CN107255371A

CN107255371A - Turborefrigerator

Info

Publication number: CN107255371A
Application number: CN201710430104.XA
Authority: CN
Inventors: 古贺淳; 上田宪治
Original assignee: Mitsubishi Heavy Industries Ltd
Current assignee: Mitsubishi Heavy Industries Thermal Systems Ltd
Priority date: 2013-06-24
Filing date: 2013-06-24
Publication date: 2017-10-17
Anticipated expiration: 2033-06-24
Also published as: CN105247298A; US20160123639A1; CN107255371B; WO2014207796A1; CN105247298B

Abstract

The present invention provides a kind of turborefrigerator, and it 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 of its condenser in future (11) is depressurized 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 from the second expansion valve (13)；Energy-saving appliance (14), it is configured between first expansion valve (12) and the second expansion valve (13), separates the refrigerant into gas-liquid two-phase；And road (16) are flowed into, it can be such that the gas phase (W1) isolated in energy-saving appliance (14) from refrigerant is flowed into the adjacent interlobate primary flow path (FC) of impeller (18) between the leading edge (21a) and trailing edge (21b) of blade (21).

Description

Turborefrigerator

The application be Application No. 201380076771.2, the applying date be June 24, entitled turbine system in 2013 The divisional application of the patent application of cold.

Technical field

The present invention relates to the turborefrigerator for having used 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 the large-size air conditioning in tall building, chemical device group etc..

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

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

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 depressurized.

By doing so it is possible, the enthalpy difference i.e. refrigerating capacity R raising 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, the multistage centrifugal compressor with multiple impellers is being applied in the turborefrigerator of compressor, To configuration, i.e. the stream of impeller to each other is blown through the gas phase for 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, series of the setting quantity than compressor of gas-liquid separator It is few one, it is impossible to further to expect to have used the raising of the refrigerating capacity of gas-liquid separator.

In addition, as noted previously, as the gas phase of the refrigerant from gas-liquid separator is blown to the stream of impeller to each other Enter, therefore, in the case where being used as compressor using the single-stage radial compressor being for example compressed by an impeller, it is impossible to It is blown through the gas phase for 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 of single-stage radial compressor has been used, 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 to be limited by the series of compressor, it is difficult to reducing compression Refrigerating capacity is improved while the series of machine.

The content of the invention

The present invention allow for such situation and complete 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) according to the 1st aspect of the present invention, turborefrigerator possesses centrifugal compressor, condenser, multiple pressure reducers, steaming Send out device, gas-liquid separator and flow into road.Centrifugal compressor is by the rotation of the impeller with multiple blades come compression refrigerant. Condenser is cooled down to the refrigerant after compression.Pressure reducer shape by the refrigerant decompression from the condenser Connected into gas-liquid two-phase, and 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 among at least one in the gas-liquid separator from refrigerant separation The gas phase gone out is flowed between the adjacent interlobate leading edge and trailing edge.

According to said structure, the gas phase isolated at least one gas-liquid separator from refrigerant is from flowing into road direction blade Leading edge and trailing edge between be blown into.Therefore, it is not necessary to which 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, can not be by addition, the series of centrifugal compressor is single-stage or multistage The series limitation ground of centrifugal compressor reliably sets gas-liquid separator.

Also, due to refrigerant can be formed as by gas-liquid separator be only liquid phase state, therefore, it is possible to again Depressurized using pressure reducer.That is, can be that the kind of refrigeration cycle that single stage compress single-stage expansion is circulated is formed by such as kind of refrigeration cycle Circulated for single stage compress compound expansion.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.In addition, by will using gas-liquid separator from The gas phase that refrigerant is isolated is blown into centrifugal compressor, can reduce the temperature of the refrigerant in 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 The position that the leading edge of blade and the pars intermedia of trailing edge are stated by front edge side is flowed into.

According to said structure, flow into gas phase in this way due to flowing into road, therefore enable in particular to make the blade in impeller Around the stall region speedup that produces of front edge side, realize the action model of centrifugal compressor 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, gas phase is flowed into this way due to flowing into road, therefore, will not be flowed in gas phase in impeller The smoothness of the flowing of main flow is hindered during the main flow mixing of logical refrigerant., can be further thereby, it is possible to reduce losses by mixture 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 When stating the main flow mixing of refrigerant of the gas phase into impeller, direction of the gas phase along the flowing of main flow is in the circumferential along identical Direction is flowed into.Therefore, the smoothness of the flowing of main flow will not be hindered, losses by mixture can be reduced, the performance of impeller is improved.

