CN105247298A - Turbo refrigerator - Google Patents
Turbo refrigerator Download PDFInfo
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- CN105247298A CN105247298A CN201380076771.2A CN201380076771A CN105247298A CN 105247298 A CN105247298 A CN 105247298A CN 201380076771 A CN201380076771 A CN 201380076771A CN 105247298 A CN105247298 A CN 105247298A
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- Prior art keywords
- producing medium
- cold
- gas
- impeller
- turborefrigerator
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
- F25B43/006—Accumulators
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
- F25B1/053—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type of turbine type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/58—Cooling; Heating; Diminishing heat transfer
- F04D29/582—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps
- F04D29/5846—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps cooling by injection
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/13—Economisers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/23—Separators
Abstract
A turbo refrigerator (1A) provided with: a centrifugal compressor (10) for compressing a refrigerant (W) using the rotation of an impeller (18) having a plurality of blades (21); a condenser (11) for cooling the compressed refrigerant (W); a first expansion valve (12) and a second expansion valve (13), which are serially connected, for decompressing the refrigerant (W) from the condenser (11) so as to produce a gas-liquid two-phase; an evaporator (15) for causing the refrigerant (W) from the second expansion valve (13) to evaporate; an economizer (14) for separating the refrigerant (W) into gas and liquid phases, the economizer (14) being disposed between the first expansion valve (12) and the second expansion valve (13); and an inlet channel (16) for enabling the gas phase (W1) separated from the refrigerant (W) by the economizer (14) to flow between the front edges (21a) and the rear edges (21b) of the blades (21) in a main channel (FC) between the adjacent blades of the impeller (18).
Description
Technical field
The present invention relates to the turborefrigerator employing centrifugal compressor.
Background technology
For refrigeration machine, the known turborefrigerator employing centrifugal compressor.This turborefrigerator is widely used in the cooling device etc. in the large-size air conditioning of mansion, chemical device group.
Further, in recent years, increase along with to the consciousness of environmental problem, the high performance that the raising based on refrigerating capacity brings also is required to this turborefrigerator.
In addition, requiring high performance on the one hand, on the other hand from the view point of reducing costs, needing the progression reducing compressor.Therefore, even if decrease compressor progression to reduce costs, also must maintain refrigerating capacity, that is, the necessity of the further raising of refrigerating capacity increases.
Here, the CO disclosed in patent document 1
2in refrigerating circulatory device, gas-liquid separator is configured between two decompressors (expansion valve and capillary) be connected in series, after isolating gas phase and liquid phase from the cold-producing medium that have passed first decompressor, only liquid phase imported to second decompressor and reduce pressure.
By doing like this, realize the enthalpy difference of the cold-producing medium before and after evaporimeter and the raising of refrigerating capacity R.
At first technical literature
Patent document
Patent document 1: Japanese Unexamined Patent Publication 2006-292229 publication
Brief summary of the invention
The problem that invention will solve
But the structure disclosed in patent document 1 is defined in scroll compressor, the example being applied to the centrifugal compressor possessing impeller is not shown.
Here, before this, the multistage centrifugal compressor with multiple impeller is being applied in the turborefrigerator of compressor, be blown through the gas phase of the cold-producing medium that gas-liquid separator separates goes out to the inter-stage and impeller stream to each other that are configured in compressor, thus utilize gas-liquid separator to realize the raising of refrigerating capacity.Therefore, fewer than the progression of compressor one of the magnitude setting of gas-liquid separator, cannot expect the raising of the refrigerating capacity employing gas-liquid separator further.
In addition, as mentioned above, due to the gas phase of the cold-producing medium from gas-liquid separator is blown into impeller stream to each other, therefore, when adopt such as carry out the single-stage radial compressor that compresses as compressor by an impeller, the gas phase of the cold-producing medium that gas-liquid separator separates goes out cannot be blown through.Therefore, be difficult to single-stage radial compressor application gas-liquid separator.Therefore, in the refrigeration machine employing single-stage radial compressor, be difficult to use gas-liquid separator to realize the raising of refrigerating capacity.
Like this, when using gas-liquid separator, its magnitude setting is compressed the progression restriction of machine, is difficult to improve refrigerating capacity while the progression reducing compressor.
Summary of the invention
The present invention considers this type of situation and completes, provide can suppress cost and improve refrigerating capacity thus realize performance improve turborefrigerator.
