CN104949368A - Turbine refrigerator - Google Patents
Turbine refrigerator Download PDFInfo
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- CN104949368A CN104949368A CN201510136558.7A CN201510136558A CN104949368A CN 104949368 A CN104949368 A CN 104949368A CN 201510136558 A CN201510136558 A CN 201510136558A CN 104949368 A CN104949368 A CN 104949368A
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- Prior art keywords
- expansion valve
- condenser
- pressure
- saving appliance
- evaporimeter
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- 238000005057 refrigeration Methods 0.000 claims abstract description 34
- 239000007788 liquid Substances 0.000 claims abstract description 33
- 239000012530 fluid Substances 0.000 claims abstract description 6
- 239000012809 cooling fluid Substances 0.000 claims abstract description 5
- 239000003507 refrigerant Substances 0.000 claims description 34
- 230000006835 compression Effects 0.000 claims description 8
- 238000007906 compression Methods 0.000 claims description 8
- 230000005494 condensation Effects 0.000 claims description 4
- 238000009833 condensation Methods 0.000 claims description 4
- 238000001704 evaporation Methods 0.000 claims description 4
- 230000008020 evaporation Effects 0.000 claims description 3
- 230000000694 effects Effects 0.000 abstract description 2
- 230000001276 controlling effect Effects 0.000 abstract 1
- 230000000630 rising effect Effects 0.000 abstract 1
- 238000010586 diagram Methods 0.000 description 6
- 230000007246 mechanism Effects 0.000 description 6
- 239000000498 cooling water Substances 0.000 description 5
- 238000000034 method Methods 0.000 description 5
- 230000004044 response Effects 0.000 description 5
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 5
- 230000008859 change Effects 0.000 description 4
- 230000009471 action Effects 0.000 description 3
- 230000005520 electrodynamics Effects 0.000 description 3
- 230000008569 process Effects 0.000 description 3
- 230000002950 deficient Effects 0.000 description 2
- 238000004378 air conditioning Methods 0.000 description 1
- 150000001875 compounds Chemical class 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 230000003252 repetitive effect Effects 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
Classifications
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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
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
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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
-
- 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
- F25B41/34—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators
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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
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
-
- 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
- F25B2600/2513—Expansion valves
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Air Conditioning Control Device (AREA)
Abstract
A turbine refrigerator can prevent controlling property drop of an electric expansion valve, and can prevent cost rising caused by arranging more expansion valves; the turbine refrigerator comprises the following elements: an evaporator obtaining heat energy from a cooled fluid so as to evaporate a refrigeration agent, thus having refrigeration effect; a multi-stage turbine compressor using a multi-stage impeller to compress the refrigeration agent; a condenser using cooling fluid to cool off and condense compressed refrigeration agent air; an energy saver serving as an intercooler, so part of condensed liquid refrigeration agent fluid is evaporated and supplied to a middle portion of the multi-stage compressor of the multi-stage turbine refrigerator; the refrigeration agent is led to a refrigeration agent tube of the energy saver from the condenser; a flow control valve and the expansion valves are arranged according to orders.
Description
Technical field
The present invention relates to turborefrigerator, particularly relate to the expansion mechanism of turborefrigerator.
Background technology
In the past, turborefrigerator for refrigerating air conditioning device etc. is made up of the closed system being sealed with cold-producing medium, this turborefrigerator is configured to utilize refrigerant piping will link as lower component: evaporimeter, and it obtains heat and cold-producing medium is evaporated and plays refrigeration from cold water (cooled fluid); Compressor, it compresses the refrigerant gas after above-mentioned evaporator evaporation and makes it to become the refrigerant gas of high pressure; Condenser, it utilizes cooling water (cooling fluid) refrigerant gas to high pressure cool and make it condensation; And expansion valve (expansion mechanism), it reduces pressure to above-mentioned condensed cold-producing medium and makes it to expand.And, when by by multi-stage impeller multistage compound compressor that refrigerant gas is compressed be used as compressor, for the refrigerant gas produced at intercooler and energy-saving appliance (economizer), imported to the intergrade (mid portion of multi-stage impeller) of compressor, wherein, described intercooler is arranged in the refrigerant piping between condenser and evaporimeter.