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

It is expanding in blade-side due to flowing into road according to said structure, therefore, it is possible in the state for the flow velocity for reducing gas phase It is lower to be blown into gas phase into impeller.Therefore, main flow from gas phase to impeller mixing 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 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 for the turborefrigerator for showing the first embodiment of the present invention.

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

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

Fig. 4 is related to the turborefrigerator of the first embodiment of the present invention, is to simplify the figure for showing kind of refrigeration cycle.

Fig. 5 is related to the centrifugal compressor in the turborefrigerator of the first embodiment of the present 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 the first embodiment of the present invention.

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

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

Fig. 9 is related to the centrifugal compressor of the 3rd variation of the turborefrigerator of the first embodiment of the present 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, Figure 10 A-A sections 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.

Embodiment

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

Turborefrigerator 1A is the cooling device for the compressor for having used 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 Condenser 11 that refrigerant W is cooled down, the first expansion valve (pressure reducer) depressurized to the refrigerant W for carrying out condenser 11 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.

In addition, turborefrigerator 1A, which possesses, can make what the gas phase W1 from energy-saving appliance 14 was flowed into 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 is such as using the R134a (HFC) for replacing freon.

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 shell 17 of impeller 18 can be covered around the axis P impellers 18 rotated together with rotary shaft 5 and from axis P radial outside.

Rotary shaft 5 and the isometric 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 For the refrigerant W upstream sides flowed into face be with from upstream side towards downstream from axis P radially inner side laterally by The curved surface in flaring footpath；And multiple (being 17 in the present embodiment) are 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 of no 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.

Condenser 11 makes the refrigerant W after being compressed using centrifugal compressor 10 carry out heat exchange and carry out by cooling water etc. Cooling, makes the state of refrigerant W formation liquid.

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

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

The gas phase W1 that is isolated by energy-saving appliance 14 from the refrigerant W of gas-liquid two-phase can be made to centrifugal compressed by flowing into road 16 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 End with downstream is between trailing edge 21b, to be arranged on the shell 17 of centrifugal compressor 10.Flowing into road 16 has towards leaf Take turns the inflow entrance 22 of the face opening of 18 sides and the inflow pipe 23 of connection inflow entrance 22 and 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, which is formed at, compares blade The position of 21 leading edge 21a and trailing edge the 21b forward edge 21a sides of pars intermedia.

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, condenser 11 is passed through The refrigerant W of gas is cooled down, is allowed to be formed the state of saturated liquid, the point C on saturation curve is reached, and then, pass through first Expansion valve 12 is by the heat-insulated expansions of the refrigerant W of liquid, the state as gas-liquid two-phase and point of arrival D.

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 primary flow path FC of impeller 18 of the inflow entrance 22 of approach 16 into centrifugal compressor 10 is blown into.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 Fig. 4 point D 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, beginning through evaporator 15 from point F evaporates the refrigerant W of liquid and forms 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 refrigerant W gas phase W1 to the primary flow path FC of impeller 18, therefore even in use single-stage radial compressor In the case of, energy-saving appliance 14 can be also set.That is, point D to point E that can be to kind of refrigeration cycle addition from Fig. 4 isobaric variable quantity.

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 in Fig. 4 from point D To point E line segment.That is, point F is changed into positioned at point F1 position.Therefore, it is possible to confirm that point F1 is located at the position by high enthalpy side than point F Put, compared with point A and point F1 is apart from R1, point A and point F's 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, it will can not followed from the refrigerant W single stage compress single-stage expansions for separating gas phase W1 Annular turns into 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.

In addition, will be blown into by using energy-saving appliance 14 from the refrigerant W gas phase W1 isolated 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 formation of inflow entrance 22 is preferably formed between the leading edge 21a and trailing edge 21b of blade 21 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 are produced.This improves the inhibition of surge, the action of centrifugal compressor 10 is realized The expansion of scope.

According to the turborefrigerator 1A of 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, by the way that centrifugal compressor 10 is set into single 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, the gap of gas phase W1 to guard ring 29 and dividing plate 28 is blown into, by seal 24 from upstream Lateral impeller 18A primary flow path FC suctions.

