CN109715955A - Centrifugal compressor - Google Patents
Centrifugal compressor Download PDFInfo
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- CN109715955A CN109715955A CN201780056596.9A CN201780056596A CN109715955A CN 109715955 A CN109715955 A CN 109715955A CN 201780056596 A CN201780056596 A CN 201780056596A CN 109715955 A CN109715955 A CN 109715955A
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- impeller
- magnetic bearing
- motor
- centrifugal compressor
- axis
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- 230000006835 compression Effects 0.000 claims abstract description 31
- 238000007906 compression Methods 0.000 claims abstract description 31
- 230000007246 mechanism Effects 0.000 claims abstract description 30
- 239000003507 refrigerant Substances 0.000 claims description 33
- 206010000060 Abdominal distension Diseases 0.000 claims 1
- 208000024330 bloating Diseases 0.000 claims 1
- 239000007788 liquid Substances 0.000 description 8
- 239000007789 gas Substances 0.000 description 7
- 230000006870 function Effects 0.000 description 6
- 230000008859 change Effects 0.000 description 5
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 5
- 230000007423 decrease Effects 0.000 description 4
- 238000000034 method Methods 0.000 description 4
- 230000008901 benefit Effects 0.000 description 3
- 238000005057 refrigeration Methods 0.000 description 3
- 235000013290 Sagittaria latifolia Nutrition 0.000 description 2
- 230000005540 biological transmission Effects 0.000 description 2
- 235000015246 common arrowhead Nutrition 0.000 description 2
- 238000010276 construction Methods 0.000 description 2
- 238000001816 cooling Methods 0.000 description 2
- 238000001514 detection method Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 239000000047 product Substances 0.000 description 2
- 239000006227 byproduct Substances 0.000 description 1
- 238000005119 centrifugation Methods 0.000 description 1
- 239000003795 chemical substances by application Substances 0.000 description 1
- 239000000498 cooling water Substances 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 238000009792 diffusion process Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 230000002706 hydrostatic effect Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
- 238000010025 steaming Methods 0.000 description 1
- 239000002918 waste heat Substances 0.000 description 1
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
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
- F04D17/08—Centrifugal pumps
- F04D17/10—Centrifugal pumps for compressing or evacuating
- F04D17/12—Multi-stage pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D23/00—Other rotary non-positive-displacement pumps
- F04D23/001—Pumps adapted for conveying materials or for handling specific elastic fluids
- F04D23/003—Pumps adapted for conveying materials or for handling specific elastic fluids of radial-flow type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D25/00—Pumping installations or systems
- F04D25/02—Units comprising pumps and their driving means
- F04D25/06—Units comprising pumps and their driving means the pump being electrically driven
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D25/00—Pumping installations or systems
- F04D25/16—Combinations of two or more pumps ; Producing two or more separate gas flows
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
- F04D27/004—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids by varying driving speed
-
- 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
- F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
- F04D29/051—Axial thrust balancing
-
- 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
- F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
- F04D29/056—Bearings
- F04D29/058—Bearings magnetic; electromagnetic
-
- 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
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/284—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for compressors
- F04D29/286—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for compressors multi-stage rotors
-
- 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
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/44—Fluid-guiding means, e.g. diffusers
- F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
- F04D29/444—Bladed diffusers
Abstract
A kind of centrifugal compressor (22), including shell (30), the first compression mechanism (23a) and the second compression mechanism (23b).Shell (30) has first entrance portion (31a), first outlet part (33a), second entrance portion (31b) and second outlet part (33b).First compression mechanism (23a) includes: first entrance guide vane (32a), is configured at first entrance portion (31a)；First impeller (34a), is configured at the downstream of first entrance guide vane (32a)；First diffuser (36a) is configured at the first outlet part (33a) in the downstream the first impeller (34a)；And first motor (38a).Second compression mechanism (23b) includes: second entrance guide vane (32b), is configured at second entrance portion (31b)；Second impeller (34b), is configured at the downstream of second entrance guide vane (32b)；Second diffuser (36b) is configured at the second outlet part (33b) in the downstream the second impeller (34b)；And second motor (38b).First and second motors (38a, 38b) are arranged to rotate the first and second axis (42a, 42b), so that the first and second impellers (34a, 34b) be made to rotate.
Description
Background technique
Technical field
Present invention relates in general to a kind of centrifugal compressors.More particularly it relates to a kind of with pairs of pressure
The centrifugal compressor of contracting machine and pairs of motor.
Background technique
Chiller system is the refrigerating machine or device that heat is removed from medium.Usually using the liquid of such as water etc
As medium, and chiller system operates in Vapor Compression Refrigeration Cycle.The liquid can then be carried out by heat exchanger
Circulation, to be cooled down as needed to air or equipment.As necessary byproduct, refrigeration can generate waste heat, it is necessary to by it
It is discharged into environment, or in order to obtain higher efficiency, is recycled with purpose for heating.Conventional chiller system
Usually using centrifugal compressor, which is commonly known as turbo-compressor.Thus, this chiller system can be by
Referred to as cooling turbine unit.Alternatively, other types of compressor, such as helical-lobe compressor can be used.
In conventional (turbine) cooler, refrigerant is compressed in centrifugal compressor and is sent to heat exchanger,
In above-mentioned heat exchanger, heat exchange occurs between refrigerant and heat exchange medium (liquid).This heat exchanger is referred to as cold
Condenser, because refrigerant condenses in the heat exchanger.As a result, heat is passed to medium (liquid) with heat medium.
The refrigerant for leaving condenser is expanded by expansion valve, and is sent to another heat exchanger, in the heat exchanger, is being freezed
Heat exchange occurs between agent and heat exchange medium (liquid).The heat exchanger is referred to as evaporator, because refrigerant is handed in the heat
(evaporation) is heated in parallel operation.As a result, heat is transmitted to refrigerant from medium (liquid), to keep liquid cooling.From steaming
The refrigerant of hair device then returns to centrifugal compressor, and repeats the circulation.Liquid used is usually water.
Conventional centrifugal compressor consist essentially of shell, inlet guide vane, impeller, diffuser, motor, various sensors with
And controller.Refrigerant flows successively through inlet guide vane, impeller and diffuser.Thus, inlet guide vane is connected to centrifugal compressor
Air inlet port, and diffuser is connected to the air outlet of impeller.Flow of the inlet guide vane to the refrigerant gas for entering impeller
It is controlled.The speed of impeller increase refrigerant gas.The speed for the refrigerant gas that diffuser is used to be provided by impeller is (dynamic
State pressure) it is converted into (static state) pressure.Motor rotates impeller.Controller controls motor, inlet guide vane and expansion valve
System.In this way, refrigerant is compressed in conventional centrifugal compressor.Conventional centrifugal compressor can have level-one or double
Grade.Motor drives one or more impellers.
