CN103748425B - hybrid compressor system and method - Google Patents
hybrid compressor system and method Download PDFInfo
- Publication number
- CN103748425B CN103748425B CN201280026803.3A CN201280026803A CN103748425B CN 103748425 B CN103748425 B CN 103748425B CN 201280026803 A CN201280026803 A CN 201280026803A CN 103748425 B CN103748425 B CN 103748425B
- Authority
- CN
- China
- Prior art keywords
- compressor
- positive displacement
- mode
- centrifugal compressor
- displacement compressor
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
Classifications
-
- 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
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
- F25B41/24—Arrangement of shut-off valves for disconnecting a part of the refrigerant cycle, e.g. an outdoor part
-
- 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
-
- 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
-
- 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
- F25B31/00—Compressor arrangements
-
- 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
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
Abstract
A kind of equipment (20), it has：Centrifugal compressor (24), positive displacement compressor (26), First Heat Exchanger (32), and the second heat exchanger (36).Multiple valves (70,72,74) are positioned, to provide with the operation of at least both of which：In the first mode, refrigerant is compressed in positive displacement compressor and centrifugal compressor at least partly in parallel.In a second mode, refrigerant is compressed in positive displacement compressor, and centrifugal compressor is offline.In the 3rd pattern, refrigerant is compressed in the positive displacement compressor and centrifugal compressor of at least part series connection.
Description
The cross reference of related application
This application claims entitled " the Hybrid Compressor System and submitted on May 31st, 2011
Methods " U.S. Patent application No.61/491,515 rights and interests, the disclosure of the patent application is by quoting by whole
It is incorporated herein, just as elaborating herein.
Background technology
This disclosure relates to freeze.More specifically, this disclosure relates to chiller system.
Large-size water-cooling freezer unit (for example, 300~1500 tons of capacity (1055~5275W)) usually because the reason for cost and
Use single centrifugal compressor.However, this compressor is subject to surge (surge) (particularly in fractional load).
A kind of method for solving the problem is to provide multiple centrifugal compressors of parallel connection.This allow single compressor from
Line, to make compressor capacity preferably match the load of needs.
The content of the invention
One aspect of the present invention is related to a kind of equipment, and the equipment includes：Centrifugal compressor, positive displacement compressor,
First Heat Exchanger and the second heat exchanger.Multiple valves are positioned, to provide the operation of at least two patterns.In the first mode,
Refrigerant is compressed in positive displacement compressor and centrifugal compressor at least partly in parallel.In a second mode, refrigerant
Compressed in positive displacement compressor, and centrifugal compressor is in offline.In the 3rd pattern, refrigerant is at least partly
Compressed in the positive displacement compressor and centrifugal compressor of series connection.
In various embodiments, positive displacement compressor can be screw compressor.
The other side of the present invention is related to such at least two pattern to run.
One or more embodiments of the detail are set forth in accompanying drawing and following explanation.Other features, objects and advantages from
Specification and drawings and it will become obvious from claims.
Brief description of the drawings
Fig. 1 is the schematic diagram of chiller system.
Fig. 2 is the vertical schematic diagram in longitudinal direction of the condenser in Fig. 1 system.
Fig. 3 is the vertical schematic diagram in longitudinal direction of the cooler in Fig. 1 system.
Fig. 4 is chart of the temperature relative to the capacity of percentage into the water of condenser.
Fig. 5 is the control flow chart of the system for Fig. 1.
In various figures, same reference and instruction represent same element.
Embodiment
Except by surge problems, centrifugal compressor usual specific volume formula compressor when providing high-head is more poorly efficient.
This causes centrifugal compressor when being run for recuperation of heat by as poor alternative.As discussed below, hybrid system
It is characterized by centrifugal compressor and positive displacement compressor.Exemplary positive displacement compressor is carried by variable frequency drive
For two rotors or triple-spool screw compressor of power.The positive displacement compressor of replacement includes reciprocating compressor and vortex pressure
Contracting machine.
Fig. 1 shows steam compression system 20, and it has compressor subsystem 22.Compressor subsystem 22 includes the first pressure
Contracting machine 24 (centrifugal) and the second compressor 26 (positive displacement).In the exemplary embodiment, two compressors all have capacity
Controlling feature, it can be any of type (for example, for the variable inlet guide card of centrifugal compressor and for spiral
The guiding valve of compressor (screw compressor is used as positive displacement compressor), and the speed change driver for two kinds of compressors).