In turborefrigerator, fixed orifice, float-controlled valve, motor-driven valve etc. are used for from condenser to energy-saving appliance and from energy-saving appliance to the expansion mechanism of evaporimeter.
In kind of refrigeration cycle, if utilize compressor to compress the refrigerant gas being helpless to refrigerating capacity, then can consume remaining power, therefore, cause the efficiency of refrigeration machine to reduce.
In the past, adopted motor-driven valve as expansion mechanism, and guaranteeing the liquid level of the tank body (condenser, energy-saving appliance) of the primary side of expansion valve, avoiding gas distribution by carrying out fluid-tight to the primary side of expansion mechanism.
In most cases, motor-driven valve is used for expansion valve, according to the difference of spool kind, flow Cv value (discharge coefficient) can change with the control characteristic of aperture.
As the expansion valve of turborefrigerator, mostly adopt ball valve, butterfly valve, but, in low valve opening region, relative to the operational ton of valve, the change of Cv value (discharge coefficient) reduces, be formed as so-called dead band, thus be not suitable for the level control requiring foregoing precision.
Fig. 6 is the curve map of the relation illustrated between the valve opening of ball valve, butterfly valve and Cv value (discharge coefficient).As shown in Figure 6, in low valve opening region, reduce relative to the change of the Cv value of the operational ton of valve, be formed as controlling defective region.And, in the region that valve opening is higher, increase relative to the change of the Cv value of valve operational ton, be formed as controlling good area.
In figure 6, if use small-bore expansion valve premised on using in controlling good area, then under the low lift condition that the temperature difference of cold water and cooling water is less, the situation that cold-producing medium returns to evaporimeter is deteriorated sometimes, produce the suction low pressure of evaporimeter, thus refrigeration machine continuous running cannot be made.
Therefore, bigbore expansion valve and small-bore expansion valve are arranged in parallel, carry out the switching control etc. of expansion valve according to the temperature conditions of refrigeration load or cold water cooling water.
Patent document 1: Japanese Patent No. 4109997 publication
In above-mentioned prior art, produce following problem.
(1) there is the controlling defective region of electrodynamic type expansion valve, cannot high-precision level control be carried out.
(2) when being arranged in parallel multiple bigbore expansion valves and small-bore expansion valve in order to ensure controlling, there is the problem that cost increases.
Summary of the invention
The present invention completes in view of the foregoing, and its object is to provides a kind of turborefrigerator, can avoid the reduction of the controlling of electrodynamic type expansion valve, in addition, can avoid causing cost to increase because arranging multiple expansion valve.
To achieve these goals, turborefrigerator of the present invention possesses: evaporimeter, and it makes cold-producing medium evaporate from cooled fluid acquisition heat and plays refrigeration, multistage turbocompressor, it utilizes multi-stage impeller to compress cold-producing medium, condenser, it utilizes cooling fluid cool the refrigerant gas after compression and make it condensation, and as the energy-saving appliance of intercooler, it makes a part for condensed liquid refrigerant liquid evaporate, refrigerant gas after evaporation is supplied to the mid portion of the multi-stage compression level of above-mentioned multistage turbocompressor, the feature of described turborefrigerator is, cold-producing medium is being guided to the refrigerant piping of above-mentioned energy-saving appliance from above-mentioned condenser, according to throttle orifice, the order of expansion valve is arranged throttle orifice and expansion valve, cold-producing medium is being guided to the refrigerant piping of above-mentioned evaporimeter from above-mentioned energy-saving appliance, according to throttle orifice, the order of expansion valve is arranged throttle orifice and expansion valve.
