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US3767328A - Rotary compressor with capacity modulation - Google Patents

Rotary compressor with capacity modulation Download PDF

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Publication number
US3767328A
US3767328A US3767328DA US3767328A US 3767328 A US3767328 A US 3767328A US 3767328D A US3767328D A US 3767328DA US 3767328 A US3767328 A US 3767328A
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port
cylinder
compressor
plunger
suction
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W Ladusaw
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General Electric Co
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General Electric Co
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C28/00Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/10Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
    • F04C28/16Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using lift valves

Abstract

A rotary refrigerant compressor comprising a compression cylinder, a rotor eccentrically rotatable in the cylinder, suction and discharge ports communicating with the cylinder and a vane slidably mounted in a slot in the cylinder wall between the ports dividing the cylinder into high and low pressure sides includes means for modulating the compressor capacity. The modulation means comprises a bore communicating with the cylinder at a point intermediate the suction and discharge ports and having a modulating port on a side wall of the bore connected to the suction port. The modulating port is opened or closed by means of a plunger slidably mounted in the bore to modulate the compressor capacity.

Description

United States Patent [1 1 Ladusaw Oct. 23, 1973 [75] lnventor: William T. Ladusaw, Louisville, Ky.

[73] Assignee: General Electric Company,

Louisville, Ky.

[22] Filed: July 19, 1972 [21] Appl. No; 273,117

Primary ExaminerCarlton R. Croyle Assistant ExaminerRichard Sher AttorneyWalter E Rule et al.

[57] ABSTRACT A rotary refrigerant compressor comprising a compression cylinder, a rotor eccentrically rotatable in the cylinder, suction and discharge ports communicating with the cylinder and a vane slidably mounted in a slot in the cylinder wall between the ports dividing the cylinder into high and low pressure sides includes means for modulating the compressor capacity. The modulation means comprises a bore communicating with the cylinder at a point intermediate the suction and discharge ports and having a modulating port on a side wall of the bore connected to the suction port. The modulating port is opened or closed by means of'a plunger slidably mounted in the bore to modulate the compressor capacity.

4 Claims, 3 Drawing Figures ROTARY COMPRESSOR WITH CAPACITY MODULATION BACKGROUND OF THE INVENTION In many uses of refrigerant compressors, it is desirable to be able to reduce the capacity or volume of displacement of the compressor under certain operating conditions in order to provide a cooling rate more closely matching the heat load. A means intended to provide the modulation or partial unloading of a rotary compressor is described in US. Pat. No. 2,904,973- Kosfeld as comprising an unloading or bypass passage having an unloading port communicating with the compressor cylinder in spaced relationship with the suction port and valve means in the port. In the compressor disclosed in the Kosfeld patent, the port contains a check valve. The compressor is intended to operate at full capacity by introducing high pressure refrigerant into the bypass passage behind the check valve to hold the valve closed. When suction pressure is substituted, the valve opens and gas compression in the cylinder is delayed until the passage is sealed by the rotor.

A check valve of the type disclosed in the Kosfeld patent has certain disadvantages. Under the changing pressure conditions within the compressor cylinder, it may not remain completely seated or completely open under varying operating conditions. In other words, a check valve operating only on pressure differences does not have a positiveflow control for assuring continued operation of the compressor at either full or reduced capacity. Specifically, the Kosfeld unloading means having the control port and valve in the cylinder wall does not provide a high-low pressure seal when the rotor is tangent to the port. When the rotor reaches the center of the modulating port, the vertical seal is lost and high pressure gas leaks into and out of the port past the rotor cylinder wall seal and into the low pressure side causing'a reduced compressor performance. Also, all gas compressed into the volume between the cylinder wall and the check valve, along with abovedescribed volume of leakage, is re-expanded to occupy suction volume when the rotor tangent point is passing the unloader port. This reduces effective displacement and causes decrease in efficiency as well.

SUMMARY OF THE INVENTION It is a general object of the present invention to provide a rotary compressor of the stationary vane type with improved valving means for controlling the full and partial capacity operation of the compressor.