In the first operational mode, compressor subsystem drives along refrigerant flowpath 30 toward downstream direction 500 and made
Cryogen.Flow path 30 passes sequentially through First Heat Exchanger 32, the heat exchanger 36 of expansion gear 34 and second.In the first mode,
First Heat Exchanger 32 is heat rejection heat exchanger, and the second heat exchanger 36 is heat absorbing heat exchanger.
Example system 20 is chiller system, and wherein First Heat Exchanger 32 is the cold condenser or gas cooler of liquid,
And the second heat exchanger 36 is cooler.Exemplary expansion device 34 is electric expansion valve (EV), and it can pass through freezer unit
Controller 40 (for example, computer or microcontroller) is controlled.The expansion gear 34 of replacement is the float-controlled valve in condenser 32
(or float valve).Exemplary First Heat Exchanger has at least one entrance 50 and at least one outlet along refrigerant flowpath 30
52.Similarly, the second heat exchanger 36 has at least one entrance 54 and at least one outlet 56 along refrigerant flowpath.Pressure
Contracting machine 24 has ingress port 60 and outlet port 62.Similarly, the second compressor 26 has ingress port 64 and outlet port
66。
As discussed below, compressor subsystem includes being coupled to one or more valves of these compressors, to permit
Perhaps switching of these compressors between the compact model of two or more.Example system includes three valves 70,72 and 74.
In the first operational mode, these compressors are at least partly run in parallel.What is illustrated at one is complete
In the case of parallel connection, the respective inhalation port of these compressors and discharge port are under substantially the same situation.In order to carry
For this parallel running, exemplary flowpath has two branch roads 80 and 82 in parallel, and branch road 80 and 82 is in the second heat exchanger
The downstream of outlet 56 abutment 84 at diverge to, and at the entrance 50 positioned at First Heat Exchanger or at the position 86 of its upstream
Reconsolidate.In the case of part in parallel, separating and/or rejoin can be in different position.
Bypass branch or circuit 90 extend between branch road 80 and 82.Exemplary bypass branch 90 is upper compressor
Swim over to extension between another downstream.In the exemplary embodiment, the branch road prolongs from the position 92 in the first compressor downstream
Reach the position 94 of the second upstream of compressor.For the flowing in controlling brancher 80 and 82, exemplary valve 70 and 74 edge respectively
These branch roads.In the exemplary embodiment, valve 70 be in the downstream of the first end 92 of bypass line 90, and valve 74 be
The upstream at end 94.
In the operation in parallel of exemplary at least part, valve 72 is closed, and valve 74 and 70 is opened.In a second mode,
Only the second compressor 26 is run.Valve 70 and 72 is all closed, and valve 74 is opened.3rd pattern is series model, and wherein these are pressed
Contracting machine is run in series.In exemplary tandem pattern, valve 70 and 74 is closed, and valve 72 is opened.Refrigerant is changed into first
Before the entrance 50 of hot device, compressed from the outlet 56 of the second heat exchanger by the first compressor, valve 72 and second with not shunting
Machine.4th possible pattern includes only running the first compressor 24.In this mode, valve 72 and 74 is closed, and valve 70
Open.
Fig. 1 shows the other examples details of condenser 32 and cooler 36.It is cold that exemplary condenser 32 includes top
Condenser tube bank 120 and bottom aftercooler tube bank 122.Fig. 1 also show the liquid refrigerant accumulation 124 in condenser.Pipe
Beam 120 and 122 is connected to one or more heat transfer fluid sources, to remove heat from refrigerant.Aftercooler restrains 122 quilts
In chamber 126.Bottom of one or more ingates 128 along chamber 126.Float-controlled valve 130 is supplied to outlet 52.Pressure is passed
Sensor 132 can be located in the headroom of the close entrance 50 of condenser.
