US20060073026A1 - Oil balance system and method for compressors connected in series - Google Patents
Oil balance system and method for compressors connected in series Download PDFInfo
- Publication number
- US20060073026A1 US20060073026A1 US10/959,254 US95925404A US2006073026A1 US 20060073026 A1 US20060073026 A1 US 20060073026A1 US 95925404 A US95925404 A US 95925404A US 2006073026 A1 US2006073026 A1 US 2006073026A1
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- US
- United States
- Prior art keywords
- compressor
- oil
- sump
- low side
- shell
- 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
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B31/00—Compressor arrangements
- F25B31/002—Lubrication
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/02—Lubrication
- F04B39/0207—Lubrication with lubrication control systems
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B41/00—Pumping installations or systems specially adapted for elastic fluids
- F04B41/06—Combinations of two or more pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S417/00—Pumps
- Y10S417/902—Hermetically sealed motor pump unit
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/8593—Systems
- Y10T137/85978—With pump
- Y10T137/86131—Plural
- Y10T137/86139—Serial
Abstract
Description
- This invention relates to an oil balance system for compressors connected in series. More particularly, this invention relates to apparatus and a method for an oil balance system in which each compressor is contained in a separate shell, and in which each oil sump for each compressor is a low side sump, i.e., the inlet to each compressor is open to its respective shell, and the outlet from each compressor is sealed to the compressor.
- My prior U.S. Pat. No. 5,839,886, the entire contents of which are incorporated herein by reference, relates to an oil balance system for primary and booster compressors connected in series for a heating/cooling or refrigeration system. The primary compressor has a low side sump, but the booster compressor has a high side sump (i.e., the inlet to the booster compressor is sealed to the compressor, and the outlet from the compressor is open to its shell. An open conduit extends between the oil sumps of the two compressors to transfer oil from the sump of the booster compressor to the sump of the primary compressor when the oil level in the booster compressor exceeds a normal operating level.
- My prior U.S. Pat. Nos. 5,927,088 and 6,276,148, the entire contents of both of which are incorporated herein by reference, relate to boosted air source heat pumps especially suitable for cold weather climates. In the systems of these patents, a booster compressor and a primary compressor are connected in series.
- Most compressors will entrain and pump out some oil, entrained in the refrigerant, during the normal course of operation. So, for a system of series connected compressors housed in separate casings, the pumped out oil will eventually return to the first compressor in the system, thus tending to raise the oil level in the sump of that compressor. As that oil level rises, this will likely cause the first compressor to pump oil to the inlet to the second compressor, so some oil will be delivered from that first compressor to the second compressor in the system, thus tending to prevent a dangerous loss of lubricant in the second compressor. Various compressor designs react differently in regard to this characteristic of pumping out oil entrained in the refrigerant, and it is known to make modifications to specific designs to enhance the tendency to pump out more oil as the level of oil rises.
- However, during the course of operation of a series connected compressor system, such as the heat pump systems of my U.S. Pat. Nos. 5,927,088 and 6,276,148, refrigerant/oil imbalances can occur due to such things as, e.g., defrosting requirements, extreme load changes, etc. These imbalances may lead to unbalancing the oil levels in the two compressors; and this may result in taxing the normal oil balancing tendencies beyond their normal capabilities. Accordingly, it may be desirable to incorporate a specific oil balance system in the series connected compressor system.
- In accordance with the present invention an oil balancing system is incorporated in a series connected compressor system, such as the heat pump system of my U.S. Pat. Nos. 5,927,088 and 6,276,148, wherein each compressor is housed in a hermetic casing and has a low side oil sump. An oil transfer conduit extends from the sump of the first compressor in the system (usually the booster compressor) to the sump of the second compressor (usually the primary compressor). When the first compressor is not operating and the second compressor is operating, the pressure within the casing of the first compressor is slightly higher than the pressure within the casing of the second compressor, so oil will, as desired, flow from the sump of the first compressor to the sump of the second compressor when the oil level in the first sump exceeds the height of the oil transfer conduit. However, when both compressors are operating, the pressure in the shell of the second compressor will be much higher than the pressure in the shell of the first compressor, which could cause undesirable oil and/or flow from the sump of the second compressor to the sump of the first compressor. Accordingly, and most importantly, the oil transfer conduit has a check valve which permits oil flow from the first compressor sump to the second compressor sump, but which prevents oil and/or gas flow from the second compressor sump to the first compressor sump.