For solving the means of problem
(1) according to the 1st aspect of the present invention, turborefrigerator possesses centrifugal compressor, condenser, multiple pressure reducer, evaporimeter, gas-liquid separator and flows into road.Centrifugal compressor carrys out compressed refrigerant by the rotation of the impeller with multiple blade.Condenser cools the described cold-producing medium after compression.Described cold-producing medium decompression from described condenser is formed gas-liquid two-phase by pressure reducer, and connects with the number of tandem more than the progression of described centrifugal compressor.Evaporimeter make by described multiple pressure reducer after the evaporation of described cold-producing medium.Gas-liquid separator is respectively configured with one each other at described pressure reducer, and described cold-producing medium is separated into gas-liquid two-phase.Inflow road makes to flow between adjacent described interlobate frontier and rear from the isolated gas phase of described cold-producing medium among at least one in described gas-liquid separator.
According to said structure, be blown between the frontier and rear of inflow road direction blade from the isolated gas phase of cold-producing medium at least one gas-liquid separator.Therefore, be not necessarily blown into each other to the inter-stage of centrifugal compressor and impeller and utilize gas-liquid separator from the isolated gas phase of cold-producing medium.In addition, even if the progression of centrifugal compressor is single-stage or multistage, by the progression restriction ground of centrifugal compressor, reliably gas-liquid separator can not both be set.
Further, owing to can cold-producing medium is formed as be only the state of liquid phase by gas-liquid separator, therefore, it is possible to again utilize pressure reducer to reduce pressure.That is, can be that the kind of refrigeration cycle that single stage compress single-stage expansion circulates is formed as single stage compress compound expansion circulation by such as kind of refrigeration cycle.Therefore, compare with the situation not utilizing gas-liquid separator to be separated gas phase from cold-producing medium, the enthalpy difference of the cold-producing medium before and after by evaporimeter can be expanded, can refrigerating capacity be improved.In addition, by by utilizing gas-liquid separator to be blown in centrifugal compressor from the isolated gas phase of cold-producing medium, the temperature of the cold-producing medium in compressor can be reduced, the raising of compression efficiency can also be realized.
(2) on the basis of the turborefrigerator of described (1), also can be that described inflow road makes described gas phase flow into the pars intermedia of the frontier and rear than described blade by the position of front edge side.
According to said structure, make gas phase flow in this way owing to flowing into road, therefore especially can make the stall region speedup that the front edge side around the blade of impeller produces, realized the expansion of the actuating range of centrifugal compressor by the inhibition of raising surge.Improve therefore, it is possible to realize performance further.
(3) on the basis of the turborefrigerator of described (1) or (2), also can be that described inflow road makes described gas phase flow into along the circulating direction of the described cold-producing medium in the meridian plane of described impeller.
According to said structure, gas phase is made to flow in this way owing to flowing into road, therefore, can not in the smoothness of flowing of gas phase to obstruction main flow during the main flow mixing of the cold-producing medium circulated in impeller.Thereby, it is possible to minimizing losses by mixture, the performance that can realize impeller further improves.
(4) on the basis of the turborefrigerator according to any one of described (1) to (3), also can be, described inflow road has the water conservancy diversion leaf arranged abreast with described blade on the inner peripheral surface on this inflow road.
According to said structure, utilize such water conservancy diversion leaf, from gas-liquid separator gas phase by flow into road be blown into, main flow from described gas phase to the cold-producing medium in impeller mixing time, described gas phase flows into along equidirectional in the circumferential along the direction of the flowing of main flow.Therefore, the smoothness of the flowing of main flow can not be hindered, can losses by mixture be reduced, improve the performance of impeller.
(5) on the basis of the turborefrigerator according to any one of described (1) to (4), also can be, the end of the described blade-side on described inflow road be along with expanding towards downstream.
According to said structure, expanding in blade-side owing to flowing into road, therefore, it is possible to gas phase is blown in impeller under the state of flow velocity reducing gas phase.Therefore, when gas phase mixes to the main flow in impeller, the smoothness of the flowing of main flow can not be hindered, can losses by mixture be reduced, prevent the performance of impeller from reducing.
Invention effect
According to described turborefrigerator, flowing into road by arranging between adjacent interlobate frontier and rear, the setting of gas-liquid separator can be carried out when the progression restriction of magnitude setting not by centrifugal compressor.Therefore, decrease the progression of centrifugal compressor, can cost be suppressed and improve refrigerating capacity, realize performance and improve.
Accompanying drawing explanation
Fig. 1 is the overall system view of the turborefrigerator that the first embodiment of the present invention is shown.
Fig. 2 relates to the centrifugal compressor in the turborefrigerator of the first embodiment of the present invention, is the sectional view that impeller periphery is shown.
Fig. 3 relates to the centrifugal compressor in the turborefrigerator of the first embodiment of the present invention, is the overall perspective view of impeller.
