CN103635752A - Outdoor machine of refrigeration device - Google Patents

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 that carries out multi-stage compression formula kind of refrigeration cycle.

Background technology

Up to now, as utilizing the cold-producing medium in supercritical region work to carry out one of refrigerating plant of multi-stage compression formula kind of refrigeration cycle, exist a kind of as Patent Document 1, with carbon dioxide, as cold-producing medium, carry out the aircondition of two-stage compression kind of refrigeration cycle.This aircondition is by carrying out after cooling allowing rear class one side compression member suck this cold-producing medium to the cold-producing medium spraying from prime one side compression member with intercooler again, thereby reduce from the temperature of the cold-producing medium of rear class one side compression member ejection, reduce the radiation loss of outdoor heat converter.

In the aircondition shown in patent documentation 1, as shown in figure 20, intercooler a and heat source side heat exchanger b are incorporated in thermal source unit c.In thermal source unit c, on its side, be provided with intercooler a and heat source side heat exchanger b.And intercooler a is arranged in the top of heat source side heat exchanger b.Above intercooler a, be provided with heat source side fan.

Patent documentation 1: Japanese Laid-Open Patent Publication JP 2009-150641 communique

Summary of the invention

-invent technical problem to be solved-

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

At this, in intercooler a, the pressure of the pressure ratio of mobile cold-producing medium mobile cold-producing medium in heat source side heat exchanger b is low, thereby the density of density ratio mobile cold-producing medium in heat source side heat exchanger b of mobile cold-producing medium is little in intercooler a.For this reason, if respectively in intercooler a and heat source side heat exchanger b the mass flow of mobile cold-producing medium about equally, the volume flow of the cold-producing medium in intercooler a will be greater than the volume flow of cold-producing medium mobile 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 about equally, also the flow velocity due to cold-producing medium mobile in intercooler a is greater than the cold-producing medium flow velocity in heat source side heat exchanger b, thereby the pressure loss of the cold-producing medium 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, with regard to the problem that there will be the pressure loss of cold-producing medium in intercooler a to increase.On the other hand, if suppress cold-producing medium the pressure loss increase and intercooler a realized and maximize, will produce the problem that thermal source unit c maximizes.

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

-in order to the technical scheme of technical solution problem-

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

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, middle heat exchange department 41, 42, 43, 161, outdoor heat exchange department 44, 162 and casing 121, 163, this multi-stage compression portion 20, 150 have a plurality of compressing mechanisms 21～24 that are one another in series, 151, 152, and a senior side compressing mechanism 22, 23, 24, 152 suck a rudimentary side compressing mechanism 21, 22, 23, after 151 cold-producing mediums that spray, compress this centre heat exchange department 41, 42, 43, 161 are arranged on two adjacent described compressing mechanisms 21, 22, 23, 24, 151, between 152, make from a rudimentary side compressing mechanism 21, 22, 23, 151 flow to a senior side compressing mechanism 22, 23, 24, 152 cold-producing medium and outdoor air carry out heat exchange and this cold-producing medium is carried out cooling, this outdoor heat exchange department 44, 162 make from a highest side compressing mechanism 24, cold-producing medium and the outdoor air of 152 ejections carry out heat exchange, at this casing 121, on 163 side, be formed with the suction inlet 123 of air, 164, and at this casing 121, on 163 upper surface, be formed with the blow-off outlet 124 of air, 165, at this casing 121, in 163, taken in described compressing mechanism 21～24, 151, 152, middle heat exchange department 41, 42, 43, 161 and outdoor heat exchange department 44, 162.The state setting that in the middle of described, heat exchange department 41,42,43,161 and described outdoor heat exchange department 44,162 erect with the suction inlet 123,164 along described casing 121,163, and described outdoor heat exchange department 44,162 is arranged in than on the position of heat exchange department 41,42,43,161 top sides in the middle of described.

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

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

After the air that is inhaled into casing 121,163 inside from suction inlet 123,164 carries out heat exchange middle heat exchange department 41,42,43,161 and outdoor heat exchange department 44,162, flow to casing 121,163 above from blow-off outlet 124,165, be blown again.

At this, off-premises station of the present invention is configured to after suction inlet 123,164 air amounts from the side from blow-off outlet 124,165 towards upper blowing type top blow out air, so-called, thereby the air velocity of suction inlet 123,164 tops is faster than its below.In middle heat exchange department 41,42,43,161, the pressure of the pressure ratio of mobile cold-producing medium mobile cold-producing medium in outdoor heat exchange department 44,162 is low, thereby the density of mobile cold-producing medium is less than the density of cold-producing medium mobile in outdoor heat exchange department 44,162 in middle heat exchange department 41,42,43,161.For this reason, if respectively in middle heat exchange department 41,42,43,161 and outdoor heat exchange department 44,162 mass flow of mobile cold-producing medium about equally, in the middle of in heat exchange department 41,42,43,161 volume flow of cold-producing medium will be greater than the volume flow of cold-producing medium mobile in outdoor heat exchange department 44,162.Even if the quantity of the refrigerant path in middle heat exchange department 41,42,43,161 and outdoor heat exchange department 44,162 about equally, also the flow velocity due to cold-producing medium mobile in middle heat exchange department 41,42,43,161 is greater than the cold-producing medium flow velocity in outdoor heat exchange department 44,162, thereby the pressure loss of the cold-producing medium in middle heat exchange department 41,42,43,161 is greater than the pressure loss of cold-producing medium in outdoor heat exchange department 44,162.

Be arranged at casing 121,163 interior air velocitys higher above outdoor heat exchange department 44,162 in, because heat exchange performance is higher, thereby can make its size realize miniaturization.On the other hand, be arranged at casing 121,163 interior air velocitys lower below middle heat exchange department 41,42,43,161 in, heat-exchange capacity is lower.For this reason, if will increase heat exchange amount, middle heat exchange department 41,42,43,161 will be larger than time above being arranged on.

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

If heat exchange department 41,42,43,161 is realized and being maximized in the middle of making, in middle heat exchange department 41,42,43,161, the quantity of refrigerant path will increase.For this reason, in middle heat exchange department 41,42,43,161, in each refrigerant path, the flow velocity of cold-producing medium reduces, and the pressure loss of cold-producing medium reduces when by each refrigerant path.Because the flow velocity of cold-producing medium mobile in middle heat exchange department 41,42,43,161 is originally higher, if thereby the increase of refrigerant path quantity flow velocity is reduced, therefore the pressure loss will reduce greatly.

On the other hand, if outdoor heat exchange department 44,162 is realized miniaturization, in outdoor heat exchange department 44,162, the quantity of refrigerant path will reduce.If the quantity of refrigerant path reduces, in each refrigerant path, the flow velocity of cold-producing medium will be accelerated, and the pressure loss of cold-producing medium increases when by each refrigerant path.

Yet the flow velocity of mobile cold-producing medium is originally lower in outdoor heat exchange department 44,162, even thereby flow velocity because refrigerant path quantity reduces some, accelerate, it is also smaller resulting from this increase of the pressure loss.

Therefore, in the situation that outdoor heat exchange department 44,162 being arranged on above middle heat exchange department 41,42,43,161, can suppress the maximization of off-premises station, the pressure loss of cold-producing medium in heat exchange department 41,42,43,161 in the middle of can also reducing simultaneously.

The invention of second aspect is such, in the invention of described first aspect, described multi-stage compression portion 20 has three above compressing mechanisms 21～24, and in the middle of a highest side, heat exchange department 43 is arranged in than heat exchange department 41,42 top sides in the middle of other 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 three above compressing mechanisms 21～24, after the cold-producing medium that the rudimentary side compressing mechanism 21,22,23 of senior side compressing mechanism 22,23,24 suction sprays, compresses.For this reason, be provided with a plurality of middle heat exchange departments 41,42,43, in the middle of a highest side, heat exchange department 43 is arranged on than on the position of heat exchange department 41,42 top sides in the middle of other.In the middle of a highest side, heat exchange department 43 is also arranged on than on outdoor heat exchange department 44 position on the lower.

Due to the pressure ratio of cold-producing medium mobile in highest one heat exchange department 43 in the middle of side in the middle of other in heat exchange department 41,42 pressure of mobile cold-producing medium high, thereby in the middle of other in heat exchange department 41,42 density ratio of mobile cold-producing medium in the middle of a highest side in heat exchange department 43 density of mobile cold-producing medium little.For this reason, if respectively in the middle of other in the middle of heat exchange department 41,42 and a highest side in heat exchange department 43 mass flow of mobile cold-producing medium about equally, in the middle of other, in heat exchange department 41,42, the volume flow of cold-producing medium will be greater than in the middle of a highest side volume flow of mobile cold-producing medium in heat exchange department 43.Even if the quantity of the refrigerant path in the middle of other in heat exchange department 41,42 and the middle heat exchange department 43 of a highest side about equally, also the flow velocity due to cold-producing medium mobile in heat exchange department 41,42 in the middle of other is greater than the cold-producing medium flow velocity in the middle heat exchange department 43 of a highest side, thereby the pressure loss of the cold-producing medium in other middle heat exchange department 41,42 is greater than the pressure loss of cold-producing medium in the middle heat exchange department 43 of a highest side.

Be arranged at the interior air velocity of casing 121 higher above senior one heat exchange department 43 in the middle of side in, because heat exchange performance is higher, thereby can make its size realize miniaturization.On the other hand, be arranged at the interior air velocity of casing 121 lower below other in the middle of in heat exchange department 41,42, heat-exchange capacity is lower.For this reason, if will increase heat exchange amount, in the middle of other, heat exchange department 41,42 will be larger than time above being arranged on.

Therefore, the off-premises station maximization that can not become due to the maximization of senior one heat exchange department 43 in the middle of side and other intermediate heat exchange portion 41,42.

If heat exchange department 41,42 is realized maximization in the middle of making other, in the middle of other, in heat exchange department 41,42, the quantity of refrigerant path will increase.For this reason, in heat exchange department 41,42, in each refrigerant path, the flow velocity of cold-producing medium reduces in the middle of other, and the pressure loss of cold-producing medium reduces when by each refrigerant path.Because the flow velocity of cold-producing medium mobile in heat exchange department 41,42 in the middle of other is originally higher, if thereby the increase of refrigerant path quantity flow velocity is reduced, therefore the pressure loss will reduce greatly.

On the other hand, if heat exchange department 43 is realized miniaturization in the middle of a senior side, in the middle of a senior side, in heat exchange department 43, the quantity of refrigerant path will reduce.If the quantity of refrigerant path reduces, in each refrigerant path, the flow velocity of cold-producing medium will be accelerated, and the pressure loss of cold-producing medium increases when by each refrigerant path.

Yet the flow velocity of mobile cold-producing medium is originally lower in senior one heat exchange department 43 in the middle of side, even thereby flow velocity because refrigerant path quantity reduces some, accelerate, it is also smaller resulting from this increase of the pressure loss.

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

The invention of the third aspect is such, in the invention of described second aspect, a plurality of described in the middle of heat exchange departments 41,42,43 be arranged to: flow into described in the middle of the pressure of cold-producing medium of heat exchange department higher, this centre heat exchange department is located in more top side's position.

In the invention of the third aspect, a plurality of described in the middle of heat exchange departments 41,42,43 be arranged to: flow into described in the middle of the pressure of cold-producing medium of heat exchange department higher, this centre heat exchange department is located in more top side's position.