In the exemplary embodiment, heat-transfer fluid (such as water) is transmitted along water loop 138 (Fig. 2), is connect by entrance 140
Receive, and discharged from outlet 142.Corresponding temperature sensor 144 and 146 measures the inlet temperature T of water1CONDAnd outlet temperature
T2COND.Exemplary stream gauge 147 measures the flow F of water along water loop 138MCOND。
Cooler 36 also includes lower tube bundle 160 and upper bundle 162.Fig. 1 also show the refrigeration in the cooler
Agent accumulation 164.In the exemplary embodiment, heat-transfer fluid (such as water) is transmitted along water loop 168 (Fig. 3), passes through entrance 170
Receive, and discharged from outlet 172.Corresponding temperature sensor 174 and 176 measures the inlet temperature T of water1COOLAnd outlet temperature
T2COOL.Exemplary stream gauge 177 measures the flow F of water along water loop 168MCOOL.Fig. 1 also show in the bottom of cooler
The distributor 180 supplied approximately through entrance 54.Pressure sensor 182 is shown as being in the top close to outlet 56
In space.
Fig. 4 shows the temperature T into the water of condenser1CONDRelative to the chart of capacity.Line 200 represents U.S.'s refrigeration
The loaded line (or load line) of meeting (ARI).In the U.S., freezer unit will obey ARI standards 550.The standard recognizes four and refers to bar
Part, percentage and associated Water in Condenser that this four reference conditions pass through freezer unit rated load (being represented to cool down tonnage)
Entrance/entrance temperature characterize.The operation of progress will realize the outlet of chilled water/leave temperature for 44F (6.67C).Four
Condition is：100%, 85F (29.44C)；75%, 75F (23.89C), 50%, 65F (18.33C)；(it is also with 25%, 65F
18.33C).These conditions (or along the condition of similarity for connecting their curve) can provide the correlation for measurement efficiency
Condition.In API experiments, the flow by the water of cooler is that 2.4 gallons per minutes often cool down (0.043 liter of ton (gpm/ton)
(l/s/kW) per second every kilowatt, and the flow of the water of condenser is 3gpm/ton (0.054l/s/kW).
Using typical heat exchanger, it is that substantially 8F (4.4C) multiplies percent load to be risen by the temperature of the water of condenser,
Or 8F during 100% load, 6F (3.3C) during 75% load, 4F (2.2C) and 2F (1.1C) during 25% load during 50% load.
The low 1F of temperature (0.6C) or 2F (1.1C) (for example, 43F in ARI experiments) of chilled water of the cooler saturation temperature than leaving.
Similarly, the temperature and water temperature of water of the condenser saturation temperature than entering condenser rise sum high 1F or 2F.For 85F's
Into for the temperature of the water of condenser, temperature rise is 8F, therefore it is 93F to leave the temperature of the water of condenser, and condenser is full
It is 93+2=95F with temperature.
Line 202 represents 85F (29.44C) constant temperature.Tropical climate area, environment temperature from daytime to night almost without
Change.In such kind of area, the temperature of the water of condenser keeps constant.Industrial standard is that the temperature thought into the water of condenser exists
85F is constant between 25% and 100% load.Table 1 shows the temperature difference on ARI situations and corresponding tropical situation.It is Celsius
Temperature is converted from listed Fahrenheit temperature value, therefore does not increase and provide the precision of falseness.Other states in bracket
The analogously represented transformation result come from the original U.S. or Britain's value of the border system of unit (SI).
Table I
In the first exemplary implementation, at least partly first mode in parallel is used for top load situation, and second mode is (only
Positive displacement compressor) it is used for low load situation.For example, second mode can be used for be basically zero load to centre carry
Charge values.Between intermediate cycling load value and maximum load, at least partly pattern in parallel is used.It is noted, however, that when fortune
When row is near conversion condition, intermediate cycling load value can be subjected to suitable Delay control to avoid excessive circulation.For example, from zero
To conversion condition, the second compressor can be run with increased speed and/or power.In conversion, the first compressor can be with
It is directed to online with full capacity or close to full capacity, and the second compressor reset-to-zero or other low capacity values.Hereafter, with
Increased load, the speed and/or power of the second compressor can increase.Therefore, in pattern at least partly in parallel, system
Load/volume change adapted to mainly by positive displacement compressor.For example, at least positive displacement compressor can be than centrifugal
Compressor realizes more changes.More properly, positive displacement compressor can realize load change at least 75% or at least
90%.Exemplarily, load change can at least represent the 30% of the peak load of system, more properly, be at least 40%.
