CN105247298B

CN105247298B - Turborefrigerator

Info

Publication number: CN105247298B
Application number: CN201380076771.2A
Authority: CN
Inventors: 古贺淳; 上田宪治
Original assignee: Mitsubishi Heavy Industries Ltd
Current assignee: Mitsubishi Heavy Industries Air Conditioning and Refrigeration Systems Corp
Priority date: 2013-06-24
Filing date: 2013-06-24
Publication date: 2017-06-23
Anticipated expiration: 2033-06-24
Also published as: CN107255371B; CN105247298A; WO2014207796A1; US20160123639A1; CN107255371A

Abstract

Turborefrigerator (1A) possesses：Centrifugal compressor (10), it is by the rotation of the impeller (18) with multiple blades (21) come compression refrigerant (W)；Condenser (11), it is cooled down to the refrigerant (W) after compression；First expansion valve (12) and the second expansion valve (13), the refrigerant (W) in its condenser in future (11) depressurizes and forms gas-liquid two-phase, and the first expansion valve (12) and the second expansion valve (13) are connected in series；Evaporator (15), it evaporates the refrigerant (W) from the second expansion valve (13)；Energy-saving appliance (14), it is configured between first expansion valve (12) and the second expansion valve (13), and refrigerant (W) is separated into gas-liquid two-phase；And road (16) are flowed into, it can be such that the gas phase (W1) isolated from refrigerant (W) in energy-saving appliance (14) is flowed between the leading edge (21a) and trailing edge (21b) of blade (21) in the adjacent interlobate primary flow path (FC) of impeller (18).

Description

Turborefrigerator

Technical field

Turborefrigerator the present invention relates to use centrifugal compressor.

Background technology

For refrigeration machine, the turborefrigerator of centrifugal compressor has been known to use.The turborefrigerator is widely used in greatly Cooling device in large-size air conditioning, the chemical device group in tall building etc..

Also, the turborefrigerator is also required that based on refrigerating capacity as the consciousness to environmental problem increases in recent years, The high performance that is brought of raising.

In addition, high performance on the one hand is required, on the other hand from from the viewpoint of reduces cost, it is desirable to reduce compressor Series.Therefore, even if reducing compressor series for reduces cost, it is also necessary to maintain refrigerating capacity, i.e. refrigerating capacity The necessity for further improving increases.

Here, in the CO disclosed in patent document 1₂It is (swollen in two decompressors being connected in series in refrigerating circulatory device Swollen valve and capillary) between configure gas-liquid separator, from the refrigerant for having passed through first decompressor isolate gas phase with After liquid phase, only liquid phase is imported to second decompressor and is depressurized.

By doing so it is possible, the enthalpy difference i.e. raising of refrigerating capacity R of the refrigerant before and after realizing evaporator.

Citation

Patent document

Patent document 1：Japanese Unexamined Patent Publication 2006-292229 publications

Brief summary of the invention

The invention problem to be solved

However, the construction disclosed in patent document 1 is defined in scroll compressor, do not show to be applied to possess impeller Centrifugal compressor example.

Here, before this, in the turborefrigerator that the multistage centrifugal compressor will with multiple impellers is applied to compressor, To configuration, i.e. impeller stream to each other is blown through the gas phase of the refrigerant that gas-liquid separator separates go out between the level of compressor, So as to realize the raising of refrigerating capacity using gas-liquid separator.Therefore, the series of the setting quantity than compressor of gas-liquid separator It is few one, it is impossible to which that further expectation has used the raising of the refrigerating capacity of gas-liquid separator.

Additionally, as noted previously, as the stream by the gas phase of the refrigerant from gas-liquid separator to impeller to each other blows Enter, therefore, in the case where compressor is used as using the single-stage radial compressor being for example compressed by an impeller, it is impossible to It is blown through the gas phase of the refrigerant that gas-liquid separator separates go out.Accordingly, it is difficult to single-stage radial compressor application gas-liquid separation Device.Therefore, in the refrigeration machine for having used single-stage radial compressor, it is difficult to carrying for refrigerating capacity is realized using gas-liquid separator It is high.

