EP0009145A1 - Refrigerant compressor capacity control apparatus - Google Patents
Refrigerant compressor capacity control apparatus Download PDFInfo
- Publication number
- EP0009145A1 EP0009145A1 EP79103180A EP79103180A EP0009145A1 EP 0009145 A1 EP0009145 A1 EP 0009145A1 EP 79103180 A EP79103180 A EP 79103180A EP 79103180 A EP79103180 A EP 79103180A EP 0009145 A1 EP0009145 A1 EP 0009145A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- refrigerant
- flow
- cylinders
- manifold
- load
- 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.)
- Granted
Links
Images
Classifications
-
- 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
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
- F04B49/225—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves with throttling valves or valves varying the pump inlet opening or the outlet opening
-
- 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
- F25B2400/07—Details of compressors or related parts
- F25B2400/074—Details of compressors or related parts with multiple cylinders
-
- 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
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
- F25B41/22—Disposition of valves, e.g. of on-off valves or flow control valves between evaporator and compressor
Abstract
Description
- This invention relates to capacity control of a refrigeration compressor, and in particular, to a capacity control device which decreases the power input requirements of the compressor motor as the load on the refrigeration unit decreases.
- Mechanical refrigeration units, such as those employed in air conditioning systems, normally operate under varying load conditions. Typically, the units are designed to deliver conditioned air at a temperature of 25°C at high ambients, such as 40°C (hereinafter maximum load.) When the refrigeration unit is operating at less than maximum load conditions, it is desirable to reduce the refrigeration producing capacity thereof.
- Numerous schemes have been proposed to reduce the capacity of a refrigeration unit operating at less than maximum load conditions to not only reduce the refrigeration producing capabilities of the unit to prevent undesired overcooling of a space being served by the unit, but also to reduce the input power required to operate the refrigeration unit. In effect, a refrigeration unit operating under conditions that require less than 100% capacity should ideally be designed to operate at reduced input power requirements to effectively conserve energy.
- It has heretofore been known to employ a valve disposed between the suction manifold of the refrigeration compressor and one or more of the refrigerant compressor cylinders to unload one or more cylinders of a refrigeration compressor when reduced capacity is desired. When it is desired to unload the cylinders, to reduce the capacity of the compressor, the valve disposed within the manifold is placed in a position to terminate flow of the refrigerant gas from the manifold to the cylinders. While this method of achieving capacity control has proven somewhat effective, it has been found that further reductions in power input requirements at reduced loads may be obtained by modulating the valve as compared to operating the valve so it either is in an "open" position whereby full flow of refrigerant passes from the manifold to the cylinder or in a "closed" position whereby total flow of refrigerant gas is terminated.
- Test results have indicated that a reduction of the input power requirements of approximately 10% may be achieved by modulating the valve to vary the flow of refrigerant to at least one of the cylinders of the compressor as compared to opening or closing a valve in the manner disclosed in the cited patent, particularly when it is desirable to reduce the capacity of the unit to 20% - 40% of its maximum load rating.
- The above improved performance is attained in capacity control apparatus of a multi-cylinder refrigerant compressor employed in a mechanical refrigeration unit including a modulating valve disposed between a suction manifold, and less than all of the compressor's cylinders, the apparatus including control means for regulating the operation of the modulating valve directly in accordance with changes in the load on the refrigeration unit such that the valve increases the flow of refrigerant to the cylinders as the load increases and decreases the flow of refrigerant as the load decreases.
- This invention will now be described by way of example, with reference to the accompanying drawing in which:
- Figure 1 of the drawing schematically illustrates a mechanical refrigeration unit including a refrigeration compressor embodying the present invention; and
- Figure 2 is an enlarged sectional view showing the details of the present invention.
- Referring to the drawing, there is disclosed a preferred embodiment of the present invention. In referring to the various figures of the drawing, like numerals shall refer to like parts.