In accordance with the preferred embodiment of the invention, there is provided a hermetic rotary refrigerant compressor comprising a hermetic casing containing a rotary-compressor including a cylinder block having a cylindrical wall defining a compression cylinder, a rotor eccentrically rotatable in the cylinder, spaced suction and discharge ports in the wall communicating with the cylinder and a vane slidably mounted between the ports for engagement with the rotor to divide the cylinder into high and low pressure sides or chambers. In order to modulate the capacity of the compressor, there is provided a radially extending bore in the cylinder wall spaced from the suction port and communicating with the cylinder. A modulating port in a wall portion of the bore is connected by a passage to the suction port and is opened or closed by means of a plunger slidably mounted in the bore for movement between a restracted position in which the modulating port is open and an extended position in which the plunger engages the rotor and closes the port. For the purpose of positioning the rotor in one or the other of these two positions, means are provided for introducing either high pressure or suction'pressure refrigerant into the bore rearwardly of the plunger. Preferably, also, there is provided a spring means for assisting retraction of the plunger.

BRIEF DESCRIPTION OF THE DRAWING In the accompanying drawing:

FIG. 1 is an elevational view, partly in section, of a hermetic compressor incorporating the present invention;

FIG. 2 is a sectional view taken along line 2-2 of FIG. 1; and

FIG. 3 is a schematic view of a refrigeration system disclosing one means for controlling the operation of the unloading valve.

DESCRIPTION OF THE PREFERRED EMBODIMENT With reference to FIGS. 1 and 2 of the drawing, there is shown a hermetic compressor comprising a casing l in which there is disposed a rotary compressor unit 2 connected by means of a drive shaft 3 to an electric motor 4. The compressor includes a cylinder block 5 having an inner cylinderical wall or surface 6 which, in combination with upper and low end plates 8 and 9, defines an annular compression cylinder 10. A rotor or roller 11 driven by and rotatable on an eccentric 12 on the shaft 3 is contained within the cylinder 10. A vane 14 is slidably disposed within a radial slot 15 in the cylinder wall 6 and is adapted to engage the periphery of the rotor 11 to divide the cylinder into a high pressure side 16 and a low pressure side 17.

A low pressure or suction port 18 communicates with the cylinder on the low pressure side 17 of the vane 14 and an outlet or discharge port 19 communicates with the high pressure side 16 of the cylinder on the opposite side of the vane. The discharge port 19 includes a discharge valve 20 for assuring proper compression of the gases issuing through the discharge port and for preventing reverse flow of discharge gases back into the compression cylinder. The discharge gas entering the valve chamber 21 passes through'a passage 22 in the upper plate 8 into the upper portion of the case 1.

A compressor of this type is adapted to be connected into a refrigeration system as shown, for example, in the schematic of FIG. 3.

Such a system, in addition to the compressor, in-

cludes a condenser 26, a capillary flow restrictor 27 and an evaporator 28. Low pressure refrigerant is withdrawn from the evaporator 28 through a suction line 29 connected to the suction port 18 and high pressure refrigerant is discharged from the compressor case through a discharge line 20 to the condenser. As the compressor rotor 12 rotates, in a clockwise direction as viewed in FIG. 2 of the drawing, low pressure refrigerant is drawn into the cylinder through the suction port 18, is compressed by rotation of the rotor and the compressed refrigerant is discharged through the discharge passage 19.

It will be seen that the maximum volume displacement of this type of compressor occurs at a time during the cycle of rotation of the rotor when the periphery of the rotor engaging the cylinder wall progresses just beyond the suction port 18. At this point the maximum volume of gas has been drawn into the cylinder and the suction port sealed by the rotor for compression of the gas during the remaining portion of the rotor cycle.

For the purpose of decreasing the volume of gas compressed by the rotor during each cycle, or, in other words, to decrease the capacity of the compressor, means are provided for delaying the closing of the suction port connection to the compression cylinder or, in other words, decreasing the volumetric capacity of the effective compressor cylinder.

The present invention is directed to an improved valve means for controlling the modulating means. The modulating and valving means comprises a cylindrical bore 32 in the cylinder wall member spaced from the vane 14 and opening into the cylinder and a modulating port 33 (FIG. 2) opening into the wall of the bore at a point spaced from the cylinder end 34 thereof. Means within the casing for connecting this port to suction port 18 comprises, in series, a passage 35 in the cylinder block, a tubular conduit 36 and a second block passage 37. The valving of port 33 is accomplished by means of a plunger 38 slidably positioned in the bore 32 and adapted to move between an extended position, as illustrated in FIG. 1 of the drawing, in which the plunger engages rotor 11 and closes the port 33 in all positions of the rotor 11 and a retracted position in which the plunger is recessed in the bore a distance sufficient to open the port 33. Thus, when the plunger is in its extended position, the modulating port 33 is closed and while it is in its retracted position the modulating port 33 is open to the compression volume through cylinder bore 32.