So, when using gas-liquid separator, it sets quantity and is limited by the series of compressor, it is difficult to compressed reducing Refrigerating capacity is improved while the series of machine.

The content of the invention

The present invention allows for such situation and completes, there is provided can suppress cost and improve refrigerating capacity so as to realisation The turborefrigerator that can be improved.

Means for solving the problems

(1) first method of the invention, turborefrigerator possesses centrifugal compressor, condenser, multiple pressure reducers, steaming Hair device, gas-liquid separator and inflow road.Centrifugal compressor is by the rotation of the impeller with multiple blades come compression refrigerant. Condenser to compression after the refrigerant cool down.Pressure reducer depressurizes and shape the refrigerant from the condenser Into gas-liquid two-phase, and connected with the number of tandem more than the series than the centrifugal compressor.Evaporator makes by the multiple Refrigerant evaporation after pressure reducer.Gas-liquid separator is respectively configured with one between the pressure reducer, will be described Refrigerant is separated into gas-liquid two-phase.Flowing into road makes to be separated from the refrigerant among at least one of described gas-liquid separator The gas phase for going out is flowed between adjacent described interlobate leading edge and trailing edge.

According to said structure, the gas phase isolated from refrigerant at least one gas-liquid separator is from flowing into road direction blade Leading edge and trailing edge between be blown into.Therefore, it is not necessary to i.e. impeller is blown into utilizes gas-liquid to each other between the level of an orientation centrifugal compressor The gas phase that separator is isolated from refrigerant.Even if additionally, the series of centrifugal compressor is single-stage or multistage, can not receive The series limitation ground of centrifugal compressor reliably sets gas-liquid separator.

Also, due to can by gas-liquid separator refrigerant is formed as only be liquid phase state, therefore, it is possible to again Depressurized using pressure reducer.That is, the kind of refrigeration cycle that such as kind of refrigeration cycle is the circulation of single stage compress single-stage expansion can be formed For single stage compress compound expansion is circulated.Therefore, compare with the situation for not utilizing gas-liquid separator to separate gas phase from refrigerant, can Expand the enthalpy difference by the refrigerant before and after evaporator, it is possible to increase refrigerating capacity.Additionally, by will using gas-liquid separator from The gas phase that refrigerant is isolated can reduce the temperature of the refrigerant in compressor to being blown into centrifugal compressor, additionally it is possible to real The raising of existing compression efficiency.

(2) on the basis of the turborefrigerator of (1), or, the inflow road makes the gas phase to than institute Position of the leading edge of blade with the pars intermedia of trailing edge by front edge side is stated to flow into.

According to said structure, in this way flow into gas phase due to flowing into road, therefore enable in particular to make the blade in impeller The stall region speedup that the front edge side of surrounding is produced, the action model of centrifugal compressor is realized by improving the inhibition of surge The expansion enclosed.Therefore, it is possible to further realize that performance is improved.

(3) on the basis of the turborefrigerator of (1) or (2), or, the inflow road makes the gas phase edge The circulating direction of the refrigerant in the meridian plane of the impeller is flowed into.

According to said structure, in this way flow into gas phase due to flowing into road, therefore, will not be flowed in impeller in gas phase The smoothness of the flowing of main flow is hindered when the main flow of logical refrigerant mixes.Thereby, it is possible to reduce losses by mixture, can be further Realize that the performance of impeller is improved.

(4) on the basis of (1) to the turborefrigerator any one of (3), or, the inflow road There is the water conservancy diversion leaf abreast set with the blade on the inner peripheral surface on the inflow road.

According to said structure, using such water conservancy diversion leaf, the gas phase from gas-liquid separator is blown into by flowing into road, in institute State main flow from gas phase to the refrigerant in impeller mix when, the gas phase is along the direction of the flowing of main flow in the circumferential along identical Direction flows into.Therefore, the smoothness of the flowing of main flow will not be hindered, losses by mixture can be reduced, improve the performance of impeller.

(5) on the basis of (1) to the turborefrigerator any one of (4), or, the inflow road The blade-side end with expanding towards downstream.