According to the present invention, the senior side between condenser and energy-saving appliance, utilizes the throttle orifice being arranged at the primary side of expansion valve to produce basic pressure loss, limits circulating mass of refrigerant thus, utilizes the expansion valve being positioned at downstream to carry out the level control of condenser.By like this throttle orifice being arranged at the primary side of expansion valve, the controlling good area that the region making expansion valve carry out on-off action changes to Cv value (discharge coefficient) delicately relative to valve operational ton switches, and can solve the problem controlling response and reduce thus.Utilize throttle orifice and expansion valve to carry out high-precision level control at condenser, the gas distribution amount of kind of refrigeration cycle can be reduced thus, the efficiency of refrigeration machine can be avoided to reduce.In addition, the rudimentary side between energy-saving appliance and evaporimeter too, utilizes the throttle orifice being arranged at the primary side of expansion valve to produce basic pressure loss, limits circulating mass of refrigerant thus, utilizes the expansion valve being positioned at downstream to carry out the level control of energy-saving appliance.By utilizing throttle orifice and expansion valve to carry out high-precision level control at energy-saving appliance like this, the gas distribution amount of kind of refrigeration cycle can be reduced, the efficiency of refrigeration machine can be avoided to reduce.
According to preferred embodiment of the present invention, it is characterized in that, above-mentioned throttle orifice is made up of fixed orifice, and above-mentioned expansion valve is made up of the DYN dynamic expansion valve that aperture is variable.
According to preferred embodiment of the present invention, it is characterized in that, possess: liquid level sensor, it is arranged at above-mentioned condenser and above-mentioned energy-saving appliance respectively, measures cold-producing medium liquid level; And control device, it controls the aperture of above-mentioned expansion valve, above-mentioned control device based on be arranged at above-mentioned condenser liquid level sensor measured value and the aperture of the expansion valve between above-mentioned condenser and above-mentioned energy-saving appliance is controlled, based on be arranged at above-mentioned energy-saving appliance liquid level sensor measured value and the aperture of the expansion valve between above-mentioned energy-saving appliance and above-mentioned evaporimeter is controlled.
According to preferred embodiment of the present invention, it is characterized in that, possess: pressure sensor, it is arranged at above-mentioned condenser and above-mentioned evaporimeter respectively, measures the pressure of condenser and the pressure of evaporimeter; And control device, it controls the aperture of above-mentioned expansion valve, above-mentioned control device, based on the pressure differential of the pressure of the condenser gone out by above-mentioned determination of pressure sensor and the pressure of evaporimeter, controls the aperture of the aperture of the expansion valve between above-mentioned condenser and above-mentioned energy-saving appliance and the expansion valve between above-mentioned energy-saving appliance and above-mentioned evaporimeter.
According to preferred embodiment of the present invention, it is characterized in that, obtain the relation between the pressure differential of the pressure of condenser and the pressure of evaporimeter and the aperture of above-mentioned expansion valve in advance, and the relation this obtained in advance is pre-stored within above-mentioned control device, the above-mentioned relation that above-mentioned control device is obtained in advance based on the pressure differential according to the pressure of condenser gone out by above-mentioned determination of pressure sensor and the pressure of evaporimeter, determines the aperture of the aperture of the expansion valve between above-mentioned condenser and above-mentioned energy-saving appliance and the expansion valve between above-mentioned energy-saving appliance and above-mentioned evaporimeter.
The present invention plays the following effect enumerated.
(1) by carrying out the level control of condenser and energy-saving appliance with good precision, the gas distribution amount of kind of refrigeration cycle can be reduced, the efficiency of refrigeration machine can be avoided to reduce.
(2) operation range that the control response avoiding occurring electrodynamic type expansion valve is poor, can realize the operation range that controlling is good.
(3) avoiding causing cost to increase because being arranged in parallel multiple expansion valve to guarantee to control response, single expansion valve can be utilized respectively to carry out the level control of condenser and energy-saving appliance.
Accompanying drawing explanation
Fig. 1 is the schematic diagram of the first embodiment that turborefrigerator involved in the present invention is shown.