As the example of routine techniques, referring to U.S. Patent No. 7,942,628 and U.S. Patent Application Publication the 2010/th
No. 0251750.
Summary of the invention
Cooler industry starts to provide variable speed compressor during generation nineteen ninety to improve efficiency.
Cooler industry also developed twin-stage type centrifugal compressor, to obtain higher chiller efficiency.
In the case where two stage centrifugal compressor arrangement, two impellers are driven using a motor.Have been found that the knot
Structure has a problem in that (1) operating range；(2) efficiency.
About (1) operating range, it has been found that there are relationships between the operating range and revolving speed of each impeller.Due to existing
Technology only allows each impeller to rotate with speed identical with another impeller, it has been found that when attempting outside the range
When operating any impeller, compressor will be difficult to and/or can not operate.
About (2) efficiency, it has been found that, once any impeller does not operate on the point of design, then the efficiency of compressor
It will decline.
About (1) operating range, it has been found that, by rotating each impeller with different revolving speed, impeller possibly can not be
(that is, can maintain in their operating range) is operated except their operating range.
About (2) efficiency, it has been found that, the revolving speed of first order impeller and second level impeller is adjusted to improve their effect
Therefore rate can improve compressor whole efficiency.
The operating range of operating for the prior art, each compressor will be determined by the operating range of impeller.Due to every
Grade can have the boundary Limit (the chokes limit, stall and surge limit, the minimum unloading limit) of its own, therefore, Two-stage Compression
Machine can have more limited operating range ability.Thus, when impeller operates outside this range, compressor can not or not
It should operate.
Operating for the prior art, if any impeller does not operate on its design point, compressor efficiency will decline.
The reason is that due to the variation of head coefficient and discharge coefficient.Once these values change, compressor just can not be in its design
It is operated on (peak efficiency) point.
Further, it has been found that when far from design point operating, twin-stage is relative to list if two grades are not well matched with
The cycle efficieny advantage of pole can reduce or weaken, and when to separate design point and mobile peak efficiencies point, will lead to more serious
Efficiency reduces.It has been found that this can lead to the duration of runs that cooler spends significant proportion when far from " fully loaded design point ".
Therefore, it is an object of the present invention to provide a kind of centrifugal compresseds that can be maintained operating in operating range
Machine.
It is another object of the present invention to provide the centrifugal compressors that one kind can improve efficiency.
Yet another object of the invention is that providing a kind of centrifugal compressor, solution is described above or those skilled in the art
One or more of the other the problem of having found known to member.
One or more above-mentioned purposes can include substantially shell, the first compression mechanism and the second pressure by providing a kind of
The centrifugal compressor of contracting mechanism is realized.Shell has first entrance portion, first outlet part, second entrance portion and second outlet
Portion.First compression mechanism includes: first entrance guide vane, is configured at first entrance portion；First impeller, is configured at first entrance
The downstream of guide vane；First diffuser is configured at the first outlet part in the first impeller downstream；And first motor.First impeller
Being attached to can be around the first axle that first rotation rotates.First motor arrangement is at first axle is rotated, to make the first impeller
Rotation.Second compression mechanism includes: second entrance guide vane, is configured at second entrance portion；Second impeller is configured at second and enters
The downstream of mouth guide vane；Second diffuser is configured at the second outlet part in the second impeller downstream；And second motor.Second leaf
Wheel is attached to the second axis that can be rotated around the second rotation axis.Second motor arrangement is at the second axis is rotated, to make the second leaf
Wheel rotation.
From the detailed description for disclosing preferred embodiment below in conjunction with attached drawing, those skilled in the art can know more about this hair
Bright above and other purpose, feature, aspect and advantage.
Detailed description of the invention
Referring now to attached drawing, these attached drawings form the original disclosed a part:
Fig. 1 is to show the twin-stage chiller system with centrifugal compressor according to an embodiment of the present invention (to have section
Hot device) schematic diagram；
Fig. 2 is the perspective view of the centrifugal compressor of chiller system shown in FIG. 1, wherein, will be above-mentioned in order to be illustrated
A part of centrifugal compressor is cut off and is shown with section；
Fig. 3 is the internal part (for example, axis, impeller, magnetic bearing and motor) of centrifugal compressor shown in FIG. 1 to FIG. 2
Perspective view；
Fig. 4 is the main view of the internal part (for example, axis, impeller, magnetic bearing and motor) of centrifugal compressor shown in Fig. 3
Figure；
Fig. 5 is Fig. 3~centrifugal compressor shown in Fig. 4 internal part (for example, axis, impeller, magnetic bearing and motor)
Illustrate partial, longitudinal cross-sectional, schematically illustrates the additional components such as sensor, replacement bearing and coil in more detail；
Fig. 6 is the flow chart for showing the normal control of centrifugal compressor shown in FIG. 1 to FIG. 5；
Fig. 7 A is the chart for showing the operating range (integrating compressor operating) of double-stage compressor, wherein A is indicated entire
Overall operation point except operating range；
Fig. 7 B is the chart for showing the operating range of first order impeller of double-stage compressor shown in Fig. 7 A, wherein A1 table
Show the first order operation point except first order operating range；
Fig. 7 C is the chart for showing the operating range of second level impeller of double-stage compressor shown in Fig. 7 A, wherein A2 table
Show the second level operation point except the operating range of the second level；
Fig. 8 A is the chart for showing the operating range (integrating compressor operating) of double-stage compressor, wherein A is indicated entire
Overall operation point (similar to Fig. 7 A) except operating range, and B indicates inclined in entire operating range according to the present invention
Movement turning point；
Fig. 8 B is the chart for showing the operating range of first order impeller of double-stage compressor shown in Fig. 8 A, wherein A1 table
Show the first order operation point (similar to Fig. 7 B) except first order operating range, and B1 indicates according to the present invention by reducing
The revolving speed of first order impeller and the first operation point to shift；
Fig. 8 C is the chart for showing the operating range of second level impeller of double-stage compressor shown in Fig. 7 A, wherein A2 table
Show the second level operation point (similar to Fig. 7 C) in the operating range of the second level；
Fig. 9 A is the chart for showing the efficiency (reduced overall engine efficiency) of double-stage compressor, wherein E indicates that design is most efficient
Rate point, and D and E indicates the lower efficiency operation point deviated；
Fig. 9 B is the chart for showing the efficiency of first order impeller of double-stage compressor shown in Fig. 9 A, wherein E1 indicates the
The design best efficiency point of level-one, and what D1 and E1 indicated the first order has occurred the lower efficiency operation point deviated；
Fig. 9 C is the chart for showing the efficiency of second level impeller of double-stage compressor shown in Fig. 9 A, wherein E2 indicates the
The design best efficiency point of second level, and what D2 and E2 indicated the second level has occurred the lower efficiency operation point deviated；
Figure 10 A is the chart for showing the efficiency (reduced overall engine efficiency) of double-stage compressor similar with Fig. 9 A, wherein E
Indicate design best efficiency point, and D and E indicates the lower efficiency operation point deviated；
Figure 10 B is the chart for showing the efficiency of first order impeller of double-stage compressor shown in Fig. 9 A, wherein E1 indicates the
The design best efficiency point of level-one, and what D1 and F1 indicated the first order has occurred the lower efficiency operation point deviated, wherein arrow
Head respectively indicates how to improve efficiency by reducing or improving the first impeller speed from point D1 or F1；
Figure 10 C is the chart for showing the efficiency of second level impeller of double-stage compressor shown in Fig. 9 A, wherein E2 indicates the
The design best efficiency point of second level, and what D2 and F2 indicated the second level has occurred the lower efficiency operation point deviated, wherein arrow
Head respectively indicates how to improve efficiency by reducing or improving the second impeller speed from point D2 or F2.
