CN1237240A - Refrigeration circuit arrangement for refrigeration system - Google Patents
Refrigeration circuit arrangement for refrigeration system Download PDFInfo
- Publication number
- CN1237240A CN1237240A CN98801227A CN98801227A CN1237240A CN 1237240 A CN1237240 A CN 1237240A CN 98801227 A CN98801227 A CN 98801227A CN 98801227 A CN98801227 A CN 98801227A CN 1237240 A CN1237240 A CN 1237240A
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- Prior art keywords
- refrigeration
- fluid
- evaporimeter
- temperature
- valve
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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
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/31—Expansion valves
- F25B41/33—Expansion valves with the valve member being actuated by the fluid pressure, e.g. by the pressure of the refrigerant
- F25B41/335—Expansion valves with the valve member being actuated by the fluid pressure, e.g. by the pressure of the refrigerant via diaphragms
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- Physics & Mathematics (AREA)
- Engineering & Computer Science (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Compressor (AREA)
- Devices That Are Associated With Refrigeration Equipment (AREA)
- Details Of Measuring And Other Instruments (AREA)
- Motor Or Generator Cooling System (AREA)
- Temperature-Responsive Valves (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
A refrigeration circuit arrangement for a refrigeration system including, between the outlet of the condenser (4) and the inlet of the evaporator (8) of said circuit, a valve (20) of refrigerant fluid flow control, having a refrigerant fluid passage (22), whose cross section varies during the operation of the hermetic compressor (1) in a manner inversely proportional to the variation of the condensation temperature, in order to allow the condensed refrigerant fluid supplied to the evaporator (8) to have a temperature substantially correspondent to a nominal condensation temperature of the system.
Description
The present invention relates to a kind of refrigeration pipeline configuration of refrigerating system, this refrigerating system comprises the air-tight compressor that is contained on the gas pump pipeline, and this pumping pipeline comprises that condenser, evaporimeter and refrigeration fluid flow to the current limiter of above-mentioned evaporimeter.
In conventional refrigeration system, coolant tubes road order basically comprises air-tight compressor, condenser, decompression member for example capillary and evaporimeter.
In this pipeline, air-tight compressor draws low pressure cooling gas will pump it to condenser, become HTHP gas gas.During passing through condenser, above-mentioned gas liquefaction looses its heat to surrounding environment.
This refrigerant liquid reduces just to flow to evaporimeter from condenser after its pressure in capillary, and it becomes gaseous state again in evaporimeter, is compressed pump subsequently and send, and begins a new work period.
Cryogenic fluid becomes gaseous state from liquid state and just absorbs the heat of placing the evaporimeter environment during passing evaporimeter, make the internal environment cooling of the chiller that the refrigeration pipeline is housed.
In refrigeration pipe, temperature and pressure in the temperature of evaporimeter, the pressure of compressor and the condenser are controlled by capillary, and this size capillaceous changes with the predetermined average operation condition of system.Because this rigid structure, capillary can not make system reach optimization in the operation of its some operational phases (starting, routine operation and shutdown).Size capillaceous is to determine according to the best point of its operating characteristics.
Optimization capillaceous changes with the temperature of the condenser of the temperature of the room temperature of the infield of the refrigerating plant that the refrigeration pipeline is housed, refrigerator and above-mentioned refrigeration pipe.The load of refrigerating system pressure inside thereby compressor is corresponding to each temperature in these temperature.The reduction of room temperature reduces all pressure of system.In this state, compressor is with a small amount of gas of pumping, and its efficient reduces.The room temperature increase means that the load of compressor increases, and needs the outer load capacity of compressor amount of exports, and for the pumping of cooling gas in the increase system, this extra load is essential.The increase of load capacity will cause the rising of compressor temperature, may shorten its service life, probably cause the damaged of valve or even burn out motor.
The result who raises in the room temperature of cooled environmental externality is the rising of the condensation temperature of the compressor pump gas of delivering to condenser.Because condensation is to be caused by the heat exchange between condenser and environment,, the rising of room temperature rises so meaning the condensation temperature of refrigeration fluid.The refrigeration fluid of condensation enters evaporimeter under higher temperature, thereby has reduced evaporation efficiency, thereby has reduced the refrigeration that carries out the environment of heat exchange with evaporimeter.
