US20100050673A1 - Oil return algorithm for capacity modulated compressor - Google Patents
Oil return algorithm for capacity modulated compressor Download PDFInfo
- Publication number
- US20100050673A1 US20100050673A1 US12/203,164 US20316408A US2010050673A1 US 20100050673 A1 US20100050673 A1 US 20100050673A1 US 20316408 A US20316408 A US 20316408A US 2010050673 A1 US2010050673 A1 US 2010050673A1
- Authority
- US
- United States
- Prior art keywords
- compressor
- oil
- capacity
- set forth
- motor
- 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
- 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
-
- 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
-
- 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
- F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
-
- 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
- F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
-
- 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
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
- F25B49/022—Compressor control arrangements
-
- 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
- F25B2500/00—Problems to be solved
- F25B2500/16—Lubrication
Definitions
- This application relates to an algorithm for ensuring adequate oil return in a refrigerant system including a capacity modulated compressor.
- Compressors are utilized as an integral part of a refrigerant system.
- a compressor compresses a refrigerant and passes it downstream to a condenser.
- Refrigerant from the condenser passes through an expansion device, and then through an evaporator. From the evaporator, the refrigerant returns to the compressor.
- Lubricant is included in the refrigerant system, typically an Air Conditioner, Heat Pump or refrigeration application, and is particularly important to lubricate moving parts in the compressor.
- the lubricant becomes entrained in the refrigerant, and can flow with the refrigerant throughout the refrigerant system. As such, there may sometimes be an inadequate supply of lubricant returned to the compressor. Lubricant can sit in other areas of the refrigerant system, and in particular in the condenser and evaporator.
- compressor and refrigerant systems being of a variable capacity.
- Typical applications of the compressor's ability to vary capacity include variable speed, multi-stepped modulation, PWM of compression element engagement, or other means of affecting capacity and the mass flow rates of the compressor.
- the compressor may be operated at a lower capacity to improve energy efficiency. While operating at a higher capacity, the refrigerant may well drive sufficient lubricant back from the condenser and evaporator to the compressor such that there is an adequate lubricant supply. However, at lower capacities, it may sometimes be difficult to adequately drive the lubricant back.
- One known system periodically provides an increase in speed when the compressor is operating at the lower speed.
- the increased speed is maintained for a short period of time to drive lubricant back to the compressor.
- the increase in speed is not tied to any existing conditions in the refrigerant system, and thus may be operated too frequently, or not frequently enough.
- operating at the increased speed too frequency somewhat defeats the purpose of operating the compressor at the lower speed.
- running at the higher speed to return lubricant too infrequently would be even more undesirable.
- system conditions are monitored to predict an amount of oil migration from the compressor during low capacity operation.
- an increased compressor capacity is run for a period of time.
- a variable speed compressor is used as an example of a particular application of the invention.
- FIG. 1 schematically shows a refrigerant system.
- FIG. 2 is a chart showing oil loss per hour at various compressor speeds.
- FIG. 3 is a flowchart.
- a refrigerant system 20 is illustrated in FIG. 1 .
- a compressor shell 23 includes a lubricant sump 22 , which maintains a quantity of lubricant.
- a compressor pump unit 24 compresses refrigerant and delivers the refrigerant to a discharge tube 26 . From the discharge tube 26 , the lubricant passes through a condenser 28 , an expansion device 30 , an evaporator 32 , and back through a suction tube 33 into the compressor shell 23 .
- a control 36 for a compressor motor 37 may operate the compressor motor 37 at various speeds.
- the compressor may be operating at a relatively low speed to increase energy efficiency when a cooling demand is also low.
- Sensors 34 and 35 monitor a condition, such as pressure, at the evaporator 32 and condenser 28 , respectively.
- sensors that monitor temperature or an estimated saturated refrigerant temperature can be used to detect the conditions the compressor is operating at, These conditions may be sent to the control 36 to assist in quantifying the amount of oil which has likely migrated outwardly of the compressor shell 23 into other system components at low speed operation.
- a curve may be developed which equates oil loss for a period of time for various low compressor speeds.
- the oil loss no longer occurs.
- the present invention integrates the amount of oil loss over time based upon a relationship such as shown in FIG. 2 , and actuates the motor control 36 to increase the speed of the motor for a short period of oil return time when that integrated amount passes a particular limit.
- the amount of oil loss is calculated and the speed is increased when the amount passes a limit.
