CN1264019A - Constant temp. and humidity system - Google Patents
Constant temp. and humidity system Download PDFInfo
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- CN1264019A CN1264019A CN00100657A CN00100657A CN1264019A CN 1264019 A CN1264019 A CN 1264019A CN 00100657 A CN00100657 A CN 00100657A CN 00100657 A CN00100657 A CN 00100657A CN 1264019 A CN1264019 A CN 1264019A
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- G—PHYSICS
- G01—MEASURING; TESTING
- G01N—INVESTIGATING OR ANALYSING MATERIALS BY DETERMINING THEIR CHEMICAL OR PHYSICAL PROPERTIES
- G01N17/00—Investigating resistance of materials to the weather, to corrosion, or to light
- G01N17/002—Test chambers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/0008—Control or safety arrangements for air-humidification
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
- F24F3/12—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling
- F24F3/14—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification
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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
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
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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
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2501—Bypass valves
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Abstract
A thermo-hydrostatic system is provided, which reduces the operation cost while maintaining the thermo-hydrostatic function. In this system, the compressed refrigerant is distributed and respectively fed to the cooling system and heating system which are installed in the thermostatic chamber. By controlling each flow rate of the refrigerant flowing through the cooling system and heating system, the temperature of the thermostatic chamber can be kept constant. Meanwhile, the humidity can be controlled by keeping well-balanced correlation between dehumidification effect of the cooling system and humidification effect of the water sprayer.
Description
The present invention relates to a kind of constant temperature and humidity system, be used for the product various parts such as automobile, auto parts machinery, household electrical appliance and employing thereof, food, clothes and the chemicals is carried out environmental test.
The arbitrary temp that the constant temperature and humidity system that environmental test is used requires to have in very wide temperature range (for example, from-70 ℃ to 80 ℃ approximately) keeps all constant function of temperature and humidity down.Usually, this constant temperature and humidity system is that the thermostatic chamber 1 of adiabatic wall, the humidifier 3 that uses electronics boiling vessel 2, the cooling device 5 that uses refrigerator 4 and electronic heater 6 form by assembling on every side.
In the constant temperature and humidity system of aforementioned type, refrigerator 4 constantly starts and carries out humidity control, reduces simultaneously and the rising temperature.For the temperature that raises, must therefore need energy to start refrigerator 4 and electronic heater 6 with electronic heater heated constant temperature chambers 16.Also need more energy in order to start electronics boiling vessel 2, the cost that causes starting this constant temperature and humidity system is very high.
An object of the present invention is to provide a kind of constant temperature and humidity system that solves foregoing problems, can reduce cost significantly, keep the constant temperature and humidity function simultaneously.
To achieve these goals, this constant temperature and humidity system comprises: be the thermostatic chamber of adiabatic wall on every side; The compressor of compressible cold-producing medium; Cooling system can use the refrigerant cools thermostatic chamber of compressor compresses; Heating system can be used a part of compressed cold-producing medium heated constant temperature chamber; And temperature control system, the flow velocity that can pass through the adjusting cold-producing medium is controlled the temperature of thermostatic chamber.
In according to the constant temperature and humidity system aspect above-mentioned, can use the cold-producing medium that temperature raises under compression to come the heated constant temperature chamber.In this case, can use this part high temperature refrigerant to come the heated constant temperature chamber, needn't cool off.Therefore, do not need extra heater to come the heated constant temperature chamber, reduce the totle drilling cost of starting this system thus.