- Referring particularly to Figure 1, there is disclosed a
mechanical refrigeration unit 10 including an outdoorheat exchange coil 12, an indoorheat exchange coil 24, acompressor 20 and anexpansion device 22. High pressure refrigerant gas compressed by operation ofcompressor 20 is discharged throughconduit 16 and delivered to outdoorheat exchange coil 12 whereatfan 14 routes ambient air over the surface of the coil to condense the vaporous refrigerant flowing therethrough. The condensed refrigerant is delivered viaconduit 18 throughexpansion device 22 to indoorheat exchange coil 24. The indoor coil has air or water to be cooled routed thereover by operation offan 26. The air routed over the surface ofcoil 24 rejects heat to the refrigerant flowing therethrough causing the refrigerant to be vaporized. The vaporous refrigerant is returned to the suction side of the compressor viaconduit 28. The aforedescribed mechanical refrigeration unit is conventional and is typical of units employed in mechanical air conditioning systems. - In many applications, multi-cylinder compressors are utilized. Generally multi-cylinder compressors are designed to function with all cylinders fully loaded when ambient temperatures are relatively high, as for example at 40°C. At such high ambient temperatures, the cooling load on the refrigeration unit is also large. At less than maximum load conditions, it is desirable to reduce the refrigeration capacity of the refrigeration unit to prevent overcooling of the space served by the unit and to reduce the power input requirements thereof. Many known compressor capacity control devices have been used on multi-cylinder compressors in attempts to achieve the aforegoing capacity reduction at reduced cooling loads. One such capacity control device includes the utilization of a valve disposed between the suction manifold and some of the cylinders of the compressor to terminate flow of refrigerant from the manifold to the cylinders when reduced capacity of the compressor is desired. While this form of capacity control has been found to be relatively efficient, it has been additionally determined that improvements in such arrangement can effectively reduce the power input requirements by a considerable amount.
- Referring particularly to figure 2, there are disclosed the details of the present capacity control arrangement employed to reduce the cooling capabilities of the refrigeration unit at reduced cooling loads and simultaneously to decrease the input power requirements of the compressor to conserve energy.
- The capacity control device of the present invention includes a
housing 42 mounted within thecylinder head 46 of the compressor. The housing has aninlet 43 in communication withsuction manifold 34 and includes an outlet preferably defined by one ormore ports 58. Refrigerant gas flowing throughports 58 is delivered into asuction header 35 for an individual cylinder. Each cylinder or bank of cylinders will generally be associated with a separate suction header. The suction gas passing fromheader 35 flows throughsuction ports 36 intocompressor cylinder 30. The refrigerant gas incylinder 30 is compressed by reciprocal movement ofpiston 31 therein and is discharged therefrom throughports 38 intodischarge chamber 32. The flow of refrigerant gas throughports - A
piston type device 52 is movably disposed withinbore 41 defined byhousing 42. Aretainer ring 48 maintainspiston 52 within the bore. Springs 54 and 56, mounted onretainer 60, provide a force to movepiston 52 upwardly withinbore 41. A relatively constant magnitude force is developed inchamber 49 located above the top surface ofpiston 52 in opposition to the force acting on the bottom surface thereof generated bysprings conduits constant pressure valve 44 is utilized to control the pressure of the gas flowing throughconduit 17 to maintain the pressure inchamber 49 at a predetermined magnitude. An 0-ring 50 is provided to prevent leakage between the opposed surfaces ofhousing 42 and the cylinder block in which thevalve 40 is mounted. A force developed by the suction pressure of the gas inmanifold 34 operates in combination with the force developed bysprings piston 52 to move the piston upwardly withinbore 41. - In operation, let us first assume that a maximum load condition exists on the refrigeration unit to require operation of all cylinders of the compressor to maintain the desired refrigeration capabilities of the unit. If the load on
refrigeration unit 10 should diminish, the pressure of the refrigerant flowing throughconduit 28 intomanifold 34 will decrease. In essence, the suction pressure of the refrigerant gas flowing intomanifold 34 varies directly with the load on the refrigeration unit; as the load decreases so will the pressure of refrigerant passing intomanifold 34. The reduced pressure inmanifold 34 will cause a concurrent reduction in the total force acting on the bottom surface ofpiston 52. As the pressure inchamber 49 is maintained at a constant level, the force acting on the top surface ofpiston 52 also remains at a constant magnitude. Thus, the force imbalance thus created results inpiston 52 moving from the position shown in figure 2 (whereat a maximum flow of refrigerant passes to cylinder 30) downwardly withinbore 41 towardsmanifold 34. The movement ofpiston 52 relative toport 58 resulting from a reduction in the refrigeration load tends to decrease the quantity of refrigerant passing frommanifold 34 intosuction chamber 35. In effect,piston 52 modulates the flow of refrigerant moving intoheader 35 in accordance with the changes in load on the refrigeration unit by changing the active flow area ofport 58. As the load continues to decrease, thus reducing the force acting on the lower surface ofpiston 52, the piston will move withinbore 41 to further reduce the active area ofport 58 to further reduce the flow of refrigerant passing therethrough. Eventually, upon further decreases in the refrigeration load,piston 52 will move with respect toport 58 to completely terminate the flow of refrigerant therethrough. When this occurs,cylinder 30 is completely unloaded. The power input to the compressor is reduced generally in proportion to the movement ofpiston 52 with respect toport 58; as the piston reduces the flow of refrigerant throughport 58 tocylinder 30, the power input to the compressor will likewise decrease since the compressor will require less energy to compress the refrigerant still flowing to its cylinders. - If the refrigeration load increases, the pressure of the refrigerant gas passing into
manifold 34 increases to increase the force acting on the lower surface ofpiston 52 to thereby raise the piston withinbore 41 to permit renewed flow of refrigerant gas throughport 58. The quantity of refrigerant gas passing through the port will vary directly with the pressure of the refrigerant gas acting on the lower surface ofpiston 52. Thus, as the load continues to increase, the pressure acting on the lower surface ofpiston 52 will also increase to further movepiston 52 with respect toport 58 to increase the flow passage opening defined thereby to permit a greater quantity of refrigerant gas to pass intosuction header 35. - As may be readily recognized, the capacity control device of the present invention modulates the gas flowing to a bank of cylinders to improve the performance of the refrigeration unit by reducing the power consumption requirements of the unit at part-load conditions. The specific embodiment herein disclosed achieves the desired capacity control by regulating the movement of the capacity control device in response to changes in the difference in the pressure between suction pressure and a predetermined pressure-operating in a chamber provided above a piston of the capacity control device. While the capacity control device has been illustrated as employed with a compressor used in an air conditioning system, the invention may also readily be employed with refrigeration units employed to chill water. Generally in such units, the temperature of the water leaving the evaporator is monitored to sense changes of the refrigeration load on the unit.