- the compressor speed may be ramped up from the low energy efficiency speed to a predetermined amount, e.g., 2400 rpm in a compressor having the characteristics as shown below, for a short period of time (e.g. 3 seconds).
- the point at which the oil return speed-up will occur can be defined as a function of the pressure at the suction and discharge of the compressor, as a function of compressor capacity or based upon other variables.
- a ten coefficient map can be utilized to set a curve similar to that shown in FIG. 2 .
- oil loss rate may be calculated as:
- oil loss rate (oz/hr) a 1 +a 2( PE )+ a 3( PC )+ a 4( PE ) 2 +a 5( PE )( PC )+ a 6( PC ) 2 +a 7( PE ) 3 +a 8( PE ) 2 ( PC )+ a 9( PE )( PC ) 2 +a 10( PC ) 3 .
- the oil loss rate shown above is based upon the pressure at the evaporator and the pressure at the condenser.
- the same form of equation could be applied to evap and condensing temperatures. It could also be multiplied by a multiplier which brings in a capacity level factor.
- variable speed compressors this would be the current rpm/max RPM.
- the quantity of oil which is “lost” or which has migrated from the compressor is calculated, or integrated, over time while the compressor is operating at a low capacity. Once that quantity exceeds a predetermined limit, then the compressor capacity is ramped up to the oil return speed for a short period of time.
- the amount of oil lost is calculated in a plurality of discrete time units when the compressor is operating at a lower speed. As an example, this can occur every five seconds.
Abstract
A control for a compressor motor is programmed to operate the motor at at least one low capacity and at least one higher capacity. The control is operable to estimate an amount of oil which will have migrated from said compressor shell, at least when the compressor is operating at the lower capacity rate. The motor control moves the compressor motor from the lower capacity to at least one higher capacity once the estimated quantity of oil exceeds a predetermined limit. The capacity may be related to space.
Description
- This application relates to an algorithm for ensuring adequate oil return in a refrigerant system including a capacity modulated compressor.
- Compressors are utilized as an integral part of a refrigerant system. In general, a compressor compresses a refrigerant and passes it downstream to a condenser. Refrigerant from the condenser passes through an expansion device, and then through an evaporator. From the evaporator, the refrigerant returns to the compressor.
- Lubricant is included in the refrigerant system, typically an Air Conditioner, Heat Pump or refrigeration application, and is particularly important to lubricate moving parts in the compressor. However, the lubricant becomes entrained in the refrigerant, and can flow with the refrigerant throughout the refrigerant system. As such, there may sometimes be an inadequate supply of lubricant returned to the compressor. Lubricant can sit in other areas of the refrigerant system, and in particular in the condenser and evaporator.
- Recently, system energy efficiency improvements have resulted in the compressor and refrigerant systems being of a variable capacity. Typical applications of the compressor's ability to vary capacity include variable speed, multi-stepped modulation, PWM of compression element engagement, or other means of affecting capacity and the mass flow rates of the compressor. Thus, should the cooling demand on the refrigerant system be low, the compressor may be operated at a lower capacity to improve energy efficiency. While operating at a higher capacity, the refrigerant may well drive sufficient lubricant back from the condenser and evaporator to the compressor such that there is an adequate lubricant supply. However, at lower capacities, it may sometimes be difficult to adequately drive the lubricant back.
- One known system periodically provides an increase in speed when the compressor is operating at the lower speed. The increased speed is maintained for a short period of time to drive lubricant back to the compressor. However, the increase in speed is not tied to any existing conditions in the refrigerant system, and thus may be operated too frequently, or not frequently enough. Of course, operating at the increased speed too frequency somewhat defeats the purpose of operating the compressor at the lower speed. On the other hand, running at the higher speed to return lubricant too infrequently would be even more undesirable.
- In a disclosed embodiment of this invention, system conditions are monitored to predict an amount of oil migration from the compressor during low capacity operation. When a particular amount of lubricant is deemed to have migrated from the compressor, an increased compressor capacity is run for a period of time. As an example of a particular application of the invention, a variable speed compressor is used.
- These and other features of the present invention can be best understood from the following specification and drawings, the following of which is a brief description.