In the higher middle heat exchange department 42 of flowed into refrigerant pressure, the density of its cold-producing medium is greater than the refrigerant density in the middle heat exchange department 41 that flowed into refrigerant pressure is lower.For this reason, if respectively low pressure one in the middle of side in the middle of heat exchange department 41 and high pressure one side in heat exchange department 42 mass flow of mobile cold-producing medium about equally, in the middle of low pressure one side, in heat exchange department 41, the volume flow of cold-producing medium will be greater than in the middle of high pressure one side the volume flow of mobile cold-producing medium in heat exchange department 42.Even if the quantity of the refrigerant path in the middle of low pressure one side in heat exchange department 41 and the middle heat exchange department 42 of high pressure one side about equally, also the flow velocity due to cold-producing medium mobile in heat exchange department 41 in the middle of low pressure one side is greater than the cold-producing medium flow velocity in the middle heat exchange department 42 of high pressure one side, thereby the pressure loss of the cold-producing medium in the middle heat exchange department 41 of low pressure one side is greater than the pressure loss of cold-producing medium in the middle heat exchange department 42 of high pressure one side.

Be arranged at the interior air velocity of casing 121 higher above high pressure one in the middle of side in heat exchange department 42, because heat exchange performance is higher, thereby can make its size realize miniaturization.On the other hand, be arranged at the interior air velocity of casing 121 lower below low pressure one in the middle of side in heat exchange department 41, heat-exchange capacity is lower.For this reason, if will increase heat exchange amount, in the middle of low pressure one side, heat exchange department 41 will be larger than time above being arranged on.

Therefore, off-premises station can be due to high pressure one maximization of heat exchange department 41 maximization that not become in the middle of heat exchange department 42 and low pressure one side in the middle of side.

If heat exchange department 41 is realized maximization in the middle of making low pressure one side, in the middle of low pressure one side, in heat exchange department 41, the quantity of refrigerant path will increase.For this reason, in low pressure one, in the middle of side in heat exchange department 41, in each refrigerant path, the flow velocity of cold-producing medium reduces, and the pressure loss of cold-producing medium reduces when by each refrigerant path.Due to low pressure one in the middle of side in heat exchange department 41 flow velocity of mobile cold-producing medium originally higher, if thereby the increase of refrigerant path quantity flow velocity is reduced, therefore the pressure loss will reduce greatly.

On the other hand, if heat exchange department 42 is realized miniaturization in the middle of high pressure one side, in the middle of high pressure one side, in heat exchange department 42, the quantity of refrigerant path will reduce.If the quantity of refrigerant path reduces, in each refrigerant path, the flow velocity of cold-producing medium will be accelerated, and the pressure loss of cold-producing medium increases when by each refrigerant path.

Yet, high pressure one in the middle of side in heat exchange department 42 flow velocity of mobile cold-producing medium originally lower, even thereby flow velocity because refrigerant path quantity reduces some, accelerate, it is also smaller resulting from this increase of the pressure loss.

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

The invention of fourth aspect is such, described first in the invention of either side in the third aspect, in the middle of described, heat exchange department 41,42,43,161 comprises many flat tubes 231 and a plurality of fin 235,235, these many flat tubes 231 sides are arranged above and below opposite to each other and in inside, are formed with many fluid passages 232 that extend along pipe range direction, and the plurality of fin 235,235 is by many ventilation roads that are divided into air between adjacent described flat tube 231 and flow through.

In the invention of described fourth aspect, flat tube 231 and fin 235,235 are respectively provided with a plurality of.Between the flat tube 231 being arranged above and below, be provided with fin 235,235.In middle heat exchange department 41,42,43,161, air passes through between the flat tube 231 being arranged above and below, and fluid mobile in this air and the fluid passage 232 in flat tube 231 carries out heat exchange.

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

Yet, be arranged at casing 121,163 interior air velocitys lower below middle heat exchange department 41,42,43,161 in, heat-exchange capacity is lower.For this reason, if will increase heat exchange amount, middle heat exchange department 41,42,43,161 will be larger than time above being arranged on.If middle heat exchange department increases, in middle heat exchange department 41,42,43,161, the quantity of fluid passage 232 will increase, thereby in intermediate heat transformation component 41,42,43,161, in each fluid passage 232, the flow velocity of cold-producing medium reduces, and the pressure loss of cold-producing medium reduces when by each fluid passage 232.

Therefore, even if the increase that causes refrigerant pressure loss to increase due to the caliber path that uses flat tube 231 to cause is also 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 a plurality of fin 235,235, these many flat tubes 231 sides are arranged above and below opposite to each other and in inside, are formed with many fluid passages 232 that extend along pipe range direction, and the plurality of fin 235,235 is by many ventilation roads that are divided into air between adjacent described flat tube 231 and flow through.

In invention aspect the described the 5th, flat tube 231 and fin 235,235 are respectively provided with a plurality of.Between the flat tube 231 being arranged above and below, be provided with fin 235,235.In outdoor heat exchange department 44,162, air passes through between the flat tube 231 being arranged above and below, and fluid mobile in this air and the fluid passage 232 in flat tube 231 carries out heat exchange.

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

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

-effect of invention-

According to the invention of described first aspect, because outdoor heat exchange department 44,162 is arranged on to casing 121, the 163 higher tops of interior air velocity, so can improve the heat exchange performance of outdoor heat exchange department 44,162.Also because the lower outdoor heat exchange department 44,162 of cold-producing medium flow velocity is arranged on to casing 121, the 163 higher tops of interior air velocity, so can not make refrigerant pressure loss increase the miniaturization that realizes outdoor heat exchange department 44,162.

On the other hand, by middle heat exchange department 41,42,43,161 being arranged on to casing 121, the 163 lower belows of interior air velocity, increase the quantity of refrigerant path, thus the pressure loss of cold-producing medium increase in heat exchange department 41,42,43,161 in the middle of can preventing reliably.

As mentioned above, by the outdoor heat exchange department of the more difficult increase of the pressure loss of cold-producing medium 44,162 being arranged on to top, realize miniaturization, thereby the size that can suppress off-premises station increases, the pressure loss of cold-producing medium in heat exchange department 41,42,43,161 simultaneously in the middle of can also suppressing.

According to the invention of described second aspect, because heat exchange department 43 in the middle of a highest side is arranged on to the higher top of the interior air velocity of casing 121, can improve the heat exchange performance of the middle heat exchange department 43 of a highest side.Also because the slower middle heat exchange department 43 of the superlative degree one side of cold-producing medium flow velocity is arranged on to the higher top of the interior air velocity of casing 121, so can not make refrigerant pressure loss increase the miniaturization that realizes the middle heat exchange department 43 of a highest side.

On the other hand, by by cold-producing medium flow velocity faster in the middle of other heat exchange department 41,42 be arranged on the quantity that the lower below of the interior air velocity of casing 121 increases refrigerant path, thereby can prevent reliably in the middle of other in heat exchange department 41,42 that the pressure loss of cold-producing medium increases.

As mentioned above, by being arranged on to top, heat exchange department 43 in the middle of the superlative degree of the more difficult increase of the pressure loss of cold-producing medium one side realizes miniaturization, thereby the size that can suppress off-premises station increases, can also suppress the pressure loss of cold-producing medium in other middle heat exchange department 41,42 simultaneously.

According to the invention of the described third aspect, because heat exchange department 42 in the middle of high pressure one side is arranged on to the higher top of the interior air velocity of casing 121, can improve the heat exchange performance of the middle heat exchange department 42 of high pressure one side.Also because the slower middle heat exchange department 42 of high pressure one side of cold-producing medium flow velocity is arranged on to the higher top of the interior air velocity of casing 121, so can not make refrigerant pressure loss increase the miniaturization that realizes the middle heat exchange department 42 of high pressure one side.

On the other hand, by by cold-producing medium flow velocity faster low pressure one in the middle of side heat exchange department 41 be arranged on the quantity that the lower below of the interior air velocity of casing 121 increases refrigerant path, thereby can prevent reliably in the middle of low pressure one side in heat exchange department 41 that the pressure loss of cold-producing medium increases.

As mentioned above, by being arranged on to top, heat exchange department 42 in the middle of the high pressure of the more difficult increase of the pressure loss of cold-producing medium one side realizes miniaturization, thereby the size that can suppress off-premises station increases, can also suppress the pressure loss of cold-producing medium in the middle heat exchange department 41 of low pressure one side simultaneously.

According to the invention of described fourth aspect, because comprised many flat tubes 231 and a plurality of fin 235,235 that is formed with many fluid passages 232, so can reduce flowing resistance.For this reason, in ventilation road, mobile air velocity increases.Also the heat transfer area due to cold-producing medium increases by flat tube 231, thereby the heat exchange performance of cold-producing medium is improved.For this reason, can improve the COP (coefficient of performance) of refrigerating plant.

According to the invention of described the 5th aspect, because comprised many flat tubes 231 and a plurality of fin 235,235 that is formed with many fluid passages 232, so can reduce flowing resistance.For this reason, in ventilation road, mobile air velocity increases.Also the heat transfer area due to cold-producing medium increases by flat tube 231, thereby the heat exchange performance of cold-producing medium is improved.For this reason, can improve the COP (coefficient of performance) of refrigerating plant.

Accompanying drawing explanation

Fig. 1 means the piping diagram of the cooling operation of the refrigerant loop that first embodiment of the invention is related.

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

Fig. 3 means the figure of the outdoor unit that first embodiment of the invention is related.

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

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

Fig. 6 means the figure of air velocity distribution situation in the related outdoor machine shell of first embodiment of the invention.

Fig. 7 means the piping diagram that heats running of the refrigerant loop that first embodiment of the invention is related.

Fig. 8 means the piping diagram of the cooling operation of the refrigerant loop that second embodiment of the invention is related.

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

Figure 10 means the piping diagram of the cooling operation of the refrigerant loop that third embodiment of the invention is related.

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

Figure 12 means the figure of the outdoor unit that third embodiment of the invention is related.

Figure 13 means the piping diagram that heats running of the refrigerant loop that third embodiment of the invention is related.

Figure 14 means the schematic diagram of the outdoor unit that the variation of third embodiment of the invention is related.

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

Figure 16 means the schematic diagram of the outdoor unit that other embodiment is related.

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

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

Figure 19 is the cutaway view of the related outdoor heat exchanger group of reference example.

Figure 20 means the figure of the outdoor unit that existing example is related.

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

The specific embodiment

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

The first embodiment > of < invention

-refrigerant loop of aircondition-

As shown in Figure 1, the related aircondition 1 of the first embodiment of the present invention is described.This aircondition 1 comprises and is configured to the refrigerant loop 10 that can reversibly switch flow of refrigerant, and is configured to and can carries out cold and hot switching.This aircondition 1 comprises setting outdoor unit 3 without and is arranged on indoor units 2 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.In this refrigerant loop 10, enclosed carbon dioxide (hereinafter referred to as cold-producing medium.), and be configured to: this cold-producing medium is circulated in refrigerant loop 10, thereby can carry out multi-stage compression formula supercritical refrigeration cycle.

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 4th four-way change-over valve 93,94,95,96, the first to the 3rd supercooling heat exchanger 100,101,102, the first to the 5th expansion valve 80～84, decompressor 87 and gas-liquid separator 88.Described outdoor heat exchanger group 40 comprises the first to the 3rd 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 3rd intermediate heat exchanger 41,42,43 forms middle heat exchange department involved in the present invention.The first and second intermediate heat exchangers 41,42 form other middle heat exchange department involved in the present invention, and the 3rd intermediate heat exchanger 43 forms the middle heat exchange department of the superlative degree involved in the present invention one side.