In addition; in the refrigeration pipe configuration of routine; when the temperature of evaporimeter reaches predetermined value and compressor shutdown; the fluid that is present in the condensation of the system high pressure part in the condenser will be moved to the low-pressure section that evaporimeter is housed of said system; this refrigeration fluid that is stained with condensation at each condenser causes the reduction of refrigerating system efficient to the migration of evaporimeter, has increased the energy consumption of said system.The solution that alleviates these problems partly as far as possible is to use variable speed compressor.Yet the effect of this solution is local, because capillary has constant throttling action, and when increasing rotor rotation, swabbing pressure reduces, thereby reduces compressor efficiency, and may increase the mass flow that is not proportional to the rotation increase.
Therefore the purpose of this invention is to provide a kind of refrigeration pipeline configuration of refrigerating system, this pipeline disposes under the operating condition that can obtain the maximal efficiency of compressor and not need to make above-mentioned compressor operate in restriction.
Specific purposes of the present invention provide a kind of refrigeration pipeline configuration, this configuration can regulated the flow that condensed fluid flows to evaporimeter consistently near under the temperature of specified condensation temperature, and this specified condensation temperature considers that the refrigeration of cooled environment requires and be added in the load operation condition on the compressor.
Another object of the present invention provides a kind of refrigeration system that has refrigeration pipe, and when compressor shutdown, this refrigeration pipe prevents the refrigeration fluid of heating to move to evaporimeter from condenser.
Utilize a kind of refrigeration pipeline of refrigeration system to achieve the above object, this pipeline comprises: air-tight compressor; Condenser has the entrance and exit that is connected in compressor discharge port; Evaporimeter has the entrance and exit that connects condensator outlet.Above-mentioned configuration is included in the refrigeration fluid flow control valve between condensator outlet and the evaporator inlet; this valve has the refrigeration fluid passage; the cross-sectional area of this passage was inversely proportional to the variation of condensation temperature and changes in air-tight compressor operating period; so that make the condensation cryogenic fluid of inflow evaporator have the temperature that equals the specified condensation temperature of system substantially; when air-tight compressor is shut down; the cross section of above-mentioned cryogenic fluid passage is closed, and cuts off the fluid passage between condenser and the evaporimeter fully.
The present invention is described with reference to the accompanying drawings, and accompanying drawing is:
Fig. 1 schematically illustrates for example refrigeration pipe of refrigerator of the chiller made by prior art;
Fig. 2 schematically illustrates the refrigeration pipe of making by the present invention shown in Figure 1;
Fig. 3 is a longitdinal cross-section diagram, schematically illustrates flow of refrigeration fluids control valve of the present invention.
As shown in Figure 1, conventional refrigerating system comprises refrigeration pipe, and this pipeline comprises: air-tight compressor 1 has outlet 2 and Pump Suction Nozzle 3; Condenser 4 has gaseous fluid inlet 5 that is connected in air-tight compressor 1 outlet 2 in the operation and the outlet of condensed fluid 6 that is connected in capillary 7; Evaporimeter 8 has condensed fluid inlet 9 that is connected in capillary 7 in the operation and the gas vent 10 that is communicated with Pump Suction Nozzle 3 fluids of air-tight compressor 1.
In this pipeline, air-tight compressor 1 pump is inhaled the low pressure cooling gas, and it is pumped into condenser as the high voltage variable hot gas, and in above-mentioned condenser, above-mentioned gas liquefaction is dispersed into its heat in the surrounding environment.Heat exchange generation condensation by condenser 4 and its external environment condition.
The liquefaction fluid reduces above-mentioned gas pressure by capillary 7, and this gas enters evaporimeter 8 then, and after carrying out heat exchange with the internal environment of refrigerator, this gas is aspirated by compressor 1 again, begins a new work period.