-
FIG. 1 schematically shows a refrigerant system. -
FIG. 2 is a chart showing oil loss per hour at various compressor speeds. -
FIG. 3 is a flowchart. - A
refrigerant system 20 is illustrated inFIG. 1 . Acompressor shell 23 includes alubricant sump 22, which maintains a quantity of lubricant. Acompressor pump unit 24 compresses refrigerant and delivers the refrigerant to adischarge tube 26. From thedischarge tube 26, the lubricant passes through acondenser 28, anexpansion device 30, anevaporator 32, and back through asuction tube 33 into thecompressor shell 23. - A
control 36 for acompressor motor 37 may operate thecompressor motor 37 at various speeds. Thus, the compressor may be operating at a relatively low speed to increase energy efficiency when a cooling demand is also low. -
Sensors evaporator 32 andcondenser 28, respectively. Alternatively, sensors that monitor temperature or an estimated saturated refrigerant temperature can be used to detect the conditions the compressor is operating at, These conditions may be sent to thecontrol 36 to assist in quantifying the amount of oil which has likely migrated outwardly of thecompressor shell 23 into other system components at low speed operation. - As shown in
FIG. 2 , a curve may be developed which equates oil loss for a period of time for various low compressor speeds. Thus, as shown, at some point, here 2400 rpm, the oil loss no longer occurs. However, at other speeds, there is pronounced oil loss. - The present invention integrates the amount of oil loss over time based upon a relationship such as shown in
FIG. 2 , and actuates themotor control 36 to increase the speed of the motor for a short period of oil return time when that integrated amount passes a particular limit. - Thus, as shown in the flowchart of
FIG. 3 , the amount of oil loss is calculated and the speed is increased when the amount passes a limit. - In one embodiment, the compressor speed may be ramped up from the low energy efficiency speed to a predetermined amount, e.g., 2400 rpm in a compressor having the characteristics as shown below, for a short period of time (e.g. 3 seconds).
- The point at which the oil return speed-up will occur can be defined as a function of the pressure at the suction and discharge of the compressor, as a function of compressor capacity or based upon other variables. A ten coefficient map can be utilized to set a curve similar to that shown in
FIG. 2 . - Thus, the oil loss rate may be calculated as:
-
oil loss rate (oz/hr)=a1+a2(PE)+a3(PC)+a4(PE)2 +a5(PE)(PC)+a6(PC)2 +a7(PE)3 +a8(PE)2(PC)+a9(PE)(PC)2 +a10(PC)3. - The oil loss rate shown above is based upon the pressure at the evaporator and the pressure at the condenser. The same form of equation could be applied to evap and condensing temperatures. It could also be multiplied by a multiplier which brings in a capacity level factor. One such multiplier factor may be determined by the following equation: Multiplier factor=b1(Rc)̂3+b2(Rc)̂2+b3(Rc)+b4.
- Where Rc=Current capacity level/Max capacity level
- As an example of this, for variable speed compressors this would be the current rpm/max RPM.
- With the present invention, and once an adequate curve is developed, the quantity of oil which is “lost” or which has migrated from the compressor is calculated, or integrated, over time while the compressor is operating at a low capacity. Once that quantity exceeds a predetermined limit, then the compressor capacity is ramped up to the oil return speed for a short period of time.
- In one application, the amount of oil lost is calculated in a plurality of discrete time units when the compressor is operating at a lower speed. As an example, this can occur every five seconds.
- Although an embodiment of this invention has been disclosed, a worker of ordinary skill in this art would recognize that certain modifications would come within the scope of this invention. For that reason, the following claims should be studied to determine the true scope and content of this invention.
Claims (18)
1. A compressor comprising:
a compressor pump unit, and said compressor pump unit and said motor being housed within a shell, said shell having a sump for maintaining a quantity of lubricant;
a control for said compressor, said control being programmed to operate at at least one low capacity and at least one higher capacity, and said control also being operable to estimate an amount of oil which will have migrated from said compressor shell at least when said compressor is operating at said at least one lower capacity, and said motor control being operable to move said compressor motor from the at least one lower capacity to the at least one higher capacity once the estimated quantity of oil exceeds a predetermined limit.
2. The compressor as set forth in claim 1 , wherein said at least one lower capacity and said at least one higher capacity are achieved by varying the speed of the motor.
3. The compressor as set forth in claim 1 , wherein said estimate of the amount of oil is based upon pressures in the system.
4. The compressor as set forth in claim 3 , wherein the amount of oil estimate is based upon the pressures at both a condenser and an evaporator that are connected to said compressor.
