CN103748425A - Hybrid compressor system and methods - Google Patents
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- CN103748425A CN103748425A CN201280026803.3A CN201280026803A CN103748425A CN 103748425 A CN103748425 A CN 103748425A CN 201280026803 A CN201280026803 A CN 201280026803A CN 103748425 A CN103748425 A CN 103748425A
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- 238000000034 method Methods 0.000 title claims description 10
- 238000006073 displacement reaction Methods 0.000 claims abstract description 37
- 230000001351 cycling effect Effects 0.000 claims description 5
- 230000006835 compression Effects 0.000 claims description 3
- 238000007906 compression Methods 0.000 claims description 3
- 239000003507 refrigerant Substances 0.000 abstract description 7
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 26
- 238000001816 cooling Methods 0.000 description 4
- 230000000875 corresponding effect Effects 0.000 description 4
- 238000006243 chemical reaction Methods 0.000 description 3
- 238000010586 diagram Methods 0.000 description 3
- 239000013529 heat transfer fluid Substances 0.000 description 3
- 238000011144 upstream manufacturing Methods 0.000 description 3
- 238000009825 accumulation Methods 0.000 description 2
- 239000007788 liquid Substances 0.000 description 2
- 238000005057 refrigeration Methods 0.000 description 2
- 238000012360 testing method Methods 0.000 description 2
- 238000010521 absorption reaction Methods 0.000 description 1
- 238000013459 approach Methods 0.000 description 1
- 230000002596 correlated effect Effects 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000011084 recovery Methods 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 238000004513 sizing Methods 0.000 description 1
- 230000009466 transformation Effects 0.000 description 1
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/58—Cooling; Heating; Diminishing heat transfer
- F04D29/582—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- 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
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
An apparatus (20) has a centrifugal compressor (24), a positive displacement compressor (26), a first heat exchanger (32), and a second heat exchanger (36). A plurality of valves (70, 72, 74) are positioned to provide operation in at least two modes. In a first mode, refrigerant is compressed in the positive displacement compressor and the centrifugal compressor at least partially in parallel. In a second mode, refrigerant is compressed in the positive displacement compressor and the centrifugal compressor is offline. In a third mode, refrigerant is compressed in the positive displacement compressor and the centrifugal compressor at least partially in series.
Description
The cross reference of related application
The application requires the name of submission on May 31st, 2011 to be called the U.S. Patent application No.61/491 of " Hybrid Compressor System and Methods ", 515 rights and interests, the disclosure of this patent application is all incorporated to herein by reference, just as elaborating in this article.
Background technology
The disclosure relates to refrigeration.More specifically, the disclosure relates to chiller system.
Large-size water-cooling freezer unit (for example, 300～1500 tons of capacity (1055～5275W)) is conventionally because cost former thereby use single centrifugal compressor.But this compressor subjects to surge (surge) (particularly when fractional load).
A kind of method addressing this problem is to provide multiple centrifugal compressors in parallel.This allows independent compressor off-line, to make compressor capacity mate better the load of needs.
Summary of the invention
One aspect of the present invention relates to a kind of equipment, and described equipment comprises: centrifugal compressor, positive displacement compressor, First Heat Exchanger and the second heat exchanger.Multiple valves are positioned, to the operation of at least two kinds of patterns is provided.In first mode, cold-producing medium is compressed in positive displacement compressor in parallel at least partly and centrifugal compressor.In the second pattern, cold-producing medium is compressed in positive displacement compressor, and centrifugal compressor is in off-line.In three-mode, cold-producing medium is compressed in the positive displacement compressor of connecting at least partly and centrifugal compressor.
In various embodiments, positive displacement compressor can be screw compressor.
Other side of the present invention relates to at least two kinds of such patterns to be moved.
One or more embodiments of the detail are set forth in accompanying drawing and following explanation.Other features, objects and advantages are from description and accompanying drawing and will become apparent from claims.
Accompanying drawing explanation
Fig. 1 is the schematic diagram of chiller system.
Fig. 2 is the longitudinally vertical schematic diagram of condenser in the system of Fig. 1.
Fig. 3 is the longitudinally vertical schematic diagram of cooler in the system of Fig. 1.
Fig. 4 enters the temperature of water of condenser with respect to the chart of the capacity of percentage.
Fig. 5 is the control flow chart for the system of Fig. 1.
In each accompanying drawing, same Reference numeral and indication represent same element.