Fig. 4 relates to the turborefrigerator of the first embodiment of the present invention, is to simplify the figure that kind of refrigeration cycle is shown.
Fig. 5 relates to the centrifugal compressor in the turborefrigerator of the first embodiment of the present invention, is the sectional view that impeller periphery is shown, and illustrates that impeller is case type situation.
Fig. 6 is the overall system view of the first variation of the turborefrigerator that the first embodiment of the present invention is shown.
Fig. 7 is the overall system view of the second variation of the turborefrigerator that the first embodiment of the present invention is shown.
Fig. 8 is the overall system view of the 3rd variation of the turborefrigerator that the first embodiment of the present invention is shown.
Fig. 9 relates to the centrifugal compressor of the 3rd variation of the turborefrigerator of the first embodiment of the present invention, is the sectional view that impeller periphery is shown.
Figure 10 relates to the centrifugal compressor in the turborefrigerator of the second embodiment of the present invention, is the sectional view that impeller periphery is shown.
Figure 11 relates to the centrifugal compressor in the turborefrigerator of the second embodiment of the present invention, is figure when observing inflow road from radial outside, the A-A section of Figure 10 is shown.
Figure 12 relates to the centrifugal compressor in the turborefrigerator of the 3rd embodiment of the present invention, is the sectional view that impeller periphery is shown.
Figure 13 relates to the centrifugal compressor in the turborefrigerator of the first variation of the turborefrigerator of the 3rd embodiment of the present invention, is the sectional view that impeller periphery is shown.
Figure 14 relates to the centrifugal compressor in the turborefrigerator of the second variation of the turborefrigerator of the 3rd embodiment of the present invention, is the sectional view that impeller periphery is shown.
Detailed description of the invention
Below, the turborefrigerator 1A of the first embodiment of the present invention is described.
Turborefrigerator 1A is the use of the cooling device of the compressor of the turbine types such as centrifugal compressor, is used in the aircondition in the large-scale equipment such as office building.
And, as shown in Figure 1, this turborefrigerator 1A possess compressed refrigerant W centrifugal compressor 10, condenser 11, the first expansion valve (pressure reducer) 12 that the cold-producing medium W carrying out condenser 11 is reduced pressure and the energy-saving appliance (gas-liquid separator) the 14 cold-producing medium W from the first expansion valve 12 being separated into gas-liquid two-phase that the cold-producing medium W after compression is cooled.
In addition, the turborefrigerator 1A evaporimeter 15 that possesses the inflow road 16 that the gas phase W1 from energy-saving appliance 14 can be made to flow in centrifugal compressor 10, the second expansion valve (pressure reducer) 13 liquid phase from energy-saving appliance 14 again reduced pressure and the cold-producing medium W from the second expansion valve 13 is evaporated.
Here, described cold-producing medium W such as uses the R134a (hydrogen fluorohydrocarbon) etc. replacing freon.
As shown in Figure 2, centrifugal compressor 10 is installed on the rotating shaft 5 that can rotate around axis P.Centrifugal compressor 10 possesses the impeller 18 that can rotate around axis P together with rotating shaft 5 and the shell 17 covering impeller 18 from the radial outside of axis P.
Rotating shaft 5 is combined with axles such as not shown motor, can rotate around axis P.
As shown in Figure 3, impeller 18 has: dish 20, and the face of the upstream side flowed into for cold-producing medium W of the side (upside in Fig. 3) becoming axis P direction of this dish 20 is along with from upstream side towards downstream from the curved surface that the radially inner side of axis P is expanding gradually laterally; And multiple (being 17 in the present embodiment) is formed as foliated blade 21, it is set to erect from this curved surface.
In addition, in the present embodiment, impeller 18 is formed as the style of opening without guard ring.
Further, adjacent blade 21 is formed as the primary flow path FC that cold-producing medium W can circulate from upstream side towards downstream to each other.
Shell 17 is the parts covering impeller 18 with the state of standard width of a room in an old-style house gap empty between impeller 18 from radial outside.
Here, in the present embodiment, centrifugal compressor 10 is the single-stage compressors being carried out the adiabatic compression of cold-producing medium W by an impeller 18.
Condenser 11 makes the cold-producing medium W after utilizing centrifugal compressor 10 to compress carry out heat exchange by cooling water etc. and cools, and makes cold-producing medium W form the state of liquid.
First expansion valve 12 makes the heat insulation expansion of cold-producing medium W of the liquid of condenser 11 and reduces pressure, and a part for liquid is evaporated, thus cold-producing medium W is formed as the state of gas-liquid two-phase.
The cold-producing medium W being formed as the state of gas-liquid two-phase in the first expansion valve 12 is separated into gas phase W1 and liquid phase by energy-saving appliance 14.