Here, for example as shown in fig. 6, in the case of applying two-stage centrifugal compressor in centrifugal compressor 10, also can The energy-saving appliance 14 illustrated by present embodiment is enough 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, two energy-saving appliances 14 can be also set.That is, can not be by series Limitation ground carries out the setting of energy-saving appliance 14, can suppress cost and improve refrigerating capacity, can realize that performance is improved.

In addition, 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, the inflow entrance 22 that will start from the inflow pipe 23 and an impeller 18 of two energy-saving appliances 14 connects Connect, the gas phase W1 of the refrigerant W from energy-saving appliance 14 is imported to primary flow path FC.

In addition, in the case where being provided with two energy-saving appliances 14, as shown in figure 9, relative to one 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 relative to one impeller 18, more than three energy-saving appliances 14 and more than four expansion valves are set.That is, As long as by the quantity set of expansion valve be than energy-saving appliance 14 quantity more than one, then the setting quantity of energy-saving appliance 14 do not pressed by centrifugation 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.Also, also can be 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 marking identical reference with first embodiment identical structural element and omitting detailed 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 embodiment is different.

As shown in Figure 10, inflow entrance 42, Yi Jilian that road 36 includes being formed on the shell 17 of centrifugal compressor 30 are flowed into 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 are preferably located at Side.

In addition, 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 The water conservancy diversion leaf 44 extended on the whole in the height of inflow entrance 42.The bearing of trend of the water conservancy diversion leaf 44 and blade 21 is abreast set.

In addition, inflow entrance 42 in primary flow path FC towards the refrigerant W in the meridian plane of impeller 18 circulating direction opening. Specifically, as shown in Figure 10, in order that circulating directions of the gas phase W1 along refrigerant W is flowed into, 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 can also be 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, the refrigeration from energy-saving appliance 14 is mixed into the refrigerant W circulated in primary flow path FC Agent W gas phase W1.Now, the primary flow path FC in meridian planes of the gas phase W1 of the refrigerant W from energy-saving appliance 14 along impeller 18 Interior refrigerant W circulating direction is flowed into.In addition, by water conservancy diversion leaf 44, the gas phase W1 is in the circumferential also along primary flow path FC Interior refrigerant W circulating direction 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 of from the refrigerant W to primary flow path FC.

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

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

If it should be noted that 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, set water conservancy diversion leaf 44, the formation direction of inflow entrance 42 can also not towards refrigerant W circulation side 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 description will be omitted.

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 embodiment.

As shown in figure 12, inflow entrance 62, Yi Jilian that road 56 includes being formed on the shell 17 of centrifugal compressor 50 are flowed into 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.

In addition, 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 in the case where the half-way from opening towards the inside of shell 17 to inflow entrance is from circumferential 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 refrigerant W of device 14 gas phase W1 is flowed into the state for reducing flow velocity.Therefore, the refrigerant W in primary flow path FC will not be hindered Flowing smoothness, the losses by mixture of from the refrigerant W to primary flow path FC can be reduced.

It is identical with first embodiment and second embodiment according to the turborefrigerator 1C of present embodiment, pass through The series of centrifugal compressor 50 is reduced, cost can be suppressed and realize 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 embodiment)

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

(the second variation of the 3rd embodiment)

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

More than, embodiments of the present invention are described in detail, but in the range of the technical concept of the present invention is not departed from, Some design alterations can be carried out.

For example, it is also possible to which the water conservancy diversion leaf 44 of second embodiment is applied into first embodiment and the 3rd embodiment 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 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, and the impeller is opened for multistage Put the impeller of type；

Condenser, it is cooled down to the refrigerant after compression；

Multiple pressure reducers, the refrigerant from the condenser is depressurized and forms 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 evaporate 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

Road is flowed into, it makes what is isolated from the refrigerant among a gas-liquid separator in the multiple gas-liquid separator Flow into, and make in other gas-liquids between the adjacent interlobate leading edge and trailing edge of the gas phase into an impeller The gas phase isolated among separator from the refrigerant enters to the mutual interstage flow of the impeller,

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

2. turborefrigerator according to claim 1, wherein,

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

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

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

4. turborefrigerator according to claim 1 or 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.