In the first simple illustrative embodiments, the rated capacity of two compressors is substantially the same (for example, identical
Or it is appropriate be differently sized, to solve any lag issues).Therefore, change point is at substantially half load.
It is wider broadly, change point can be between the 45% and 55% of total rating system load, or in 40% He
Between 60%.
Centrifugal compressor is used by (or wider broadly, not in low load) near the rated load only possessed at it or its
Machine, surge problems can be largely avoided by.
For example, the exemplary peaking capacity of positive displacement compressor is the 50 of the peaking capacity of centrifugal compressor
~200%, more properly, 100% to 150%.
In one deforms, the 4th (series connection) pattern can be added and use in high condenser water temperature, and for example water adds
Heat or heat recovery mode.
In an alternative variation, (for example, less than 25F (13.9C)), centrifugal compressor when needing the low-down temperature difference
It can be used alone.
In the second more complicated illustrative embodiments, by measuring or determining 302 condensers otherwise
Saturation temperature (TCOND) and cooler saturation temperature (TCOOL) start control process 300 (Fig. 5).TCONDAnd TCOOLCan be with
Determined separately by following, i.e.,：Pressure is measured by pressure sensor 132 and 182, saturation temperature is then calculated and (passes through
Look-up table or the function of programming).The temperature difference (lift) is calculated as TCONDSubtract TCOOL, 304.If the temperature difference is more than given threshold value
(for example, 50F (28C)), then the system can be with the 4th (series connection) mode operation, 306.In the series model, centrifugal pressure
The capacity of contracting machine is controlled by the orientation of compressor speed and entrance guide card.If the gas flow discharged from centrifugal compressor
Higher than the capacity of screw compressor, then the pressure between centrifugal compressor and screw compressor will be raised, and be caused centrifugal
The surge of compressor.Now, the speed of centrifugal compressor is incrementally increased and its guide card is gradually closed up, until centrifugation
The no longer surge of formula compressor.Similar logic is applied to screw compressor (that is, the First Speed followed by guiding valve).Slow down total
It is that result in reduced power consumption or increased efficiency.
For the less temperature difference, non-series operation can be performed.To flow FMCOOLAnd temperature T1COOLAnd T2COOLSurveyed
Amount, 308.Capacity can also be calculated, and 310.
Then, at low capacity (for example, first value less than for example the maximum amount of 50%), operation is changed based on pressure head
Enter.For low-head, these compressors can be run with equal loads and in the first pattern, and 320.This can include：When
When there is speed change driver, by speed come control capability；And for the situation of fixed speed, pass through centrifugal compressor
The guiding valve of entrance guide card and screw compressor carrys out control capability.Pressure head is proportional to temperature-difference.In this example, low-head correspondence
In the temperature-difference less than 35F (19C), high-head is then between 35F and 50F (19C and 28C).
For high-head, (only screw compressor) is run system in a second mode, and 322.When there is speed change driver
When, by speed come control capability；When fixed speed, then by guiding valve come control capability.
In the case of interim capacities (for example, 50~75%), it can also be run in the first pattern.In these pressures
Balance between contracting machine can be modified based on pressure head.For low-head, system is run with paralleling model, wherein spiral pressure
Contracting machine is run with fixed capacity, and centrifugal compressor is run with variable capacity, to provide the total capacity of needs.For example,
In the case of the centrifugal compressor and screw compressor with equal maximum capacity, screw compressor can be maximum with it
The 50% of capacity is run, and centrifugal compressor operate in its maximum capacity 50 and 100% between (thus carry out group
Close, exemplarily to provide 50~75% operation of maximum system capacity).Selection is such to be run, to avoid centrifugation
The surge of formula compressor.
In the case of high-head, system can be in substantially fixed capacity and spiral with wherein centrifugal compressor
Compressor provides the first mode of volume controlled to run, and 332.The exemplary set point of constant volume compressor can be relative to
Situation 330 and it is different.Centrifugal compressor can be run with higher capacity.In the examples described above, centrifugal compressor
Machine can be run with the 80% of its maximum capacity, thus provide the 40% of total power system capacity.Screw compressor can be run
Between the 20% of its maximum capacity and 70% (thus provide maximum system capacity 10~35%, and with centrifugal pressure
Contracting machine combination so as to provide maximum system capacity 50~75%).This running situation can be selected, because centrifugal pressure
Contracting machine low load and it is high-head in the case of be subjected to surge.