Specific embodiment
Now with reference to the selected embodiment of Detailed description of the invention.Those skilled in the art will be clear that according to the disclosure,
Being described below for embodiment be merely provided for illustrating, and be not intended to limitation by appended claims and its equivalent Lai
The present invention of restriction.
With reference first to Fig. 1, the chiller system 10 of the centrifugal compressor 22 including an embodiment of the present invention is shown.Figure
1 centrifugal compressor 22 is double-stage compressor, thus, the chiller system 10 of Fig. 1 is twin-stage chiller system.The twin-stage of Fig. 1
Chiller system further includes economizer.Fig. 1 illustrates only the chiller system that centrifugal compressor 22 according to the present invention can be used
An example.For example, those skilled in the art will be clear that according to the disclosure, chiller system 10 also can remove
Economizer.However, in the illustrated embodiment, there are economizers due to following discussion the reason of.
Other than centrifugal compressor 22 and the mode controlled centrifugal compressor 22, chiller system 10 is conventional
Chiller system.Specifically, in the illustrated embodiment, structure of the centrifugal compressor 22 including following more detailed description is simultaneously
It is controlled to be operated and maintain in its operating range to improve efficiency.Therefore, unless with centrifugal compressor 22 and to centrifugation
Except the mode that compressor 22 is controlled is related, will no longer chiller system 10 be discussed in detail and/or be illustrated herein.
However, it will be clear that, the conventional components of chiller system 10 can be configured to respectively to those skilled in the art
Kind mode, without departing from the scope of the present invention.In the illustrated embodiment, chiller system 10 preferably makes in a conventional manner
With the water cooler of cooling water and cooler water.
Now referring now still to Fig. 1, the component of chiller system 10 is briefly described.Chiller system 10 consists essentially of string
Connection be joined together to form the cooler controller 20 of loop refrigeration cycle, centrifugal compressor 22, condenser 24, expansion valve or
Aperture 25, economizer 26, expansion valve or aperture 27 and evaporator 28.Economizer 26 is connected to the first pressure in refrigerant circuit
Between contracting mechanism and the second compression mechanism (for example, being connected to intergrade).Various sensor (not shown) are configured at cooler system
The entire circuit of system 10.These sensors and chiller system 10 is controlled using the information from these sensors is conventional
, thus, unless except related with the control of centrifugal compressor 22 according to the present invention, will not be described in further detail herein and/or
Diagram.Therefore, those skilled in the art will be clear that according to the disclosure, for simplicity, in addition to centrifugal compressed
Except the structure of machine 22 is related to operating, the normal operation of chiller system 10 will be omitted.
Referring now to Fig. 1-Fig. 5, compressor 22 will be described in more detail.In the embodiment shown, compressor 22
It is two stage centrifugal compressor.Thus, compressor 22 shown in this article includes two impellers.However, compressor 22 may include three
Above impeller (not shown).Other than compressor 22 includes for driving the independent motor of two impellers, shown implementation
The two stage centrifugal compressor 22 of mode is conventional two stage centrifugal compressor.In addition, according to the present invention, motor is controlled.
Thus, centrifugal compressor 22 includes first and second grades that fluid is connected in series, so that being compressed in the first stage
Refrigerant then compressed in the second level.The first order includes first order inlet guide vane 32a, the first impeller 34a, the first diffusion
Device/spiral case 36a, first order compressor motor 38a and first order magnetic bearing 40a.Similarly, the second level includes that second level entrance is led
Leaf 32b, the second impeller 34b, the second diffuser/spiral case 36b, high stage compressor motor 38b and second level magnetic bearing 40b.Separately
Outside, centrifugal compressor 22 includes various conventional sensors (only showing).
While characterized as magnetic bearing, but those skilled in the art will be clear that according to the disclosure, the present invention
The bearing of compressor of other types and form can be used.Other components of the covering centrifugal compressor 22 of shell 30.Shell 30 includes
The inlet portion 31a and outlet portion 33a of the first order for compressor.Shell 30 further includes the entrance of the second level for compressor
Portion 31b and outlet portion 33b.Thus, shell 30 has first entrance portion 31a, first outlet part 33a, second entrance portion 31b and the
Two outlet portion 33b.
Thus, in the illustrated embodiment, centrifugal compressor 22 includes shell 30, the first compression mechanism (first order) 23a
With the second compression mechanism (second level) 23b.First compression mechanism 23a includes: first entrance guide vane 32a, and configuration enters first
In oral area 31a；First impeller 34a is configured in the downstream of first entrance guide vane 32a；First diffuser 36a, configuration is the
In the first outlet part 33a in one downstream impeller 34a；And the first motor 38a, it is configured to rotate first axle 42a, to make
First impeller 34a rotation.First impeller 34a is attached to can be around first rotation X1The first axle 42a of rotation.Second compressor
Structure 23b includes: second entrance guide vane 32b, is configured in second entrance portion 31b；Second impeller 34b, configuration enter second
The downstream of mouth guide vane 32b；Second diffuser 36b is configured in the second outlet part 33b in the second downstream impeller 34b；And the
Two motor 38b is configured to rotate the second axis 42b, so that the second impeller 34b be made to rotate.Second impeller 34b is attached to can be around
Second rotation axis X2Second axis 42b of rotation.
