EP2456980B1 - Suction cutoff unloader valve for compressor capacity control - Google Patents

Suction cutoff unloader valve for compressor capacity control Download PDF

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Publication number
EP2456980B1
EP2456980B1 EP10802664.2A EP10802664A EP2456980B1 EP 2456980 B1 EP2456980 B1 EP 2456980B1 EP 10802664 A EP10802664 A EP 10802664A EP 2456980 B1 EP2456980 B1 EP 2456980B1
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EP
European Patent Office
Prior art keywords
suction
unloader valve
suction cutoff
cutoff unloader
cylinder
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.)
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Application number
EP10802664.2A
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German (de)
English (en)
French (fr)
Other versions
EP2456980A4 (en
EP2456980A2 (en
Inventor
Alexander Lifson
Michael F. Taras
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Carrier Corp
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Carrier Corp
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Publication of EP2456980A2 publication Critical patent/EP2456980A2/en
Publication of EP2456980A4 publication Critical patent/EP2456980A4/en
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    • 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
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/08—Actuation of distribution members
    • 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
    • F04B27/04—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B27/0404—Details, component parts specially adapted for such pumps
    • F04B27/0451—Particularities relating to the distribution members
    • 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
    • F04B27/04—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B27/053—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with an actuating element at the inner ends of the cylinders
    • 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
    • F04B27/04—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B27/067—Control
    • 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
    • F04B27/04—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B27/067—Control
    • F04B27/0673—Control by using a valve in a system with several pumping chambers, wherein the flow-path through the chambers can be changed, e.g. series-parallel
    • 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
    • F04B27/24—Control not provided for in a single group of groups F04B27/02 - F04B27/22
    • 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
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/01—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being mechanical
    • 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
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/10—Adaptations or arrangements of distribution members
    • F04B39/1073—Adaptations or arrangements of distribution members the members being reed valves
    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/02—Stopping, starting, unloading or idling control
    • F04B49/03—Stopping, starting, unloading or idling control by means of valves
    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • F04B49/225—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves with throttling valves or valves varying the pump inlet opening or the outlet opening
    • 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
    • F04B2201/00—Pump parameters
    • F04B2201/06—Valve parameters
    • F04B2201/0601—Opening times
    • F04B2201/06011—Opening times of the inlet valve only
    • 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
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/074—Details of compressors or related parts with multiple 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
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/026—Compressor control by controlling unloaders
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2521—On-off valves controlled by pulse signals

Definitions

  • Refrigeration and air conditioning systems are commonly configured with means for system capacity control, thereby allowing the systems to improve temperature control accuracy, reliability, and energy efficiency.
  • unit cycling turning the compressor on and off in response to fluctuations in temperature or system pressure.
  • unit cycling does not allow for tight temperature control, and therefore, commonly creates discomfort and/or undesired temperature variations in the conditioned/refrigerated space.
  • a suction modulation valve located on a suction line downstream of the compressor is another means commonly utilized for system capacity control.
  • suction modulation valves are expensive and are inefficient for system capacity control.
  • suction cutoff unloader valves integral to the compressor have been developed.
  • One such suction cutoff unloader valve is disclosed in United States Patent Application Publication Number 2006/0218959 to Sandkoetter .
  • the suction cutoff unloader valve disclosed in Sandkoetter is adapted to be operable only in a single stage compressor, where compression is accomplished only by lower stage cylinders operating in parallel.
  • Sandkoetter discloses that all cylinder units 44 have the same switching intervals in a lower part-load range and that all the suction cutoff unloader valves are preferably operated with the same switching intervals in an upper part-load range to avoid balancing problems with the compressor pistons.
  • WO 97/13066 A1 discloses an unloader system for a gas compressor including a cylinder, an unloader valve assembly and an unloader actuation system including a controller.
  • a reciprocating compressor for refrigerant comprising: a first cylinder and a second cylinder; movable reciprocal pistons disposed in the cylinders; a first suction cutoff unloader valve assembly integral to the compressor and adapted for pulse width modulation cycling to interrupt flow of the refrigerant to the first cylinder; a second suction cutoff unloader valve assembly integral to the compressor and adapted for pulse width modulation cycling to interrupt flow of the refrigerant to the second cylinder; and a controller configured to operate at least one of the suction cutoff unloader valve assemblies in pulse width modulation cycling and monitor a number of pulse width modulation cycles for at least one of the suction cutoff unloader valve assemblies; wherein operating in pulse width modulation cycling achieves a variable part-load capacity; characterised in that the controller is configured such that pulse width modulation cycling includes an alternating cycling mode that operates the first suction cutoff unloader valve assembly in pulse width modulation cycling, while the second suction cutoff unloader
  • FIG. 1A shows a cross-section of a multi-stage reciprocating compressor 10M with a controller 12 is electrically connected to suction cutoff unloader valve assembly(s) 14.
  • the compression is accomplished in two steps, where the first stage of compression (from the suction pressure to intermediate pressure) is accomplished by the lower stage cylinder(s) and the second stage of compression (from the intermediate pressure to discharge pressure) is accomplished by higher stage cylinder(s).