According to this configuration, owing to have difference between the actual temperature when being pumped into condensation of gas in the condenser 4 in predetermined condensation rated temperature with by compressor 1, so the heat exchanger effectiveness of condenser 4 reduces.This structure also has the shortcoming of above-mentioned compressor overload.
According to the present invention; the refrigeration pipeline comprises the refrigeration fluid flow control valve 20 between the inlet of condensed fluid 9 of the condensed fluid outlet 6 that is configured in condenser 4 and evaporimeter 8; this valve can be automatically and change condensed fluid flows to evaporimeter 8 from condenser 4 flow consistently in 1 operating period of air-tight compressor; the refrigeration fluid flow is changed between maximum and minimum of a value, and when compressor 1 is shut down, can close above-mentioned traffic channel.When above-mentioned air-tight compressor 1 belongs to the sort of compressor with hesitation operating condition; this compressor for example will be shut down with the variations in temperature of evaporimeter 8, just can reach this hesitation operating condition and remain under this condition when the temperature sensor that is mounted in it detects the predetermined temperature state of evaporimeter 8.
Valve 20 of the present invention is set, so that the variation that makes the flow of the condensation refrigeration fluid that flows to evaporimeter 8 be inversely proportional to refrigeration fluid condensation temperature in the condenser changes, thereby make the condensation refrigeration fluid that flows to evaporimeter 8 arrive evaporimeter under the temperature that approaches specified condensation temperature substantially, this specified condensation temperature is for example to optimize temperature conditions in room temperature and the case and definite according to the optimization operating condition of refrigerating system.
In having the on/off-type compressor of one or more velocities of rotation and in the variable speed compressor, when the condensation temperature that obtains was higher than specified condensation temperature, the flow that flows to the condensed fluid of evaporimeter 8 reached minimum of a value.Owing to the pressure of valve 20 upstreams increases this minimum discharge state that reaches.This pressure increase is proportional to the increase of refrigerant quality of the refrigeration pipeline of condenser 4.
According to the present invention, valve 20 has valve body 21, this valve body for example is contained in the evaporimeter 8, form refrigeration fluid passage 22 in this valve body, be inversely proportional to the condensation temperature of the refrigeration fluid in the condenser 4 and change at the cross section of air-tight compressor this passage of 1 operating period, have the temperature that approaches the specified condensation temperature of system basically so that be transported to the condensation refrigeration fluid of boil-off gas 8.
For example when air-tight compressor 1 was shut down along with the variations in temperature of evaporimeter 8, refrigeration fluid passage 22 was closed.
Valve body 21 also has opening 23, this opening always with the condensed fluid of evaporimeter 89 fluid communication that enter the mouth.
In valve body 21, form valve seat 24; sealing device 25 selectively is pressed against on this valve seat 24 when air-tight compressor 1 is shut down; above-mentioned sealing device 25 engages with refrigeration fluid passage 22 in operation, so that the effect that the pump that makes the sealing device directly and side by side be subjected to the condensing pressure of valve 20 upstreams and valve 20 downstreams is inhaled pressure.
The cross section of refrigeration fluid passage 22 is owing to act on the dynamic balance that condensing pressure on the sealing device 25 and pump inhale between the pressure simultaneously in 1 operating period of air-tight compressor and cause in the variation between above-mentioned refrigeration fluid passage 22 complete closing state and the various open mode, this buttoned-up status forms when sealing device 25 is placed on the valve seat 24, and these various open modes are corresponding to the temperature that approaches specified condensation temperature substantially.
Condensing pressure is to make the refrigeration fluid be converted to the necessary pressure of gaseous state in condenser 4, and pump suction pressure is because the pressure that compressor operation obtains.The variation that sealing device 25 is inhaled the power of pressure formation in the complete closed position and the displacement between the various open position of refrigeration fluid passage 22 with condensing pressure and pump changes, and this power changes the cross section of refrigeration fluid passage 22.Sealing device 25 has hermetic unit and propulsive units, the former is subjected to the effect of condensing pressure, be formed on the upstream of valve 20, and the latter is positioned at the downstream of valve seat, so that impression is inhaled pressure at this regional pump easily, above-mentioned propulsive units utilizes spring part 26 to be connected in valve body 21, and this spring part is always pushed sealing device 25 to the closed condition of refrigeration fluid passage.