The specific embodiment
Except suffering surge problem, centrifugal compressor is more poor efficiency of common specific volume formula compressor when high-head is provided.It is poor alternative that this is used as centrifugal compressor when moving for recuperation of heat.As discussed below, hybrid system is characterised in that and has centrifugal compressor and positive displacement compressor.Exemplary positive displacement compressor is two rotors or the triple-spool screw compressor that power is provided by variable frequency drive.Alternative positive displacement compressor comprises reciprocating compressor and scroll compressor.
Fig. 1 shows steam compression system 20, and it has compressor subsystem 22.Compressor subsystem 22 comprises the first compressor 24 (centrifugal) and the second compressor 26 (positive displacement).In the exemplary embodiment, two compressors all have volume controlled feature, its can be any known type (for example, for the variable inlet guide card of centrifugal compressor with for the guiding valve of screw compressor (described screw compressor is as positive displacement compressor), and for the speed change driver of two kinds of compressors).
In the first operational mode, compressor subsystem drives cold-producing medium along refrigerant flowpath 30 toward downstream direction 500.Flow path 30 is sequentially by First Heat Exchanger 32, expansion gear 34 and the second heat exchanger 36.In first mode, First Heat Exchanger 32 is heat rejection heat exchanger, and the second heat exchanger 36 is heat absorption heat exchangers.
As discussed below, compressor subsystem comprises the one or more valves that are coupled to these compressors, to allow the switching of these compressors between two or more compact models.Example system comprises three valves 70,72 and 74.
In the first operational mode, these compressors are operation in parallel at least partly.In the situation of a complete parallel connection illustrating, these compressors inhalation port separately and discharge port are under identical in fact situation.For this parallel running is provided, exemplary flowpath has two branch roads 80 and 82 in parallel, branch road 80 and 82 diverges at 84 places, abutment in outlet 56 downstreams of the second heat exchanger, and is being positioned at entrance 50 places of First Heat Exchanger or 86 places, position of its upstream reconsolidate.In part situation in parallel, separating and/or rejoin can be in different position.
Bypass branch road or circuit 90 extend between branch road 80 and 82.Exemplary bypass branch road 90 is swum between another downstream and is extended on a compressor.In the exemplary embodiment, this branch road extends to the position 94 of the second upstream of compressor from the position 92 in the first compressor downstream.In order to control flowing in branch road 80 and 82, exemplary valve 70 and 74 is respectively along these branch roads.In the exemplary embodiment, valve 70 is in the downstream of the first end 92 of bypass line 90, and valve 74 is the upstreams at end 94.
In service in exemplary at least part of parallel connection, valve 72 cuts out, and valve 74 and 70 is opened.In the second pattern, only have the second compressor 26 to move.Valve 70 and 72 all cuts out, and valve 74 is opened.Three-mode is series model, and wherein these compressors in series move.In exemplary tandem pattern, valve 70 and 74 cuts out, and valve 72 is opened.Cold-producing medium, before entering the entrance 50 of First Heat Exchanger, does not pass through the first compressor, valve 72 and the second compressor from the outlet 56 of the second heat exchanger with shunting.The 4th possible pattern comprises only makes the first compressor 24 move.In this pattern, valve 72 and 74 cuts out, and valve 70 is opened.
Fig. 1 shows other exemplary details of condenser 32 and cooler 36.Exemplary condenser 32 comprises upper condensator tube bank 120 and bottom aftercooler tube bank 122.Fig. 1 also shows the liquid refrigerant accumulation 124 in condenser.Tube bank 120 and 122 is connected to one or more heat transfer fluid source, to remove heat from cold-producing medium.Aftercooler tube bank 122 is comprised in chamber 126.One or more ingates 128 are along the bottom in chamber 126.Float-controlled valve 130 offers outlet 52.Pressure sensor 132 can be arranged in the headroom of the close entrance 50 of condenser.
In the exemplary embodiment, heat-transfer fluid (for example water) transmits along water loop 138 (Fig. 2), by entrance 140, receive, and from exporting 142 discharges.Corresponding temperature sensor 144 and 146 is measured the inlet temperature T of water
1CONDwith outlet temperature T
2COND.Exemplary flow rate meter 147 is measured the flow F of water along water loop 138
mCOND.
