CN101514857B - Refrigeration system - Google Patents
Refrigeration system Download PDFInfo
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- CN101514857B CN101514857B CN 200910004350 CN200910004350A CN101514857B CN 101514857 B CN101514857 B CN 101514857B CN 200910004350 CN200910004350 CN 200910004350 CN 200910004350 A CN200910004350 A CN 200910004350A CN 101514857 B CN101514857 B CN 101514857B
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- temperature
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- thermistor
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- 238000005057 refrigeration Methods 0.000 title claims abstract description 23
- 230000009183 running Effects 0.000 claims abstract description 25
- 238000001816 cooling Methods 0.000 claims abstract description 5
- 239000003507 refrigerant Substances 0.000 claims description 23
- 238000001514 detection method Methods 0.000 claims description 5
- 230000006835 compression Effects 0.000 claims description 3
- 238000007906 compression Methods 0.000 claims description 3
- 238000007599 discharging Methods 0.000 claims description 3
- 238000010438 heat treatment Methods 0.000 abstract description 2
- 239000012595 freezing medium Substances 0.000 abstract 5
- 230000000754 repressing effect Effects 0.000 abstract 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 46
- 238000004134 energy conservation Methods 0.000 description 3
- 230000000630 rising effect Effects 0.000 description 3
- 230000007812 deficiency Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 239000000446 fuel Substances 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
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- Y02B40/32—
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- Air Conditioning Control Device (AREA)
Abstract
Refrigeration device to save energy via running of controlling compressor capacity as main body, otherwise, capable of repressing exit temperature raise for supplying onus even second freezing medium bypass. Refrigeration device includes a plurality of compressors capable of controlling capacity and heat converter refrigerating device for using freezing medium extracted from the compressor to cooling or heating the second freezing medium. The heat converter includes thermistor for detecting entrance temperature of the second freezing medium and thermistor for detecting exit temperature, parallel connecting the second freezing medium flow path of the heat converter in refrigerating device to supply for heat load, which is characterized in that, based on the detected running stations numberof entrance temperature control refrigerating device by thermistor for detecting entrance temperature of refrigerating device and detected exit temperature control compressor capacity by the thermistor for detecting exit temperature.
Description
Technical field
The present invention relates to refrigeration system that secondary refrigerant is cooled off or heats.
Background technology
In the past, as the refrigeration system that secondary refrigerant (for example air, water) is cooled off or heats, as record in the patent documentation 1, be that the compressor capacity of refrigerating plant is reduced to minimum from maximum, after a refrigerating plant heat stops, the compressor capacity that makes next refrigerating plant repeatedly thus, makes the volume controlled of the running capacity variation of refrigeration system from the action of maximum to the minimum reduction with trickle step.
Patent documentation 1: TOHKEMY 2005-188907 communique
Summary of the invention
Invent problem to be solved
But, in above-mentioned volume controlled mode,, the adjustment precision of temperature is improved though the running capacity by making refrigeration system changes with trickle step, can not use compressor capacity effectively is about 75% the good running of coefficient of refrigerating performance.In addition because the secondary refrigerant stream is being connected side by side, so the refrigerating plant that heat has stopped because the secondary refrigerant bypass, inlet temperature and outlet temperature equate.Thus, because the outlet temperature of supplying with to load rises, thus in order further to seek the raising of temperature accuracy, need pump be set to each refrigerating plant, and stop pump being stopped with heat.
In order to solve above-mentioned existing problem, the objective of the invention is, energy-conservation by seeking with the running that is controlled to be main body of compressor capacity, in addition, even the secondary refrigerant bypass also can suppress the rising to the outlet temperature of load supply.