- While a preferred embodiment of the present invention has been described and illustrated, the present invention may be otherwise embodied within the scope of the following claims.
Claims (6)
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
AT79103180T ATE1396T1 (en) | 1978-09-20 | 1979-08-28 | DEVICE FOR CONTROLLING THE POWER OF A REFRIGERATION COMPRESSOR. |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US94423778A | 1978-09-20 | 1978-09-20 | |
US944237 | 1978-09-20 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0009145A1 true EP0009145A1 (en) | 1980-04-02 |
EP0009145B1 EP0009145B1 (en) | 1982-07-28 |
Family
ID=25481045
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP79103180A Expired EP0009145B1 (en) | 1978-09-20 | 1979-08-28 | Refrigerant compressor capacity control apparatus |
Country Status (15)
Country | Link |
---|---|
EP (1) | EP0009145B1 (en) |
JP (1) | JPS5551978A (en) |
AR (1) | AR221901A1 (en) |
AT (1) | ATE1396T1 (en) |
AU (1) | AU532017B2 (en) |
BR (1) | BR7905936A (en) |
DE (1) | DE2963419D1 (en) |
DK (1) | DK361879A (en) |
ES (2) | ES484265A1 (en) |
IL (1) | IL58116A (en) |
IN (1) | IN152999B (en) |
MX (1) | MX147475A (en) |
NO (1) | NO146446C (en) |
PH (1) | PH18397A (en) |
ZA (1) | ZA794377B (en) |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4382749A (en) * | 1980-11-14 | 1983-05-10 | The Trane Company | Reciprocating compressor with integral unloader valve |
US4452570A (en) * | 1981-11-12 | 1984-06-05 | Mitsubishi Denki Kabushiki Kaisha | Multiple cylinder rotary compressor |
US4452571A (en) * | 1981-06-19 | 1984-06-05 | Mitsubishi Denki Kabushiki Kaisha | Multiple cylinder rotary compressor |
EP0297514A1 (en) * | 1987-06-30 | 1989-01-04 | Sanden Corporation | Refrigerant circuit with passagaway control mechanism |
EP1279833A2 (en) * | 2001-07-26 | 2003-01-29 | Copeland Corporation | Compressor with blocked suction capacity modulation |
Citations (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE146420C (en) * | ||||
US2309773A (en) * | 1941-03-29 | 1943-02-02 | Gen Motors Corp | Refrigerating apparatus |
FR1259473A (en) * | 1960-03-15 | 1961-04-28 | Chantiers De Latlantique | Method and device for controlling the power of compressors comprising two or more cylinder and piston assemblies |
FR1284287A (en) * | 1961-03-17 | 1962-02-09 | Borg Warner | Device for controlling the flow rate of a compressor of automotive cooling equipment |
GB1089694A (en) * | 1964-02-24 | 1967-11-01 | J & E Hall Ltd | Improvements in or relating to gas and vapour compressors |
US3360952A (en) * | 1966-06-28 | 1968-01-02 | Trane Co | Capacity controlled refrigeration system |
US3518032A (en) * | 1968-05-24 | 1970-06-30 | Dresser Ind | Compressor cylinder unloader |
US3578883A (en) * | 1969-05-14 | 1971-05-18 | Copeland Refrigeration Corp | Unloader for multicylinder refrigeration compressors |
US3759057A (en) * | 1972-01-10 | 1973-09-18 | Westinghouse Electric Corp | Room air conditioner having compressor with variable capacity and control therefor |
US3781135A (en) * | 1972-05-19 | 1973-12-25 | C Nickell | Refrigerant compressor for vehicles |
US3872685A (en) * | 1973-03-16 | 1975-03-25 | Controls Co Of America | Evaporator temperature control for refrigeration systems |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5538415Y2 (en) * | 1972-06-09 | 1980-09-08 | ||
JPS5130287A (en) * | 1974-09-06 | 1976-03-15 | Sumitomo Chemical Co | EKIJOHORIBUTAJENNOSEIZOHOHO |
JPS53109211A (en) * | 1977-03-04 | 1978-09-22 | Toshiba Corp | Heat pump type air conditioner |
-
1979
- 1979-08-20 ZA ZA00794377A patent/ZA794377B/en unknown
- 1979-08-21 IN IN597/DEL/79A patent/IN152999B/en unknown
- 1979-08-27 IL IL58116A patent/IL58116A/en unknown
- 1979-08-28 AT AT79103180T patent/ATE1396T1/en active
- 1979-08-28 EP EP79103180A patent/EP0009145B1/en not_active Expired
- 1979-08-28 DE DE7979103180T patent/DE2963419D1/en not_active Expired
- 1979-08-29 DK DK361879A patent/DK361879A/en not_active Application Discontinuation
- 1979-08-29 AU AU50384/79A patent/AU532017B2/en not_active Ceased
- 1979-09-11 JP JP11664379A patent/JPS5551978A/en active Pending
- 1979-09-17 BR BR7905936A patent/BR7905936A/en not_active IP Right Cessation
- 1979-09-18 AR AR278094A patent/AR221901A1/en active
- 1979-09-19 ES ES484265A patent/ES484265A1/en not_active Expired
- 1979-09-19 NO NO793007A patent/NO146446C/en unknown
- 1979-09-20 MX MX179351A patent/MX147475A/en unknown
- 1979-09-20 PH PH23048A patent/PH18397A/en unknown
- 1979-10-18 ES ES485139A patent/ES485139A1/en not_active Expired
Patent Citations (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE146420C (en) * | ||||
US2309773A (en) * | 1941-03-29 | 1943-02-02 | Gen Motors Corp | Refrigerating apparatus |
FR1259473A (en) * | 1960-03-15 | 1961-04-28 | Chantiers De Latlantique | Method and device for controlling the power of compressors comprising two or more cylinder and piston assemblies |
FR1284287A (en) * | 1961-03-17 | 1962-02-09 | Borg Warner | Device for controlling the flow rate of a compressor of automotive cooling equipment |
GB1089694A (en) * | 1964-02-24 | 1967-11-01 | J & E Hall Ltd | Improvements in or relating to gas and vapour compressors |
US3360952A (en) * | 1966-06-28 | 1968-01-02 | Trane Co | Capacity controlled refrigeration system |
US3518032A (en) * | 1968-05-24 | 1970-06-30 | Dresser Ind | Compressor cylinder unloader |
US3578883A (en) * | 1969-05-14 | 1971-05-18 | Copeland Refrigeration Corp | Unloader for multicylinder refrigeration compressors |
US3759057A (en) * | 1972-01-10 | 1973-09-18 | Westinghouse Electric Corp | Room air conditioner having compressor with variable capacity and control therefor |
US3781135A (en) * | 1972-05-19 | 1973-12-25 | C Nickell | Refrigerant compressor for vehicles |
US3872685A (en) * | 1973-03-16 | 1975-03-25 | Controls Co Of America | Evaporator temperature control for refrigeration systems |
Cited By (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4382749A (en) * | 1980-11-14 | 1983-05-10 | The Trane Company | Reciprocating compressor with integral unloader valve |
US4452571A (en) * | 1981-06-19 | 1984-06-05 | Mitsubishi Denki Kabushiki Kaisha | Multiple cylinder rotary compressor |
US4452570A (en) * | 1981-11-12 | 1984-06-05 | Mitsubishi Denki Kabushiki Kaisha | Multiple cylinder rotary compressor |
EP0297514A1 (en) * | 1987-06-30 | 1989-01-04 | Sanden Corporation | Refrigerant circuit with passagaway control mechanism |
EP1279833A2 (en) * | 2001-07-26 | 2003-01-29 | Copeland Corporation | Compressor with blocked suction capacity modulation |
EP1279833A3 (en) * | 2001-07-26 | 2004-11-10 | Copeland Corporation | Compressor with blocked suction capacity modulation |
EP1876354A2 (en) * | 2001-07-26 | 2008-01-09 | Copeland Corporation LLC | Compressor with blocked suction capacity modulation |
EP1876354A3 (en) * | 2001-07-26 | 2008-01-23 | Copeland Corporation LLC | Compressor with blocked suction capacity modulation |
KR100898023B1 (en) * | 2001-07-26 | 2009-05-19 | 코우프랜드 코포레이션 엘엘씨 | Compressor with blocked suction capacity modulation |
Also Published As
Publication number | Publication date |
---|---|
JPS5551978A (en) | 1980-04-16 |
AR221901A1 (en) | 1981-03-31 |
IN152999B (en) | 1984-05-19 |
IL58116A (en) | 1982-11-30 |
PH18397A (en) | 1985-06-21 |
ZA794377B (en) | 1980-11-26 |
NO793007L (en) | 1980-03-21 |
NO146446C (en) | 1982-09-29 |
EP0009145B1 (en) | 1982-07-28 |
NO146446B (en) | 1982-06-21 |
DE2963419D1 (en) | 1982-09-16 |
AU5038479A (en) | 1980-03-27 |
AU532017B2 (en) | 1983-09-15 |
ATE1396T1 (en) | 1982-08-15 |
ES484265A1 (en) | 1980-04-01 |
BR7905936A (en) | 1980-05-27 |
IL58116A0 (en) | 1979-12-30 |
MX147475A (en) | 1982-12-03 |
ES485139A1 (en) | 1980-05-16 |
DK361879A (en) | 1980-03-21 |
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