configured with in the left side (i.e. windward side) of Fig. 5, be configured with the second pipe row 54 in the central authorities of Fig. 5, be configured with the 3rd pipe row 55 on the right side (i.e. leeward side) of Fig. 5.That is, each heat transfer tube group 50 is arranged to: heat-transfer pipe 52 is all two-tube at each row.

In each heat transfer tube group 50, be joined to one another with the end except one end (the second end) of one end (first end) of higher level's heat-transfer pipe 52 of the first pipe row 53 in described many heat-transfer pipes 52 and subordinate's heat-transfer pipe 52 of the 3rd pipe row 55 of described U-shaped pipe by heat-transfer pipe 52, thus define one using described first end and described second end as the refrigerant path at two ends.The first end of the first pipe row 53 of each heat transfer tube group 50 is connected with the first refrigerant tubing 70 of refrigerant loop 10 through collector.Second end of the 3rd pipe row 55 of each heat transfer tube group 50 is communicated with the 3rd valve port of the first four-way change-over valve 93.

As shown in Figure 5, thermofin 51 described in each is formed as approximate rectangle thin plate.Thermofin 51 arranges along the bearing of trend of heat transfer tube group 50 arrange every predetermined distance.On each thermofin 51, be formed as three row with the multiple through holes run through for heat-transfer pipe 52, heat-transfer pipe 52 runs through this through hole.So, around heat-transfer pipe 52, be just provided with thermofin 51, make heat transfer area increase and be promoted heat trnasfer.

Described second intermediate heat exchanger 42 is made up of so-called tubes provided with cross ribs plate heat exchanger.Second intermediate heat exchanger 42 comprises: multiple heat transfer tube group 50 and the thermofin 51 respectively with many heat-transfer pipes 52 and Duo Gen U-shaped pipe.

Described multiple heat transfer tube group 50 is arranged in order setting by seven heat transfer tube group about 50 and forms.In each heat transfer tube group 50, many heat-transfer pipes 52 (being the six roots of sensation in Figure 5) along air flow direction up and down each one two ground be set altogether be arranged to three row, the first pipe row 53 are configured with in the left side (i.e. windward side) of Fig. 5, be configured with the second pipe row 54 in the central authorities of Fig. 5, be configured with the 3rd pipe row 55 on the right side (i.e. leeward side) of Fig. 5.That is, each heat transfer tube group 50 is configured to: heat-transfer pipe 52 is all arranged as two-tube at each row.

In each heat transfer tube group 50, be joined to one another with the end except one end (the second end) of one end (first end) of higher level's heat-transfer pipe 52 of the first pipe row 53 in described many heat-transfer pipes 52 and subordinate's heat-transfer pipe 52 of the 3rd pipe row 55 of described U-shaped pipe by heat-transfer pipe 52, thus define one using described first end and described second end as the refrigerant path at two ends.The first end of the first pipe row 53 of each heat transfer tube group 50 is connected with the second refrigerant pipeline 71 of refrigerant loop 10 through collector.Second end of the 3rd pipe row 55 of each heat transfer tube group 50 is communicated with the 3rd valve port of the second four-way change-over valve 94.

Described 3rd intermediate heat exchanger 43 is made up of so-called tubes provided with cross ribs plate heat exchanger.3rd intermediate heat exchanger 43 comprises: multiple heat transfer tube group 50 and the thermofin 51 respectively with many heat-transfer pipes 52 and Duo Gen U-shaped pipe.

Described multiple heat transfer tube group 50 is arranged in order setting by six heat transfer tube group about 50 and forms.In each heat transfer tube group 50, many heat-transfer pipes 52 (being the six roots of sensation in Figure 5) along air flow direction up and down each one two ground be set altogether be arranged to three row, the first pipe row 53 are configured with in the left side (i.e. windward side) of Fig. 5, be configured with the second pipe row 54 in the central authorities of Fig. 5, be configured with the 3rd pipe row 55 on the right side (i.e. leeward side) of Fig. 5.That is, each heat transfer tube group 50 is configured to: heat-transfer pipe 52 is all arranged as two-tube at each row.

In each heat transfer tube group 50, be joined to one another with the end except one end (the second end) of one end (first end) of higher level's heat-transfer pipe 52 of the first pipe row 53 in described many heat-transfer pipes 52 and subordinate's heat-transfer pipe 52 of the 3rd pipe row 55 of described U-shaped pipe by heat-transfer pipe 52, thus define one using described first end and described second end as the refrigerant path at two ends.The first end of the first pipe row 53 of each heat transfer tube group 50 is connected with the 3rd refrigerant tubing 72 of refrigerant loop 10 through collector.Second end of the 3rd pipe row 55 of each heat transfer tube group 50 is communicated with the 3rd valve port of the 3rd four-way change-over valve 95.

Described outdoor heat converter 44 is made up of so-called tubes provided with cross ribs plate heat exchanger.Outdoor heat converter 44 comprises: multiple heat transfer tube group 50 and the thermofin 51 respectively with many heat-transfer pipes 52 and Duo Gen U-shaped pipe.

Described multiple heat transfer tube group 50 is arranged in order setting by eight heat transfer tube group about 50 and forms.In each heat transfer tube group 50, many heat-transfer pipes 52 (being the six roots of sensation in Figure 5) along air flow direction up and down each one two ground be set altogether be arranged to three row, the first pipe row 53 are configured with in the left side (i.e. windward side) of Fig. 5, be configured with the second pipe row 54 in the central authorities of Fig. 5, be configured with the 3rd pipe row 55 on the right side (i.e. leeward side) of Fig. 5.That is, each heat transfer tube group 50 is configured to: heat-transfer pipe 52 is all arranged as two-tube at each row.

In each heat transfer tube group 50, be joined to one another with the end except one end (the second end) of one end (first end) of higher level's heat-transfer pipe 52 of the first pipe row 53 in described many heat-transfer pipes 52 and subordinate's heat-transfer pipe 52 of the 3rd pipe row 55 of described U-shaped pipe by heat-transfer pipe 52, thus define one using described first end and described second end as the refrigerant path at two ends.The first end of the first pipe row 53 of each heat transfer tube group 50 is connected with the 4th refrigerant tubing 73 of refrigerant loop 10 through collector.Second end of the 3rd pipe row 55 of each heat transfer tube group 50 is communicated with the 3rd valve port of the 4th four-way change-over valve 96.

-motion-

Then, the motion of aircondition 1 is described.In this aircondition 1, by switching the first to the four four-way change-over valve 93,94,95,96, thus the running of described refrigerant loop 10 is switched to cooling operation or heats running.In addition, what 1 to 26 in Fig. 1 and Fig. 2 represented is the pressure state of cold-producing medium.

-cooling operation-

See figures.1.and.2 and the cooling operation of aircondition 1 is described.In FIG, the flowing of the cold-producing medium when this cooling operation is represented with solid arrow.Under cooling operation, make outdoor heat converter 44 play radiator, make each indoor heat converter 110,111 play evaporimeter, thus carry out four stage compression type supercritical refrigeration cycle.The first to the three intermediate heat exchanger 41,42,43 plays the cooler to the high-pressure refrigerant of ejection cools from each compression unit 21,22,23.

Under cooling operation, all four-way change-over valves 93,94,95,96 are all configured to the first state, and four-stage compressor 20 drives.When four-stage compressor 20 drives, in each compression unit 21,22,23,24, cold-producing medium is compressed.The cold-producing medium having obtained compressing in the first compression unit 21 is sprayed (2 in Fig. 1 and Fig. 2) by towards the first bleed pipe 25.In addition, in the first gs-oil separator 89 now on the first bleed pipe 25, the lubricating oil be included in the gaseous refrigerant flowing through this first bleed pipe 25 is separated.The lubricating oil separated is sent to the second suction line 30 from oily effuser 16.Further, the cold-producing medium of flowing in the first bleed pipe 25 is by flowing into the first intermediate heat exchanger 41 after the first four-way change-over valve 93.In the first intermediate heat exchanger 41, cold-producing medium is cooled towards outdoor air heat release.The cold-producing medium be cooled in the first intermediate heat exchanger 41 flows into the first refrigerant tubing 70.In the first refrigerant tubing 70 cold-producing medium of flowing by check-valves CV8 after flow into the second suction line 30 and be inhaled into the second compression unit 22 (3 in Fig. 1 and Fig. 2).

The cold-producing medium having obtained compressing in the second compression unit 22 is sprayed (4 in Fig. 1 and Fig. 2) by towards the second bleed pipe 26.In addition, in the second gs-oil separator 90 now on the second bleed pipe 26, the lubricating oil be included in the gaseous refrigerant flowing through this second bleed pipe 26 is separated.The lubricating oil separated is sent to the 3rd suction line 31 from oily effuser 16.Further, the cold-producing medium of flowing in the second bleed pipe 26 is by flowing into the second intermediate heat exchanger 42 after the second four-way change-over valve 94.In the second intermediate heat exchanger 42, cold-producing medium is cooled towards outdoor air heat release.The cold-producing medium be cooled in the second intermediate heat exchanger 42 flows into second refrigerant pipeline 71 (5 in Fig. 1 and Fig. 2).The cold-producing medium of flowing in second refrigerant pipeline 71, by converging with the cold-producing medium flowing through ascending pipe 106 after check-valves CV9, then flows into the 3rd suction line 31 and is inhaled into the 3rd compression unit 23 (6 in Fig. 1 and Fig. 2).

The cold-producing medium having obtained compressing in the 3rd compression unit 23 is sprayed (7 in Fig. 1 and Fig. 2) by towards the 3rd bleed pipe 27.In addition, in the 3rd gs-oil separator 91 now on the 3rd bleed pipe 27, the lubricating oil be included in the gaseous refrigerant flowing through the 3rd bleed pipe 27 is separated.The lubricating oil separated is sent to the 4th suction line 32 from oily effuser 16.Further, the cold-producing medium of flowing in the 3rd bleed pipe 27 is by flowing into the 3rd intermediate heat exchanger 43 after the 3rd four-way change-over valve 95.In the 3rd intermediate heat exchanger 43, cold-producing medium is cooled towards outdoor air heat release.The cold-producing medium be cooled in the 3rd intermediate heat exchanger 43 flows into the 3rd refrigerant tubing 72.In the 3rd refrigerant tubing 72 cold-producing medium of flowing by check-valves CV10 after flow into the 4th suction line 32 and be inhaled into the 4th compression unit 24 (8 in Fig. 1 and Fig. 2).

The cold-producing medium having obtained compressing in the 4th compression unit 24 is sprayed (9 in Fig. 1 and Fig. 2) by towards the 4th bleed pipe 28.Repeatedly alternately carry out compressing and cooling as mentioned above, thus make the compression process of described four-stage compressor 20 close to isotherm compression, seek to reduce the compression power needed for described four-stage compressor 20.In addition, in the 4th gs-oil separator 92 now on the 4th bleed pipe 28, the lubricating oil be included in the gaseous refrigerant flowing through the 4th bleed pipe 28 is separated.The lubricating oil be separated is sent to the first suction line 29 from oily effuser 16.The cold-producing medium of flowing in the 4th bleed pipe 28 is by inflow outdoor heat exchanger 44 after the 4th four-way change-over valve 96.In outdoor heat converter 44, cold-producing medium is cooled towards outdoor air heat release.The cold-producing medium be cooled in outdoor heat converter 44 flows into the 4th refrigerant tubing 73.In the 4th refrigerant tubing 73 flowing cold-producing medium by check-valves CV11 after flow into inflow pipe 60.

In inflow pipe 60, a part for the cold-producing medium of flowing flows into the first branched pipe 62.In the first branched pipe 62, the cold-producing medium (10 in Fig. 1 and Fig. 2) of flowing is reduced pressure by the second expansion valve 81.The cold-producing medium (11 in Fig. 1 and Fig. 2) reduced pressure by the second expansion valve 81 flows into the low-pressure side stream 100b of the first supercooling heat exchanger 100.On the other hand, in inflow pipe 60, the remainder of the cold-producing medium of flowing flows into the high-pressure side stream 100a (10 in Fig. 1 and Fig. 2) of the first supercooling heat exchanger 100.In the first supercooling heat exchanger 100, between the cold-producing medium flowed in high-pressure side stream 100a and low-pressure side stream 100b, carry out heat exchange, make the cold-producing medium flowing through high-pressure side stream 100a by supercooling.