It is expanding in blade-side due to flowing into road according to said structure, therefore, it is possible in the state of the flow velocity for reducing gas phase It is lower by gas phase to being blown into impeller.Therefore, gas phase in impeller main flow mix when, will not hinder main flow flowing it is smooth Property, losses by mixture can be reduced, preventing the performance of impeller reduces.

Invention effect

According to described turborefrigerator, road, energy are flowed into by being set between adjacent interlobate leading edge and trailing edge It is enough to carry out setting for gas-liquid separator in the case where setting quantity is not limited by the series of centrifugal compressor.Therefore, reduce The series of centrifugal compressor, can suppress cost and improve refrigerating capacity, realize that performance is improved.

Brief description of the drawings

Fig. 1 is the overall system view of the turborefrigerator for showing first embodiment of the invention.

Fig. 2 is related to the centrifugal compressor in the turborefrigerator of first embodiment of the invention, is to show impeller periphery Sectional view.

Fig. 3 is related to the centrifugal compressor in the turborefrigerator of first embodiment of the invention, is the integral vertical of impeller Body figure.

Fig. 4 is related to the turborefrigerator of first embodiment of the invention, is the figure that simplification shows kind of refrigeration cycle.

Fig. 5 is related to the centrifugal compressor in the turborefrigerator of first embodiment of the invention, is to show impeller periphery Sectional view, and show impeller be case type situation.

Fig. 6 is the overall system view of the first variation of the turborefrigerator for showing first embodiment of the invention.

Fig. 7 is the overall system view of the second variation of the turborefrigerator for showing first embodiment of the invention.

Fig. 8 is the overall system view of the 3rd variation of the turborefrigerator for showing first embodiment of the invention.

Fig. 9 is related to the centrifugal compressor of the 3rd variation of the turborefrigerator of first embodiment of the invention, is to show Go out the sectional view of impeller periphery.

Figure 10 is related to the centrifugal compressor in the turborefrigerator of second embodiment of the present invention, is to show impeller periphery Sectional view.

Figure 11 is related to the centrifugal compressor in the turborefrigerator of second embodiment of the present invention, is seen from radial outside Figure when flowing into road is examined, the A-A sections of Figure 10 are shown.

Figure 12 is related to the centrifugal compressor in the turborefrigerator of third embodiment of the present invention, is to show impeller periphery Sectional view.

Figure 13 is related in the turborefrigerator of the first variation of the turborefrigerator of third embodiment of the present invention Centrifugal compressor, is the sectional view for showing impeller periphery.

Figure 14 is related in the turborefrigerator of the second variation of the turborefrigerator of third embodiment of the present invention Centrifugal compressor, is the sectional view for showing impeller periphery.

Specific embodiment

Hereinafter, the turborefrigerator 1A to first embodiment of the invention is illustrated.

Turborefrigerator 1A is the use of the cooling device of the compressor of the turbine types such as centrifugal compressor, is used in office big Air-conditioning device in the large-scale equipments such as tall building.

Also, as shown in figure 1, turborefrigerator 1A possess compression refrigerant W centrifugal compressor 10, to compression after The first expansion valve (pressure reducer) that condenser 11 that refrigerant W is cooled down, the refrigerant W to carrying out condenser 11 are depressurized 12 and the refrigerant W from the first expansion valve 12 is separated into the energy-saving appliance (gas-liquid separator) 14 of gas-liquid two-phase.

Additionally, turborefrigerator 1A possesses can make the gas phase W1 from energy-saving appliance 14 to inflow in centrifugal compressor 10 Flow into road 16, the second expansion valve (pressure reducer) 13 that the liquid phase from energy-saving appliance 14 is depressurized again and make swollen from second The evaporator 15 of the refrigerant W evaporations of swollen valve 13.

Here, the refrigerant W for example uses R134a (HFC) for replacing freon etc..

As shown in Fig. 2 centrifugal compressor 10 is installed on the rotary shaft 5 that can be rotated around axis P.Centrifugal compressor 10 possesses The impeller 18 that can be rotated around axis P together with rotary shaft 5 and the shell 17 that impeller 18 is covered from the radial outside of axis P.

Rotary shaft 5 and the equiaxial combination of motor (not shown), can rotate around axis P.