  • the compressor 10 includes lower stage cylinder heads 16L, a higher stage cylinder head 16H, a housing 18, a cylinder block 20, lower stage cylinder banks 22L, a higher stage cylinder bank 22H, lower stage cylinders 24L, a higher stage cylinder 24H, pistons 26, connecting rods 28, a crankshaft 30, an oil sump 32, a suction manifold 34, and an intermediate manifold 36.
  • Each of the lower and higher stage cylinder heads 16L and 16H includes a suction plenum 38 and a plenum 40.
  • the multi-stage reciprocating compressor 10M has suction cutoff unloader valve assembly or assemblies 14 which interconnect with the low stage cylinder heads 16L. At least one suction cut off assembly 14 is capable of operating in a rapid cycle mode. In embodiments such as the one illustrated in FIG. 1A , the compressor 10M can have two or more suction cutoff unloader valve assemblies 14, where both suction cutoff valve assemblies are operating in rapid cycle mode, or only one suction cut off assembly 14 is operating in rapid cycle mode.
  • the suction cutoff unloader valve assemblies 14 are integral to the compressor 10M.
  • the housing 18 of the multi-stage compressor 10M has an upper portion of which forms the cylinder block 20.
  • the cylinder block 20 forms one or more low lower stage cylinder banks 22L, as well as the higher stage cylinder bank 22H.
  • the cylinder block 20 defines lower stage cylinders 24L and a higher stage cylinder 24H.
  • the cylinders 24L and 24H which extend through the cylinder block 20, are disposed adjacent to the cylinder heads 16L and 16H and the suction cutoff unloader valve assemblies 14.
  • the lower stage cylinder heads 16L are secured to the cylinder block 20 overlaying the lower stage cylinders 24L in the low stage cylinder banks 22L.
  • the higher stage cylinder head 16H is secured to the cylinder block 20 overlaying the higher stage cylinders 24H in the higher stage cylinder bank 22H.
  • Each cylinder bank 22L or 22H includes at least one cylinder 24L or 24H and may include multiple cylinders 24L or 24H which are overlaid by cylinder head 16L or 16H.
  • the pistons 26 are disposed in the lower and higher stage cylinders 24L and 24H and are reciprocally movable therein.
  • the pistons 26 interconnect with the connecting rods 28 which extend internally within the multi-stage compressor 10M to interconnect with an eccentric portion of the crankshaft 30.
  • the crankshaft 30 is rotatably disposed internally in the compressor 10M and extends through the oil sump 32.
  • the suction manifold 34 and intermediate manifold 36 are defined by the cylinder block 20.
  • the suction manifold 34 communicates with the oil sump 32 or directly with a suction line (not shown).
  • the suction manifold 34 extends to the lower stage cylinder heads 16L to fluidly communicate with the suction plenum 38 in each cylinder head 16L.
  • a low pressure refrigerant enters the multi-stage compressor 10M from the suction line (not shown) through an inlet port (not shown).
  • the reciprocating movement of the piston(s) 26 within the low stage cylinder(s) 24L draws the refrigerant from the suction line (not shown).
  • the refrigerant is drawn into the suction manifold 34, and from there the refrigerant is drawn into the suction plenum 38 in the lower stage cylinder head 16L.
  • the refrigerant passes into the low stage cylinder 24L (or cylinders) where it is compressed by the piston(s) 26.
  • a reed valve (not shown) is positioned above each lower stage cylinder 24L to control the flow of refrigerant thereto.
  • the higher pressure vapor refrigerant is discharged through another reed valve (not shown) into the plenum 40.
  • a first portion of the suction cutoff unloader valve 14 fluidly communicates with the plenum 40 and is configured to allow the refrigerant (at intermediate discharge pressure) to hold open a piston portion of the suction cutoff unloader valve 14 to permit the flow of the refrigerant through the suction plenum 38 to the lower stage cylinder(s) 24L.
  • the intermediate pressure refrigerant eventually passes to the intermediate manifold 36.
  • the intermediate pressure refrigerant is drawn from the intermediate manifold 36 to the suction plenum 38 of the higher stage cylinder head 16H where compression of the refrigerant in the higher stage cylinder 24H (or cylinders) is repeated.
  • no suction cutoff unloader valve 14 is necessary on the higher stage cylinder head 16H.
  • the multi-stage reciprocating compressor 10M When the multi-stage reciprocating compressor 10M is in a fully unloaded mode, i.e. all the suction cutoff unloader valve assemblies 14 are constantly on and, are therefore, not cycling in a pulse width modulated manner.
  • the first portion of each of the suction cutoff unloader valve assemblies 14 is disposed to block flow of the refrigerant from the plenum 40 to the piston portion of the suction cutoff unloader valve assembly 14.
  • This configuration allows the biased piston portion of the suction cutoff unloader valve assembly 14 to move to a position where it substantially halts the flow of the refrigerant through the suction plenum 38 to the lower stage cylinder(s) 24L.
  • the controller 12 can be provided with control logic which allows one or more of the suction cutoff unloader valve assemblies 14 on the first stage of the multi-stage compressor 10M to be operated in rapid cycling (for example, using a pulse width modulation technique) to provide a continuously variable amount of capacity (part-load operation) between the capacity achieved by the multi-stage compressor 10M when the suction cutoff unloader valve assemblies 14 are in the fully unloaded position, and the capacity achieved by the multi-stage compressor 10M when the suction cutoff unloader valve assemblies 14 are in the fully loaded position.