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FIG. 1 is a schematic of the oil balance system of the present invention. -
FIG. 2 is a sectional view of the oil balance check valve ofFIG. 1 . - The present invention will be described in the context of a boosted sir source heat pump as disclosed in my prior U.S. Pat. Nos. 5,927,088 and 6,276,148. However, it will be understood that the present invention is applicable to any system of compressors in series where the compressors each have low side oil pumps.
- Referring to
FIG. 1 , abooster compressor 10 is housed in a hermetically sealedcasing 12, and aprimary compressor 14 is housed in a hermetically sealedcasing 16. The compressors are preferably reciprocating compressors, but rotary or other types of compressors may be used. Each compressor is a low side sump compressor. That is, the inlet to each compressor is open to the shell of the compressor, and the outlet from each compressor is sealed to the compressor. Each compressor/casing has an oil sump at the bottom of the casing, the normal level of which is shown in shown inFIG. 1 . The oil in these sumps is used to lubricate the compressors in ways presently known in the art. - An
oil balance conduit 18 extends between the compressor shells at the lower parts thereof.Oil balance conduit 18 is positioned just slightly above the normal level of the sump oil inbooster casing 12. A normallyopen check valve 20 is positioned inoil balance conduit 16.Check valve 20 permits oil flow from the sump ofbooster casing 12 to the sump ofprimary casing 16 whenprimary compressor 14 is on andbooster compressor 10 is off or when both compressors are off, but prevents oil flow from the sump ofprimary casing 16 to the sump ofbooster casing 12 whenever both compressors are on. - A
conduit 22 is connected to the low side of a system (e.g., an evaporator in a heating or cooling system), to receive refrigerant from the system low side. Abranch conduit 24 is connected to theinlet 26 toprimary compressor casing 16 to deliver refrigerant to the interior volume ofcasing 16 and toprimary compressor 14. Acheck valve 28 inconduit 24 controls the direction of flow inconduit 24.Check valve 28 is preferably normally open to minimize the pressure drop of the fluid flowing throughcheck valve 28 toprimary inlet 26. Anotherbranch conduit 30 connectsconduit 22 to theinlet 32 tobooster compressor casing 12 to deliver refrigerant to the interior volume ofcasing 12 and tobooster compressor 10. - One end of a booster
compressor discharge line 34 is sealed tobooster compressor 10, and the other end ofdischarge line 34 is connected tobranch conduit 24 downstream ofcheck valve 28, wherebydischarge line 34 delivers the discharge frombooster compressor 10 toprimary inlet 26 and to the interior volume ofprimary casing 16 and toprimary compressor 14. - One end of a primary
compressor discharge line 36 is sealed toprimary compressor 14 and the other end ofdischarge line 34 is connected to the high side of the system (e.g., a condenser in a heating or cooling system). - If the system includes an economizer, a
conduit 38 would be connected to conduit 24 downstream ofcheck valve 28. - Normally
open check valve 20 may be maintained normally open in any chosen manner. Examples may be understood by reference toFIG. 2 wherevalve 20 has aspherical chamber 40 in thesegments 18′ and 18″ ofoil balance line 18.Chamber 40 is divided into upper and lower segments by awall 42 which hasperipheral flow passages 44. Aball 46 is loaded againstwall 42 either by the force of gravity, or by alight spring 48 or bymagnets 50. Regardless of the mechanism chosen,valve 20 is normally open to permit flow inline 18 frombooster casing 10 toprimary casing 16 when the pressure in the interior volume ofprimary casing 16 is essentially equal to or lower than the pressure in the interior volume ofbooster casing 12. However, if the pressure in the interior ofprimary casing 16 is substantially higher than the pressure in the interior volume ofbooster casing 12,ball 46 will be moved to engage a conical orspherical seat 52 to close the entrance fromline 18′ to the upper segment ofchamber 40, thus blocking flow inoil balance line 18. In the operation of this invention,check valve 20 must be open whenprimary compressor 14 is on andbooster compressor 10 is off, and when both theprimary compressor 14 and thebooster compressor 10 are off, andcheck valve 20 must be closed when both the primary compressor and the booster compressor are on. - Normally