As illustrate, the propulsive units of sealing device 25 is connected in this spring 26 by annular jockey 29 adjustablely, this annular jockey is contained on the spring part 26, the end that faces toward the sealing device 25 of its hermetic unit is displaced in this circular connector inside, and moving sealing device just can carry out continuous buffering to be regulated.
Selection scheme according to structure of the present invention, sealing device 25 is contained in the valve 20 by valve seat 24, its hermetic unit is configured on the valve seat 24, and its propulsive units is positioned at valve body 21 consistently, the appearance profile of the appearance profile of sealing portion and valve seat 24 is complementary.
According to the present invention, valve body 21 forms chamber 27 in inside, so that by the refrigeration fluid, this chamber is communicated with the condensed fluid outlet 6 of condenser 4 by valve seat 24, and is communicated with the condensed fluid inlet 9 of evaporimeter 8 continuously by opening 23.In this structure, spring part 26 is the dividing plate form, constitutes the wall that passes through the refrigeration fluid facing to valve seat 24 in chamber 27.
The operation of air-tight compressor 1 of suction cooling gas causes acting in the above-mentioned chamber 27 of valve body 21 insufficient pressure on the spring part 26, causes the relative position between sealing device 25 and the valve seat 24 to change.
Refrigeration fluid passage 22 is determined by the annular space that forms between valve seat 24 and the sealing device 25.
In illustrative version, the cross section of refrigeration fluid passage 22 also changes with the variations in temperature of evaporimeter 8.This variations in temperature determines easily to experience the pucker ﹠ bloat state of variations in temperature fluid, and this fluid is contained in the valve 20, and acts on the sealing device 25, and is as described below.
Spring part 26 is contained in the valve body 21, makes it can consistently sealing device 25 be shifted onto the closed condition of refrigeration fluid passage 22.According to the present invention; spring part 26 has sealing station and position, many fluid passages; when air-tight compressor 1 is shut down, just reach the sealing position, and when take place in the chamber 27 suction make the refrigeration fluid by the time can reach these many fluids owing to the elastic deformation of spring part 26 and pass through the position.
In illustrative structure, spring 26 laterally is divided into valve body 21 chamber 27 and the airtight chamber 28 by the refrigeration fluid, this airtight chamber 28 comprises the easy fluid of experiencing variations in temperature in the evaporimeter 8, and forces spring part 26 to form different case of bendings with the variations in temperature in the evaporimeter 8.
The parts of easily experiencing temperature are defined as variations in temperature in its characteristic response evaporimeter 8 and change, make when compressor 1 is in off position, the above-mentioned easy fluid of experiencing temperature guarantees that spring part 26 is at sealing station, and during compressor operation, when temperature in the evaporimeter 8 reduces, easily experiencing the contraction of temperature flow body will push spring part 26 to its detent position continuously, when the temperature in the evaporimeter 8 raises, then push the position that it separates to.
The spring part 26 that is contained in the valve body 21 is divided into the zone that equates basically, i.e. chamber 27 and airtight chamber 28 with above-mentioned valve body 21.
Spring part 26 is fixed on the propulsive units and valve body 21 of sealing device 25, makes the complete closed position that can consistently sealing device 25 be pushed to refrigeration fluid passage 22 in 1 operating period of air-tight compressor.Variation along with the difference between the power that acts on the above-mentioned elastic component 26, can make spring part 26 be in position, various fluid passage, these power specifically comprise by condensing pressure and pump inhales the power that pressure causes, according to the operation of preferred structure of the present invention, also comprise because of in the formed power of easily experiencing on the variations in temperature fluid of variations in temperature.
In illustrative structure, when pump is inhaled pressure and is zero and ought for example easily experience the temperature flow body and shrink, produce a power that acts on above-mentioned spring part 26, make spring part 26 move apart valve seat 24, spring part 26 reaches its sealing station when making sealing device 25 be in its hermetic unit to be enclosed in the state on the valve seat 24 and to remain on this state, until compressor entry into service again.