Flow into road 16 can make to be flowed into the primary flow path FC the impeller 18 of centrifugal compressor 10 by the isolated gas phase W1 of cold-producing medium W of energy-saving appliance 14 from gas-liquid two-phase.Specifically, flow into road 16 between the end and trailing edge 21b in the end of the upstream side of blade 21 and leading edge 21a and downstream, be arranged on the shell 17 of centrifugal compressor 10.Flow into road 16 have the face opening towards impeller 18 side inflow entrance 22 and connect the inflow pipe 23 of inflow entrance 22 and energy-saving appliance 14.
Inflow entrance 22 is formed as inside and outside through shell 17.More preferably the aperture position of this inflow entrance 22 is formed at the position than the leading edge 21a of blade 21 and the pars intermedia forward edge 21a side of trailing edge 21b.
Second expansion valve 13 identically with the first expansion valve 12, isolates gas phase W1 by energy-saving appliance 14, makes only to become the heat insulation expansion of cold-producing medium W of liquid phase and reduces pressure.
Evaporimeter 15 makes carry out heat exchange from the cold-producing medium W of the second expansion valve 13 and water etc. and evaporate, and forms the state of saturated vapor.
In such turborefrigerator 1A, the p-h line chart according to Fig. 4, as shown by the solid line, first, begins through centrifugal compressor 10 by the cold-producing medium W adiabatic compression of gas, with the state point of arrival B of constant entropy from an A.Afterwards, by condenser 11, the cold-producing medium W of gas is cooled, make it to form the state of saturated liquid, arrive the some C on saturation curve, and then, by the cold-producing medium W heat insulation expansion of the first expansion valve 12 by liquid, become the state of gas-liquid two-phase and point of arrival D.
Here, utilize energy-saving appliance 14 to isolate gas phase W1 by the cold-producing medium W after the first expansion valve 12, this gas phase W1 is blown into from the inflow entrance 22 flowing into road 16 to the primary flow path FC of the impeller 18 centrifugal compressor 10.Therefore, owing to being only left the liquid phase of cold-producing medium W, therefore cold-producing medium W imports to the second expansion valve 13 with the state becoming saturated liquid state.That is, the some E saturation curve is arrived from the some D of Fig. 4.
The cold-producing medium W heat insulation expansion once again that the second expansion valve 13 makes to become cold-producing medium W, the i.e. liquid of only liquid phase is begun through, point of arrival F from an E.Then, begin through evaporimeter 15 from a F and the cold-producing medium W of liquid is evaporated and form the state of saturated vapor, arrive the some A on saturation curve.
Like this, owing to can pass through to flow into the inflow pipe 23 in road 16, the gas phase W1 of cold-producing medium W is imported, even if therefore when using single-stage radial compressor, also energy-saving appliance 14 can be arranged from the inflow entrance 22 of shell 17 being formed at centrifugal compressor 10 to the primary flow path FC of impeller 18.That is, the isobaric variable quantity of the some D a to E from Fig. 4 can be added to kind of refrigeration cycle.
Here, as indicated with broken lines in fig. 4, when suppose do not arrange energy-saving appliance 14, do not deposit in the diagram from a D to the line segment of an E.That is, put F and become the position being positioned at a F1.Therefore, it is possible to confirm that a F1 is positioned at than the position of a F by high enthalpy side, compare with the distance R1 of some F1 with an A, the distance R of some A and some F is larger.
This 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, and on the other hand, the kind of refrigeration cycle shown in solid line is single stage compress compound expansion circulation.
Like this, by arranging energy-saving appliance 14, single stage compress compound expansion circulation can will be formed as from the single stage compress single-stage expansion circulation of cold-producing medium W separation gas phase W1.Consequently, the enthalpy difference of the cold-producing medium W before and after by evaporimeter 15 can be expanded.That is, R > R1, can realize the raising of refrigerating capacity.
In addition, by utilizing energy-saving appliance 14 will be blown in centrifugal compressor 10 from the isolated gas phase W1 of cold-producing medium W, the temperature of the cold-producing medium W in centrifugal compressor 10 can be 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, is preferably formed in the position than the leading edge 21a of blade 21 and the pars intermedia forward edge 21a side of trailing edge 21b.Thereby, it is possible to make the stall region speedup that the leading edge 21a side around blade 21 produces.This improves the inhibition of surge, realize the expansion of the actuating range of centrifugal compressor 10.