Cooler controller 20 from various sensors receive signal, and to inlet guide vane 32a, 32b, compressor motor 38a,
38b and magnetic axis bearing assembly 40a, 40b are controlled, and are illustrated in further detail below.Refrigerant flows successively through first order entrance and leads
Leaf 32a, first order impeller 34a, second level inlet guide vane 32b and second level impeller 34b.Inlet guide vane 32a, 32b respectively with
Usual manner controls the flow for the refrigerant gas for flowing into impeller 34a, 34b.Impeller 34a, 34b are not usually changing pressure
Increase the speed of refrigerant gas in the case where power.The increment of motor speed decision refrigerant gas speed.Diffuser/spiral case
36a, 36b increase refrigerant pressure.
Diffuser/spiral case 36a, 36b is immovably fixed relative to shell 30.Compressor motor 38a, 38b are passed through respectively
Impeller 34a, 34b are rotated by first axle 42a and the second axis 42b.As Fig. 1 is best it is found that the first diffuser 36a is connected to second
Impeller 34b, so that compressed refrigerant is further compressed in the second compression mechanism 23b in the first compression mechanism 23a.
First magnetic bearing 40a and the second magnetic bearing 40b can support axis 42a, 42b to magnetic rotation respectively.Alternatively, bearing arrangement
It may include roller element, hydrodynamic bearing, hydrostatic bearing and/or magnetic bearing or any combination of these bearings.With this
Kind mode, refrigerant compress in centrifugal compressor 22.
When chiller system 10 operates, first order impeller 34a and the second level impeller 34b rotation of compressor 22, and
Low pressure refrigerant in cooler 10 is sucked by first order impeller 34a.The flow of refrigerant is adjusted by inlet guide vane 32a
Section.It is compressed into middle pressure by the refrigerant that first order impeller 34a is sucked, refrigerant is increased by the first diffuser/spiral case 36a
Pressure, refrigerant are subsequently led to second level impeller 34b.The flow of refrigerant is adjusted by inlet guide vane 32b.Second
The refrigerant compression of middle pressure is increased refrigerant pressure at high pressure, and by the second diffuser/spiral case 36b by grade impeller 34b.With
Afterwards, high-pressure gas refrigerant is discharged to chiller system 10.In the illustrated embodiment, since impeller 34a, 34b are by independence
Motor 38a or 38b driving, therefore, the revolving speed of the first impeller 34a and the second impeller 34b are independent variables.
Now with reference to Fig. 2-Fig. 5, the first magnetic bearing 40a and the second magnetic bearing 40b are described in more detail.In addition to herein
Except illustrating, the first magnetic bearing 40a and the second magnetic bearing 40b are conventional magnetic bearings.Thus, in addition to it is related with the present invention it
Outside, the first magnetic bearing 40a and the second magnetic bearing 40b will not be discussed in detail and/or is illustrated herein.On the contrary, this field
Technical staff will be clear that, without deviating from the invention, can use any suitable magnetic bearing.First magnetic
Bearing 40a preferably includes the first impeller side radial direction magnetic bearing 44a, the first distal side radial direction magnetic bearing 46a and first axis (thrust)
Magnetic bearing 48a.Similarly, the second magnetic bearing 40b preferably includes the second impeller side radial direction magnetic bearing 44b, the second distal side radial direction magnetic
Axial (thrust) the magnetic bearing 48b of bearing 46b and second.
At least one radial direction magnetic bearing 44a or 46a revolvably supports first axle 42a, and at least one radial magnetic axis
It holds 44b or 46b and revolvably supports the second axis 42b.Thrust magnetic bearing 48a and acting on the first thrust disc 45a along
First rotation X1Axial bearing first axle 42a.Thrust magnetic bearing 48a includes the thrust disc 45a for being attached to first axle 42a.
Similarly, thrust magnetic bearing 48b is and acting on the second thrust disc 45b along the second rotation axis X2Axial bearing second
Axis 42b.Thrust magnetic bearing 48b includes the thrust disc 45b for being attached to the second axis 42b.
First thrust disc 45a is along perpendicular to first rotation X1Direction from first axle 42a radially, and phase
First axle 42a is fixed.Second thrust disc 45b is along perpendicular to the second rotation axis X2Direction from the second axis 42b radially
Extend, and is fixed relative to the second axis 42b.First axle 42a along first rotation X1Position (axial position) by
Axial position to the first thrust disc 45a controls.Similarly, the second axis 42b along the second rotation axis X2Position it is (axial
Position) it is controlled by the axial position of the second thrust disc 45b.First radial direction magnetic bearing 44a, 46a is configured in the first compressor horse
Up on the opposite axial end portion of 38a, and second radial direction magnetic bearing 44b, 46b configuration is in the opposite of the second compressor motor 38b
Axial end portion on.In the illustrated embodiment, first rotation X1With the second rotation axis X2It coincides with one another.In addition, institute
Show in embodiment, first rotation X1With the second rotation axis X2It is parallel.
Referring now still to Fig. 2-Fig. 5, various sensors in a usual manner to axis 42a, 42b relative to magnetic bearing 44a, 44b, 46a,
The radial position of 46b, 48a, 48b and axial position are detected, and send signal to cooler controller 20.Cooler control
The electric current for being sent to magnetic bearing 44a, 44b, 46a, 46b, 48a, 48b is controlled in a usual manner after device 20 processed, it will
Axis 42a, 42b maintain correct position.Thus, magnetic axis bearing assembly 40a is preferably the combination of active magnetic bearings 44a, 46a, 48a,
Magnetic axis bearing assembly 40a monitors shaft position, and the letter that will indicate shaft position using gap sensor 54a, 56a, 58a (Fig. 5)
Number it is sent to cooler controller 20.Thus, each magnetic bearing 44a, 46a, 48a are preferably active magnetic bearings.Similarly, magnetic axis
Bearing assembly 40b is preferably the combination of active magnetic bearings 44b, 46b, 48b, magnetic axis bearing assembly 40b using gap sensor 54b,
56b, 58b (Fig. 5) send cooler controller 20 for the signal for indicating shaft position to monitor shaft position.Thus, each magnetic
Bearing 44b, 46b, 48b are preferably active magnetic bearings.