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 4th four-way change-over valve 93,94,95,96, thereby 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 4th compression unit 21,22,23,24, forms multi-stage compression portion involved in the present invention.Ejection side at the first to the 4th compression unit 21,22,23,24 is connected with the first to the 4th bleed pipe 25,26,27,28, is connected with the first to the 4th suction line 29,30,31,32 in the suction side of the first to the 4th compression unit 21,22,23,24.In each compression unit 21,22,23,24, till the gaseous refrigerant sucking 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.

The first valve port of described the first four-way change-over valve 93 is connected with the first bleed pipe 25 of the first compression unit 21, one distolateral being connected of the second valve port of this first four-way change-over valve 93 and collecting fitting 67, the 3rd valve port of this first four-way change-over valve 93 and distolateral being connected of the first intermediate heat exchanger 41, 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.Between the first state that this first four-way change-over valve 93 is communicated with the 3rd valve port at the first valve port and the second valve port is communicated with the 4th valve port (in Fig. 1 with the state shown in solid line) and the first valve port is communicated with the 4th valve port and the second valve port is communicated with the 3rd valve port the second state (in Fig. 1 with the state shown in dotted line), switch.

The first valve port of described the second four-way change-over valve 94 is connected with the second bleed pipe 26 of the second compression unit 22, the second valve port of this second four-way change-over valve 94 is connected to collecting fitting 67 midway, the 3rd valve port of this second four-way change-over valve 94 and distolateral being connected of the second intermediate heat exchanger 42, 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.Between the first state that this second four-way change-over valve 94 is communicated with the 3rd valve port at the first valve port and the second valve port is communicated with the 4th valve port (in Fig. 1 with the state shown in solid line) and the first valve port is communicated with the 4th valve port and the second valve port is communicated with the 3rd valve port the second state (in Fig. 1 with the state shown in dotted line), switch.

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

The first valve port of described the 4th four-way change-over valve 96 is connected with the 4th bleed pipe 28 of the 4th compression unit 24, one distolateral being connected of the second valve port of the 4th four-way change-over valve 96 and tube connector 66, the 3rd valve port of the 4th four-way change-over valve 96 is connected with gas side connecting pipe 13 with distolateral being connected of outdoor heat converter 44, the 4th valve port of the 4th four-way change-over valve 96.Between the first state that the 4th four-way change-over valve 96 is communicated with the 3rd valve port at the first valve port and the second valve port is communicated with the 4th valve port (in Fig. 1 with the state shown in solid line) and the first valve port is communicated with the 4th valve port and the second valve port is communicated with the 3rd valve port the second state (in Fig. 1 with the state shown in dotted line), switch.

At this, at the second to the 4th suction line 30,31,32, be connected with check-valves CV1, CV2, CV3 midway.Each check-valves CV1, CV2, CV3 allow cold-producing medium the from first to the 3rd four-way change-over valve 93,94,95 towards described four-stage compressor 20 circulations, and stop cold-producing medium to circulate in the opposite direction.

At the first to the 4th bleed pipe 25,26,27,28, be connected with respectively gs- oil separator 89,90,91,92 midway.This gs- oil separator 89,90,91,92 is used for the lubricating oil being included in the cold-producing medium of this bleed pipe 25,26,27,28 of flowing through to separate from this cold-producing medium.On this gs- oil separator 89,90,91,92, be connected with and make the lubricating oil of separating in this gs- oil separator 89,90,91,92 towards the outside oily effuser 16,16,16,16 flowing out of this gs- oil separator 89,90,91,92.

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

The described first to the 3rd 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: at the outdoor air of being sent here by this outdoor fan 122 and in the heat-transfer pipe 52 of each heat exchanger 41,42,43,44, between mobile cold-producing medium, 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 the first intermediate heat exchanger 41 is connected with the 3rd valve port of described the first four-way change-over valve 93, one end of described the second intermediate heat exchanger 42 is connected with the 3rd valve port of described the second four-way change-over valve 94, one end of described the 3rd intermediate heat exchanger 43 is connected with the 3rd valve port of described the 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 the 4th four-way change-over valve 96.On the other hand, the other end of the described first to the 3rd intermediate heat exchanger 41,42,43 is connected with the first to the 3rd 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 the 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 branching portion of described the 4th refrigerant tubing 73 and the 4th flow export P4 of described current divider, be provided with check-valves CV7 and capillary 15.This check-valves CV7 allows the branching portion circulation of cold-producing medium from described current divider 18 towards described the 4th refrigerant tubing 73, and stops cold-producing medium to circulate in the opposite direction.

After the other end branch of described the 3rd refrigerant tubing 72, an arm is connected to (the check-valves CV3 with the 4th compression unit 24 between) midway of described the 4th suction line 32 and another arm is connected with the 3rd flow export P3 of described current divider 18.In addition, between the branching portion of described the 3rd refrigerant tubing 72 and the 3rd flow export P3 of described current divider 18, be provided with check-valves CV6 and capillary 15.This check-valves CV6 allows the branching portion circulation of cold-producing medium from described current divider 18 towards described the 3rd refrigerant tubing 72, and stops cold-producing medium to circulate in the opposite direction.Between the branching portion of described the 3rd refrigerant tubing 72 and the connecting portion of described the 4th suction line 32, be provided with check-valves CV10.This check-valves CV10 allows the connecting portion circulation of cold-producing medium from the branching portion of described the 3rd refrigerant tubing 72 towards described the 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 check-valves CV2 with the 3rd compression unit 23 between) midway of described the 3rd suction line 31 and another arm is connected with the second outlet P2 of described current divider 18.Between the branching portion of described second refrigerant pipeline 71 and the second of described current divider 18 outlet P2, be provided with check-valves CV5 and capillary 15.This check-valves CV5 allows the branching portion circulation of cold-producing medium from described current divider 18 towards described second refrigerant pipeline 71, and stops cold-producing medium to circulate in the opposite direction.Between the branching portion of described second refrigerant pipeline 71 and the connecting portion of described the 3rd suction line 31, be provided with check-valves CV9.This check-valves CV9 allows the connecting portion circulation of cold-producing medium from the branching portion of described second refrigerant pipeline 71 towards described the 3rd suction line 31, and stops cold-producing medium to circulate in the opposite direction.

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

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

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

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

Inflow end at described high-pressure side stream 100a is connected with inflow pipe 60, is connected with the first branched pipe 62 usings as supercooling path at the inflow end of low-pressure side stream 100b.On this first branched pipe 62, be provided with the second expansion valve 81 for supercooling.This second expansion valve 81 consists 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 check-valves CV9 on second refrigerant pipeline 71.

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

Inflow end at described high-pressure side stream 101a is connected with inflow pipe 60.Another of tube connector 66 is distolateral to be 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.

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

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

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

On described inflow pipe 60, be provided with the shunt valve 64 of walking around described decompressor 87.One of shunt valve 64 is distolaterally connected with the inflow side of decompressor 87, and another of this shunt valve 64 is distolateral to be connected with the outflow side of decompressor 87, thereby walks around decompressor 87.On this shunt valve 64, be provided with the first expansion valve 80.This first expansion valve 80 consists of aperture adjustable electron expansion valve.

Described gas-liquid separator 88 consists of the cylindric closed container of lengthwise.On gas-liquid separator 88, be connected with inflow pipe 60, the first effuser 61 and the second effuser 65.Inflow pipe 60 is uncovered towards the top of gas-liquid separator 88 inner spaces.The first effuser 61 is uncovered towards the below of gas-liquid separator 88 inner spaces.The second effuser 65 is uncovered towards the top of gas-liquid separator 88 inner spaces.In gas-liquid separator 88, the cold-producing medium having 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.

One of described the second effuser 65 is distolaterally connected with gas-liquid separator 88, and another of this second effuser 65 is distolateral is connected to return duct 68 midway.On this second effuser 65, be provided with the 4th expansion valve 83.The 4th expansion valve 83 consists of aperture adjustable electron expansion valve.

The 3rd supercooling heat exchanger 102 is connected to described the first effuser 61 midway.The 3rd supercooling heat exchanger 102 comprises high-pressure side stream 102a and low-pressure side stream 102b.The 3rd supercooling heat exchanger 102 is configured to: make to carry out heat exchange between cold-producing medium mobile in high-pressure side stream 102a and low-pressure side stream 102b, the cold-producing medium of the high-pressure side stream 102a that makes to flow through is 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.At the inflow end of low-pressure side stream 102b, be connected with the second branched pipe 63 and using as supercooling path, another distolateral connection of the outflow end of low-pressure side stream 102b and return duct 68.

Between the one distolateral gas-liquid separator 88 and the 3rd supercooling heat exchanger 102 being connected on the first effuser 61 of described the second branched pipe 63, the inflow end of the distolateral low-pressure side stream 102b with the 3rd supercooling heat exchanger 102 of another of this second branched pipe 63 is connected.On this second branched pipe 63, be provided with the 3rd expansion valve 82.The 3rd expansion valve 82 consists 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 this return duct 68 midway.

The indoor loop > of <

In indoor loop 12, from its liquid side towards gas side, be disposed with the first indoor expansion valve 85 and the first indoor heat converter 110, and from its liquid side towards gas side, be also disposed with the second indoor expansion valve 86 and the second indoor heat converter 111, 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 consists of aperture adjustable electron expansion valve.Each indoor heat converter 110,111 consists of tubes provided with cross ribs plate heat exchanger.Near each indoor heat converter 110,111, be respectively arranged with the indoor fan that room air is sent to each indoor heat converter 110,111, but this does not illustrate out.And, in each indoor heat converter 110,111, between cold-producing medium and room air, carry out heat exchange.

The structure > of the outdoor unit of <

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

Described outdoor fan 122 is for the air being drawn in outdoor machine shell 121 is sent to the fan of 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.And outdoor fan 122 passes through each heat exchanger 41,42,43,44 air sucking from suction inlet 123, then this air is blown out towards outside from blow-off outlet 124.

As shown in Figure 5, in the inside of outdoor machine shell 121, from downside towards upside, piling up successively and be provided with the first intermediate heat exchanger 41, the 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 the first intermediate heat exchanger 41 consists of so-called tubes provided with cross ribs plate heat exchanger.The first intermediate heat exchanger 41 comprises: a plurality of heat transfer tube group 50 and the thermofin 51 respectively with many heat-transfer pipes 52 and Duo Gen U word pipe.

Described a plurality of heat transfer tube group 50 is arranged in order up and down to arrange by seven heat transfer tube group 50 and forms.In each heat transfer tube group 50, many heat-transfer pipes 52 (being the six roots of sensation in Fig. 5) along the flow direction of air up and down each two ground be set be altogether arranged to three row, in the left side of Fig. 5 (being windward one side), form and have the first pipe row 53, central authorities' formation at Fig. 5 has the second pipe row 54, forms have the 3rd pipe row 55 on the right side of Fig. 5 (being leeward one side).That is to say, 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, the end of with described U word pipe, one end (first end) and the 3rd of higher level's heat-transfer pipe 52 of the first pipe row 53 in described many heat-transfer pipes 52 of heat-transfer pipe 52 being managed one end (the second end) of subordinate's heat-transfer pipe 52 of row 55 is joined to one another, thereby formed one, usings described first end and described the second end refrigerant path as 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.The 3rd pipe the second end of row 55 and the 3rd valve port of the first four-way change-over valve 93 of each heat transfer tube group 50 are communicated with.