For full displacement operating conditions, the plunger is positioned in its fully extended position where it is in constant contact with the rotor completely filling the cylinder end on the bore. The end of the plunger is provided with a flat face so that the cylindrical wall vertical seal of the rotor will be maintained when the rotor passes the point of the plunger location in the cylindrical wall.

To maintain the plunger in contact with the rotor and thereby close the modulating port 33, high or discharge pressure can be introduced into the bore 32 behind the plunger 38. When reduced capacity is desired, suction pressure is valved to the volume behind the plunger. This low pressure reduces the gas force on the plunger so that the plunger can move to its retracted position. Preferably, there isalso provided a tension spring 41 threaded into the outer end of the plunger and having tension force biasing the plunger to its retracted position. In the retracted position of the plunger, the modulating port 33 is open so that the cylinder is connected to suction pressure until such time as the rotor closes the outlet or cylinder end of the bore. For example, by positioning of the bore as illustrated about 180 from the suction port, there is reduction in compressor capacity of approximately 42 percent when the modulating port is open, since the compression of the gas within the cylinder does not start until the rotor has passed the point of sealing the bore at which time part of the suction gas drawn into the cylinder through port 18 has been expelled through the modulating port 33 and the passage to the suction port.

Any suitable means may be provided for selectively connecting the volume of the bore behind the plunger to either discharge or suction pressures. The means schematically illustrated in FIG. 3 of the drawing comprises a three-way valve 45 having an outlet 46 connected to the bore 32. In one position of the three-way valve 45, the line 46 is connected by line 47 to the system discharge line 30 so that high pressure refrigerant is introduced into the bore. In the other position of the valve, the line 48 connects the suction line 29 to the bore so that the volume of the bore behind the plunger is at suction pressure. Thus, the positioning of the three-way valve 45 controls the positioning of the plunger 38 and hence the capacity modulation of the compressor by using system pressures.

During startup of the compressor, when the pressures are substantially equal throughout the system, the plunger 38 will normally be retracted with the aid of the tension spring 41 and the compressor will start in a partially unloaded condition of operation. If the three-way valve 45 is set to operate the compressor at full capacity, the discharge pressure built up in line 30 will thereafter force the plunger to its extended position to close the modulating port 33.

An alternative means for controlling the modulation of the compressor comprises the substitution of a solenoid for the three-way valve 45 and its connections to the system and bore and connecting the solenoid armature directly to the plunger 38. An armature spring forming part of the solenoid is employed to hold the plunger into contact with the rotor when the solenoid coil is not energized, the spring flexing to permit plunger movement during rotation of the rotor. When compressor capacity is to be reduced, energization of the coil and compression of the spring removes the plunger back past the port 33.

From the foregoing description, it will be seen that the valving arrangement of the present invention provides a positive control of the flow of gas through the modulating port. The spring aids in retaining the plunger in its retracted position and also assures full opening of the port 33 under conditions in which the pressure behind the plunger may be somewhat higher than cylinder pressure due to a pressure drop between the connection point of tube 48 and the cylinder pressure. When the plunger is extended in engagement with the rotor, its mass and the minimal effect of cylinder gas pressure thereon assures continuous closing of the port 33.

While there has been shown and described specific embodiments of the invention, it will be understood that it is not limited thereto and it is intended by the appended claims to cover all such modifications as fall within the true spirit and scope of the invention.

I claim:

1. A hermetic rotary refrigerant compressor comprising:

a hermetic casing;

a rotary compressor positioned in said casing and comprising means including a cylindrical wall member defining a compression cylinder;

a rotor eccentrically rotatable in said cylinder;

spaced suction and discharge ports in said wall member communicating with said cylinder;

a vane slidably mounted in said cylindrical wall member between said ports for engagement with said rotor to divide said cylinder into high and low pressure sides; and

means for modulating the capacity of said compressor comprising:

a radially extending bore in said cylindrical wall member spaced from said suction port and communicating with said cylinder;

means including a passage in said wall member having a modulating port in a wall portion of said bore connecting said suction port to said bore; and

a plunger slidably mounted in said bore for movement between a retracted position opening said modulating port and an extended position closing said modulating port and contacting said rotor.