In order to solve the means of problem
In order to solve above-mentioned problem, refrigeration system of the present invention possesses a plurality of compressors with the capacity of can controlling and secondary refrigerant is cooled off or the refrigerating plant of the heat exchanger that heats by the cold-producing medium of discharging from this compressor, the inlet temperature that above-mentioned heat exchanger has the inlet temperature of detection secondary refrigerant detects with thermistor and the outlet temperature detection thermistor that detects outlet temperature, the secondary refrigerant stream of the above-mentioned heat exchanger of above-mentioned refrigerating plant is connected side by side, supply with to thermic load, it is characterized in that, above-mentioned inlet temperature based on above-mentioned a plurality of refrigerating plants detects the operating number of controlling refrigerating plant with the detected inlet temperature of thermistor, and detects with the detected outlet temperature control of thermistor compressor capacity based on the above-mentioned outlet temperature of above-mentioned a plurality of refrigerating plants; Minimum temperature in detecting with the detected inlet temperature of thermistor by the above-mentioned inlet temperature at above-mentioned a plurality of refrigerating plants when cooling is turned round detects the operating number of using maximum temperature control refrigerating plant in the detected inlet temperature of thermistor by the above-mentioned inlet temperature at above-mentioned a plurality of refrigerating plants when adding heat run.
In addition, it is characterized in that, the inlet design temperature of the secondary refrigerant of above-mentioned heat exchanger be by the outlet design temperature of the secondary refrigerant of above-mentioned heat exchanger and the value of the lower limit capacity that multiply by above-mentioned compressor with the gateway temperature difference under the situation of maximum compression machine capacity running and with the platform number from above-mentioned a plurality of refrigerating plants deduct one on duty with according to the platform number of increase and decrease refrigerating plant and the value sum of predefined temperature difference is set.
In addition, it is characterized in that, is the control of operating number of the above-mentioned refrigerating plant of difference beginning of 100% o'clock inlet temperature and outlet temperature based on the compressor capacity of the secondary refrigerant of above-mentioned heat exchanger.
The effect of invention
According to the present invention, can be energy-conservation by seeking with the running that is controlled to be main body of compressor capacity, in addition, even the secondary refrigerant bypass also can suppress the rising to the outlet temperature of load supply.
Description of drawings
Fig. 1 is the system diagram of the refrigeration system of expression one embodiment of the present of invention.Fig. 2 is the control flow chart of one embodiment of the present of invention.Fig. 3 is the compressor operation capacity of expression one embodiment of the present of invention and the figure of coefficient of refrigerating performance rate of change.
1a, 1b, 1c, 1d: refrigerating plant 2a～2d: heat exchanger 3a～3d: inlet temperature detects with thermistor 4a～4d: outlet temperature detects with thermistor 5: water supply pump 6: controller
The specific embodiment
Below, with reference to the accompanying drawings, embodiments of the invention are described.Fig. 1 is the system diagram of the refrigeration system of expression one embodiment of the present of invention.
In addition, in the present embodiment, be that an example describes with the situation that refrigeration system is utilized as water cooling equipment.As shown in Figure 1, refrigeration system has for example disposed four refrigerating plant 1a, 1b, 1c, 1d.Refrigerating plant 1a has the compressor of the cold-producing medium that can carry out interim volume controlled (for example 100%, 75%, 50%, 0%) or successional volume controlled (for example 100%～10%, 0%) and the heat exchanger 2a that secondary refrigerant (for example water) is cooled off by the heat of evaporation of the cold-producing medium of discharging from this compressor.In addition, connecting inlet temperature at the inlet portion that flows into from load heat exchanger 2a and detecting and use thermistor 3a, connecting outlet temperature detection thermistor 4a in the export department of the heat exchanger 2a that flows out to load.For refrigerating plant 1b, 1c, 1d also is same.The heat exchanger that is arranged on each refrigerating plant is connecting the cold water stream respectively side by side, and cold water is circulated by water supply pump 5 in heat exchanger 2a, 2b, 2c, 2d and the load that is connecting side by side.As compressor, use screw compressor, still, also can use in addition compressor (for example screw compressor etc.).But though the volume controlled of above-mentioned compressor also can be to carry out continuously in 100%～0% scope, because following reason, the volume controlled of compressor is not carried out in decision in 10%～0% scope.At first, first reason is, though with the motor of compressor by refrigerant cools, if the running under low capacity (10%～0% scope), then there is the circulating mass of refrigerant deficiency that is used for cooling motor, can not suppresses the possibility of the heating of motor.In addition, second reason is, in this compressor, though supply with the differential pressure fuel system that refrigerator oil has adopted the difference of the high pressure that utilizes freeze cycle and low pressure to bearing, but if the running under low capacity (10%～0% scope), because differential pressure reduces, so there is the possibility of fuel delivery deficiency.