After the cold-producing medium having flowed out the high-pressure side stream 100a of the first supercooling heat exchanger 100 flows through inflow pipe 60 (13 in Fig. 1 and Fig. 2) again, flow into the high-pressure side stream 101a of the second supercooling heat exchanger 101.On the other hand, the cold-producing medium (12 in Fig. 1 and Fig. 2) having flowed out the low-pressure side stream 100b of the first supercooling heat exchanger 100 flows into ascending pipe 106.After the cold-producing medium inflow second refrigerant pipeline 71 of flowing in ascending pipe 106, converge (6 in Fig. 1 and Fig. 2) with the cold-producing medium in second refrigerant pipeline 71.That is, the cold-producing medium having flowed to ascending pipe 106 is injected into the suction side of the 3rd compression unit 23.

In the second supercooling heat exchanger 101, between the cold-producing medium flowed in high-pressure side stream 101a and low-pressure side stream 101b, carry out heat exchange, make the cold-producing medium flowing through high-pressure side stream 101a by supercooling.

After the cold-producing medium having flowed out the high-pressure side stream 101a of the second supercooling heat exchanger 101 flows through inflow pipe 60 (14 in Fig. 1 and Fig. 2) again, a part for this cold-producing medium flows into decompressor 87.In decompressor 87, the cold-producing medium flowed into is expanded (in Fig. 1 and Fig. 2 14 to 16), then the cold-producing medium after expansion is sent towards inflow pipe 60 again.On the other hand, shunt valve 64 is flowed to after having flowed out the remainder shunting of the cold-producing medium of the high-pressure side stream 101a of the second supercooling heat exchanger 101.The cold-producing medium of flowing in shunt valve 64 is reduced pressure after (15 in Fig. 1 and Fig. 2) by the first expansion valve 80 and again returns inflow pipe 60.The cold-producing medium having flowed out decompressor 87 and the cold-producing medium having flowed out shunt valve 64 converge (17 in Fig. 1 and Fig. 2) and flow into gas-liquid separator 88 afterwards in inflow pipe 60.In gas-liquid separator 88, the cold-producing medium flowed into is separated into gaseous refrigerant (22 in Fig. 1 and Fig. 2) and liquid refrigerant (18 in Fig. 1 and Fig. 2).

After the liquid refrigerant (18 in Fig. 1 and Fig. 2) of effluent gases liquid/gas separator 88 flows through the first effuser 61, a part for this cold-producing medium flows into the second branched pipe 63.In the second branched pipe 63, the cold-producing medium of flowing is reduced pressure by the 3rd expansion valve 82.The cold-producing medium (19 in Fig. 1 and Fig. 2) reduced pressure by the 3rd expansion valve 82 flows into the low-pressure side stream 102b of the 3rd supercooling heat exchanger 102.On the other hand, in inflow pipe 60, the remainder of the cold-producing medium of flowing flows into the high-pressure side stream 102a of the 3rd supercooling heat exchanger 102.

In the 3rd supercooling heat exchanger 102, carry out heat exchange between the cold-producing medium flowing through high-pressure side stream 102a and low-pressure side stream 102b, make the liquid refrigerant flowing through high-pressure side stream 102a by supercooling.

The liquid refrigerant (20 in Fig. 1 and Fig. 2) having flowed out the high-pressure side stream 102a of the 3rd supercooling heat exchanger 102 flows through the first effuser 61 again, influent side connecting pipe 14 after the check-valves CV13 passing through bridge circuit 17.On the other hand, the cold-producing medium having flowed out the low-pressure side stream 102b of the 3rd supercooling heat exchanger 102 flows in return duct 68.Further, the cold-producing medium (24 in Fig. 1 and Fig. 2) flowed in return duct 68 converges follow-up afterflow and moves with the gaseous refrigerant (23 in Fig. 1 and Fig. 2) flowed out from the second effuser 65 in the midway of this return duct 68.The cold-producing medium having flowed out return duct 68 converges with the cold-producing medium flowing out tube connector 66.The cold-producing medium (26 in Fig. 1 and Fig. 2) converged flows into the low-pressure side stream 101b of the second supercooling heat exchanger 101.

In hydraulic fluid side connecting pipe 14, a part for the liquid refrigerant of flowing is reduced pressure by the first indoor expansion valve 85 after shunting.The cold-producing medium (21a in Fig. 1 and Fig. 2) be depressurized flows into the first indoor heat converter 110.In the first indoor heat converter 110, liquid refrigerant heat absorption and evaporating in air indoor.Gaseous refrigerant (25a in Fig. 1 and Fig. 2) the inflow gas side connecting pipe 13 of having evaporated.

In hydraulic fluid side connecting pipe 14, the remainder of the liquid refrigerant of flowing is reduced pressure by the second indoor expansion valve 86.The cold-producing medium (21b in Fig. 1 and Fig. 2) be depressurized flows into the second indoor heat converter 111.In the second indoor heat converter 111, liquid refrigerant heat absorption and evaporating in air indoor.Gaseous refrigerant (25b in Fig. 1 and Fig. 2) the inflow gas side connecting pipe 13 of having evaporated.

In gas side connecting pipe 13, the cold-producing medium flowed out from the first indoor heat converter 110 converges with the cold-producing medium flowed out from the second indoor heat converter 111.The cold-producing medium of flowing in gas side connecting pipe 13 is by flowing into tube connector 66 after the 4th four-way change-over valve 96.In tube connector 66, a part for the cold-producing medium of flowing flows to the first to the three four-way change-over valve 93,94,95 respectively after collecting fitting 67 is shunted.

Flow into the second suction line 30 by the cold-producing medium of the second valve port of the first four-way change-over valve 93.In the second suction line 30 cold-producing medium of flowing by check-valves CV1 after converge with the cold-producing medium that flows in the first refrigerant tubing 70, be then inhaled into the second compression unit 22.Flow into the 3rd suction line 31 by the cold-producing medium of the second valve port of the second four-way change-over valve 94.In the 3rd suction line 31 cold-producing medium of flowing by check-valves CV2 after converge with the cold-producing medium that flows in second refrigerant pipeline 71, be then inhaled into the 3rd compression unit 23.Flow into the 4th suction line 32 by the cold-producing medium of the second valve port of the 3rd four-way change-over valve 95.In the 4th suction line 32 cold-producing medium of flowing by check-valves CV3 after converge with the cold-producing medium that flows in the 3rd refrigerant tubing 72, be then inhaled into the 4th compression unit 24.

In tube connector 66, the remainder of the cold-producing medium of flowing converges with the cold-producing medium flowed in return duct 68.The cold-producing medium (26 in Fig. 1 and Fig. 2) converged is by flowing into the first suction line 29 after the low-pressure side stream 101b of the second supercooling heat exchanger 101.In the first suction line 29, the cold-producing medium (1 in Fig. 1 and Fig. 2) of flowing is compressed again in the first compression unit 21 of four-stage compressor 20.

-heat running-

Then, be described with reference to the running that heats of Fig. 7 to this aircondition 1.In the figure 7, the flowing of the cold-producing medium when this heats running is represented with dotted arrow.Under this heats running, make each indoor heat converter 110,111 play radiator, make the first to the three intermediate heat exchanger 41,42,43 and outdoor heat converter 44 play evaporimeter, thus carry out four stage compression type supercritical refrigeration cycle.

Heating under running, all four-way change-over valves 93,94,95,96 are all configured to the second state, and four-stage compressor 20 drives.When four-stage compressor 20 drives, in each compression unit 21,22,23,24, cold-producing medium is compressed.The cold-producing medium having obtained compressing in the first compression unit 21 is sprayed by towards the first bleed pipe 25.Further, the cold-producing medium flowed in the first bleed pipe 25 is by being inhaled into the second compression unit 22 after the first four-way change-over valve 93.The cold-producing medium be further compressed in the second compression unit 22 is by being inhaled into the 3rd compression unit 23 after the second four-way change-over valve 94.The cold-producing medium be further compressed in the 3rd compression unit 23 is by being inhaled into the 4th compression unit 24 after the 3rd four-way change-over valve 95.In the 4th compression unit 24, cold-producing medium is further compressed.As mentioned above, different from cooling operation, do not carry out level Four compression with cooling when heating running.Thus, with along with cool carry out level Four compression situation compared with, from four-stage compressor 20, the temperature of cold-producing medium of ejection does not reduce.Consequently, with along with cool carry out level Four compression situation compared with, heating capacity when heating running increases.

The cold-producing medium sprayed from the 4th compression unit 24 is by being sent to the first and second indoor heat converters 110,111 after the 4th four-way change-over valve 96.In the first and second indoor heat converters 110,111, cold-producing medium is cooled towards room air heat release.The cold-producing medium be cooled in each indoor heat converter 110,111 is sent to bridge circuit 17 after being reduced pressure by the first and second indoor expansion valve 85,86.Further, this cold-producing medium is by flowing into inflow pipe 60 after check-valves CV12.

In inflow pipe 60, a part for the cold-producing medium of flowing flows into the first branched pipe 62.In the first branched pipe 62, the cold-producing medium of flowing is reduced pressure by the second expansion valve 81.The cold-producing medium reduced pressure by the second expansion valve 81 flows into the low-pressure side stream 100b of the first supercooling heat exchanger 100.On the other hand, in inflow pipe 60, the remainder of the cold-producing medium of flowing flows into the high-pressure side stream 100a of the first supercooling heat exchanger 100.In the first supercooling heat exchanger 100, between the cold-producing medium flowed in high-pressure side stream 100a and low-pressure side stream 100b, carry out heat exchange, make the cold-producing medium flowing through high-pressure side stream 100a by supercooling.

After the cold-producing medium having flowed out the high-pressure side stream 100a of the first supercooling heat exchanger 100 flows through inflow pipe 60 again, flow into the high-pressure side stream 101a of the second supercooling heat exchanger 101.On the other hand, the cold-producing medium having flowed out the low-pressure side stream 100b of the first supercooling heat exchanger 100 flows into ascending pipe 106.After the cold-producing medium inflow second refrigerant pipeline 71 of flowing in ascending pipe 106, converge with the cold-producing medium in second refrigerant pipeline 71.That is, the cold-producing medium having flowed to ascending pipe 106 is injected into the suction side of the 3rd compression unit 23.

After the cold-producing medium having flowed out the high-pressure side stream 101a of the second supercooling heat exchanger 101 flows through inflow pipe 60 again, a part for this cold-producing medium flows into decompressor 87.In decompressor 87, the cold-producing medium flowed into is expanded, then the cold-producing medium after expansion is sent towards inflow pipe 60 again.On the other hand, shunt valve 64 is flowed to after having flowed out the remainder shunting of the cold-producing medium of the high-pressure side stream 101a of the second supercooling heat exchanger 101.In shunt valve 64, the cold-producing medium of flowing returns inflow pipe 60 after being reduced pressure by the first expansion valve 80 again.Gas-liquid separator 88 is flowed into after the cold-producing medium having flowed out decompressor 87 and the cold-producing medium having flowed out shunt valve 64 converge in inflow pipe 60.In gas-liquid separator 88, the cold-producing medium flowed into is separated into gaseous refrigerant and liquid refrigerant.

After the liquid refrigerant of effluent gases liquid/gas separator 88 flows through the first effuser 61, a part for this cold-producing medium flows into the second branched pipe 63.In the second branched pipe 63, the cold-producing medium of flowing is reduced pressure by the 3rd expansion valve 82.The cold-producing medium reduced pressure by the 3rd expansion valve 82 flows into the low-pressure side stream 102b of the 3rd supercooling heat exchanger 102.On the other hand, in the first effuser 61, the remainder of the cold-producing medium of flowing flows into the high-pressure side stream 102a of the 3rd supercooling heat exchanger 102.

The liquid refrigerant having flowed out the high-pressure side stream 102a of the 3rd supercooling heat exchanger 102 flows through the first effuser 61 again, after the 5th expansion valve 84 by bridge circuit 17 reduces pressure, is sent to current divider 18.The cold-producing medium be assigned with in current divider 18 is by flowing into the first to the three intermediate heat exchanger 41,42,43 and outdoor heat converter 44 after capillary 15 and check-valves CV4, CV5, CV6, CV7.In the first to the three intermediate heat exchanger 41,42,43 and outdoor heat converter 44, liquid refrigerant heat absorption and evaporating in air outdoor.The cold-producing medium flowed out from the first intermediate heat exchanger 41 is by flowing into collecting fitting 67 after the first four-way change-over valve 93.The cold-producing medium flowed out from the second intermediate heat exchanger 42 is by flowing into collecting fitting 67 after the second four-way change-over valve 94.The cold-producing medium flowed out from the 3rd intermediate heat exchanger 43 is by flowing into collecting fitting 67 after the 3rd four-way change-over valve 95.Further, the cold-producing medium flowed out from the first to the three intermediate heat exchanger 41,42,43 is by flowing into tube connector 66 after collecting fitting 67.