2. A compressor according to claim 1 including means connecting the volume of said bore behind said plunger to discharge pressure for normally holding said plunger to its extended position; and

means connecting said volume to suction pressure to move said plunger to its retracted position for opening said modulating port and thereby reducing the capacity of said compressor.

3. A compressor according to claim 1 including tension spring means biasing said plunger to its retracted position.

4. A compressor according to claim 1 in which the connection to said suction port is within the hermetic casing.

Claims (4)

1. A hermetic rotary refrigerant compressor comprising: a hermetic casing; a rotary compressor positioned in said casing and comprising means including a cylindrical wall member defining a compression cylinder; a rotor eccentrically rotatable in said cylinder; spaced suction and discharge ports in said wall member communicating with said cylinder; a vane slidably mounted in said cylindrical wall member between said ports for engagement with said rotor to divide said cylinder into high and low pressure sides; and means for modulating the capacity of said compressor comprising: a radially extending bore in said cylindrical wall member spaced from said suction port and communicating with said cylinder; means including a passage in said wall member having a modulating port in a wall portion of said bore connecting said suction port to said bore; and a plunger slidably mounted in said bore for movement between a retracted position opening said modulating port and an extended position closing said modulating port and contacting said rotor.
2. A compressor according to claim 1 including means connecting the volume of said bore behind said plunger to discharge pressure for normally holding said plunger to its extended position; and means connecting said volume to suction pressure to move said plunger to its retracted position for opening said modulating port and thereby reducing the capacity of said compressor.
3. A compressor according to claim 1 including tension spring means biasing said plunger to its retracted position.
4. A compressor according to claim 1 in which the connection to said suction port is within the hermetic casing.
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Cited By (36)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5214253A (en) * 1975-06-18 1977-02-03 Daikin Ind Ltd Cooling system
FR2490749A1 (en) * 1980-09-19 1982-03-26 Mitsubishi Heavy Ind Ltd capacity control device for a compressor
US4331002A (en) * 1981-03-12 1982-05-25 General Electric Company Rotary compressor gas injection
EP0085246A1 (en) * 1981-12-21 1983-08-10 Sanden Corporation A control circuit for a variable displacement air conditioning compressor
US4522038A (en) * 1982-06-04 1985-06-11 Tokyo Shibaura Denki Kabushiki Kaisha Refrigerating cycle apparatus
US4558993A (en) * 1983-08-03 1985-12-17 Matsushita Electric Industrial Co., Ltd. Rotary compressor with capacity modulation
US4664608A (en) * 1985-11-04 1987-05-12 General Electric Company Rotary compressor with reduced friction between vane and vane slot
EP0519580A2 (en) * 1988-08-12 1992-12-23 Mitsubishi Jukogyo Kabushiki Kaisha Rotary compressor
US6551069B2 (en) * 2001-06-11 2003-04-22 Bristol Compressors, Inc. Compressor with a capacity modulation system utilizing a re-expansion chamber