As shown in Figure 5, described in each, thermofin 51 forms approximate rectangle thin plate.Thermofin 51 along the bearing of trend of heat transfer tube group 50 every predetermined distance arranging and arranging.On each thermofin 51, use a plurality of through holes that run through for heat-transfer pipe 52 to form three row, heat-transfer pipe 52 runs through this through hole.So, in the surrounding of heat-transfer pipe 52, be just provided with thermofin 51, heat transfer area is increased and promoted heat transmission.

Described the second intermediate heat exchanger 42 consists of so-called tubes provided with cross ribs plate heat exchanger.The second intermediate heat exchanger 42 comprises: a plurality of heat transfer tube group 50 and the thermofin 51 respectively with many heat-transfer pipes 52 and Duo Gen U word pipe.

Described a plurality of heat transfer tube group 50 is arranged in order up and down to arrange by seven heat transfer tube group 50 and forms.In each heat transfer tube group 50, many heat-transfer pipes 52 (being the six roots of sensation in Fig. 5) along the flow direction of air up and down each two ground be set be altogether arranged to three row, in the left side of Fig. 5 (being windward one side), form and have the first pipe row 53, central authorities' formation at Fig. 5 has the second pipe row 54, forms have the 3rd pipe row 55 on the right side of Fig. 5 (being leeward one side).That is to say, 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, the end of with described U word pipe, one end (first end) and the 3rd of higher level's heat-transfer pipe 52 of the first pipe row 53 in described many heat-transfer pipes 52 of heat-transfer pipe 52 being managed one end (the second end) of subordinate's heat-transfer pipe 52 of row 55 is joined to one another, thereby formed one, usings described first end and described the second end refrigerant path as 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.The 3rd pipe the second end of row 55 and the 3rd valve port of the second four-way change-over valve 94 of each heat transfer tube group 50 are communicated with.

As shown in Figure 5, described in each, thermofin 51 forms approximate rectangle thin plate.Thermofin 51 along the bearing of trend of heat transfer tube group 50 every predetermined distance arranging and arranging.On each thermofin 51, use a plurality of through holes that run through for heat-transfer pipe 52 to form three row, heat-transfer pipe 52 runs through this through hole.So, in the surrounding of heat-transfer pipe 52, be just provided with thermofin 51, heat transfer area is increased and promoted heat transmission.

Described the 3rd intermediate heat exchanger 43 consists of so-called tubes provided with cross ribs plate heat exchanger.The 3rd intermediate heat exchanger 43 comprises: a plurality of heat transfer tube group 50 and the thermofin 51 respectively with many heat-transfer pipes 52 and Duo Gen U word pipe.

Described a plurality of heat transfer tube group 50 is arranged in order up and down to arrange by six heat transfer tube group 50 and forms.In each heat transfer tube group 50, many heat-transfer pipes 52 (being the six roots of sensation in Fig. 5) along the flow direction of air up and down each two ground be set be altogether arranged to three row, in the left side of Fig. 5 (being windward one side), form and have the first pipe row 53, central authorities' formation at Fig. 5 has the second pipe row 54, forms have the 3rd pipe row 55 on the right side of Fig. 5 (being leeward one side).That is to say, 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, the end of with described U word pipe, one end (first end) and the 3rd of higher level's heat-transfer pipe 52 of the first pipe row 53 in described many heat-transfer pipes 52 of heat-transfer pipe 52 being managed one end (the second end) of subordinate's heat-transfer pipe 52 of row 55 is joined to one another, thereby formed one, usings described first end and described the second end refrigerant path as 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.The 3rd pipe the second end of row 55 and the 3rd valve port of the 3rd four-way change-over valve 95 of each heat transfer tube group 50 are communicated with.

As shown in Figure 5, described in each, thermofin 51 forms approximate rectangle thin plate.Thermofin 51 along the bearing of trend of heat transfer tube group 50 every predetermined distance arranging and arranging.On each thermofin 51, use a plurality of through holes that run through for heat-transfer pipe 52 to form three row, heat-transfer pipe 52 runs through this through hole.So, in the surrounding of heat-transfer pipe 52, be just provided with thermofin 51, heat transfer area is increased and promoted heat transmission.

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

Described a plurality of heat transfer tube group 50 is arranged in order up and down to arrange by eight heat transfer tube group 50 and forms.In each heat transfer tube group 50, many heat-transfer pipes 52 (being the six roots of sensation in Fig. 5) along the flow direction of air up and down each two ground be set be altogether arranged to three row, in the left side of Fig. 5 (being windward one side), form and have the first pipe row 53, central authorities' formation at Fig. 5 has the second pipe row 54, forms have the 3rd pipe row 55 on the right side of Fig. 5 (being leeward one side).That is to say, 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, the end of with described U word pipe, one end (first end) and the 3rd of higher level's heat-transfer pipe 52 of the first pipe row 53 in described many heat-transfer pipes 52 of heat-transfer pipe 52 being managed one end (the second end) of subordinate's heat-transfer pipe 52 of row 55 is joined to one another, thereby formed one, usings described first end and described the second end refrigerant path as 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.The 3rd pipe the second end of row 55 and the 3rd valve port of the 4th four-way change-over valve 96 of each heat transfer tube group 50 are communicated with.

As shown in Figure 5, described in each, thermofin 51 forms approximate rectangle thin plate.Thermofin 51 along the bearing of trend of heat transfer tube group 50 every predetermined distance arranging and arranging.On each thermofin 51, use a plurality of through holes that run through for heat-transfer pipe 52 to form three row, heat-transfer pipe 52 runs through this through hole.So, in the surrounding of heat-transfer pipe 52, be just provided with thermofin 51, heat transfer area is increased and promoted heat transmission.

-running action-

Then, the running action of aircondition 1 is described.In this aircondition 1, by switching the first to the 4th four-way change-over valve 93,94,95,96, thereby the running of described refrigerant loop 10 is switched to cooling operation or heats running.In addition, 1 to 26 expression in Fig. 1 and Fig. 2 is the pressure state of cold-producing medium.

-cooling operation-

See figures.1.and.2 the cooling operation of aircondition 1 is described.In Fig. 1, while being illustrated in this cooling operation with solid arrow, cold-producing medium flows.Under cooling operation, make outdoor heat converter 44 play radiator, make each indoor heat converter 110,111 play evaporimeter, thereby carry out level Four compression supercritical refrigeration cycle.The high-pressure refrigerant that the first to the 3rd intermediate heat exchanger 41,42,43 plays a part spraying from each compression unit 21,22,23 carries out cooling cooler.

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 that has obtained compression in the first compression unit 21 is sprayed (2 in Fig. 1 and Fig. 2) towards the first bleed pipe 25.In addition, now in the first gs-oil separator 89 on the first bleed pipe 25, the lubricating oil being included in the gaseous refrigerant of this first bleed pipe 25 of flowing through is separated.The lubricating oil of having separated is sent to the second suction line 30 from oily effuser 16.And cold-producing medium mobile in the first bleed pipe 25 is by rear inflow the first intermediate heat exchanger 41 of 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 being cooled in the first intermediate heat exchanger 41 flows into the first refrigerant tubing 70.In the first refrigerant tubing 70, mobile cold-producing medium flows into the second suction line 30 after by check-valves CV8 and is inhaled into the second compression unit 22 (3 in Fig. 1 and Fig. 2).

The cold-producing medium that has obtained compression in the second compression unit 22 is sprayed (4 in Fig. 1 and Fig. 2) towards the second bleed pipe 26.In addition, now in the second gs-oil separator 90 on the second bleed pipe 26, the lubricating oil being included in the gaseous refrigerant of this second bleed pipe 26 of flowing through is separated.The lubricating oil of having separated is sent to the 3rd suction line 31 from oily effuser 16.And cold-producing medium mobile in the second bleed pipe 26 is by rear inflow the second intermediate heat exchanger 42 of 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 being cooled in the second intermediate heat exchanger 42 flows into second refrigerant pipeline 71 (5 in Fig. 1 and Fig. 2).In second refrigerant pipeline 71, mobile cold-producing medium converges with the cold-producing medium of the ascending pipe 106 of flowing through after by 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 that has obtained compression in the 3rd compression unit 23 is sprayed (7 in Fig. 1 and Fig. 2) towards the 3rd bleed pipe 27.In addition, now in the 3rd gs-oil separator 91 on the 3rd bleed pipe 27, the lubricating oil being included in the gaseous refrigerant of the 3rd bleed pipe 27 of flowing through is separated.The lubricating oil of having separated is sent to the 4th suction line 32 from oily effuser 16.And cold-producing medium mobile in the 3rd bleed pipe 27 is by the rear inflow of the 3rd four-way change-over valve 95 the 3rd intermediate heat exchanger 43.In the 3rd intermediate heat exchanger 43, cold-producing medium is cooled towards outdoor air heat release.The cold-producing medium being cooled in the 3rd intermediate heat exchanger 43 flows into the 3rd refrigerant tubing 72.In the 3rd refrigerant tubing 72, mobile cold-producing medium flows into the 4th suction line 32 after by check-valves CV10 and is inhaled into the 4th compression unit 24 (8 in Fig. 1 and Fig. 2).

The cold-producing medium that has obtained compression in the 4th compression unit 24 is sprayed (9 in Fig. 1 and Fig. 2) towards the 4th bleed pipe 28.Repeatedly alternately compress as mentioned above with cooling, thereby make the compression process of described four-stage compressor 20 approach isotherm compression, seek to reduce the required compression power of described four-stage compressor 20.In addition, now in the 4th gs-oil separator 92 on the 4th bleed pipe 28, the lubricating oil being included in the gaseous refrigerant of the 4th bleed pipe 28 of flowing through is separated.The lubricating oil being separated is sent to the first suction line 29 from oily effuser 16.Cold-producing medium mobile in the 4th bleed pipe 28 is by the rear inflow outdoor heat exchanger 44 of 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 being cooled in outdoor heat converter 44 flows into the 4th refrigerant tubing 73.In the 4th refrigerant tubing 73, mobile cold-producing medium flows into inflow pipe 60 after by check-valves CV11.

In inflow pipe 60, a part for mobile cold-producing medium flows into the first branched pipe 62.Cold-producing medium (10 in Fig. 1 and Fig. 2) mobile in the first branched pipe 62 is by the second expansion valve 81 decompressions.By the cold-producing medium (11 in Fig. 1 and Fig. 2) of the second expansion valve 81 decompressions, flowed 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 mobile cold-producing medium 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, in high-pressure side stream 100a and low-pressure side stream 100b, between mobile cold-producing medium, carry out heat exchange, the cold-producing medium of the high-pressure side stream 100a that makes to flow through is by supercooling.

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

In the second supercooling heat exchanger 101, in high-pressure side stream 101a and low-pressure side stream 101b, between mobile cold-producing medium, carry out heat exchange, the cold-producing medium of the high-pressure side stream 101a that makes to flow through is by supercooling.

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

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

In the 3rd supercooling heat exchanger 102, to flow through and carry out heat exchange between high-pressure side stream 102a and the cold-producing medium of low-pressure side stream 102b, the liquid refrigerant of the high-pressure side stream 102a that makes to flow through is by supercooling.