Fig. 4 shows the temperature T of the water that enters condenser
1CONDwith respect to the chart of capacity.Line 200 represents the loaded line (or load line) of U.S. refrigeration association (ARI).In the U.S., freezer unit will be obeyed ARI standard 550.Four reference conditions of this standard identification, these four reference conditions are by the percentage of freezer unit rated load (representing with cooling tonnage) and the entrance of the Water in Condenser being associated/enter temperature to characterize.It is 44F (6.67C) that the operation of carrying out will realize the outlet of chilled water/leave temperature.Four conditions are: 100%, 85F (29.44C); 75%, 75F (23.89C), 50%, 65F (18.33C); With 25%, 65F (being also 18.33C).These conditions (or along connecting their condition of similarity of curve) can be provided for measuring the correlated condition of efficiency.In API test, the flow of the water by cooler is 2.4 gallons of every cooling tons per minute (gpm/ton) (0.043 liter every kilowatt per second (l/s/kW), and the flow of the water of condenser is 3gpm/ton (0.054l/s/kW).
Utilize typical heat exchanger, the temperature rise of the water by condenser is that roughly 8F (4.4C) takes advantage of percentage load, or 8F during 100% load, 6F during 75% load (3.3C), 2F (1.1C) when 4F during 50% load (2.2C) and 25% load.Cooler saturation temperature for example, than the low 1F of the temperature of the chilled water leaving (0.6C) or 2F (1.1C) (, the 43F in ARI test).Similarly, condenser saturation temperature is than temperature and the high 1F of water temperature rising sum or the 2F of water that enters condenser.For the temperature of the water that enters condenser of 85F, temperature rise is 8F, and the temperature of therefore leaving the water of condenser is 93F, and condenser saturation temperature is 93+2=95F.
Table I
In the first exemplary enforcement, first mode in parallel is used to top load situation at least partly, and the second pattern (only positive displacement compressor) is used to low load situation.For example, the second pattern can be for the load from being substantially zero to intermediate cycling load value.Between intermediate cycling load value and maximum load, pattern in parallel is used at least partly.But be noted that intermediate cycling load value can stand suitable hysteresis and control the circulation of avoiding excessive when operating near conversion condition.For example, from zero to conversion condition, the second compressor can move with the speed and/or the power that increase.When conversion, the first compressor can or approach full capacity with full capacity and be directed to online, and the second compressor reset-to-zero or other low capacity value.After this, along with the load increasing, the speed of the second compressor and/or power can increase.Therefore,, in pattern in parallel at least partly, the load/volume change of system mainly adapts to by positive displacement compressor.For example, at least positive displacement compressor can be realized more variation than centrifugal compressor.More properly, positive displacement compressor can be realized at least 75% or at least 90% of load change.Exemplarily, load change at least can represent system peak load 30%, more properly, be at least 40%.
In the first simple illustrative embodiments, the rated capacity of two compressors substantially the same (for example, identical or suitably differently carry out sizing, to solve any hysteresis problem).Therefore, change point is at half load place substantially.
More largo, change point can be between 45% and 55% of total rating system load, or between 40% and 60%.
By (or more largo, not in low load) near the rated load that only has at it or its, use centrifugal compressor, surge problem can be avoided to a great extent.
For example, the exemplary peaking capacity of positive displacement compressor be centrifugal compressor peaking capacity 50～200%, more properly, 100% to 150%.
In a distortion, the 4th (series connection) pattern can be added and use when high condenser water temperature, for example water heating or heat recovery mode.
In another distortion, when the low-down temperature difference of needs, (for example, be less than 25F (13.9C)), centrifugal compressor can be used alone.
In the second more complicated illustrative embodiments, by measuring or determine in other mode the saturation temperature (T of 302 condensers
cOND) and the saturation temperature (T of cooler
cOOL) start control procedure 300 (Fig. 5).T
cONDand T
cOOLcan by following, determine respectively, that is:, by pressure sensor 132 and 182 gaging pressures, then calculate saturation temperature (by the function of look-up table or programming).The temperature difference (lift) is calculated as T
cONDdeduct T
cOOL, 304.For example, if the temperature difference is greater than given threshold value (, 50F (28C)), this system can be with the 4th (series connection) mode operation, 306 so.At this series model, the capacity of centrifugal compressor is controlled by the orientation of compressor speed and entrance guide card.If the gas flow of discharging from centrifugal compressor is higher than the capacity of screw compressor, the pressure between centrifugal compressor and screw compressor will raise, and cause the surge of centrifugal compressor.Now, the speed of centrifugal compressor little by little increases and its guide card is little by little closed, until no longer surge of centrifugal compressor.Similarly logic is applied to screw compressor (that is the First Speed of, being followed by guiding valve).Slow down and always caused the power consumption of minimizing or the efficiency of increase.
For the less temperature difference, can carry out non-series operation.To flow F
mCOOLand temperature T
1COOLand T
2COOLmeasure 308.Capacity also can be calculated, and 310.