The cold-producing medium flowed out in heat exchanger 44 outdoor, by flowing into tube connector 66 after the 4th four-way change-over valve 96, converges with the cold-producing medium flowed out from the first to the three intermediate heat exchanger 41,42,43.The cold-producing medium converged flows and converges with the cold-producing medium flowed in return duct 68 in tube connector 66.The cold-producing medium converged flows into the first suction line 29.In the first suction line 29, the cold-producing medium of flowing is compressed again in the first compression unit 21 of four-stage compressor 20.

-outdoor unit-

Then, outdoor unit is described.As shown in Figure 3, flow to above outdoor machine shell 121 after the air being inhaled into outdoor machine shell 121 inside from suction inlet 123 carries out heat exchange the first to the three intermediate heat exchanger 41,42,43 and outdoor heat converter 44 and be blown from blow-off outlet 124 again.

At this, as shown in Figure 6, described outdoor unit 3 suction inlet 123 be configured to from the side sucks again from blow-off outlet 124 blow out air, so-called upper blowing type upward after air, and the air velocity thus above suction inlet 123 is than fast below it.As shown in Figure 2, in the first to the three intermediate heat exchanger 41,42,43, the pressure of the cold-producing medium that the pressure ratio of the cold-producing medium of flowing flows in outdoor heat converter 44 is low, and thus in the first to the three intermediate heat exchanger 41,42,43, the density of the cold-producing medium of flowing is less than the density of the cold-producing medium of flowing in outdoor heat converter 44.For this reason, if in the first to the three intermediate heat exchanger 41,42,43 and outdoor heat converter 44, the mass flow of the cold-producing medium of flowing is roughly equal respectively, then in the first to the three intermediate heat exchanger 41,42,43, the volume flow of cold-producing medium will be greater than the volume flow of the cold-producing medium of flowing in outdoor heat converter 44.Even if the refrigerant path quantity in the first to the three intermediate heat exchanger 41,42,43 and outdoor heat converter 44 is roughly equal, also be greater than the refrigerant flow rates in outdoor heat converter 44 due to the flow velocity of cold-producing medium of flowing in the first to the three intermediate heat exchanger 41,42,43, the pressure loss of the cold-producing medium thus in the first to the three intermediate heat exchanger 41,42,43 is greater than the pressure loss of cold-producing medium in outdoor heat converter 44.

In outdoor heat converter 44 above being arranged at air velocity in outdoor machine shell 121 and being higher, because heat exchange performance is higher, its size thus can be made to realize miniaturized.On the other hand, in the first to the three intermediate heat exchanger 41,42,43 being arranged at the below that in outdoor machine shell 121, air velocity is lower, heat-exchange capacity is lower.For this reason, to increase heat exchange amount, the first to the three intermediate heat exchanger 41,42,43 will than be arranged on top time large.

Therefore, outdoor heat exchanger group 40 can not become maximization due to the maximization of outdoor heat converter 44 and the first to the three intermediate heat exchanger 41,42,43.

If make the first to the three intermediate heat exchanger 41,42,43 realize maximizing, in the first to the three intermediate heat exchanger 41,42,43, the quantity of refrigerant path will increase.For this reason, in the first to the three intermediate heat exchanger 41,42,43, in each bar refrigerant path, the flow velocity of cold-producing medium reduces, the pressure loss reduction of cold-producing medium when by each bar refrigerant path.Because in the first to the three intermediate heat exchanger 41,42,43, the flow velocity of the cold-producing medium of flowing is originally higher, if thus the increase of refrigerant path quantity makes flow velocity reduce, therefore and greatly the pressure loss will reduce.

On the other hand, if outdoor heat converter 44 realizes miniaturization, in outdoor heat converter 44, the quantity of refrigerant path will reduce.If the quantity of refrigerant path reduces, in each bar refrigerant path, the flow velocity of cold-producing medium will be accelerated, the pressure loss increase of cold-producing medium when by each bar refrigerant path.

But the flow velocity of the cold-producing medium of flowing is originally lower in outdoor heat converter 44, though thus flow velocity because refrigerant path quantity reduces, some is accelerated, it is also smaller for resulting from this increase of the pressure loss.

Therefore, when outdoor heat converter 44 being arranged on above the first to the three intermediate heat exchanger 41,42,43, the maximization of outdoor heat exchanger group 40 can be suppressed, the pressure loss of cold-producing medium in the first to the three intermediate heat exchanger 41,42,43 can also be reduced simultaneously.

As shown in Figure 2, the pressure of cold-producing medium flow in the first and second intermediate heat exchangers 41,42 due to the pressure ratio of cold-producing medium of flowing in the 3rd intermediate heat exchanger 43 is high, and the density of the cold-producing medium that the density ratio of the cold-producing medium thus flowed in the first and second intermediate heat exchangers 41,42 flows in the 3rd intermediate heat exchanger 43 is little.For this reason, if in the first and second intermediate heat exchanger the 41,42 and the 3rd intermediate heat exchangers 43, the mass flow of the cold-producing medium of flowing is roughly equal respectively, then in the first and second intermediate heat exchangers 41,42, the volume flow of cold-producing medium will be greater than the volume flow of the cold-producing medium of flowing in the 3rd intermediate heat exchanger 43.Even if the quantity of the refrigerant path in the first and second intermediate heat exchanger the 41,42 and the 3rd intermediate heat exchangers 43 is roughly equal, also be greater than the refrigerant flow rates in the 3rd intermediate heat exchanger 43 due to the flow velocity of cold-producing medium of flowing in the first and second intermediate heat exchangers 41,42, the pressure loss of the cold-producing medium thus in the first and second intermediate heat exchangers 41,42 is greater than the pressure loss of cold-producing medium in the 3rd intermediate heat exchanger 43.

In the 3rd intermediate heat exchanger 43 above being arranged at air velocity in outdoor machine shell 121 and being higher, because heat exchange performance is higher, its size thus can be made to realize miniaturized.On the other hand, in the first and second intermediate heat exchangers 41,42 being arranged at the below that in outdoor machine shell 121, air velocity is lower, heat-exchange capacity is lower.For this reason, to increase heat exchange amount, the first and second intermediate heat exchangers 41,42 will than be arranged on top time large.

Therefore, outdoor heat exchanger group 40 can not become maximization due to the maximization of the 3rd intermediate heat exchanger 43 and the first and second intermediate heat exchangers 41,42.

If make the first and second intermediate heat exchangers 41,42 realize maximizing, the quantity of the refrigerant path in the first and second intermediate heat exchangers 41,42 will increase.For this reason, in the first and second intermediate heat exchangers 41,42, in each bar refrigerant path, the flow velocity of cold-producing medium reduces, the pressure loss reduction of cold-producing medium when by each bar refrigerant path.Because in the first and second intermediate heat exchangers 41,42, the flow velocity of the cold-producing medium of flowing is originally higher, if thus the increase of refrigerant path quantity makes flow velocity reduce, therefore and greatly the pressure loss will reduce.

On the other hand, if the 3rd intermediate heat exchanger 43 realizes miniaturization, in the 3rd intermediate heat exchanger 43, the quantity of refrigerant path will reduce.If the quantity of refrigerant path reduces, in each bar refrigerant path, the flow velocity of cold-producing medium will be accelerated, the pressure loss increase of cold-producing medium when by each bar refrigerant path.

But the flow velocity of the cold-producing medium of flowing is originally lower in the 3rd intermediate heat exchanger 43, though thus flow velocity because refrigerant path quantity reduces, some is accelerated, it is also smaller for resulting from this increase of the pressure loss.

Therefore, when the 3rd intermediate heat exchanger 43 is arranged on above the first and second intermediate heat exchangers 41,42, the maximization of outdoor heat exchanger group 40 can be suppressed, the pressure loss of cold-producing medium in the first and second intermediate heat exchangers 41,42 can also be reduced simultaneously.

As shown in Figure 2, in the second intermediate heat exchanger 42 that the pressure of flowed into cold-producing medium is higher, the density of its cold-producing medium is greater than the refrigerant density in the first lower intermediate heat exchanger 41 of flowed into refrigerant pressure.For this reason, if in the first intermediate heat exchanger 41 and the second intermediate heat exchanger 42, the mass flow of the cold-producing medium of flowing is roughly equal respectively, then in the first intermediate heat exchanger 41, the volume flow of cold-producing medium will be greater than the volume flow of the cold-producing medium of flowing in the second intermediate heat exchanger 42.Even if the quantity of the refrigerant path in the first intermediate heat exchanger 41 and the second intermediate heat exchanger 42 is roughly equal, also be greater than the refrigerant flow rates in the second intermediate heat exchanger 42 due to the flow velocity of cold-producing medium of flowing in the first intermediate heat exchanger 41, the pressure loss of the cold-producing medium thus in the first intermediate heat exchanger 41 is greater than the pressure loss of the cold-producing medium in the second intermediate heat exchanger 42.In the first intermediate heat exchanger 41 being arranged at the below that in outdoor machine shell 121, air velocity is lower, because heat-exchange capacity does not improve, its size is not thus made to realize miniaturized.Because the quantity of bar refrigerant path each in the first intermediate heat exchanger 41 does not reduce, thus the pressure loss of cold-producing medium does not increase.As mentioned above, the pressure loss of cold-producing medium in the first intermediate heat exchanger 41 can be suppressed to increase.

-effect of the first embodiment-

According to above-mentioned first embodiment, because by top higher for air velocity in casing 121 disposed in the outdoor for outdoor heat converter 44, so the heat exchange performance of outdoor heat converter 44 can be improved.Also because by top higher for air velocity in outdoor heat converter 44 casing disposed in the outdoor 121 lower for refrigerant flow rates, so refrigerant pressure loss can not be made with increasing to realize the miniaturization of outdoor heat converter 44.

On the other hand, by below lower for air velocity in the first to the three intermediate heat exchanger 41,42,43 casing 121 disposed in the outdoor being increased the quantity of refrigerant path, thus can reliably prevent the pressure loss of cold-producing medium in the first to the three intermediate heat exchanger 41,42,43 from increasing.

As mentioned above, miniaturization is realized by the outdoor heat converter 44,162 of more difficult for the pressure loss of cold-producing medium increase being arranged on top, thus the size of outdoor heat exchanger group 40 can be suppressed to increase, the pressure loss of cold-producing medium in the first to the three intermediate heat exchanger 41,42,43 can also be suppressed simultaneously.

Because by top higher for air velocity in the 3rd intermediate heat exchanger 43 casing disposed in the outdoor 121, so the heat exchange performance of the 3rd intermediate heat exchanger 43 can be improved.Also because by top higher for air velocity in the 3rd intermediate heat exchanger 43 casing disposed in the outdoor 121 lower for refrigerant flow rates, so refrigerant pressure loss increase ground can not be made can to realize the miniaturization of the 3rd intermediate heat exchanger 43.

On the other hand, by below lower for air velocity in refrigerant flow rates faster the first and second intermediate heat exchangers 41,42 casing 121 disposed in the outdoor being increased the quantity of refrigerant path, thus can reliably prevent the pressure loss of cold-producing medium in the first and second intermediate heat exchangers 41,42 from increasing.

As mentioned above, miniaturization is realized by the 3rd intermediate heat exchanger 43 of more difficult for the pressure loss of cold-producing medium increase being arranged on top, thus the size of outdoor heat exchanger group 40 can be suppressed to increase, the pressure loss of cold-producing medium in other intermediate heat exchanger 41,42 can also be suppressed simultaneously.

By below lower for air velocity in refrigerant flow rates faster the first intermediate heat exchanger 41 casing disposed in the outdoor 121 being increased the quantity of refrigerant path, thus can reliably prevent the pressure loss of cold-producing medium in the first intermediate heat exchanger 41 from increasing.Thereby, it is possible to suppress the pressure loss of cold-producing medium in the first intermediate heat exchanger 41.

Second embodiment > of < invention

Then, the second embodiment of the present invention is described.As shown in Figure 8, the aircondition 1 involved by second embodiment of the invention is from the difference of the aircondition 1 involved by above-mentioned first embodiment: the structure of refrigerant loop is different.In addition, in the second embodiment of the present invention, only the structure different from above-mentioned first embodiment is illustrated, and to identical parts mark same symbol.

Specifically, in the refrigerant loop 10 involved by the invention described above second embodiment, be provided with 1a supercooling heat exchanger 103,1b supercooling heat exchanger 104 and these three supercooling heat exchangers of 1c supercooling heat exchanger 105.

-structure in loop-

Described 1a supercooling heat exchanger 103 comprises high-pressure side stream 103a and low-pressure side stream 103b.1a supercooling heat exchanger 103 is configured to: make to carry out heat exchange between the cold-producing medium that flows in high-pressure side stream 103a and low-pressure side stream 103b, make the cold-producing medium flowing through high-pressure side stream 103a by supercooling.

