US20130232975A1 - Compact energy cycle construction utilizing some combination of a scroll type expander, pump, and compressor for operating according to a rankine, an organic rankine, heat pump, or combined organic rankine and heat pump cycle - Google Patents
Compact energy cycle construction utilizing some combination of a scroll type expander, pump, and compressor for operating according to a rankine, an organic rankine, heat pump, or combined organic rankine and heat pump cycle Download PDFInfo
- Publication number
- US20130232975A1 US20130232975A1 US13/986,349 US201313986349A US2013232975A1 US 20130232975 A1 US20130232975 A1 US 20130232975A1 US 201313986349 A US201313986349 A US 201313986349A US 2013232975 A1 US2013232975 A1 US 2013232975A1
- Authority
- US
- United States
- Prior art keywords
- construction
- expander
- pump
- cycle
- along
- 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.)
- Abandoned
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K13/00—General layout or general methods of operation of complete plants
- F01K13/02—Controlling, e.g. stopping or starting
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C1/00—Rotary-piston machines or engines
- F01C1/02—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F01C1/0207—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
- F01C1/0215—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C1/00—Rotary-piston machines or engines
- F01C1/02—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F01C1/0207—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
- F01C1/0246—Details concerning the involute wraps or their base, e.g. geometry
- F01C1/0269—Details concerning the involute wraps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C11/00—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type
- F01C11/006—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of dissimilar working principle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K11/00—Plants characterised by the engines being structurally combined with boilers or condensers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K11/00—Plants characterised by the engines being structurally combined with boilers or condensers
- F01K11/04—Plants characterised by the engines being structurally combined with boilers or condensers the boilers or condensers being rotated in use
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K13/00—General layout or general methods of operation of complete plants
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K9/00—Plants characterised by condensers arranged or modified to co-operate with the engines
- F01K9/02—Arrangements or modifications of condensate or air pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
- F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
- F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
- F04C18/0269—Details concerning the involute wraps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/008—Hermetic pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/02—Lubrication; Lubricant separation
- F04C29/023—Lubricant distribution through a hollow driving shaft
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/04—Heating; Cooling; Heat insulation
- F04C29/042—Heating; Cooling; Heat insulation by injecting a fluid
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
-
- 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
- F25B3/00—Self-contained rotary compression machines, i.e. with compressor, condenser and evaporator rotating as a single unit
-
- 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
- F25B30/00—Heat pumps
- F25B30/02—Heat pumps of the compression 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
- F25B11/00—Compression machines, plants or systems, using turbines, e.g. gas turbines
- F25B11/02—Compression machines, plants or systems, using turbines, e.g. gas turbines as expanders
- F25B11/04—Compression machines, plants or systems, using turbines, e.g. gas turbines as expanders centrifugal type
Definitions
- the present invention is directed to an energy cycle construction, several rotating components of which are integrated within a compact container housing to share a common shaft along which working fluid transits as the construction operates.
- the container housing is preferably of a generally cylindrical configuration with some combination of a scroll type expander, pump, and compressor disposed therein to form an integrated system, with the working fluid of the system circulating about a torus in the poloidal direction.
- the assembled construction may operate generally as or in accordance with a Rankine Cycle, an Organic Rankine Cycle (ORC), a Heat Pump Cycle, a air conditioning or refrigeration cycle, or a Combined Organic Rankine and Heat Pump or refrigeration Cycle.
- ORC Organic Rankine Cycle
- Heat Pump Cycle a heat Pump Cycle
- air conditioning or refrigeration cycle a Combined Organic Rankine and Heat Pump or refrigeration Cycle.
- Such energy cycle constructions may take many forms, it has been found advantageous in many instances to employ multiple rotating components as components of such energy cycle constructions to effect the desired energy cycles while realizing advantages attendant to the use of such rotating components.
- Such rotating components may include not only rotary equipment such as generators and motors, but also other rotary devices such as expanders, pumps, and compressors, as well as scroll type devices that include both compressor and expander functions such as are disclosed in U.S. Provisional Patent Application Ser. No. 61/574,771, filed Aug. 9, 2011 (DN8108).
- working fluid treatment devices For convenience of further reference, such other rotary devices and the like are often hereinafter referred to generically as working fluid treatment devices, and reference to energy cycle devices is intended to encompass motors and generators and like equipment in addition to working fluid treatment devices, especially as they may be utilized in energy cycle constructions.
- This invention has thus been developed to result in a more compact, lower cost, and more reliable energy cycle construction.
- the resulting construction integrates system components into a closed, preferably cylindrical, container housing, sometimes hereinafter referred to more simply as the container, within which container housing the working fluid flows about a torus in the poloidal direction.
- the rotary working fluid treatment devices utilize a scroll type design and rotate about a common shaft, with the evaporation and condensing processes being affected while the fluid is in transit between the rotary fluid treatment devices.
- This type of system design can be advantageously used for power generation through the use of a Rankine Cycle or ORC, or can be used for heat pumping through the use of a Refrigeration/Heat Pump Cycle, sometimes hereinafter referred to more simply as a Heat Pump Cycle or a Refrigeration Cycle.
- the word “Scroll” can refer to either the traditional orbiting scroll design, or to what is commonly referred to as a Spinning or Co-rotating scroll design.
- a preferred embodiment employs five (5) major components within the container housing, including an expander, generator, pump, condenser, and evaporator.
- a scroll expander is used to extract power from the working fluid and move it into the condenser, while a scroll liquid pump, or other rotating liquid pump, such as a gear or vane pump, is used to pump the working fluid through the evaporator.
- the pump, expander, and generator are aligned on the same shaft, with the evaporation process occurring inside the shaft and the condensation process occurring along the containment shell of the container housing.
- the end result of such preferred embodiment is the production of electrical energy by moving heat from a high temperature source to a low temperature source.
- refrigerant can be used as the working fluid to extract heat from a variety of waste heat applications, such as solar power, geothermal, or waste heat from power production or manufacturing processes.
- waste heat applications such as solar power, geothermal, or waste heat from power production or manufacturing processes.
- steam can be used as the working fluid to extract heat from burning fossil fuels or high temperature geothermal.
- a preferred embodiment also employs five (5) major components within the container housing, including a compressor, motor, expander, condenser, and evaporator, although the expander could be replaced with a capillary tube or expansion valve as used in a traditional heat pump/refrigeration cycle.
- a scroll compressor is used to compress the working fluid from the evaporator and to supply it to the condenser
- a scroll expander is used to expand the liquid from the condenser and to supply it as a two-phase gas to the evaporator.
- the expander, compressor, and motor are located on the same shaft, with the condensation process occurring inside the shaft and the evaporation process occurring along the containment shell of the container housing.
- the end result of such preferred embodiment is the use of electrical energy to move heat from a low temperature source to a high temperature source.
- refrigerant can be used as the working fluid to move heat from ambient air to a heated area.
- refrigerant can be used to remove heat from a cooled area to the ambient air.
- Another system variation can be readily realized through the integration into a common construction of both an ORC and a refrigeration cycle, with the ORC being utilized to power the refrigeration cycle.
- ORC being utilized to power the refrigeration cycle.
- a generator excess power generated from ORC
- motor deficiency in power generation from ORC
- a preferred form of such system includes six (6) major components within the container housing, including a compressor-expander, a motor/generator, a pump-expander, high and low pressure evaporator portions, and a condenser, certain components of which may be designed to operate in accordance with U.S. Provisional Patent Application Ser. No. 61/574,771, filed Aug. 9, 2011 (DN8108).
- the compressor-expander has two functions: on the outer portion of such compressor-expander refrigerant from the low pressure evaporator is compressed to be provided to the intermediate pressure condenser; on the inner portion of such compressor-expander refrigerant from the high pressure evaporator is expanded to be provided to the intermediate pressure condenser.
- the pump-expander also has two functions: on the outer portion of such pump-expander liquid refrigerant from the intermediate pressure condenser is expanded to be provided to the low pressure evaporator; on the inner portion of the pump-expander the liquid refrigerant from the intermediate pressure condenser is pumped to the high pressure evaporator.
- the compressor-expander, motor/generator, and pump-expander are all located on the same shaft.
- the high pressure evaporation process occurs inside the hollow shaft while the intermediate pressure condensation process occurs along the inside of the containment shell.
- the low pressure evaporation process occurs in an evaporator external to the containment shell inside a cooled space.
- the present invention may thus be encompassed within and practiced by various constructions that incorporate all the rotary components within a single container housing, including systems such as the three (3) unique, preferred constructions noted hereinabove.
- Such design decreases the risk of refrigerant leakage, reduces overall system cost, due to the integration of components, and simplifies the energy cycle, which increases reliability, by eliminating all piping between components.
- FIG. 1 depicts a preferred embodiment of the present invention incorporated within a compact housing, operating as or in accordance with a Rankine Cycle or Organic Rankine Cycle (ORC);
- ORC Organic Rankine Cycle
- FIG. 2 depicts a preferred embodiment of the present invention as incorporated within a compact housing, operating as or in accordance with a Heat Pump or Refrigeration Cycle;
- FIGS. 3 and 4 depict a preferred embodiment of the present invention as incorporated within a compact housing, operating as or in accordance with a Combined Refrigeration and Organic Rankine Cycle (ORC);
- ORC Combined Refrigeration and Organic Rankine Cycle
- FIG. 5 shows a preferred housing fin configuration that can optionally be employed with the embodiments of FIGS. 1-4 ;
- FIG. 6 shows several rotating shaft fin configurations that can be optionally employed with hollow shaft components such as are employed with the preferred embodiments of FIGS. 1-3 .
- FIG. 1 depicts an embodiment according to the present invention, operating as or in accordance with a Rankine Cycle or Organic Rankine Cycle, with components and features of such embodiment having the identification symbols as set forth in the following Table 1:
- FIG. 1 Identifiers Identifier Item Description Components (Alphabetized circles) A Orbiting portion of the orbital scroll expander, or driving portion of a co-rotating scroll expander B Fixed portion of the orbital scroll expander, or driven portion of a co-rotating scroll expander C Scroll expander Outlet D Insulation/sealing between condenser and rotating equipment E Scroll pump inlet F Driving portion of a co-rotating scroll pump G Driven portion of a co-rotating scroll pump H Scroll pump outlet I Hollow rotating shaft connecting pump to expander J Generator rotor K Generator stator L Heat transfer fins transferring heat between (I) and (N) M Heat source fluid inlet N Spiral fluid path for heat source fluid O Heat source fluid outlet P Scroll expander inlet Q Containment shell housing all components (can include fins on outside) State Points between Components (Numbered Squares) 1 Low pressure liquid refrigerant after condensation and before pumping 2 High pressure liquid refrigerant after pumping and before evaporation
- the scroll expander of FIG. 1 thus comprises the components marked therein by the identification symbols circled-A through circled-C and circle-P, that the scroll pump comprises circled-F through circled-H, and that the generator comprises circled-J through circled-K.
- the pumping process, marked or designated in FIG. 1 and by the foregoing as Orange occurs between numbered-square- and numbered-square- 2 ; that the evaporation process, marked or designated in FIG. 1 and by the foregoing as Red, occurs between numbered-square- 2 and numbered-square- 3 ; that the expansion process, marked or designated in FIG.