Then, for example, when low capacity (, being less than the first value of 50% of for example maximum), operation is modified based on pressure head.For low-head, these compressors can be with equal loads and with first mode operation, 320.This can comprise: when there is speed change driver, Negotiation speed carrys out control capacity; And for the situation of fixed speed, by the entrance guide card of centrifugal compressor and the guiding valve of screw compressor, carry out control capacity.Pressure head and temperature-difference are proportional.In example, low-head is corresponding to the temperature-difference that is less than 35F (19C), and high-head is between 35F and 50F (19C and 28C).
For high-head, system is with the second pattern (only screw compressor) operation, 322.When there is speed change driver, Negotiation speed carrys out control capacity; For the situation of fixed speed, by guiding valve, carry out control capacity.
For example, in the situation of middle capacity (, 50～75%), also can move with first mode.Balance between these compressors can be modified based on pressure head.For low-head, system is moved with paralleling model, and wherein screw compressor moves with fixed capacity, and centrifugal compressor moves with variable capacity, to the total capacity needing is provided.For example, in the case of the centrifugal compressor and screw compressor with equal heap(ed) capacity, screw compressor can move with 50% of its heap(ed) capacity, and centrifugal compressor operate in it heap(ed) capacity 50 and 100% between (combining thus, to 50～75% operation of maximum system capacity is exemplarily provided).Select such operation, to avoid the surge of centrifugal compressor.
In high-head situation, system can provide the first mode of volume controlled to move in fixed capacity and screw compressor substantially with centrifugal compressor wherein, and 332.The exemplary set point of constant volume compressor can be with respect to situation 330 and is different.Centrifugal compressor can move with higher capacity.In above-mentioned example, centrifugal compressor can move with 80% of its heap(ed) capacity, and 40% of total power system capacity is provided thus.Screw compressor may operate in it heap(ed) capacity 20% and 70% between (10～35% of maximum system capacity is provided thus, and close with centrifugal compressor units in case provide maximum system capacity 50～75%).Can select this ruuning situation, this is because centrifugal compressor easily stands surge in low load and high-head situation.
For example, high power capacity (75～100%) in the situation that, also can move with first mode the wherein load operation of these compressors to equate, 340.Therefore, depend on essential capacity, the heap(ed) capacity that each compressor can have at it 75% and 100% between operation so that the capacity of satisfying the demand.
One or more embodiment have been described.However, but be understandable that, can carry out various modifications.For example, in the situation that rebuilding existing system, the details of existing system or its predetermined use may affect the details of any specific implementations.Therefore, other embodiment within the scope of the appended claims.
Claims (16)
1. an equipment (20) comprising:
Centrifugal compressor (24);
Positive displacement compressor (26);
First Heat Exchanger (32);
The second heat exchanger (36); With
Multiple valves (70,72,74), described multiple valves (70,72,74) are oriented to provide at least two kinds in following:
With first mode operation, wherein:
Cold-producing medium is compressed in described positive displacement compressor in parallel at least partly and described centrifugal compressor;
With the second mode operation, wherein:
Cold-producing medium is compressed in described positive displacement compressor, and described centrifugal compressor off-line; With
With three-mode operation, wherein:
Cold-producing medium is compressed in the described positive displacement compressor of connecting at least partly and described centrifugal compressor.
2. equipment as claimed in claim 1, wherein: described positive displacement compressor is screw compressor.
3. equipment as claimed in claim 1, wherein:
Described centrifugal compressor has peaking capacity; With
Described positive displacement compressor has 100～150% peaking capacity of the peaking capacity of described centrifugal compressor.
4. equipment as claimed in claim 1, wherein: described multiple valves are oriented to provide whole three kinds of described patterns.
5. equipment as claimed in claim 1, wherein: described multiple valves are oriented at least provide described first mode and described the second pattern.
6. equipment as claimed in claim 1 is freezer unit, wherein:
Described First Heat Exchanger is a part for condenser unit;
Described the second heat exchanger is a part for cooler; With
Expansion gear (34) is positioned between described condenser and described cooler.
7. equipment as claimed in claim 1, wherein, described multiple valves comprise:
The first valve (70), described the first valve (70) is between described centrifugal compressor and described First Heat Exchanger;
Second valve (72), described second valve (72) is along the bypass (90) that extends to the position (94) between described second valve and described screw compressor from the position (92) between described centrifugal compressor and described the first valve; With
The 3rd valve (74), described the 3rd valve (74) is between described the second heat exchanger and described positive displacement compressor.