As shown in figure 3, impeller 18 has：Disk 20, the side (upside in Fig. 3) as axis P directions of the disk 20 The face of the upstream side flowed into for refrigerant W be with from upstream side towards downstream from the radially inner side of axis P laterally by The curved surface in flaring footpath；And multiple (being in the present embodiment 17) is formed as foliated blade 21, it is set to from this Curved surface is erected.

In addition, in the present embodiment, impeller 18 is formed as the style of opening without guard ring.

Also, adjacent blade 21 is formed as the main flow that refrigerant W can circulate from upstream side towards downstream to each other Road FC.

Shell 17 is the part for covering impeller 18 from radial outside with the state in air switch gap between impeller 18.

Here, in the present embodiment, centrifugal compressor 10 is the adiabatic compression that refrigerant W is carried out by an impeller 18 Single-stage compressor.

Refrigerant W of the condenser 11 after cooling water etc. makes to be compressed using centrifugal compressor 10 carries out heat exchange and carries out Cooling, makes refrigerant W form the state of liquid.

First expansion valve 12 makes the heat-insulated expansions of the refrigerant W of the liquid for carrying out condenser 11 and depressurizes, and makes one of liquid Divide evaporation, so as to refrigerant W to be formed as the state of gas-liquid two-phase.

Energy-saving appliance 14 by the refrigerant W for being formed as the state of gas-liquid two-phase in the first expansion valve 12 be separated into gas phase W1 with Liquid phase.

Flowing into road 16 can make the gas phase W1 that is isolated from the refrigerant W of gas-liquid two-phase by energy-saving appliance 14 to centrifugal compressed Primary flow path FC in the impeller 18 of machine 10 is flowed into.Specifically, it is leading edge 21a in the end of the upstream side of blade 21 to flow into road 16 It is between trailing edge 21b, to be arranged on the shell 17 of centrifugal compressor 10 with the end in downstream.Flowing into road 16 has towards leaf Take turns the inflow entrance 22 and connection inflow entrance 22 of the face opening of 18 sides and the inflow pipe 23 of energy-saving appliance 14.

Inflow entrance 22 is formed completely through the inside and outside of shell 17.The aperture position of the more preferably inflow entrance 22 is formed at and compares blade The position of the forward edge 21a sides of pars intermedia of 21 leading edge 21a and trailing edge 21b.

Second expansion valve 13 identically with the first expansion valve 12, gas phase W1 is isolated by energy-saving appliance 14, makes only to turn into liquid The heat-insulated expansion of the refrigerant W of phase and depressurize.

Evaporator 15 makes refrigerant W from the second expansion valve 13 and water etc. carry out heat exchange and evaporate, and forms saturation and steams The state of gas.

In such turborefrigerator 1A, the p-h line charts according to Fig. 4, as shown by the solid line, first, since point A By centrifugal compressor 10 by the refrigerant W adiabatic compressions of gas, with the state point of arrival B of constant entropy.Afterwards, by condenser 11 The refrigerant W of gas is cooled down, is allowed to be formed the state of saturated liquid, reach the point C on saturation curve, and then, by first The point of arrival D by the heat-insulated expansions of refrigerant W of liquid, the state as gas-liquid two-phase of expansion valve 12.

Here, gas phase W1 is isolated using energy-saving appliance 14 by the refrigerant W after the first expansion valve 12, gas phase W1 is from stream The inflow entrance 22 of approach 16 is blown into the primary flow path FC of the impeller 18 in centrifugal compressor 10.Therefore, because being only left refrigerant W Liquid phase, therefore refrigerant W imports with the state as saturated liquid state to the second expansion valve 13.That is, from the point D of Fig. 4 to Up to the point E on saturation curve.

From point E begin through the second expansion valve 13 become only liquid phase refrigerant W, i.e. liquid refrigerant W once again every Thermal expansion, point of arrival F.Then, from point F begin through evaporator 15 make liquid refrigerant W evaporate and form saturated vapor State, reaches the point A on saturation curve.