Turborefrigerator 1A according to the present embodiment, by between the leading edge 21a and trailing edge 21b of blade 21, the inflow entrance 22 flowing into road 16 is preferably set in leading edge 21a side, the gas phase W1 from the cold-producing medium W of energy-saving appliance 14 can be made to flow into primary flow path FC, in single-stage radial compressor, also energy-saving appliance 14 can be set thus.Therefore, by centrifugal compressor 10 is set to single-stage, namely reduce progression, can cost be suppressed and improve refrigerating capacity, in addition, the raising of compression efficiency can also be realized, improve so performance can be realized.
It should be noted that, the first expansion valve 12, second expansion valve 13 also can be the capillary etc. be such as made up of metal capillary shape pipe.
In addition, in the present embodiment, describing impeller 18 is opening situation, but also can be the case type impeller 18A such as with guard ring 29.In this case, the inflow entrance 22 starting from the inflow road 16 of energy-saving appliance 14 is formed at the dividing plate 28 in the outside of guard ring 29 as shown in Figure 5.
Further, in this case, gas phase W1 is blown into the gap of guard ring 29 and dividing plate 28, is sucked from upstream side to the primary flow path FC of impeller 18A by seal 24.
Here, such as shown in Figure 6, when applying two-stage centrifugal compressor in centrifugal compressor 10, also can be arranged through the energy-saving appliance 14 that present embodiment illustrates, the gas phase W1 of the cold-producing medium W from energy-saving appliance 14 is directed into the shell 17 of centrifugal compressor 10 towards the primary flow path FC of impeller 18.
Specifically, three expansion valves 25,26,27 are connected in series, two energy-saving appliances 14 are set between each expansion valve.Further, start from the inflow pipe 23 of the energy-saving appliance 14 of a side and be connected with the inflow entrance 22 of the impeller 18 of a side, start from the inflow pipe 23 of the energy-saving appliance 14 of the opposing party and be connected with the inflow entrance 22 of the impeller 18 of the opposing party.
Like this, not necessarily impeller 18 to each other namely inter-stage connect the inflow pipe 23 starting from energy-saving appliance 14, even if therefore when centrifugal compressor 10 is two-stage centrifugal compressor, two energy-saving appliances 14 also can be set.That is, the setting of energy-saving appliance 14 can not be carried out by progression restriction ground, can cost be suppressed and improve refrigerating capacity, performance can be realized and improve.
In addition, as shown in Figure 7, when centrifugal compressor 10 is formed as two-stage centrifugal compressor, also can be, start from the inflow pipe 23 of the energy-saving appliance 14 of a side to be connected with the inflow entrance 22 of the impeller 18 of a side, the inflow pipe 23 starting from the energy-saving appliance 14 of the opposing party is connected with impeller 18 inter-stage to each other.
Further, as shown in Figure 8, when centrifugal compressor 10 is formed as single-stage radial compressor, the energy-saving appliance 14 and two expansion valves that were illustrated by present embodiment is not limited to.Such as, two energy-saving appliances 14 and three expansion valves 25,26,27 also can be set, the inflow entrance 22 of the inflow pipe 23 with an impeller 18 that start from two energy-saving appliances 14 is connected, import the gas phase W1 from the cold-producing medium W of energy-saving appliance 14 to primary flow path FC.
In addition, when being provided with two energy-saving appliance 14, as shown in Figure 9, relative to an impeller 18, between the leading edge 21a and trailing edge 21b of blade 21, two or more inflow entrance 22 is formed discretely.Further, the inflow entrance 22 of a side can be connected with the energy-saving appliance 14 of a side, the inflow entrance 22 of the opposing party is connected with the energy-saving appliance 14 of the opposing party.
In addition, also more than more than three energy-saving appliances 14 and four expansion valve can be set relative to an impeller 18.That is, as long as be more than the quantity of energy-saving appliance 14 one by the quantity set of expansion valve, then the magnitude setting of energy-saving appliance 14 does not limit by the progression of centrifugal compressor 10.Therefore, it is possible to not by the magnitude setting of the progression restriction ground selection energy-saving appliance 14 of centrifugal compressor 10, the further raising of the refrigerating capacity based on energy-saving appliance 14 can be realized, can improve performance further.Further, also such structure can be applied to two-stage centrifugal compressor, multistage centrifugal compressor.
Next, the turborefrigerator 1B of the second embodiment of the present invention is described.
It should be noted that, identical Reference numeral is marked and detailed to the structural element identical with the first embodiment.
In the present embodiment, in centrifugal compressor 30, different from the inflow road 16 of the first embodiment towards the inflow road 36 of impeller 18 from energy-saving appliance 14.
As shown in Figure 10, flow into road 36 and comprise the inflow entrance 42 be formed on the shell 17 of centrifugal compressor 30 and the inflow pipe 43 connecting inflow entrance 42 and energy-saving appliance 14.The forming position of inflow entrance 42 is located between the leading edge 21a of blade 21 and trailing edge 21b identically with the first embodiment, is preferably located at the pars intermedia forward edge 21a side of leading edge 21a than blade 21 and trailing edge 21b.