Be connected with inflow pipe 60 at the inflow end of described high-pressure side stream 103a, be connected with 1a branched pipe 62a using as supercooling path at the inflow end of low-pressure side stream 103b.This 1a branched pipe 62a is provided with supercooling 2a expansion valve 81a.This 2a expansion valve 81a is made up of aperture adjustable electron expansion valve.One end of first ascending pipe 107 is connected with the outflow end of low-pressure side stream 103b.

Described one end of first ascending pipe 107 is connected with the low-pressure side stream 103b of 1a supercooling heat exchanger 103, and the other end is connected with the 3rd refrigerant tubing 72.In addition, the other end of the first ascending pipe 107 is connected with the outflow side of the check-valves CV10 on the 3rd refrigerant tubing 72.Described 1a supercooling heat exchanger 103 and 2a expansion valve 81a form so-called economizer.

Described 1b supercooling heat exchanger 104 comprises high-pressure side stream 104a and low-pressure side stream 104b.1b supercooling heat exchanger 104 is configured to: make to carry out heat exchange between the cold-producing medium that flows in high-pressure side stream 104a and low-pressure side stream 104b, make the cold-producing medium flowing through high-pressure side stream 104a by supercooling.

Be connected with inflow pipe 60 at the inflow end of described high-pressure side stream 104a, be connected with 1b branched pipe 62b using as supercooling path at the inflow end of low-pressure side stream 104b.This 1b branched pipe 62b is provided with supercooling 2b expansion valve 81b.This 2b expansion valve 81b is made up of aperture adjustable electron expansion valve.One end of second ascending pipe 108 is connected with the outflow end of low-pressure side stream 104b.

Described one end of second ascending pipe 108 is connected with the low-pressure side stream 104b of 1b supercooling heat exchanger 104, and the other end is connected with second refrigerant pipeline 71.In addition, the other end of the second ascending pipe 108 is connected with the outflow side of the check-valves CV9 on second refrigerant pipeline 71.Described 1b supercooling heat exchanger 104 and 2b expansion valve 81b form so-called economizer.

Described 1c supercooling heat exchanger 105 comprises high-pressure side stream 105a and low-pressure side stream 105b.1c supercooling heat exchanger 105 is configured to: make to carry out heat exchange between the cold-producing medium that flows in high-pressure side stream 105a and low-pressure side stream 105b, make the cold-producing medium flowing through high-pressure side stream 105a by supercooling.

Be connected with inflow pipe 60 at the inflow end of described high-pressure side stream 105a, be connected with 1c branched pipe 62c using as supercooling path at the inflow end of low-pressure side stream 105b.This 1c branched pipe 62c is provided with supercooling 2c expansion valve 81c.This 2c expansion valve 81c is made up of aperture adjustable electron expansion valve.One end of 3rd ascending pipe 109 is connected with the outflow end of low-pressure side stream 105b.

Described one end of 3rd ascending pipe 109 is connected with the low-pressure side stream 105b of 1c supercooling heat exchanger 105, and the other end is connected with the first refrigerant tubing 70.In addition, the other end of the 3rd ascending pipe 109 is connected with the outflow side of the check-valves CV8 on the first refrigerant tubing 70.Described 1c supercooling heat exchanger 105 and 2c expansion valve 81c form so-called economizer.

-motion in loop-

Then, be described with reference to the motion situation of Fig. 8 and Fig. 9 to each supercooling heat exchanger 103,104,105 and each expansion valve 81a, 81b, 81c.In addition, the explanation to the action identical with above-mentioned first embodiment is omitted.

The cold-producing medium having obtained compressing in the 4th compression unit 24 of described four-stage compressor 20 is sprayed by towards the 4th bleed pipe 28.By repeatedly alternately carrying out compressing and cooling in four-stage compressor 20 and the first to the three intermediate heat exchanger 41,42,43, thus make the compression process of described four-stage compressor 20 close to isotherm compression, seek to reduce the compression power needed for described four-stage compressor 20.

The cold-producing medium of flowing in the 4th bleed pipe 28 is by inflow outdoor heat exchanger 44 after the 4th four-way change-over valve 96.In outdoor heat converter 44, cold-producing medium is cooled towards outdoor air heat release.The cold-producing medium be cooled in outdoor heat converter 44 flows into the 4th refrigerant tubing 73.In the 4th refrigerant tubing 73 flowing cold-producing medium by check-valves CV11 after flow into inflow pipe 60.

In inflow pipe 60, a part for the cold-producing medium of flowing flows into 1a branched pipe 62a.The cold-producing medium (27 in Fig. 8 and Fig. 9) flowed in 1a branched pipe 62a is reduced pressure by 2a expansion valve 81a.The cold-producing medium (28 in Fig. 8 and Fig. 9) reduced pressure by 2a expansion valve 81a flows into the low-pressure side stream 103b of 1a supercooling heat exchanger 103.On the other hand, in inflow pipe 60, the remainder of the cold-producing medium of flowing flows into the high-pressure side stream 103a (27 in Fig. 8 and Fig. 9) of 1a supercooling heat exchanger 103.In 1a supercooling heat exchanger 103, between the cold-producing medium flowed in high-pressure side stream 103a and low-pressure side stream 103b, carry out heat exchange, make the cold-producing medium flowing through high-pressure side stream 103a by supercooling.

After the cold-producing medium having flowed out the high-pressure side stream 103a of 1a supercooling heat exchanger 103 flows through inflow pipe 60 (31 in Fig. 8 and Fig. 9) again, flow into the high-pressure side stream 104a of 1b supercooling heat exchanger 104.On the other hand, the cold-producing medium (29 in Fig. 8 and Fig. 9) having flowed out the low-pressure side stream 103b of 1a supercooling heat exchanger 103 flows into the first ascending pipe 107.After cold-producing medium inflow the 3rd refrigerant tubing 72 of flowing in the first ascending pipe 107, converge (8 in Fig. 8 and Fig. 9) with the cold-producing medium (30 in Fig. 8 and Fig. 9) in the 3rd refrigerant tubing 72.That is, the cold-producing medium having flowed to the first ascending pipe 107 is injected into the suction side of the 4th compression unit 24.

Then, after flowing out 1a supercooling heat exchanger 103, in inflow pipe 60, a part for the cold-producing medium of flowing flows into 1b branched pipe 62b.The cold-producing medium (31 in Fig. 8 and Fig. 9) flowed in 1b branched pipe 62b is reduced pressure by 2b expansion valve 81b.The cold-producing medium (32 in Fig. 8 and Fig. 9) reduced pressure by 2b expansion valve 81b flows into the low-pressure side stream 104b of 1b supercooling heat exchanger 104.On the other hand, in inflow pipe 60, the remainder of the cold-producing medium of flowing flows into the high-pressure side stream 104a (31 in Fig. 8 and Fig. 9) of 1b supercooling heat exchanger 104.In 1b supercooling heat exchanger 104, between the cold-producing medium flowed in high-pressure side stream 104a and low-pressure side stream 104b, carry out heat exchange, make the cold-producing medium flowing through high-pressure side stream 104a by supercooling.

After the cold-producing medium having flowed out the high-pressure side stream 104a of 1b supercooling heat exchanger 104 flows through inflow pipe 60 (34 in Fig. 8 and Fig. 9) again, flow into the high-pressure side stream 105a of 1c supercooling heat exchanger 105.On the other hand, the cold-producing medium (33 in Fig. 8 and Fig. 9) having flowed out the low-pressure side stream 104b of 1b supercooling heat exchanger 104 flows into the second ascending pipe 108.After the cold-producing medium inflow second refrigerant pipeline 71 of flowing in the second ascending pipe 108, converge (6 in Fig. 8 and Fig. 9) with the cold-producing medium (5 in Fig. 8 and Fig. 9) in second refrigerant pipeline 71.That is, the cold-producing medium having flowed to the second ascending pipe 108 is injected into the suction side of the 3rd compression unit 23.

Then, after flowing out 1b supercooling heat exchanger 104, in inflow pipe 60, a part for the cold-producing medium of flowing flows into 1c branched pipe 62c.The cold-producing medium (34 in Fig. 8 and Fig. 9) flowed in 1c branched pipe 62c is reduced pressure by 2c expansion valve 81c.The cold-producing medium (35 in Fig. 8 and Fig. 9) reduced pressure by 2c expansion valve 81c flows into the low-pressure side stream 105b of 1c supercooling heat exchanger 105.On the other hand, in inflow pipe 60, the remainder of the cold-producing medium of flowing flows into the high-pressure side stream 105a (34 in Fig. 8 and Fig. 9) of 1c supercooling heat exchanger 105.In 1c supercooling heat exchanger 105, between the cold-producing medium flowed in high-pressure side stream 105a and low-pressure side stream 105b, carry out heat exchange, make the cold-producing medium flowing through high-pressure side stream 105a by supercooling.

After the cold-producing medium having flowed out the high-pressure side stream 105a of 1c supercooling heat exchanger 105 flows through inflow pipe 60 (38 in Fig. 8 and Fig. 9) again, flow into the high-pressure side stream 101a of the second supercooling heat exchanger 101.On the other hand, the cold-producing medium (36 in Fig. 8 and Fig. 9) having flowed out the low-pressure side stream 105b of 1c supercooling heat exchanger 105 flows into the first ascending pipe 107.After in the first ascending pipe 107, the cold-producing medium of flowing flows into the first refrigerant tubing 70, converge (3 in Fig. 8 and Fig. 9) with the cold-producing medium (37 in Fig. 8 and Fig. 9) in the first refrigerant tubing 70.That is, the cold-producing medium having flowed to the 3rd ascending pipe 109 is injected into the suction side of the second compression unit 22.Other structure, effect are all identical with the first embodiment.

3rd embodiment > of < invention

Then, the 3rd embodiment of the present invention is described.As shown in Figure 10, the aircondition 140 involved by third embodiment of the invention is from the difference of the aircondition 1 involved by above-mentioned first embodiment: the structure of refrigerant loop is different.In addition, in the 3rd embodiment of the present invention, only the structure different from above-mentioned first embodiment is illustrated.

Specifically, the aircondition 140 involved by the 3rd embodiment of the present invention is described.This aircondition 140 comprises the refrigerant loop 143 being configured to reversibly switch flow of refrigerant, and is configured to carry out cold and hot switching.This aircondition 140 comprises setting outdoor unit 142 without and the indoor units 141 be arranged within doors.The refrigerant loop 143 of above-mentioned aircondition 140 is that the indoor loop 145 that the outdoor loop 144 that has of outdoor unit 142 and indoor units 141 have is formed by connecting by gas side connecting pipe 146 and hydraulic fluid side connecting pipe 147.Carbon dioxide has been enclosed (hereinafter referred to as cold-producing medium in this refrigerant loop 143.), and be configured to: this cold-producing medium is circulated in refrigerant loop 143, thus can multiple compression supercritical refrigeration cycle be carried out.

The outdoor loop > of <

As shown in Figure 10, in described outdoor loop 144, be connected with double-stage compressor 150, outdoor heat exchanger group 160, first and second four-way change-over valve 175,176, first and second supercooling heat exchanger 191,192, the first to the five expansion valve 201 ~ 205, decompressor 193 and gas-liquid separator 194.Described outdoor heat exchanger group 160 comprises intermediate heat exchanger 161 and outdoor heat converter 162.

Except above-mentioned inscape, be also connected with two gs-oil separators 174,174, current divider 173, capillary 170, bridge circuit 172 and check-valves CV1 ~ CV7.

In third embodiment of the invention, by switching the first and second four-way change-over valves 175,176, thus the running of described refrigerant loop 143 is switched to cooling operation or heats running.

Described double-stage compressor 150 comprises the first and second compression units 151,152, forms multi-stage compression portion involved in the present invention.Be connected with the first and second bleed pipes 153,154 in the ejection side of the first and second compression units 151,152, be connected with the first and second suction lines 155,156 in the suction side of the first and second compression units 151,152.In each compression unit 151,152, the low-pressure gaseous refrigerant sucked is compressed to authorized pressure and becomes high-pressure gaseous refrigerant, then this high-pressure gaseous refrigerant is sprayed from each bleed pipe 153,154 by each suction line 155,156.