In the case of high power capacity (such as 75~100%), can also run in the first pattern, wherein these compressors with
Equal load operation, 340.Therefore, depending on required capacity, the maximum capacity that each compressor can possess at it
Run between 75% and 100%, to meet the capacity of needs.
One or more embodiments have been described.Nevertheless, but it is understood that, various modifications can be carried out.
For example, in the case where rebuilding existing system, the details of existing system or its predetermined use may influence any particular implementation
The details of mode.Therefore, in other embodiments are within the scope of the appended claims.
Claims (19)
1. a kind of both vapor compression equipment（20）, including：
Centrifugal compressor（24）；
Positive displacement compressor（26）, the centrifugal compressor（24）With the positive displacement compressor（26）It is special including volume controlled
Levy；
First Heat Exchanger（32）；
Second heat exchanger（36）；
Positioned at the First Heat Exchanger（32）Interior first pressure sensor（132）；
Positioned at second heat exchanger（36）Interior second pressure sensor（182）；With
Multiple valves（70,72,74）, the multiple valve（70,72,74）Be oriented to provide it is following at least two：
Run in the first pattern, wherein：
Refrigerant is in the positive displacement compressor at least partly in parallel（26）With the centrifugal compressor（24）It is middle to be compressed；
Run in a second mode, wherein：
Refrigerant is in the positive displacement compressor（26）It is middle to be compressed, and the centrifugal compressor（24）Offline；
Run in a third mode, wherein：
The positive displacement compressor of the refrigerant at least part series connection（26）With the centrifugal compressor（24）It is middle to be compressed；
With
Run with fourth mode, wherein：
Refrigerant is in the centrifugal compressor（24）It is middle to be compressed, and the positive displacement compressor（26）Offline.
2. equipment as claimed in claim 1, wherein：The positive displacement compressor is screw compressor.
3. equipment as claimed in claim 1, wherein：
The centrifugal compressor has peaking capacity；With
The positive displacement compressor has the specified maximum appearance of the 100 ~ 150% of the peaking capacity of the centrifugal compressor
Amount.
4. equipment as claimed in claim 1, wherein：The multiple valve is oriented to provide all four kinds of patterns.
5. equipment as claimed in claim 1, wherein：The multiple valve is oriented at least provide the first mode and described
Second mode.
6. equipment as claimed in claim 1, wherein：The equipment is freezer unit, and wherein：
The First Heat Exchanger is a part for condenser unit；
Second heat exchanger is a part for cooler；With
Expansion gear（34）It is positioned between the condenser and the cooler.
7. equipment as claimed in claim 1, wherein, the multiple valve includes：
First valve（70）, first valve（70）Between the centrifugal compressor and the First Heat Exchanger；
Second valve（72）, second valve（72）Along the position between the centrifugal compressor and first valve（92）
The position extended between second valve and the positive displacement compressor（94）Bypass（90）；With
3rd valve（74）, the 3rd valve（74）Between second heat exchanger and the positive displacement compressor.
8. equipment as claimed in claim 1, further comprises：
Controller（40）, the controller（40）It is programmed to automatically between at least two patterns switch.
9. equipment as claimed in claim 8, wherein：
The controller is programmed to automatically between the first mode and the second mode switch.
10. equipment as claimed in claim 9, wherein：
The controller is programmed, so that the reduction in response to load is switched to the second mode from the first mode, with
And from the second mode it is switched to the first mode in response to the increase of load.
11. equipment as claimed in claim 10, wherein：
The controller is programmed to be switched to the 3rd pattern in response to calculating the high demand for the temperature difference.
12. equipment as claimed in claim 1, wherein：Both the positive displacement compressor and the centrifugal compressor lead to
Speed change driver is crossed electrically to provide power.