Therefore, centrifugal compressor 22 includes: the first magnetic bearing 40a, revolvably supports first axle 42a；And second
Magnetic bearing 40b revolvably supports the second axis 42b.First axle 42a includes first entrance end, is equipped with the first leaf thereon
Take turns 34a；And first distal portion, what the first motor 38a was mounted on first axle 42a is located at the first impeller 34a and the first distal portion
Between position at, and the second axis 42b includes second entrance end, is equipped with the second impeller 34b thereon；And second distal end
Portion, the second motor 38b are mounted at the position between the second impeller 34b and the second distal portion of the second axis 42b.
As described above, the first magnetic bearing 40a and the second magnetic bearing 40b include the group of radial direction magnetic bearing and axial magnetic bearing
It closes.Specifically, magnetic bearing 44a is the first impeller side radial direction being configured axially between the first impeller 34a and the first motor 38
Magnetic bearing, and magnetic bearing 44b is the second impeller side radial direction magnetic being configured axially between the second impeller 34b and the second motor 38b
Bearing.Magnetic bearing 46a is the first distal side radial direction magnetic bearing, and axial arrangement is equipped with the first leaf the first motor 38a, separate
The side of 34a is taken turns, and magnetic bearing 46b is the second distal side radial direction magnetic bearing, is configured axially in the second motor 38b, separate peace
Side equipped with the second impeller 34b.Under any circumstance, the first magnetic bearing 40a includes at least one first radial direction magnetic bearing 44a
Or 44b and at least one first axis thrust magnetic bearing 48a, the second magnetic bearing 40b include at least one second radial magnetic axis
Hold 44b or 46b and at least one second axial thrust magnetic bearing 48b.
In the illustrated embodiment, first axis thrust magnetic bearing 48a axial arrangement is attached in the first distal side transverse bearing 46a
Closely, and the second axial thrust magnetic bearing 48b axial arrangement near the second distal side transverse bearing 46b.Thus, first axis thrust
Magnetic bearing 48a is configured axially the first remote end part in first axle 42a, and the second axial thrust magnetic bearing 48b axial arrangement is the
The second remote end part of two axis 42b.In addition, (axis 42a's) the first distal portion and first axis thrust magnetic bearing 48a are axial each other
It is spaced apart, to form gap between them, (axis 42b's) the second distal portion and the second axial thrust magnetic bearing 48b are each other
It is axially spaced, to form gap between them.
Gap sensor 54a, 54b, 56a, 56b, 58a, 58b are only schematically illustrated in Fig. 5.Similarly, as only in Fig. 5
Shown in, it is provided with replacement bearing (unnumbered) in the illustrated embodiment, is located at each end of each axis 42a, 42b
Place.Those skilled in the art will be clear that according to the disclosure, can remove replacement bearing (unnumbered).Similarly, ability
Field technique personnel will be clear that according to the disclosure, can remove one or more gap sensor, to simplify magnetic bearing
40a,40b.In addition, those skilled in the art will be clear that according to the disclosure, and if showing gap sensor, magnetic bearing
It can passively be controlled by cooler controller 20.
Now with reference to Fig. 1-Fig. 5, motor 38a, 38b according to the present invention are described in more detail.First motor 38a packet
Include the first stator 60a and the first rotor 62a.Similarly, the second motor 38b includes the second stator 60b and the second rotor 62b.It is fixed
Sub- 60a is fixed to the inner surface of shell 30, and rotor 62a is fixed to axis 42a.Similarly, stator 60b is fixed to the interior of shell 30
Surface, and rotor 62b is fixed to axis 42b.Stator 60a, 60b and rotor 62a, 62b are conventional.Thus, when power Transmission arrives
When stator 60a, rotate rotor 62a with speed corresponding with the electric power of supply.In addition, making when power Transmission is to stator 60b
Rotor 62b is rotated with speed corresponding with the electric power of supply.Since rotor is fixed to axis, also rotate axis, thus also make
Impeller 34a, 34b rotation.
As noted previously, as two independent motor 38a, 38b of setting are so that the first impeller 34a and the second impeller 34b rotation
Turn, therefore, the first impeller 34a and the second impeller 34b can be rotated independently at different rates.More specifically, motor
38a, 38b preferably receive electric power from independent variable frequency drives (VFD) 64a, 64b respectively.Variable frequency drives (VFD) 64a, 64b
Control signal is received from cooler controller 20, separately to control the revolving speed of the first impeller 34a and the second impeller 34b.
Illustrate to control variable frequency drives (VFD) hereinafter with reference to chart shown in control flow chart shown in fig. 6 and Fig. 7 A- Figure 10 C
The mode of 64a, 64b.
It will be referring to Fig. 6, to motor 38a, 38b of the revolving speed for independently controlling the first impeller 34a and the second impeller 34b
Independent control be described in more detail.As described above, the revolving speed of the first motor 38a and the second motor 38b are can independent control
's.Specifically, controller 20 is programmed to independently control the first motor 38a and the second motor 38b according to the flow chart of Fig. 6
Revolving speed.This cycles through following triggering and starts and repeat shown in Fig. 6: (1) compressor discharge pressure variation is more than
10%/minute；And/or the variation of (2) compressor suction pressure is more than 10%/minute.However, if client changes the setting of cooler
(i.e. remnants/releasing water temperature is set), this also can be the triggering of Fig. 6.First variable frequency drives (VFD) 64a is connected to first
Motor 38a and controller 20, to be changeably controlled the revolving speed of the first motor 38a according to Fig. 6, and the second variable frequency drives (VFD)
64b is connected to the second motor 38b and controller 20, the revolving speed of the second motor 38b to be changeably controlled according to Fig. 6.
Beginning/repetition point of Fig. 6 is in step S1, and end/repetition point is in step S14.Step S2-S4 is worked as calculating
Whether preceding efficiency simultaneously judges the first order compression mechanism 23a the step of most high-efficiency point (see, for example, Fig. 9 B) is operated.If in step
It is judged as that first order compression mechanism 23a is operated in most high-efficiency point in S4, then controller 20 proceeds to step S5.If it has not, then controlling
Device 20 processed proceeds to step S8.In step S8-S10, controller 20 adjusts inlet guide vane 32a and the first VFD speed, to improve
The efficiency of first compression mechanism 23a (see, for example, Figure 10 B).If being judged as first order compression mechanism 23a at this in step slo
It is operated after a little changes in most high-efficiency point, then controller 20 proceeds to step S5.If it has not, then controller 20 returns to * A, with
Repeat above-mentioned judgement and control.