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

In hydraulic fluid side connecting pipe 14, after a part for mobile liquid refrigerant shunting, by the first indoor expansion valve 85, reduced pressure.The cold-producing medium being depressurized (21a in Fig. 1 and Fig. 2) flows into the first indoor heat converter 110.In the first indoor heat converter 110, liquid refrigerant absorbs heat and evaporates from room air.The gaseous refrigerant having evaporated (25a in Fig. 1 and Fig. 2) inflow gas side connecting pipe 13.

In hydraulic fluid side connecting pipe 14, the remainder of mobile liquid refrigerant is by the second indoor expansion valve 86 decompressions.The cold-producing medium being depressurized (21b in Fig. 1 and Fig. 2) flows into the second indoor heat converter 111.In the second indoor heat converter 111, liquid refrigerant absorbs heat and evaporates from room air.The gaseous refrigerant having evaporated (25b in Fig. 1 and Fig. 2) inflow gas side connecting pipe 13.

In gas side connecting pipe 13, the cold-producing medium having flowed out from the first indoor heat converter 110 converges with the cold-producing medium flowing out from the second indoor heat converter 111.Cold-producing medium mobile in gas side connecting pipe 13 is by the rear inflow tube connector 66 of the 4th four-way change-over valve 96.In tube connector 66, a part for mobile cold-producing medium flows to respectively the first to the 3rd four-way change-over valve 93,94,95 after collecting fitting 67 shuntings.

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

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

-heat running-

Then, with reference to Fig. 7, the running that heats of this aircondition 1 is described.In Fig. 7, with dotted arrow, be illustrated in this and heat flowing of when running cold-producing medium.Under this heats running, make each indoor heat converter 110,111 play radiator, make the first to the 3rd intermediate heat exchanger 41,42,43 and outdoor heat converter 44 play evaporimeter, thereby carry out level Four compression 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 that has obtained compression in the first compression unit 21 is sprayed towards the first bleed pipe 25.And mobile cold-producing medium is inhaled into the second compression unit 22 after by the first four-way change-over valve 93 in the first bleed pipe 25.The cold-producing medium being further compressed in the second compression unit 22 is inhaled into the 3rd compression unit 23 after by the second four-way change-over valve 94.The cold-producing medium being further compressed in the 3rd compression unit 23 is inhaled into the 4th compression unit 24 after by 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, in the situation that heating running, do not follow and carry out level Four compression coolingly.Thus, compare with being accompanied by cooling situation of carrying out level Four compression, from four-stage compressor 20, the temperature of the cold-producing medium of ejection does not reduce.Consequently, compare with being accompanied by cooling situation of carrying out level Four compression, the heating capacity while heating running increases.

From the 4th compression unit 24, the cold-producing medium of ejection is sent to the first and second indoor heat converters 110,111 after by 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 being cooled in each indoor heat converter 110,111 by the first and second indoor expansion valves 85,86 decompressions after, be sent to bridge circuit 17.And this cold-producing medium flows into inflow pipe 60 after by check-valves CV12.

In inflow pipe 60, a part for mobile cold-producing medium flows into the first branched pipe 62.Cold-producing medium mobile in the first branched pipe 62 is by the second expansion valve 81 decompressions.By the cold-producing medium of the second expansion valve 81 decompressions, flowed 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 mobile cold-producing medium flows into the high-pressure side stream 100a of the first supercooling heat exchanger 100.In the first supercooling heat exchanger 100, in high-pressure side stream 100a and low-pressure side stream 100b, between mobile cold-producing medium, carry out heat exchange, the cold-producing medium of the high-pressure side stream 100a that makes to flow through is by supercooling.

The cold-producing medium that has flowed out the high-pressure side stream 100a of the first supercooling heat exchanger 100 is flowed through after inflow pipe 60 again, flows into the high-pressure side stream 101a of the second supercooling heat exchanger 101.On the other hand, flowed out the cold-producing medium inflow ascending pipe 106 of the low-pressure side stream 100b of the first supercooling heat exchanger 100.Cold-producing medium mobile in ascending pipe 106 flows into after second refrigerant pipeline 71, converges with the cold-producing medium in second refrigerant pipeline 71.That is to say, the cold-producing medium that has flowed to ascending pipe 106 is injected into the suction side of the 3rd compression unit 23.

In the second supercooling heat exchanger 101, in high-pressure side stream 101a and low-pressure side stream 101b, between mobile cold-producing medium, carry out heat exchange, the cold-producing medium of the high-pressure side stream 101a that makes to flow through is by supercooling.

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

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

In the 3rd supercooling heat exchanger 102, to flow through and carry out heat exchange between high-pressure side stream 102a and the cold-producing medium of low-pressure side stream 102b, the liquid refrigerant of the high-pressure side stream 102a that makes to flow through is by supercooling.

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

The cold-producing medium having flowed out from outdoor heat converter 44 is by the rear inflow tube connector 66 of the 4th four-way change-over valve 96, converges with the cold-producing medium flowing out the from first to the 3rd intermediate heat exchanger 41,42,43.The cold-producing medium having converged flows and converges with cold-producing medium mobile in return duct 68 in tube connector 66.The cold-producing medium having converged flows into the first suction line 29.Cold-producing medium mobile in the first suction line 29 is again compressed in the first compression unit 21 of four-stage compressor 20.

-outdoor unit-

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

At this, as shown in Figure 6, described outdoor unit 3 is configured to after suction inlet 123 air amounts from the side again from blow-off outlet 124 towards upper blowing type top blow out air, so-called, thereby the air velocity of suction inlet 123 tops is faster than its below.As shown in Figure 2, in the first to the 3rd intermediate heat exchanger 41,42,43, the pressure of pressure ratio mobile cold-producing medium in outdoor heat converter 44 of mobile cold-producing medium is low, thereby the density of mobile cold-producing medium is less than the density of cold-producing medium mobile in outdoor heat converter 44 in the first to the 3rd intermediate heat exchanger 41,42,43.For this reason, if respectively in the first to the 3rd intermediate heat exchanger 41,42,43 and outdoor heat converter 44 mass flow of mobile cold-producing medium about equally, in the first to the 3rd intermediate heat exchanger 41,42,43, the volume flow of cold-producing medium will be greater than the volume flow of cold-producing medium mobile in outdoor heat converter 44.Even if the refrigerant path quantity in the first to the 3rd intermediate heat exchanger 41,42,43 and outdoor heat converter 44 about equally, also the flow velocity due to cold-producing medium mobile in the first to the 3rd intermediate heat exchanger 41,42,43 is greater than the cold-producing medium flow velocity in outdoor heat converter 44, thereby the pressure loss of the cold-producing medium in the first to the 3rd intermediate heat exchanger 41,42,43 is greater than the pressure loss of cold-producing medium in outdoor heat converter 44.

Be arranged at the interior air velocity of outdoor machine shell 121 higher above outdoor heat converter 44 in, because heat exchange performance is higher, thereby can make its size realize miniaturization.On the other hand, be arranged at the interior air velocity of outdoor machine shell 121 lower below the first to the 3rd intermediate heat exchanger 41,42,43 in, heat-exchange capacity is lower.For this reason, if will increase heat exchange amount, the first to the 3rd intermediate heat exchanger 41,42,43 will be larger than time above being arranged on.

Therefore, outdoor heat exchanger group 40 maximization that can not become due to the maximization of outdoor heat converter 44 and the first to the 3rd intermediate heat exchanger 41,42,43.

If the first to the 3rd intermediate heat exchanger 41,42,43 is realized, maximize, in the first to the 3rd intermediate heat exchanger 41,42,43, the quantity of refrigerant path will increase.For this reason, in the first to the 3rd intermediate heat exchanger 41,42,43, in each refrigerant path, the flow velocity of cold-producing medium reduces, and the pressure loss of cold-producing medium reduces when by each refrigerant path.Because the flow velocity of cold-producing medium mobile in the first to the 3rd intermediate heat exchanger 41,42,43 is originally higher, if thereby the increase of refrigerant path quantity flow velocity is reduced, therefore the pressure loss will reduce greatly.

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

Yet the flow velocity of mobile cold-producing medium is originally lower in outdoor heat converter 44, even thereby flow velocity because refrigerant path quantity reduces some, accelerate, it is also smaller resulting from this increase of the pressure loss.

Therefore, in the situation that outdoor heat converter 44 being arranged on above the first to the 3rd 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 3rd intermediate heat exchanger 41,42,43 can also be reduced simultaneously.

As shown in Figure 2, because the pressure of pressure ratio mobile cold-producing medium in the first and second intermediate heat exchangers 41,42 of cold-producing medium mobile in the 3rd intermediate heat exchanger 43 is high, thereby the density of density ratio mobile cold-producing medium in the 3rd intermediate heat exchanger 43 of mobile cold-producing medium is little in the first and second intermediate heat exchangers 41,42.For this reason, if respectively in the first and second intermediate heat exchangers 41,42 and the 3rd intermediate heat exchanger 43 mass flow of mobile cold-producing medium about equally, 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 cold-producing medium mobile in the 3rd intermediate heat exchanger 43.Even if the quantity of the refrigerant path in the first and second intermediate heat exchangers 41,42 and the 3rd intermediate heat exchanger 43 about equally, also the flow velocity due to cold-producing medium mobile in the first and second intermediate heat exchangers 41,42 is greater than the cold-producing medium flow velocity in the 3rd intermediate heat exchanger 43, thereby the pressure loss of the cold-producing medium 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.

Be arranged at the interior air velocity of outdoor machine shell 121 higher above the 3rd intermediate heat exchanger 43 in, because heat exchange performance is higher, thereby can make its size realize miniaturization.On the other hand, be arranged at the interior air velocity of outdoor machine shell 121 lower below the first and second intermediate heat exchangers 41,42 in, heat-exchange capacity is lower.For this reason, if will increase heat exchange amount, the first and second intermediate heat exchangers 41,42 will be larger than time above being arranged on.

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

If the first and second intermediate heat exchangers 41,42 are realized, maximize, 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 refrigerant path, the flow velocity of cold-producing medium reduces, and the pressure loss of cold-producing medium reduces when by each refrigerant path.Because the flow velocity of cold-producing medium mobile in the first and second intermediate heat exchangers 41,42 is originally higher, if thereby the increase of refrigerant path quantity flow velocity is reduced, therefore the pressure loss will reduce greatly.

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

Yet the flow velocity of mobile cold-producing medium is originally lower in the 3rd intermediate heat exchanger 43, even thereby flow velocity because refrigerant path quantity reduces some, accelerate, it is also smaller resulting from this increase of the pressure loss.

Therefore, in the situation that the 3rd intermediate heat exchanger 43 being 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 higher intermediate heat exchanger 42 of the pressure of flowed into cold-producing medium, the density of its cold-producing medium is greater than the refrigerant density in the first intermediate heat exchanger 41 that flowed into refrigerant pressure is lower.For this reason, if respectively in the first intermediate heat exchanger 41 and the second intermediate heat exchanger 42 mass flow of mobile cold-producing medium about equally, in the first intermediate heat exchanger 41, the volume flow of cold-producing medium will be greater than the volume flow of cold-producing medium mobile 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 about equally, also the flow velocity due to cold-producing medium mobile in the first intermediate heat exchanger 41 is greater than the cold-producing medium flow velocity in the second intermediate heat exchanger 42, thereby the pressure loss of the cold-producing medium 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.Be arranged at the interior air velocity of outdoor machine shell 121 lower below the first intermediate heat exchanger 41 in, because heat-exchange capacity does not improve, thereby do not make its size realize miniaturization.Due to the not minimizing of quantity of each refrigerant path in the first intermediate heat exchanger 41, thereby the pressure loss of cold-producing medium does not increase.As mentioned above, can suppress the pressure loss increase of cold-producing medium in the first intermediate heat exchanger 41.