Fig. 1 is the schematic diagram according to the constant temperature and humidity system of first embodiment of the invention;
Fig. 2 illustrates the various schematic representation of apparatus that constitute cooling and heating system;
Fig. 3 is the curve map that the design temperature of the thermostatic chamber of expression first embodiment changes;
Fig. 4 is the schematic diagram that is illustrated in flow of refrigerant under the temperature that is set to normal temperature;
Fig. 5 is the schematic diagram that is illustrated in flow of refrigerant under the situation that design temperature raises;
Fig. 6 is the schematic diagram that is illustrated in flow of refrigerant under the situation that design temperature reduces;
Fig. 7 is the schematic diagram that is illustrated in flow of refrigerant under the further situation about reducing of design temperature;
Fig. 8 is the schematic diagram that is illustrated in flow of refrigerant under the situation that design temperature raises once more;
Fig. 9 is the schematic diagram according to the constant temperature and humidity system of second embodiment of the invention;
Figure 10 is the curve map that the design temperature of the thermostatic chamber of expression second embodiment changes;
Figure 11 is the schematic diagram that is illustrated in flow of refrigerant under the temperature that is set to room temperature;
Figure 12 is the schematic diagram that is illustrated in flow of refrigerant under the situation that design temperature raises from room temperature;
Figure 13 is the schematic diagram that is illustrated in flow of refrigerant under design temperature is reduced to room temperature from high temperature the situation;
Figure 14 is the schematic diagram that is illustrated in flow of refrigerant under the situation that design temperature reduces from room temperature;
Figure 15 is the schematic diagram that is illustrated in flow of refrigerant under design temperature is elevated to room temperature from low temperature the situation; And
Figure 16 is the schematic diagram of the constant temperature and humidity system of prior art.
Embodiments of the invention are described below with reference to accompanying drawings.
Fig. 1 is the schematic diagram according to the constant temperature and humidity system of first embodiment of the invention.Around the thermostatic chamber 10 is adiabatic wall 11.Thermostatic chamber 10 is divided into test cabinet 13 and air conditioning chamber 14 by dividing plate 12.Pore 15 is formed on top and bottom at dividing plate 12, and by these pores 15, the air circulation under the driving of the fan 17 that is rotated by motor 16 that is regulated temperature and humidity by air conditioning chamber 14 flows into test cabinet 13.In addition, test cabinet 13 and air conditioning chamber 14 can become one, and separate without dividing plate 12.
The constant temperature and humidity system of present embodiment is provided with cold-producing medium compression-type refrigerator 20 and compressor 21.The air conditioning chamber 14 of thermostatic chamber 10 is provided with cooler 22, heater 23 and sprayer 24.Sprayer 24 is used for by pressure-air ejection water smoke.
Fig. 2 illustrates cooling system of the present invention and heating system.
The cold-producing medium that compressor 21 compressions import is also discharged compressed cold-producing medium.CFC (CFC) or analog can be used as cold-producing medium and use.Aforementioned compression can make the temperature of cold-producing medium be elevated to 110 degrees centigrade, and pressure also raises simultaneously.The cold-producing medium of discharging from compressor 21 becomes gas form to be divided into two circuits through two high pressure control valves 25,26.These high pressure control valves 25,26 only are controlled when beginning, make cold-producing medium suitably be divided into two circuits.
The flow through high temperature refrigerant inflow heat exchanger 27 of high pressure control valve 25, by from the water quench of cooling water tube 28 to normal temperature.The result is that refrigerant gas changes liquid under such as 32 degrees centigrade temperature.So the cold-producing medium of cooling is removed the water that comprises in the cold-producing medium by baker 29 oven dry, and distributes to advance magnetic valve 30,31.This cooling and heating system are configured to make these magnetic valves 30 and 31 not open simultaneously.
Flow through the cold-producing medium of magnetic valve 31 by expansion valve 33 adiabatic expansions, its temperature is reduced to arbitrary temp (such as about 20 degrees centigrade).Then, cold-producing medium enters the cooler 22 (evaporimeter) in the air conditioning chamber 14 that is arranged on thermostatic chamber 10.So can cool off thermostatic chamber 10.Expansion valve 33 links to each other with the adjuster 61 that is used to cool off control, like this, and the opening/closing action of the control module control expansion valve 33 that links to each other with temperature sensor 62 in being arranged on thermostatic chamber 10.In order further to cool off, close magnetic valve 31, open magnetic valve 30.Flow through the cold-producing medium of magnetic valve 30 by expansion valve 32 adiabatic expansions, make its temperature be reduced to subzero 40 degrees centigrade.Then, cold-producing medium enters the cooler 22 (evaporimeter) that is arranged in the air conditioning chamber 14, so that cooling thermostatic chamber 10.Expansion valve 32 by be arranged on the control module opening/closing that ducted temperature sensor 66 links to each other, can introduce the cold-producing medium of the cooler 22 of flowing through by these pipelines.