- the scroll expander operates to extract power from the working fluid provided thereto at numbered-square- 3 and to move the working fluid into the condenser, as at numbered-square- 4
- the scroll liquid pump operates to pump the working fluid provided from the condenser at numbered-square- 1 to the evaporator at numbered-square- 2 and through the evaporator to numbered-suare- 3
- the pump, expander, and generator are aligned on the same shaft, with the evaporation process occurring inside the shaft and the condensation process occurring along the containment shell of the container housing.
- the end result of such preferred embodiment is the production of electrical energy by moving heat from a high temperature source to a low temperature source.
- FIG. 2 depicts a preferred embodiment of the present invention, operating as or in accordance with a Heat Pump or Refrigeration Cycle, with components of such embodiment having the identification symbols as set forth in the following Table 2:
- FIG. 2 Identifiers Identifier Item Description Components (Alphabetized circles) A Orbiting portion of an orbital scroll compressor, or driving portion of a co-rotating scroll compressor B Fixed portion of an orbital scroll compressor, or driven portion of a co-rotating scroll compressor C Scroll compressor inlet D Insulation/sealing between evaporator and rotating equipment E Scroll liquid expander outlet F Driving portion of a co-rotating scroll liquid expander, or capillary tube or expansion valve G Driven portion of a co-rotating scroll liquid expander H Scroll liquid expander inlet I Hollow rotating shaft connecting compressor to liquid expander J Motor rotor K Motor stator L Heat transfer fins transferring heat between (I) and (N) M Heat sink fluid inlet N Spiral fluid path for heat sink fluid O Heat sink fluid outlet P Scroll compressor outlet Q Containment shell housing all components (can include fins on outside) State Points between Components (Numbered Squares) 1 Low pressure refrigerant gas after evaporation and before compression 2 High pressure
- the scroll compressor of FIG. 2 thus comprises the components marked therein by the identification symbols circled-A through circled-C and circle-P, that the scroll expander comprises circled-F through circled-H, and that the motor comprises circled-J through circled-K.
- the expansion process, marked or designated in FIG. 2 and by the foregoing as Orange occurs between numbered-square- 3 and numbered-square- 4 ; that the evaporation process, marked or designated in FIG. 2 and by the foregoing as Red, occurs between numbered-square- 4 and numbered-square- 1 ; that the compression process, marked or designated in FIG.
- the scroll compressor operates to compress the working fluid provided thereto from the evaporator at numbered-square- 1 and to move the working fluid into the condenser, as at numbered-square- 2
- the scroll expander operates to expand the working fluid provided as a liquid from the condenser at numbered-square- 3 and to provide it to the evaporator at numbered-square- 4 as a two-phase gas.
- the expander, compressor, and motor are aligned on the same shaft, with the condensation process occurring inside the shaft and the evaporation process occurring along the containment shell of the container housing.
- the end result of such preferred embodiment is the use of electrical energy to move heat from a low temperature source to a high temperature source.
- refrigerant can be used as the working fluid to move heat from ambient air to a heated area.
- refrigerant can be used to remove heat from a cooled area to the ambient air.
- FIGS. 3 and 4 depict a preferred embodiment of the present invention as incorporated within a compact housing, operating as or in accordance with a Combined Refrigeration and Organic Rankine Cycle, with components of such embodiment having the identification symbols as set forth in the following Table 3:
- FIGS. 3 and 4 Identifiers Identifier Item Description Components (Alphabetized circles)
- E Scroll pump-expander inlet
- F1 Rotating pump portion of the scroll pump-expander G1 Fixed pump portion of the scroll pump-expander
- F2 Rotating expander portion of the scroll pump-expander G2 Fixed expander portion of the scroll pump-expander H1 Scroll pump outlet or the pump-expander H2 Scroll expander outlet or the pump-expander
- the scroll compressor-expander of FIGS. 3-4 which may take a form as disclosed in U.S. Provisional Patent Application Ser. No. 61/574,771, filed Aug. 9, 2011 (DN8108), thus comprises the components marked therein by the identification symbols circled-A 1 through circled-B 1 , circled-A 2 through circled-B 2 , circled-C, and circled-P 1 through circled P 2 ; that the scroll pump-expander, which may also take a form as disclosed in U.S. Provisional Patent Application Ser. No. 61/574,771, filed Aug. 9, 2011 (DN8108), comprises circled-F 1 through circled-H 1 and circled-F 2 through circled-H 2 ; and that the generator/motor comprises circled-J through circled-K.
- the outer portion of the pump-expander of FIG. 3 operates to expand liquid refrigerant provided at numbered-square- 1 from the intermediate pressure condenser and to provide such expanded refrigerant at numbered-square- 2 b to the low pressure evaporator ( FIG. 4 ), while the inner portion of such pump-expander operates to pump the liquid refrigerant provided thereto at numbered-square- 1 to the high pressure evaporator at numbered-square- 2 a .
- the manner in which both of such operations are affected by the pump-expander of FIG. 3 is also explained in greater detail in U.S. Provisional Patent Application Ser. No. 61/574,771, filed Aug. 9, 2011 (DN8108), which is incorporated herein by reference thereto.
- the compressor-expander, motor/generator, and pump-expander are all located on the same shaft.
- the high pressure evaporation process occurs inside the hollow shaft while the intermediate pressure condensation process occurs along the inside of the containment shell.
- the low pressure evaporation process occurs in an evaporator component shell inside a cooled space, which may typically be located external to the containment, such as shown in FIG. 4 , but which could also, with some redesign and/or segmentation of the areas within the containment shell between the outer housing circled-Q and the insulation circled-D, be included within such outer housing.
- FIG. 5 shows a preferred housing fin configuration that can optionally be employed with the embodiments of FIGS. 1-4 , with components thereof having the identification symbols as set forth in the following Table 4:
- FIG. 5 Identifiers for Housing Fin Configuration Identifier Item Description Components (Alphabetized circles) A External horizontal fins attached to the containment shell (C) B Spiral fin between the inside wall of the containment shell (C) and the Insulation/sealing wall (D) C Containment Shell D Separation/sealing wall
- FIG. 5 shows a fin array construction in which a number of fins of a straight vertical fin configuration are disposed generally radially about the generally cylindrical containment shell circled-C, any suitable fin geometry/configuration could be utilized to optimize heat transfer.
- an external fan system (not shown) could optionally be included on the outside to add forced convection across the fin array.
- a large spiral fin circled-B could also be added to the inside wall of the containment shell circled-C of FIG. 5 .
- such fin is presented in FIG. 5 as being one fin having a spiral fin configuration, any fin geometry/configuration could be used to optimize heat transfer.
- FIG. 6 shows several rotating shaft fin configurations that can be optionally employed with hollow shaft components such as are employed with the preferred embodiments of FIGS. 1-3 , with the components thereof having the identification symbols as set forth in the following Table 5:
- FIG. 6 Identifiers for Rotating Shaft Fin Configuration Identifier Item Description Components A Spiral fin spanning the entire length of the rotating shaft B Offset fins spanning the entire length of the rotating shaft
- a spiral fin system or channel can also optionally be added inside the hollow shaft in order to increase heat transfer surface area.
- Such fin systems can take various forms, including the two preferred, alternative configurations depicted in FIG. 6 as Configurations A and B.
- the fin system of Configuration A includes one spiral fin along the entire length while the fin system of Configuration B includes a series of offset fins.
- the low pressure evaporator of a set of both external and internal fins, depicted as components circled-T and circled-U in FIG. 4 , to increase surface area.
- Such fins can be any configuration/geometry to optimize heat transfer. It is envisioned that, in at least some instances, an off the shelf evaporator could be used as the external low pressure evaporator component.
- the expander of FIG. 2 could be replaced with a capillary tube. Although such a substitution would lower overall efficiency, it would lower system cost substantially.
- the expander component in the pump-expander of FIG. 3 could be replaced with a capillary tube to decrease system cost.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Geometry (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Rotary Pumps (AREA)
Abstract
A compact energy cycle construction that operates as or in accordance with a Rankine, Organic Rankine, Heat Pump, or Combined Organic Rankine and Heat Pump Cycle, comprising a compact housing of a generally cylindrical form with some combination of a scroll type expander, pump, and compressor disposed therein to share a common shaft with a motor or generator and to form an integrated system, with the working fluid of the system circulating within the housing as a torus along the common shaft and toroidally within the housing as the system operates.
Description
- This patent application claims priority to the provisional patent application having Ser. No. 61/687,464, filed on Apr. 25, 2012, which claims priority as a continuation-in-part patent application to the patent application having Ser. No. 13/507,779, filed on Jul. 30, 2012, now Publication No. US 2013-0036762 A1, which claims priority to the provisional patent application having Ser. No. 61/574,771, filed Aug. 9, 2011, now expired.
- The present invention is directed to an energy cycle construction, several rotating components of which are integrated within a compact container housing to share a common shaft along which working fluid transits as the construction operates.
- The container housing is preferably of a generally cylindrical configuration with some combination of a scroll type expander, pump, and compressor disposed therein to form an integrated system, with the working fluid of the system circulating about a torus in the poloidal direction.
- The assembled construction may operate generally as or in accordance with a Rankine Cycle, an Organic Rankine Cycle (ORC), a Heat Pump Cycle, a air conditioning or refrigeration cycle, or a Combined Organic Rankine and Heat Pump or refrigeration Cycle.
- Rankine Cycles, Organic Rankine Cycles (ORC), and Refrigeration/Heat Pump Cycles are well known, and many systems of various designs have been developed over the years to operate in accordance with such cycles. For convenience of further reference, such cycles will often hereinafter be referred to generically as energy cycles. Principles of operation of such energy cycles have been addressed in detail in numerous prior publications, and operations of various systems in accordance with such energy cycles are also explained in numerous prior art publications. For convenience of further reference, such systems or constructions are often hereinafter referred to as energy cycle constructions.
- Although such energy cycle constructions may take many forms, it has been found advantageous in many instances to employ multiple rotating components as components of such energy cycle constructions to effect the desired energy cycles while realizing advantages attendant to the use of such rotating components. Such rotating components may include not only rotary equipment such as generators and motors, but also other rotary devices such as expanders, pumps, and compressors, as well as scroll type devices that include both compressor and expander functions such as are disclosed in U.S. Provisional Patent Application Ser. No. 61/574,771, filed Aug. 9, 2011 (DN8108). For convenience of further reference, such other rotary devices and the like are often hereinafter referred to generically as working fluid treatment devices, and reference to energy cycle devices is intended to encompass motors and generators and like equipment in addition to working fluid treatment devices, especially as they may be utilized in energy cycle constructions.
- Many energy cycle constructions are thus configured to operate as or in accordance with a Rankine Cycle, an Organic Rankine Cycle (ORC), and/or a Refrigeration/Heat Pump Cycle, and to employ one or more, and often two, rotary working fluid treatment devices, often of a scroll type design, as part of their systems. Generally, many such rotary based energy cycle constructions share a common set up in that they include two rotary working fluid treatment devices as well as an evaporator and condenser, and a motor or generator. Typically, such energy cycle constructions are constructed with the individual components thereof interconnected to form the completed system, but with each of such individual components existing as a separate independent component in a closed loop connected via piping. Due to the independence and separateness of such components, such completed or assembled energy cycle constructions have necessarily been of larger size.
- For many reasons, it would generally be desirable if the sizes, and cost of such energy cycle constructions could be decreased or minimized, and the reliability improved. To this point in time, however, that desire has remained largely unsatisfied.
- This invention has thus been developed to result in a more compact, lower cost, and more reliable energy cycle construction. The resulting construction integrates system components into a closed, preferably cylindrical, container housing, sometimes hereinafter referred to more simply as the container, within which container housing the working fluid flows about a torus in the poloidal direction. The rotary working fluid treatment devices utilize a scroll type design and rotate about a common shaft, with the evaporation and condensing processes being affected while the fluid is in transit between the rotary fluid treatment devices. This type of system design can be advantageously used for power generation through the use of a Rankine Cycle or ORC, or can be used for heat pumping through the use of a Refrigeration/Heat Pump Cycle, sometimes hereinafter referred to more simply as a Heat Pump Cycle or a Refrigeration Cycle.
- In the following explanation of the invention, the word “Scroll” can refer to either the traditional orbiting scroll design, or to what is commonly referred to as a Spinning or Co-rotating scroll design.
- For power generation, a preferred embodiment employs five (5) major components within the container housing, including an expander, generator, pump, condenser, and evaporator. A scroll expander is used to extract power from the working fluid and move it into the condenser, while a scroll liquid pump, or other rotating liquid pump, such as a gear or vane pump, is used to pump the working fluid through the evaporator. The pump, expander, and generator are aligned on the same shaft, with the evaporation process occurring inside the shaft and the condensation process occurring along the containment shell of the container housing. The end result of such preferred embodiment is the production of electrical energy by moving heat from a high temperature source to a low temperature source.
- For an ORC, refrigerant can be used as the working fluid to extract heat from a variety of waste heat applications, such as solar power, geothermal, or waste heat from power production or manufacturing processes. For a Rankine Cycle, steam can be used as the working fluid to extract heat from burning fossil fuels or high temperature geothermal.
- For heat pumping/refrigeration, a preferred embodiment also employs five (5) major components within the container housing, including a compressor, motor, expander, condenser, and evaporator, although the expander could be replaced with a capillary tube or expansion valve as used in a traditional heat pump/refrigeration cycle. A scroll compressor is used to compress the working fluid from the evaporator and to supply it to the condenser, while a scroll expander is used to expand the liquid from the condenser and to supply it as a two-phase gas to the evaporator. The expander, compressor, and motor are located on the same shaft, with the condensation process occurring inside the shaft and the evaporation process occurring along the containment shell of the container housing. The end result of such preferred embodiment is the use of electrical energy to move heat from a low temperature source to a high temperature source.
- For a heat pump cycle, refrigerant can be used as the working fluid to move heat from ambient air to a heated area. For a refrigeration cycle, refrigerant can be used to remove heat from a cooled area to the ambient air.
- Another system variation can be readily realized through the integration into a common construction of both an ORC and a refrigeration cycle, with the ORC being utilized to power the refrigeration cycle. Depending upon the net power difference, either a generator (excess power generated from ORC) or motor (deficiency in power generation from ORC) or combination motor and generator can be used. A preferred form of such system includes six (6) major components within the container housing, including a compressor-expander, a motor/generator, a pump-expander, high and low pressure evaporator portions, and a condenser, certain components of which may be designed to operate in accordance with U.S. Provisional Patent Application Ser. No. 61/574,771, filed Aug. 9, 2011 (DN8108).
- In such system, the compressor-expander has two functions: on the outer portion of such compressor-expander refrigerant from the low pressure evaporator is compressed to be provided to the intermediate pressure condenser; on the inner portion of such compressor-expander refrigerant from the high pressure evaporator is expanded to be provided to the intermediate pressure condenser. The pump-expander also has two functions: on the outer portion of such pump-expander liquid refrigerant from the intermediate pressure condenser is expanded to be provided to the low pressure evaporator; on the inner portion of the pump-expander the liquid refrigerant from the intermediate pressure condenser is pumped to the high pressure evaporator. The compressor-expander, motor/generator, and pump-expander are all located on the same shaft. The high pressure evaporation process occurs inside the hollow shaft while the intermediate pressure condensation process occurs along the inside of the containment shell. The low pressure evaporation process occurs in an evaporator external to the containment shell inside a cooled space.
- The present invention may thus be encompassed within and practiced by various constructions that incorporate all the rotary components within a single container housing, including systems such as the three (3) unique, preferred constructions noted hereinabove. Such design decreases the risk of refrigerant leakage, reduces overall system cost, due to the integration of components, and simplifies the energy cycle, which increases reliability, by eliminating all piping between components.
- In addition, the unique design of such systems increases system efficiency and decreases system complexity, including by placing all the rotating equipment on a single shaft. For a refrigeration/heat pump cycle the design increases efficiency by replacing an expansion valve with an expander to recover power in the expansion process.
- Although the preferred construction is described here, it may be necessary in some cases to place some of the components discretely in some ORC, heat pump and refrigeration cycle applications. Such alternate configurations are obvious and included herein.
- In referring to the drawings:
-
FIG. 1 depicts a preferred embodiment of the present invention incorporated within a compact housing, operating as or in accordance with a Rankine Cycle or Organic Rankine Cycle (ORC); -
FIG. 2 depicts a preferred embodiment of the present invention as incorporated within a compact housing, operating as or in accordance with a Heat Pump or Refrigeration Cycle; -
FIGS. 3 and 4 depict a preferred embodiment of the present invention as incorporated within a compact housing, operating as or in accordance with a Combined Refrigeration and Organic Rankine Cycle (ORC); -
FIG. 5 shows a preferred housing fin configuration that can optionally be employed with the embodiments ofFIGS. 1-4 ; and -
FIG. 6 shows several rotating shaft fin configurations that can be optionally employed with hollow shaft components such as are employed with the preferred embodiments ofFIGS. 1-3 . - With reference now to the drawings, where like identification symbols in any given figure refer to like items, but where such identification symbols may vary from figure to figure,
FIG. 1 depicts an embodiment according to the present invention, operating as or in accordance with a Rankine Cycle or Organic Rankine Cycle, with components and features of such embodiment having the identification symbols as set forth in the following Table 1: -
TABLE 1 FIG. 1 Identifiers Identifier Item Description Components (Alphabetized circles) A Orbiting portion of the orbital scroll expander, or driving portion of a co-rotating scroll expander B Fixed portion of the orbital scroll expander, or driven portion of a co-rotating scroll expander C Scroll expander Outlet D Insulation/sealing between condenser and rotating equipment E Scroll pump inlet F Driving portion of a co-rotating scroll pump G Driven portion of a co-rotating scroll pump H Scroll pump outlet I Hollow rotating shaft connecting pump to expander J Generator rotor K Generator stator L Heat transfer fins transferring heat between (I) and (N) M Heat source fluid inlet N Spiral fluid path for heat source fluid O Heat source fluid outlet P Scroll expander inlet Q Containment shell housing all components (can include fins on outside) State Points between Components (Numbered Squares) 1 Low pressure liquid refrigerant after condensation and before pumping 2 High pressure liquid refrigerant after pumping and before evaporation 3 High pressure refrigerant gas, after evaporation and before expansion 4 Low pressure single or two phase refrigerant gas after expansion before condensation Processes (Colored broken lines) Orange Pumping process Red Evaporation process Green Expansion process Blue Condensation process - From the foregoing, it should be apparent to those skilled in the art that the scroll expander of
FIG. 1 thus comprises the components marked therein by the identification symbols circled-A through circled-C and circle-P, that the scroll pump comprises circled-F through circled-H, and that the generator comprises circled-J through circled-K. It should be further apparent that the pumping process, marked or designated inFIG. 1 and by the foregoing as Orange, occurs between numbered-square- and numbered-square-2; that the evaporation process, marked or designated inFIG. 1 and by the foregoing as Red, occurs between numbered-square-2 and numbered-square-3; that the expansion process, marked or designated inFIG. 1 and by the foregoing as Green, occurs between numbered-square-3 and numbered-square-4; and that the condensation process, marked or designated inFIG. 1 and by the foregoing as Blue, occurs between numbered-square-1 and numbered-square-2. The design and operation of individual components of such construction are well known and those skilled in the art will appreciate and understood fromFIGS. 1 , 5, and 6, and from the Tables associated therewith and the discussions hereinabove, how the various components are connected to one another to be operable and integrated within a common container, with various rotating components sharing a common shaft through which the working fluid flows while transiting between certain of the component devices. - The scroll expander operates to extract power from the working fluid provided thereto at numbered-square-3 and to move the working fluid into the condenser, as at numbered-square-4, while the scroll liquid pump operates to pump the working fluid provided from the condenser at numbered-square-1 to the evaporator at numbered-square-2 and through the evaporator to numbered-suare-3. The pump, expander, and generator are aligned on the same shaft, with the evaporation process occurring inside the shaft and the condensation process occurring along the containment shell of the container housing. The end result of such preferred embodiment is the production of electrical energy by moving heat from a high temperature source to a low temperature source.
-
FIG. 2 depicts a preferred embodiment of the present invention, operating as or in accordance with a Heat Pump or Refrigeration Cycle, with components of such embodiment having the identification symbols as set forth in the following Table 2: -
TABLE 2 FIG. 2 Identifiers Identifier Item Description Components (Alphabetized circles) A Orbiting portion of an orbital scroll compressor, or driving portion of a co-rotating scroll compressor B Fixed portion of an orbital scroll compressor, or driven portion of a co-rotating scroll compressor C Scroll compressor inlet D Insulation/sealing between evaporator and rotating equipment E Scroll liquid expander outlet F Driving portion of a co-rotating scroll liquid expander, or capillary tube or expansion valve G Driven portion of a co-rotating scroll liquid expander H Scroll liquid expander inlet I Hollow rotating shaft connecting compressor to liquid expander J Motor rotor K Motor stator L Heat transfer fins transferring heat between (I) and (N) M Heat sink fluid inlet N Spiral fluid path for heat sink fluid O Heat sink fluid outlet P Scroll compressor outlet Q Containment shell housing all components (can include fins on outside) State Points between Components (Numbered Squares) 1 Low pressure refrigerant gas after evaporation and before compression 2 High pressure refrigerant gas after compression and before condensation 3 High pressure liquid refrigerant after condensation and before expansion 4 Low pressure two phase refrigerant gas after expansion before evaporation Processes (Colored broken lines) Orange Expansion process Red Evaporation process Green Compression process Blue Condensation process - From the foregoing, it should be apparent to those skilled in the art that the scroll compressor of
FIG. 2 thus comprises the components marked therein by the identification symbols circled-A through circled-C and circle-P, that the scroll expander comprises circled-F through circled-H, and that the motor comprises circled-J through circled-K. It should be further apparent that the expansion process, marked or designated inFIG. 2 and by the foregoing as Orange, occurs between numbered-square-3 and numbered-square-4; that the evaporation process, marked or designated inFIG. 2 and by the foregoing as Red, occurs between numbered-square-4 and numbered-square-1; that the compression process, marked or designated inFIG. 2 and by the foregoing as Green, occurs between numbered-square-1 and numbered-square-2; and that the condensation process, marked or designated inFIG. 2 and by the foregoing as Blue, occurs between numbered-square-2 and numbered-square-3. The design and operation of individual components of such construction are well known and those skilled in the art will appreciate and understood fromFIGS. 2 , 5, and 6, and from the Tables associated therewith and the discussions hereinabove, how the various components are connected to one another to be operable and integrated within a common container, with various rotating components sharing a common shaft through which the working fluid flows while transiting between certain of the component devices. - The scroll compressor operates to compress the working fluid provided thereto from the evaporator at numbered-square-1 and to move the working fluid into the condenser, as at numbered-square-2, while the scroll expander operates to expand the working fluid provided as a liquid from the condenser at numbered-square-3 and to provide it to the evaporator at numbered-square-4 as a two-phase gas. The expander, compressor, and motor are aligned on the same shaft, with the condensation process occurring inside the shaft and the evaporation process occurring along the containment shell of the container housing. The end result of such preferred embodiment is the use of electrical energy to move heat from a low temperature source to a high temperature source. For a heat pump cycle, refrigerant can be used as the working fluid to move heat from ambient air to a heated area. For a refrigeration cycle, refrigerant can be used to remove heat from a cooled area to the ambient air.
-
FIGS. 3 and 4 depict a preferred embodiment of the present invention as incorporated within a compact housing, operating as or in accordance with a Combined Refrigeration and Organic Rankine Cycle, with components of such embodiment having the identification symbols as set forth in the following Table 3: -
TABLE 3 FIGS. 3 and 4 Identifiers Identifier Item Description Components (Alphabetized circles) A1 Rotating or orbital expander portion of the scroll compressor-expander B1 Fixed or co-rotating expander portion of the scroll compressor-expander A2 Rotating or orbital compressor portion of the scroll compressor-expander B2 Fixed or co-rotating compressor portion of the scroll compressor-expander C Scroll compressor-expander outlet D Insulation/sealing between condenser and rotating equipment E Scroll pump-expander inlet F1 Rotating pump portion of the scroll pump-expander G1 Fixed pump portion of the scroll pump-expander F2 Rotating expander portion of the scroll pump-expander G2 Fixed expander portion of the scroll pump-expander H1 Scroll pump outlet or the pump-expander H2 Scroll expander outlet or the pump-expander I Hollow rotating shaft connecting pump-expander to compressor-expander J Generator/motor rotor K Generator/motor stator L Heat transfer fins transferring heat between (I) and (N) M Heat source fluid inlet N Spiral fluid path for heat source fluid O Heat source fluid outlet P1 Scroll expander inlet of the compressor-expander P2 Scroll compressor inlet of the compressor-expander Q Containment shell housing all components (can included fins on outside) R1 Insulation/sealing between compressor inlet and condensation process R2 Insulation/sealing between expander outlet and condensation process S Low pressure evaporator T Low pressure evaporator external fin configuration U Low pressure evaporator internal spiral fin configuration State Points between Components (Numbered Squares) 1 Intermediate pressure liquid refrigerant after condensation and before pumping or expansion 2a High pressure liquid refrigerant after pumping and before high pressure evaporation 2b Low pressure two phase refrigerant gas after expansion and before low pressure evaporation 3a High pressure refrigerant gas after high pressure evaporation and before expansion 3b Low pressure refrigerant gas after low pressure evaporation and before compression 4 Low pressure refrigerant gas after expansion or compression and before condensation Processes (Colored broken/solid lines) Orange Intermediate pressure to high pressure pumping process (broken line) Red (broken High pressure evaporation process line) Green High pressure to intermediate pressure expansion (broken line) process Blue (broken Intermediate condensation process line) Green (solid Intermediate pressure to low pressure expansion line) Red (solid Low pressure evaporation process line) Orange (solid Low pressure to intermediate pressure compression line) - From the foregoing, it should be apparent to those skilled in the art that the scroll compressor-expander of
FIGS. 3-4 , which may take a form as disclosed in U.S. Provisional Patent Application Ser. No. 61/574,771, filed Aug. 9, 2011 (DN8108), thus comprises the components marked therein by the identification symbols circled-A1 through circled-B1, circled-A2 through circled-B2, circled-C, and circled-P1 through circled P2; that the scroll pump-expander, which may also take a form as disclosed in U.S. Provisional Patent Application Ser. No. 61/574,771, filed Aug. 9, 2011 (DN8108), comprises circled-F1 through circled-H1 and circled-F2 through circled-H2; and that the generator/motor comprises circled-J through circled-K. - It should be further apparent that the intermediate pressure to high pressure pumping process, marked or designated in
FIG. 3 and by the foregoing as Orange (broken line), occurs between numbered-square-1 and numbered-square-2 a; that the high pressure evaporation process, marked or designated inFIG. 3 and by the foregoing as Red (broken line), occurs between numbered-square-2 a and numbered-square-3 a; that the high pressure to intermediate pressure expansion process, marked or designated inFIG. 3 and by the foregoing as Green (broken line), occurs between numbered-square-3 a and numbered-square-4; that the intermediate condensation process, marked or designated inFIG. 3 and by the foregoing as Blue (broken line), occurs between numbered-square-4 and numbered-square 1; that the intermediate pressure to low pressure expansion process, marked or designated inFIG. 3 and by the foregoing as Green (solid line), occurs between numbered-square-1 and numbered-square-2 b; that the low pressure evaporation process, marked or designated inFIGS. 3 and 4 and by the foregoing as Red (solid line), occurs between numbered-square-2 b onFIG. 3 and throughFIG. 4 back to numbered-square-3 b onFIG. 3 ; and that the low pressure to intermediate pressure compression process, marked or designated inFIG. 3 and by the foregoing as Orange (solid line), occurs between numbered-square-3 b and numbered-square-4. - The design and operation of individual components of such construction are known from the prior art and/or from U.S. Provisional Patent Application Ser. No. 61/574,771, filed Aug. 9, 2011 (DN8108), incorporated herein by reference thereto, and those skilled in the art will appreciate and understood from
FIGS. 3-6 , and from the Tables associated therewith and the discussions hereinabove, how the various components are connected to one another to be operable and integrated within a common container, with various rotating components sharing a common shaft through which the working fluid flows while transiting between certain of the component devices. The outer portion of the compressor-expander ofFIG. 3 operates to compress refrigerant provided thereto at numbered-square-3 b onFIG. 3 from the low pressure evaporator ofFIG. 4 and to provide the compressed refrigerant to the intermediate pressure condenser at numbered-square-4 onFIG. 3 , while the inner portion of such compressor-expander operates to expand refrigerant provided thereto at numbered-square-3 a onFIG. 3 from the high pressure evaporator and to provide the expanded refrigerant to the intermediate pressure condenser at numbered-square-4. The manner in which both of such operations are affected by the compressor-expander ofFIG. 3 is explained in greater detail in U.S. Provisional Patent Application Ser. No. 61/574,771, filed Aug. 9, 2011 (DN8108), which is incorporated herein by reference thereto. - Somewhat similarly, the outer portion of the pump-expander of
FIG. 3 operates to expand liquid refrigerant provided at numbered-square-1 from the intermediate pressure condenser and to provide such expanded refrigerant at numbered-square-2 b to the low pressure evaporator (FIG. 4 ), while the inner portion of such pump-expander operates to pump the liquid refrigerant provided thereto at numbered-square-1 to the high pressure evaporator at numbered-square-2 a. The manner in which both of such operations are affected by the pump-expander ofFIG. 3 is also explained in greater detail in U.S. Provisional Patent Application Ser. No. 61/574,771, filed Aug. 9, 2011 (DN8108), which is incorporated herein by reference thereto. - As can be observed from
FIG. 3 , the compressor-expander, motor/generator, and pump-expander are all located on the same shaft. The high pressure evaporation process occurs inside the hollow shaft while the intermediate pressure condensation process occurs along the inside of the containment shell. The low pressure evaporation process occurs in an evaporator component shell inside a cooled space, which may typically be located external to the containment, such as shown inFIG. 4 , but which could also, with some redesign and/or segmentation of the areas within the containment shell between the outer housing circled-Q and the insulation circled-D, be included within such outer housing. -
FIG. 5 shows a preferred housing fin configuration that can optionally be employed with the embodiments ofFIGS. 1-4 , with components thereof having the identification symbols as set forth in the following Table 4: -
TABLE 4 FIG. 5 Identifiers for Housing Fin Configuration Identifier Item Description Components (Alphabetized circles) A External horizontal fins attached to the containment shell (C) B Spiral fin between the inside wall of the containment shell (C) and the Insulation/sealing wall (D) C Containment Shell D Separation/sealing wall - If desired by a user, an optional fin array construction circled-A can be readily added to the outside of the containment shell of
FIG. 5 . AlthoughFIG. 5 shows a fin array construction in which a number of fins of a straight vertical fin configuration are disposed generally radially about the generally cylindrical containment shell circled-C, any suitable fin geometry/configuration could be utilized to optimize heat transfer. In addition, an external fan system (not shown) could optionally be included on the outside to add forced convection across the fin array. - A large spiral fin circled-B could also be added to the inside wall of the containment shell circled-C of
FIG. 5 . Although such fin is presented inFIG. 5 as being one fin having a spiral fin configuration, any fin geometry/configuration could be used to optimize heat transfer. -
FIG. 6 shows several rotating shaft fin configurations that can be optionally employed with hollow shaft components such as are employed with the preferred embodiments ofFIGS. 1-3 , with the components thereof having the identification symbols as set forth in the following Table 5: -
TABLE 5 FIG. 6 Identifiers for Rotating Shaft Fin Configuration Identifier Item Description Components A Spiral fin spanning the entire length of the rotating shaft B Offset fins spanning the entire length of the rotating shaft - A spiral fin system or channel can also optionally be added inside the hollow shaft in order to increase heat transfer surface area. Such fin systems can take various forms, including the two preferred, alternative configurations depicted in
FIG. 6 as Configurations A and B. The fin system of Configuration A includes one spiral fin along the entire length while the fin system of Configuration B includes a series of offset fins. - Various other and additional changes and modifications are also possible. Among the changes and modifications contemplated is the use with the low pressure evaporator of a set of both external and internal fins, depicted as components circled-T and circled-U in
FIG. 4 , to increase surface area. Such fins can be any configuration/geometry to optimize heat transfer. It is envisioned that, in at least some instances, an off the shelf evaporator could be used as the external low pressure evaporator component. - It is also envisioned that, in order to minimize overall cost, the expander of
FIG. 2 could be replaced with a capillary tube. Although such a substitution would lower overall efficiency, it would lower system cost substantially. Similarly, the expander component in the pump-expander ofFIG. 3 could be replaced with a capillary tube to decrease system cost. - In light of all the foregoing, it should thus be apparent to those skilled in the art that there has been shown and described a compact energy cycle construction of a unique design that integrates within a compact container rotating components that share a common shaft along which working fluid transits between rotary working fluid treatment devices to flow toroidally within the container as the construction operates as or in accordance with an energy cycle. However, it should also be apparent that, within the principles and scope of the invention, many changes are possible and contemplated, including in the details, materials, and arrangements of parts which have been described and illustrated to explain the nature of the invention. Thus, while the foregoing description and discussion addresses certain preferred embodiments or elements of the invention, it should further be understood that concepts of the invention, as based upon the foregoing description and discussion, may be readily incorporated into or employed in other embodiments and constructions without departing from the scope of the invention. Accordingly, the following claims are intended to protect the invention broadly as well as in the specific form shown, and all changes, modifications, variations, and other uses and applications which do not depart from the spirit and scope of the invention are deemed to be covered by the invention, which is limited only by the claims which follow.
Claims (29)
1. A compact energy cycle construction that utilizes a working fluid in its operation, comprising:
a compact housing of a generally cylindrical form,
a plurality of energy cycle devices disposed within said housing and interconnected to form an integrated system operable in accordance with an energy cycle, at least two of which energy cycle devices include a rotatable shaft shared thereby as a common shaft, and
said system effecting circulation of the working fluid in a torus within said housing as said system operates.
2. The construction of claim 1 wherein said energy cycle is one of a Rankine Cycle, an Organic Rankine Cycle, a Heat Pump Cycle, or a Combined Heat Pump and Organic Rankine Cycle.
3. The construction of claim 1 wherein said common shaft is hollow and includes a central passageway therethrough for the transit through said hollow shaft of the working fluid.
4. The construction of claim 3 including a heat transfer portion that employs a heat transfer fluid during its operation, said heat transfer portion disposed along said hollow shaft and including a heat transfer fluid conduit spirally wrapped about said hollow shaft, said conduit being spaced outwardly from said hollow shaft to define a space therebetween and having a fluid inlet and a fluid outlet, and heat transfer fins disposed along said hollow shaft and said conduit in the space therebetween.
5. The construction of claim 4 wherein said plurality of energy cycle devices includes a scroll type expander, a generator, and a pump, all sharing said common shaft.
6. The construction of claim 5 wherein said generator is disposed along said common shaft intermediate said expander and said pump.
7. The construction of claim 6 wherein said system operates in accordance with one of a Rankine Cycle or Organic Rankine Cycle.
8. The construction of claim 7 wherein said housing includes an outer working fluid passageway along the inside of said container housing between said expander and said pump, with condensation occurring along said passageway and evaporation occurring along the interior of said hollow shaft as said system operates.
9. The construction of claim 4 wherein said plurality of energy cycle devices includes a scroll type compressor, a motor, and an expander, all sharing said common shaft.
10. The construction of claim 9 wherein said motor is disposed along said common shaft intermediate said compressor and said expander.
11. The construction of claim 10 wherein said system operates in accordance with a Heat Pump Cycle.
12. The construction of claim 11 wherein said housing includes an outer working fluid passageway along the inside of said container housing between said compressor and said expander, with evaporation occurring along said passageway and condensation occurring along the interior of said hollow shaft as said system operates.
13. The construction of claim 4 wherein said plurality of energy cycle devices includes a scroll type compressor-expander, a generator/motor, and a pump-expander, all sharing said common shaft.
14. The construction of claim 13 wherein said generator/motor is disposed along said common shaft intermediate said compressor-expander and said pump-expander.
15. The construction of claim 14 wherein said system operates in accordance with a Combined Refrigeration and Rankine Cycle.
16. The construction of claim 15 wherein said housing includes an outer working fluid passageway along the inside of said container housing between said compressor-expander and said pump-expander, with intermediate condensation occurring along said passageway and high pressure evaporation occurring along the interior of said hollow shaft as said system operates.
17. The construction of claim 16 including a low pressure working fluid passageway construction between said compressor-expander and said pump-expander, said low pressure working fluid passageway construction including a passageway along which low pressure evaporation occurs as said system operates.
18. The construction of claim 17 wherein said low pressure passageway construction is disposed within a cool space and includes an internal spiral fin configuration along said passageway and an external fin configuration along said passageway construction.
19. The construction of claim 4 , wherein said plurality of energy cycle devices includes a scroll type compressor and a motor, sharing said common shaft, and a capillary tube.
20. The construction of claim 19 wherein said system operates in accordance with a Heat Pump Cycle.
21. The construction of claim 4 wherein said plurality of energy cycle devices includes a scroll type compressor-expander and a generator/motor, sharing said common shaft, and a capillary tube.
22. The construction of claim 19 wherein said system operates in accordance with a Combined Refrigeration and Organic Rankine Cycle.
23. The construction of claim 3 . wherein said container housing has an external fin array disposed about the periphery of said container housing.
24. The construction of claim 24 wherein said container housing has a generally cylindrical configuration and said external fin array includes a plurality of fins of a generally straight vertical fin configuration extending generally radially from said container housing.
25. The construction of claim 3 wherein said container housing includes an inner wall surface and an internal fin construction disposed about said inner wall surface.
26. The construction of claim 25 wherein said internal fin construction includes a spiral fin extending along said inner wall surface.
27. The construction of claim 3 including a fin system disposed in and along said central passageway of said hollow shaft.
28. The construction of claim 27 wherein said fin system includes a spiral fin extending along at least a portion of said central passageway.
29. The construction of claim 27 wherein said fin system includes a series of offset fins along at least a portion of said central passageway.
Priority Applications (7)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US13/986,349 US20130232975A1 (en) | 2011-08-09 | 2013-04-23 | Compact energy cycle construction utilizing some combination of a scroll type expander, pump, and compressor for operating according to a rankine, an organic rankine, heat pump, or combined organic rankine and heat pump cycle |
PCT/US2014/000076 WO2014175928A2 (en) | 2013-04-23 | 2014-04-16 | Compact energy cycle construction utilizing some combination of a scroll type expander, pump, and compressor for operating according to a rankine, an organic rankine, heat pump, or combined organic rankine and heat pump cycle |
DE112014002095.8T DE112014002095T5 (en) | 2013-04-23 | 2014-04-16 | Compact energy cycle design using a combination of a hoist expander, pump and compressor operating according to a Rankine temperature scale, a Rankine organic temperature heat pump or a combined organic Rankine temperature and heat pump cycle |
GB1516769.5A GB2527691B (en) | 2013-04-23 | 2014-04-16 | Compact Energy Cycle Construction |
US14/756,594 US9784139B2 (en) | 2011-08-09 | 2015-09-22 | Compact energy cycle construction utilizing some combination of a scroll type expander, pump, and compressor for operating according to a rankine, an organic rankine, heat pump, or combined organic rankine and heat pump cycle |
US15/731,929 US10519815B2 (en) | 2011-08-09 | 2017-08-24 | Compact energy cycle construction utilizing some combination of a scroll type expander, pump, and compressor for operating according to a rankine, an organic rankine, heat pump or combined organic rankine and heat pump cycle |
US15/932,150 US10774690B2 (en) | 2011-08-09 | 2018-02-12 | Compact energy cycle construction utilizing some combination of a scroll type expander, pump, and compressor for operating according to a rankine, an organic rankine, heat pump, or combined organic rankine and heat pump cycle |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US201161574771P | 2011-08-09 | 2011-08-09 | |
US201261687464P | 2012-04-25 | 2012-04-25 | |
US13/507,779 US9074598B2 (en) | 2011-08-09 | 2012-07-30 | Scroll type device including compressor and expander functions in a single scroll plate pair |
US13/986,349 US20130232975A1 (en) | 2011-08-09 | 2013-04-23 | Compact energy cycle construction utilizing some combination of a scroll type expander, pump, and compressor for operating according to a rankine, an organic rankine, heat pump, or combined organic rankine and heat pump cycle |
Related Parent Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US13/507,779 Continuation-In-Part US9074598B2 (en) | 2011-08-09 | 2012-07-30 | Scroll type device including compressor and expander functions in a single scroll plate pair |
Related Child Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US14/756,594 Continuation US9784139B2 (en) | 2011-08-09 | 2015-09-22 | Compact energy cycle construction utilizing some combination of a scroll type expander, pump, and compressor for operating according to a rankine, an organic rankine, heat pump, or combined organic rankine and heat pump cycle |
Publications (1)
Publication Number | Publication Date |
---|---|
US20130232975A1 true US20130232975A1 (en) | 2013-09-12 |
Family
ID=62977683
Family Applications (4)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US13/986,349 Abandoned US20130232975A1 (en) | 2011-08-09 | 2013-04-23 | Compact energy cycle construction utilizing some combination of a scroll type expander, pump, and compressor for operating according to a rankine, an organic rankine, heat pump, or combined organic rankine and heat pump cycle |
US14/756,594 Active 2032-12-04 US9784139B2 (en) | 2011-08-09 | 2015-09-22 | Compact energy cycle construction utilizing some combination of a scroll type expander, pump, and compressor for operating according to a rankine, an organic rankine, heat pump, or combined organic rankine and heat pump cycle |
US15/731,929 Active 2032-10-10 US10519815B2 (en) | 2011-08-09 | 2017-08-24 | Compact energy cycle construction utilizing some combination of a scroll type expander, pump, and compressor for operating according to a rankine, an organic rankine, heat pump or combined organic rankine and heat pump cycle |
US15/932,150 Active 2033-03-07 US10774690B2 (en) | 2011-08-09 | 2018-02-12 | Compact energy cycle construction utilizing some combination of a scroll type expander, pump, and compressor for operating according to a rankine, an organic rankine, heat pump, or combined organic rankine and heat pump cycle |
Family Applications After (3)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US14/756,594 Active 2032-12-04 US9784139B2 (en) | 2011-08-09 | 2015-09-22 | Compact energy cycle construction utilizing some combination of a scroll type expander, pump, and compressor for operating according to a rankine, an organic rankine, heat pump, or combined organic rankine and heat pump cycle |
US15/731,929 Active 2032-10-10 US10519815B2 (en) | 2011-08-09 | 2017-08-24 | Compact energy cycle construction utilizing some combination of a scroll type expander, pump, and compressor for operating according to a rankine, an organic rankine, heat pump or combined organic rankine and heat pump cycle |
US15/932,150 Active 2033-03-07 US10774690B2 (en) | 2011-08-09 | 2018-02-12 | Compact energy cycle construction utilizing some combination of a scroll type expander, pump, and compressor for operating according to a rankine, an organic rankine, heat pump, or combined organic rankine and heat pump cycle |
Country Status (1)
Country | Link |
---|---|
US (4) | US20130232975A1 (en) |
Cited By (15)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN103485850A (en) * | 2013-09-22 | 2014-01-01 | 南京航空航天大学 | Time-sharing power generation/air conditioning integrated system and operating method thereof |
US20160265390A1 (en) * | 2015-03-13 | 2016-09-15 | International Business Machines Corporation | Working fluid for a device, device and method for converting heat into mechanical energy |
US10508543B2 (en) | 2015-05-07 | 2019-12-17 | Air Squared, Inc. | Scroll device having a pressure plate |
US10519815B2 (en) | 2011-08-09 | 2019-12-31 | Air Squared, Inc. | Compact energy cycle construction utilizing some combination of a scroll type expander, pump, and compressor for operating according to a rankine, an organic rankine, heat pump or combined organic rankine and heat pump cycle |
US10683865B2 (en) | 2006-02-14 | 2020-06-16 | Air Squared, Inc. | Scroll type device incorporating spinning or co-rotating scrolls |
US10865793B2 (en) | 2016-12-06 | 2020-12-15 | Air Squared, Inc. | Scroll type device having liquid cooling through idler shafts |
US20210164707A1 (en) * | 2019-12-02 | 2021-06-03 | Wei-Sung WENG | Mechanical device and operating method thereof |
US11047389B2 (en) | 2010-04-16 | 2021-06-29 | Air Squared, Inc. | Multi-stage scroll vacuum pumps and related scroll devices |
US11067080B2 (en) | 2018-07-17 | 2021-07-20 | Air Squared, Inc. | Low cost scroll compressor or vacuum pump |
US11454241B2 (en) | 2018-05-04 | 2022-09-27 | Air Squared, Inc. | Liquid cooling of fixed and orbiting scroll compressor, expander or vacuum pump |
US11473572B2 (en) | 2019-06-25 | 2022-10-18 | Air Squared, Inc. | Aftercooler for cooling compressed working fluid |
US11530703B2 (en) | 2018-07-18 | 2022-12-20 | Air Squared, Inc. | Orbiting scroll device lubrication |
US11885328B2 (en) | 2021-07-19 | 2024-01-30 | Air Squared, Inc. | Scroll device with an integrated cooling loop |
US11898557B2 (en) | 2020-11-30 | 2024-02-13 | Air Squared, Inc. | Liquid cooling of a scroll type compressor with liquid supply through the crankshaft |
US11933299B2 (en) | 2018-07-17 | 2024-03-19 | Air Squared, Inc. | Dual drive co-rotating spinning scroll compressor or expander |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US10228198B2 (en) * | 2016-10-03 | 2019-03-12 | Aleksandr Reshetnyak | Multi-disk heat exchanger and fan unit |
US10570784B2 (en) | 2017-09-22 | 2020-02-25 | Tenneco Gmbh | Rankine power system for use with exhaust gas aftertreatment system |
CN108634537B (en) * | 2018-05-21 | 2021-11-16 | 滕州市裕维电子科技有限公司 | Make things convenient for clear cosmetic mirror of cosmetic mirror |
Citations (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2079118A (en) * | 1935-01-19 | 1937-05-04 | Rheinmetall Borsig Ag | Combined turbine and steam generator |
US2330121A (en) * | 1940-10-04 | 1943-09-21 | Jack & Heintz Inc | Motor cooling system |
US3613368A (en) * | 1970-05-08 | 1971-10-19 | Du Pont | Rotary heat engine |
US4395885A (en) * | 1981-10-08 | 1983-08-02 | Cozby Enterprises, Inc. | Unitary steam engine |
DE19957425A1 (en) * | 1998-12-02 | 2000-08-24 | Gerd Degener | Energy converter for utilising environmental heat energy has heat exchanger and expansion device with eccentric rotor for utilising evaporation and condensation of working medium |
US6464467B2 (en) * | 2000-03-31 | 2002-10-15 | Battelle Memorial Institute | Involute spiral wrap device |
US7124585B2 (en) * | 2002-02-15 | 2006-10-24 | Korea Institute Of Machinery & Materials | Scroll-type expander having heating structure and scroll-type heat exchange system employing the expander |
US20100287954A1 (en) * | 2009-03-25 | 2010-11-18 | Jayden Harman | Supersonic Cooling System |
US8674525B2 (en) * | 2007-07-09 | 2014-03-18 | Universiteit Gent | Combined heat power system |
Family Cites Families (154)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US801182A (en) | 1905-06-26 | 1905-10-03 | Leon Creux | Rotary engine. |
US1022185A (en) | 1909-05-19 | 1912-04-02 | Ethel Mary Elsden | Spool-holder for sewing-machines. |
DE460936C (en) * | 1925-05-05 | 1928-06-11 | Otto Hardung | Ice or cooling machine with rotating evaporator and condenser housings |
GB513827A (en) | 1937-01-06 | 1939-10-23 | American Centrifugal Corp | Improvements in or relating to the treatment and disposal of sewage and like waste material |
US2968157A (en) * | 1956-05-03 | 1961-01-17 | Walter I Cronan | Closed circuit steam turbine marine motor |
US3011694A (en) | 1958-09-12 | 1961-12-05 | Alsacienne Constr Meca | Encapsuling device for expanders, compressors or the like |
US3470704A (en) * | 1967-01-10 | 1969-10-07 | Frederick W Kantor | Thermodynamic apparatus and method |
US3999400A (en) * | 1970-07-10 | 1976-12-28 | Gray Vernon H | Rotating heat pipe for air-conditioning |
US3842596A (en) * | 1970-07-10 | 1974-10-22 | V Gray | Methods and apparatus for heat transfer in rotating bodies |
FR2153129B2 (en) | 1971-06-01 | 1974-01-04 | Vulliez Paul | |
US3994636A (en) | 1975-03-24 | 1976-11-30 | Arthur D. Little, Inc. | Axial compliance means with radial sealing for scroll-type apparatus |
US3986852A (en) * | 1975-04-07 | 1976-10-19 | E. I. Du Pont De Nemours And Company | Rotary cooling and heating apparatus |
US3994635A (en) | 1975-04-21 | 1976-11-30 | Arthur D. Little, Inc. | Scroll member and scroll-type apparatus incorporating the same |
US4069673A (en) * | 1975-10-01 | 1978-01-24 | The Laitram Corporation | Sealed turbine engine |
US3986799A (en) | 1975-11-03 | 1976-10-19 | Arthur D. Little, Inc. | Fluid-cooled, scroll-type, positive fluid displacement apparatus |
NL7607040A (en) * | 1976-06-28 | 1977-12-30 | Ultra Centrifuge Nederland Nv | INSTALLATION EQUIPPED WITH A HOLLOW ROTOR. |
US4065279A (en) | 1976-09-13 | 1977-12-27 | Arthur D. Little, Inc. | Scroll-type apparatus with hydrodynamic thrust bearing |
US4082484A (en) | 1977-01-24 | 1978-04-04 | Arthur D. Little, Inc. | Scroll-type apparatus with fixed throw crank drive mechanism |
US4141677A (en) | 1977-08-15 | 1979-02-27 | Ingersoll-Rand Company | Scroll-type two stage positive fluid-displacement apparatus with intercooler |
US4192152A (en) | 1978-04-14 | 1980-03-11 | Arthur D. Little, Inc. | Scroll-type fluid displacement apparatus with peripheral drive |
DE2831179A1 (en) | 1978-07-15 | 1980-01-24 | Leybold Heraeus Gmbh & Co Kg | DISPLACEMENT MACHINE ACCORDING TO THE SPIRAL PRINCIPLE |
JPS55109793A (en) | 1979-02-17 | 1980-08-23 | Sanden Corp | Displacement type fluid compressor |
JPS5619369A (en) | 1979-07-25 | 1981-02-24 | Toshiba Corp | Non-commutator motor for driving compressor of refrigerator, etc. |
US4382754A (en) | 1980-11-20 | 1983-05-10 | Ingersoll-Rand Company | Scroll-type, positive fluid displacement apparatus with diverse clearances between scroll elements |
US4462771A (en) | 1981-02-09 | 1984-07-31 | The Trane Company | Wrap element and tip seal for use in fluid apparatus of the scroll type and method for making same |
US4415317A (en) | 1981-02-09 | 1983-11-15 | The Trane Company | Wrap element and tip seal for use in fluid apparatus of the scroll type |
US4416597A (en) | 1981-02-09 | 1983-11-22 | The Trane Company | Tip seal back-up member for use in fluid apparatus of the scroll type |
US4436495A (en) | 1981-03-02 | 1984-03-13 | Arthur D. Little, Inc. | Method of fabricating two-piece scroll members for scroll apparatus and resulting scroll members |
US4892469A (en) | 1981-04-03 | 1990-01-09 | Arthur D. Little, Inc. | Compact scroll-type fluid compressor with swing-link driving means |
JPS57171002A (en) | 1981-04-13 | 1982-10-21 | Ebara Corp | Scroll type machine |
JPS6037320B2 (en) | 1981-10-12 | 1985-08-26 | サンデン株式会社 | Scroll compressor |
US4411605A (en) | 1981-10-29 | 1983-10-25 | The Trane Company | Involute and laminated tip seal of labyrinth type for use in a scroll machine |
US4472120A (en) | 1982-07-15 | 1984-09-18 | Arthur D. Little, Inc. | Scroll type fluid displacement apparatus |
US4511091A (en) | 1983-01-06 | 1985-04-16 | Augusto Vasco | Method and apparatus for recycling thermoplastic scrap |
US4477238A (en) | 1983-02-23 | 1984-10-16 | Sanden Corporation | Scroll type compressor with wrap portions of different axial heights |
JPS60243301A (en) | 1984-05-18 | 1985-12-03 | Mitsubishi Electric Corp | Scroll fluid machine |
JPS6128782A (en) | 1984-07-20 | 1986-02-08 | Toshiba Corp | Scroll compressor |
FR2567970B1 (en) | 1984-07-23 | 1989-04-28 | Normetex | COMPLETELY DRY AND WATERPROOF VACUUM PUMP WITH RECTILINEAR MOTION OF COMPRESSION COMPRESSION |
JPH03547Y2 (en) | 1985-10-25 | 1991-01-10 | ||
JPS62126207A (en) | 1985-11-27 | 1987-06-08 | Mitsubishi Electric Corp | Scroll hydraulic machine |
DE3711986A1 (en) | 1986-04-11 | 1987-10-15 | Hitachi Ltd | SPIRAL COMPRESSOR AND METHOD FOR THE PRODUCTION THEREOF |
US4726100A (en) | 1986-12-17 | 1988-02-23 | Carrier Corporation | Method of manufacturing a rotary scroll machine with radial clearance control |
JPH0672521B2 (en) | 1987-02-04 | 1994-09-14 | 三菱電機株式会社 | Scroll fluid machinery |
DK148588A (en) | 1987-03-20 | 1988-09-21 | Toshiba Kk | SPIRAL COMPRESSOR AND SPIRAL ELEMENT, AND PROCEDURE FOR MANUFACTURING THE SPIRAL ELEMENT |
JPS6424191A (en) | 1987-07-16 | 1989-01-26 | Mitsubishi Electric Corp | Scroll fluid machine |
US4867657A (en) | 1988-06-29 | 1989-09-19 | American Standard Inc. | Scroll compressor with axially balanced shaft |
CH678969A5 (en) | 1989-04-08 | 1991-11-29 | Aginfor Ag | |
US5040956A (en) | 1989-12-18 | 1991-08-20 | Carrier Corporation | Magnetically actuated seal for scroll compressor |
JPH0826761B2 (en) | 1989-12-25 | 1996-03-21 | 三菱電機株式会社 | Scroll fluid machinery |
US5044904A (en) | 1990-01-17 | 1991-09-03 | Tecumseh Products Company | Multi-piece scroll members utilizing interconnecting pins and method of making same |
US5051079A (en) | 1990-01-17 | 1991-09-24 | Tecumseh Products Company | Two-piece scroll member with recessed welded joint |
JP2756014B2 (en) | 1990-02-21 | 1998-05-25 | 株式会社日立製作所 | Scroll compressor |
WO1991018207A1 (en) | 1990-05-11 | 1991-11-28 | Sanyo Electric Co., Ltd. | Scroll compressor |
JPH0481587A (en) | 1990-07-20 | 1992-03-16 | Tokico Ltd | Scroll type hydraulic machinery |
US5099658A (en) * | 1990-11-09 | 1992-03-31 | American Standard Inc. | Co-rotational scroll apparatus with optimized coupling |
US5214932A (en) * | 1991-01-25 | 1993-06-01 | Abdelmalek Fawzy T | Hermetically sealed electric driven gas compressor - expander for refrigeration |
US5258046A (en) | 1991-02-13 | 1993-11-02 | Iwata Air Compressor Mfg. Co., Ltd. | Scroll-type fluid machinery with seals for the discharge port and wraps |
US5142885A (en) | 1991-04-19 | 1992-09-01 | American Standard Inc. | Method and apparatus for enhanced scroll stability in a co-rotational scroll |
US5232355A (en) | 1991-05-17 | 1993-08-03 | Mitsubishi Denki K.K. | Scroll-type fluid apparatus having a labyrinth and oil seals surrounding a scroll shaft |
JP3192469B2 (en) | 1991-05-17 | 2001-07-30 | 花王株式会社 | Method for producing nonionic detergent particles |
US5338159A (en) | 1991-11-25 | 1994-08-16 | American Standard Inc. | Co-rotational scroll compressor supercharger device |
JPH05157076A (en) | 1991-11-29 | 1993-06-22 | Mitsubishi Heavy Ind Ltd | Scroll type fluid machine |
US5222882A (en) | 1992-02-20 | 1993-06-29 | Arthur D. Little, Inc. | Tip seal supporting structure for a scroll fluid device |
US5228309A (en) * | 1992-09-02 | 1993-07-20 | Arthur D. Little, Inc. | Portable self-contained power and cooling system |
US5470214A (en) | 1992-12-17 | 1995-11-28 | Goldstar Co., Ltd. | Lubricating device for horizontal type hermetic compressor |
US5449279A (en) | 1993-09-22 | 1995-09-12 | American Standard Inc. | Pressure biased co-rotational scroll apparatus with enhanced lubrication |
JPH07109981A (en) | 1993-10-13 | 1995-04-25 | Nippondenso Co Ltd | Scroll fluid machinery |
JP3046486B2 (en) | 1993-12-28 | 2000-05-29 | 株式会社日立製作所 | Scroll type fluid machine |
US5466134A (en) | 1994-04-05 | 1995-11-14 | Puritan Bennett Corporation | Scroll compressor having idler cranks and strengthening and heat dissipating ribs |
US5759020A (en) | 1994-04-05 | 1998-06-02 | Air Squared, Inc. | Scroll compressor having tip seals and idler crank assemblies |
JP3424322B2 (en) | 1994-05-30 | 2003-07-07 | ダイキン工業株式会社 | Co-rotating scroll fluid machine |
US5417554A (en) | 1994-07-19 | 1995-05-23 | Ingersoll-Rand Company | Air cooling system for scroll compressors |
FR2731051B1 (en) | 1995-02-24 | 1997-04-30 | Mecanique De Normandie Soc | VACUUM PUMP WITH CIRCULAR TRANSLATION CYCLE |
EP1101943B1 (en) | 1995-02-28 | 2003-12-03 | Anest Iwata Corporation | Control of a two-stage vacuum pump |
US5616015A (en) | 1995-06-07 | 1997-04-01 | Varian Associates, Inc. | High displacement rate, scroll-type, fluid handling apparatus |
US5609478A (en) | 1995-11-06 | 1997-03-11 | Alliance Compressors | Radial compliance mechanism for corotating scroll apparatus |
JPH09144674A (en) | 1995-11-20 | 1997-06-03 | Tokico Ltd | Scroll type fluid machinery |
JP3423514B2 (en) | 1995-11-30 | 2003-07-07 | アネスト岩田株式会社 | Scroll fluid machine |
JPH09177684A (en) | 1995-12-21 | 1997-07-11 | Anest Iwata Corp | Scroll type vacuum pump |
US5987894A (en) | 1996-07-16 | 1999-11-23 | Commissariat A L'energie Atomique | Temperature lowering apparatus using cryogenic expansion with the aid of spirals |
BR9706766A (en) | 1996-09-24 | 1999-07-20 | Bosch Gmbh Robert | Bearing mainly for an electric machine |
US5752816A (en) | 1996-10-10 | 1998-05-19 | Air Squared,Inc. | Scroll fluid displacement apparatus with improved sealing means |
US5836752A (en) | 1996-10-18 | 1998-11-17 | Sanden International (U.S.A.), Inc. | Scroll-type compressor with spirals of varying pitch |
US5833443A (en) | 1996-10-30 | 1998-11-10 | Carrier Corporation | Scroll compressor with reduced separating force between fixed and orbiting scroll members |
US5857844A (en) | 1996-12-09 | 1999-01-12 | Carrier Corporation | Scroll compressor with reduced height orbiting scroll wrap |
US5938419A (en) | 1997-01-17 | 1999-08-17 | Anest Iwata Corporation | Scroll fluid apparatus having an intermediate seal member with a compressed fluid passage therein |
US6068459A (en) | 1998-02-19 | 2000-05-30 | Varian, Inc. | Tip seal for scroll-type vacuum pump |
US6129530A (en) | 1998-09-28 | 2000-10-10 | Air Squared, Inc. | Scroll compressor with a two-piece idler shaft and two piece scroll plates |
US6439864B1 (en) | 1999-01-11 | 2002-08-27 | Air Squared, Inc. | Two stage scroll vacuum pump with improved pressure ratio and performance |
US6511308B2 (en) | 1998-09-28 | 2003-01-28 | Air Squared, Inc. | Scroll vacuum pump with improved performance |
US6193487B1 (en) | 1998-10-13 | 2001-02-27 | Mind Tech Corporation | Scroll-type fluid displacement device for vacuum pump application |
JP4026099B2 (en) | 1998-10-15 | 2007-12-26 | アネスト岩田株式会社 | Scroll fluid machinery |
US6074185A (en) | 1998-11-27 | 2000-06-13 | General Motors Corporation | Scroll compressor with improved tip seal |
US6050792A (en) | 1999-01-11 | 2000-04-18 | Air-Squared, Inc. | Multi-stage scroll compressor |
JP4424821B2 (en) | 2000-05-16 | 2010-03-03 | サンデン株式会社 | Scroll compressor |
US6283737B1 (en) | 2000-06-01 | 2001-09-04 | Westinghouse Air Brake Technologies Corporation | Oiless rotary scroll air compressor antirotation assembly |
KR100382341B1 (en) | 2000-07-06 | 2003-05-01 | 엘지전자 주식회사 | Heat exchanger |
JP2002106484A (en) | 2000-09-29 | 2002-04-10 | Toyota Industries Corp | Motor type scroll compressor |
US6434943B1 (en) | 2000-10-03 | 2002-08-20 | George Washington University | Pressure exchanging compressor-expander and methods of use |
JP2002310073A (en) | 2001-04-17 | 2002-10-23 | Toyota Industries Corp | Scroll compressor and gas compression method for scroll compressor |
WO2002090747A2 (en) * | 2001-05-07 | 2002-11-14 | Battelle Memorial Institute | Heat energy utilization system |
JP2003035261A (en) | 2001-07-19 | 2003-02-07 | Toyota Industries Corp | Compressor |
JP4074075B2 (en) | 2001-09-19 | 2008-04-09 | アネスト岩田株式会社 | Scroll fluid machinery |
JP4040300B2 (en) | 2001-12-28 | 2008-01-30 | アネスト岩田株式会社 | Scroll fluid machine, pin crank mechanism thereof, and assembly method thereof |
US6705848B2 (en) | 2002-01-24 | 2004-03-16 | Copeland Corporation | Powder metal scrolls |
US7121817B2 (en) | 2002-05-30 | 2006-10-17 | Anest Iwata Corporation | Scroll fluid machine comprising compressing and expanding sections |
AU2003263794A1 (en) | 2002-07-22 | 2004-02-09 | Robert D. Hunt | Turbines utilizing jet propulsion for rotation |
US6922999B2 (en) | 2003-03-05 | 2005-08-02 | Anest Iwata Corporation | Single-winding multi-stage scroll expander |
US6736622B1 (en) | 2003-05-28 | 2004-05-18 | Scroll Technologies | Scroll compressor with offset scroll members |
US7249459B2 (en) | 2003-06-20 | 2007-07-31 | Denso Corporation | Fluid machine for converting heat energy into mechanical rotational force |
JP2005337189A (en) | 2004-05-31 | 2005-12-08 | Anest Iwata Corp | Method for manufacturing revolving scroll of scroll fluid machine |
JP2008506885A (en) | 2004-07-13 | 2008-03-06 | タイアックス エルエルシー | Refrigeration system and refrigeration method |
US7458414B2 (en) | 2004-07-22 | 2008-12-02 | Parker-Hannifin Corporation | Hydraulic reservoir with integrated heat exchanger |
US7014435B1 (en) | 2004-08-28 | 2006-03-21 | Anest Iwata Corporation | Scroll fluid machine |
JP2006097531A (en) | 2004-09-29 | 2006-04-13 | Anest Iwata Corp | Turning scroll in scroll fluid machine |
FR2881189A1 (en) | 2005-01-21 | 2006-07-28 | V G B Vulliez Gestion Brevets | VACUUM PUMP CIRCULAR CIRCULAR TRANSLATION CYCLE WITH SEVERAL TREES |
GB0513827D0 (en) | 2005-07-06 | 2005-08-10 | Ball Stephen J | Household waste/rubbish bin |
US7439702B2 (en) | 2005-11-15 | 2008-10-21 | York International Corporation | Application of a switched reluctance motion control system in a chiller system |
US7467933B2 (en) | 2006-01-26 | 2008-12-23 | Scroll Laboratories, Inc. | Scroll-type fluid displacement apparatus with fully compliant floating scrolls |
US7942655B2 (en) | 2006-02-14 | 2011-05-17 | Air Squared, Inc. | Advanced scroll compressor, vacuum pump, and expander |
US10683865B2 (en) | 2006-02-14 | 2020-06-16 | Air Squared, Inc. | Scroll type device incorporating spinning or co-rotating scrolls |
US8523544B2 (en) | 2010-04-16 | 2013-09-03 | Air Squared, Inc. | Three stage scroll vacuum pump |
US8668479B2 (en) | 2010-01-16 | 2014-03-11 | Air Squad, Inc. | Semi-hermetic scroll compressors, vacuum pumps, and expanders |
JP4969878B2 (en) | 2006-03-13 | 2012-07-04 | アネスト岩田株式会社 | Scroll fluid machinery |
JP4948869B2 (en) | 2006-03-28 | 2012-06-06 | アネスト岩田株式会社 | Scroll fluid machinery |
JP4864689B2 (en) * | 2006-04-17 | 2012-02-01 | 株式会社デンソー | Fluid machinery and Rankine cycle |
JP4999157B2 (en) | 2006-12-28 | 2012-08-15 | アネスト岩田株式会社 | Fluid machine coupled to drive source via magnetic coupling |
WO2008087958A1 (en) * | 2007-01-18 | 2008-07-24 | Panasonic Corporation | Fluid machine and refrigeration cycle device |
JP2008255795A (en) | 2007-03-30 | 2008-10-23 | Anest Iwata Corp | Scroll type fluid machine |
CH697852B1 (en) | 2007-10-17 | 2009-02-27 | Eneftech Innovation Sa | compression spiral device or expansion. |
US7958862B2 (en) | 2007-12-07 | 2011-06-14 | Secco2 Engines, Inc. | Rotary positive displacement combustor engine |
US8128387B2 (en) | 2008-03-26 | 2012-03-06 | Visteon Global Technologies, Inc. | Discharge chamber for dual drive scroll compressor |
US7980078B2 (en) * | 2008-03-31 | 2011-07-19 | Mccutchen Co. | Vapor vortex heat sink |
JP2009264370A (en) | 2008-03-31 | 2009-11-12 | Hitachi Ltd | Scroll type fluid machine |
US8177534B2 (en) | 2008-10-30 | 2012-05-15 | Advanced Scroll Technologies (Hangzhou), Inc. | Scroll-type fluid displacement apparatus with improved cooling system |
JP5075810B2 (en) | 2008-12-26 | 2012-11-21 | 株式会社日立産機システム | Scroll type fluid machine |
GB0914230D0 (en) | 2009-08-14 | 2009-09-30 | Edwards Ltd | Scroll pump |
US8484974B1 (en) * | 2009-10-28 | 2013-07-16 | Lockheed Martin Corporation | Dual-phase thermal electricity generator |
JP5236619B2 (en) | 2009-11-30 | 2013-07-17 | 株式会社日立産機システム | Injection scroll air compressor |
US11047389B2 (en) | 2010-04-16 | 2021-06-29 | Air Squared, Inc. | Multi-stage scroll vacuum pumps and related scroll devices |
US9074598B2 (en) | 2011-08-09 | 2015-07-07 | Air Squared Manufacturing, Inc. | Scroll type device including compressor and expander functions in a single scroll plate pair |
US20130232975A1 (en) | 2011-08-09 | 2013-09-12 | Robert W. Saffer | Compact energy cycle construction utilizing some combination of a scroll type expander, pump, and compressor for operating according to a rankine, an organic rankine, heat pump, or combined organic rankine and heat pump cycle |
JP2013169029A (en) * | 2012-02-14 | 2013-08-29 | Kobe Steel Ltd | Power generator |
US9022758B2 (en) | 2012-03-23 | 2015-05-05 | Bitzer Kuehlmaschinenbau Gmbh | Floating scroll seal with retaining ring |
WO2014018530A1 (en) | 2012-07-23 | 2014-01-30 | Emerson Climate Technologies, Inc. | Anti-wear coatings for compressor wear surfaces |
US9046287B2 (en) * | 2013-03-15 | 2015-06-02 | Whirlpool Corporation | Specialty cooling features using extruded evaporator |
US9657733B2 (en) | 2013-12-16 | 2017-05-23 | Wabco Compressor Manufacturing Co. | Compressor for a vehicle air supply system |
US10294936B2 (en) | 2014-04-22 | 2019-05-21 | Project Phoenix, Llc. | Fluid delivery system with a shaft having a through-passage |
EP3239526B1 (en) | 2014-12-24 | 2019-08-14 | Valeo Japan Co., Ltd. | Electrically driven scroll compressor |
US10508543B2 (en) | 2015-05-07 | 2019-12-17 | Air Squared, Inc. | Scroll device having a pressure plate |
JP6622527B2 (en) | 2015-09-10 | 2019-12-18 | アネスト岩田株式会社 | Scroll fluid machinery |
CN105402134B (en) | 2015-12-18 | 2017-10-10 | 珠海格力节能环保制冷技术研究中心有限公司 | A kind of oil blocking cover and the screw compressor with the oil blocking cover |
US10865793B2 (en) | 2016-12-06 | 2020-12-15 | Air Squared, Inc. | Scroll type device having liquid cooling through idler shafts |
US10400771B2 (en) | 2016-12-09 | 2019-09-03 | Air Squared, Inc. | Eccentric compensating torsional drive system |
-
2013
- 2013-04-23 US US13/986,349 patent/US20130232975A1/en not_active Abandoned
-
2015
- 2015-09-22 US US14/756,594 patent/US9784139B2/en active Active
-
2017
- 2017-08-24 US US15/731,929 patent/US10519815B2/en active Active
-
2018
- 2018-02-12 US US15/932,150 patent/US10774690B2/en active Active
Patent Citations (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2079118A (en) * | 1935-01-19 | 1937-05-04 | Rheinmetall Borsig Ag | Combined turbine and steam generator |
US2330121A (en) * | 1940-10-04 | 1943-09-21 | Jack & Heintz Inc | Motor cooling system |
US3613368A (en) * | 1970-05-08 | 1971-10-19 | Du Pont | Rotary heat engine |
US4395885A (en) * | 1981-10-08 | 1983-08-02 | Cozby Enterprises, Inc. | Unitary steam engine |
DE19957425A1 (en) * | 1998-12-02 | 2000-08-24 | Gerd Degener | Energy converter for utilising environmental heat energy has heat exchanger and expansion device with eccentric rotor for utilising evaporation and condensation of working medium |
US6464467B2 (en) * | 2000-03-31 | 2002-10-15 | Battelle Memorial Institute | Involute spiral wrap device |
US7124585B2 (en) * | 2002-02-15 | 2006-10-24 | Korea Institute Of Machinery & Materials | Scroll-type expander having heating structure and scroll-type heat exchange system employing the expander |
US8674525B2 (en) * | 2007-07-09 | 2014-03-18 | Universiteit Gent | Combined heat power system |
US20100287954A1 (en) * | 2009-03-25 | 2010-11-18 | Jayden Harman | Supersonic Cooling System |
Cited By (18)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US10683865B2 (en) | 2006-02-14 | 2020-06-16 | Air Squared, Inc. | Scroll type device incorporating spinning or co-rotating scrolls |
US11047389B2 (en) | 2010-04-16 | 2021-06-29 | Air Squared, Inc. | Multi-stage scroll vacuum pumps and related scroll devices |
US10774690B2 (en) | 2011-08-09 | 2020-09-15 | Air Squared, Inc. | Compact energy cycle construction utilizing some combination of a scroll type expander, pump, and compressor for operating according to a rankine, an organic rankine, heat pump, or combined organic rankine and heat pump cycle |
US10519815B2 (en) | 2011-08-09 | 2019-12-31 | Air Squared, Inc. | Compact energy cycle construction utilizing some combination of a scroll type expander, pump, and compressor for operating according to a rankine, an organic rankine, heat pump or combined organic rankine and heat pump cycle |
CN103485850A (en) * | 2013-09-22 | 2014-01-01 | 南京航空航天大学 | Time-sharing power generation/air conditioning integrated system and operating method thereof |
US9739179B2 (en) * | 2015-03-13 | 2017-08-22 | International Business Machines Corporation | Working fluid for a device, device and method for converting heat into mechanical energy |
US20160265390A1 (en) * | 2015-03-13 | 2016-09-15 | International Business Machines Corporation | Working fluid for a device, device and method for converting heat into mechanical energy |
US10508543B2 (en) | 2015-05-07 | 2019-12-17 | Air Squared, Inc. | Scroll device having a pressure plate |
US11692550B2 (en) | 2016-12-06 | 2023-07-04 | Air Squared, Inc. | Scroll type device having liquid cooling through idler shafts |
US10865793B2 (en) | 2016-12-06 | 2020-12-15 | Air Squared, Inc. | Scroll type device having liquid cooling through idler shafts |
US11454241B2 (en) | 2018-05-04 | 2022-09-27 | Air Squared, Inc. | Liquid cooling of fixed and orbiting scroll compressor, expander or vacuum pump |
US11933299B2 (en) | 2018-07-17 | 2024-03-19 | Air Squared, Inc. | Dual drive co-rotating spinning scroll compressor or expander |
US11067080B2 (en) | 2018-07-17 | 2021-07-20 | Air Squared, Inc. | Low cost scroll compressor or vacuum pump |
US11530703B2 (en) | 2018-07-18 | 2022-12-20 | Air Squared, Inc. | Orbiting scroll device lubrication |
US11473572B2 (en) | 2019-06-25 | 2022-10-18 | Air Squared, Inc. | Aftercooler for cooling compressed working fluid |
US20210164707A1 (en) * | 2019-12-02 | 2021-06-03 | Wei-Sung WENG | Mechanical device and operating method thereof |
US11898557B2 (en) | 2020-11-30 | 2024-02-13 | Air Squared, Inc. | Liquid cooling of a scroll type compressor with liquid supply through the crankshaft |
US11885328B2 (en) | 2021-07-19 | 2024-01-30 | Air Squared, Inc. | Scroll device with an integrated cooling loop |
Also Published As
Publication number | Publication date |
---|---|
US9784139B2 (en) | 2017-10-10 |
US10774690B2 (en) | 2020-09-15 |
US10519815B2 (en) | 2019-12-31 |
US20160069219A1 (en) | 2016-03-10 |
US20180216498A1 (en) | 2018-08-02 |
US20170362962A1 (en) | 2017-12-21 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US10519815B2 (en) | Compact energy cycle construction utilizing some combination of a scroll type expander, pump, and compressor for operating according to a rankine, an organic rankine, heat pump or combined organic rankine and heat pump cycle | |
US11906212B2 (en) | Rotary heat exchanger | |
JP3771561B2 (en) | Scroll expander having heating structure, and scroll-type heat exchange system using the same | |
JP5824451B2 (en) | Application example of motor cooling | |
US7726129B2 (en) | Stirling cycle engine | |
RU2581469C2 (en) | Device for compressing gaseous media | |
US11698198B2 (en) | Isothermal-turbo-compressor-expander-condenser-evaporator device | |
CN104074566B (en) | TRT and electricity generation system | |
US10281177B2 (en) | Caloric heat pump system | |
US10041701B1 (en) | Heating and cooling devices, systems and related method | |
CN105378295B (en) | Turbo-compressor and turbo refrigerating machine | |
JP6070224B2 (en) | Power generator | |
US20150107249A1 (en) | Extracting Heat From A Compressor System | |
WO2014175928A2 (en) | Compact energy cycle construction utilizing some combination of a scroll type expander, pump, and compressor for operating according to a rankine, an organic rankine, heat pump, or combined organic rankine and heat pump cycle | |
EP2744989B1 (en) | Compression and energy-recovery unit | |
US20140369877A1 (en) | Expander for recovery of thermal energy from a fluid | |
JP6371139B2 (en) | Switching method | |
JP6102292B2 (en) | Trochoid pump | |
US10578342B1 (en) | Enhanced compression refrigeration cycle with turbo-compressor | |
JP6731860B2 (en) | Scroll type fluid machinery | |
JP2020183727A (en) | Rotary compressor | |
CN105179251A (en) | Vertical fully-closed two-stage revolving compressor with oval rotors |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |
|
AS | Assignment |
Owner name: AIR SQUARED, INC., COLORADO Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:SHAFFER, ROBERT W.;SHAFFER, BRYCE R.;REEL/FRAME:043754/0108 Effective date: 20170726 |