The controller 6 that the operating number to refrigerating plant 1a, 1b, 1c, 1d of control system is controlled is connected with refrigerating plant 1a, 1b, 1c, 1d through holding wire, and the compressor operation capacity of refrigerating plant 1a, 1b, 1c, 1d is controlled according to each refrigerating plant.
The elemental motion of the refrigeration system of Gou Chenging is by each refrigerating plant 1a, the 1b that is circulated by water supply pump 5, the water that 1c, 1d cool off secondary refrigerant in this wise.The water that has been cooled carries out the action that heated up, cooled off by each refrigerating plant 1a, 1b, 1c, 1d by load repeatedly.
Fig. 2 represents control flow chart of the present invention.Set control object table number (being four in the present embodiment) (step 101) by controller 6, and set inlet water temperature Ta, the ladder temperature difference a (step 102) that platform numerical control system is used.In addition, according to each refrigerating plant, set outlet water temperature T b, ladder temperature difference b (step 102) that volume controlled is used.
Then, be changed at the compressor capacity of each refrigerating plant 1a, 1b, 1c, 1d under 100%, 75%, 50%, 0% the situation interimly, in refrigerating plant 1a, to export water temperature setting Tb and export water temperature T o1 and compare (step 114), if satisfy the condition of Tb＜To1, then making the compressor operation capacity is 100% (step 115), under ungratified situation, implements the judgement (step 116) of Tb-b 〉=To1.If do not satisfy condition, then making the compressor operation capacity is 75% (step 117), if satisfy, then implements the judgement (step 118) of Tb-2b 〉=To1.If do not satisfy condition, then making the compressor operation capacity is 50% (step 119), if satisfy, then making the compressor operation capacity is 0% volume controlled (step 120).
Fig. 3 represents compressor operation capacity and coefficient of refrigerating performance rate of change.As can be seen from the figure, coefficient of refrigerating performance is the most excellent when the compressor operation capacity is 75% left and right sides.
Fig. 4 represents the volume change of existing refrigeration system.In existing refrigeration system, the running capacity that is a refrigerating plant just makes next refrigerating plant from 100% → 75% → 50% → 0% mode that changes after heat stops from 100% → 75% → 50% → 0% variation.The running capacity of refrigeration system integral body is 75%, and in the time will having now with coefficient of refrigerating performance of the present invention relatively, in existing refrigeration system, three refrigerating plants are with 100% running of compressor operation capacity, and another stops.On the other hand, in the present embodiment, be that four refrigerating plants are with 75% running of compressor operation capacity.Because compare with compressor capacity 100% running, 75% this side's coefficient of refrigerating performance of running is more excellent, so, compare with existing refrigeration system, can seek energy-conservation in the present invention.
With regard to the relation of inlet design temperature and outlet design temperature, compressor capacity is changed under the situation of compressor of (for example 100%～10%, 0%) having carried, can realize by the following formula 1 of present embodiment with the corresponding optimal control of use.In addition, in following formula 1, the inlet design temperature is Ta, the outlet design temperature is Tb, gateway temperature difference during compressor capacity 100% is Δ T, the lower limit capacity of the compressor that can turn round is A, and the control object table number of refrigerating plant is B, and the ladder temperature difference of the operating number of increase and decrease refrigerating plant is a.
(formula 1) Ta=Tb+ Δ T * A/100+ (B-1) * a here, the cold water gateway temperature difference Δ T (T=5 ℃ of supposition Δ) by controller 6 identification during as 100% running of maximum compression machine capacity.Under the situation of carrying out energy-saving operation, according to compressor operation capacity and the coefficient of refrigerating performance rate of change of Fig. 3, the lower limit capacity A of the compressor that can turn round is set at 50%, so that do not carry out the following 50% capacity running of the coefficient of refrigerating performance of 100% capacity.Be set at 7 ℃ cold water outlet temperature being set Tb, the console of refrigerating plant is counted B be set at four, the ladder temperature difference a of operating number of control refrigerating plant is set under 0.5 ℃ the situation, as long as the inlet water temperature of suitable energy-saving operation is set Ta and set Ta=7 ℃+5 ℃ * 50/100+ (4-1) * 0.5=11 ℃ for.