  • the low pressure stage can have of only one suction cutoff valve assembly and only one cylinder, where the suction cutoff valve is capable of operating in a rapid cycle mode.
  • the controller 12 can also be provided with control logic which allows a first suction cutoff unloader valve assembly 14 and a second suction cutoff unloader valve assembly 14 to alternate rapid cycling in a mode that allows one of the suction cutoff unloader valve assemblies 14 to operate in rapid cycling while the other suction cutoff unloader valve assembly 14 is not operated in rapid cycling but is disposed in the fully loaded position or the fully unloaded position.
  • the first suction cutoff unloader valve assembly 14 can operate in rapid cycling for a first time period. During the first time period, the second suction cutoff unloader valve assembly 14 is not operated in rapid cycling.
  • the second suction cutoff unloader valve assembly 14 is then operated in rapid cycling for a second time period. During that second time period, the first suction cutoff unloader valve assembly 14 is not operated in rapid cycling. In this manner, the suction cutoff unloader valve assemblies 14 can be alternated in rapid cycling to achieve continuously variable part-load system capacity.
  • the pattern of changing the suction cutoff unloader valve assembly 14 that is operated in rapid cycling while the other valve or valves, if present, are not operated in rapid cycling can be repeated for each valve in the compressor 10M.
  • the alternating sequence can be modified, for example, instead of a single suction cutoff unloader valve assembly 14 that is operated in rapid cycling, multiple suction cutoff unloader valve assemblies 14 can be operated in rapid cycling while a single (or multiple) suction cutoff unloader valve assembly 14 is not operated in rapid cycling.
  • all the suction cutoff unloader valve assemblies 14 in the compressor 10M can be operated in rapid cycling to achieve part-load system capacities.
  • one or more suction cutoff unloader valve assemblies 14 can achieve part-load system operation by rapid cycling between the fully loaded position and the fully unloaded position with a single cycle period that is between 0.3 second and 180 seconds. This cycle period is short enough to account for the inertia of the reaction of the refrigeration or air conditioning system.
  • the operation of the suction cutoff unloader valve assemblies during the cycle period may vary. For example, within 180 second period, one suction cutoff unloader valve assembly 14 can be operated at the fully loaded position (or nearly fully loaded position) for 10 seconds and then operated at the fully unloaded (or nearly fully unloaded position) position for 170 seconds.
  • the suction cutoff unloader valve assembly 14 can be operated at the fully unloaded position for 20 seconds and then operated at the fully loaded position for 160 seconds. Thus, various different operation patterns during a single cycle period are possible.
  • the suction cutoff unloader valve assembly 14 operates with a 5 second cycle period. In this embodiment, the suction cutoff unloader valve assembly 14 can be operated at the fully loaded position for 1 second and then operated at the fully unloaded position for 4 seconds. Alternatively, the suction cutoff unloader valve assembly 14 can be operated at the fully unloaded position for 2 seconds and then operated at the fully loaded position for 3 seconds, etc.
  • a compressor 10S has at least two suction cutoff valve assemblies 14 that are capable of operation in rapid cycle mode.
  • This embodiment monitors the number of cycles for the at least two suction cutoff valve assemblies 14 .
  • the controller 12 can adjust the amount of rapid cycles each valve undergoes. Thus the rapid cycling can be split between the valves to increase the longevity of the at least two suction cutoff valve assemblies 14.
  • FIG. 1B shows a cross-section of a single low stage compression reciprocating compressor 10S with a controller 12 electrically connected to multiple suction cutoff unloader valve assemblies 14.
  • the single low stage compressor can have more than one low stage compression stages connected in parallel to each other in other embodiments.
  • the compressor 10 includes cylinder heads 16L, the housing 18, the cylinder block 20, cylinder banks 22L, cylinders 24L, pistons 26, connecting rods 28, the crankshaft 30, the oil sump 32, and the suction manifold 34.
  • Each of the cylinder heads 16L includes the suction plenum 38 and the plenum 40.
  • the compressor 10S includes a discharge manifold 42.
  • the single stage reciprocating compressor 10S has suction cutoff unloader valve assemblies 14 which interconnect with the cylinder heads 16L.
  • the housing 18 of the compressor 10S has an upper portion of which forms the cylinder block 20.
  • the cylinder block 20 forms one or more cylinder banks 22L.
  • the cylinder block 20 defines cylinders 24L.
  • the cylinders 24L which extend through the cylinder block 20, are disposed adjacent to the cylinder heads 16L.
  • the cylinder heads 16L are secured to the cylinder block 20 overlaying the cylinders 24L in the cylinder banks 22L.
  • Each cylinder bank 22L includes at least one cylinder 24L and may include multiple cylinders 24L which are overlaid by cylinder head 16L.
  • the pistons 26 are disposed in the cylinders 24L and are reciprocally movable therein.
  • the pistons 26 interconnect with the connecting rods 28 which extend internally within the single stage compressor 10S to interconnect with an eccentric portion of the crankshaft 30.