-effect of the first embodiment-

According to above-mentioned the first embodiment, because outdoor heat converter 44 is arranged on to the higher top of the interior air velocity of outdoor machine shell 121, so can improve the heat exchange performance of outdoor heat converter 44.Also because the lower outdoor heat converter 44 of cold-producing medium flow velocity is arranged on to the higher top of the interior air velocity of outdoor machine shell 121, so can not make refrigerant pressure loss increase the miniaturization that realizes outdoor heat converter 44.

On the other hand, by the first to the 3rd intermediate heat exchanger 41,42,43 is arranged on to the quantity that the lower below of the interior air velocity of outdoor machine shell 121 increases refrigerant path, thereby can prevent reliably that the pressure loss of cold-producing medium in the first to the 3rd intermediate heat exchanger 41,42,43 from increasing.

As mentioned above, by the outdoor heat converter of the more difficult increase of the pressure loss of cold-producing medium 44,162 being arranged on to top, realize miniaturization, thereby the size that can suppress outdoor heat exchanger group 40 increases, and can also suppress the pressure loss of cold-producing medium in the first to the 3rd intermediate heat exchanger 41,42,43 simultaneously.

Because the 3rd intermediate heat exchanger 43 is arranged on to the higher top of the interior air velocity of outdoor machine shell 121, so can improve the heat exchange performance of the 3rd intermediate heat exchanger 43.Also because the 3rd lower intermediate heat exchanger 43 of cold-producing medium flow velocity is arranged on to the higher top of the interior air velocity of outdoor machine shell 121, so can not make refrigerant pressure loss increase the miniaturization that the 3rd intermediate heat exchanger 43 can be realized in ground.

On the other hand, by by cold-producing medium flow velocity faster the first and second intermediate heat exchangers 41,42 be arranged on the quantity that the lower below of the interior air velocity of outdoor machine shell 121 increases refrigerant path, thereby can prevent reliably that the pressure loss of cold-producing medium in the first and second intermediate heat exchangers 41,42 from increasing.

As mentioned above, by the 3rd intermediate heat exchanger 43 of the more difficult increase of the pressure loss of cold-producing medium being arranged on to top, realize miniaturization, thereby the size that can suppress outdoor heat exchanger group 40 increases, and can also suppress the pressure loss of cold-producing medium in other intermediate heat exchanger 41,42 simultaneously.

By by cold-producing medium flow velocity faster the first intermediate heat exchanger 41 be arranged on the quantity that the lower below of the interior air velocity of outdoor machine shell 121 increases refrigerant path, thereby can prevent reliably that the pressure loss of cold-producing medium in the first intermediate heat exchanger 41 from increasing.The pressure loss that can suppress thus, cold-producing medium in the first intermediate heat exchanger 41.

The second embodiment > of < invention

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

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

-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 cold-producing medium mobile in high-pressure side stream 103a and low-pressure side stream 103b, the cold-producing medium of the high-pressure side stream 103a that makes to flow through is by supercooling.

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

One end of described the 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 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 cold-producing medium mobile in high-pressure side stream 104a and low-pressure side stream 104b, the cold-producing medium of the high-pressure side stream 104a that makes to flow through is by supercooling.

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

One end of described the 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 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 cold-producing medium mobile in high-pressure side stream 105a and low-pressure side stream 105b, the cold-producing medium of the high-pressure side stream 105a that makes to flow through is by supercooling.

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

One end of described the 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 check-valves CV8 on the first refrigerant tubing 70.Described 1c supercooling heat exchanger 105 and 2c expansion valve 81c form so-called economizer.

-the running action in loop-

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

The cold-producing medium that has obtained compression in the 4th compression unit 24 of described four-stage compressor 20 is sprayed towards the 4th bleed pipe 28.By repeatedly alternately compressing in four-stage compressor 20 and the first to the 3rd intermediate heat exchanger 41,42,43 and cooling, thereby make the compression process of described four-stage compressor 20 approach isotherm compression, seek to reduce the required compression power of described four-stage compressor 20.

Cold-producing medium mobile in the 4th bleed pipe 28 is by the rear inflow outdoor heat exchanger 44 of 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 being cooled in outdoor heat converter 44 flows into the 4th refrigerant tubing 73.In the 4th refrigerant tubing 73, mobile cold-producing medium flows into inflow pipe 60 after by check-valves CV11.

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

The cold-producing medium that has flowed out the high-pressure side stream 103a of 1a supercooling heat exchanger 103 is flowed through after inflow pipe 60 (31 in Fig. 8 and Fig. 9) again, flows 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) that has flowed out the low-pressure side stream 103b of 1a supercooling heat exchanger 103 flows into the first ascending pipe 107.Cold-producing medium mobile in the first ascending pipe 107 flows into after the 3rd refrigerant tubing 72, converges (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 to say, the cold-producing medium that has flowed to the first ascending pipe 107 is injected into the suction side of the 4th compression unit 24.

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

The cold-producing medium that has flowed out the high-pressure side stream 104a of 1b supercooling heat exchanger 104 is flowed through after inflow pipe 60 (34 in Fig. 8 and Fig. 9) again, flows 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) that has flowed out the low-pressure side stream 104b of 1b supercooling heat exchanger 104 flows into the second ascending pipe 108.Cold-producing medium mobile in the second ascending pipe 108 flows into after second refrigerant pipeline 71, converges (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 to say, the cold-producing medium that has flowed to the second ascending pipe 108 is injected into the suction side of the 3rd compression unit 23.

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

The cold-producing medium that has flowed out the high-pressure side stream 105a of 1c supercooling heat exchanger 105 is flowed through after inflow pipe 60 (38 in Fig. 8 and Fig. 9) again, flows 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) that has flowed out the low-pressure side stream 105b of 1c supercooling heat exchanger 105 flows into the first ascending pipe 107.In the first ascending pipe 107, mobile cold-producing medium flows into after the first refrigerant tubing 70, converges (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 to say, the cold-producing medium that has 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.

The 3rd embodiment > of < invention

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

Particularly, the related aircondition 140 of the 3rd embodiment of the present invention is described.This aircondition 140 comprises and is configured to the refrigerant loop 143 that can reversibly switch flow of refrigerant, and is configured to and can carries out cold and hot switching.This aircondition 140 comprises setting outdoor unit 142 without and is arranged on indoor units 141 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.In this refrigerant loop 143, enclosed carbon dioxide (hereinafter referred to as cold-producing medium.), and be configured to: this cold-producing medium is circulated in refrigerant loop 143, thereby can carry out multi-stage compression formula supercritical refrigeration cycle.

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, the first and second four-way change-over valves 175,176, the first and second supercooling heat exchangers 191,192, the first to the 5th 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, thereby 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.Ejection side at the first and second compression units 151,152 is connected with the first and second bleed pipes 153,154, is 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 sucking by each suction line 155,156 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.

The first valve port of described the first four-way change-over valve 175 is connected with the first bleed pipe 153 of the first compression unit 151, one distolateral being connected of the second valve port of this first four-way change-over valve 175 and collecting fitting 187, the 3rd valve port of this first four-way change-over valve 175 and distolateral being connected of intermediate heat exchanger 161, 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.Between the first state that this first four-way change-over valve 175 is communicated with the 3rd valve port at the first valve port and the second valve port is communicated with the 4th valve port (in Figure 10 with the state shown in solid line) and the first valve port is communicated with the 4th valve port and the second valve port is communicated with the 3rd valve port the second state (in Figure 10 with the state shown in dotted line), switch.

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

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

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

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

Described intermediate heat exchanger 161 and outdoor heat converter 162 are configured to Gilled heat exchanger.This intermediate heat exchanger 161 forms middle heat exchange department 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: at the outdoor air of being sent here by this outdoor fan 122 and in the heat-transfer pipe of each heat exchanger 161,162, between mobile cold-producing medium, carry out heat exchange.

At this, one end of described intermediate heat exchanger 161 is connected with the 3rd valve port of described the 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 the 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 the second outlet P2 of another arm and described current divider 173 is connected.In addition, between the branching portion of described second refrigerant pipeline 182 and the second of described current divider outlet P2, be provided with check-valves CV3 and capillary 170.This check-valves CV3 allows the branching portion circulation of cold-producing medium from described current divider 173 towards described second refrigerant pipeline 182, and stops cold-producing medium to circulate in the opposite direction.

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

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

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

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

Inflow end at described high-pressure side stream 191a is connected with inflow pipe 179, is connected with the first branched pipe 177 usings as supercooling path at the inflow end of low-pressure side stream 191b.On this first branched pipe 177, be provided with the second expansion valve 202 for supercooling.This second expansion valve 202 by aperture through regulating variable electric expansion valve to form.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 check-valves CV4 on the first refrigerant tubing 181.

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

On described inflow pipe 179, be provided with the shunt valve 183 of walking around described decompressor 193.One of shunt valve 183 is distolaterally connected with the inflow side of decompressor 193, and another of this shunt valve 183 is distolateral to be connected with the outflow side of decompressor 193, thereby walks around decompressor 193.On this shunt valve 183, be provided with the first expansion valve 201.This first expansion valve 201 by aperture through regulating variable electric expansion valve to form.

Described gas-liquid separator 194 consists of the cylindric closed container of lengthwise.On gas-liquid separator 194, be connected with inflow pipe 179, the first effuser 180 and the second effuser 184.Inflow pipe 179 is uncovered towards the top of gas-liquid separator 194 inner spaces.The first effuser 180 is uncovered towards the below of gas-liquid separator 194 inner spaces.The second effuser 184 is uncovered towards the top of gas-liquid separator 194 inner spaces.In gas-liquid separator 194, the cold-producing medium having 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.

One of described the second effuser 184 is distolaterally connected with gas-liquid separator 194, and another is distolaterally connected to the second branched pipe 178 midway.On this second effuser 184, be provided with the 4th expansion valve 204.The 4th expansion valve 204 by aperture through regulating variable electric expansion valve to form.

The second supercooling heat exchanger 192 is connected to described the first effuser 180 midway.This second supercooling heat exchanger 192 comprises high-pressure side stream 192a and low-pressure side stream 192b.The second supercooling heat exchanger 192 is configured to: make to carry out heat exchange between cold-producing medium mobile in high-pressure side stream 192a and low-pressure side stream 192b, the cold-producing medium of the high-pressure side stream 192a that makes to flow through is 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.At the inflow end of low-pressure side stream 192b, be connected with the second branched pipe 178 and using as supercooling path, another distolateral connection of the outflow end of low-pressure side stream 192b and return duct 185.

Between the one distolateral gas-liquid separator 194 and the second supercooling heat exchanger 192 being connected on the first effuser 180 of described the second branched pipe 178, the inflow end of the distolateral low-pressure side stream 192b with the second supercooling heat exchanger 192 of another of this second branched pipe 178 is connected, and at this second branched pipe 178, is connected with the second effuser 184 midway.On this second branched pipe 178, be provided with the 3rd expansion valve 203.The 3rd expansion valve 203 by aperture through regulating variable electric expansion valve to form.

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.