First valve port of described first four-way change-over valve 175 is connected with the first bleed pipe 153 of the first compression unit 151, second valve port of this first four-way change-over valve 175 is connected with the end side of collecting fitting 187,3rd valve port of this first four-way change-over valve 175 is connected with the end side of intermediate heat exchanger 161, and the 4th valve port of this first four-way change-over valve 175 is connected with the second suction line 156 of the second compression unit 152.This first four-way change-over valve 175 to be communicated with the 3rd valve port and the first state (by the state shown in solid line in Figure 10) of being communicated with the 4th valve port of the second valve port and the first valve port to be communicated with the 4th valve port and to switch between the second state (by the state shown in dotted line in Figure 10) of being communicated with the 3rd valve port of the second valve port at the first valve port.

First valve port of described second four-way change-over valve 176 is connected with the second bleed pipe 154 of the second compression unit 152, second valve port of this second four-way change-over valve 176 is connected with the end side of tube connector 186,3rd valve port of this second four-way change-over valve 176 is connected with the end side of outdoor heat converter 162, and the 4th valve port of this second four-way change-over valve 176 is connected with gas side connecting pipe 146.This second four-way change-over valve 176 to be communicated with the 3rd valve port and the first state (by the state shown in solid line in Figure 10) of being communicated with the 4th valve port of the second valve port and the first valve port to be communicated with the 4th valve port and to switch between the second state (by the state shown in dotted line in Figure 10) of being communicated with the 3rd valve port of the second valve port at the first valve port.

At this, be connected with check-valves CV1 in the midway of the second suction line 156.Check-valves CV1 allows cold-producing medium to circulate from the first four-way change-over valve 175 towards described double-stage compressor 150, and stops cold-producing medium to circulate in the opposite direction.

Gs-oil separator 174,174 is connected in the midway of the first and second bleed pipes 153,154.This gs-oil separator 174,174 is used for the lubricating oil be included in the high-pressure gaseous refrigerant flowing through this bleed pipe 153,154 to separate from this high-pressure gaseous refrigerant.On this gs-oil separator 174,174, be connected with the oily effuser 171,171 that the lubricating oil that makes to separate in this gs-oil separator 174,174 flows out towards this gs-oil separator 174,174 outside.

Specifically, the oily effuser 171 of the gs-oil separator 174 corresponding to described first bleed pipe 153 is connected with described second suction line 156.The oily effuser 171 of the gs-oil separator 174 corresponding to described second bleed pipe 154 is connected with described first suction line 155.In addition, capillary 170,170 is connected in the midway of each oily effuser 171,171.

Described intermediate heat exchanger 161 and outdoor heat converter 162 are configured to Gilled heat exchanger.This intermediate heat exchanger 161 forms intermediate heat exchange part involved in the present invention, and outdoor heat converter 162 forms outdoor heat exchange department involved in the present invention.Near each heat exchanger 161,162, be provided with outdoor fan 122, and each heat exchanger 161,162 is configured to: between the outdoor air sent here by this outdoor fan 122 and the cold-producing medium flowed in the heat-transfer pipe of each heat exchanger 161,162, carry out heat exchange.

At this, one end of described intermediate heat exchanger 161 is connected with the 3rd valve port of described first four-way change-over valve 175, and one end of described outdoor heat converter 162 is connected with the 3rd valve port of described second four-way change-over valve 176.On the other hand, the other end of described intermediate heat exchanger 161 is connected with the first refrigerant tubing 181, and the other end of outdoor heat converter 162 is connected with second refrigerant pipeline 182.

After the other end branch of described second refrigerant pipeline 182, an arm is connected with described bridge circuit 172 and another arm exports P2 with the second of described current divider 173 is connected.In addition, export between P2 at the branch of described second refrigerant pipeline 182 and the second of described current divider and be provided with check-valves CV3 and capillary 170.This check-valves CV3 allows cold-producing medium from described current divider 173 towards the circulation of the branch of described second refrigerant pipeline 182, and stops cold-producing medium to circulate in the opposite direction.

After the other end branch of described first refrigerant tubing 181, an arm is connected to the midway (between check-valves CV1 with the second compression unit 152) of described second suction line 156 and another arm is connected with the first-class outlet P1 of described current divider 173.In addition, between the branch and the first-class outlet P1 of described current divider 173 of described first refrigerant tubing 181, check-valves CV2 and capillary 170 is provided with.This check-valves CV2 allows cold-producing medium from described current divider 173 towards the circulation of the branch of described first refrigerant tubing 181, and stops cold-producing medium to circulate in the opposite direction.Check-valves CV4 is provided with between the branch and the connecting portion of described second suction line 156 of described first refrigerant tubing 181.This check-valves CV4 allows cold-producing medium to circulate from the branch of described first refrigerant tubing 181 towards the connecting portion of described second suction line 156, and stops cold-producing medium to circulate in the opposite direction.

Described bridge circuit 172 is loops check-valves CV5, CV6, CV7 and the 5th expansion valve 205 bridge-type coupled together.In bridge circuit 172, the link of the inflow side and another side of the 5th expansion valve 205 that are positioned at check-valves CV7 is connected with the first effuser 180, and the link of the outflow side and the inflow side of check-valves CV6 that are positioned at check-valves CV7 is connected with hydraulic fluid side connecting pipe 147.In addition, on refrigerant tubing hydraulic fluid side connecting pipe 147 and the first indoor heat converter 211 coupled together, the first indoor expansion valve 206 that aperture is variable is provided with.On refrigerant tubing hydraulic fluid side connecting pipe 147 and the second indoor heat converter 212 coupled together, be provided with the second indoor expansion valve 207 that aperture is variable.The link of the outflow side and the outflow side of check-valves CV5 that are positioned at check-valves CV6 is connected with inflow pipe 179.Be connected with current divider 173 in the end side of the 5th expansion valve 205, the inflow end of check-valves CV5 is connected with second refrigerant pipeline 182.

The first supercooling heat exchanger 191, decompressor 193, gas-liquid separator 194 and the second supercooling heat exchanger 192 is connected with in turn in the midway of described inflow pipe 179.

Described first supercooling heat exchanger 191 comprises high-pressure side stream 191a and low-pressure side stream 191b.First supercooling heat exchanger 191 is configured to: make to carry out heat exchange between the cold-producing medium that flows in high-pressure side stream 191a and low-pressure side stream 191b, make the cold-producing medium flowing through high-pressure side stream 191a by supercooling.

Be connected with inflow pipe 179 at the inflow end of described high-pressure side stream 191a, be connected with the first branched pipe 177 using as supercooling path at the inflow end of low-pressure side stream 191b.This first branched pipe 177 is provided with supercooling the second expansion valve 202.This second expansion valve 202 is made up of through regulating variable electric expansion valve aperture.One end of ascending pipe 188 is connected with the outflow end of low-pressure side stream 191b.

One end of described ascending pipe 188 is connected with the low-pressure side stream 191b of the first supercooling heat exchanger 191, and the other end is connected with the first refrigerant tubing 181.In addition, the other end of ascending pipe 188 is connected with the outflow side of the check-valves CV4 on the first refrigerant tubing 181.

Described decompressor 193 comprises and is formed as the columnar decompressor casing of lengthwise, and this decompressor 193 is arranged between the first supercooling heat exchanger 191 on inflow pipe 179 and gas-liquid separator 194.Be provided with in the inside of decompressor casing and make cold-producing medium expand and produce the expansion mechanism of power.Decompressor 193 forms so-called rotary displacement fluid mechanism.Decompressor 193 is configured to: the cold-producing medium flowed into is expanded, and is again sent towards inflow pipe 179 by the cold-producing medium after expanding.

Described inflow pipe 179 is provided with the shunt valve 183 walking around described decompressor 193.The end side of shunt valve 183 is connected with the inflow side of decompressor 193, and another side of this shunt valve 183 is connected with the outflow side of decompressor 193, thus walks around decompressor 193.This shunt valve 183 is provided with the first expansion valve 201.This first expansion valve 201 is made up of through regulating variable electric expansion valve aperture.

Described gas-liquid separator 194 is made up of the cylindric closed container of lengthwise.On gas-liquid separator 194, be connected with inflow pipe 179, first effuser 180 and the second effuser 184.Inflow pipe 179 is uncovered towards the top of gas-liquid separator 194 inner space.First effuser 180 is uncovered towards the below of gas-liquid separator 194 inner space.Second effuser 184 is uncovered towards the top of gas-liquid separator 194 inner space.In gas-liquid separator 194, the cold-producing medium flowed into from inflow pipe 179 is separated into saturated liquid and saturated gas, and saturated liquid flows out from the first effuser 180, and saturated gas flows out from the second effuser 184.

The end side of described second effuser 184 is connected with gas-liquid separator 194, and another side is connected to the midway of the second branched pipe 178.This second effuser 184 is provided with the 4th expansion valve 204.4th expansion valve 204 is made up of through regulating variable electric expansion valve aperture.

Second supercooling heat exchanger 192 is connected to the midway of described first effuser 180.This second supercooling heat exchanger 192 comprises high-pressure side stream 192a and low-pressure side stream 192b.Second supercooling heat exchanger 192 is configured to: make to carry out heat exchange between the cold-producing medium that flows in high-pressure side stream 192a and low-pressure side stream 192b, make the cold-producing medium flowing through high-pressure side stream 192a by supercooling.

The inflow end of described high-pressure side stream 192a is connected with the outflow side of gas-liquid separator 194, and the outflow end of this high-pressure side stream 192a is connected with bridge circuit 172.Be connected with the second branched pipe 178 using as supercooling path at the inflow end of low-pressure side stream 192b, the outflow end of low-pressure side stream 192b is connected with another side of return duct 185.

The end side of described second branched pipe 178 is connected between gas-liquid separator 194 on the first effuser 180 and the second supercooling heat exchanger 192, another side of this second branched pipe 178 is connected with the inflow end of the low-pressure side stream 192b of the second supercooling heat exchanger 192, is connected with the second effuser 184 in the midway of this second branched pipe 178.This second branched pipe 178 is provided with the 3rd expansion valve 203.3rd expansion valve 203 is made up of through regulating variable electric expansion valve aperture.

One end of described return duct 185 is connected with the other end of tube connector 186, and the other end of this return duct 185 is connected with the outflow end of the low-pressure side stream 192b of the second supercooling heat exchanger 192.

The end side of described tube connector 186 is connected with the second valve port of the second four-way change-over valve 176, another side of this tube connector 186 is connected with the other end of one end of return duct 185 and the first suction line 155, and the other end of collecting fitting 187 is connected to the midway of this tube connector 186.

The end side of described collecting fitting 187 is connected with the second valve port of the first four-way change-over valve 175, and another side of this collecting fitting 187 is connected to the midway of tube connector 186.

The indoor loop > of <

In indoor loop 145, the first indoor expansion valve 206 and the first indoor heat converter 211 is disposed with from its liquid side towards gas side, and be also disposed with the second indoor expansion valve 207 and the second indoor heat converter 212 from its liquid side towards gas side, this first indoor expansion valve 206 and the first indoor heat converter 211, be connected in parallel to each other with the second indoor expansion valve 207 and the second indoor heat converter 212.Each indoor expansion valve 206,207 is made up of aperture adjustable electron expansion valve.Each indoor heat converter 211,212 is made up of tubes provided with cross ribs plate heat exchanger.Near each indoor heat converter 211,212, be respectively arranged with indoor fan room air being sent to each indoor heat converter 211,212, but this and not shown come.Further, in each indoor heat converter 211,212, between cold-producing medium and room air, heat exchange is carried out.

The structure > of the outdoor unit of <

As shown in figure 12, outdoor unit 142 comprises outdoor machine shell 163.Outdoor machine shell 163 is formed as the casing of the rectangular shape of lengthwise, is formed with the suction inlet 164 of air in the below in this outdoor machine shell 163 front, and is formed with the blow-off outlet 165 of air at the upper surface of this outdoor machine shell 163.Outdoor heat exchanger group 160 and outdoor fan 166 is provided with in the inside of outdoor machine shell 163.

Described outdoor fan 166 is used to the fan air be drawn in outdoor machine shell 163 being sent to each heat exchanger 161,162, and is configured to so-called Sirocco fan.Outdoor fan 166 is arranged in the top of each heat exchanger 161,162 in outdoor machine shell 163.Further, this air after the air making to suck from suction inlet 164 is by each heat exchanger 161,162, then blows out from blow-off outlet 165 by outdoor fan 166 towards the outside.

As shown in figure 12, in the inside of outdoor machine shell 163, outdoor heat exchanger group 160 to be piled up successively towards upside from downside and is provided with intermediate heat exchanger 161 and outdoor heat converter 162.That is, outdoor heat converter 162 is arranged on the top of intermediate heat exchanger 161.

Each heat exchanger 161,162 described is made up of so-called tubes provided with cross ribs plate heat exchanger.Each heat exchanger 161,162 comprises: multiple heat transfer tube group and the thermofin respectively with many heat-transfer pipes and Duo Gen U-shaped pipe.