  • the crankshaft 30 is rotatably disposed internally in the compressor 10S and extends through the oil sump 32, which is optional but illustrated in the embodiment shown in FIG. 1B .
  • the suction manifold 34 and discharge manifold 42 are defined by the cylinder block 20.
  • Each of the cylinder heads 16L has a suction plenum 38 and plenum 40 therein which selectively communicate with the underlying cylinders 24L during a portion of the stroke of the pistons 26.
  • the suction manifold 34 communicates with the oil sump 32 or directly with a suction line (not shown).
  • the suction manifold 34 extends to the cylinder heads 16L to fluidly communicate with the suction plenum 38 in each cylinder head 16L.
  • the discharge manifold 42 selectively fluidly communicates with the plenum 40 through ports in the valve plate.
  • the discharge manifold 42 also fluidly communicates a discharge line (not shown) to allow refrigerant discharged from the cylinders 24L to pass to the other components of the heating or cooling system.
  • the suction cutoff unloader valve assemblies 14 of the compressor 10S are capable of operating in a manner similar to that of the suction cutoff unloader valve assemblies 14 of the multi-stage compressor 10M shown in FIG. 1A .
  • the compressor 10S when the compressor 10S is in a fully loaded mode of operation, i.e. all the suction cutoff unloader valve assemblies 14 are activated but are not cycling in a pulse width modulated mode.
  • refrigerant is drawn through the suction manifold 34, and from there into the suction plenum 38 in the cylinder head 16L. From the suction plenum 38 the refrigerant passes into the cylinder 24L (or cylinders) where it is compressed by the piston(s) 26.
  • a first portion of the suction cutoff unloader valve 14 fluidly communicates with the plenum 40 and is positioned to allow the refrigerant (at discharge pressure) to force open a piston portion of the suction cutoff unloader valve 14 to permit the flow of the refrigerant through the suction plenum 38 to the cylinder 24L.
  • the refrigerant passes to the discharge manifold 42.
  • the compressed refrigerant exits the compressor 10S through an outlet port (not shown) to other components of the heating or cooling system.
  • the compressor 10S When the single stage reciprocating compressor 10S is in a fully unloaded mode, i.e. all the suction cutoff unloader valve assemblies 14 are constantly on and, are therefore, not cycling in a pulse width modulated manner, the compressor 10S operates as described above until the point at which the compressed refrigerant is discharged from the cylinder 24L (or cylinders) into the plenum 40. Because all the suction cutoff unloader valve assemblies 14 are deactivated, the first portion of each of the suction cutoff unloader valve assemblies 14 is disposed to block discharge flow of the refrigerant from the plenum 40 to the piston portion of the suction cutoff unloader valve assembly 14. This configuration allows the biased piston portion of the suction cutoff unloader valve assembly 14 to move to a position where it substantially halts the flow of the refrigerant through the suction plenum 38 to the cylinder(s) 24L.
  • the controller 12 can be provided with control logic which allows a first suction cutoff unloader valve assembly 14 and a second suction cutoff unloader valve assembly 14 to alternate rapid cycling in a mode that allows one of the suction cutoff unloader valve assemblies 14 to operate in rapid cycling while the other suction cutoff unloader valve assembly 14 is not operated in rapid cycling but is disposed in the fully loaded position or the fully unloaded position.
  • the first suction cutoff unloader valve assembly 14 can operate in rapid cycling for a first time period.
  • the second suction cutoff unloader valve assembly 14 is not operated in rapid cycling.
  • the second suction cutoff unloader valve assembly 14 is then operated in rapid cycling for a second time period.
  • the suction cutoff unloader valve assemblies 14 can be alternated in rapid cycling to achieve continuously variable part-load system capacity. Alternating the cycles of the valve assemblies can be achieved by the controller 12, which monitors and counts the number of rapid cycles for each valve and alternates the first and second suction cutoff unloader valve assemblies 14 based on the count to assure that the first suction cutoff unloader valve assembly 14 is not operated in a rapid cycling mode for a substantially higher number of cycles more than the second suction cutoff unloader valve assembly 14. In this manner, wear on any single valve assembly due to rapid cycling can be reduced.
  • a controller 12 it is possible for a controller 12 to only count the number of cycles on one valve assembly 14 and when the number of cycles approaches a limit on this valve, the other valve would then be operated in the rapid cycling mode, while the first valve would stop operating in the rapid cycling mode.
  • the counting does not need to be direct but, for example, can be estimated based on the number of days the compressor is in service or the number of hours the compressor has been operational, etc. In this case, for example, the switching between the valves can be done based on how many days one valve was operating in the rapid cycling mode versus the other valve. Alternating the cycling of the valves reduces the overall number of cycles each valve experiences to achieve the desired system part-load capacity. Thus, the service life of the suction cutoff unloader valves and reliability of the compressor can be increased via alternating the cycling of the valves.
  • One or more of the suction cutoff unloader valve assemblies 14 of the single stage compressor 10S can be operated in a pulse width modulation mode to provide a continuously variable capacity (part-load mode of operation) between the capacity achieved by the single stage compressor 10S when the suction cutoff unloader valve assemblies 14 are in the fully unloaded position, and the capacity achieved by the single stage compressor 10S when the suction cutoff unloader valve assemblies 14 are in the fully loaded position.