As shown in Figure 2, except magnetic valve 30,31, the magnetic valve 34,35 that bypass is provided with links to each other with the outside of baker 29.These magnetic valves 34,35 link to each other with capacitor 38,39 with the injection apparatus 36,37 that can carry out continuous flow rate control respectively.The temperature of cold-producing medium of magnetic valve 35 of flowing through is about subzero 40 degrees centigrade.The temperature of cold-producing medium of magnetic valve 34 of flowing through is higher than subzero 40 degrees centigrade, at this moment because high temperature refrigerant is added in the zone around the magnetic valve 34, will describe below.The cold-producing medium that these two kinds of temperature are different mixes to normal temperature with cooling water is warm in capacitor 38,39 respectively then, returns compressor 21.Temperature sensor 63 detects the temperature of mixed cold-producing medium, and the opening degree based on the temperature control magnetic valve 34 that detects makes temperature constant remain on 18 ± 5 ℃.Simultaneously, control magnetic valves 35 by the adjuster 64 of the load control that is used for control module.Can be by aforesaid cooling system cooling thermostatic chamber 10.
The heating system of present embodiment will be described below.
The cold-producing medium that the temperature of a part by compressor 21 compression the raises high pressure control valve 26 of flowing through, and entering heater 23 in the air conditioning chamber 14 that is arranged on thermostatic chamber 10 through magnetic valve 40 and automatic high pressure control valve 41, this moment, the temperature of cold-producing medium was maintained at about 110 ℃ high.But high temperature refrigerant heated constant temperature chamber 10.Automatic high pressure control valve 41 links to each other with the adjuster 65 that is used to add thermal control, control module control degree of heat.The cold-producing medium of heater 23 of flowing through mixes with the low-temperature refrigerant of the magnetic valve 34 of flowing through.Then, mixed cold-producing medium returns compressor 21 through capacitor 38.By aforesaid heating system heated constant temperature chamber 10.
To be described in each operation of the aforementioned means under the state that design temperature changes as shown in Figure 3 below.
Fig. 4 illustrate state identical with A be slightly less than flowing of cold-producing medium under 20 ℃ the temperature of room temperature at design temperature.Electromagnetic valve closed will be used in the circles mark of the blacking in the outside.In this case, magnetic valve 40 is opened, and makes a small amount of high temperature refrigerant of automatic high pressure control valve 41 controls enter heater 23.Because the magnetic valve 30,31 of cooling system cuts out, low-temperature refrigerant does not enter cooler 22, will return compressor 21 through magnetic valve 35.The result is to enter thermostatic chamber 10 slightly.Sprayer 24 remains on such as 65% humidity by spraying into water.
Fig. 5 illustrates the state temperature and humidity identical with B-C and is elevated to flowing of cold-producing medium under 50 ℃ and 95% the situation.In this case, a large amount of high temperature refrigerants enters heater 23 by automatic high pressure control valve 41, and a large amount of water is sprayed into by sprayer 24.Under above-mentioned state, magnetic valve 34 is opened, and controls by the internal circulating load that increases low-temperature refrigerant, raises with the temperature of the cold-producing medium that prevents to turn back to compressor 21.That is to say, only increase the flow rate of high temperature refrigerant.This operator scheme is applied in state J-K.
Fig. 6 illustrates flowing of cold-producing medium under 20 ℃ the situation that the state design temperature identical with D-E be reduced to requirement.Automatic high pressure control valve 41 reduces the flow rate of high temperature refrigerant.Simultaneously, magnetic valve 31 is opened, and makes low-temperature refrigerant enter cooler 22.The result is to reduce the temperature of thermostatic chamber 10.By controlling to the water yield that sprayed into by sprayer 24 with by the relation between the moisture removal of cooling, humidity can remain on the constant set value.This operator scheme is applied in state L-M.
Fig. 7 illustrates flowing of cold-producing medium under-30 ℃ the situation that the state design temperature identical with F-G be reduced to requirement.In this case, automatic high pressure control valve 41 significantly reduces the flow rate of high temperature refrigerant.Magnetic valve 31 cuts out, and magnetic valve 30 is opened, and makes cold-producing medium enter cooler 22 through expansion valve 32, so cool off thermostatic chamber 10 strongly.At this moment, sprayer 24 stops to spray into water, and is freezing to prevent.