In addition, as shown in figure 11, each road 36 that flows into, at the front place of the opening of inflow entrance 42, inner peripheral surface 42a has the water conservancy diversion leaf 44 extended on the whole at the height of inflow entrance 42.This water conservancy diversion leaf 44 is arranged abreast 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 cold-producing medium W in the meridian plane of impeller 18.Specifically, as shown in Figure 10, in order to make gas phase W1 flow into along the circulating direction of cold-producing medium W, the opening portion of inflow entrance 42 is formed as the circulating direction along cold-producing medium W.In this case, inflow entrance 42 both can have been made to turn to smoothly in the front of opening portion (with reference to Figure 10), also can turn in the midway of inflow pipe 43.
In such turborefrigerator 1B, the gas phase W1 from the cold-producing medium W of energy-saving appliance 14 is blown into the primary flow path FC in impeller 18 by flowing into road 36.So, in the cold-producing medium W circulated in primary flow path FC, mix the gas phase W1 of the cold-producing medium W from energy-saving appliance 14.Now, the gas phase W1 from the cold-producing medium W of energy-saving appliance 14 flows into along the circulating direction of the cold-producing medium W in the primary flow path FC in the meridian plane of impeller 18.In addition, by water conservancy diversion leaf 44, described gas phase W1 also flows into along the circulating direction of the cold-producing medium W in primary flow path FC in the circumferential.Therefore, the smoothness of the flowing of the cold-producing medium W in primary flow path FC can not be hindered, the losses by mixture to the cold-producing medium W in primary flow path FC can be reduced.
Turborefrigerator 1B according to the present embodiment, identical with the first embodiment, by reducing the progression of centrifugal compressor 30, can cost be suppressed and realize performance to improve.
On this basis, losses by mixture when flowing in primary flow path FC owing to can utilize formation direction and the water conservancy diversion leaf 44 of the inflow entrance 42 the flowing into road 36 gas phase W1 reduced from the cold-producing medium W of energy-saving appliance 14, therefore, it is possible to realize the performance raising of impeller 18 further.
It should be noted that, if the formation direction of inflow entrance 42 is towards the circulating direction of cold-producing medium W, then also water conservancy diversion leaf 44 can not be set.In addition, if arrange water conservancy diversion leaf 44, then the formation direction of inflow entrance 42 also can not towards the circulating direction of cold-producing medium W.
Next, the turborefrigerator 1C of the 3rd embodiment of the present invention is described.
It should be noted that, identical Reference numeral is marked and detailed to the structural element identical with the first embodiment and the second embodiment.
In the present embodiment, in centrifugal compressor 50, different from the inflow road 16 of the first embodiment and the inflow road 36 of the second embodiment towards the inflow road 56 of impeller 18 from energy-saving appliance 14.
As shown in figure 12, flow into road 56 and comprise the inflow entrance 62 be formed on the shell 17 of centrifugal compressor 50 and the inflow pipe 63 connecting inflow entrance 62 and energy-saving appliance 14.The forming position of inflow entrance 62 is located between the leading edge 21a of blade 21 and trailing edge 21b identically with the first embodiment and the second embodiment, is preferably located at the position than the leading edge 21a of blade 21 and the pars intermedia forward edge 21a side of trailing edge 21b.
In addition, the open side of the end of blade 21 side that flow into road 56, that become inflow entrance 62 is expanding.That is, flow into road 56 to have at the wide diameter portion 64 becoming concavity from opening towards the inside of shell 17 to the half-way of inflow entrance under circumference is observed with the dimensioned recesses larger than inflow entrance 62.
In such turborefrigerator 1C, the gas phase W1 from the cold-producing medium W of energy-saving appliance 14 is blown into the primary flow path FC in impeller 18 by flowing into road 56, mixes the gas phase W1 from the cold-producing medium W of energy-saving appliance 14 to the cold-producing medium W circulated in primary flow path FC.Now, have wide diameter portion 64, thus the sectional area of inflow entrance 62 increases owing to flowing into road 56 in open side, the gas phase W1 from the cold-producing medium W of energy-saving appliance 14 flows into the state reducing flow velocity.Therefore, the smoothness of the flowing of the cold-producing medium W in primary flow path FC can not be hindered, the losses by mixture to the cold-producing medium W in primary flow path FC can be reduced.
Turborefrigerator 1C according to the present embodiment, identical with the first embodiment and the second embodiment, by reducing the progression of centrifugal compressor 50, can cost be suppressed and realize performance to improve.