Described multiple heat transfer tube group is arranged in sequence with setting up and down and forms.In each heat transfer tube group, many heat-transfer pipes along air flow direction up and down each one two ground be set altogether be arranged to three row, side of being in the wind is configured with the first pipe row, is configured with the second pipe row in central authorities, is configured with the 3rd pipe row in leeward side.That is, each heat transfer tube group is arranged to: heat-transfer pipe is all two-tube at each row.

-motion-

Then, the motion of aircondition 140 is described.In this aircondition 140, by switching the first and second four-way change-over valves 175,176, thus the running of described refrigerant loop 143 is switched to cooling operation or heats running.In addition, what 1 to 18 in Figure 10 and Figure 11 represented is the pressure state of cold-producing medium.

-cooling operation-

Be described with reference to the cooling operation of Figure 10 to aircondition 140.In Fig. 10, the flowing of the cold-producing medium when this cooling operation is represented with solid arrow.Under cooling operation, make outdoor heat converter 162 play radiator, make each indoor heat converter 211,212 play evaporimeter, thus carry out two-stage compression supercritical refrigeration cycle.Intermediate heat exchanger 161 plays the cooler to the high-pressure refrigerant of ejection cools from the first compression unit 151.

Under cooling operation, all four-way change-over valves 175,176 are all configured to the first state, and double-stage compressor 150 drives.When double-stage compressor 150 drives, in each compression unit 151,152, cold-producing medium is compressed.The cold-producing medium having obtained compressing in the first compression unit 151 is sprayed (2 in Figure 10 and Figure 11) by towards the first bleed pipe 153.In addition, in the gs-oil separator 174 now on the first bleed pipe 153, the lubricating oil be included in the gaseous refrigerant flowing through this first bleed pipe 153 is separated.The lubricating oil separated is sent to the second suction line 156 from oily effuser 171.Further, the cold-producing medium of flowing in the first bleed pipe 153 is by flowing into intermediate heat exchanger 161 after the first four-way change-over valve 175.In intermediate heat exchanger 161, cold-producing medium is cooled towards outdoor air heat release.The cold-producing medium be cooled in intermediate heat exchanger 161 flows into the first refrigerant tubing 181.In the first refrigerant tubing 181 cold-producing medium (3 in Figure 10 and Figure 11) of flowing by check-valves CV4 after converge with the cold-producing medium that flows in ascending pipe 188, then flow into the second suction line 156 and be inhaled into the second compression unit 152 (4 in Figure 10 and Figure 11).

The cold-producing medium (5 in Figure 10 and Figure 11) having obtained compressing in the second compression unit 152 is sprayed by towards the second bleed pipe 154.Alternately carry out compressing and cooling as mentioned above, thus make the compression process of described double-stage compressor 150 close to isotherm compression, seek to reduce the compression power needed for described double-stage compressor 150.In addition, in the gs-oil separator 174 now on the second bleed pipe 154, the lubricating oil be included in the gaseous refrigerant flowing through this second bleed pipe 154 is separated.The lubricating oil be separated is sent to the first suction line 155 from oily effuser 171.The cold-producing medium of flowing in the second bleed pipe 154 is by inflow outdoor heat exchanger 162 after the second four-way change-over valve 176.In outdoor heat converter 162, cold-producing medium is cooled towards outdoor air heat release.The cold-producing medium be cooled in outdoor heat converter 162 flows into second refrigerant pipeline 182.In second refrigerant pipeline 182, the cold-producing medium of flowing is by flowing into inflow pipe 179 after check-valves CV5.

In inflow pipe 179, a part for the cold-producing medium (6 in Figure 10 and Figure 11) of flowing flows into the first branched pipe 177.In the first branched pipe 177, the cold-producing medium of flowing is reduced pressure by the second expansion valve 202.The cold-producing medium (7 in Figure 10 and Figure 11) reduced pressure by the second expansion valve 202 flows into the low-pressure side stream 191b of the first supercooling heat exchanger 191.On the other hand, in inflow pipe 179, the remainder of the cold-producing medium of flowing flows into the high-pressure side stream 191a (6 in Figure 10 and Figure 11) of the first supercooling heat exchanger 191.In the first supercooling heat exchanger 191, between the cold-producing medium flowed in high-pressure side stream 191a and low-pressure side stream 191b, carry out heat exchange, make the cold-producing medium flowing through high-pressure side stream 191a by supercooling.

The cold-producing medium having flowed out the high-pressure side stream 191a of the first supercooling heat exchanger 191 flows through inflow pipe 179 again, and the cold-producing medium having flowed out the low-pressure side stream 191b of the first supercooling heat exchanger 191 on the other hand flows into ascending pipe 188.After in ascending pipe 188, the cold-producing medium (8 in Figure 10 and Figure 11) of flowing flows into the first refrigerant tubing 181, converge (4 in Figure 10 and Figure 11) with the cold-producing medium in the first refrigerant tubing 181.That is, the cold-producing medium having flowed to ascending pipe 188 is injected into the suction side of the second compression unit 152.

After the cold-producing medium having flowed out the high-pressure side stream 191a of the first supercooling heat exchanger 191 flows through inflow pipe 179 (9 in Fig. 1 and Fig. 2) again, a part for this cold-producing medium flows into decompressor 193.In decompressor 193, the cold-producing medium flowed into is expanded (in Figure 10 and Figure 11 9 to 11), then the cold-producing medium after expansion is sent towards inflow pipe 179 again.On the other hand, shunt valve 183 is flowed to after having flowed out the remainder shunting of the cold-producing medium of the high-pressure side stream 191a of the first supercooling heat exchanger 191.The cold-producing medium of flowing in shunt valve 183 is reduced pressure after (in Figure 10 and Figure 11 9 to 10) by the first expansion valve 201 and again returns inflow pipe 179.The cold-producing medium having flowed out decompressor 193 and the cold-producing medium having flowed out shunt valve 183 converge (12 in Figure 10 and Figure 11) and flow into gas-liquid separator 194 afterwards in inflow pipe 179.In gas-liquid separator 194, the cold-producing medium flowed into is separated into gaseous refrigerant (15 in Figure 10 and Figure 11) and liquid refrigerant (13 in Figure 10 and Figure 11).

After the liquid refrigerant (13 in Figure 10 and Figure 11) of effluent gases liquid/gas separator 194 flows through inflow pipe 179, a part for this cold-producing medium flows into the second branched pipe 178.On the other hand, in inflow pipe 179, the remainder of the cold-producing medium of flowing flows into the high-pressure side stream 192a of the second supercooling heat exchanger 192.

Reduce pressure after (18 in Figure 10 and Figure 11) by the 4th expansion valve 204 after the gaseous refrigerant (15 in Figure 10 and Figure 11) of effluent gases liquid/gas separator 194 flows through the second effuser 184, flow into the second branched pipe 178.Further, in the second branched pipe 178, the cold-producing medium of flowing is reduced pressure by the 3rd expansion valve 203.The cold-producing medium (17 in Figure 10 and Figure 11) reduced pressure by the 3rd expansion valve 203 and the cold-producing medium flowed in the second effuser 184 converge.

The cold-producing medium converged flows into the low-pressure side stream 192b of the second supercooling heat exchanger 192.In the second supercooling heat exchanger 192, between the cold-producing medium flowed in high-pressure side stream 192a and low-pressure side stream 192b, carry out heat exchange, make the liquid refrigerant flowing through high-pressure side stream 192a by supercooling.

The liquid refrigerant (14 in Figure 10 and Figure 11) having flowed out the high-pressure side stream 192a of the second supercooling heat exchanger 192 flows through the first effuser 180 again, influent side connecting pipe 147 after the check-valves CV7 passing through bridge circuit 172.On the other hand, the cold-producing medium having flowed out the low-pressure side stream 192b of the second supercooling heat exchanger 192 flows in return duct 185.The cold-producing medium having flowed out return duct 185 converges with the cold-producing medium flowing out tube connector 186.The cold-producing medium converged flows into the suction side of the first compression unit 151.

In hydraulic fluid side connecting pipe 147, a part for the liquid refrigerant of flowing is reduced pressure by the first indoor expansion valve 206 after shunting.The cold-producing medium (16a in Figure 10 and Figure 11) be depressurized flows into the first indoor heat converter 211.In the first indoor heat converter 211, liquid refrigerant heat absorption and evaporating in air indoor.The gaseous refrigerant inflow gas side connecting pipe 146 of having evaporated.

In hydraulic fluid side connecting pipe 147, the remainder of the liquid refrigerant of flowing is reduced pressure by the second indoor expansion valve 207.The cold-producing medium (16b in Figure 10 and Figure 11) be depressurized flows into the second indoor heat converter 212.In the second indoor heat converter 212, liquid refrigerant heat absorption and evaporating in air indoor.The gaseous refrigerant inflow gas side connecting pipe 146 of having evaporated.

In gas side connecting pipe 146, the cold-producing medium flowed out from the first indoor heat converter 211 converges with the cold-producing medium flowed out from the second indoor heat converter 212.The cold-producing medium of flowing in gas side connecting pipe 146 is by flowing into tube connector 186 after the second four-way change-over valve 176.The first suction line 155 is flowed into after the cold-producing medium flowed in tube connector 186 and the cold-producing medium flowed in return duct 185 converge.In the first suction line 155, the cold-producing medium (1 in Figure 10 and Figure 11) of flowing is compressed again in the first compression unit 151 of double-stage compressor 150.

-heat running-

Then, be described with reference to the running that heats of Figure 13 to this aircondition 140.In fig. 13, the flowing of the cold-producing medium when this heats running is represented with dotted arrow.Under this heats running, make each indoor heat converter 211,212 play radiator, make intermediate heat exchanger 161 and outdoor heat converter 162 play evaporimeter, thus carry out two-stage compression supercritical refrigeration cycle.

Heating under running, all four-way change-over valves 175,176 are all configured to the second state, and double-stage compressor 150 drives.When double-stage compressor 150 drives, in each compression unit 151,152, cold-producing medium is compressed.The cold-producing medium having obtained compressing in the first compression unit 151 is sprayed by towards the first bleed pipe 153.In addition, in the gs-oil separator 174 now on the first bleed pipe 153, the lubricating oil be included in the gaseous refrigerant flowing through this first bleed pipe 153 is separated.The lubricating oil be separated is sent to the second suction line 156 from oily effuser 171.Further, the cold-producing medium flowed in the first bleed pipe 153 is by being inhaled into the second compression unit 152 after the first four-way change-over valve 175.In the second compression unit 152, cold-producing medium is further compressed.As mentioned above, different from cooling operation, do not carry out Two-stage Compression with cooling when heating running.Thus, with along with cool carry out Two-stage Compression situation compared with, from double-stage compressor 150, the temperature of cold-producing medium of ejection does not reduce.Consequently, with along with cool carry out Two-stage Compression situation compared with, heating capacity when heating running increases.

The cold-producing medium sprayed from the second compression unit 152 is by being sent to the first and second indoor heat converters 211,212 after the second four-way change-over valve 176.In the first and second indoor heat converters 211,212, cold-producing medium is cooled towards room air heat release.The cold-producing medium be cooled in each indoor heat converter 211,212 is sent to bridge circuit 172 after being reduced pressure by the first and second indoor expansion valve 206,207.Further, this cold-producing medium is by flowing into inflow pipe 179 after check-valves CV6.

In inflow pipe 179, a part for the cold-producing medium of flowing flows into the first branched pipe 177.In the first branched pipe 177, the cold-producing medium of flowing is reduced pressure by the second expansion valve 202.The cold-producing medium reduced pressure by the second expansion valve 202 flows into the low-pressure side stream 191b of the first supercooling heat exchanger 191.On the other hand, in inflow pipe 179, the remainder of the cold-producing medium of flowing flows into the high-pressure side stream 191a of the first supercooling heat exchanger 191.In the first supercooling heat exchanger 191, between the cold-producing medium flowed in high-pressure side stream 191a and low-pressure side stream 191b, carry out heat exchange, make the cold-producing medium flowing through high-pressure side stream 191a by supercooling.

The cold-producing medium having flowed out the high-pressure side stream 191a of the first supercooling heat exchanger 191 flows through inflow pipe 179 again, and the cold-producing medium having flowed out the low-pressure side stream 191b of the first supercooling heat exchanger 191 on the other hand flows into ascending pipe 188.After in ascending pipe 188, the cold-producing medium of flowing flows into the first refrigerant tubing 181, converge with the cold-producing medium in the first refrigerant tubing 181.That is, the cold-producing medium having flowed to ascending pipe 188 is injected into the suction side of the second compression unit 152.