  • the controller 12 can also be provided with control logic which allows rapid cycling of a first suction cutoff unloader valve assembly 14 and a second suction cutoff unloader valve assembly 14 to alternate in rapid cycling such that while one of the suction cutoff unloader valve assemblies 14 operates in rapid cycling the other suction cutoff unloader valve assembly 14 is not operated in rapid cycling but is disposed in the fully loaded position or fully unloaded position.
  • the pattern, sequence, and number of suction cutoff unloader valve assemblies 14 alternated can be altered in the manner discussed above with reference to the multi-stage compressor 10M ( FIG. 1A ).
  • FIG. 2A is a partial sectional view of a portion of the compressor 10S or 10M with the suction cutoff unloader valve assembly 14 in a fully loaded position.
  • FIG. 2B is a partial sectional view of a portion of the compressor 10S or 10M with the suction cutoff unloader valve assembly 14 in a fully unloaded position.
  • the compressor 10S or 10M includes a valve plate 44, fasteners 46, suction ports 48A and 48B, a suction valve 50, discharge ports 52A and 52B, a discharge valve 54, and a channel port 56.
  • the cylinder head 16 includes a channel 58, guide walls 60, and a suction cutoff wall 62.
  • the suction cutoff unloader valve assembly 14 includes the channel 58, channels 58A and 58B, a pressure chamber 64, a piston chamber 66, a valve piston 68, a valve 70, a solenoid 72, a valve body 74, and a bias spring 76.
  • the lower stage cylinder head 16L overlays the cylinder block 20 and the lower stage cylinder 24L.
  • the valve plate 44 is disposed between the cylinder block 20 and the lower stage cylinder head 16L.
  • the fasteners 46 secure the lower stage cylinder head 16L to the cylinder block 20.
  • the valve plate 44 defines suction ports 48A and 48B.
  • Suction port 48A extends through the valve plate 44 between the suction manifold 34 and the suction plenum 38.
  • Suction port 48B extends through the valve plate 44 between the suction plenum 38 and the lower stage cylinder 24L.
  • the suction valve 50 connects to the valve plate 44 and selectively covers the suction port 48B.
  • the suction valve 50 is selectively movable from over the suction port 48B to allow refrigerant to enter the lower stage cylinder 24L.
  • the discharge port 52A extends through the valve plate 44 between the lower stage cylinder 24L and the plenum 40.
  • Discharge valve 54 connects to the valve plate 44 and interacts with the valve plate 44 to selectively cover and uncover the discharge port 52A.
  • Discharge port 52B extends through the valve plate 44 between the plenum 40 and the intermediate or discharge manifold 36 or 42.
  • Channel port 56 extends through the lower stage cylinder head 16L to allow the channel 58 to communicate with the plenum 38.
  • the channel 58 extends through the casing of the lower stage cylinder head 16L and stator casing portion of the suction cutoff unloader valve assembly 14.
  • the guide walls 60 are internal walls in the lower stage cylinder head 16L which are sized to receive a movable portion of the suction cutoff unloader valve assembly 14.
  • the suction cutoff wall 62 is disposed adjacent the suction port 48A to extend into the suction plenum 38. The suction cutoff wall 62 interacts with another movable portion of the suction cutoff unloader valve assembly 14 to halt the flow of refrigerant through the suction plenum 38 to the lower stage cylinder 24L.
  • the channel 58 extends from the plenum 40 (through channel port 56) to the pressure chamber 64.
  • the channel 58A extends from pressure chamber 64 through the stator portion of the suction cutoff valve assembly 14 to the suction plenum 38 (around the guide wall 60), while the channel 58B extends from the pressure chamber 64 through the stator portion of the suction cutoff valve assembly 14 to communicate with the piston chamber 66.
  • the valve piston 68 is received between the guide walls 60 (which define the piston chamber 66) and is movable relative thereto.
  • the valve 70 extends through the pressure chamber 64 and interconnects with the solenoid 72 which movably actuates the valve 70 within the pressure chamber 64.
  • the valve 70 blocks channel 58 from fluid communication with the pressure chamber 64 when the suction cutoff valve assembly 14 enters the fully unloaded position.
  • the valve 70 blocks channel 58A from fluid communication with the pressure chamber 64 when the suction cutoff valve assembly 14 enters the fully loaded position.
  • the piston chamber 66 receives the valve piston 68 therein.
  • the valve piston 68 connects to the valve body 74 which extends through the suction plenum 38.
  • the portion of the valve body 74 extending away from the valve piston 68 is configured to receive the bias spring 76.
  • the bias spring 76 is disposed in the suction plenum 38 and contacts the valve body 74 and the wall of the low stage cylinder head 16L.
  • the suction port 48A provides a pathway for refrigerant to fluidly communicate from the suction manifold 34 to the suction plenum 38.
  • Suction port 48B provides a pathway for refrigerant to be drawn by reciprocation of the piston 26 from the suction plenum 38 to the lower stage cylinder 24L.