So, due to can be by flowing into the inflow pipe 23 in road 16, from the shell 17 for being formed at centrifugal compressor 10 Inflow entrance 22 imports the gas phase W1 of refrigerant W to the primary flow path FC of impeller 18, even if therefore using single-stage radial compressor In the case of, it is also possible to energy-saving appliance 14 is set.That is, can be additional from the point D of Fig. 4 to the isobaric variable quantity of point E to kind of refrigeration cycle.

Here, as indicated with broken lines in fig. 4, in the case of assuming that being not provided with energy-saving appliance 14, in the absence of Fig. 4 in from point D To the line segment of point E.That is, point F is changed into being located at the position of point F1.Therefore, it is possible to confirm that point F1 is located at the position by enthalpy side high than point F Put, compared with point A and point F1 is apart from R1, point A's and point F is bigger apart from R.

The situation is shown in Figure 4 for, and the kind of refrigeration cycle shown in dotted line is the circulation of single stage compress single-stage expansion, the opposing party Face, kind of refrigeration cycle shown in solid is single stage compress compound expansion circulation.

So, by setting energy-saving appliance 14, the single stage compress single-stage expansion for not separating gas phase W1 from refrigerant W can be followed Annular is as single stage compress compound expansion circulation.As a result, the enthalpy by the refrigerant W before and after evaporator 15 can be expanded Difference.That is, R ＞ R1, can realize the raising of refrigerating capacity.

Additionally, the gas phase W1 that will be isolated from refrigerant W by using energy-saving appliance 14 is to being blown into centrifugal compressor 10, energy The temperature of the refrigerant W in centrifugal compressor 10 is enough reduced, so compression efficiency can be improved.

In addition, the aperture position of inflow entrance 22 is formed between the leading edge 21a of blade 21 and trailing edge 21b, it is preferably formed in The position of the forward edge 21a sides of pars intermedia than the leading edge 21a and trailing edge 21b of blade 21.Thereby, it is possible to make around blade 21 The stall region speedup that leading edge 21a sides produce.This improves the inhibition of surge, the action of centrifugal compressor 10 is realized The expansion of scope.

Turborefrigerator 1A according to present embodiment, by between the leading edge 21a and trailing edge 21b of blade 21, preferably The inflow entrance 22 for flowing into road 16 is set in leading edge 21a sides, the gas phase W1 of the refrigerant W from energy-saving appliance 14 can be made to primary flow path FC is flowed into, and energy-saving appliance 14 thus can be also set in single-stage radial compressor.Therefore, it is set to list by by centrifugal compressor 10 Level, that is, reduce series, can suppress cost and improve refrigerating capacity, additionally it is possible to the raising of compression efficiency is realized, so energy Enough realize that performance is improved.

It should be noted that the first expansion valve 12, the second expansion valve 13 can also be for example by metal capillary shape pipe Capillary of composition etc..

In addition, in the present embodiment, illustrating situation of the impeller 18 for style of opening but it is also possible to be for example with guard ring 29 case type impeller 18A.In this case, start from energy-saving appliance 14 inflow road 16 inflow entrance 22 it is as shown in Figure 5 that Sample is formed at the dividing plate 28 in the outside of guard ring 29.

Also, in this case, gas phase W1 is blown into guard ring 29 with the gap of dividing plate 28, by seal 24 from upstream The primary flow path FC suctions of lateral impeller 18A.

Here, for example as shown in fig. 6, in the case of applying two-stage centrifugal compressor in centrifugal compressor 10, also can It is enough that the energy-saving appliance 14 illustrated by present embodiment is set, by the gas phase W1 of the refrigerant W from energy-saving appliance 14 towards impeller 18 Primary flow path FC be directed into the shell 17 of centrifugal compressor 10.

Specifically, three expansion valves 25,26,27 are connected in series, two energy-saving appliances 14 is set between each expansion valve. Also, the inflow pipe 23 for starting from the energy-saving appliance 14 of a side is connected with the inflow entrance 22 of the impeller 18 of a side, starts from the section of the opposing party The inflow pipe 23 of energy device 14 is connected with the inflow entrance 22 of the impeller 18 of the opposing party.