By the above-mentioned spring part of respective curved, make it near valve seat 24 and make sealing device 25 relative valve seats 24 move apart its sealing station, then spring part 26 can reach various fluids and passes through the position.
For the on/off-type compressor that has constant speed or have at least two kinds of service speeds, when the temperature in the evaporimeter 8 reaches the predetermined value that can start air-tight compressor 1, the operation of this compressor will produce a pump and inhale pressure, this pressure is positioned at the low-pressure side of refrigeration pipeline, act on the propulsive units of sealing device 25, thereby make its hermetic unit move apart valve seat 24.
In the operating period of air-tight compressor 1, it is constant that the swabbing pressure in these compressors keeps.In this case, the pressure that acts on the above-mentioned sealing device 25 changes with the condensation temperature of condensation refrigeration fluid and the variation of condensing pressure in the condenser 4.
In the variable speed compressor that exists air-tight compressor 1 operation to shut down, the rotating speed of compressor is reduced the low temperature in the evaporimeter 8 and swabbing pressure reduces.The changes in flow rate that flows to the condensed fluid of evaporimeter 8 is to be caused formed making a concerted effort by the swabbing pressure in the chamber 27 and the condensation temperature of condensation refrigeration fluid and the state of condensing pressure.
During compressor operation, the suction inlet 10 by above-mentioned valve and air-tight compressor 1 forms swabbing pressure in the chamber 27 of valve body 21.This swabbing pressure acts on spring part 26, make its bending and the valve seat 24 of close valve body 21, thereby reduce the volume in chamber 27, and expanded in airtight chamber 28, above-mentioned motion causes sealing device 25 to move on to the position that separates with valve seat 24, thereby makes the condensation refrigeration fluid of scheduled volume flow to evaporimeter 8 under basically near condensation temperature specified condensation temperature and that no longer influence evaporimeter 8 evaporation efficiencies.
According to above-mentioned sealing device and sealing device seat, the condensed fluid flow that flows through the refrigeration fluid passage is proportional to the spacing between the annular surface of the outer surface of 25 parts of sealing device and valve seat 24.Along with the variation of air-tight compressor 1 operation, thereby along with the variation of the swabbing pressure that exists during the compressor operation, the hermetic unit of sealing device 25 can not reach sealing station with respect to valve seat 24.
When the condensation temperature of the fluid that is pumped into condenser increases, pressure on the hermetic unit of sealing device 25 increases, thereby make the sealing device move on to the position of close valve seat 24, restriction refrigeration fluid is by the flow of refrigeration fluid flow control valve, thereby the flow of restriction inflow evaporator 8.
The maximum pressure state of sealing device 25 forms the minimum stream value that the refrigeration fluid flows through the refrigeration fluid flow control valve.Limit fluid flows to evaporimeter 8 makes compressor diminish gradually at the volume of the refrigerant gas of refrigeration pipeline low-pressure side suction.The overload of air-tight compressor 1 has been avoided in the reduction of this mass flow.
Along with the restriction that increases the flow of refrigeration direction of flow evaporimeter 8, fluid will accumulate in the condenser 4, thereby increased pressure and temperature wherein, thus reach the temperature that an external environment condition that can make above-mentioned fluid and condenser 4 is carried out heat exchange, cause above-mentioned fluid condenses.This throttling is maintained to the fluid temperature (F.T.) that makes condensation and reduces, and has reduced the pressure on the sealing device 25 thus, makes the sealing device to separate with valve seat 24.Because this separately the cross section of refrigeration fluid passage 22 just increases gradually, thereby condensed fluid flows to the flow increase of evaporimeter.In 1 operating period of air-tight compressor, pressure on the sealing device 25 changes the flow of controlling refrigeration direction of flow evaporimeter 8, thus can be automatically and regulate above-mentioned flow continuously, thereby the efficient of increase condenser 4, the mainly load that when the over proof condensation temperature of ambient temperature, has alleviated air-tight compressor.