After the cold-producing medium having flowed out the high-pressure side stream 191a of the first supercooling heat exchanger 191 flows through inflow pipe 179 again, a part for this cold-producing medium flows into decompressor 193.In decompressor 193, the cold-producing medium flowed into is expanded, then the cold-producing medium after expansion is sent towards inflow pipe 179 again.On the other hand, shunt valve 183 is flowed to after having flowed out the remainder shunting of the cold-producing medium of the high-pressure side stream 191a of the first supercooling heat exchanger 191.In shunt valve 183, the cold-producing medium of flowing returns inflow pipe 179 after being reduced pressure by the first expansion valve 201 again.Gas-liquid separator 194 is flowed into after the cold-producing medium having flowed out decompressor 193 and the cold-producing medium having flowed out shunt valve 183 converge in inflow pipe 179.In gas-liquid separator 194, the cold-producing medium flowed into is separated into gaseous refrigerant and liquid refrigerant.

After the liquid refrigerant of effluent gases liquid/gas separator 194 flows through the first effuser 180, a part for this cold-producing medium flows into the second branched pipe 178.On the other hand, in the first effuser 180, the remainder of the cold-producing medium of flowing flows into the high-pressure side stream 192a of the second supercooling heat exchanger 192.

The gaseous refrigerant of effluent gases liquid/gas separator 194 flows in the second effuser 184, after being reduced pressure, flows into the second branched pipe 178 by the 4th expansion valve 204.Further, in the second branched pipe 178, the cold-producing medium of flowing is reduced pressure by the 3rd expansion valve 203.The cold-producing medium reduced pressure by the 3rd expansion valve 203 and the cold-producing medium flowed in the second effuser 184 converge.

The liquid refrigerant having flowed out the high-pressure side stream 192a of the second supercooling heat exchanger 192 flows through the first effuser 180 again, after the 5th expansion valve 205 by bridge circuit 172 reduces pressure, is sent to current divider 173.The cold-producing medium be assigned with in current divider 173 is by flowing into intermediate heat exchanger 161 and outdoor heat converter 162 after capillary 170 and check-valves CV2, CV3.In intermediate heat exchanger 161 and outdoor heat converter 162, liquid refrigerant heat absorption and evaporating in air outdoor.The cold-producing medium flowed out from intermediate heat exchanger 161, by flowing into collecting fitting 187 after the first four-way change-over valve 175, then flows into tube connector 186.

The cold-producing medium flowed out in heat exchanger 162 outdoor, by flowing into tube connector 186 after the second four-way change-over valve 176, converges with the cold-producing medium flowed out from intermediate heat exchanger 161.The cold-producing medium converged flows and converges with the cold-producing medium flowed in return duct 185 in tube connector 186.The cold-producing medium converged flows into the first suction line 155.In the first suction line 155, the cold-producing medium of flowing is compressed again in the first compression unit 151 of double-stage compressor 150.

-outdoor unit-

As shown in figure 12, flow to above outdoor machine shell 163 after the air being inhaled into outdoor machine shell 163 inside from suction inlet 164 carries out heat exchange intermediate heat exchanger 161 and outdoor heat converter 162 and be blown from blow-off outlet 165 again.

At this, described outdoor unit 142 suction inlet 164 be configured to from the side sucks again from blow-off outlet 165 blow out air, so-called upper blowing type upward after air, and the air velocity thus above suction inlet 164 is than fast below it.As shown in figure 11, in intermediate heat exchanger 161, the pressure of the cold-producing medium that the pressure ratio of the cold-producing medium of flowing flows in outdoor heat converter 162 is low, and thus in intermediate heat exchanger 161, the density of the cold-producing medium of flowing is less than the density of the cold-producing medium of flowing in outdoor heat converter 162.For this reason, if in intermediate heat exchanger 161 and outdoor heat converter 162, the mass flow of the cold-producing medium of flowing is roughly equal respectively, then in intermediate heat exchanger 161, the volume flow of cold-producing medium will be greater than the volume flow of the cold-producing medium of flowing in outdoor heat converter 162.Even if the quantity of the refrigerant path in intermediate heat exchanger 161 and outdoor heat converter 162 is roughly equal, also the refrigerant flow rates owing to flowing in intermediate heat exchanger 161 is greater than the refrigerant flow rates in outdoor heat converter 162, and the pressure loss of the cold-producing medium thus in intermediate heat exchanger 161 is greater than the pressure loss of cold-producing medium in outdoor heat converter 162.

In outdoor heat converter 162 above being arranged at air velocity in outdoor machine shell 163 and being higher, because heat exchange performance is higher, its size thus can be made to realize miniaturized.On the other hand, in the intermediate heat exchanger 161 being arranged at the below that air velocity is lower in outdoor machine shell 163, heat-exchange capacity is lower.For this reason, to increase heat exchange amount, intermediate heat exchanger 161 will than be arranged on top time large.

Therefore, outdoor heat exchanger group 160 can not become maximization due to the maximization of outdoor heat converter 162 and intermediate heat exchanger 161.

If make intermediate heat exchanger 161 realize maximizing, in intermediate heat exchanger 161, the quantity of refrigerant path will increase.For this reason, in intermediate heat exchanger 161, in each bar refrigerant path, the flow velocity of cold-producing medium reduces, the pressure loss reduction of cold-producing medium when by each bar refrigerant path.Because in intermediate heat exchanger 161, the flow velocity of the cold-producing medium of flowing is originally higher, if thus the increase of refrigerant path quantity makes flow velocity reduce, therefore and greatly the pressure loss will reduce.

On the other hand, if outdoor heat converter 162 realizes miniaturization, in outdoor heat converter 162, the quantity of refrigerant path will reduce.If refrigerant path quantity reduces, in each bar refrigerant path, the flow velocity of cold-producing medium will be accelerated, the pressure loss increase of cold-producing medium when by each bar refrigerant path.

But the flow velocity of the cold-producing medium of flowing is originally lower in outdoor heat converter 162, though thus flow velocity because refrigerant path quantity reduces, some is accelerated, it is also smaller for resulting from this increase of the pressure loss.

Therefore, when being arranged on above intermediate heat exchanger 161 by outdoor heat converter 162, the maximization of outdoor heat exchanger group 160 can be suppressed, the pressure loss of cold-producing medium in intermediate heat exchanger 161 can also be reduced simultaneously.

-effect of three embodiment-

According to above-mentioned 3rd embodiment, because by top higher for air velocity in casing 163 disposed in the outdoor for outdoor heat converter 162, so the heat exchange performance of outdoor heat converter 162 can be improved.Also because by top higher for air velocity in outdoor heat converter 162 casing disposed in the outdoor 163 lower for refrigerant flow rates, so refrigerant pressure loss can not be made with increasing to realize the miniaturization of outdoor heat converter 162.

On the other hand, by below lower for air velocity in casing 163 disposed in the outdoor for intermediate heat exchanger 161 being increased the quantity of refrigerant path, thus can reliably prevent the pressure loss of cold-producing medium in intermediate heat exchanger 161 from increasing.

As mentioned above, miniaturization is realized by the outdoor heat converter 162 of more difficult for the pressure loss of cold-producing medium increase being arranged on top, thus the size of outdoor heat exchanger group 160 can be suppressed to increase, the pressure loss of cold-producing medium in intermediate heat exchanger 161 can also be suppressed simultaneously.Other structure, effect are all identical with the second embodiment with the first embodiment.

-variation of three embodiment-

Then, be described with reference to the variation of accompanying drawing to the 3rd embodiment of the present invention.Aircondition involved by this variation is from the difference of the aircondition 140 involved by above-mentioned 3rd embodiment: the structure of heat exchanger is different.In addition, in this variation, only the structure different from above-mentioned 3rd embodiment is illustrated.

Specifically, as shown in Figure 14 and Figure 15, outdoor unit 142 comprises outdoor machine shell 163.Outdoor machine shell 163 is formed as the casing of the rectangular shape of lengthwise, is formed with the suction inlet 164 of air in the below in this outdoor machine shell 163 front, and is formed with the blow-off outlet 165 of air at the upper surface of this outdoor machine shell 163.Outdoor heat exchanger group 160 and outdoor fan 166 is provided with in the inside of outdoor machine shell 163.Outdoor heat exchanger group 160 comprises outdoor heat converter 162 and intermediate heat exchanger 161.

As shown in figure 14, in the inside of outdoor machine shell 163, to pile up successively from downside towards upside and be provided with intermediate heat exchanger 161 and outdoor heat converter 162.

-structure of heat exchanger-

As shown in Figure 14 and Figure 15, each heat exchanger 161,162 of this variation comprises: a first total collection pipe 240, second total collection pipe 250, many flat tubes 231 and multiple fin 235.First total collection pipe 240, second total collection pipe 250, flat tube 231 and fin 235 are all aluminium alloy part, are engaged with each other together through soldering.

First total collection pipe 240 and the second total collection pipe 250 are all formed as elongated hollow tubular.In each heat exchanger 161,162, the first total collection pipe 240 founds the end side being arranged on flat tube 231, and the second total collection pipe 250 stands another side being arranged on flat tube 231.That is, the first total collection pipe 240 and the second total collection pipe 250 with respective axially for vertical direction downward-extension on the ground.

Upper end and the bottom of the first total collection pipe 240 are closed, and the bottom of this first total collection pipe 240 is connected with the first tube connector 240b.First tube connector 240b is communicated with the hydraulic fluid side of refrigerant loop 143.That is, the first total collection pipe 240 forms the hydraulic fluid side collector that the cold-producing medium (liquid single-phase refrigerant or gas-liquid two-phase cold-producing medium) that comprises liquid flows through.Upper end and the bottom of the second total collection pipe 250 are closed, above this second total collection pipe 250, be connected with the second tube connector 250b.Second tube connector 250b is connected with the gas side of refrigerant loop 143.That is, the second total collection pipe 250 forms the gas side collector that gaseous refrigerant flows through.

Each heat exchanger 161,162 of this variation has many flat tubes 231.The heat-transfer pipe of flat tube 231 to be its section shapes perpendicular to axle be flat Long Circle or rectangle.In each heat exchanger 161,162, many flat tubes 231 are with its bearing of trend for left and right directions, and respective flattened side form toward each other sets.Many flat tubes 231 are arranged above and below and arrange with keeping certain intervals each other.The first total collection pipe 240 is inserted in one end of each flat tube 231, and the second total collection pipe 250 is inserted in the other end of each flat tube 231.

As shown in figure 15, in each flat tube 231, many refrigerant path 232 are formed with.Each bar refrigerant path 232 is the paths extended along the bearing of trend of flat tube 231.In each flat tube 231, many refrigerant path 232 form a line along the width orthogonal with the bearing of trend of flat tube 231.The one end being formed in refrigerant path 232 in each flat tube 231 respective communicates with the inner space of the first total collection pipe 240, and the respective other end communicates with the inner space of the second total collection pipe 250.In addition, described refrigerant path 232 forms fluid passage involved in the present invention.

Fin 235 is the corrugated fin bending extension up and down, is arranged between neighbouring flat tube 231.Fin 235 is formed the multiple heat transfer parts 236 be arranged on flat tube 231 bearing of trend.Heat transfer part 236 is formed as from the flat tube in adjacent flat tube 231 until the tabular of another flat tube.On heat transfer part 236, be provided with and a part for this heat transfer part 236 cut and the multiple louver board portions (louver) 237 formed.Downward-extension is gone up abreast with the leading edge (that is, the end of windward side) of heat transfer part 236 in fact by these louver board portions 237.On heat transfer part 236, each louver board portion 237 to arrange from windward side towards leeward side and is formed.

At leeward one side end of heat transfer part 236, be connected to the projecting plate portion 238 that side is outstanding more alee.Projecting plate portion 238 is formed as the trapezoidal tabular more outstanding more up and down than heat transfer part 236.In each heat exchanger 161,162, neighbouring projecting plate portion 238,238 overlaps in a thickness direction, contacts with each other in fact.

Be provided with many flat tubes 231 and multiple fin 235,235.Fin 235,235 is provided with between the flat tube 231 be arranged above and below.In intermediate heat exchange part 41,42,43,161, air passes through between the flat tube 231 be arranged above and below, and the fluid flowed in this air and fluid passage 232 in flat tube 231 carries out heat exchange.

In intermediate heat exchanger 161, because flowing resistance reduces, the flow velocity of thus flowed air is accelerated.Also because the heat transfer area of cold-producing medium increases by flat tube 231, therefore the heat exchange performance of cold-producing medium is improved.For this reason, the COP (coefficient of performance) of refrigerating plant improves.Because the caliber of flat tube 231 is less than existing heat-transfer pipe, so velocity in pipes increases.For this reason, increased by the pressure loss of the cold-producing medium of refrigerant path 232.