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

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

The indoor loop > of <

In indoor loop 145, from its liquid side towards gas side, be disposed with the first indoor expansion valve 206 and the first indoor heat converter 211, and from its liquid side towards gas side, be also disposed with the second indoor expansion valve 207 and the second indoor heat converter 212, 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 consists of aperture adjustable electron expansion valve.Each indoor heat converter 211,212 consists of tubes provided with cross ribs plate heat exchanger.Near each indoor heat converter 211,212, be respectively arranged with the indoor fan that room air is sent to each indoor heat converter 211,212, but this does not illustrate out.And, in each indoor heat converter 211,212, between cold-producing medium and room air, carry out heat exchange.

The structure > of the outdoor unit of <

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

Described outdoor fan 166 is for the air being drawn in outdoor machine shell 163 is sent to the fan of 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.And outdoor fan 166 passes through each heat exchanger 161,162 air sucking from suction inlet 164, then this air is blown out towards outside from blow-off outlet 165.

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

Described each heat exchanger 161,162 consists of so-called tubes provided with cross ribs plate heat exchanger.Each heat exchanger 161,162 comprises: a plurality of heat transfer tube group and the thermofin respectively with many heat-transfer pipes and Duo Gen U word pipe.

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

-running action-

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

-cooling operation-

With reference to Figure 10, the cooling operation of aircondition 140 is described.In Figure 10, while being illustrated in this cooling operation with solid arrow, cold-producing medium flows.Under cooling operation, make outdoor heat converter 162 play radiator, make each indoor heat converter 211,212 play evaporimeter, thereby carry out two-stage compression supercritical refrigeration cycle.The high-pressure refrigerant that intermediate heat exchanger 161 plays a part spraying from the first compression unit 151 carries out cooling cooler.

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 that has obtained compression in the first compression unit 151 is sprayed (2 in Figure 10 and Figure 11) towards the first bleed pipe 153.In addition, now in the gs-oil separator 174 on the first bleed pipe 153, the lubricating oil being included in the gaseous refrigerant of this first bleed pipe 153 of flowing through is separated.The lubricating oil of having separated is sent to the second suction line 156 from oily effuser 171.And cold-producing medium mobile in the first bleed pipe 153 is by the rear inflow intermediate heat exchanger 161 of 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 being cooled in intermediate heat exchanger 161 flows into the first refrigerant tubing 181.In the first refrigerant tubing 181, mobile cold-producing medium (3 in Figure 10 and Figure 11) converges with cold-producing medium mobile in ascending pipe 188 after by check-valves CV4, then flows into the second suction line 156 and is 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) that has obtained compression in the second compression unit 152 is sprayed towards the second bleed pipe 154.Alternately compress as mentioned above with cooling, thereby make the compression process of described double-stage compressor 150 approach isotherm compression, seek to reduce the required compression power of described double-stage compressor 150.In addition, now in the gs-oil separator 174 on the second bleed pipe 154, the lubricating oil being included in the gaseous refrigerant of this second bleed pipe 154 of flowing through is separated.The lubricating oil being separated is sent to the first suction line 155 from oily effuser 171.Cold-producing medium mobile in the second bleed pipe 154 is by the rear inflow outdoor heat exchanger 162 of 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 being cooled in outdoor heat converter 162 flows into second refrigerant pipeline 182.In second refrigerant pipeline 182, mobile cold-producing medium flows into inflow pipe 179 after by check-valves CV5.

In inflow pipe 179, a part for mobile cold-producing medium (6 in Figure 10 and Figure 11) flows into the first branched pipe 177.Cold-producing medium mobile in the first branched pipe 177 is by the second expansion valve 202 decompressions.By the cold-producing medium (7 in Figure 10 and Figure 11) of the second expansion valve 202 decompressions, flowed 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 mobile cold-producing medium 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, in high-pressure side stream 191a and low-pressure side stream 191b, between mobile cold-producing medium, carry out heat exchange, the cold-producing medium of the high-pressure side stream 191a that makes to flow through is by supercooling.

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

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

The liquid refrigerant of effluent gases liquid/gas separator 194 (13 in Figure 10 and Figure 11) is flowed through after inflow pipe 179, and 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 mobile cold-producing medium 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 (15 in Figure 10 and Figure 11) is flowed through after the second effuser 184 after the 4th expansion valve 204 decompressions (18 in Figure 10 and Figure 11), flows into the second branched pipe 178.And cold-producing medium mobile in the second branched pipe 178 is by the 3rd expansion valve 203 decompressions.Cold-producing medium (17 in Figure 10 and Figure 11) by the 3rd expansion valve 203 decompressions converges with cold-producing medium mobile in the second effuser 184.

The cold-producing medium having converged flows into the low-pressure side stream 192b of the second supercooling heat exchanger 192.In the second supercooling heat exchanger 192, in high-pressure side stream 192a and low-pressure side stream 192b, between mobile cold-producing medium, carry out heat exchange, the liquid refrigerant of the high-pressure side stream 192a that makes to flow through is by supercooling.

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

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

In hydraulic fluid side connecting pipe 147, the remainder of mobile liquid refrigerant is by the second indoor expansion valve 207 decompressions.The cold-producing medium being depressurized (16b in Figure 10 and Figure 11) flows into the second indoor heat converter 212.In the second indoor heat converter 212, liquid refrigerant absorbs heat and evaporates from room air.The gaseous refrigerant inflow gas side connecting pipe 146 of having evaporated.

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

-heat running-

Then, with reference to Figure 13, the running that heats of this aircondition 140 is described.In Figure 13, with dotted arrow, be illustrated in this and heat flowing of when running cold-producing medium.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, thereby 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 that has obtained compression in the first compression unit 151 is sprayed towards the first bleed pipe 153.In addition, now in the gs-oil separator 174 on the first bleed pipe 153, the lubricating oil being included in the gaseous refrigerant of this first bleed pipe 153 of flowing through is separated.The lubricating oil being separated is sent to the second suction line 156 from oily effuser 171.And mobile cold-producing medium is inhaled into the second compression unit 152 after by the first four-way change-over valve 175 in the first bleed pipe 153.In the second compression unit 152, cold-producing medium is further compressed.As mentioned above, different from cooling operation, in the situation that heating running, do not follow and carry out Two-stage Compression coolingly.Thus, compare with being accompanied by cooling situation of carrying out Two-stage Compression, from double-stage compressor 150, the temperature of the cold-producing medium of ejection does not reduce.Consequently, compare with being accompanied by cooling situation of carrying out Two-stage Compression, the heating capacity while heating running increases.

From the second compression unit 152, the cold-producing medium of ejection is sent to the first and second indoor heat converters 211,212 after by 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 being cooled in each indoor heat converter 211,212 by the first and second indoor expansion valves 206,207 decompressions after, be sent to bridge circuit 172.And this cold-producing medium flows into inflow pipe 179 after by check-valves CV6.

In inflow pipe 179, a part for mobile cold-producing medium flows into the first branched pipe 177.Cold-producing medium mobile in the first branched pipe 177 is by the second expansion valve 202 decompressions.By the cold-producing medium of the second expansion valve 202 decompressions, flowed 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 mobile cold-producing medium flows into the high-pressure side stream 191a of the first supercooling heat exchanger 191.In the first supercooling heat exchanger 191, in high-pressure side stream 191a and low-pressure side stream 191b, between mobile cold-producing medium, carry out heat exchange, the cold-producing medium of the high-pressure side stream 191a that makes to flow through is by supercooling.

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

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

The liquid refrigerant of effluent gases liquid/gas separator 194 is flowed through after the first effuser 180, and 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 mobile cold-producing medium 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 the 4th expansion valve 204 decompressions, flows into the second branched pipe 178.And cold-producing medium mobile in the second branched pipe 178 is by the 3rd expansion valve 203 decompressions.Cold-producing medium by the 3rd expansion valve 203 decompressions converges with cold-producing medium mobile in the second effuser 184.

The cold-producing medium having converged flows into the low-pressure side stream 192b of the second supercooling heat exchanger 192.In the second supercooling heat exchanger 192, in high-pressure side stream 192a and low-pressure side stream 192b, between mobile cold-producing medium, carry out heat exchange, the liquid refrigerant of the high-pressure side stream 192a that makes to flow through is by supercooling.

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

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

-outdoor unit-

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

At this, described outdoor unit 142 is configured to after suction inlet 164 air amounts from the side again from blow-off outlet 165 towards upper blowing type top blow out air, so-called, thereby the air velocity of suction inlet 164 tops is faster than its below.As shown in figure 11, in intermediate heat exchanger 161, the pressure of the pressure ratio of mobile cold-producing medium mobile cold-producing medium in outdoor heat converter 162 is low, thereby the density of mobile cold-producing medium is less than the density of cold-producing medium mobile in outdoor heat converter 162 in intermediate heat exchanger 161.For this reason, if respectively in intermediate heat exchanger 161 and outdoor heat converter 162 mass flow of mobile cold-producing medium about equally, in intermediate heat exchanger 161, the volume flow of cold-producing medium will be greater than the volume flow of cold-producing medium mobile in outdoor heat converter 162.Even if the quantity of the refrigerant path in intermediate heat exchanger 161 and outdoor heat converter 162 about equally, also because cold-producing medium flow velocity mobile in intermediate heat exchanger 161 is greater than the cold-producing medium flow velocity in outdoor heat converter 162, thereby the pressure loss of the cold-producing medium in intermediate heat exchanger 161 is greater than the pressure loss of cold-producing medium in outdoor heat converter 162.

Be arranged at the interior air velocity of outdoor machine shell 163 higher above outdoor heat converter 162 in, because heat exchange performance is higher, thereby can make its size realize miniaturization.On the other hand, be arranged at the interior air velocity of outdoor machine shell 163 lower below intermediate heat exchanger 161 in, heat-exchange capacity is lower.For this reason, if will increase heat exchange amount, intermediate heat exchanger 161 will be larger than time above being arranged on.

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

If intermediate heat exchanger 161 is realized, maximize, in intermediate heat exchanger 161, the quantity of refrigerant path will increase.For this reason, in intermediate heat exchanger 161, in each refrigerant path, the flow velocity of cold-producing medium reduces, and the pressure loss of cold-producing medium reduces when by each refrigerant path.Because the flow velocity of cold-producing medium mobile in intermediate heat exchanger 161 is originally higher, if thereby the increase of refrigerant path quantity flow velocity is reduced, therefore the pressure loss will reduce greatly.

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

Yet the flow velocity of mobile cold-producing medium is originally lower in outdoor heat converter 162, even thereby flow velocity because refrigerant path quantity reduces some, accelerate, it is also smaller resulting from this increase of the pressure loss.

Therefore, in the situation that outdoor heat converter 162 being arranged on above intermediate heat exchanger 161, 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 tri-embodiments-

According to above-mentioned the 3rd embodiment, because outdoor heat converter 162 is arranged on to the higher top of the interior air velocity of outdoor machine shell 163, so can improve the heat exchange performance of outdoor heat converter 162.Also because the lower outdoor heat converter 162 of cold-producing medium flow velocity is arranged on to the higher top of the interior air velocity of outdoor machine shell 163, so can not make refrigerant pressure loss increase the miniaturization that realizes outdoor heat converter 162.

On the other hand, by intermediate heat exchanger 161 being arranged on to the lower below of the interior air velocity of outdoor machine shell 163, increase the quantity of refrigerant path, thereby can prevent reliably that the pressure loss of cold-producing medium in intermediate heat exchanger 161 from increasing.

As mentioned above, by the outdoor heat converter 162 of the more difficult increase of the pressure loss of cold-producing medium being arranged on to top, realize miniaturization, thereby the size that can suppress outdoor heat exchanger group 160 increases, and can also suppress the pressure loss of cold-producing medium in intermediate heat exchanger 161 simultaneously.Other structure, effect are all identical with the second embodiment with the first embodiment.