When controller 20 has proceeded to step S5, for high stage compressor structure, patrol identical with above-mentioned paragraph is repeated
Volume.Step S5-S7 be for calculate current efficiency and judge high stage compressor structure 23b whether most high-efficiency point (see, for example,
Fig. 9 C) operating the step of.If being judged as in the step s 7, high stage compressor structure 23b is operated in most high-efficiency point, controller 20
Proceed to step S14.If it has not, then controller 20 proceeds to step S11.In step S11-S13, controller 20 adjusts entrance
Guide vane 32b and the 2nd VFD speed, to improve the efficiency of the second compression mechanism 23b (see, for example, Figure 10 C).If in step s 13
It is judged as that high stage compressor structure 23b is operated in most high-efficiency point after these changes, then controller 20 proceeds to step S14.
If it has not, then controller 20 returns to * B, to repeat above-mentioned judgement and control.
Other than control shown in fig. 6, the revolving speed of also controllable VFD 64a, 64b, by the first compression mechanism 23a and
Second compression mechanism 23b is maintained in its operating range.However, this will not illustrate in flow charts, because in addition to " efficiency " quilt
Except " operating range " replaces, the logic of Fig. 6 can be used.Such control can also be understood according to Fig. 7 A- Fig. 8 C,
This will be described below.
The more details of centrifugal compressor operating according to the present invention are now discussed.In the illustrated embodiment, two grades
It is independent, so that each grade (each impeller) is operated by independent speed control.By the way that each leaf is changed independently
The operating range of the speed of wheel, each impeller can maintain in the boundary Limit that earlier paragraphs are previously mentioned.In addition, working as the speed of impeller
When spending independent variable as disclosed herein, economizer flow can be changed under the operating condition of wide scope.In addition, by
It can be operated by independent speed control in each grade (each impeller), therefore, by the way that the speed of each impeller is changed independently,
Boundary Limit can be adjusted, preferably to match each grade and to increase the operating range of double-stage compressor, is especially being examined
When considering the economizer flow changed under the operating condition of wide scope, independent speed control to be better balanced each grade it
Between quality stream and work input.
The most stringent of operating boundary Limit of any level becomes the limit of double-stage compressor, and therefore, impeller matching is (compatible
The selection of impeller) for it can construct product may become extremely important, this can construct product can be sold to have it is many not
With many different clients of operating condition, bad matching leads to useless operating range, and (it works at or near design point
It is very good, but far from cannot operate well at design point, or can operate but efficiency and cost are relative to single-stage design
It is nocompetitive), even the matched optimal cases of impeller, also improved fortune can be shown by this new theory of application
Turn range, under the operating condition of wide scope, enters the effluent of the entrance of the second level for finding " best " from economizer steam
Design gives huge design challenge, because second level Impeller Mass rheologyization is very big.
There are relationships between the operating range and revolving speed of each impeller.Since the prior art (has a motor and two
The common double-stage compressor of impeller) rotate each impeller with identical speed, therefore, when any impeller outside this range
When operating, compressor will be unable to operate.In addition, utilizing the prior art (the common twin-stage pressure with a motor and two impellers
Contracting machine), once any impeller is not operated in design point, the efficiency of compressor will decline.
The technology of illustrated embodiment can improve the operating range and efficiency of compressor, because new construction makes each compression
Machine rotates at different rates.Specifically, impeller will not be in operating model by rotating each impeller with different revolving speeds
It is operated except enclosing.Moreover, by the efficiency of first order impeller and second level wheel speed is adjusted, to improve its efficiency, this
Reduced overall engine efficiency will be improved.
Fig. 7 A is the chart for showing the operating range (integrating compressor operating) of double-stage compressor, wherein A is indicated entire
Overall operation point except operating range.Fig. 7 B is the chart for showing the operating range of first order impeller, wherein A1 is indicated the
First order operation point except level-one operating range.Fig. 7 C is the chart for showing the operating range of second level impeller, wherein A2 table
Show the second level operation point except the operating range of the second level.
Operating (the common double-stage compressor with a motor and two impellers) for the prior art, each compressor
Operating range determined by the operating range of impeller.Therefore, when impeller operates outside this range, compressor can not be operated.
As shown in Fig. 7 A- Fig. 7 C, second level impeller can operate (Fig. 7 C) at A2, but first order impeller can not operate (figure at A1
7B).As a result, compressor will not operate (Fig. 7 A) at A.
Fig. 8 A is the chart for showing the operating range (integrating compressor operating) of double-stage compressor, wherein A is indicated entire
Overall operation point (similar to Fig. 7 A) except operating range, and B indicates inclined in entire operating range according to the present invention
Movement turning point.In the fig. 8b, A1 indicates the first order operation point (similar to Fig. 7 B) except first order operating range, and B1 is indicated
The first operation point that revolving speed by reducing first order impeller according to the present invention shifts.Fig. 8 C is similar to Fig. 7 C,
In, A2 indicates the second level operation point in the operating range of the second level.
By rotating each impeller at different rates, two impellers can operate in the range.Such as Fig. 8 B institute
Show, by reducing revolving speed, the operation point of first order impeller will move on to B1 from A1.As a result, the operation point of entire compressor will
B is moved on to from the A in Fig. 8 A.The operation point of second level impeller will not change, because it is operated in range.
Fig. 9 A is the chart for showing the efficiency (reduced overall engine efficiency) of double-stage compressor, wherein E indicates that design is most efficient
Rate point, and D and E indicates the lower efficiency operation point deviated.In figures 9 b and 9, E1 indicates that the design of the first order is most efficient
Rate point, and what D1 and E1 indicated the first order has occurred the lower efficiency operation point deviated.Similarly, in Fig. 9 C, E2 is indicated
The design best efficiency point of the second level, and what D2 and E2 indicated the second level has occurred the lower efficiency operation point deviated.
Operating (the common double-stage compressor with a motor and two impellers) for the prior art, if any impeller
It is not operated in design point, then compressor efficiency will decline.The reason is that due to the variation of head coefficient and discharge coefficient.Once
These values change, and compressor can not just be put in design (peak efficiency) and operate.See Fig. 9 A- Fig. 9 C.