5. The compressor as set forth in claim 3 , wherein the amount of oil estimate is based upon the estimated saturated temperature at both a condenser and an evaporator that are connected to said compressor
6. The compressor as set forth in claim 1 , wherein said estimate of the amount of oil is based upon temperature measurements.
7. The compressor as set forth in claim 1 , wherein a multiplier factor which includes a Capacity ratio quantity multiplied by an oil loss rate calculated from the pressures or estimate of saturated temperatures at said condenser and said evaporator.
8. A refrigerant system comprising:
a condenser, an evaporator, an expansion device and a compressor;
the compressor having a motor for driving a compressor pump unit, and said compressor pump unit and motor being housed within a shell, said shell having a sump for maintaining a quantity of lubricant, a control for said motor, said control being programmed to operate at at least one low capacity and at least one higher capacity, and said control also being operable to estimate an amount of oil which will have migrated from said compressor shell at least when said compressor is operating at said at least one lower capacity, and said motor control being operable to move said compressor motor from the at least one lower capacity to the at least one higher capacity once the estimated quantity of oil exceeds a predetermined limit.
9. The refrigerant system as set forth in claim 8 , wherein said estimate of the amount of oil lost is based upon pressures in the system.
10. The refrigerant system as set forth in claim 8 , wherein the amount of oil estimate is based upon the pressures at both the condenser and the evaporator.
11. The refrigerant system as set forth in claim 8 , wherein a multiplier factor which includes an RPM quantity is multiplied by an oil loss rate calculated from the pressures at said condenser and said evaporator.
12. The refrigerant system as set forth in claim 8 , wherein said at least one lower capacity and said at least one higher capacity are achieved by varying the speed of the motor.
13. A method of operating a compressor comprising the steps of:
(a) operating a motor for a compressor at at least one low capacity and at least one higher capacity;
(b) estimating an amount of oil which will have migrated from a compressor shell at least when said compressor is operating at said at least one lower capacity rate; and
(c) moving said motor from the at least one lower capacity to the at least one higher capacity once the estimated quantity of oil exceeds a predetermined limit.
14. The method as set forth in claim 13 , wherein said estimate of the amount of oil lost is based upon pressures in the system.
15. The method as set forth in claim 14 , wherein the amount of oil estimate is based upon the pressures at both a condenser and an evaporator that are connected to said compressor.
16. The method as set forth in claim 13 , wherein a multiplier factor which includes an RPM quantity is multiplied by an oil loss rate calculated from the pressures at said condenser and said evaporator.
17. The method as set forth in claim 13 , wherein said at least one lower capacity and said at least one higher capacity are achieved by varying the speed of the motor
18. The method as set forth in claim 13 , wherein said estimate of the amount of oil is based upon temperature measurements.
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US12/203,164 US20100050673A1 (en) | 2008-09-03 | 2008-09-03 | Oil return algorithm for capacity modulated compressor |
KR1020090042416A KR20100027946A (en) | 2008-09-03 | 2009-05-15 | Oil return algorithm for capacity modulated compressor |
EP09251462A EP2161519A1 (en) | 2008-09-03 | 2009-06-01 | Oil return algorithm for capacity modulated compressor |
CN200910147499.8A CN101666305B (en) | 2008-09-03 | 2009-06-16 | Oil return algorithm for capacity modulated compressor |
JP2009164618A JP2010059962A (en) | 2008-09-03 | 2009-07-13 | Oil return algorithm for capacity modulated compressor |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US12/203,164 US20100050673A1 (en) | 2008-09-03 | 2008-09-03 | Oil return algorithm for capacity modulated compressor |
Publications (1)