The Structural Characteristics of above-mentioned device is determined to be in air-tight compressor 1 when resetting, and sealing device can separate with valve seat 24.The activity of the spring part 26 that variation of temperature causes on air-tight compressor 1 operating period evaporimeter 8, this activity decisive action synthetic power on sealing device.
Claims (10)
1. the refrigeration pipeline of refrigeration system configuration comprises: air-tight compressor (1); Condenser (4) has an inlet and that is connected in compressor (1) outlet and exports; Evaporimeter (8); having an inlet and that is connected in condenser (4) outlet exports; it is characterized in that; it comprises the refrigeration fluid flow control valve (20) that is contained between condenser (4) outlet and evaporimeter (8) inlet; this valve has refrigeration fluid passage (22); the cross section of this passage was inversely proportional to the variation of condensation temperature and changes in air-tight compressor (1) operating period; thereby make the condensation refrigeration fluid that is transported to evaporimeter (8) have the temperature that equals the specified condensation temperature of system substantially; between air-tight compressor (1) down period; its cross section of above-mentioned refrigeration fluid passage (22) is closed, and makes the fluid flow disruption between condenser (4) and the evaporimeter (8) fully.
2. refrigeration pipeline configuration as claimed in claim 1, it is characterized in that, above-mentioned valve (20) comprises sealing device (25), this device combines with refrigeration fluid passage (22) in operation, can be directly and be subjected to the effect of valve (20) swabbing pressure in the condensing pressure of valve (20) upstream and valve (20) downstream simultaneously, the variation of the power that above-mentioned sealing device (25) forms with above-mentioned pressure and displacement, thus the cross section that makes refrigeration fluid passage (22) changes between the state that the buttoned-up status and the refrigeration fluid of this passage reaches specified condensation temperature.
3. refrigeration pipeline configuration as claimed in claim 2 is characterized in that refrigeration fluid passage (22) are determined by the annular space between valve seat (24) and the sealing device (25).
4. refrigeration pipeline configuration as claimed in claim 3, it is characterized in that, valve (20) comprises valve body (21), form the chamber (27) of flowing through the refrigeration fluid in this valve body, this chamber is communicated with the outlet of condenser (4) by valve seat (24) and has opening (23), and this opening always communicates with the inlet fluid of evaporimeter (8).
5. refrigeration pipeline configuration as claimed in claim 4; it is characterized in that; sealing device (25) comprises hermetic unit that is positioned at valve seat (24) upstream and the propulsive units that is positioned at the valve seat downstream; above-mentioned propulsive units is connected in valve body (21) by spring part (26); this spring part is always pushed sealing device (25) to the closed condition of refrigeration fluid passage (22); above-mentioned spring part (26) has sealing station and passes through the position to the fluid that reduces a lot; this spring arrives detent position when air-tight compressor (1) is shut down, and when exist in chamber (27) aspirate so that the refrigeration fluid when flowing through this spring (26) reach these many fluids by strain and pass through the position.
6. refrigeration pipeline configuration as claimed in claim 5 is characterized in that spring members (26) is the dividing plate form, forms the wall facing to valve seat (24) in chamber (27).
7. refrigeration pipeline configuration as claimed in claim 6, it is characterized in that spring part (26) is contained in the valve body (21), valve body is divided into chamber (27) and airtight chamber (28) by the refrigeration fluid, in this airtight chamber a kind of fluid is housed, this fluid is experienced the variations in temperature of evaporimeter (8) easily.
8. refrigeration pipeline configuration as claimed in claim 7, it is characterized in that, the fluid of easily experiencing temperature acts on the spring part (26), thereby when the temperature of evaporimeter (8) reduces, push this elastic component to sealing station, pass through the position and when the temperature of evaporimeter (8) rises, push this spring part (26) to various fluids.
9. refrigeration pipeline configuration as claimed in claim 7 is characterized in that valve body (21) is airtight, is contained in the evaporimeter (8), near its condensed fluid inlet.