  • the suction valve 50 selectively covers the suction port 48B to substantially block fluid communication of the refrigerant from the suction plenum 38 to the lower stage cylinder 24L and is selectively movable from over the suction port 48B to allow refrigerant to enter the lower stage cylinder 24L during a suction portion of the piston 26 stroke.
  • the discharge port 52A allows higher pressure compressed refrigerant to fluidly communicate from the lower stage cylinder 24L to the plenum 40 during the discharge stroke of the piston 26.
  • the discharge valve(s) 54 selectively covers the discharge port(s) 52A to substantially block fluid communication of the refrigerant from the lower stage cylinder 24L to the plenum 40 until the refrigerant is a sufficient pressure to raise the discharge valve(s) 54 away from the valve plate 44.
  • Discharge port 52B provides a pathway for compressed refrigerant to fluidly communicate from the plenum 40 to the intermediate or discharge manifold 36 or 42.
  • the channel 58 extends from the plenum 40 (through channel port 56) to the pressure chamber 64 to allow refrigerant to communicate therewith.
  • the channel 58A extending from the pressure chamber 64 to the suction plenum 38 is substantially blocked by the valve 70 which is actuated into this blocking position by the solenoid 72.
  • the refrigerant is directed from the plenum 40 through the channel 58 to the pressure chamber 64, and from the pressure chamber 64 through channel 58B into the piston chamber 66.
  • the compressed high pressure refrigerant causes the internal pressure to build within the piston chamber 66 to a level sufficient to overcome the bias on the valve body 74 by the bias spring 76.
  • valve piston 68 and valve body 74 move within the piston chamber 66 and suction plenum 38 to a position which allows refrigerant to flow through the suction plenum 38 between the valve body 74 and the suction cutoff wall 62, such that the refrigerant can communicate with the low stage cylinder 24L through the suction port(s) 48B.
  • the solenoid 72 actuates the valve 70 away from a position which blocks communication of refrigerant through channel 58A.
  • the actuation of the valve 70 moves the valve 70 to a position which blocks communication of refrigerant through channel 58.
  • high pressure compressed refrigerant is substantially blocked from entering the piston chamber 66.
  • the refrigerant in the piston chamber 66 is decreased in pressure by communication between the suction plenum 38 and piston chamber 66 (through channels 58A and 58B) and by a bleed orifice (not shown), which allows the refrigerant to bleed from the piston chamber 66 back into the channel 58.
  • the pressure exerted on the valve piston 68 is insufficient to overcome the bias of the bias spring 76.
  • the bias spring 76 moves the valve piston 68 and valve body 74 within the piston chamber 66 and suction plenum 38 to a position which substantially halts the flow of refrigerant through the suction plenum 38 between the valve body 74 and the suction cutoff wall 62.
  • the configuration and arrangement of the valve body 74 and suction cutoff wall 62 do not allow for the flow of refrigerant to the lower stage cylinder 24L when the suction cutoff valve assembly 14 is in the fully unloaded position.
  • the suction cutoff unloader valve assemblies 14 can be operated in a pulse width modulation mode to provide a continuously variable capacity (part-load mode of operation) between the capacity achieved by the compressor 10 ( FIGS. 1A and 1B ) when the suction cutoff unloader valve assembly 14 is in the fully unloaded mode, and the capacity achieved by the compressor 10S or 10M when the suction cutoff unloader valve assembly 14 is in the fully loaded position.
  • the solenoid 72 can be activated by the controller 12 ( FIGS.
  • valve 70 to operate in a pulse width modulation mode and provide for a continuously variable capacity by moving the valve 70 to block and unblock the channels 58 and 58A in a rapid fashion to allow/disallow communication between the plenum 40 and the piston chamber 66 (and thereby cause valve piston 68 and valve body 74 to move relative to the suction cutoff wall 62 to block/unblock the flow of refrigerant through the suction plenum 38 to the lower stage cylinder 24L).
  • the solenoid 70 can cycle between the fully loaded position of FIG. 2A , and the fully unloaded position of FIG. 2B , either rapidly or more slowly as dictated by the inertia of the system.
  • the cycle period of the suction cutoff unloader valve assembly 14 and solenoid 72 is between 0.3 second and 180 seconds. In another embodiment, the cycle period is between 3 seconds and 30 seconds. In yet another embodiment, the cycle period of the suction cutoff unloader valve assembly 14 is approximately 15 seconds.
  • Pulse width modulation of the solenoid 72 of the suction cutoff unloader valve assembly 14 allows for greater compressor 10 capacity control, thereby allowing the suction cutoff unloader valve assembly 14 to dial in on a desired compressor 10 capacity.
  • Greater compressor 10 capacity control allows the refrigeration or air conditioning system to achieve improved temperature control accuracy, reliability, and energy efficiency.
  • the controller 12 ( FIGS. 1A and 1B ) can also be provided with control logic which allows a first suction cutoff unloader valve assembly 14 and a second suction cutoff unloader valve assembly 14 to alternate cycling modes such that while one of the suction cutoff unloader valve assemblies 14 operates in the pulse width modulated mode the other suction cutoff unloader valve assembly 14 is not operated in the pulse width modulation mode but is disposed in the fully loaded position or the fully unloaded position.
