EP4130473A1 - Compresseur alternatif destiné à être utilisé avec un économiseur - Google Patents

Compresseur alternatif destiné à être utilisé avec un économiseur Download PDF

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Publication number
EP4130473A1
EP4130473A1 EP22188812.6A EP22188812A EP4130473A1 EP 4130473 A1 EP4130473 A1 EP 4130473A1 EP 22188812 A EP22188812 A EP 22188812A EP 4130473 A1 EP4130473 A1 EP 4130473A1
Authority
EP
European Patent Office
Prior art keywords
cylinder
compressor
flow
refrigerant
economizer
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.)
Pending
Application number
EP22188812.6A
Other languages
German (de)
English (en)
Inventor
Vishnu M. Sishtla
Emir ALEMIC
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Carrier Corp
Original Assignee
Carrier Corp
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Carrier Corp filed Critical Carrier Corp
Publication of EP4130473A1 publication Critical patent/EP4130473A1/fr
Pending legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • 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
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B41/00—Pumping installations or systems specially adapted for elastic fluids
    • F04B41/06—Combinations of two or more 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
    • F25B1/02—Compression machines, plants or systems with non-reversible cycle with compressor of reciprocating-piston type
    • 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
    • F25B31/02—Compressor arrangements of motor-compressor units
    • F25B31/023—Compressor arrangements of motor-compressor units with compressor of reciprocating-piston type
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers

Definitions

  • the present invention relates to the art of compressors, and more particularly, to a system and method for compressing a flow from an economizer within a compressor.
  • a multi-stage compressor is used in a vapor compression system including an economizer.
  • a multi-stage compressor includes a first compressor stage and a separate second compressor stage arranged in fluid communication with an outlet of the first compressor stage.
  • refrigerant compressed within the first compressor stage is discharged from an outlet of the first compressor stage and is delivered to an inlet of the second compressor stage.
  • the refrigerant gas from the economizer is typically injected into the conduit connecting the two compressor stages. Accordingly, the refrigerant output from the first compressor stage and the refrigerant from the economizer are compressed together within the second compressor stage.
  • Each compressor stage adds size, complexity, and cost to the compressor.
  • a compressor includes a housing having a suction inlet, at least one economizer inlet, and an outlet.
  • a first cylinder arranged within the housing includes a first suction valve arranged in fluid communication with the suction inlet and a first discharge valve fluidly connected to the outlet.
  • At least one second cylinder is arranged within the housing.
  • the at least one second cylinder has a second suction valve in fluid communication with the at least one economizer inlet and a second discharge valve fluidly connected to the outlet.
  • a first piston is arranged within the first cylinder and a second piston is arranged within the at least one second cylinder.
  • the fluid provided at the first discharge valve is configured to bypass the at least one second cylinder.
  • the first cylinder has a first configuration and the at least one second cylinder has a second configuration, the first configuration and the second configuration being different.
  • the at least one second cylinder is smaller than the first cylinder.
  • an amount of compression that occurs within the at least one second cylinder is reduced relative to an amount of compression that occurs within the first cylinder.
  • a compression ratio of the first cylinder to the at least one second cylinder is between 1:2 and 1:5.
  • the at least one second cylinder includes a plurality of second cylinders and the at least one economizer inlet includes a plurality of economizer inlets, each of the plurality of second cylinders is arranged in fluid communication with a different one of the plurality of economizer inlets.
  • At least one of the plurality of second cylinders has a different configuration than another of the plurality of second cylinders.
  • a compressor for use in a vapor compression system includes a housing having a suction inlet, an economizer inlet, and an outlet and a plurality of cylinders arranged within the housing.
  • the plurality of cylinders includes a first cylinder configured to receive a first flow of refrigerant from the suction inlet and a second cylinder configured to receive a second flow of refrigerant from the economizer inlet. The second flow of refrigerant is compressed within the plurality of cylinders independently from the first flow of refrigerant.
  • the first cylinder further includes a first suction valve arranged in fluid communication with the suction inlet and a first discharge valve fluidly connected to the outlet; and the second cylinder further includes a second suction valve in fluid communication with the economizer inlet and a second discharge valve fluidly connected to the outlet.
  • the first cylinder has a first configuration and the second cylinder has a second configuration, the first configuration and the second configuration being different.
  • the second cylinder is smaller than the first cylinder.
  • an amount of compression that occurs within the second cylinder is reduced relative to an amount of compression that occurs within the first cylinder.
  • a compression ratio of the first cylinder to the at least one second cylinder is between 1:2 and 1:5.
  • a method of operating a compressor includes providing a first flow of refrigerant to a suction inlet of the compressor, compressing the first flow of refrigerant within a first cylinder of the compressor, providing a second flow of refrigerant to an economizer inlet of the compressor, compressing the second flow of refrigerant within a second cylinder of the compressor, and delivering the first flow of refrigerant output from the first cylinder and the second flow of refrigerant output from the second cylinder to an outlet of the compressor.
  • first flow of refrigerant is compressed within the first cylinder
  • second flow of refrigerant is compressed within the second cylinder
  • the first flow of refrigerant output from the first cylinder and the second flow of refrigerant output from the second cylinder are delivered to the outlet independently.
  • the method comprises mixing the first flow of refrigerant output from the first cylinder and the second flow of refrigerant output from the second cylinder upstream from the outlet.
  • the first cylinder has a first configuration and the second cylinder has a second configuration that is different from the first configuration.
  • the method comprises providing a third flow of refrigerant to a second economizer inlet of the compressor and compressing the third flow of refrigerant within another second cylinder of the compressor.
  • the compressor 20 has a housing 22 including a suction port or inlet 24 and a discharge port or outlet 26.
  • the housing 22 includes a cylinder block 28 having one or more bores 30 formed therein, each of which defines a "cylinder" of the compressor 20.
  • a cylinder head 32 overlies a portion of the cylinder block 28.
  • the cylinder head 32 includes one or more bores 34 corresponding to and aligned with the one or more bores 30 formed in the cylinder block 28.
  • Each cylinder 30 is configured to accommodate a piston 36 mounted for reciprocal movement at least partially within a cylinder 30.
  • multicylinder configurations include, but are not limited to, in-line, V, and horizontally opposed.
  • the compressor 20 includes three cylinders 30. However, it should be understood that a compressor 20 having a single cylinder, two cylinders, or more than three cylinders are also contemplated herein.
  • the one or more pistons 36 are coupled to a crankshaft 38 mounted within the housing 22.
  • a motor 40 operably coupled to the crankshaft 38 is configured to rotate the crankshaft 38 about an axis of rotation X. Rotation of the crankshaft 38 causes each piston 36 to reciprocate within a respective cylinder 30 within the interior of the cylinder block 28.
  • a bore 34 formed in the cylinder head 32 may be divided into a plurality of fluidly distinct regions.
  • the regions include a suction region 42 and a discharge region 44.
  • a plurality of valves are disposed at the interface between the bore 34 of the cylinder head 32 and a corresponding, aligned bore 30 within the cylinder block 28.
  • a suction valve 50 may be associated with the suction region 42 and a discharge valve 52 may be associated with the discharge region 44.
  • the suction valve 50 and the discharge valve 52 are check valves or no-back valves.
  • one or both of the suction and discharge valves 50, 52 may be actuated in response to a command from a controller C rather than automatically in response to a pressure or flow rate of the refrigerant acting thereon for example.
  • a low pressure fluid such as refrigerant gas for example, is drawn into the cylinder 30.
  • the piston 36 After reaching a bottom of the cylinder 30, or the bottom of the cycle of movement of the piston 36, the piston 36 begins to move upwardly within the cylinder 30.
  • the low pressure refrigerant gas within the cylinder 30 is compressed causing the pressure to build within the cylinder 30. This increase in pressure in combination with the movement of the piston 36 causes the high pressure refrigerant gas to flow from the cylinder 30.
  • An existing compressor configured for use with a vapor compression system including an economizer or economizing heat exchanger typically includes a first compressor stage having at least one first piston and a second compressor stage having at least one second piston.
  • the flow from the economizer is provided via an economizer inlet to an intermediate region of the compressor arranged between the outlet of the first compressor stage and the inlet of the second compressor stage.
  • the flow provided from the economizer bypasses the first compression stage and is therefore only compressed within the second compressor stage with the refrigerant flow output from the first compressor stage.
  • the compressor 20 includes at least one first cylinder 30a having a first configuration and at least one second cylinder 30b having a second configuration. Similar to the cylinders previously described with respect to FIG. 2 , a first piston 36a is movable within the first cylinder 30a and a second piston 36b is movable within the second cylinder 30b, respectively.
  • a first suction valve 50a and a first discharge valve 52a are arranged between the bore 34a formed in the cylinder head 32 and the first cylinder 30a, and a second suction valve 50b and second discharge valve 52b are arranged between the bore 34b formed in the cylinder head 32 and the second cylinder 30b.
  • the at least one first cylinder 30a may be configured to receive a flow of low pressure gaseous refrigerant, such as provided to the compressor 20 from an evaporator located upstream of the compressor 20 within the vapor compression system.
  • the one or more second cylinders 30b may be configured to receive a flow of a medium pressure gaseous refrigerant, such as provided to the compressor 20 from an economizer heat exchanger, also referred to herein as an economizer, of the vapor compression system.
  • an economizer heat exchanger also referred to herein as an economizer
  • each of the plurality of first cylinders 30a may have a similar or identical configuration.
  • each of the plurality of second cylinders 30b may be configured to receive a flow from the same economizer within the vapor compression system.
  • each of the plurality of second cylinders 30b may have a similar configuration.
  • the plurality of second cylinders 30b may be configured to receive a flow from multiple economizers within the vapor compression system.
  • one second cylinder 30b may be associated with each economizer of the vapor compression system. If the vapor compression system has three separate economizers, each connected to a separate economizer inlet of the compressor 20, the compressor 20 will include at least three second cylinders 30b, one associated with each economizer, respectively.
  • each of the plurality of second cylinders 30b may be designed based on the respective pressure of the refrigerant provided thereto. Accordingly, the plurality of second cylinders 30b may have similar, or alternatively, may have different configurations.
  • the configuration of the one or more first cylinders 30a may be different from the configuration of the one or more second cylinders 30b.
  • the one or more second cylinders 30b are smaller than the one or more first cylinders 30a.
  • the amount of compression that occurs within the first cylinders 30a may be double or more than double, such as up to five times the amount of compression that occurs within the second cylinders 30b.
  • the compression ratio of the compression that occurs within the first cylinder 30a relative to the compression that occurs within one of the second cylinders 30b may be anywhere between 1:2 and 1:5.
  • the compressor 20 includes a plurality of second cylinders 30b, it should be understood that the ratio of compression of a first cylinder relative to each of the plurality of second cylinders 30b may vary.
  • each flow of refrigerant provided to one of the plurality of inlets is compressed independently of the other refrigerant flows provided to the other inlets of the compressor 20.
  • a first flow of refrigerant having a first pressure provided to the main inlet or suction inlet 24 of the compressor 20 is delivered to the one or more first cylinders 30a through the first suction valve 50a.
  • the first flow of refrigerant is provided via the first discharge valve 52a to the outlet 26 of the compressor 20 for delivery to a downstream component within the vapor compression system.
  • a second flow of refrigerant provided from an economizer and having a second pressure is delivered to a second cylinder 30b via another inlet 25 of the compressor 20, through second suction valve 50b.
  • the second flow of refrigerant is compressed and then output via the second discharge valve 52b.
  • the second flow of refrigerant output from the second cylinder 30b may be delivered to the same outlet 26, or alternatively, to a different outlet as the first flow of refrigerant output from the at least one first cylinder 30a.
  • the compressed first flow of refrigerant output from the first cylinder 30a may be provided to the outlet 26 independently from the compressed second flow of refrigerant output from the second cylinder 30b.
  • the compressed flows may be mixed together upstream from the outlet 26.
  • the resulting pressure of the flows output from both the at least one first cylinder 30a and the at least one second cylinder 30b may be substantially identical.
  • the compressed refrigerant output from any of the cylinders 30a, 30b need not be delivered to another compression stage or cylinder within the compressor 20.
  • a third flow of refrigerant output from the second economizer and having a third pressure may be delivered to the compressor 20 via a second economizer inlet (not shown).
  • This third flow of refrigerant may be compressed within another second cylinder of the plurality of second cylinders.
  • the another second cylinder is a different second cylinder than the second cylinder used to compressed the flow from the economizer.
  • each flow can be compressed within the compressor 20.
  • each stage of cylinders By using each stage of cylinders to compressor one of the flows, the need for sequential compressing of the refrigerant via multiple stages is eliminated. As a result, the foot print, complexity, and associated cost of the compressor 20 can be reduced.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Compressor (AREA)
EP22188812.6A 2021-08-04 2022-08-04 Compresseur alternatif destiné à être utilisé avec un économiseur Pending EP4130473A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US202163229255P 2021-08-04 2021-08-04

Publications (1)

Publication Number Publication Date
EP4130473A1 true EP4130473A1 (fr) 2023-02-08

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP22188812.6A Pending EP4130473A1 (fr) 2021-08-04 2022-08-04 Compresseur alternatif destiné à être utilisé avec un économiseur

Country Status (3)

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US (1) US20230039145A1 (fr)
EP (1) EP4130473A1 (fr)
CN (1) CN115704370A (fr)

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1722173A2 (fr) * 2005-05-10 2006-11-15 Hussmann Corporation Compresseur linéaire à deux étages
EP1739372A2 (fr) * 2005-06-24 2007-01-03 Hussmann Corporation Compresseur linéaire à deux étages
WO2008082410A1 (fr) * 2006-12-31 2008-07-10 Carrier Corporation Compresseur
US20140170003A1 (en) * 2012-12-18 2014-06-19 Emerson Climate Technologies, Inc. Reciprocating compressor with vapor injection system
US20160123314A1 (en) * 2014-10-29 2016-05-05 Emerson Climate Technologies, Inc. Reciprocating compressor system
WO2016182998A1 (fr) * 2015-05-13 2016-11-17 Carrier Corporation Compresseur à va-et-vient économisé

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1722173A2 (fr) * 2005-05-10 2006-11-15 Hussmann Corporation Compresseur linéaire à deux étages
EP1739372A2 (fr) * 2005-06-24 2007-01-03 Hussmann Corporation Compresseur linéaire à deux étages
WO2008082410A1 (fr) * 2006-12-31 2008-07-10 Carrier Corporation Compresseur
US20140170003A1 (en) * 2012-12-18 2014-06-19 Emerson Climate Technologies, Inc. Reciprocating compressor with vapor injection system
US20160123314A1 (en) * 2014-10-29 2016-05-05 Emerson Climate Technologies, Inc. Reciprocating compressor system
WO2016182998A1 (fr) * 2015-05-13 2016-11-17 Carrier Corporation Compresseur à va-et-vient économisé

Also Published As

Publication number Publication date
CN115704370A (zh) 2023-02-17
US20230039145A1 (en) 2023-02-09

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