This way, it is not necessary to one is scheduled on impeller 18 connection starts from the inflow pipe 23 of energy-saving appliance 14 i.e. between level to each other, even if therefore In the case where centrifugal compressor 10 is two-stage centrifugal compressor, it is also possible to which two energy-saving appliances 14 are set.That is, series can not be received The setting of energy-saving appliance 14 is carried out to limitation, cost can be suppressed and refrigerating capacity is improved, can realize that performance is improved.

Additionally, as shown in fig. 7, in the case where centrifugal compressor 10 is formed as into two-stage centrifugal compressor, or, The inflow pipe 23 for starting from the energy-saving appliance 14 of a side is connected with the inflow entrance 22 of the impeller 18 of a side, starts from the energy-saving appliance 14 of the opposing party Inflow pipe 23 and impeller 18 level to each other between connect.

Also, as shown in figure 8, in the case where centrifugal compressor 10 is formed as into single-stage radial compressor, it is not limited to The energy-saving appliance 14 and two expansion valves illustrated by present embodiment.For example, it is also possible to set two energy-saving appliances 14 And three expansion valves 25,26,27, two inflow pipes 23 of energy-saving appliance 14 will be started from and connected with an inflow entrance for impeller 18 22 Connect, the gas phase W1 of the refrigerant W from energy-saving appliance 14 is imported to primary flow path FC.

Additionally, in the case where two energy-saving appliances 14 are provided with, as shown in figure 9, relative to an impeller 18, in blade 21 Leading edge 21a and trailing edge 21b between be formed separately two or more inflow entrance 22.And it is possible to by the inflow entrance 22 of a side with The energy-saving appliance 14 of one side is connected, and the inflow entrance 22 of the opposing party is connected with the energy-saving appliance 14 of the opposing party.

Alternatively, it is also possible to set more than three energy-saving appliances 14 and more than four expansion valves relative to an impeller 18.That is, As long as being that one more than quantity than energy-saving appliance 14, then the setting quantity of energy-saving appliance 14 is not pressed by centrifugation by the quantity set of expansion valve The series limitation of contracting machine 10.Therefore, it is possible to not selected the setting quantity of energy-saving appliance 14 by the series of centrifugal compressor 10 with being limited, The further raising of the refrigerating capacity based on energy-saving appliance 14 can be realized, performance can be further improved.And, it is also possible to by this The structure of sample is applied to two-stage centrifugal compressor, multistage centrifugal compressor.

Next, being illustrated to the turborefrigerator 1B of second embodiment of the present invention.

It should be noted that pair with first embodiment identical structural element mark identical reference and omit in detail Describe in detail bright.

In the present embodiment, in centrifugal compressor 30, from energy-saving appliance 14 towards the inflow road 36 and first of impeller 18 The inflow road 16 of implementation method is different.

As shown in Figure 10, flowing into road 36 includes the inflow entrance 42, Yi Jilian being formed on the shell 17 of centrifugal compressor 30 Connect the inflow pipe 43 of inflow entrance 42 and energy-saving appliance 14.The forming position of inflow entrance 42 is located at blade identically with first embodiment Between 21 leading edge 21a and trailing edge 21b, the forward edge 21a of pars intermedia of the leading edge 21a and trailing edge 21b than blade 21 is preferably located at Side.

Additionally, as shown in figure 11, each road 36 that flows into has at the front of the opening of inflow entrance 42 on inner peripheral surface 42a In the water conservancy diversion leaf 44 that the height of inflow entrance 42 extends on the whole.The water conservancy diversion leaf 44 is abreast set with the bearing of trend of blade 21.

In addition, inflow entrance 42 in primary flow path FC towards the circulating direction opening of the refrigerant W in the meridian plane of impeller 18. Specifically, as shown in Figure 10, in order that gas phase W1 is flowed into along the circulating direction of refrigerant W, the opening portion shape of inflow entrance 42 As the circulating direction along refrigerant W.In this case, inflow entrance 42 can both smoothly turned in the front of opening portion To (reference picture 10), it is also possible to turned in the midway for flowing into pipe 43.