8. equipment as claimed in claim 1, further comprises:
Controller (40), described controller (40) is programmed to automatically switch between at least two kinds of patterns.
9. equipment as claimed in claim 8, wherein:
Described controller is programmed to automatically switch between described first mode and described the second pattern.
10. equipment as claimed in claim 9, wherein:
Described controller is programmed, to be switched to described the second pattern in response to the minimizing of load from described first mode, and from described the second pattern, is switched to described first mode in response to the increase of load.
11. equipment as claimed in claim 10, wherein:
Described controller is programmed to be switched to described three-mode in response to calculating for the high demand of the temperature difference.
12. 1 kinds of equipment, comprising:
Centrifugal compressor (24);
Positive displacement compressor (26);
First Heat Exchanger (32);
The second heat exchanger (36); With
Device (70,72,74), described device (70,72,74) is for providing following at least two kinds:
With first mode operation, wherein:
Cold-producing medium is compressed in described positive displacement compressor in parallel at least partly and described centrifugal compressor;
With the second mode operation, wherein:
Cold-producing medium is compressed in described positive displacement compressor, and described centrifugal compressor off-line; With
With three-mode operation, wherein:
Cold-producing medium is compressed in the described positive displacement compressor of connecting at least partly and described centrifugal compressor.
13. 1 kinds for moving the method for steam compression system (20), described steam compression system (20) has centrifugal compressor (24) and positive displacement compressor (26), and described method comprises at least two kinds in following:
With first mode operation, wherein:
Cold-producing medium is compressed in described positive displacement compressor in parallel at least partly and described centrifugal compressor;
With the second mode operation, wherein:
Cold-producing medium is compressed in described positive displacement compressor, and described centrifugal compressor off-line; With with three-mode operation, wherein:
Cold-producing medium is compressed in the described positive displacement compressor of connecting at least partly and described centrifugal compressor.
14. methods as claimed in claim 13, wherein:
From lowest load situation to intermediate cycling load situation, described system is with described the second mode operation; With
Under the load higher than described intermediate cycling load situation, described system is moved with described first mode.
15. methods as claimed in claim 14, wherein:
In described first mode, the variation of load mainly adapts to by described positive displacement compressor.
16. methods as claimed in claim 13, wherein:
The combination of described operation based on desired volume and the required temperature difference, and wherein, some that comprise following content are to all:
The situation of the required temperature difference in, described system is moved (306) with described three-mode; With
In the situation of the low required temperature difference, comprise that some in following content are to all:
In low capacity situation:
Described system operates (320) with described first mode; With
In high-head situation, described system operates (322) with described three-mode;
In middle capacity situation:
In low-head situation, described system operates (330) with described three-mode, and the capacity substantial constant of wherein said positive displacement compressor and described centrifugal compressor are in variable capacity; With
In high-head situation, described system operates (322) with described first mode, and the capacity of wherein said centrifugal compressor in substantial constant and described positive displacement compressor are in variable capacity; With
In high power capacity situation, described system operates (340) with described first mode, and wherein two compressors all provide variable capacity.
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 true CN103748425A (en) | 2014-04-23 |
| CN103748425B CN103748425B (en) | 2017-10-17 |
Family
ID=46147093
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201280026803.3A Expired - Fee Related 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) |
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| 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 |
| EP3365675B1 (en) | 2015-10-20 | 2022-11-30 | Carrier Corporation | Biodegradable parameter monitor |
| DE102017115623A1 (en) | 2016-07-13 | 2018-01-18 | Trane International Inc. | Variable economizer injection position |
| US11268744B2 (en) | 2017-10-24 | 2022-03-08 | Hussmann Corporation | Refrigeration system and method of refrigeration load control |
| US11994135B2 (en) | 2021-06-14 | 2024-05-28 | Air Products And Chemicals, Inc. | Method and apparatus for compressing a gas feed with a variable flow rate |
| 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 type refrigeration cycle device |
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- 2012-05-15 WO PCT/US2012/037872 patent/WO2012166338A2/en active Application Filing
- 2012-05-15 US US13/818,210 patent/US20130177393A1/en not_active Abandoned
- 2012-05-15 CN CN201280026803.3A patent/CN103748425B/en not_active Expired - Fee Related
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Also Published As
| Publication number | Publication date |
|---|---|
| WO2012166338A2 (en) | 2012-12-06 |
| US20130177393A1 (en) | 2013-07-11 |
| WO2012166338A3 (en) | 2013-01-24 |
| CN103748425B (en) | 2017-10-17 |
| EP2715254A2 (en) | 2014-04-09 |
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