But in the intermediate heat exchanger 161 being arranged at the below that air velocity is lower in outdoor machine shell 163, heat-exchange capacity is lower.For this reason, to increase heat exchange amount, intermediate heat exchanger 161 will than be arranged on top time large.If intermediate heat exchanger 161 increases, in intermediate heat exchanger 161, the quantity of refrigerant path 232 will increase, thus in intermediate heat exchanger 161, in each bar refrigerant path 232, the flow velocity of cold-producing medium reduces, the pressure loss reduction of cold-producing medium when by each bar refrigerant path 232.Therefore, even if the increase causing refrigerant pressure loss to increase due to the caliber path using flat tube 231 to cause also is smaller.

In outdoor heat exchange department 162, because flowing resistance reduces, the flow velocity of thus flowed air is accelerated.Also because the heat transfer area of cold-producing medium increases by flat tube 231, thus the heat exchange performance of cold-producing medium is improved.For this reason, the COP (coefficient of performance) of refrigerating plant improves.Because the caliber of flat tube 231 is less than existing heat-transfer pipe, so velocity in pipes increases.For this reason, increased by the pressure loss of the cold-producing medium of refrigerant path 232.

But the flow velocity of the cold-producing medium of flowing is originally lower in outdoor heat exchange department 162, even if thus make flow velocity because adopting flat tube 231 to make caliber realize path, some is accelerated, and it is also smaller for resulting from this increase of the pressure loss.

According to described variation, be configured to owing to making intermediate heat exchanger 161 and outdoor heat exchange department 162: include the many flat tubes 231 and multiple fin 235,235 that are formed with many refrigerant path 232, thus can reduce flowing resistance.For this reason, the flow velocity of the air flowed in ventilation path is accelerated.Also because the heat transfer area of cold-producing medium increases by flat tube 231, thus the heat exchange performance of cold-producing medium is improved.For this reason, the COP (coefficient of performance) of aircondition can be made to improve.Other structure, effect are all identical with the 3rd embodiment.

< reference example >

Then, reference example is described.In this reference example, as shown in Figure 18 and Figure 19, in indoor units, wind speed profile is all equal distribution in the vertical direction.

In outdoor heat exchanger group 40 involved by this reference example, pile up successively from downside towards upside and be provided with outdoor heat converter 44, first intermediate heat exchanger 41, second intermediate heat exchanger 42 and the 3rd intermediate heat exchanger 43.In addition, also can be arranged to: turned upside down in the position of the first intermediate heat exchanger 41 and the second intermediate heat exchanger 42.

The size of each heat exchanger is formed as: increase successively according to the order of outdoor heat converter 44, the 3rd intermediate heat exchanger 43, first intermediate heat exchanger 41 and the second intermediate heat exchanger 42.

Each heat exchanger 41,42,43,44 described is made up of so-called tubes provided with cross ribs plate heat exchanger.Each heat exchanger 41,42,43,44 comprises: multiple heat transfer tube group 50 and the thermofin 51 respectively with many heat-transfer pipes 52 and Duo Gen U-shaped pipe.

Described multiple heat transfer tube group about 50 is arranged in sequence with setting and forms.In each heat transfer tube group 50, many heat-transfer pipes 52 along air flow direction up and down each one two ground be set altogether be arranged to three row, the first pipe row 53 are configured with in the left side (i.e. windward side) of Figure 19, be configured with the second pipe row 54 in the central authorities of Figure 19, be configured with the 3rd pipe row 55 on the right side (i.e. leeward side) of Figure 19.That is, each heat transfer tube group 50 is arranged to: heat-transfer pipe 52 is all two-tube at each row.

Other embodiment of < >

The present invention also can adopt following structure in above-mentioned first embodiment and the second embodiment.

In above-mentioned first embodiment and the second embodiment, employ four-stage compressor 20, but the present invention is not limited to this structure, two double-stage compressors also can be set.

In above-mentioned first embodiment ~ the 4th embodiment, be set as two-stage compression supercritical refrigeration cycle and four stage compression type supercritical refrigeration cycle, but the present invention is not limited to this, such as three stage compression formula supercritical refrigeration cycle and other multiple compression kind of refrigeration cycle also can be applied to.

In above-mentioned first embodiment and the second embodiment, be pipe type by the configuration settings of heat exchanger, but the present invention is not limited to this.

Specifically, as shown in figure 16, outdoor unit 3 comprises outdoor machine shell 121.Outdoor machine shell 121 is formed as the casing of the rectangular shape of lengthwise, is formed with the suction inlet 123 of air in the below in this outdoor machine shell 121 front, and is formed with the blow-off outlet 124 of air at the upper surface of this outdoor machine shell 121.Outdoor heat exchanger group 40 and outdoor fan 122 is provided with in the inside of outdoor machine shell 121.Outdoor heat exchanger group 40 comprises: outdoor heat converter 44, first intermediate heat exchanger 41, second intermediate heat exchanger 42 and the 3rd intermediate heat exchanger 43.

As shown in figure 16, in the inside of outdoor machine shell 121, pile up successively from downside towards upside and be provided with the first intermediate heat exchanger 41, second intermediate heat exchanger 42, the 3rd intermediate heat exchanger 43 and outdoor heat converter 44.That is, outdoor heat converter 44 is arranged on than on the first to the three intermediate heat exchanger 41,42,43 position by the top.In addition, now also can be arranged to: turned upside down in the position of the first intermediate heat exchanger 41 and the second intermediate heat exchanger 42.

-structure of heat exchanger-

As shown in Figure 16 and Figure 17, each heat exchanger 41,42,43,44 of the manner comprises respectively: a first total collection pipe 240, second total collection pipe 250, many flat tubes 231 and multiple fin 235.First total collection pipe 240, second total collection pipe 250, flat tube 231 and fin 235 are all aluminium alloy part, are engaged with each other together through soldering.

First total collection pipe 240 and the second total collection pipe 250 are all formed as elongated hollow tubular.In each heat exchanger 41,42,43,44, the first total collection pipe 240 founds the end side being arranged on flat tube 231, and the second total collection pipe 250 stands another side being arranged on flat tube 231.That is, the first total collection pipe 240 and the second total collection pipe 250 with respective axially for vertical direction downward-extension on the ground.

Upper end and the bottom of the first total collection pipe 240 are closed, and are connected with the first tube connector 240b on its lower end.First tube connector 240b is communicated with the hydraulic fluid side of refrigerant loop 10.That is, the first total collection pipe 240 forms the hydraulic fluid side collector that the cold-producing medium (liquid single-phase refrigerant or gas-liquid two-phase cold-producing medium) that comprises liquid flows through.Upper end and the bottom of the second total collection pipe 250 are closed, and are connected with the second tube connector 250b above it.Second tube connector 250b is connected with the gas side of refrigerant loop 143.That is, the second total collection pipe 250 forms the gas side collector that gaseous refrigerant flows through.

Each heat exchanger 41,42,43,44 of the manner has many flat tubes 231.The heat-transfer pipe of flat tube 231 to be its section shapes perpendicular to axle be flat Long Circle or rectangle.In each heat exchanger 41,42,43,44, many flat tubes 231 are with its bearing of trend for left and right directions, and respective flattened side form toward each other sets.Many flat tubes 231 are arranged above and below and arrange with keeping certain intervals each other.The first total collection pipe 240 is inserted in one end of each flat tube 231, and the second total collection pipe 250 is inserted in the other end of each flat tube 231.

As shown in figure 17, in each flat tube 231, many refrigerant path 232 are formed with.Each bar refrigerant path 232 is the paths extended along the bearing of trend of flat tube 231, and is configured to fluid passage involved in the present invention.In each flat tube 231, many refrigerant path 232 form a line along the width orthogonal with the bearing of trend of flat tube 231.The respective one end of refrigerant path 232 in each flat tube 231 communicates with the inner space of the first total collection pipe 240, and the respective other end communicates with the inner space of the second total collection pipe 250.

Fin 235 is the corrugated fin bending extension up and down, and is arranged between neighbouring flat tube 231.Fin 235 is formed the multiple heat transfer parts 236 be arranged on flat tube 231 bearing of trend.Heat transfer part 236 is formed as from the flat tube in adjacent flat tube 231 until the tabular of another flat tube.On heat transfer part 236, be provided with and a part for this heat transfer part 236 cut and the multiple louver board portions 237 formed.Downward-extension is gone up abreast with the leading edge (that is, the end of windward side) of heat transfer part 236 in fact by these louver board portions 237.On heat transfer part 236, each louver board portion 237 to arrange from windward side towards leeward side and is formed.

At leeward one side end of heat transfer part 236, be connected to the projecting plate portion 238 that side is outstanding more alee.Projecting plate portion 238 is formed as the trapezoidal tabular more outstanding more up and down than heat transfer part 236.In each heat exchanger 41,42,43,44, neighbouring projecting plate portion 238,238 overlaps in a thickness direction, contacts with each other in fact.Other structure, effect are all identical with the variation of the 3rd embodiment.

In addition, above embodiment is preferred example in essence, and the scope of intention to the present invention, its application or its purposes is not limited.

-industrial applicability-

In sum, the present invention is very useful to the refrigerating plant carrying out multiple compression kind of refrigeration cycle.

-symbol description-

21 first compression units

22 second compression units

23 the 3rd compression units

24 the 4th compression units

41 first intermediate heat exchangers

42 second intermediate heat exchangers

43 the 3rd intermediate heat exchangers

44 outdoor heat converters

121 outdoor machine shells

123 suction inlets

151 first compression units

152 second compression units

161 intermediate heat exchangers

162 outdoor heat converters

163 outdoor machine shells

164 suction inlets

231 flat tubes

232 refrigerant path

235 fins

Claims

1. an off-premises station for refrigerating plant, it comprises:

Multi-stage compression portion (20,150), it has the multiple compressing mechanisms (21 ~ 24,151,152) be one another in series, and senior side compressing mechanism (22,23,24,152) compresses after sucking the cold-producing medium that rudimentary side compressing mechanism (21,22,23,151) sprays

Intermediate heat exchange part (41,42,43,161), it is arranged between adjacent two described compressing mechanisms (21,22,23,24,151,152), make to flow to the cold-producing medium of senior side compressing mechanism (22,23,24,152) from rudimentary side compressing mechanism (21,22,23,151) and outdoor air carries out heat exchange and cools this cold-producing medium

Outdoor heat exchange department (44,162), it makes the cold-producing medium that sprays from highest side compressing mechanism (24,152) and outdoor air carry out heat exchange, and

Casing (121,163), the side of this casing (121,163) is formed the suction inlet (123,164) of air, and on the upper surface of this casing (121,163), be formed with the blow-off outlet (124,165) of air, in this casing (121,163), be accommodated with described compressing mechanism (21 ~ 24,151,152), intermediate heat exchange part (41,42,43,161) and outdoor heat exchange department (44,162), it is characterized in that:

Described intermediate heat exchange part (41,42,43,161) and described outdoor heat exchange department (44,162) are arranged with the state erected along the suction inlet (123,164) of described casing (121,163), and described outdoor heat exchange department (44,162) is arranged in than on all described intermediate heat exchange part (41,42,43,161) position all by the top.

2. the off-premises station of refrigerating plant according to claim 1, is characterized in that:

Described multi-stage compression portion (20) has the compressing mechanism (21 ~ 24) of more than three,

Highest side intermediate heat exchange part (43) is arranged in than other intermediate heat exchange part (41,42) by the top and than on described outdoor heat exchange department (44) position on the lower.

3. the off-premises station of refrigerating plant according to claim 2, is characterized in that:

Multiple described intermediate heat exchange part (41,42,43) is arranged to: the pressure flowing into the cold-producing medium of described intermediate heat exchange part is higher, and this intermediate heat exchange part is located in position more by the top.

4. the off-premises station of refrigerating plant according to claim 1, is characterized in that:

Described intermediate heat exchange part (41,42,43,161) comprises many flat tubes (231) and multiple fin (235,235), these many flat tubes (231) are arranged above and below in side mode in opposite directions and are formed with many fluid passages (232) extended along pipe range direction in inside, the plurality of fin (235,235) will be divided into air and flows through many ventilation path between adjacent described flat tube (231).

5. the off-premises station of refrigerating plant according to claim 4, is characterized in that:

Described outdoor heat exchange department (44,162) comprises many flat tubes (231) and multiple fin (235,235), these many flat tubes (231) are arranged above and below in side mode in opposite directions and are formed with many fluid passages (232) extended along pipe range direction in inside, the plurality of fin (235,235) will be divided into air and flows through many ventilation path between adjacent described flat tube (231).