open check valve 28 may be held normally open in the same manner asvalve 20 if it is also mounted vertically. However, ifvalve 28 is mounted horizontally, spring or magnetic loading will be required. - When both
primary compressor 14 andbooster compressor 10 are off, the gas pressure inprimary shell 16 and inbooster shell 12 will be equal. Accordingly, oil flow inbalance line 18 will be bidirectional depending on the oil heads in the sumps of the primary and booster shells. - In the heating mode of operation, the booster compressor is off and only the primary compressor is operating at low heating load on the system. In this situation, normally
open check valves booster shell 12 is slightly higher than the pressure in primary shell. Therefore, if the oil level in the sump ofbooster shell 12 is higher than its intended normal level, which means that the oil level in the sump ofprimary shell 16 is lower than normal, oil will flow viabalance line 18 from the sump ofbooster shell 12 to the sump ofprimary shell 16 to restore normal oil levels in both sumps. Also, if the oil level in the sump ofprimary shell 16 is very high, which means that the oil level in the sump ofbooster shell 12 is low, and the pressure drop between the sump ofbooster shell 12 and the sump ofprimary shell 16 is low enough, oil can flow viabalance line 18 from the sump ofprimary shell 16 to the sump ofbooster shell 12. - At higher heating loads on the system, both the booster compressor and the primary compressor will be operating. In that situation, the pressure in the primary shell will be higher than the pressure in the booster shell, because the discharge from
booster compressor 10 will be delivered vialine 34 tocasing 16,check valve 28 will be closed, and system low side will be connected viaconduits inlet 32 tobooster shell 12. Accordingly, normallyopen check valve 20 will be closed, thus preventing back-flow of compressed gas (which would go from the discharge ofbooster compressor 10 toprimary shell 16 and then back tobooster shell 12 viabalance line 18 ifcheck valve 20 were open). However, the closure ofcheck valve 20 also prevents oil balance flow vialine 18, which can lead to oil imbalance in the sumps of the compressors, particularly creating a concern about low oil level in the sump ofprimary shell 16. - Some oil becomes entrained in the circulating refrigerant during the operation of the system. When both
booster compressor 10 andprimary compressor 16 are on, all oil entrained in the refrigerant is delivered to theshell 12 ofbooster compressor 10, where it tends to separate out and fall into the sump ofbooster shell 12. If the oil accumulates in the sump ofbooster shell 12 above the predetermined normal level, operation of the booster compressor will tend to agitate the oil to create a mist that will be entrained in the refrigerant discharged frombooster compressor 10. This entrained oil will be delivered to the interior ofprimary shell 16, where it will tend to drop out from the gas due to differences in gas and oil velocities upon entering into the interior ofprimary shell 16. This separated oil will fall into the sump ofprimary shell 16 to replenish the level of oil in this sump. - Since this concern about low oil level in the sump of
primary shell 16 occurs only when both the booster and primary compressors are operating, other steps can be taken to address the potential problem in addition to relying on the mist and precipitation action described in the preceding paragraph. One solution is to program the system to turn off the booster compressor for a short time (on the order of 2-4 minutes). As described above for the operational state where the primary compressor is on and the booster is off, this will result in opening normallyopen valve 20, and any oil built up above normal level in the sump ofbooster shell 12 will be transferred to the sump ofprimary shell 16 viatransfer line 18. - Also, during defrost cycling and cooling operation, the booster compressor is off, and only the primary compressor is operating. Thus, normally
open check valve 20 will be open, and oil balance transfer can take place from the sump ofbooster shell 12 to the sump ofprimary shell 16. - While a preferred embodiment of the present invention has been shown and described, various modifications and substitutions may be made thereto without departing from the spirit and scope of the invention. Accordingly, it is to be understood that the present invention has been described by way of illustration and not limitation.