Fig. 8 illustrates flowing of cold-producing medium under the situation that the state design temperature identical with H-I raise on request.In this case, a large amount of high temperature refrigerants enters heater 23 by automatic high pressure control valve 41, and magnetic valve 30 and 31 cuts out, so that make cold-producing medium stop to enter cooler 22.H is the same with state, under 20 ℃ or lower temperature, stops to spray into water by sprayer 24.When temperature surpassed 20 ℃ the same with state I, sprayer 24 continued to spray into water.
Present embodiment can make the temperature and humidity of thermostatic chamber 10 remain on arbitrary value by controlling cooling system, heating system and water spray device respectively.The refrigerator of present embodiment is a kind of single-stage expansion type.But if require further cooling, frozen portions can be two-stage or twin-stage intumescent, can controlledly reach-70 ℃.
As mentioned above, in the unit of present embodiment, the expansion rising temperature of the cold-producing medium that is used to cool off by necessity can use the heat that is wasted under usual manner to come the heated constant temperature chamber.The result is, can use same refrigerator to cool off and heats.This can eliminate and the similar heating system independently of electronic heater.In addition, carry out humidification, can remove the energy that offers the electronics boiling vessel by mixing the water that sprays into by pressure-air in the air that in thermostatic chamber, circulates.Provide the relation between the water yield that sprays into and the effect on moisture extraction that comes from cooling system is controlled, can regulate humidity arbitrarily.
Various details second embodiment.
Fig. 9 is the schematic diagram of present embodiment.Around the thermostatic chamber 110 is adiabatic wall, and its part constitutes the air conditioning chamber 114 that is limited by dividing plate 111.Air conditioning chamber 114 is provided with cooler 122 and heater 123.Fan 112 be used for circulating test cabinet 113 in the thermostatic chamber 110 and the air between the air conditioning chamber 114.Water spray device 124 is arranged on the bottom of air conditioning chamber 114, demineralized water and dry air can be respectively by the feed water valve 143 that is used for humidification and the steam supply valve 144 that is used to spray into water smoke infeed.Steam supply valve 144 comprises magnetic valve and cylinder, and can control the flow rate of dry air.
The cooling system of present embodiment will be described below.
The compressor 121 that is used for compressed refrigerant has following function, can be the temperature of gaseous state that 18 ± 5 ℃, pressure are 3.92 * 10
5Pa or littler " cold-producing medium that returns " boil down to temperature are that 110 ℃, pressure limit are 1.274 * 10
6-2.548 * 10
6The high temperature and high pressure gas of Pa is discharged.
Can regulate by high pressure control valve 125 from a part of high-temperature high-pressure refrigerant that compressor 121 is discharged, make it to remain under the constant compression force, carry out heat exchange with the cooling water that provides by cooling water tube 128 then.The result is that refrigerant cools liquefies then to such as 32 degrees centigrade.Heat exchanger 127 is provided with baker 129, so that the cold-producing medium of oven dry liquefaction.
The heating system of present embodiment is described below.
Except those enter cold-producing medium in the aforementioned cooling system, a part of high-temperature high-pressure refrigerant of discharging from compressor 121 enters heating system, and high-temperature gas is 110 degrees centigrade.This high temperature refrigerant gas enters the shunt circuit of high pressure control valve 126 and magnetic valve 140.The high pressure control valve 125 that uses in cooling system can be controlled high pressure control valve 126, makes it always to remain under the constant compression force.As shown in Figure 10 and 11, when raising, temperature opens magnetic valve 140, and air-stable makes a large amount of high temperature refrigerant gas enter under predetermined or higher temperature.
The high temperature refrigerant gas of shunt circuit of aforementioned high pressure control valve 126 and magnetic valve 140 of flowing through enters the heater 123 in the air conditioning chamber 114, carries out pressure by automatic high pressure control valve 141 simultaneously and regulates.The opening degree of automatic high pressure control valve 141 is controlled by the adjuster 165 that is used to add thermal control, like this, enters the degree of the flow rate control heating of the higher pressure refrigerant gas in the heater 123 by control." cold-producing medium that returns " passage 150 is provided with magnetic valve 142, high temperature " cold-producing medium that returns " passage 151 is provided with magnetic valve 135, and " cold-producing medium that returns " passage 150 and high temperature " cold-producing medium that returns " passage 151 is arranged in parallel returning on the side at heater 132.Magnetic valve 142 or magnetic valve 135 will optionally be opened, and make to flow through the refrigerant gas of heater 123 or to turn back to compressor 121 by " cold-producing medium that returns " passage 150 or by " cold-producing medium that returns " passage 151.