-variation of tri-embodiments-

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

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

Described outdoor fan 166 is for the air being drawn in outdoor machine shell 163 is sent to the fan of 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.And outdoor fan 166 passes through each heat exchanger 161,162 air sucking from suction inlet 164, then this air is blown out towards outside from blow-off outlet 165.

As shown in figure 14, in the inside of outdoor machine shell 163, from downside towards upside, piling up successively 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: first total collection pipe 240, second total collection pipe 250, many flat tubes 231 and a plurality of fin 235.The first total collection pipe 240, the second total collection pipe 250, flat tube 231 and fin 235 are all aluminium alloy part, through soldering, are engaged with each other together.

The first total collection pipe 240 and the second total collection pipe 250 all form elongated hollow tubular.In each heat exchanger 161,162, the first total collection pipe 240 is standing and is being arranged on the distolateral of flat tube 231, and the second total collection pipe 250 is standing that to be arranged on another of flat tube 231 distolateral.That is to say, the first total collection pipe 240 and the second total collection pipe 250 take separately be axially vertical direction ground downward-extension.

Upper end and the bottom of the first total collection pipe 240 are closed, and are connected with the first tube connector 240b on the bottom of this first total collection pipe 240.The first tube connector 240b is communicated with the hydraulic fluid side of refrigerant loop 143.That is to say the hydraulic fluid side collector that the cold-producing medium (liquid single-phase refrigerant or gas-liquid two-phase cold-producing medium) that the first total collection pipe 240 formations comprise liquid is flowed 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 this second total collection pipe 250.The second tube connector 250b is connected with the gas side of refrigerant loop 143.That is to say, the second total collection pipe 250 forms the gas side collector that gaseous refrigerant is flowed through.

Each heat exchanger 161,162 of this variation has many flat tubes 231.Flat tube 231 is that its section shape perpendicular to axle is flat Long Circle or the heat-transfer pipe of rectangle.In each heat exchanger 161,162, many flat tubes 231 be take its bearing of trend as left and right directions, and the form toward each other of flattened side separately sets.Many flat tubes 231 keep certain intervals and are being arranged above and below arranging each other.The first total collection pipe 240 is inserted in one end of each root flat tube 231, and the second total collection pipe 250 is inserted in the other end of each root flat tube 231.

As shown in figure 15, in each root flat tube 231, be formed with many refrigerant path 232.Each refrigerant path 232 is the paths along the bearing of trend extension of flat tube 231.In each root flat tube 231, many refrigerant path 232 form a line along the width of the bearing of trend quadrature with flat tube 231.Be formed on refrigerant path 232 in each root flat tube 231 one end separately and communicate with the inner space of the first total collection pipe 240, the other end separately 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 upper and lower crooked corrugated fin of extending, and is arranged between neighbouring flat tube 231.On fin 235, be formed with a plurality of heat transfer parts 236 that are arranged on flat tube 231 bearing of trends.Heat transfer part 236 forms from the flat tube adjacent flat tube 231 until another flat tube tabular.On heat transfer part 236, be provided with a plurality of shutter boards (louver) 237 that a part for this heat transfer part 236 cut and form.These shutter boards 237 are gone up downward-extension abreast with the leading edge (that is, the end of windward one side) of heat transfer part 236 in fact.On heat transfer part 236, each shutter board 237 is being arranged and is being formed towards leeward one side from windward one side.

At leeward one side end of heat transfer part 236, connecting a more side-prominent outstanding board 238.Outstanding board 238 forms give prominence to more up and down than heat transfer part 236 trapezoidal tabular.In each heat exchanger 161,162, neighbouring outstanding board 238,238 overlaid on thickness direction, is in contact with one another in fact.

Be provided with many flat tubes 231 and a plurality of fin 235,235.Between the flat tube 231 being arranged above and below, be provided with fin 235,235.In middle heat exchange department 41,42,43,161, air passes through between the flat tube 231 being arranged above and below, and fluid mobile in this air and the fluid passage 232 in flat tube 231 carries out heat exchange.

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

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

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

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

According to described variation, due to intermediate heat exchanger 161 and outdoor heat exchange department 162 are configured to: comprised the many flat tubes 231 and a plurality of fin 235,235 that are formed with many refrigerant path 232, thereby can reduce flowing resistance.For this reason, in ventilation road, the flow velocity of mobile air is accelerated.Also the heat transfer area due to cold-producing medium increases by flat tube 231, thereby the heat exchange performance of cold-producing medium is improved.For this reason, can make the COP (coefficient of performance) of aircondition 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 on above-below direction.

In the related outdoor heat exchanger group 40 of this reference example, from downside towards upside, piling up successively and be provided with outdoor heat converter 44, the first intermediate heat exchanger 41, the 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 forms: the order according to outdoor heat converter 44, the 3rd intermediate heat exchanger 43, the first intermediate heat exchanger 41 and the second intermediate heat exchanger 42 increases successively.

Described each heat exchanger 41,42,43,44 consists of so-called tubes provided with cross ribs plate heat exchanger.Each heat exchanger 41,42,43,44 comprises: a plurality of heat transfer tube group 50 and the thermofin 51 respectively with many heat-transfer pipes 52 and Duo Gen U word pipe.

Described a plurality of heat transfer tube group 50 is being arranged in order up and down to arrange and is forming.In each heat transfer tube group 50, many heat-transfer pipes 52 along the flow direction of air up and down each two ground be set be altogether arranged to three row, in the left side of Figure 19 (being windward one side), form and have the first pipe row 53, central authorities' formation at Figure 19 has the second pipe row 54, forms have the 3rd pipe row 55 on the right side of Figure 19 (being leeward one side).That is to say, 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 the first embodiment and the second embodiment.

In above-mentioned the first embodiment and the second embodiment, used 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 the first embodiment～four embodiment, be set as two-stage compression supercritical refrigeration cycle and level Four compression supercritical refrigeration cycle, but the present invention is not limited to this, also can be applied to for example three stage compression type supercritical refrigeration cycle and other multi-stage compression formula kind of refrigeration cycle.

In above-mentioned the first embodiment and the second embodiment, the structure of heat exchanger is set as to pipe type, but the present invention is not limited to this.

Particularly, as shown in figure 16, outdoor unit 3 comprises outdoor machine shell 121.Outdoor machine shell 121 forms the casing of the rectangular shape of lengthwise, is formed with the suction inlet 123 of air below these outdoor machine shell 121 fronts, and at the upper surface of this outdoor machine shell 121, is formed with the blow-off outlet 124 of air.In the inside of outdoor machine shell 121, be provided with outdoor heat exchanger group 40 and outdoor fan 122.Outdoor heat exchanger group 40 comprises: outdoor heat converter 44, the first intermediate heat exchanger 41, the 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, from downside towards upside, piling up successively and be provided with the first intermediate heat exchanger 41, the second intermediate heat exchanger 42, the 3rd intermediate heat exchanger 43 and outdoor heat converter 44.That is to say, outdoor heat converter 44 is arranged on than on the first to the 3rd intermediate heat exchanger 41,42,43 top sides' position.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: first total collection pipe 240, second total collection pipe 250, many flat tubes 231 and a plurality of fin 235.The first total collection pipe 240, the second total collection pipe 250, flat tube 231 and fin 235 are all aluminium alloy part, through soldering, are engaged with each other together.

The first total collection pipe 240 and the second total collection pipe 250 all form elongated hollow tubular.In each heat exchanger 41,42,43,44, the first total collection pipe 240 is standing and is being arranged on the distolateral of flat tube 231, and the second total collection pipe 250 is standing that to be arranged on another of flat tube 231 distolateral.That is to say, the first total collection pipe 240 and the second total collection pipe 250 take separately be axially vertical direction ground downward-extension.

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 bottom.The first tube connector 240b is communicated with the hydraulic fluid side of refrigerant loop 10.That is to say the hydraulic fluid side collector that the cold-producing medium (liquid single-phase refrigerant or gas-liquid two-phase cold-producing medium) that the first total collection pipe 240 formations comprise liquid is flowed through.Upper end and the bottom of the second total collection pipe 250 are closed, and are connected with above it the second tube connector 250b.The second tube connector 250b is connected with the gas side of refrigerant loop 143.That is to say, the second total collection pipe 250 forms the gas side collector that gaseous refrigerant is flowed through.

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

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

Fin 235 is upper and lower crooked corrugated fin of extending, and is arranged between neighbouring flat tube 231.On fin 235, be formed with a plurality of heat transfer parts 236 that are arranged on flat tube 231 bearing of trends.Heat transfer part 236 forms from the flat tube adjacent flat tube 231 until another flat tube tabular.On heat transfer part 236, be provided with a plurality of shutter boards 237 that a part for this heat transfer part 236 cut and form.These shutter boards 237 are gone up downward-extension abreast with the leading edge (that is, the end of windward one side) of heat transfer part 236 in fact.On heat transfer part 236, each shutter board 237 is being arranged and is being formed towards leeward one side from windward one side.

At leeward one side end of heat transfer part 236, connecting a more side-prominent outstanding board 238.Outstanding board 238 forms give prominence to more up and down than heat transfer part 236 trapezoidal tabular.In each heat exchanger 41,42,43,44, neighbouring outstanding board 238,238 overlaid on thickness direction, is in contact with one another 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 intention is not limited the scope of the present invention, its application or its purposes.

-industrial applicability-

In sum, the present invention to the refrigerating plant that carries out multi-stage compression formula kind of refrigeration cycle of great use.

-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 (5)

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

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

Middle heat exchange department (41,42,43,161), it is arranged between adjacent two described compressing mechanisms (21,22,23,24,151,152), make the cold-producing medium and the outdoor air that from a rudimentary side compressing mechanism (21,22,23,151), flow to a senior side compressing mechanism (22,23,24,152) carry out heat exchange and carry out cooling to this cold-producing medium

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

Casing (121,163), on the side of this casing (121,163), be formed with 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), taken in described compressing mechanism (21～24,151,152), middle heat exchange department (41,42,43,161) and outdoor heat exchange department (44,162), it is characterized in that:

The state setting that in the middle of described, heat exchange department (41,42,43,161) and described outdoor heat exchange department (44,162) erect with the suction inlet along described casing (121,163) (123,164), and described outdoor heat exchange department (44,162) is arranged in than on the position of the top side of heat exchange department (41,42,43,161) in the middle of described.

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

Described multi-stage compression portion (20) has three above compressing mechanisms (21～24),

In the middle of a highest side, heat exchange department (43) is arranged in than heat exchange department (41,42) top side in the middle of other 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:

A plurality of described in the middle of heat exchange departments (41,42,43) be arranged to: flow into described in the middle of the pressure of cold-producing medium of heat exchange department higher, this centre heat exchange department is located in more top side's position.

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

In the middle of described, heat exchange department (41,42,43,161) comprises many flat tubes (231) and a plurality of fin (235,235), this many flat tubes (231) side is arranged above and below opposite to each other and in inside, is formed with many fluid passages (232) that extend along pipe range direction, and the plurality of fin (235,235) will be divided into many ventilation roads that air is flowed through 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 a plurality of fin (235,235), this many flat tubes (231) side is arranged above and below opposite to each other and in inside, is formed with many fluid passages (232) that extend along pipe range direction, and the plurality of fin (235,235) will be divided into many ventilation roads that air is flowed through between adjacent described flat tube (231).

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