In such turborefrigerator 1B, the gas phase W1 of the refrigerant W from energy-saving appliance 14 is by flowing into road 36 to leaf Primary flow path FC in wheel 18 is blown into.Then, to mixing the refrigeration from energy-saving appliance 14 in the refrigerant W circulated in the primary flow path FC The gas phase W1 of agent W.Now, the gas phase W1 of the refrigerant W from energy-saving appliance 14 is along the primary flow path FC in the meridian plane of impeller 18 The circulating direction of interior refrigerant W is flowed into.Additionally, by water conservancy diversion leaf 44, the gas phase W1 is in the circumferential also along primary flow path FC The circulating direction of interior refrigerant W is flowed into.Therefore, the smoothness of the flowing of refrigerant W in primary flow path FC will not be hindered, can Reduce the losses by mixture to the refrigerant W in primary flow path FC.

Turborefrigerator 1B according to present embodiment, it is identical with first embodiment, by reducing centrifugal compressor 30 Series, cost can be suppressed and realize performance improve.

On this basis, reduced with water conservancy diversion leaf 44 due to the formation direction that can utilize the inflow entrance 42 for flowing into road 36 and come from The gas phase W1 of the refrigerant W of energy-saving appliance 14 towards flow into primary flow path FC when losses by mixture, therefore, it is possible to further realize leaf The performance of wheel 18 is improved.

If it should be noted that the formation circulating direction of the direction towards refrigerant W of inflow entrance 42, can also be not provided with Water conservancy diversion leaf 44.If in addition, setting water conservancy diversion leaf 44, the formation direction of inflow entrance 42 can also be not towards the circulation side of refrigerant W To.

Next, being illustrated to the turborefrigerator 1C of third embodiment of the present invention.

It should be noted that pair with first embodiment and second embodiment identical structural element mark identical Reference and detailed.

In the present embodiment, in centrifugal compressor 50, from energy-saving appliance 14 towards the inflow road 56 and first of impeller 18 The difference of inflow road 36 for flowing into road 16 and second embodiment of implementation method.

As shown in figure 12, flowing into road 56 includes the inflow entrance 62, Yi Jilian being formed on the shell 17 of centrifugal compressor 50 Connect the inflow pipe 63 of inflow entrance 62 and energy-saving appliance 14.The forming position of inflow entrance 62 and first embodiment and the second embodiment party Formula is located between the leading edge 21a of blade 21 and trailing edge 21b in the same manner, is preferably located at leading edge 21a and trailing edge 21b than blade 21 The position of the forward edge 21a sides of pars intermedia.

Additionally, the open side for flowing into road 56, the side of blade 21 as inflow entrance 62 end is expanding.That is, road 56 is flowed into With from opening towards the inside of shell 17 to the half-way of inflow entrance circumferentially observation under with the chi bigger than inflow entrance 62 Very little depression wide diameter portion 64 in a concave shape.

In such turborefrigerator 1C, the gas phase W1 of the refrigerant W from energy-saving appliance 14 is by flowing into road 56 to leaf Primary flow path FC in wheel 18 is blown into, and the gas of the refrigerant W from energy-saving appliance 14 is mixed to the refrigerant W circulated in primary flow path FC Phase W1.Now, there is wide diameter portion 64 due to flowing into road 56, so that the sectional area of inflow entrance 62 increases in open side, from energy-conservation The gas phase W1 of the refrigerant W of device 14 is flowed into reducing the state of flow velocity.Therefore, the refrigerant W in primary flow path FC will not be hindered Flowing smoothness, the losses by mixture to the refrigerant W in primary flow path FC can be reduced.

Turborefrigerator 1C according to present embodiment, it is identical with first embodiment and second embodiment, pass through The series of centrifugal compressor 50 is reduced, cost can be suppressed and realized that performance is improved.

On this basis, due to that can reduce the refrigerant W's from energy-saving appliance 14 by flowing into the wide diameter portion 64 on road 56 Gas phase W1 is towards the losses by mixture in primary flow path FC during inflow, so can further realize that the performance of impeller 18 is improved.

(the first variation of the 3rd implementation method)

Here, as the first variation of the 3rd described implementation method, as shown in figure 13, wide diameter portion 64 may not be Concavity, and formed with the curved surface gradually expanding towards opening by the inner peripheral surface 62a of inflow entrance 62.In this case, flow The sectional area of entrance 62 will not be increased dramatically, and inner peripheral surface 62a is smoothly expanding.Thereby, it is possible to suppress from the blowout of inflow entrance 62 Situations such as gas phase W1 of refrigerant W is peeled off, and gas phase W1 can be made more swimmingly to primary flow path to reduce the state of flow velocity FC is flowed into.