13. a kind of both vapor compression equipment, including：
Centrifugal compressor（24）；
Positive displacement compressor（26）, the centrifugal compressor（24）With the positive displacement compressor（26）It is special including volume controlled
Levy；
First Heat Exchanger（32）；
Second heat exchanger（36）；
Positioned at the First Heat Exchanger（32）Interior first pressure sensor（132）；
Positioned at second heat exchanger（36）Interior second pressure sensor（182）；With
Device（70,72,74）, described device（70,72,74）For provide it is following at least two：
Run in the first pattern, wherein：
Refrigerant is in the positive displacement compressor at least partly in parallel（26）With the centrifugal compressor（24）It is middle to be compressed；
Run in a second mode, wherein：
Refrigerant is in the positive displacement compressor（26）It is middle to be compressed, and the centrifugal compressor（24）Offline；
Run in a third mode, wherein：
The positive displacement compressor of the refrigerant at least part series connection（26）With the centrifugal compressor（24）It is middle to be compressed；
With
Run with fourth mode, wherein：
Refrigerant is in the centrifugal compressor（24）It is middle to be compressed, and the positive displacement compressor（26）Offline.
14. equipment as claimed in claim 13, wherein：Both the positive displacement compressor and the centrifugal compressor lead to
Speed change driver is crossed electrically to provide power.
15. one kind is used to run steam compression system（20）Method, the steam compression system（20）With centrifugal compressor
Machine（24）, positive displacement compressor（26）, First Heat Exchanger（32）, the second heat exchanger（36）, positioned at the First Heat Exchanger（32）
Interior first pressure sensor（132）With positioned at second heat exchanger（36）Interior second pressure sensor（182）, it is described from
Core type compressor（24）With the positive displacement compressor（26）Including volume controlled feature, methods described include it is following at least
Two kinds：
Run in the first pattern, wherein：
Refrigerant is in the positive displacement compressor at least partly in parallel（26）With the centrifugal compressor（24）It is middle to be compressed；
Run in a second mode, wherein：
Refrigerant is in the positive displacement compressor（26）It is middle to be compressed, and the centrifugal compressor（24）Offline；
Run in a third mode, wherein：
The positive displacement compressor of the refrigerant at least part series connection（26）With the centrifugal compressor（24）It is middle to be compressed；
With
Run with fourth mode, wherein：
Refrigerant is in the centrifugal compressor（24）It is middle to be compressed, and the positive displacement compressor（26）Offline.
16. method as claimed in claim 15, wherein：
From lowest load situation to intermediate cycling load situation, the system is run with the second mode；With
Under the load higher than the intermediate cycling load situation, the system is run with the first mode.
17. method as claimed in claim 16, wherein：
In the first mode, the change of load is mainly adapted to by the positive displacement compressor.
18. method as claimed in claim 15, wherein：
The combination of the operation based on required capacity and the required temperature difference, and wherein, including the description below some to all：
In the case of the high required temperature difference, the system is with the 3rd mode operation（306）；With
In the case of the low required temperature difference, including in the description below some to all：
In low capacity situation：
The system is operated with the first mode（320）；With
In high-head situation, the system is operated with the 3rd pattern（322）；
In interim capacities situation：
In low-head situation, the system is operated with the 3rd pattern（330）, wherein the capacity base of the positive displacement compressor
The constant and centrifugal compressor is in variable capacity in sheet；With
In high-head situation, the system is operated with the first mode（322）, wherein the centrifugal compressor is in substantially
Go up constant capacity and the positive displacement compressor is in variable capacity；With
In high power capacity situation, the system is operated with the first mode（340）, two of which compressor all provides variable capacity
Amount.