On this basis, due to can by flowing into the wide diameter portion 64 on the road 56 gas phase W1 that reduce from the cold-producing medium W of energy-saving appliance 14 and flowing in primary flow path FC time losses by mixture, so the performance that can realize impeller 18 further improves.
(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 by the inner peripheral surface 62a of inflow entrance 62 along with the Surface forming expanding gradually towards opening.In this case, the sectional area of inflow entrance 62 can not sharply increase, and inner peripheral surface 62a is expanding smoothly.Thereby, it is possible to suppress the situations such as the gas phase W1 stripping of the cold-producing medium W blown out from inflow entrance 62, and gas phase W1 can be flowed into more swimmingly to primary flow path FC with the state reducing flow velocity.
(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 trailing edge side of impeller 18 along with the Surface forming expanding gradually towards inflow entrance 22.In this case, the gas phase W1 of the cold-producing medium W blown out from inflow entrance 62 can be flowed into primary flow path FC with the state reducing flow velocity swimmingly.In addition, gas phase W1 can be blown out along the circulating direction of the cold-producing medium W circulated in primary flow path FC from inflow entrance 62.
Above, describe embodiments of the present invention in detail, but in the scope not departing from technical conceive of the present invention, also can carry out some design alterations.
Such as, also the water conservancy diversion leaf 44 of the second embodiment can be applied to the inflow road 16,56 of the first embodiment and the 3rd embodiment.
Industrial utilizability
According to described turborefrigerator, flowing into road by arranging between adjacent interlobate frontier and rear, the setting of gas-liquid separator can be carried out when the progression restriction of magnitude setting not by centrifugal compressor.Therefore, decrease the progression of centrifugal compressor, can cost be suppressed and improve refrigerating capacity, performance can be realized and improve.
Description of reference numerals
1A ... turborefrigerator
5 ... rotating shaft
10 ... centrifugal compressor
11 ... condenser
12 ... first expansion valve (pressure reducer)
13 ... second expansion valve (pressure reducer)
14 ... energy-saving appliance (gas-liquid separator)
15 ... evaporimeter
16 ... flow into road
17 ... shell
18 ... impeller
18A ... impeller
20 ... dish
21 ... blade
21a ... leading edge
21b ... trailing edge
22 ... inflow entrance
23 ... inflow pipe
24 ... seal
25,26,27 ... expansion valve
28 ... dividing plate
29 ... guard ring
W ... cold-producing medium
W1 ... gas phase
P ... axis
FC ... primary flow path
1B ... turborefrigerator
30 ... centrifugal compressor
36 ... flow into road
42 ... inflow entrance
42a ... inner peripheral surface
43 ... inflow pipe
44 ... water conservancy diversion leaf
1C ... turborefrigerator
50 ... centrifugal compressor
56 ... flow into road
62 ... inflow entrance
62a ... inner peripheral surface
63 ... inflow pipe
64 ... wide diameter portion
Claims (5)
1. a turborefrigerator, wherein, possesses:
Centrifugal compressor, it carrys out compressed refrigerant by the rotation of the impeller with multiple blade;
Condenser, it cools the described cold-producing medium after compression;
Multiple pressure reducer, the described cold-producing medium decompression from described condenser is formed gas-liquid two-phase by it, and connects with the number of tandem more than the progression of described centrifugal compressor;
Evaporimeter, it makes the described cold-producing medium evaporation after by described multiple pressure reducer;
Gas-liquid separator, it is respectively configured with one each other at described pressure reducer, and described cold-producing medium is separated into gas-liquid two-phase; And
Flow into road, it makes to flow between adjacent described interlobate frontier and rear from the isolated gas phase of described cold-producing medium among at least one in described gas-liquid separator.
2. turborefrigerator according to claim 1, wherein,
Described inflow road makes described gas phase flow into the pars intermedia of the frontier and rear than described blade by the position of front edge side.
3. turborefrigerator according to claim 1 and 2, wherein,
Described inflow road makes described gas phase flow into along the circulating direction of the described cold-producing medium in the meridian plane of described impeller.
4. turborefrigerator according to any one of claim 1 to 3, wherein,
Described inflow road has the water conservancy diversion leaf arranged abreast with described blade on the inner peripheral surface on this inflow road.