US6663358B2 (en) * 2001-06-11 2003-12-16 Bristol Compressors, Inc. Compressors for providing automatic capacity modulation and heat exchanging system including the same
WO2006014081A1 (en) * 2004-08-06 2006-02-09 Lg Electronics Inc. Capacity variable device for rotary compressor and driving method of air conditioner having the same
US7290398B2 (en) 2003-08-25 2007-11-06 Computer Process Controls, Inc. Refrigeration control system
US7594407B2 (en) 2005-10-21 2009-09-29 Emerson Climate Technologies, Inc. Monitoring refrigerant in a refrigeration system
US7596959B2 (en) 2005-10-21 2009-10-06 Emerson Retail Services, Inc. Monitoring compressor performance in a refrigeration system
US7644591B2 (en) 2001-05-03 2010-01-12 Emerson Retail Services, Inc. System for remote refrigeration monitoring and diagnostics
US7665315B2 (en) 2005-10-21 2010-02-23 Emerson Retail Services, Inc. Proofing a refrigeration system operating state
US7752853B2 (en) 2005-10-21 2010-07-13 Emerson Retail Services, Inc. Monitoring refrigerant in a refrigeration system
US7752854B2 (en) 2005-10-21 2010-07-13 Emerson Retail Services, Inc. Monitoring a condenser in a refrigeration system
US20100305718A1 (en) * 2009-05-29 2010-12-02 Emerson Retail Services, Inc. System and method for monitoring and evaluating equipment operating parameter modifications
US7885961B2 (en) 2005-02-21 2011-02-08 Computer Process Controls, Inc. Enterprise control and monitoring system and method
US20110071960A1 (en) * 2002-10-31 2011-03-24 Emerson Retail Services, Inc. System For Monitoring Optimal Equipment Operating Parameters
US20110112814A1 (en) * 2009-11-11 2011-05-12 Emerson Retail Services, Inc. Refrigerant leak detection system and method
US8495886B2 (en) 2001-05-03 2013-07-30 Emerson Climate Technologies Retail Solutions, Inc. Model-based alarming
US8964338B2 (en) 2012-01-11 2015-02-24 Emerson Climate Technologies, Inc. System and method for compressor motor protection
US8974573B2 (en) 2004-08-11 2015-03-10 Emerson Climate Technologies, Inc. Method and apparatus for monitoring a refrigeration-cycle system
US9121407B2 (en) 2004-04-27 2015-09-01 Emerson Climate Technologies, Inc. Compressor diagnostic and protection system and method
US9140728B2 (en) 2007-11-02 2015-09-22 Emerson Climate Technologies, Inc. Compressor sensor module
US9285802B2 (en) 2011-02-28 2016-03-15 Emerson Electric Co. Residential solutions HVAC monitoring and diagnosis
US9310094B2 (en) 2007-07-30 2016-04-12 Emerson Climate Technologies, Inc. Portable method and apparatus for monitoring refrigerant-cycle systems
US9310439B2 (en) 2012-09-25 2016-04-12 Emerson Climate Technologies, Inc. Compressor having a control and diagnostic module
US9551504B2 (en) 2013-03-15 2017-01-24 Emerson Electric Co. HVAC system remote monitoring and diagnosis
US9638436B2 (en) 2013-03-15 2017-05-02 Emerson Electric Co. HVAC system remote monitoring and diagnosis
US9765979B2 (en) 2013-04-05 2017-09-19 Emerson Climate Technologies, Inc. Heat-pump system with refrigerant charge diagnostics
US9803902B2 (en) 2013-03-15 2017-10-31 Emerson Climate Technologies, Inc. System for refrigerant charge verification using two condenser coil temperatures
US9823632B2 (en) 2006-09-07 2017-11-21 Emerson Climate Technologies, Inc. Compressor data module
US9885507B2 (en) 2006-07-19 2018-02-06 Emerson Climate Technologies, Inc. Protection and diagnostic module for a refrigeration system