10. refrigeration pipeline configuration as claimed in claim 9 is characterized in that the propulsive units of sealing device (25) is connected in spring part (26) adjustablely.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| BRPI97028037 | 1997-08-28 | ||
| BR9702803A BR9702803A (en) | 1997-08-28 | 1997-08-28 | Cooling system arrangement for cooling system |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN1237240A true CN1237240A (en) | 1999-12-01 |
Family
ID=4067303
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN98801227A Pending CN1237240A (en) | 1997-08-28 | 1998-08-28 | Refrigeration circuit arrangement for refrigeration system |
Country Status (8)
| Country | Link |
|---|---|
| EP (1) | EP0934494B1 (en) |
| JP (1) | JP2001505296A (en) |
| KR (1) | KR20000068849A (en) |
| CN (1) | CN1237240A (en) |
| AT (1) | ATE252714T1 (en) |
| BR (1) | BR9702803A (en) |
| DE (1) | DE69819127D1 (en) |
| WO (1) | WO1999011987A1 (en) |
Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7895003B2 (en) | 2007-10-05 | 2011-02-22 | Emerson Climate Technologies, Inc. | Vibration protection in a variable speed compressor |
| US8539786B2 (en) | 2007-10-08 | 2013-09-24 | Emerson Climate Technologies, Inc. | System and method for monitoring overheat of a compressor |
| US8459053B2 (en) | 2007-10-08 | 2013-06-11 | Emerson Climate Technologies, Inc. | Variable speed compressor protection system and method |
| US9541907B2 (en) | 2007-10-08 | 2017-01-10 | Emerson Climate Technologies, Inc. | System and method for calibrating parameters for a refrigeration system with a variable speed compressor |
| US8418483B2 (en) | 2007-10-08 | 2013-04-16 | Emerson Climate Technologies, Inc. | System and method for calculating parameters for a refrigeration system with a variable speed compressor |
| JP7349706B2 (en) * | 2019-07-04 | 2023-09-25 | 株式会社不二工機 | Power element and expansion valve using it |
| US11206743B2 (en) | 2019-07-25 | 2021-12-21 | Emerson Climate Technolgies, Inc. | Electronics enclosure with heat-transfer element |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3320763A (en) * | 1965-11-19 | 1967-05-23 | Westinghouse Electric Corp | Controls for refrigeration systems |
| US3638446A (en) * | 1969-06-27 | 1972-02-01 | Robert T Palmer | Low ambient control of subcooling control valve |
| US5245836A (en) * | 1989-01-09 | 1993-09-21 | Sinvent As | Method and device for high side pressure regulation in transcritical vapor compression cycle |
| US5201190A (en) * | 1992-02-24 | 1993-04-13 | White Consolidated Industries, Inc. | Refrigerator with subcooling flow control valve |
| EP0762064A1 (en) * | 1995-09-08 | 1997-03-12 | Fritz Ing. Weider | Refrigerant flow control for a heat pump and method |
-
1997
- 1997-08-28 BR BR9702803A patent/BR9702803A/en not_active IP Right Cessation
-
1998
- 1998-08-28 JP JP51606499A patent/JP2001505296A/en active Pending
- 1998-08-28 DE DE69819127T patent/DE69819127D1/en not_active Expired - Lifetime
- 1998-08-28 KR KR1019997003702A patent/KR20000068849A/en not_active Application Discontinuation
- 1998-08-28 AT AT98944909T patent/ATE252714T1/en not_active IP Right Cessation
- 1998-08-28 EP EP98944909A patent/EP0934494B1/en not_active Expired - Lifetime
- 1998-08-28 CN CN98801227A patent/CN1237240A/en active Pending
- 1998-08-28 WO PCT/BR1998/000067 patent/WO1999011987A1/en not_active Application Discontinuation
Also Published As
| Publication number | Publication date |
|---|---|
| ATE252714T1 (en) | 2003-11-15 |
| WO1999011987A1 (en) | 1999-03-11 |
| BR9702803A (en) | 1999-05-18 |
| DE69819127D1 (en) | 2003-11-27 |
| JP2001505296A (en) | 2001-04-17 |
| KR20000068849A (en) | 2000-11-25 |
| EP0934494A1 (en) | 1999-08-11 |
| EP0934494B1 (en) | 2003-10-22 |
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