Figure 10 A is the chart for showing the efficiency (reduced overall engine efficiency) of double-stage compressor similar with Fig. 9 A, wherein E
Indicate design best efficiency point, and D and E indicates the lower efficiency operation point deviated.In fig. 1 ob, E1 indicates the
The design best efficiency point of level-one, and what D1 and F1 indicated the first order has occurred the lower efficiency operation point deviated.Arrow point
Do not indicate how to improve efficiency and the first impeller speed is decreased or increased from point D1 or F1.Other than the second level, Figure 10 C
It is identical as Figure 10 B.
By rotating each impeller at different rates, each impeller can operate at design point.Work as flow
When coefficient low (such as D1 or D2 point), impeller speed will be reduced to obtain higher efficiency.On the other hand, when discharge coefficient is high
(such as F1 and F2 point) will increase impeller speed to obtain higher efficiency.Reduced overall engine efficiency will be close to peak efficiency.Revolving speed
Variation be also required to the variation of the position IGV.This is because discharge coefficient and head coefficient is caused to occur due to rotation speed change
Variation.Specifically, IGV should be closed to reduce inlet flow rate if the RPM of impeller increases.On the other hand, if the RPM of impeller
Reduce, then IGV should be opened to increase inlet flow rate.
- Fig. 6 referring to Fig.1, cooler controller 20 may include being programmed to control the multiple of conventional components in a usual manner
Control unit.For example, conventional magnetic bearings control portion, conventional compressor variable frequency driver, conventional compressor motor control unit,
The expansion valve control unit of conventional inlet guide vane control unit and routine.These parts can be part alone or in combination.
In the illustrated embodiment, as described herein and shown, control unit is the part of cooler controller 20, is compiled
Journey is the control executed according to Fig. 6 to the component of cooler 10.However, those skilled in the art will be clear that according to the disclosure
As long as one or more controllers are programmed to execute the control of the component to chiller system 10 described herein,
Control unit, the exact magnitude of component and/or cooler controller 20, position and/or structure can be without departing from feelings of the invention
It is changed under condition.
As disclosed herein, cooler controller 20 is conventional controller, thus including at least one micro- place
Manage device or CPU, input/output (I/O) interface, random access memory (RAM), read-only memory (ROM) and storage equipment
(temporarily or permanently), these components form computer-readable medium, which is programmed to execute one or more
A control program is to control chiller system 10.Cooler controller 20 can optionally include: such as keypad etc it is defeated
Incoming interface, above-mentioned input interface receive input from the user；And display equipment, above-mentioned display equipment are used for various parameters
It is shown to user.Other than herein described, above-mentioned component and program be it is conventional, thus, unless understanding embodiment institute
It needs, otherwise will not be discussed in further detail herein.
The general explanation of term
When understanding the scope of the present invention, term as used herein " comprising " and its derivative are intended to indicate that open art
Language, specifies the presence of the feature, element, part, group, entirety and/or step of statement, but is not excluded for other spies not stated
The presence of sign, element, part, group, entirety and/or step.Above content is also applied for such as term " packet with similar meaning
Include ", the term of " having " and its derivative etc.Moreover, when used in a singular form, term " component ", " portion ", " portion
Point ", " component " or " element " can have the double meaning of single component or multiple components.
Be used herein for describing include by the operation of the execution such as part, portion and equipment or the term " detection " of function
Part, portion and the equipment etc. for not needing physical detection further include determining, measuring, model, predict or calculate etc., to execute fortune
Capable or function.
Term " construction " used herein for describing the part of equipment, portion or component includes constituting and/or programming
For the hardware and/or software for executing desired function.
It is used herein such as " generally ", the degree term of " about " and " substantially " refer to improved term
Legitimate skew amount, and final result will not significantly change.
Although only having selected selected embodiment with the present invention will be described, those skilled in the art are come
It says, it should be understood that herein, can not depart from the scope of the present invention that appended claim limits from the disclosure
It makes various changes and modifications.For example, the size of various parts, shape, position or orientation can be come as needed and/or desired
It is changed.The part shown with being directly connected to or be in contact with each other can have the intermediate structure of configuration between them.One
The function of element can be executed by two elements, and vice versa.The structure and function of one embodiment can be at another
It is used in embodiment.All advantages do not need to occur simultaneously in certain embodiments.It is each unique special in the prior art
Sign is independent or combines with other feature, it should also be considered as separate description of further inventions by applicant, including by this
The structure and/or concept of function that a little features are embodied.Thus, the foregoing description of embodiment according to the present invention is only provided use
In explanation, it is no intended to limitation present invention as defined by appended claim and their equivalent.
Claims (16)
1. a kind of centrifugal compressor, which is characterized in that including shell, the first compression mechanism and the second compression mechanism, wherein
The shell has first entrance portion, first outlet part, second entrance portion and second outlet part,
First compression mechanism includes
First entrance guide vane, the first entrance guide vane are configured at the first entrance portion；
First impeller, first impeller are configured at the downstream of the first entrance guide vane, and first impeller is attached to can be around
The first axle of first rotation rotation；
First diffuser, first diffuser are configured at the first outlet part in first impeller downstream；And
First motor, first motor arrangement is at rotating the first axle, so that first impeller is rotated,
Second compression mechanism includes
Second entrance guide vane, the second entrance guide vane are configured at the second entrance portion；
Second impeller, second impeller are configured at the downstream of the second entrance guide vane, and second impeller is attached to can be around
Second axis of the second rotation axis rotation；
Second diffuser, second diffuser are configured at the second outlet part in second impeller downstream；And
Second motor, second motor arrangement is at second axis is rotated, so that second impeller be made to rotate.
2. centrifugal compressor as described in claim 1, which is characterized in that
The revolving speed of the revolving speed of first motor and second motor can independently control.
3. centrifugal compressor as claimed in claim 2, which is characterized in that further include:
Controller, the controller are programmed to independently control turn of the revolving speed of first motor and second motor
Speed.
4. centrifugal compressor as claimed in claim 3, which is characterized in that further include:
First variable frequency drives (VFD), first variable frequency drives (VFD) are connected to first motor and the control
Device, the revolving speed of first motor is changeably controlled；And
Second variable frequency drives (VFD), second variable frequency drives (VFD) are connected to second motor and the control
Device, the revolving speed of second motor is changeably controlled.
5. centrifugal compressor according to any one of claims 1 to 4, which is characterized in that further include:
First magnetic bearing, first magnetic bearing revolvably support the first axle；And
Second magnetic bearing, second magnetic bearing revolvably support second axis.