  • the pattern, sequence, and number of suction cutoff unloader valve assemblies 14 alternated can be altered in the manner discussed above with reference to the multi-stage compressor 10M ( FIG. 1A ).
  • FIG. 3A shows a portion of the suction cutoff unloader valve assembly 14 and lower stage cylinder head 16L in the fully loaded position.
  • FIG. 3B shows the portion of the suction cutoff unloader valve assembly 14 and lower stage cylinder head 16L in the fully unloaded position.
  • the low stage cylinder head 16L includes the suction plenum 38, the channel 58, and guide walls 60.
  • the suction cutoff unloader valve assembly 14 includes a movable bias member 78 and a bleed orifice 80.
  • Channel port 56 extends through the low stage cylinder head 16L to allow the channel 58 to communicate with the plenum 40.
  • the channel 58 extends through the casing of the lower stage cylinder head 16L and stator casing portion of the suction cutoff unloader valve assembly 14.
  • the guide walls 60 are internal walls in the low stage cylinder head 16L are sized to receive a movable portion of the suction cutoff unloader valve assembly 14.
  • the suction cutoff wall 62 is disposed adjacent suction port 48A to extend into the adjacent suction plenum 38. The suction cutoff wall 62 interacts with another movable portion of the suction cutoff unloader valve assembly 14 to halt the flow of refrigerant through the suction plenum 38 to the lower stage cylinder 24L.
  • the channel 58 extends from the plenum 40 (through channel port 56) to the pressure chamber 64.
  • the channel 58A extends from pressure chamber 64 through the stator portion of the suction cutoff valve assembly 14 to the suction plenum 38 (around the guide wall 60), while the second channel 58B extends from the pressure chamber 64 through the stator portion of the suction cutoff valve assembly 14 to communicate with the piston chamber 66.
  • the valve piston 68 is received between the guide walls 60 (which define the piston chamber 66) and is movable relative thereto.
  • the valve 70 extends through the pressure chamber 64 and interconnects with the movable bias member 78 portion of solenoid 72 which actuates the valve 70 within the pressure chamber 64.
  • the valve 70 blocks channel 58 from fluid communication with the pressure chamber 64 when the suction cutoff valve assembly 14 enters the fully unloaded position.
  • the valve 70 blocks channel 58A from fluid communication with the pressure chamber 64 when the suction cutoff valve assembly 14 enters the fully loaded position.
  • the bleed orifice 80 extends into the stator portion of the suction cutoff unloader valve assembly 14 and communicates with the channel 58.
  • the channel 58 extends from the plenum 40 (through channel port 56) to the pressure chamber 64 to allow refrigerant to communicate therewith.
  • the channel 58A extending from the pressure chamber 64 to the suction plenum 38 is substantially blocked by the valve 70 which is actuated into this blocking position by the solenoid 72.
  • the refrigerant is directed from the plenum 40 through channel 58 to the pressure chamber 64, and from the pressure chamber 64 through channel 58B into the piston chamber 66.
  • the compressed high pressure refrigerant causes the internal pressure to build within the piston chamber 66 to a level sufficient to overcome the bias on the valve body 74 by the bias spring 76 ( FIG. 2A ).
  • valve piston 68 and valve body 74 moves within the piston chamber 66 and suction plenum 38 to a position which allows refrigerant to flow through the suction plenum 38 between the valve body 74 and the suction cutoff wall 62 such that the refrigerant can communicate with the low stage cylinder 24L through the suction port(s) 48B ( FIG. 2A ).
  • the solenoid 72 actuates the valve 70 away from a position which blocks communication of refrigerant through channel 58A.
  • the actuation of the valve 70 moves the valve 70 to a position which blocks communication of refrigerant through channel 58.
  • high pressure compressed refrigerant is substantially blocked from entering the piston chamber 66.
  • the refrigerant in the piston chamber 66 is decreased in pressure by communication between the suction plenum 38 and piston chamber 66 (through channels 58A and 58B) and by a bleed orifice 80 which allows the refrigerant to bleed in one direction from the piston chamber 66 back into the channel 58.
  • the pressure exerted on the valve piston 68 is insufficient to overcome the bias of the bias spring 76 ( FIG 2B ).
  • the bias spring 76 moves the valve piston 68 and valve body 74 within the piston chamber 66 and suction plenum 38 to a position which substantially halts the flow of refrigerant through the suction plenum 38 between the valve body 74 and the suction cutoff wall 62 ( FIG. 2B ).
  • the configuration and arrangement of the valve body 74 and suction cutoff wall 62 do not allow for the flow of refrigerant to the lower stage cylinder 24L when the suction cutoff valve assembly 14 is in the fully unloaded position ( FIG. 2B ).
  • the manner of rapid cycling and/or alternating the cycling of the valves described herein is equally applicable to any compressor that utilizes valves designed to block and unblock one or more cylinders to alter the flow of refrigerant through the compressor. Additionally, the size of the cylinders may differ in other embodiments of the compressor.