In the present invention, the high-temperature high-pressure refrigerant of discharging from compressor 121 is directly used in heating.When a large amount of high temperature refrigerant gas enters heater 132, can surpass setting value to the temperature and pressure of " cold-producing medium that returns " of compressor 121.In order to prevent aforesaid drawbacks, the present invention is provided with the system that is used for control " cold-producing medium that returns ", and is as described below.
The temperature control system of present embodiment then will be described.
To be described in each operation of the aforementioned means under the state that the design temperature of thermostatic chamber 110 changes as shown in Figure 10 below.
Shown in Fig. 4 (in the drawings, the circle of blacking is represented the valve of closing), when design temperature is identical with state A during about room temperature, the magnetic valve 140 that is used for heating system cuts out.110 degrees centigrade the refrigerant gas of discharging from compressor 121 is subjected to the adjusting of high pressure control valve 126, so that enter automatic high pressure control valve 141 with low pressure.Automatic high pressure control valve 141 is subjected to being used to adding the control of the adjuster 165 of thermal control, makes high-temperature high-pressure refrigerant gas enter heater 123.The result is, but heated constant temperature chamber 110.
Simultaneously, a part of high-temperature high-pressure refrigerant gas of discharging from compressor 121 is subjected to the cooling of heat exchanger 127, and changes 32 degrees centigrade liquid refrigerant into and enter automatic pressure control valve 133 through magnetic valve 131.At this moment, magnetic valve 130 and 134 cuts out.Automatic pressure control valve 133 is subjected to being used to cool off adjuster 161 controls of control, so that the swell refrigeration agent.The gas of temperature step-down enters cooler 122 with cooling thermostatic chamber 110.Therefore, by between the cooling of the heating and cooling device 122 of heater 123, keeping good equilibrium relation, can make the temperature of thermostatic chamber 110 remain on design temperature.Therefore, can remove conventional independent heating system.Compare with conventional system, greatly reduce running cost.
The high-temperature high-pressure refrigerant gas of heater 123 of flowing through is got back to compressor 121 through magnetic valve 142 by passage 150.The refrigerant gas of cooler 122 of flowing through is also got back to compressor 121 by passage 150.At this moment, because magnetic valve 135 cuts out, " cold-producing medium that returns " be not by passage 151." cold-producing medium that returns " is mixed into 18 ± 5 ℃ mixture and gets back to compressor 121 in passage 150.The dry gas that is used to spray into water smoke that provides by steam supply valve 144 is provided water spray device 124, the demineralized water that is used for humidification that provides by feed water valve 143 is sprayed into, so that the humidity of silk thermostatic chamber keeps constant.
As shown in figure 12, when with the temperature of the state rising thermostatic chamber 110 identical with B-C or J-K, the magnetic valve 140 of heating system is opened, and makes a large amount of high-temperature high-pressure refrigerant gas enter heater 23.Then, the magnetic valve 131 of cooling system is opened, and makes a spot of cold-producing medium enter cooler 122.The result is that the temperature of thermostatic chamber 110 raises.Under this state, magnetic valve 142 cuts out, and magnetic valve 135 opens, and makes a large amount of high-temperature high-pressure refrigerant gas get back to compressor 121 by passage 151.But " cold-producing medium that returns " of getting back to compressor 121 may have too high temperature.In order to prevent that excessive temperature from raising, by opening magnetic valve 134, use injection apparatus 136 to make the cold-producing medium differential expansion, the low-temperature refrigerant gas admission passage 150 of generation is so that mix with " cold-producing medium that returns " from passage 151.The temperature of getting back to " cold-producing medium that returns " of compressor 121 is controlled at 18 ± 5 ℃.Temperature according to " cold-producing medium that returns " that detect by temperature sensor 163 is controlled opening of injection apparatus 136.The result is that this may be avoided causing the trouble of compressor 121 faults.