Fig. 2 is Mollier line chart when throttle orifice and expansion valve being connected in series.
Fig. 3 illustrates that the turborefrigerator shown in Fig. 1 is provided with the schematic diagram of the embodiment of liquid level sensor.
Fig. 4 illustrates that the turborefrigerator shown in Fig. 1 is provided with the schematic diagram of the embodiment of pressure sensor.
Fig. 5 is the curve map of the relation illustrated between the pressure differential of condenser and evaporimeter and the aperture of expansion valve.
Fig. 6 is the curve map of the relation illustrated between the valve opening of ball valve, butterfly valve and Cv value (discharge coefficient).
Description of reference numerals:
1 ... turbo-compressor; 2 ... condenser; 3 ... evaporimeter; 4 ... energy-saving appliance; 5 ... refrigerant piping; 6 ... senior throttle orifice; 7 ... high stage expansion valve; 8 ... stream; 9 ... rudimentary throttle orifice; 10 ... low stage expansion valve; 11 ... first order impeller; 12 ... second level impeller; 13 ... compressor motor; 14 ... pump blades; 17 ... liquid level sensor; 18 ... liquid level sensor; 20 ... control device; 21 ... pressure sensor; 22 ... pressure sensor;
Detailed description of the invention
Below, be described with reference to the embodiment of Fig. 1 ~ Fig. 5 to turborefrigerator involved in the present invention.In Fig. 1 ~ Fig. 5, also the repetitive description thereof will be omitted to mark identical Reference numeral for identical or suitable inscape.
Fig. 1 is the schematic diagram of the first embodiment that turborefrigerator involved in the present invention is shown.As shown in Figure 1, turborefrigerator possesses: turbo-compressor 1, and it compresses cold-producing medium; Condenser 2, it utilizes cooling water (cooling fluid) cool the refrigerant gas after compression and make it condensation; Evaporimeter 3, it obtains heat from cold water (cooled fluid) and cold-producing medium is evaporated and plays refrigeration; And as the energy-saving appliance 4 of intercooler, it is configured between condenser 2 and evaporimeter 3, turborefrigerator is configured to utilize the refrigerant piping 5 for refrigerant circulation will above-mentioned each equipment link.
In the embodiment shown in Fig. 1, turbo-compressor 1 is made up of multistage turbocompressor, multistage turbocompressor is made up of two-stage turbine compressor, and is configured to the compressor motor 13 that possesses first order impeller 11, second level impeller 12 and above-mentioned impeller 11,12 is rotated.The suction side of first order impeller 11 is provided with pump blades 14, and this pump blades 14 pairs of refrigerant gas adjust to the inhalation flow of impeller 11,12.Turbo-compressor 1 is connected with energy-saving appliance 4 by stream 8, is directed to the mid portion (being the part between first order impeller 11 and second level impeller 12 in this example) of multiple compression stages (being secondary in this example) of turbo-compressor 1 at the isolated refrigerant gas of energy-saving appliance 4.
In the kind of refrigeration cycle of the turborefrigerator formed as shown in Figure 1, cold-producing medium circulates in turbo-compressor 1, condenser 2, evaporimeter 3 and energy-saving appliance 4, utilize the Cooling and Heat Source obtained at evaporimeter 3 to manufacture cold water, in the mode corresponding with load by the heat carrying out flash-pot 3 obtained in refrigerative circle system and the thermal release suitable with the merit of turbo-compressor 1 that supply from motor 13 to the cooling water supplied condenser 2.On the other hand, be directed to the mid portion of multiple compression stages of turbo-compressor 1 at the isolated refrigerant gas of energy-saving appliance 4, and then converge with the refrigerant gas from first order compressor and compressed by high stage compressor.According to two-stage compression single-stage cycles, economized, owing to being also attached with the part of the refrigeration based on energy-saving appliance 4, therefore, refrigeration correspondingly improves, and compared with not arranging the situation of energy-saving appliance 4, can realize the high efficiency of refrigeration.