  • This invention applies to compressors operating with different types of refrigerant that can be used to heat, cool, and provide humidity control to a conditioned space. Some of the refrigerant types include, but not limited to R410A, R134a, R404A, CO2, and R22.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Compressor (AREA)
EP10802664.2A 2009-07-20 2010-07-12 Suction cutoff unloader valve for compressor capacity control Active EP2456980B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US22682409P 2009-07-20 2009-07-20
PCT/US2010/041691 WO2011011221A2 (en) 2009-07-20 2010-07-12 Suction cutoff unloader valve for compressor capacity control

Publications (3)

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EP2456980A2 EP2456980A2 (en) 2012-05-30
EP2456980A4 EP2456980A4 (en) 2016-02-24
EP2456980B1 true EP2456980B1 (en) 2019-06-26

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US (1) US20120192583A1 (es)
EP (1) EP2456980B1 (es)
CN (1) CN102472269B (es)
ES (1) ES2734298T3 (es)
HK (1) HK1171063A1 (es)
WO (1) WO2011011221A2 (es)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102021117724A1 (de) 2021-07-08 2023-01-12 Bitzer Kühlmaschinenbau Gmbh Kältemittelverdichterverbund

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10378533B2 (en) 2011-12-06 2019-08-13 Bitzer Us, Inc. Control for compressor unloading system
AT513603B1 (de) 2013-08-08 2014-06-15 Hoerbiger Kompressortech Hold Hubkolbenkompressor mit Kapazitätsregelung
EP2851564A1 (en) 2013-09-23 2015-03-25 Danfoss A/S A method of control of compressors with more than two capacity states
CN107965435A (zh) * 2016-10-20 2018-04-27 上海汽车集团股份有限公司 活塞式空气压缩机、供气系统及车辆
CN109538457B (zh) * 2018-10-10 2020-05-22 珠海格力电器股份有限公司 一种控制压缩机切缸的方法、装置及机组、空调系统
CN112955657B (zh) * 2018-10-31 2023-06-27 山东君睿机械科技有限公司 一种具备高低压功能的家用电器
US11946565B2 (en) 2021-02-25 2024-04-02 Hayward Industries, Inc. Valve assembly
US11137780B1 (en) * 2021-02-25 2021-10-05 Valve Technologies, LLC Fluid distribution manifold
US11579635B2 (en) 2021-04-22 2023-02-14 Hayward Industries, Inc. Systems and methods for controlling operations of a fluid distribution system

Family Cites Families (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4382749A (en) * 1980-11-14 1983-05-10 The Trane Company Reciprocating compressor with integral unloader valve
US4519752A (en) * 1982-09-03 1985-05-28 Applied Power Inc. Control system for a variable displacement pump
US4743168A (en) * 1983-03-25 1988-05-10 Carrier Corporation Variable capacity compressor and method of operating
JP3293357B2 (ja) * 1994-09-09 2002-06-17 株式会社豊田自動織機 往復動型圧縮機
US5695325A (en) * 1995-10-04 1997-12-09 Sperry; Lauren D. Synchronized unloader system and method for a gas compressor
US5768901A (en) * 1996-12-02 1998-06-23 Carrier Corporation Refrigerating system employing a compressor for single or multi-stage operation with capacity control
US6206652B1 (en) * 1998-08-25 2001-03-27 Copeland Corporation Compressor capacity modulation
US6203285B1 (en) * 1998-05-18 2001-03-20 Westinghouse Air Brake Company Compressor intercooler unloader arrangement
US6068447A (en) * 1998-06-30 2000-05-30 Standard Pneumatic Products, Inc. Semi-automatic compressor controller and method of controlling a compressor
DE19918161A1 (de) * 1999-04-22 2000-11-02 Bitzer Kuehlmaschinenbau Gmbh Kältemittelverdichteranlage
JP2007107532A (ja) * 1999-08-04 2007-04-26 Toyota Industries Corp 容量可変型圧縮機の制御弁
US6575710B2 (en) * 2001-07-26 2003-06-10 Copeland Corporation Compressor with blocked suction capacity modulation
AU2002352705A1 (en) * 2001-11-15 2003-06-10 Synapse, Inc. Controlling liquid temperature based on usage history
US20040141852A1 (en) * 2002-12-18 2004-07-22 Emilio Brown Complete capacity control kit for a reciprocating compressor system
DE102005016433A1 (de) 2005-04-05 2006-10-12 Bitzer Kühlmaschinenbau Gmbh Kältemittelverdichter
CN101360943B (zh) * 2005-11-22 2013-07-17 诺格伦公司 带传感器的阀门
CN101568777B (zh) * 2006-12-26 2012-02-15 开利公司 带有排气至吸气旁路的脉宽调制
US7565899B2 (en) * 2007-06-12 2009-07-28 Ford Global Technologies, Llc Engine fueling control during cylinder valve mode transitions

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102021117724A1 (de) 2021-07-08 2023-01-12 Bitzer Kühlmaschinenbau Gmbh Kältemittelverdichterverbund

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ES2734298T3 (es) 2019-12-05
HK1171063A1 (zh) 2013-03-15
CN102472269A (zh) 2012-05-23
EP2456980A4 (en) 2016-02-24
WO2011011221A2 (en) 2011-01-27
EP2456980A2 (en) 2012-05-30
CN102472269B (zh) 2015-12-02
WO2011011221A3 (en) 2011-04-28
US20120192583A1 (en) 2012-08-02

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