Preferential for the precision that makes water temperature, by turning round, and turn round with the big amplitude of variation of compressor capacity until the minimum capacity of compressor, even under the big situation of load change amplitude, also can carry out the supply of always stable outlet water temperature.In addition, as the effect of running until the minimum capacity of compressor, under state with the minimum capacity running, because the temperature difference of inlet water temperature and outlet water temperature is little, so, the inlet water temperature that the refrigerating plant that stops because of platform numerical control system is carried out bypass becomes and the approaching temperature of outlet water temperature, the water temperature change in the time of can suppressing because of platform numerical control system refrigerating plant to be stopped.For example, carrying out platform numerical control system by four refrigerating plants, cold water gateway temperature difference during compressor capacity 100% running is 5 ℃, the outlet water temperature is assumed under 7 ℃ the situation, lower limit capacity at the compressor that allows to turn round is 50% o'clock, and refrigerating plant is with 9.5 ℃ of inlet water temperatures, 7 ℃ of runnings of outlet water temperature.At this moment, the refrigerating plant that stops because of platform numerical control system is because inlet water temperature and outlet water temperature equate, so 9.5 ℃ cold water is supplied with to load.
On the other hand, be under 10% the situation, at the lower limit capacity of the compressor that allows to turn round with 7.5 ℃ of inlet water temperatures, 7 ℃ of runnings of outlet water temperature of refrigerating plant.At this moment, the refrigerating plant because of platform numerical control system stops though inlet water temperature is equal with the outlet water temperature, because supply with to load with 7 ℃ of 7.5 ℃ approaching cold water of outlet water temperature, so reduce the lower limit capacity of compressor more, can suppress to export the change of water temperature more.
Preferential for the precision that makes water temperature, the lower limit capacity A of the compressor that can turn round is set at 10%.As an example, be set at 7 ℃ cold water outlet temperature being set Tb, the console of refrigerating plant is counted B be set at four, the ladder temperature difference a of operating number of control refrigerating plant is set under 0.5 ℃ the situation, as long as the inlet water temperature of suitable energy-saving operation is set Ta and set Ta=7 ℃+5 ℃ * 10/100+ (4-1) * 0.5=9 ℃ for.
As mentioned above, by by inlet temperature control operating number, to each refrigerating plant control compressor operation capacity, can carry out the setting of the running that compressor capacity is about 75%, coefficient of refrigerating performance is good for a long time by outlet temperature.In addition, inlet temperature and outlet temperature adopt and to turn round until the lower limit of compressor capacity, carry out the setting of the platform numerical control system of refrigerating plant then.Thus, even the secondary refrigerant bypass of the refrigerating plant that stops, inlet temperature and outlet temperature equate, are turning round at the compressor capacity with lower limit because be, so the temperature difference of inlet temperature and outlet temperature is also little, can suppress rising to the outlet temperature of load supply.
Claims (3)
1. refrigeration system; Described refrigeration system possesses a plurality of refrigerating plants; Above-mentioned refrigerating plant has the compressor that can control capacity and the heat exchanger that secondary refrigerant is cooled off or heats by the cold-producing medium of discharging from this compressor; The inlet temperature that above-mentioned heat exchanger has the inlet temperature of detection secondary refrigerant detects with thermistor and the outlet temperature detection thermistor that detects outlet temperature; The secondary refrigerant stream of the above-mentioned heat exchanger of above-mentioned refrigerating plant is connected side by side; Supply with to thermic load
It is characterized in that, above-mentioned inlet temperature based on above-mentioned a plurality of refrigerating plants detects the operating number of controlling refrigerating plant with the detected inlet temperature of thermistor, and detects with the detected outlet temperature control of thermistor compressor capacity based on the above-mentioned outlet temperature of above-mentioned a plurality of refrigerating plants;
Minimum temperature in detecting with the detected inlet temperature of thermistor by the above-mentioned inlet temperature at above-mentioned a plurality of refrigerating plants when cooling is turned round detects the operating number of using maximum temperature control refrigerating plant in the detected inlet temperature of thermistor by the above-mentioned inlet temperature at above-mentioned a plurality of refrigerating plants when adding heat run.