As shown in Figure 1, at the refrigerant piping 5 be connected with energy-saving appliance 4 by condenser 2, be provided with senior throttle orifice 6 and DYN dynamic high stage expansion valve 7.In addition, at the refrigerant piping 5 be connected with evaporimeter 3 by energy-saving appliance 4, be provided with rudimentary throttle orifice 9 and DYN dynamic low stage expansion valve 10.Throttle orifice 6,9 is made up of fixed orifice, and expansion valve 7,10 is made up of the motor-driven valve that valve opening is variable.For throttle orifice 6,9 and expansion valve 7,10, be called that " senior " is with the reason of " rudimentary ", compared with between energy-saving appliance 4 with evaporimeter 3, pressure between condenser 2 and energy-saving appliance 4 is higher, therefore, side higher for pressure is called " senior ", side lower for pressure is called " rudimentary ".
By forming as shown in Figure 1, in senior side, utilize the senior throttle orifice 6 being arranged at the primary side of high stage expansion valve 7 to produce basic pressure loss, limit circulating mass of refrigerant thus, utilize the high stage expansion valve 7 being positioned at downstream to carry out the level control of condenser 2.By so senior throttle orifice 6 being arranged at the primary side of high stage expansion valve 7, the controlling good area that the region making high stage expansion valve 7 carry out on-off action changes to Cv value (discharge coefficient) delicately relative to valve operational ton switches, and can solve the problem controlling response and reduce.Utilize senior throttle orifice 6 and high stage expansion valve 7 and carry out high-precision level control at condenser 2, the gas distribution amount of kind of refrigeration cycle can be reduced thus, the efficiency of refrigeration machine can be avoided to reduce.
In addition, in rudimentary side too, utilize the rudimentary throttle orifice 9 being arranged at the primary side of low stage expansion valve 10 to produce basic pressure loss, limit circulating mass of refrigerant thus, utilize the low stage expansion valve 10 being positioned at downstream to carry out the level control of energy-saving appliance 4.By so rudimentary throttle orifice 9 being arranged at the primary side of low stage expansion valve 10, the controlling good area that the region making low stage expansion valve 10 carry out on-off action changes to Cv value (discharge coefficient) delicately relative to valve operational ton switches, thus can solve the problem controlling response and reduce.Utilize rudimentary throttle orifice 9 and low stage expansion valve 10 and carry out high-precision level control at energy-saving appliance 4, the gas distribution amount of kind of refrigeration cycle can be reduced thus, the efficiency of refrigeration machine can be avoided to reduce.
In addition, as shown in Figure 1, between condenser 2 and energy-saving appliance 4 and between energy-saving appliance 4 and evaporimeter 3, in a series arrangement throttle orifice and expansion valve are arranged respectively, thus can also avoid arranging with the expansion valve that parallel way is different to bore, the problem that the cost that can solve refrigeration machine increases.
Fig. 2 is Mollier line chart when throttle orifice and expansion valve being connected in series.As shown in Figure 2, carry out the expansion process from condensing pressure to energy-saving appliance pressure in two stages of senior throttle orifice 6 and high stage expansion valve 7, carry out the expansion process from energy-saving appliance pressure to evaporating pressure in two stages of rudimentary throttle orifice 9 and low stage expansion valve 10.
Next, the concrete control method of the expansion mechanism of the turborefrigerator formed as described above is described.
Fig. 3 illustrates that the turborefrigerator shown in Fig. 1 is provided with the schematic diagram of the embodiment of liquid level sensor.As shown in Figure 3, in the present embodiment, liquid level sensor 17,18 is respectively arranged with at condenser 2 and energy-saving appliance 4.Liquid level sensor 17,18 is connected with control device 20 respectively.In addition, high stage expansion valve 7 and low stage expansion valve 10 are also connected with control device 20 respectively.
In the turborefrigerator formed as shown in Figure 3, the liquid level of liquid level sensor 17 pairs of condensers 2 measures, and measured value is inputed to control device 20.Control device 20 carries out open and close controlling in the mode making the liquid level of condenser 2 and reach specified altitude to high stage expansion valve 7.Herein, specified altitude refers to the height making undermost heat pipe not be immersed in liquid refrigerant in condenser 2, controls with the aperture of mode to high stage expansion valve 7 making above-mentioned liquid level reach this specified altitude.In addition, the liquid level of liquid level sensor 18 pairs of energy-saving appliances 4 measures, and measured value is inputed to control device 20.Control device 20 carries out open and close controlling in the mode making the liquid level of energy-saving appliance 4 and reach specified altitude to low stage expansion valve 10.Herein, specified altitude refers to that the gas-liquid separation demister making to be arranged at energy-saving appliance 4 is not immersed in the height of liquid refrigerant in energy-saving appliance 4, controls with the aperture of mode to low stage expansion valve 10 making above-mentioned liquid level reach this specified altitude.
Like this, utilize senior throttle orifice 6 to carry out high-precision level control with high stage expansion valve 7 at condenser 2, the gas distribution amount of kind of refrigeration cycle can be reduced thus, the efficiency of refrigeration machine can be avoided to reduce.In addition, utilize rudimentary throttle orifice 9 to carry out high-precision level control with low stage expansion valve 10 at energy-saving appliance 4, the gas distribution amount of kind of refrigeration cycle can be reduced thus, the efficiency of refrigeration machine can be avoided to reduce.
Due to liquid level sensor that liquid level is exported continuously costly, therefore, preferred employing utilizes the pressure differential of condenser and evaporimeter to control the method for the aperture of expansion valve easily.
Fig. 4 illustrates that the turborefrigerator shown in Fig. 1 is provided with the schematic diagram of the embodiment of pressure sensor.As shown in Figure 4, be provided with respectively to the pressure sensor 21,22 that the pressure of condenser 2 and evaporimeter 3 detects.Pressure sensor 21,22 is connected with control device 20 respectively.In addition, high stage expansion valve 7 and low stage expansion valve 10 are also connected with control device 20 respectively.
In the turborefrigerator formed as shown in Figure 4, the pressure P c of pressure sensor 21 pairs of condensers 2 measures, and measured value is inputed to control device 20.In addition, the pressure P e of pressure sensor 22 pairs of evaporimeters 3 measures, and measured value is inputed to control device 20.The pressure differential (Pc-Pe) of control device 20 pairs of condensers 2 and evaporimeter 3 carries out computing, and controls in the mode making expansion valve opening reach the expansion valve opening extrapolated according to the form obtained in advance.
Fig. 5 is the curve map of the relation illustrated between the pressure differential (Pc-Pe) of condenser 2 and evaporimeter 3 and the aperture of expansion valve.Pressure differential (Pc-Pe) shown in Fig. 5 and the relation between the aperture of expansion valve are the relations of either party being applicable to high stage expansion valve 7 and low stage expansion valve 10.Obtain the relation between pressure differential (Pc-Pe) as shown in Figure 5 and expansion valve opening in advance, achieve curve table and format and store.In the operation process of turborefrigerator, pressure sensor 21,22 measures the pressure of condenser 2 and the pressure of evaporimeter 3 respectively, and measured value is inputted to control device 20.The pressure differential (Pc-Pe) of control device 20 pairs of condensers 2 and evaporimeter 3 carries out computing, based on the relation achieving Fig. 5 that tabular stores, controls the aperture of expansion valve (that is, high stage expansion valve 7 and low stage expansion valve 10).
In addition, also can not store form in control device, but the signal of telecommunication of pressure differential based on the pressure P c of the pressure sensor 21 and pressure P e of pressure sensor 22, the relation between pressure differential and the aperture of above-mentioned expansion valve utilizing Analogical Electronics to form to obtain in advance, controls the aperture of expansion valve thus.
So far, embodiments of the present invention are illustrated, but the present invention is not limited to above-mentioned embodiment, in the scope of its technological thought, certainly can be implemented by various different modes.
Claims (5)
1. a turborefrigerator, it possesses: evaporimeter, and it makes cold-producing medium evaporate from cooled fluid acquisition heat and plays refrigeration; Multistage turbocompressor, it utilizes multi-stage impeller to compress cold-producing medium; Condenser, it utilizes cooling fluid cool the refrigerant gas after compression and make it condensation; And as the energy-saving appliance of intercooler, it makes a part for condensed liquid refrigerant liquid evaporate, the refrigerant gas after evaporation is supplied to the mid portion of the multi-stage compression level of described multistage turbocompressor,
The feature of described turborefrigerator is,
Cold-producing medium is being guided to the refrigerant piping of described energy-saving appliance from described condenser, according to the order of throttle orifice, expansion valve, throttle orifice and expansion valve is being arranged,
Cold-producing medium is being guided to the refrigerant piping of described evaporimeter from described energy-saving appliance, according to the order of throttle orifice, expansion valve, throttle orifice and expansion valve are being arranged.
2. turborefrigerator according to claim 1, is characterized in that,
Described throttle orifice is made up of fixed orifice, and described expansion valve is made up of the DYN dynamic expansion valve that aperture is variable.
3. turborefrigerator according to claim 1 and 2, is characterized in that,
Described turborefrigerator possesses:
Liquid level sensor, it is arranged at described condenser and described energy-saving appliance respectively, measures cold-producing medium liquid level; And
Control device, it controls the aperture of described expansion valve,
Described control device based on be arranged at described condenser liquid level sensor measured value and the aperture of the expansion valve between described condenser and described energy-saving appliance is controlled, based on be arranged at described energy-saving appliance liquid level sensor measured value and the aperture of the expansion valve between described energy-saving appliance and described evaporimeter is controlled.
4. turborefrigerator according to claim 1 and 2, is characterized in that, possesses:
Pressure sensor, it is arranged at described condenser and described evaporimeter respectively, measures the pressure of condenser and the pressure of evaporimeter; And
Control device, it controls the aperture of described expansion valve,
Described control device, based on the pressure differential of the pressure of the condenser gone out by described determination of pressure sensor and the pressure of evaporimeter, controls the aperture of the aperture of the expansion valve between described condenser and described energy-saving appliance and the expansion valve between described energy-saving appliance and described evaporimeter.
5. turborefrigerator according to claim 4, is characterized in that,
Obtain the relation between the pressure differential of the pressure of condenser and the pressure of evaporimeter and the aperture of described expansion valve in advance, and the relation this obtained in advance is pre-stored within described control device,
The described relation that described control device is obtained in advance based on the pressure differential according to the pressure of condenser gone out by described determination of pressure sensor and the pressure of evaporimeter, determines the aperture of the aperture of the expansion valve between described condenser and described energy-saving appliance and the expansion valve between described energy-saving appliance and described evaporimeter.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2014-072680 | 2014-03-31 | ||
| JP2014072680A JP2015194301A (en) | 2014-03-31 | 2014-03-31 | turbo refrigerator |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN104949368A true CN104949368A (en) | 2015-09-30 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510136558.7A Pending CN104949368A (en) | 2014-03-31 | 2015-03-26 | Turbine refrigerator |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP2015194301A (en) |
| CN (1) | CN104949368A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113124581A (en) * | 2019-12-31 | 2021-07-16 | Lg电子株式会社 | Turbo refrigerator |
Families Citing this family (1)
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| JP2017146068A (en) * | 2016-02-19 | 2017-08-24 | 三菱重工業株式会社 | Refrigerating machine and its control method |
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| CN113124581B (en) * | 2019-12-31 | 2022-07-12 | Lg电子株式会社 | Turbo refrigerator |
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| JP2015194301A (en) | 2015-11-05 |
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