6. centrifugal compressor as claimed in claim 5, which is characterized in that
The first rotation coincides with one another with second rotation axis.
7. such as centrifugal compressor described in claim 5 or 6, which is characterized in that
The first axle includes first entrance end, and first impeller is equipped on the first entrance end；And first
Distal portion, first motor are mounted on the position between first impeller and first distal portion of the first axle
Place is set,
Second axis includes second entrance end, and second impeller is equipped on the second entrance end；And second
Distal portion, second motor are mounted on the position between second impeller and second distal portion of second axis
Place is set,
First magnetic bearing includes the first impeller side radial direction magnetic bearing, and the first impeller side radial direction magnetic bearing axial arrangement exists
Between first impeller and first motor,
Second magnetic bearing includes the second impeller side radial direction magnetic bearing, and the second impeller side radial direction magnetic bearing axial arrangement exists
Between second impeller and second motor.
8. centrifugal compressor as claimed in claim 7, which is characterized in that
First magnetic bearing includes the first distal side radial direction magnetic bearing, and first distal side radial direction magnetic bearing is configured axially described
First motor, the separate side for being equipped with first impeller,
Second magnetic bearing includes the second distal side radial direction magnetic bearing, and second distal side radial direction magnetic bearing is configured axially described
Second motor, the separate side for being equipped with second impeller.
9. the centrifugal compressor as described in any one of claim 5 to 8, which is characterized in that
First magnetic bearing includes first axis thrust magnetic bearing,
Second magnetic bearing includes the second axial thrust magnetic bearing.
10. centrifugal compressor as claimed in claim 9, which is characterized in that
The first axis thrust magnetic bearing axial configuration is equipped with the one of first impeller first motor, separate
Side,
The second axial thrust magnetic bearing axial configuration is equipped with the one of second impeller second motor, separate
Side.
11. such as centrifugal compressor described in claim 5 or 6, which is characterized in that
The first axle includes first entrance end, and first impeller is equipped on the first entrance end；And first
Distal portion, first motor are mounted on the position between first impeller and first distal portion of the first axle
Place is set,
Second axis includes second entrance end, and second impeller is equipped on the second entrance end；And second
Distal portion, second motor are mounted on the position between second impeller and second distal portion of second axis
Place is set,
First magnetic bearing includes the first distal side radial direction magnetic bearing, and first distal side radial direction magnetic bearing is configured axially described
First motor, the separate side for being equipped with first impeller,
Second magnetic bearing includes the second distal side radial direction magnetic bearing, and second distal side radial direction magnetic bearing is configured axially described
Second motor, the separate side for being equipped with second impeller.
12. such as centrifugal compressor described in claim 5 or 6, which is characterized in that
First magnetic bearing includes at least one described first radial direction magnetic bearing and at least one described first axis thrust magnetic
Bearing,
Second magnetic bearing includes at least one described second radial direction magnetic bearing and at least one described second axial thrust magnetic
Bearing.
13. centrifugal compressor as claimed in claim 12, which is characterized in that
The first axis thrust magnetic bearing axial is configured in first remote end part,
The second axial thrust magnetic bearing axial is configured in second remote end part,
First distal portion and the first axis thrust magnetic bearing are separated from each other to form gap, and described the in centre
Two distal portions and the second axial thrust magnetic bearing are separated from each other to form gap in centre.
14. the centrifugal compressor as described in any one of claims 1 to 13, which is characterized in that
First diffuser is connected to second impeller, so that compressed refrigerant exists in first compression mechanism
It is further compressed in second compression mechanism.
15. a kind of chiller system, including centrifugal compressor described in any one of claims 1 to 14, the cooler system
System further include:
Evaporator；
Condenser；And
Bloating plant,
The compressor, the evaporator, the condenser and the expansion mechanism are joined together to form refrigerant circuit.
16. chiller system as claimed in claim 15, which is characterized in that further include:
Economizer, the economizer are connected to first compression mechanism and second compressor in the refrigerant circuit
Between structure.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US15/266,403 US20180073779A1 (en) | 2016-09-15 | 2016-09-15 | Centrifugal compressor |
| US15/266,403 | 2016-09-15 | ||
| PCT/US2017/051455 WO2018053067A1 (en) | 2016-09-15 | 2017-09-14 | Centrifugal compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN109715955A true CN109715955A (en) | 2019-05-03 |
Family
ID=59969245
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201780056596.9A Pending CN109715955A (en) | 2016-09-15 | 2017-09-14 | Centrifugal compressor |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US20180073779A1 (en) |
| EP (1) | EP3513078A1 (en) |
| JP (1) | JP2019529777A (en) |
| CN (1) | CN109715955A (en) |
| WO (1) | WO2018053067A1 (en) |
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| CN113757136A (en) * | 2021-09-09 | 2021-12-07 | 鑫磊压缩机股份有限公司 | Heat dissipation system of magnetic suspension multistage compressor |
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| EP3587826B1 (en) * | 2018-06-28 | 2022-11-02 | Danfoss A/S | Variable stage compressors |
| US11603853B2 (en) * | 2018-09-14 | 2023-03-14 | Carrier Corporation | Compressor configured to control pressure against magnetic motor thrust bearings |
| US11946678B2 (en) * | 2022-01-27 | 2024-04-02 | Copeland Lp | System and method for extending the operating range of a dynamic compressor |
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2016
- 2016-09-15 US US15/266,403 patent/US20180073779A1/en not_active Abandoned
-
2017
- 2017-09-14 JP JP2019514826A patent/JP2019529777A/en not_active Withdrawn
- 2017-09-14 WO PCT/US2017/051455 patent/WO2018053067A1/en unknown
- 2017-09-14 EP EP17772817.7A patent/EP3513078A1/en not_active Withdrawn
- 2017-09-14 CN CN201780056596.9A patent/CN109715955A/en active Pending
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113757136A (en) * | 2021-09-09 | 2021-12-07 | 鑫磊压缩机股份有限公司 | Heat dissipation system of magnetic suspension multistage compressor |
| CN113757136B (en) * | 2021-09-09 | 2023-08-08 | 鑫磊压缩机股份有限公司 | Heat radiation system of magnetic suspension multistage compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2019529777A (en) | 2019-10-17 |
| WO2018053067A1 (en) | 2018-03-22 |
| EP3513078A1 (en) | 2019-07-24 |
| US20180073779A1 (en) | 2018-03-15 |
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Application publication date: 20190503 |