5. turborefrigerator according to any one of claim 1 to 4, wherein,
The end of the described blade-side on described inflow road is along with expanding towards downstream.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710430104.XA CN107255371B (en) | 2013-06-24 | 2013-06-24 | Turbo refrigerator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/JP2013/067201 WO2014207796A1 (en) | 2013-06-24 | 2013-06-24 | Turbo refrigerator |
Related Child Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710430104.XA Division CN107255371B (en) | 2013-06-24 | 2013-06-24 | Turbo refrigerator |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105247298A true CN105247298A (en) | 2016-01-13 |
| CN105247298B CN105247298B (en) | 2017-06-23 |
Family
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Family Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710430104.XA Active CN107255371B (en) | 2013-06-24 | 2013-06-24 | Turbo refrigerator |
| CN201380076771.2A Active CN105247298B (en) | 2013-06-24 | 2013-06-24 | Turborefrigerator |
Family Applications Before (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710430104.XA Active CN107255371B (en) | 2013-06-24 | 2013-06-24 | Turbo refrigerator |
Country Status (3)
| Country | Link |
|---|---|
| US (1) | US20160123639A1 (en) |
| CN (2) | CN107255371B (en) |
| WO (1) | WO2014207796A1 (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107131556A (en) * | 2017-02-07 | 2017-09-05 | 陈春材 | Air conditioner |
| CN111550944A (en) * | 2020-04-26 | 2020-08-18 | 珠海格力电器股份有限公司 | Triple throttling enthalpy-increasing double-condensation refrigerating system, air conditioner and control method |
| CN111852783A (en) * | 2020-07-13 | 2020-10-30 | 西安交通大学 | Two-phase flow device and method for wind power heating |
| CN112146308A (en) * | 2020-09-05 | 2020-12-29 | 万江新能源集团有限公司 | Device for improving efficiency of centrifugal heat pump unit |
| CN113530855A (en) * | 2020-04-21 | 2021-10-22 | Lg电子株式会社 | Compressor and cooling device comprising same |
| WO2022099748A1 (en) * | 2020-11-10 | 2022-05-19 | 艾默生环境优化技术(苏州)有限公司 | Heat pump system |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6152176B2 (en) * | 2016-01-13 | 2017-06-21 | 三菱重工業株式会社 | Turbo refrigerator |
| EP3997343B1 (en) | 2019-07-01 | 2023-08-09 | Carrier Corporation | Surge protection for a multistage compressor |
| WO2022225743A1 (en) * | 2021-04-21 | 2022-10-27 | Danfoss A/S | Refrigerant compressor with impeller having slotted shroud |
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- 2013-06-24 CN CN201710430104.XA patent/CN107255371B/en active Active
- 2013-06-24 CN CN201380076771.2A patent/CN105247298B/en active Active
- 2013-06-24 US US14/893,405 patent/US20160123639A1/en not_active Abandoned
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| US3226940A (en) * | 1963-12-12 | 1966-01-04 | Worthington Corp | Single stage centrifugal compressor refrigeration system |
| JPH04121555A (en) * | 1990-09-11 | 1992-04-22 | Daikin Ind Ltd | Turbine type refrigeration machine |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107131556A (en) * | 2017-02-07 | 2017-09-05 | 陈春材 | Air conditioner |
| CN107131556B (en) * | 2017-02-07 | 2019-07-05 | 陈春材 | Air conditioner |
| CN113530855A (en) * | 2020-04-21 | 2021-10-22 | Lg电子株式会社 | Compressor and cooling device comprising same |
| CN111550944A (en) * | 2020-04-26 | 2020-08-18 | 珠海格力电器股份有限公司 | Triple throttling enthalpy-increasing double-condensation refrigerating system, air conditioner and control method |
| CN111550944B (en) * | 2020-04-26 | 2024-03-29 | 珠海格力电器股份有限公司 | Triple throttling enthalpy-increasing double-condensation refrigerating system, air conditioner and control method |
| CN111852783A (en) * | 2020-07-13 | 2020-10-30 | 西安交通大学 | Two-phase flow device and method for wind power heating |
| CN112146308A (en) * | 2020-09-05 | 2020-12-29 | 万江新能源集团有限公司 | Device for improving efficiency of centrifugal heat pump unit |
| WO2022099748A1 (en) * | 2020-11-10 | 2022-05-19 | 艾默生环境优化技术(苏州)有限公司 | Heat pump system |
Also Published As
| Publication number | Publication date |
|---|---|
| CN107255371B (en) | 2020-04-24 |
| CN105247298B (en) | 2017-06-23 |
| WO2014207796A1 (en) | 2014-12-31 |
| US20160123639A1 (en) | 2016-05-05 |
| CN107255371A (en) | 2017-10-17 |
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Effective date of registration: 20170802 Address after: Tokyo, Japan, Japan Patentee after: MITSUBISHI heavy industry refrigeration air conditioning system Co Ltd Address before: Tokyo, Japan Patentee before: Mit-subishi Heavy Industries Ltd. |