19. method as claimed in claim 15, wherein：Both the positive displacement compressor and the centrifugal compressor lead to
Speed change driver is crossed electrically to provide power.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US201161491515P | 2011-05-31 | 2011-05-31 | |
| US61/491,515 | 2011-05-31 | ||
| US61/491515 | 2011-05-31 | ||
| PCT/US2012/037872 WO2012166338A2 (en) | 2011-05-31 | 2012-05-15 | Hybrid compressor system and methods |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103748425A CN103748425A (en) | 2014-04-23 |
| CN103748425B true CN103748425B (en) | 2017-10-17 |
Family
ID=46147093
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201280026803.3A Active CN103748425B (en) | 2011-05-31 | 2012-05-15 | hybrid compressor system and method |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US20130177393A1 (en) |
| EP (1) | EP2715254A2 (en) |
| CN (1) | CN103748425B (en) |
| WO (1) | WO2012166338A2 (en) |
Families Citing this family (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US9951984B2 (en) | 2013-05-21 | 2018-04-24 | Carrier Corporation | Tandem compressor refrigeration system and a method of using the same |
| US10684032B2 (en) * | 2015-03-09 | 2020-06-16 | Lennox Industries Inc. | Sensor coupling verification in tandem compressor units |
| US10180282B2 (en) * | 2015-09-30 | 2019-01-15 | Air Products And Chemicals, Inc. | Parallel compression in LNG plants using a positive displacement compressor |
| US11187689B2 (en) | 2015-10-20 | 2021-11-30 | Carrier Corporation | Biodegradable parameter monitor |
| DE102017115623A1 (en) * | 2016-07-13 | 2018-01-18 | Trane International Inc. | Variable economizer injection position |
| WO2019083558A1 (en) * | 2017-10-24 | 2019-05-02 | Hussmann Corporation | Refrigeration system and method of refrigeration load control |
| US11656612B2 (en) | 2021-07-19 | 2023-05-23 | Air Products And Chemicals, Inc. | Method and apparatus for managing industrial gas production |
| JP2024021198A (en) * | 2022-08-03 | 2024-02-16 | パナソニックＩｐマネジメント株式会社 | Vapor compression refrigeration cycle equipment |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1122630A (en) * | 1993-05-04 | 1996-05-15 | 埃科艾尔公司 | Zero superheat refrigeration compression system |
| CN1231401A (en) * | 1998-04-06 | 1999-10-13 | 三星电子株式会社 | Multi-unit air conditioner with shunt part capable of regulating refrigerant flow speed |
| CN1795354A (en) * | 2003-05-30 | 2006-06-28 | 大金工业株式会社 | Freezing device |
Family Cites Families (21)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2938361A (en) * | 1957-09-13 | 1960-05-31 | Borg Warner | Reversible refrigerating system |
| GB952873A (en) * | 1960-05-16 | 1964-03-18 | York Shipley Ltd | Reversible refrigerating system |
| DE2848030A1 (en) * | 1978-11-06 | 1980-05-14 | Gutehoffnungshuette Sterkrade | MULTI-STAGE COMPRESSOR |
| US4607498A (en) * | 1984-05-25 | 1986-08-26 | Dinh Company, Inc. | High efficiency air-conditioner/dehumidifier |
| JPS63212797A (en) * | 1987-02-27 | 1988-09-05 | Toshiba Corp | Two-cylinder type rotary compressor |
| DE3937152A1 (en) * | 1989-11-08 | 1991-05-16 | Gutehoffnungshuette Man | METHOD FOR OPTIMIZING OPERATION OF TWO OR SEVERAL COMPRESSORS IN PARALLEL OR SERIES |
| JPH0420751A (en) * | 1990-05-15 | 1992-01-24 | Toshiba Corp | Freezing cycle |
| US5570585A (en) * | 1994-10-03 | 1996-11-05 | Vaynberg; Mikhail | Universal cooling system automatically configured to operate in compound or single compressor mode |
| JPH09145189A (en) * | 1995-11-27 | 1997-06-06 | Sanyo Electric Co Ltd | Refrigerating cycle and air conditioner provided with the refrigerating cycle |
| JP2003176957A (en) * | 2001-10-03 | 2003-06-27 | Denso Corp | Refrigerating cycle device |
| DE602005003489T2 (en) * | 2004-03-05 | 2008-11-13 | Corac Group Plc, Uxbridge | Multi-stage oil-free gas compressor |
| US20050257545A1 (en) * | 2004-05-24 | 2005-11-24 | Ziehr Lawrence P | Dual compressor HVAC system |
| EP1640597B1 (en) * | 2004-09-22 | 2008-07-23 | Ford Global Technologies, LLC | Supercharged internal combustion engine and method for operating such an internal combustion engine |