As shown in figure 13, when the temperature that makes thermostatic chamber 110 with the state identical with D-E or L-M when high temperature drops to room temperature, the magnetic valve 140 of heating system cuts out.High pressure control valve 126 reduces the pressure of refrigerant gas, and the refrigerant gas of low pressure enters automatic high pressure control valve 141.A spot of cold-producing medium enters heater 123 and gets back to compressor 121 through magnetic valve 142 by passage 150.At this moment, magnetic valve 135 cuts out, and passage 151 is also closed.Because the magnetic valve 131 of cooling system is opened, be subjected to being used to cooling off the cold-producing medium that automatic pressure control valve 133 expansion temperatures of adjuster 161 controls of control reduce, make it to flow into cooler 122.The result is that the temperature of thermostatic chamber 110 reduces." cold-producing medium that returns " from cooler 122 gets back to compressor 121 by passage 150.
When the temperature that makes thermostatic chamber 110 with the state identical with F-G descends when lower from room temperature, the operation of heating system the same with shown in Figure 13.But as shown in Figure 14, cooling system cuts out magnetic valve 131, and opens magnetic valve 130, makes a large amount of refrigerant gas enter cooler 122." cold-producing medium that returns " from heater 123 gets back to compressor 121 with " cold-producing medium that returns " from cooler 122 by passage 150.When cold-producing medium in passage 150 with from " cold-producing medium that returns " of a small amount of high temperature of heater 123 when mixing, the temperature of getting back to " cold-producing medium that returns " of compressor 121 remains on 18 ± 5 ℃.
As shown in figure 15, when shown in state H-I, the temperature that makes thermostatic chamber 110 is when low temperature is elevated to room temperature once more, and the magnetic valve 131 and 130 of cooling system cuts out, so that stop to cooler 122 supply cold-producing mediums.Because a spot of cold-producing medium is to infeed heater 23 with the identical mode shown in Fig. 6, the temperature of thermostatic chamber 110 raises.From " cold-producing medium that returns " of heater 123 flow through magnetic valve 142 and get back to compressor 121 by passage 150.
When humidity is set in 65%, the operation substantial constant of water spray device 124.But,, stop water spray device 124, to avoid freezing become 0 degree centigrade or when lower with temperature with F, G, state that H is identical.Under the unexpected situation about raising of the temperature of state J, the rising of temperature may be relevant with heat of evaporation.Therefore, preferably stop to start water spray device 124.
In an embodiment, the cold-producing medium that the temperature that a part is compressed by compressor 121 raises directly circulates and flows into heater 123, so that heated constant temperature chamber 110.The result is to eliminate the conventional independently heating system of using such as electronic heater.Compare identical with routine can be reduced running cost greatly.By at the sprayer of water spray humidification thermostatic chamber with provide between the cooling system of effect on moisture extraction and keep good equilibrium relation, can make humidity keep constant.The needs that this also can eliminate the electronics boiling vessel of boiling water have reduced running cost thus.This system is designed to only open magnetic valve 140 when temperature raises, make a large amount of high temperature refrigerant gas enter, and temperature is smoothly raise, and irrelevant with the amount of capacity of thermostatic chamber.In addition, the temperature and pressure of " cold-producing medium that returns " of compressor 121 is got back in the control system of " cold-producing medium that returns " control, makes it to keep under predetermined level constant.Therefore, even cold-producing medium is used for heating, this system can prevent the trouble of appearance in the compressor 121.
Claims (6)
1, a kind of constant temperature and humidity system for the thermostatic chamber of adiabatic wall, is characterized in that it comprises around it has:
Be the thermostatic chamber of adiabatic wall on every side;
The compressor of compressible cold-producing medium;
Cooling device can use the refrigerant cools thermostatic chamber of compressor compresses;
Heater can use a part of compressed cold-producing medium heated constant temperature chamber; And
Temperature control equipment, the flow velocity that can pass through the adjusting cold-producing medium is controlled the temperature of thermostatic chamber.
2, constant temperature and humidity system according to claim 1 is characterized in that also comprising distributor, is used for the assignment of traffic of the cold-producing medium of discharging from compressor is become both direction.
3, constant temperature and humidity system according to claim 1 is characterized in that also comprising the bypass channel of the flow through cold-producing medium that is arranged in the cooling device.
4, constant temperature and humidity system according to claim 1 is characterized in that also comprising refrigerant controller, is used to make the flow through temperature and pressure of cold-producing medium of heater and cooling device to remain on predetermined below horizontal.
5, constant temperature and humidity system according to claim 4 is characterized in that this refrigerant controller is provided with a plurality of passages.