2. refrigeration system as claimed in claim 1, it is characterized in that, the inlet design temperature of the secondary refrigerant of above-mentioned heat exchanger be by the outlet design temperature of the secondary refrigerant of above-mentioned heat exchanger and to the value of the lower limit capacity that multiply by above-mentioned compressor with the gateway temperature difference under the situation of maximum compression machine capacity running and to the platform number from above-mentioned a plurality of refrigerating plants deduct one on duty with according to the platform number of increase and decrease refrigerating plant and the value sum of predefined temperature difference is set.
3. refrigeration system as claimed in claim 1 is characterized in that, is the control of operating number of the above-mentioned refrigerating plant of difference beginning of 100% o'clock inlet temperature and outlet temperature based on the compressor capacity of the secondary refrigerant of above-mentioned heat exchanger.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2008035438 | 2008-02-18 | ||
| JP2008-035438 | 2008-02-18 | ||
| JP2008035438A JP2009192186A (en) | 2008-02-18 | 2008-02-18 | Refrigeration system |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101514857A CN101514857A (en) | 2009-08-26 |
| CN101514857B true CN101514857B (en) | 2010-10-13 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 200910004350 Expired - Fee Related CN101514857B (en) | 2008-02-18 | 2009-02-12 | Refrigeration system |
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| Country | Link |
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| JP (1) | JP2009192186A (en) |
| CN (1) | CN101514857B (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6141089B2 (en) * | 2013-04-25 | 2017-06-07 | 三菱電機株式会社 | Cold / hot water supply system and air conditioner |
| JP6681896B2 (en) * | 2015-07-14 | 2020-04-15 | 三菱電機株式会社 | Refrigeration system |
| CN108332380B (en) * | 2018-01-29 | 2020-11-27 | 青岛海尔空调电子有限公司 | Air-cooled magnetic suspension air conditioning unit and control method thereof |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0816558B2 (en) * | 1989-10-27 | 1996-02-21 | ダイキン工業株式会社 | Refrigeration system operation controller |
| JP3410774B2 (en) * | 1993-07-23 | 2003-05-26 | 株式会社荏原製作所 | Operation control method for cold / hot water system |
| JP3405426B2 (en) * | 1995-03-31 | 2003-05-12 | 高砂熱学工業株式会社 | Refrigerator unit control device |
| JPH1089742A (en) * | 1996-09-12 | 1998-04-10 | Sanyo Electric Co Ltd | Refrigerating system |
| JP3320631B2 (en) * | 1997-05-14 | 2002-09-03 | 三菱電機株式会社 | Cooling and heating equipment |
| JP4050600B2 (en) * | 2002-08-30 | 2008-02-20 | 荏原冷熱システム株式会社 | Operation number control method and operation number control device for connected chiller / heater |
| JP3997482B2 (en) * | 2003-08-22 | 2007-10-24 | 木村工機株式会社 | Water source air conditioning system |
| JP2005188907A (en) * | 2003-12-26 | 2005-07-14 | Hitachi Ltd | Refrigeration system |
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2008
- 2008-02-18 JP JP2008035438A patent/JP2009192186A/en active Pending
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- 2009-02-12 CN CN 200910004350 patent/CN101514857B/en not_active Expired - Fee Related
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| Publication number | Publication date |
|---|---|
| JP2009192186A (en) | 2009-08-27 |
| CN101514857A (en) | 2009-08-26 |
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Effective date of registration: 20160816 Address after: Hongkong, China Patentee after: Johnson Controls Hitachi air conditioning technology (Hong Kong) Co.,Ltd. Address before: Tokyo, Japan Patentee before: Hitachi Appliances, Inc. |
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| TR01 | Transfer of patent right |
Effective date of registration: 20180629 Address after: Tokyo, Japan Patentee after: HITACHI-JOHNSON CONTROLS AIR CONDITIONING, Inc. Address before: Hongkong, China Patentee before: Johnson Controls Hitachi air conditioning technology (Hong Kong) Co.,Ltd. |
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