(the second variation of the 3rd implementation method)

In addition, the second variation of the 3rd implementation method described in, as shown in figure 14, wide diameter portion 64 may not be Concavity, and by inner peripheral surface 62a only impeller 18 rear side as towards inflow entrance 22, gradually expanding curved surface is formed.At this In the case of kind, can be made from the gas phase W1 of the refrigerant W of the blowout of inflow entrance 62 to main flow with swimmingly reducing the state of flow velocity Road FC is flowed into.In addition, gas phase can be blown out from inflow entrance 62 along the circulating direction of the refrigerant W circulated in primary flow path FC W1。

More than, it is described in detail embodiments of the present invention, but not departing from the range of technology design of the invention, Some design alterations can be carried out.

For example, it is also possible to the water conservancy diversion leaf 44 of second embodiment is applied into first embodiment and the 3rd implementation method Inflow road 16,56.

Industrial utilizability

According to described turborefrigerator, road, energy are flowed into by being set between adjacent interlobate leading edge and trailing edge It is enough to carry out setting for gas-liquid separator in the case where setting quantity is not limited by the series of centrifugal compressor.Therefore, reduce The series of centrifugal compressor, can suppress cost and improve refrigerating capacity, can realize that performance is improved.

Description of reference numerals

1A ... turborefrigerators

5 ... rotary shafts

10 ... centrifugal compressors

11 ... condensers

12 ... first expansion valves (pressure reducer)

13 ... second expansion valves (pressure reducer)

14 ... energy-saving appliances (gas-liquid separator)

15 ... evaporators

16 ... flow into road

17 ... shells

18 ... impellers

18A ... impellers

20 ... disks

21 ... blades

21a ... leading edges

21b ... trailing edges

22 ... inflow entrances

23 ... flow into pipe

24 ... seals

25th, 26,27 ... expansion valve

28 ... dividing plates

29 ... guard rings

W ... refrigerants

W1 ... gas phases

P ... axis

FC ... primary flow paths

1B ... turborefrigerators

30 ... centrifugal compressors

36 ... flow into road

42 ... inflow entrances

42a ... inner peripheral surfaces

43 ... flow into pipe

44 ... water conservancy diversion leaves

1C ... turborefrigerators

50 ... centrifugal compressors

56 ... flow into road

62 ... inflow entrances

62a ... inner peripheral surfaces

63 ... flow into pipe

64 ... wide diameter portions

Claims

1. a kind of turborefrigerator, wherein, possess：

Centrifugal compressor, it is by the rotation of the impeller with multiple blades come compression refrigerant；

Condenser, its to compression after the refrigerant cool down；

Multiple pressure reducers, the refrigerant decompression from the condenser is formed gas-liquid two-phase by it, and with than described Number of tandem connection more than the series of centrifugal compressor；

Evaporator, it makes to be evaporated by the refrigerant after the multiple pressure reducer；

Multiple gas-liquid separators, it is respectively configured with one between the pressure reducer, and the refrigerant is separated into gas-liquid Two-phase；And

Multiple flows into roads, and it makes the gas phase respectively being isolated by from the refrigerant in the multiple gas-liquid separator adjacent Discretely flowed between the leading edge and the trailing edge between the interlobate leading edge and trailing edge.

2. turborefrigerator according to claim 1, wherein,

The inflow road makes the gas phase be flowed into by the position of front edge side to the pars intermedia of the leading edge than the blade and trailing edge.

3. turborefrigerator according to claim 1 and 2, wherein,

The inflow road makes the gas phase be flowed into along the circulating direction of the refrigerant in the meridian plane of the impeller.

4. turborefrigerator according to claim 1 and 2, wherein,

The inflow road has the water conservancy diversion leaf abreast set with the blade on the inner peripheral surface on the inflow road.

5. turborefrigerator according to claim 1 and 2, wherein,

The end of the blade-side on the inflow road is with expanding towards downstream.