Claims (12)
Priority Applications (7)
Application Number | Priority Date | Filing Date | Title |
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US10/959,254 US20060073026A1 (en) | 2004-10-06 | 2004-10-06 | Oil balance system and method for compressors connected in series |
EP20050799577 EP1797376A1 (en) | 2004-10-06 | 2005-09-27 | Oil balance system and method for compressors |
US11/664,956 US7712329B2 (en) | 2004-10-06 | 2005-09-27 | Oil balance system and method for compressors |
PCT/US2005/034651 WO2006041682A1 (en) | 2004-10-06 | 2005-09-27 | Oil balance system and method for compressors |
CA 2583436 CA2583436C (en) | 2004-10-06 | 2005-09-27 | Oil balance system and method for compressors connected in series |
US11/952,366 US7651322B2 (en) | 2004-10-06 | 2007-12-07 | Oil balance system and method for compressors connected in series |
US12/143,172 US8075283B2 (en) | 2004-10-06 | 2008-06-20 | Oil balance system and method for compressors connected in series |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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US10/959,254 US20060073026A1 (en) | 2004-10-06 | 2004-10-06 | Oil balance system and method for compressors connected in series |
Related Parent Applications (1)
Application Number | Title | Priority Date | Filing Date |
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US11/952,366 Continuation US7651322B2 (en) | 2004-10-06 | 2007-12-07 | Oil balance system and method for compressors connected in series |
Related Child Applications (2)
Application Number | Title | Priority Date | Filing Date |
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US11/664,956 Continuation-In-Part US7712329B2 (en) | 2004-10-06 | 2005-09-27 | Oil balance system and method for compressors |
US11/952,366 Continuation US7651322B2 (en) | 2004-10-06 | 2007-12-07 | Oil balance system and method for compressors connected in series |
Publications (1)
Publication Number | Publication Date |
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US20060073026A1 true US20060073026A1 (en) | 2006-04-06 |
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ID=35735189
Family Applications (4)
Application Number | Title | Priority Date | Filing Date |
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US10/959,254 Abandoned US20060073026A1 (en) | 2004-10-06 | 2004-10-06 | Oil balance system and method for compressors connected in series |
US11/664,956 Expired - Fee Related US7712329B2 (en) | 2004-10-06 | 2005-09-27 | Oil balance system and method for compressors |
US11/952,366 Expired - Fee Related US7651322B2 (en) | 2004-10-06 | 2007-12-07 | Oil balance system and method for compressors connected in series |
US12/143,172 Expired - Fee Related US8075283B2 (en) | 2004-10-06 | 2008-06-20 | Oil balance system and method for compressors connected in series |
Family Applications After (3)
Application Number | Title | Priority Date | Filing Date |
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US11/664,956 Expired - Fee Related US7712329B2 (en) | 2004-10-06 | 2005-09-27 | Oil balance system and method for compressors |
US11/952,366 Expired - Fee Related US7651322B2 (en) | 2004-10-06 | 2007-12-07 | Oil balance system and method for compressors connected in series |
US12/143,172 Expired - Fee Related US8075283B2 (en) | 2004-10-06 | 2008-06-20 | Oil balance system and method for compressors connected in series |
Country Status (4)
Country | Link |
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US (4) | US20060073026A1 (en) |
EP (1) | EP1797376A1 (en) |
CA (1) | CA2583436C (en) |
WO (1) | WO2006041682A1 (en) |
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WO2009149726A1 (en) * | 2008-06-12 | 2009-12-17 | Carrier Corporation | Compressor for a refrigeration cycle, refrigeration cycle and method for operating the same |
US20110081254A1 (en) * | 2008-06-12 | 2011-04-07 | Carrier Corporation | Compressor for a refrigeration cycle, refrigeration cycle and method for operating the same |
CN101922430A (en) * | 2010-08-20 | 2010-12-22 | 桐乡锦瑞化纤有限公司 | High-low-pressure dual-purpose piston type air compressor as network yarn air source in terylene production process |
CN102278837A (en) * | 2011-01-28 | 2011-12-14 | 大连三洋压缩机有限公司 | Oil equalization system of compressor units |
EP2532991A3 (en) * | 2011-06-08 | 2018-04-04 | LG Electronics, Inc. | Refrigerating cycle apparatus and method for operating the same |
WO2013004974A1 (en) * | 2011-07-06 | 2013-01-10 | Electricite De France | Method for balancing lubricant levels in a multi-stage compression unit of a heat exchange system, and heat exchange system implementing such a method |
FR2977657A1 (en) * | 2011-07-06 | 2013-01-11 | Electricite De France | METHOD FOR BALANCING THE LUBRICANT LEVELS IN A MULTI-STAGE COMPRESSION UNIT OF A THERMAL EXCHANGE SYSTEM AND THERMAL EXCHANGE SYSTEM USING SUCH A METHOD |
WO2014154046A1 (en) * | 2013-03-29 | 2014-10-02 | 艾默生环境优化技术(苏州)有限公司 | Compressor system and control method therefor |
Also Published As
Publication number | Publication date |
---|---|
US8075283B2 (en) | 2011-12-13 |
US7651322B2 (en) | 2010-01-26 |
EP1797376A1 (en) | 2007-06-20 |
US7712329B2 (en) | 2010-05-11 |
WO2006041682A1 (en) | 2006-04-20 |
CA2583436C (en) | 2013-08-20 |
US20080283133A1 (en) | 2008-11-20 |
US20090007588A1 (en) | 2009-01-08 |
CA2583436A1 (en) | 2006-04-20 |
US20080085195A1 (en) | 2008-04-10 |
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