Publication Number | Publication Date |
---|---|
US20100050673A1 true US20100050673A1 (en) | 2010-03-04 |
Family
ID=41202660
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US12/203,164 Abandoned US20100050673A1 (en) | 2008-09-03 | 2008-09-03 | Oil return algorithm for capacity modulated compressor |
Country Status (5)
Country | Link |
---|---|
US (1) | US20100050673A1 (en) |
EP (1) | EP2161519A1 (en) |
JP (1) | JP2010059962A (en) |
KR (1) | KR20100027946A (en) |
CN (1) | CN101666305B (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US10473377B2 (en) | 2016-09-26 | 2019-11-12 | Carrier Corporation | High outdoor ambient and high suction pressure oil pump out mitigation for air conditioners |
US11247534B2 (en) * | 2017-10-12 | 2022-02-15 | Hanon Systems | Method of controlling compressor |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2853742B1 (en) * | 2013-09-27 | 2016-04-20 | Emerson Climate Technologies GmbH | Method and apparatus for oil sensing in a compressor |
CN110986430B (en) * | 2019-12-31 | 2020-11-10 | 珠海格力电器股份有限公司 | Effective oil return control method and device and air conditioning unit |
DE102021210048A1 (en) * | 2021-09-10 | 2023-03-16 | BSH Hausgeräte GmbH | Operating a speed-controlled compressor of a household refrigeration appliance |
Citations (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4722196A (en) * | 1985-10-31 | 1988-02-02 | Kabushiki Kaisha Toshiba | Device for controlling refrigeration cycle capacity |
US5067326A (en) * | 1979-07-31 | 1991-11-26 | Alsenz Richard H | Method and apparatus for controlling capacity of a multiple-stage cooling system |
US5263822A (en) * | 1989-10-31 | 1993-11-23 | Matsushita Electric Industrial Co., Ltd. | Scroll compressor with lubrication passages to the main bearing, revolving bearing, back-pressure chamber and compression chambers |
US5417078A (en) * | 1994-06-13 | 1995-05-23 | Carrier Corporation | Refrigerator flow control apparatus |
US20030051494A1 (en) * | 2001-09-20 | 2003-03-20 | Shigeki Ohya | Refrigerant cycle system including two evaporators |
US20050103035A1 (en) * | 2003-11-19 | 2005-05-19 | Massachusetts Institute Of Technology | Oil circulation observer for HVAC systems |
US20050204756A1 (en) * | 2004-03-22 | 2005-09-22 | Dobmeier Thomas J | Monitoring refrigerant charge |
US20070130973A1 (en) * | 2005-05-04 | 2007-06-14 | Scroll Technologies | Refrigerant system with multi-speed scroll compressor and economizer circuit |
US20080008614A1 (en) * | 2006-07-07 | 2008-01-10 | Takao Mizuno | Horizontal type scroll compressor |
US7370487B2 (en) * | 2004-07-20 | 2008-05-13 | Denso Corporation | Refrigerating cycle device capable of ensuring oil return |
US20080134701A1 (en) * | 2006-12-12 | 2008-06-12 | Ole Moelgaard Christensen | Variable Compressor Oil Return |
US20090324426A1 (en) * | 2008-06-29 | 2009-12-31 | Moody Bruce A | Compressor speed control system for bearing reliability |
US20100175396A1 (en) * | 2006-08-22 | 2010-07-15 | Carrier Corporation | Oil return in refrigerant system |
US7854137B2 (en) * | 2005-06-07 | 2010-12-21 | Carrier Corporation | Variable speed compressor motor control for low speed operation |
-
2008
- 2008-09-03 US US12/203,164 patent/US20100050673A1/en not_active Abandoned
-
2009
- 2009-05-15 KR KR1020090042416A patent/KR20100027946A/en not_active Application Discontinuation
- 2009-06-01 EP EP09251462A patent/EP2161519A1/en not_active Withdrawn
- 2009-06-16 CN CN200910147499.8A patent/CN101666305B/en not_active Expired - Fee Related
- 2009-07-13 JP JP2009164618A patent/JP2010059962A/en active Pending
Patent Citations (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5067326A (en) * | 1979-07-31 | 1991-11-26 | Alsenz Richard H | Method and apparatus for controlling capacity of a multiple-stage cooling system |
US4722196A (en) * | 1985-10-31 | 1988-02-02 | Kabushiki Kaisha Toshiba | Device for controlling refrigeration cycle capacity |
US5263822A (en) * | 1989-10-31 | 1993-11-23 | Matsushita Electric Industrial Co., Ltd. | Scroll compressor with lubrication passages to the main bearing, revolving bearing, back-pressure chamber and compression chambers |
US5417078A (en) * | 1994-06-13 | 1995-05-23 | Carrier Corporation | Refrigerator flow control apparatus |
US20030051494A1 (en) * | 2001-09-20 | 2003-03-20 | Shigeki Ohya | Refrigerant cycle system including two evaporators |
US20050103035A1 (en) * | 2003-11-19 | 2005-05-19 | Massachusetts Institute Of Technology | Oil circulation observer for HVAC systems |
US20050204756A1 (en) * | 2004-03-22 | 2005-09-22 | Dobmeier Thomas J | Monitoring refrigerant charge |
US7370487B2 (en) * | 2004-07-20 | 2008-05-13 | Denso Corporation | Refrigerating cycle device capable of ensuring oil return |
US20070130973A1 (en) * | 2005-05-04 | 2007-06-14 | Scroll Technologies | Refrigerant system with multi-speed scroll compressor and economizer circuit |
US7854137B2 (en) * | 2005-06-07 | 2010-12-21 | Carrier Corporation | Variable speed compressor motor control for low speed operation |
US20080008614A1 (en) * | 2006-07-07 | 2008-01-10 | Takao Mizuno | Horizontal type scroll compressor |
US20100175396A1 (en) * | 2006-08-22 | 2010-07-15 | Carrier Corporation | Oil return in refrigerant system |
US20080134701A1 (en) * | 2006-12-12 | 2008-06-12 | Ole Moelgaard Christensen | Variable Compressor Oil Return |
US20090324426A1 (en) * | 2008-06-29 | 2009-12-31 | Moody Bruce A | Compressor speed control system for bearing reliability |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US10473377B2 (en) | 2016-09-26 | 2019-11-12 | Carrier Corporation | High outdoor ambient and high suction pressure oil pump out mitigation for air conditioners |
US11247534B2 (en) * | 2017-10-12 | 2022-02-15 | Hanon Systems | Method of controlling compressor |
Also Published As
Publication number | Publication date |
---|---|
KR20100027946A (en) | 2010-03-11 |
EP2161519A1 (en) | 2010-03-10 |
JP2010059962A (en) | 2010-03-18 |
CN101666305A (en) | 2010-03-10 |
CN101666305B (en) | 2014-12-03 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
CN100339664C (en) | Refrigeration system | |
CN101162104B (en) | Air-conditioning apparatus | |
US8745999B2 (en) | Heat pump apparatus | |
US20100050673A1 (en) | Oil return algorithm for capacity modulated compressor | |
EP2823239B1 (en) | Intelligent compressor flooded start management | |
JP6509013B2 (en) | Refrigerating apparatus and refrigerator unit | |
CN112393482B (en) | Variable-frequency air-cooled water chilling unit and variable-working-condition starting control method thereof | |
US11187449B2 (en) | System and method for dynamically determining refrigerant film thickness and dynamically controlling refrigerant film thickness at rolling-element bearing of an oil free chiller | |
AU2005267347B2 (en) | Improved lubricant return schemes in refrigerant cycle | |
WO2007123085A1 (en) | Refrigeration device | |
WO2016047305A1 (en) | Control device and control method for bleed device | |
JP2008128493A (en) | Refrigerating circuit, and air conditioner for vehicle using the same | |
JP2003279175A5 (en) | ||
KR200471061Y1 (en) | Refrigerating system | |
US11624539B2 (en) | Maintaining superheat conditions in a compressor | |
CN100376854C (en) | Unit for calculating refrigerant suction pressure of compressor in refrigeration cycle | |
JP2008128570A (en) | Refrigerating apparatus | |
JP6086236B2 (en) | Capacity control method and capacity control device for compressor of refrigeration equipment | |
JP2004322933A (en) | Refrigerating cycle device for vehicle | |
KR100792052B1 (en) | Refrigerator | |
CN113390168A (en) | Air conditioner control method and device, air conditioner and storage medium | |
JP2008057835A (en) | Refrigerating apparatus | |
JP4236163B2 (en) | Ammonia refrigeration system using working fluid composition composed of lubricating oil and ammonia refrigerant | |
US11435125B2 (en) | Heating compressor at start-up | |
JPH10246521A (en) | Freezer, air conditioner and method for assembling refrigerant circuit |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: SCROLL TECHNOLOGIES,ARKANSAS Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:HAHN, GREGORY W.;REEL/FRAME:021471/0532 Effective date: 20080902 |
|
AS | Assignment |
Owner name: DANFOSS SCROLL TECHNOLOGIES, LLC,ARKANSAS Free format text: CHANGE OF NAME;ASSIGNOR:SCROLL TECHNOLOGIES, LLC;REEL/FRAME:022664/0098 Effective date: 20080815 |
|
STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO PAY ISSUE FEE |