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US1922639A (en) * 1931-03-13 1933-08-15 Worthington Pump & Mach Corp Unloading mechanism for rotary compressors
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US2904973A (en) * 1957-09-09 1959-09-22 Gen Electric Variable displacement rotary compressor
US3687572A (en) * 1969-11-27 1972-08-29 Stal Refrigeration Ab Means for regulating the capacity of rotary machines
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Cited By (62)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5547298B2 (en) * 1975-06-18 1980-11-28
JPS5214253A (en) * 1975-06-18 1977-02-03 Daikin Ind Ltd Cooling system
FR2490749A1 (en) * 1980-09-19 1982-03-26 Mitsubishi Heavy Ind Ltd capacity control device for a compressor
US4331002A (en) * 1981-03-12 1982-05-25 General Electric Company Rotary compressor gas injection
EP0085246A1 (en) * 1981-12-21 1983-08-10 Sanden Corporation A control circuit for a variable displacement air conditioning compressor
US4522038A (en) * 1982-06-04 1985-06-11 Tokyo Shibaura Denki Kabushiki Kaisha Refrigerating cycle apparatus
US4558993A (en) * 1983-08-03 1985-12-17 Matsushita Electric Industrial Co., Ltd. Rotary compressor with capacity modulation
US4664608A (en) * 1985-11-04 1987-05-12 General Electric Company Rotary compressor with reduced friction between vane and vane slot
EP0519580A2 (en) * 1988-08-12 1992-12-23 Mitsubishi Jukogyo Kabushiki Kaisha Rotary compressor
EP0519580A3 (en) * 1988-08-12 1993-07-07 Mitsubishi Jukogyo Kabushiki Kaisha Rotary compressor
US8316658B2 (en) 2001-05-03 2012-11-27 Emerson Climate Technologies Retail Solutions, Inc. Refrigeration system energy monitoring and diagnostics
US8065886B2 (en) 2001-05-03 2011-11-29 Emerson Retail Services, Inc. Refrigeration system energy monitoring and diagnostics
US8495886B2 (en) 2001-05-03 2013-07-30 Emerson Climate Technologies Retail Solutions, Inc. Model-based alarming
US7644591B2 (en) 2001-05-03 2010-01-12 Emerson Retail Services, Inc. System for remote refrigeration monitoring and diagnostics
US6551069B2 (en) * 2001-06-11 2003-04-22 Bristol Compressors, Inc. Compressor with a capacity modulation system utilizing a re-expansion chamber
US6663358B2 (en) * 2001-06-11 2003-12-16 Bristol Compressors, Inc. Compressors for providing automatic capacity modulation and heat exchanging system including the same
US8700444B2 (en) 2002-10-31 2014-04-15 Emerson Retail Services Inc. System for monitoring optimal equipment operating parameters
US20110071960A1 (en) * 2002-10-31 2011-03-24 Emerson Retail Services, Inc. System For Monitoring Optimal Equipment Operating Parameters
US7290398B2 (en) 2003-08-25 2007-11-06 Computer Process Controls, Inc. Refrigeration control system
US9121407B2 (en) 2004-04-27 2015-09-01 Emerson Climate Technologies, Inc. Compressor diagnostic and protection system and method
US9669498B2 (en) 2004-04-27 2017-06-06 Emerson Climate Technologies, Inc. Compressor diagnostic and protection system and method
CN1993555B (en) 2004-08-06 2011-01-26 Lg电子株式会社 Capacity variable device for rotary compressor and driving method of air conditioner having the same
US20080307808A1 (en) * 2004-08-06 2008-12-18 Ozu Masao Capacity Variable Device for Rotary Compressor and Driving Method of Air Conditioner Having the Same
WO2006014081A1 (en) * 2004-08-06 2006-02-09 Lg Electronics Inc. Capacity variable device for rotary compressor and driving method of air conditioner having the same
US7931453B2 (en) * 2004-08-06 2011-04-26 Lg Electronics Inc. Capacity variable device for rotary compressor and driving method of air conditioner having the same
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US7885959B2 (en) 2005-02-21 2011-02-08 Computer Process Controls, Inc. Enterprise controller display method
US7885961B2 (en) 2005-02-21 2011-02-08 Computer Process Controls, Inc. Enterprise control and monitoring system and method
US7665315B2 (en) 2005-10-21 2010-02-23 Emerson Retail Services, Inc. Proofing a refrigeration system operating state
US7596959B2 (en) 2005-10-21 2009-10-06 Emerson Retail Services, Inc. Monitoring compressor performance in a refrigeration system
US7752853B2 (en) 2005-10-21 2010-07-13 Emerson Retail Services, Inc. Monitoring refrigerant in a refrigeration system
US7752854B2 (en) 2005-10-21 2010-07-13 Emerson Retail Services, Inc. Monitoring a condenser in a refrigeration system
US7594407B2 (en) 2005-10-21 2009-09-29 Emerson Climate Technologies, Inc. Monitoring refrigerant in a refrigeration system
US9885507B2 (en) 2006-07-19 2018-02-06 Emerson Climate Technologies, Inc. Protection and diagnostic module for a refrigeration system
US9823632B2 (en) 2006-09-07 2017-11-21 Emerson Climate Technologies, Inc. Compressor data module
US9310094B2 (en) 2007-07-30 2016-04-12 Emerson Climate Technologies, Inc. Portable method and apparatus for monitoring refrigerant-cycle systems
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US20110112814A1 (en) * 2009-11-11 2011-05-12 Emerson Retail Services, Inc. Refrigerant leak detection system and method
US9285802B2 (en) 2011-02-28 2016-03-15 Emerson Electric Co. Residential solutions HVAC monitoring and diagnosis
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US9803902B2 (en) 2013-03-15 2017-10-31 Emerson Climate Technologies, Inc. System for refrigerant charge verification using two condenser coil temperatures
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