6,, it is characterized in that also comprising the sprayer unit that is used for to the thermostatic chamber water spray according to any one described constant temperature and humidity system among the claim 1-5.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP11032538A JP2000230897A (en) | 1999-02-10 | 1999-02-10 | Thermostatic apparatus and thermostatic humidifying apparatus |
| JP032538/1999 | 1999-02-10 | ||
| JP105601/1999 | 1999-04-13 | ||
| JP11105601A JP2000298093A (en) | 1999-04-13 | 1999-04-13 | Thermostatic apparatus and thermostatic and humidistatic apparatus |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN1264019A true CN1264019A (en) | 2000-08-23 |
Family
ID=26371130
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN00100657A Pending CN1264019A (en) | 1999-02-10 | 2000-01-26 | Constant temp. and humidity system |
Country Status (3)
| Country | Link |
|---|---|
| KR (1) | KR20000057872A (en) |
| CN (1) | CN1264019A (en) |
| TW (1) | TW409175B (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102003759A (en) * | 2010-12-09 | 2011-04-06 | 上海交通大学 | Regenerative evaporative cooling air conditioner |
| CN101413705B (en) * | 2007-10-15 | 2012-09-19 | 能美防灾株式会社 | Spray system for cooling |
| CN104511319A (en) * | 2013-09-30 | 2015-04-15 | 爱斯佩克株式会社 | Apparatus for environmental test |
| CN104792816A (en) * | 2015-04-10 | 2015-07-22 | 北京兴迪仪器有限责任公司 | Thermostatic chamber for gas purity detector |
| CN109916607A (en) * | 2019-02-22 | 2019-06-21 | 航天科工防御技术研究试验中心 | A kind of controlled experiments device and the test method for controlled experiments device |
| CN111974466A (en) * | 2020-08-28 | 2020-11-24 | 无锡德华仕环境科技有限公司 | Energy-saving constant temperature and humidity case |
| CN112229785A (en) * | 2020-10-27 | 2021-01-15 | 长虹美菱股份有限公司 | Temperature contrast test method |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR101626713B1 (en) * | 2015-02-23 | 2016-06-01 | 한밭대학교 산학협력단 | Water vs Air Constant Temperature System |
-
2000
- 2000-01-26 CN CN00100657A patent/CN1264019A/en active Pending
- 2000-01-31 TW TW089101656A patent/TW409175B/en not_active IP Right Cessation
- 2000-02-02 KR KR1020000005079A patent/KR20000057872A/en not_active Application Discontinuation
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101413705B (en) * | 2007-10-15 | 2012-09-19 | 能美防灾株式会社 | Spray system for cooling |
| CN102003759A (en) * | 2010-12-09 | 2011-04-06 | 上海交通大学 | Regenerative evaporative cooling air conditioner |
| CN102003759B (en) * | 2010-12-09 | 2013-02-27 | 上海交通大学 | Regenerative evaporative cooling air conditioner |
| CN104511319A (en) * | 2013-09-30 | 2015-04-15 | 爱斯佩克株式会社 | Apparatus for environmental test |
| US9551646B2 (en) | 2013-09-30 | 2017-01-24 | Espec Corp. | Apparatus for environmental test |
| TWI572855B (en) * | 2013-09-30 | 2017-03-01 | Espec Corp | Environmental test device |
| CN104792816A (en) * | 2015-04-10 | 2015-07-22 | 北京兴迪仪器有限责任公司 | Thermostatic chamber for gas purity detector |
| CN109916607A (en) * | 2019-02-22 | 2019-06-21 | 航天科工防御技术研究试验中心 | A kind of controlled experiments device and the test method for controlled experiments device |
| CN109916607B (en) * | 2019-02-22 | 2021-07-20 | 航天科工防御技术研究试验中心 | Controllable test device and test method for same |
| CN111974466A (en) * | 2020-08-28 | 2020-11-24 | 无锡德华仕环境科技有限公司 | Energy-saving constant temperature and humidity case |
| CN112229785A (en) * | 2020-10-27 | 2021-01-15 | 长虹美菱股份有限公司 | Temperature contrast test method |
Also Published As
| Publication number | Publication date |
|---|---|
| KR20000057872A (en) | 2000-09-25 |
| TW409175B (en) | 2000-10-21 |
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