| EP2097686A4 (en) * | 2006-12-26 | 2010-03-10 | Carrier Corp | Co2 refrigerant system with tandem compressors, expander and economizer |
| US8166776B2 (en) * | 2007-07-27 | 2012-05-01 | Johnson Controls Technology Company | Multichannel heat exchanger |
| WO2009048464A1 (en) * | 2007-10-10 | 2009-04-16 | Carrier Corporation | Tandem compressors of different types |
| WO2009086493A2 (en) * | 2007-12-28 | 2009-07-09 | Johnson Controls Technology Company | Vapor compression system |
| CN201297801Y (en) * | 2008-10-17 | 2009-08-26 | 广东美的电器股份有限公司 | Connecting structure of double compressors |
| JP5446694B2 (en) * | 2008-12-15 | 2014-03-19 | 株式会社デンソー | Ejector refrigeration cycle |
| US20110265506A1 (en) * | 2010-05-01 | 2011-11-03 | Gerald Allen Alston | High Ratio Mobile Electric HVAC System |
| US20110289953A1 (en) * | 2010-05-27 | 2011-12-01 | Gerald Allen Alston | Thermally Enhanced Cascade Cooling System |
-
2012
- 2012-05-15 US US13/818,210 patent/US20130177393A1/en not_active Abandoned
- 2012-05-15 CN CN201280026803.3A patent/CN103748425B/en active Active
- 2012-05-15 WO PCT/US2012/037872 patent/WO2012166338A2/en active Application Filing
- 2012-05-15 EP EP12722646.2A patent/EP2715254A2/en not_active Withdrawn
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1122630A (en) * | 1993-05-04 | 1996-05-15 | 埃科艾尔公司 | Zero superheat refrigeration compression system |
| CN1231401A (en) * | 1998-04-06 | 1999-10-13 | 三星电子株式会社 | Multi-unit air conditioner with shunt part capable of regulating refrigerant flow speed |
| CN1795354A (en) * | 2003-05-30 | 2006-06-28 | 大金工业株式会社 | Freezing device |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2012166338A2 (en) | 2012-12-06 |
| US20130177393A1 (en) | 2013-07-11 |
| EP2715254A2 (en) | 2014-04-09 |
| CN103748425A (en) | 2014-04-23 |
| WO2012166338A3 (en) | 2013-01-24 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN103748425B (en) | hybrid compressor system and method | |
| CN102777365B (en) | Method for the intelligent control of a compressor device with heat recovery | |
| CN104236173B (en) | A kind of wind-cooled evaporator with gas-liquid separator | |
| CN104567054B (en) | Anti-surge system of centrifugal type refrigerating unit | |
| EP1719960A1 (en) | Variable capacity modular refrigerating installation by frequency conversion | |
| CN105091392B (en) | Heat-reclamation multi-compressors system and its control method | |
| CN202583099U (en) | Heat exchange performance test system for electric vehicle power battery radiator | |
| CN102635921A (en) | Energy-saving system and energy-saving method by controlling comprehensive frequency conversion of circulating pump | |
| CN204757425U (en) | Centrifugal refrigerating unit anti -surge system | |
| CN207486412U (en) | Air/natural gas compressor lubricating oil system | |
| CN106704195A (en) | Screw air compressor waste heat recovery device | |
| CN110220322A (en) | Energy saving ultralow temperature precision temperature control heat-exchange system | |
| CN207600009U (en) | A kind of folding type cooling system of freezer with hot gas defrosting | |
| CN109469654A (en) | A kind of robot Hydraulically Operated Equipment | |
| CN102080893A (en) | Novel ammonia refrigerating device and technical process | |
| CN202305244U (en) | System for testing cooling and heating capacity of water source heat pump unit | |
| CN103822419A (en) | Refrigerating apparatus | |
| CN209458207U (en) | A kind of robot Hydraulically Operated Equipment | |
| CN106766455A (en) | Dynamic ice-making device | |
| CN107084122A (en) | Compressor, air energy water heater system and its control method | |
| CN108036195B (en) | Pipeline system capable of heating and cooling simultaneously | |
| CN207397925U (en) | Loaded voltage-regulating electric transformer | |
| CN105861769A (en) | Blast furnace cooling water system variable valve optimized operation and pump selecting method based on maximum temperature difference | |
| CN206281235U (en) | A kind of Water cooling low temperature Parallel sets | |
| CN206943073U (en) | Air-conditioning equipment and its cold oil system |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |