US20130255308A1 - Chiller or heat pump with a falling film evaporator and horizontal oil separator - Google Patents
Chiller or heat pump with a falling film evaporator and horizontal oil separator Download PDFInfo
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- US20130255308A1 US20130255308A1 US13/434,169 US201213434169A US2013255308A1 US 20130255308 A1 US20130255308 A1 US 20130255308A1 US 201213434169 A US201213434169 A US 201213434169A US 2013255308 A1 US2013255308 A1 US 2013255308A1
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- Prior art keywords
- compressor
- oil separator
- oil
- refrigerant
- separator vessel
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
- F25B43/02—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat for separating lubricants from the refrigerant
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
- F25B1/047—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type of screw type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/23—Separators
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B31/00—Compressor arrangements
- F25B31/002—Lubrication
- F25B31/004—Lubrication oil recirculating arrangements
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Power Engineering (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Compressor (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
A refrigerant circuit using a vapor compression cycle, the circuit usable for air conditioning, refrigeration or heat pump purposes. The circuit includes a lubricated compressor connected to an oil separator vessel separate from the compressor, a falling film or hybrid falling film evaporator and a condenser. The oil separator vessel extends substantially horizontally. The oil separator vessel is separated into a primary space and a secondary space by a filter pad configured to substantially remove entrained oil droplets of about 5 μm and larger from the refrigerant entering the oil separator vessel. The primary space is in fluid connection with a discharge of the compressor. The secondary space is in fluid connection with an inlet of the condenser. The circuit has an oil entrainment flow discharge of lubricant from the compressor of at least about two percent by mass relative to refrigerant flow.
Description
- This invention deals with machines used for refrigeration and air conditioning or heat pumps with medium to high cooling capacity (typically about 100 kW and higher), using vapor compression cycles, including falling film or hybrid falling film evaporators, in conjunction with lubricated compressors connected to oil separators that are separate from the compressor.
- In the context of research for energy savings and reduction of the emissions of greenhouse gasses, high equipment efficiency and low refrigerant charges are being sought. To achieve these goals, improvements are being made to all the components of the systems: compressors, variable speed drives, optimized choice of refrigerant, oil separators, heat exchangers, etc. Most of the compressors require an amount of lubrication, which lubrication similarly generates carry-over of an amount of oil from the compressor into the refrigerant circuit. This oil that is entrained into the refrigerant circuit must then be returned to the compressor by and adequate oil return system, in order to avoid different adverse effects like the deterioration of the performance of the heat exchangers. It is especially so for screw compressors: these machines require a particularly large amount of lubrication in order to insure proper sealing of the gas between the rotors and to avoid the need for additional synchronization gears between the rotors. Therefore, screw compressors typically require a vessel, also commonly referred to as an oil separator, positioned between the compressor discharge and the inlet of the condenser. One challenge associated with refrigeration machines and heat pumps is the management of the oil in the refrigerant circuits. This requires a careful combination between the oil carry-over, the oil return system and the technology of the heat exchangers.
- Besides separating the oil from the discharge gas, this vessel or oil separator or separator vessel usually also has the function of being the oil sump for the compressor. Separator vessels or oil separators can be based on several operating principles. The most common include:
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- Impingement separation: the two-phase mixture of oil and gas is projected onto a wall or to the end of the vessel, providing a first stage of separation.
- Gravity separation: the gas mixed with oil is allowed to travel in the vessel, either horizontally or vertically upwards; this permits the larger droplets of oil in liquid phase sufficient time to be urged by gravity toward the bottom of the vessel.
- Filter pad separation: the mix is forced through a pad of closely spaced and/or finely interwoven filaments or wires that acts as a filter. In one embodiment, the filter pad may include a wire mesh. Per the instructions of such filter manufacturers, filter pads are normally installed horizontally, with gas circulation directed upwards. The filtration level of filter pads is relatively coarse; it would not stop very fine droplets entrained in the gas or mist, but still removes smaller droplets than gravity separation.
- Centrifugal separation: the two-phase oil and gas mixture is introduced tangentially in a cylindrical vessel. The whirling motion tends to project the oil droplets onto the cylindrical wall of the vessel where the droplets coalesce and fall to the bottom of the vessel. Like gravity separation, centrifugal separation allows removing the largest droplets of oil.
- Coalescing filters: the two-phase mixture of oil and gas is forced through a cartridge acting as a filter. The filter material is typically fiberglass. The filtration is much finer as compared with the filter pads (see above). For example, coalescing filters substantially prevent droplets of 1 μm (micrometers) or larger in diameter from passing through the coalescing filter during operation of a refrigerant circuit. In a typical embodiment, the coalescing filters generally permit about 1 to 10 parts per million (PPM) by mass of oil droplets entrained in refrigerant flow to discharge from the separator.
- Several different principles are often implemented simultaneously in a single separator. For instance, when coalescing filters are used, they are normally installed to supplement a filter/separator that can incorporate one or more operating principles such as impingement, gravity, centrifugal, and/or filter pad separation. In the design of an oil separator, the challenge is to find the best compromise between various parameters such as price, size, ease of installation, pressure drop, reliability, and of course, efficiency of the separation.
- Typical designs of oil separators include:
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- A horizontal design with coalescing filters.
FIG. 1 shows an example of this well-known design. The separation begins with impingement at one end of the vessel, continues with a gravity separation section that is also used as the oil sump, and is completed by coalescing filters. - A vertical cyclone design with a coalescing filter (not shown).
- A horizontal design with coalescing filters.
- When properly implemented, these designs normally provide a highly efficient oil separation thanks to the coalescing elements. Yet, coalescing filters have some drawbacks. They tend to be relatively expensive. If the coalescing filters are not mounted properly, some separators in a series may not meet operating specifications. If the possibility of inspection and filter removal is desired, costly additional flanges or access-providing man holes are required that also increase the risk of refrigerant leaks. In addition, hydraulic pressure safety testing of vessels having internal coalescing filters raises risk of damaging these filters, as well as associated difficulties in emptying and drying the vessel properly after completing the testing.
- In case of accidental high fluid mass flow, coalescing filters can also suffer loss of performance, and are susceptible to clogging and/or destruction under the effect of elevated fluid forces. Increased fluid mass flow is especially a problem for heat pump applications with high pressure halogenated refrigerants such as HFC's. Even when used in air conditioning applications, coalescers or coalescing filters need to be oversized when high pressure HFC's, such as R-410A or R-507 are used. Use of high temperature heat pumps increases problems associated with such applications. In such high temperature heat pumps, the evaporating temperature is substantially higher than when using the same machines and refrigerant in corresponding air conditioning applications, due to higher temperature of the water or other medium being cooled at the evaporator. In high temperature heat pumps, the leaving water from the evaporator is typically above 20° C., and can reach up to 60° C. or even higher. The resulting higher evaporation temperatures substantially increase density and hence the mass flow of refrigerant, even when using a relatively low pressure refrigerant such as R-134a or even lower pressure refrigerants like R-245fa for instance.
- For heat pumps or chillers using compressors, such as a screw compressor, what is desirable is an oil separator having a radically simplified design that does not include coalescing filters, while providing a sufficient oil separation during operation.
- For heat pumps or chillers using a screw compressor, the present disclosure is directed to the use of falling film evaporators or hybrid falling film evaporators, such as described, for instance, in U.S. Pat. No. 7,849,710, which is incorporated by reference in its entirety. These evaporators offer the best state of the art compromise between optimized performance and reduced refrigerant charge. In addition, falling film and hybrid falling film evaporator performance is less sensitive to oil carry-over than traditional flooded evaporators, permitting an oil separator, such as the filter pad, to be used without sacrificing evaporator performance.
- For purposes of the present disclosure, the term filter pad generally incorporates the following performance characteristics: substantially prevents droplets of about 5 μm (micrometers) in diameter or larger from passing through the filter pad during operation of a refrigerant circuit. In one embodiment, the filter pad operates between about 50 to about 100 parts per million (PPM) of oil entrained in refrigerant flow from the separator. In another embodiment of the filter pad, the void percentage of the filter pad is between about 97 and about 99 percent. In a further embodiment of the filter pad, the diameter of filaments and/or wires generally ranges from between about 0.15 mm to about 0.35 mm (millimeters) in diameter.
- The present invention is directed to a refrigerant circuit using a vapor compression cycle, the circuit usable for air conditioning, refrigeration or heat pump purposes. The circuit includes a lubricated compressor connected to an oil separator vessel separate from the compressor, a falling film or hybrid falling film evaporator and a condenser. The oil separator vessel extends substantially horizontally. The oil separator vessel is separated into a primary space and a secondary space by a filter pad configured to substantially remove entrained oil droplets of about 5 μm and larger from the refrigerant entering the oil separator vessel. The primary space is in fluid connection with a discharge of the compressor. The secondary space is in fluid connection with an inlet of the condenser. The circuit has an oil entrainment flow discharge of lubricant from the compressor of at least about two percent by mass relative to refrigerant flow.
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FIG. 1 and shows a prior art oil separator. -
FIG. 2 shows an exemplary embodiment of an oil separator of the present disclosure. -
FIG. 3 shows an exemplary embodiment of an oil separator of the present disclosure. -
FIG. 4 shows an exemplary embodiment of an oil separator of the present disclosure. -
FIG. 5 schematically shows an exemplary embodiment of a vapor compression system of the present disclosure. -
FIG. 6 schematically shows an exemplary embodiment of a vapor compression system of the present disclosure. -
FIG. 7 shows an exemplary embodiment of an oil separator of the present disclosure. -
FIG. 8 shows an exemplary embodiment of an oil separator of the present disclosure. -
FIG. 2 shows ahorizontal vessel 1 with afilter pad 2 providing a longitudinal separation of the vessel into two spaces: aprimary space 3 having aninlet 4 to receive discharge from the compressor, and asecondary space 5 having anoutlet 6 in communication with an inlet of a condenser (not shown). In an exemplary embodiment,inlet 4 receives compressor discharge in which a gas andoil mixture 15 enteringseparator vessel 1 can be arranged to provide impingement separation at an end ofvessel 1 inprimary space 3. In addition, asecond filter pad 7 can be disposed on ornear end 17 ofvessel 1 where this impingement occurs, to limit the re-entrainment of liquid with gas discharged from the compressor after the gas discharge collides with the end of the vessel. - In this arrangement, as further shown in
FIG. 2 , the oil that is separated from the gas is allowed to move freely fromprimary space 3 tosecondary space 5. In one embodiment,filter pad 2 is installed across the complete cross section ofvessel 1, transverse to the longitudinal direction ofvessel 1. The lower part ofvessel 1 is collectingliquid oil 19 and performing the function of an oil sump. Asfilter pad 2 offers very little resistance to the circulation ofliquid oil 19 betweenprimary space 3 andsecondary space 5, the level ofliquid oil 19 is essentially the same for both spaces. It is generally better to collect theliquid oil 19 fromsecondary space 5 through anoil pipe 8 to be returned to the compressor for lubrication, because the oil has an opportunity to become separated from foam and bubbles byfilter pad 2 while migrating fromprimary space 3 tosecondary space 5. With this arrangement, evaporators 12 (FIG. 5 ), such as falling film evaporators or hybrid falling film evaporators, a circuit having an oil entrainment flow discharge of lubricant from the compressor of about two percent or more by mass relative to refrigerant flow, i.e., percentage of mass flow total of refrigerant plus lubricant, such as associated with screw compressor operation, can be accommodated by the oil separator. In one embodiment, the oil separator is separate from the compressor. - In one arrangement, a
filter pad 2 separating respective primary andsecondary spaces vessel 1, and about at mid-length of the separator vessel. In alternative arrangements, thisfilter pad 2 can be positioned non-perpendicular with respect to the vessel axis, such as shown inFIG. 3 . This arrangement has an advantage of reducing the velocity of the gas flowing throughfilter pad 2. As a result, a vessel of the present disclosure can have a smaller vessel diameter in comparison to the diameter of a vessel of conventional construction, with the smaller diameter vessel of the present disclosure operating with a gas flow velocity through thefilter pad 2 that may be similar to the operating gas flow velocity through thefilter pad 2 of the larger, conventional vessel ofFIG. 2 . In one embodiment, the smaller diameter vessel of the present disclosure may operate with a gas flow velocity through thefilter pad 2 that may be less than the gas flow velocity of the larger, conventional vessel. In another embodiment,filter pad 2 may be composed of two ormore portions FIG. 4 , which is a plan view of the vessel. In yet another embodiment,portions - In still a further arrangement, two oil separation sections or spaces utilizing the same principle can be integrated in a
single vessel 1, each section or space orsecondary space 5 receiving approximately one half of the volume of discharge gas and oil fromprimary space 3. In this arrangement, there is onevessel 1 with twofilter pads 2, and two possible options about the direction of the flow. In one embodiment as shown inFIG. 7 , there is oneprimary space 3 positioned substantially in the middle ofvessel 1 and between the twofilter pads 2, and twosecondary spaces 5, with onesecondary space 5 arranged at each end of the vessel. As shown, there is onecommon gas inlet 4 substantially positioned in the middle ofprimary space 3, and oneoutlet 6 positioned in each of opposedsecondary spaces 5, whichsecondary spaces 5 are positioned at each end ofprimary space 3. These twooutlets 6 are connected to the condenser inlet (not shown). The interconnection piping between both outlets can be internal or external tovessel 1. In another embodiment (FIG. 8 ) the flows are reversed: there is oneprimary space 3 positioned at each end ofvessel 1 with an end ofgas inlet 4 extending into each respectiveprimary space 3, and one commonsecondary space 5 positioned between opposedprimary spaces 3 with acommon gas inlet 4 enteringsecondary space 5. In this embodiment, sections ofinlet 4 connected to the compressor discharge are divided into two pipes or portions extending to each of the two primary spaces, one at each end ofvessel 1. The interconnected piping or portions ofinlet 4 can be arranged internal or external of the vessel. For instance, inFIG. 8 , there is onecommon inlet 4 extending to a bifurcatedinternal pipe 13 distributing the gas to each end ofvessel 1. - In an alternate embodiment of
FIG. 7 , bothoutlets 6 can be connected to form a single pipe that extends to one condenser inlet. In an alternate arrangement, the condenser (not shown) can have two inlets, one inlet at each end; with each of the twoseparator outlets 6 being connected to one of the condenser inlets. - The arrangement with two sections or spaces in a common vessel offers several advantages. As the flow to each section or space is reduced, such as being reduced by a factor of two, so too is a reduction of the required cross section of the vessel. Therefore, in spite of the additional length, the reduction in diameter will result in a less expensive vessel. A further advantage is that a vessel of smaller diameter will typically radiate less noise, because there is less potential for wall resonance in a shell of smaller diameter. Finally, the added length to the vessel does not raise packaging problems with other system components as long as the length of the separator or vessel does not substantially exceed that of the heat exchangers, such as the condenser and/or evaporator.
- As the oil separator vessel is horizontal, the arrangement lends itself to easy packaging with horizontal shell and tube heat exchangers, and with a horizontal screw compressor driveline. In a possible arrangement as shown in
FIG. 5 , the discharge ofcompressor 9 is directed downwards toseparator vessel 1. In another embodiment as shown inFIG. 6 , the discharge ofcompressor 9 may be directed from one side ofcompressor 9 tooil separator vessel 1. In yet another embodiment, the compressor discharge may be directed at an orientation that is between the downward direction and the side direction of the compressor to the oil separator vessel (not shown). In this arrangement, the compressor driveline can be installed at least partially above the oil separator vessel. As further shown inFIG. 5 ,evaporator 12 is positioned abovecondenser 11 and arranged near the compressor driveline and separator vessel. In other embodiments (not shown),evaporator 12 andcondenser 11 may be positioned in different arrangements with respect to each other and/or to the compressor driveline and oil separator vessel. In another arrangement, such as shown inFIG. 6 , the compressor suction is directed vertically, such thatcompressor 9 is installed on top ofevaporator 12, with compressor discharge from one side of the compressor tooil separator vessel 1. In another embodiment (not shown) the compressor suction may extend outwardly from the side, or in yet another embodiment, the compressor suction may extend between a vertical and a side orientation with respect to theoil separator vessel 1. In this arrangement,compressor 9 can be installed at least partially aboveevaporator 12. As further shown inFIG. 6 ,oil separator vessel 1 is shown positioned laterally besidecompressor 9 and on top ofcondenser 11. In other embodiments, other arrangements between the compressor, oil separator vessel, condenser and evaporator may be utilized. - This use of filter pads is especially advantageous for use with heat pumps using halogenated refrigerants like HFC's or HFO's, and when the evaporation temperature is significantly greater than evaporator temperatures normally associated with air conditioning applications (e.g., 5° C.). For such heat pumps, the evaporation temperature can be up 30° to about 40° C. with HFC refrigerant R-134a or possible equivalents, and even higher temperatures associated with lower pressure refrigerants such as R-245fa.
- In another embodiment, the refrigerants may include hydrocarbons such as R-290 or R-1270.
Claims (16)
1. A refrigerant circuit using a vapor compression cycle, the circuit usable for air conditioning, refrigeration or heat pump purposes, comprising a lubricated compressor connected to an oil separator vessel separate from the compressor, a falling film or hybrid falling film evaporator and a condenser, wherein the oil separator vessel extends substantially horizontally, the oil separator vessel separated into a primary space and a secondary space by a filter pad configured to substantially remove entrained oil droplets of about 5 μm and larger from the refrigerant entering the oil separator vessel, the primary space being in fluid connection with a discharge of the compressor; the secondary space being in fluid connection with an inlet of the condenser, the circuit having an oil entrainment flow discharge of lubricant from the compressor of at least about two percent by mass relative to refrigerant flow.
2. The refrigerant circuit of claim 1 , wherein a bottom of the oil separator vessel is used as an oil sump, and the oil sump is in fluid connection with oil supply orifices of the compressor.
3. The refrigerant circuit of claim 1 , wherein the compressor has a discharge directed substantially downwards and suction from above or sideways from the compressor, and wherein a compressor driveline is positioned at least partially above the oil separator, and the evaporator is positioned at least partially above the condenser.
4. The refrigerant circuit of claim 1 , wherein the compressor has a downwardly directed suction and a discharge from a side of the compressor, and wherein the compressor is positioned at least partially above the evaporator, and the oil separator positioned at least partially above the condenser.
5. The refrigerant circuit of claim 1 , wherein an inlet of the oil separator vessel is bifurcated, the oil separator vessel separated into three spaces by two filter pads.
6. The refrigerant circuit of claim 5 , wherein refrigerant flow is bifurcated.
7. The refrigerant circuit of claim 5 , wherein the three spaces include two secondary spaces that are not adjacent to each other.
8. The refrigerant circuit of claim 1 , wherein the filter pad is located perpendicular to a longitudinal axis of the oil separator vessel.
9. The refrigerant circuit of claim 8 , wherein the filter pad is located at about mid-length of the longitudinal axis of the oil separator vessel and including a second filter pad at one end of the oil separator vessel.
10. The refrigerant circuit of claim 1 , wherein the filter pad is positioned non-perpendicular of the longitudinal axis of the oil separator vessel.
11. The refrigerant circuit of claim 10 , wherein the filter pad is composed of two or more portions arranged at an angle to each other.
12. The refrigerant circuit of claim 11 , wherein the two or more portions are of unequal length.
13. The refrigerant circuit of claim 1 , wherein the filter pad permits between about 50 to about 100 PPM of oil entrained in refrigerant flowing from the oil separator vessel.
14. The refrigerant circuit of claim 1 , used as a heat pump, and using a halogenated fluid as the refrigerant.
15. The refrigeration circuit of claim 14 , wherein the halogenated fluid is an HFC or an HFO as the refrigerant.
16. The refrigeration circuit of claim 1 , wherein the refrigerant is a hydrocarbon.
Priority Applications (8)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US13/434,169 US20130255308A1 (en) | 2012-03-29 | 2012-03-29 | Chiller or heat pump with a falling film evaporator and horizontal oil separator |
KR1020147027499A KR101607509B1 (en) | 2012-03-29 | 2012-10-31 | Chiller or heat pump with a falling film evaporator and horizontal oil separator |
EP12795658.9A EP2831519A1 (en) | 2012-03-29 | 2012-10-31 | Chiller or heat pump with a falling film evaporator and horizontal oil separator |
CN201280072076.4A CN104204692A (en) | 2012-03-29 | 2012-10-31 | Chiller or heat pump with a falling film evaporator and horizontal oil separator |
PCT/US2012/062741 WO2013147931A1 (en) | 2012-03-29 | 2012-10-31 | Chiller or heat pump with a falling film evaporator and horizontal oil separator |
JP2015503187A JP2015512501A (en) | 2012-03-29 | 2012-10-31 | Chiller or heat pump with falling film evaporator and horizontal oil separator |
TW101143672A TWI509207B (en) | 2012-03-29 | 2012-11-22 | Refrigeration circuit using a vapor compression cycle |
JP2016226618A JP2017075776A (en) | 2012-03-29 | 2016-11-22 | Refrigerant circuit |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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US13/434,169 US20130255308A1 (en) | 2012-03-29 | 2012-03-29 | Chiller or heat pump with a falling film evaporator and horizontal oil separator |
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US20130255308A1 true US20130255308A1 (en) | 2013-10-03 |
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Family Applications (1)
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US13/434,169 Abandoned US20130255308A1 (en) | 2012-03-29 | 2012-03-29 | Chiller or heat pump with a falling film evaporator and horizontal oil separator |
Country Status (7)
Country | Link |
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US (1) | US20130255308A1 (en) |
EP (1) | EP2831519A1 (en) |
JP (2) | JP2015512501A (en) |
KR (1) | KR101607509B1 (en) |
CN (1) | CN104204692A (en) |
TW (1) | TWI509207B (en) |
WO (1) | WO2013147931A1 (en) |
Cited By (10)
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JP2017020761A (en) * | 2015-07-15 | 2017-01-26 | 株式会社神戸製鋼所 | Oil separating/recovering device |
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Publication number | Priority date | Publication date | Assignee | Title |
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Citations (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3070977A (en) * | 1961-03-31 | 1963-01-01 | Heat X Inc | Refrigeration system, including oil separator and muffler unit and oil return arrangement |
US4359329A (en) * | 1980-04-12 | 1982-11-16 | M.A.N. Maschinenfabrik Augsburg-Nurnburg A.G. | Oil separator for compressors of heat pumps and chillers |
US5086621A (en) * | 1990-12-27 | 1992-02-11 | York International Corporation | Oil recovery system for low capacity operation of refrigeration systems |
US5214937A (en) * | 1991-10-28 | 1993-06-01 | Carrier Corporation | Integral oil separator and muffler |
US5735139A (en) * | 1996-06-28 | 1998-04-07 | Carrier Corporation | Dual inlet oil separator for a chiller |
US5829265A (en) * | 1996-06-28 | 1998-11-03 | Carrier Corporation | Suction service valve |
US20030014951A1 (en) * | 2001-07-20 | 2003-01-23 | Ingersoll-Rand Company | Horizontal separator tank for oil-flooded air compressor |
US6814786B1 (en) * | 2003-04-02 | 2004-11-09 | Philip Morris Usa Inc. | Filters including segmented monolithic sorbent for gas-phase filtration |
US20050092011A1 (en) * | 2001-12-27 | 2005-05-05 | Pereira Roberto H. | Refrigeration system with a plate-type condenser and method for compacting it |
US20060123833A1 (en) * | 2004-12-14 | 2006-06-15 | Carrier Corporation | Refrigerant/oil separator |
US20110023515A1 (en) * | 2009-07-31 | 2011-02-03 | Johnson Controls Technology Company | Refrigerant control system and method |
US20110185765A1 (en) * | 2009-03-12 | 2011-08-04 | Mitsubishi Heavy Industries, Ltd. | Heat pump apparatus |
US20120125040A1 (en) * | 2010-11-18 | 2012-05-24 | Sumitomo Heavy Industries, Ltd. | Oil separator |
Family Cites Families (17)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5837848B2 (en) * | 1981-04-13 | 1983-08-19 | 株式会社クラコ | Grease filter device |
JPS6322571U (en) * | 1986-07-26 | 1988-02-15 | ||
JPS63233290A (en) * | 1987-03-20 | 1988-09-28 | Hitachi Ltd | Down flow liquid film type evaporator |
JPS63254355A (en) * | 1987-04-10 | 1988-10-21 | 株式会社日立製作所 | Screw type refrigerator unit |
JPH0484083A (en) * | 1990-07-25 | 1992-03-17 | Hitachi Ltd | Screw type freezer device |
JPH06146841A (en) * | 1992-11-10 | 1994-05-27 | Toyota Motor Corp | Blow-by gas separating device for internal combustion engine |
US5632154A (en) * | 1995-02-28 | 1997-05-27 | American Standard Inc. | Feed forward control of expansion valve |
TW568254U (en) * | 1997-01-06 | 2003-12-21 | Mitsubishi Electric Corp | Refrigerant circulating apparatus |
JP3468174B2 (en) * | 1999-09-14 | 2003-11-17 | 三菱電機株式会社 | Refrigeration and air conditioning cycle equipment |
JP4356214B2 (en) * | 2000-08-21 | 2009-11-04 | 三菱電機株式会社 | Oil separator and outdoor unit |
JP2002357376A (en) * | 2001-06-01 | 2002-12-13 | Mitsubishi Electric Corp | Oil separator |
JP2003097443A (en) * | 2001-09-25 | 2003-04-03 | Mitsubishi Heavy Ind Ltd | Compressor and refrigeration unit |
US6880360B2 (en) * | 2002-10-03 | 2005-04-19 | York International Corporation | Compressor systems for use with smokeless lubricant |
US7599759B2 (en) * | 2002-12-09 | 2009-10-06 | Hudson Technologies, Inc. | Method and apparatus for optimizing refrigeration systems |
WO2006044448A2 (en) * | 2004-10-13 | 2006-04-27 | York International Corporation | Falling film evaporator |
JP2010002074A (en) * | 2008-06-18 | 2010-01-07 | Mitsubishi Electric Corp | Mixed refrigerant and refrigerating cycle device using the same |
JP2010175171A (en) * | 2009-01-30 | 2010-08-12 | Nippon Spindle Mfg Co Ltd | Temperature control device |
-
2012
- 2012-03-29 US US13/434,169 patent/US20130255308A1/en not_active Abandoned
- 2012-10-31 CN CN201280072076.4A patent/CN104204692A/en active Pending
- 2012-10-31 EP EP12795658.9A patent/EP2831519A1/en not_active Withdrawn
- 2012-10-31 JP JP2015503187A patent/JP2015512501A/en active Pending
- 2012-10-31 WO PCT/US2012/062741 patent/WO2013147931A1/en active Application Filing
- 2012-10-31 KR KR1020147027499A patent/KR101607509B1/en not_active IP Right Cessation
- 2012-11-22 TW TW101143672A patent/TWI509207B/en not_active IP Right Cessation
-
2016
- 2016-11-22 JP JP2016226618A patent/JP2017075776A/en active Pending
Patent Citations (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3070977A (en) * | 1961-03-31 | 1963-01-01 | Heat X Inc | Refrigeration system, including oil separator and muffler unit and oil return arrangement |
US4359329A (en) * | 1980-04-12 | 1982-11-16 | M.A.N. Maschinenfabrik Augsburg-Nurnburg A.G. | Oil separator for compressors of heat pumps and chillers |
US5086621A (en) * | 1990-12-27 | 1992-02-11 | York International Corporation | Oil recovery system for low capacity operation of refrigeration systems |
US5214937A (en) * | 1991-10-28 | 1993-06-01 | Carrier Corporation | Integral oil separator and muffler |
US5735139A (en) * | 1996-06-28 | 1998-04-07 | Carrier Corporation | Dual inlet oil separator for a chiller |
US5829265A (en) * | 1996-06-28 | 1998-11-03 | Carrier Corporation | Suction service valve |
US20030014951A1 (en) * | 2001-07-20 | 2003-01-23 | Ingersoll-Rand Company | Horizontal separator tank for oil-flooded air compressor |
US20050092011A1 (en) * | 2001-12-27 | 2005-05-05 | Pereira Roberto H. | Refrigeration system with a plate-type condenser and method for compacting it |
US6814786B1 (en) * | 2003-04-02 | 2004-11-09 | Philip Morris Usa Inc. | Filters including segmented monolithic sorbent for gas-phase filtration |
US20060123833A1 (en) * | 2004-12-14 | 2006-06-15 | Carrier Corporation | Refrigerant/oil separator |
US20110185765A1 (en) * | 2009-03-12 | 2011-08-04 | Mitsubishi Heavy Industries, Ltd. | Heat pump apparatus |
US20110023515A1 (en) * | 2009-07-31 | 2011-02-03 | Johnson Controls Technology Company | Refrigerant control system and method |
US20120125040A1 (en) * | 2010-11-18 | 2012-05-24 | Sumitomo Heavy Industries, Ltd. | Oil separator |
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US20160370120A1 (en) * | 2015-06-19 | 2016-12-22 | Ingersoll-Rand Company | Modular bonnet for variable-pass heat exchanger |
JP2017020761A (en) * | 2015-07-15 | 2017-01-26 | 株式会社神戸製鋼所 | Oil separating/recovering device |
US10626860B2 (en) | 2015-07-15 | 2020-04-21 | Kobe Steel, Ltd. | Oil separate and collect device |
EP3301382A4 (en) * | 2015-07-15 | 2019-01-23 | Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel, Ltd.) | Oil-separator/collector |
US10551135B2 (en) * | 2017-03-07 | 2020-02-04 | Heatcraft Refrigeration Products, Llc | Oil separator |
US20180259274A1 (en) * | 2017-03-07 | 2018-09-13 | Heatcraft Refrigeration Products Llc | Oil separator |
EP3446766A1 (en) * | 2017-08-24 | 2019-02-27 | Ingersoll-Rand Company | Compressor system separator tank baffle |
US10801500B2 (en) | 2017-08-24 | 2020-10-13 | Ingersoll-Rand Industrial U.S., Inc. | Compressor system separator tank baffle |
CN114748941A (en) * | 2017-08-24 | 2022-07-15 | 英格索兰工业美国公司 | Compressor system separator tank baffle and separation device for compressor system |
CN107388655A (en) * | 2017-09-13 | 2017-11-24 | 珠海格力电器股份有限公司 | Oil separator device and air-conditioner set |
US11460227B2 (en) | 2017-11-15 | 2022-10-04 | Mitsubishi Electric Corporation | Oil separator and refrigeration cycle apparatus |
WO2020003852A1 (en) * | 2018-06-25 | 2020-01-02 | 東芝キヤリア株式会社 | Compressor accumulator, method for manufacturing compressor accumulator, horizontal compressor, and refrigeration cycle device |
US11719471B2 (en) | 2021-09-29 | 2023-08-08 | Johnson Controls Tyco IP Holdings LLP | Energy efficient heat pump with heat exchanger counterflow arrangement |
WO2023213558A1 (en) * | 2022-05-03 | 2023-11-09 | Knorr-Bremse Systeme für Schienenfahrzeuge GmbH | Liquid separation device for a compressor system and compressor system having such a liquid separation device |
Also Published As
Publication number | Publication date |
---|---|
JP2017075776A (en) | 2017-04-20 |
TWI509207B (en) | 2015-11-21 |
EP2831519A1 (en) | 2015-02-04 |
KR20140146598A (en) | 2014-12-26 |
KR101607509B1 (en) | 2016-03-30 |
TW201339524A (en) | 2013-10-01 |
WO2013147931A1 (en) | 2013-10-03 |
CN104204692A (en) | 2014-12-10 |
JP2015512501A (en) | 2015-04-27 |
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