KR100315959B1 - Performance tester of two-stage centrifugal compressor - Google Patents
Performance tester of two-stage centrifugal compressor Download PDFInfo
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- KR100315959B1 KR100315959B1 KR1019990041487A KR19990041487A KR100315959B1 KR 100315959 B1 KR100315959 B1 KR 100315959B1 KR 1019990041487 A KR1019990041487 A KR 1019990041487A KR 19990041487 A KR19990041487 A KR 19990041487A KR 100315959 B1 KR100315959 B1 KR 100315959B1
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- refrigerant
- gas
- centrifugal compressor
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- liquid
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- 239000003507 refrigerant Substances 0.000 claims abstract description 66
- 239000007788 liquid Substances 0.000 claims abstract description 56
- 238000011056 performance test Methods 0.000 claims abstract description 15
- 238000012360 testing method Methods 0.000 claims abstract description 11
- 238000001816 cooling Methods 0.000 claims description 7
- 230000005494 condensation Effects 0.000 claims description 6
- 238000009833 condensation Methods 0.000 claims description 6
- 238000010438 heat treatment Methods 0.000 claims description 3
- 238000007906 compression Methods 0.000 abstract description 20
- 230000006835 compression Effects 0.000 abstract description 18
- 238000000034 method Methods 0.000 description 4
- 238000012827 research and development Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 2
- 239000010687 lubricating oil Substances 0.000 description 2
- 238000005259 measurement Methods 0.000 description 2
- 238000005057 refrigeration Methods 0.000 description 2
- 230000005540 biological transmission Effects 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 238000007710 freezing Methods 0.000 description 1
- 230000008014 freezing Effects 0.000 description 1
- 239000000314 lubricant Substances 0.000 description 1
- 239000011259 mixed solution Substances 0.000 description 1
- 238000012545 processing Methods 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B51/00—Testing machines, pumps, or pumping installations
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/06—Control using electricity
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2210/00—Working fluid
- F05B2210/10—Kind or type
- F05B2210/12—Kind or type gaseous, i.e. compressible
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- 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
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S417/00—Pumps
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Control Of Positive-Displacement Pumps (AREA)
Abstract
본 발명은 2단 원심압축기의 성능시험장치에 관한 것으로서, 그 목적은 2단 원심압축기의 성능 및 제반특성(온도특성, 압력특성, 소비전력, 전류 등)을 정확하게 측정할 수 있으며, 측정된 데이터를 분석하여 2단 원심압축기 및 냉매회로시스템의 개선에 활용할 수 있도록 함에 있다.The present invention relates to a performance test apparatus for a two-stage centrifugal compressor, and its purpose is to accurately measure the performance and general characteristics (temperature, pressure, power consumption, current, etc.) of the two-stage centrifugal compressor, and to measure the measured data. It can be used to improve the two-stage centrifugal compressor and refrigerant circuit system.
본 발명은 상기목적을 구현할 수 있도록 압축기시험사이클을 이루는 측정용 2단 원심압축기(11)와 응축기(12) 사이의 냉매라인(10)에 마련되며 2단 원심압축기 (11)의 1단압축부(11a)로 흡입되는 흡입냉매온도를 조절하는 흡입온도제어기(15); 상기 응축기(12)의 출구측과 흡입온도제어기(15)의 입구측의 냉매라인(10)에 마련되며 2차에 걸쳐 기체 및 액체상태로 분리되도록 1차측에서 기체로 분리된 냉매는 2차측 액체냉매로 유입되고 1차측에서 액체로 분리된 냉매는 2차측 기체냉매로 유입되게 분기냉매라인(10a,10b)을 통해 연결된 제1,제2기액분리기(13,14); 상기 응축기(12)의 출구측과 제1기액분리기(13) 입구측 사이의 냉매라인(10)에 마련된 제1팽창밸브(B1), 상기 제1기액분리기(13)의 기체 및 액체출구측과 제2기액분리기(14)의 입구측 사이의 분기냉매라인(10a,10b)에 마련된 제2,제3팽창밸브(B2,B3)가 구비됨을 특징으로 하는 2단 원심압축기의 성능시험장치를 요지로 한다.The present invention is provided in the refrigerant line (10) between the two-stage centrifugal compressor (11) and the condenser (12) for measuring the compressor test cycle to realize the above object, and the first stage compression unit of the two-stage centrifugal compressor (11). A suction temperature controller 15 for adjusting the suction refrigerant temperature sucked into the 11a; The refrigerant separated in the gas from the primary side is provided in the refrigerant line 10 at the outlet side of the condenser 12 and the inlet side of the suction temperature controller 15 and separated into gas and liquid state over the secondary liquid. First and second gas-liquid separators 13 and 14 connected through branched refrigerant lines 10a and 10b to be introduced into the refrigerant and separated into liquid at the primary side to be introduced into the secondary gas refrigerant; The first expansion valve B 1 provided in the refrigerant line 10 between the outlet side of the condenser 12 and the inlet side of the first gas liquid separator 13, and the gas and liquid outlet side of the first gas liquid separator 13. And second and third expansion valves B 2 and B 3 provided in branch refrigerant lines 10a and 10b between the inlet side of the second gas-liquid separator 14 and the second and third gas-liquid separators. Let the device be the gist.
Description
본 발명은 2단 원심압축기의 성능시험장치에 관한 것으로서, 보다 상세하게는 2단 원심압축기의 성능 및 제반특성을 측정할 수 있도록 함으로써 이러한 2단 원심압축기의 연구개발에 폭넓게 이용될 수 있도록 한 2단 원심압축기의 성능시험장치에 관한 것이다.The present invention relates to a performance test apparatus for a two-stage centrifugal compressor, and more particularly, to measure the performance and characteristics of a two-stage centrifugal compressor, thereby making it widely applicable to the research and development of such a two-stage centrifugal compressor. However, the present invention relates to a performance test apparatus for centrifugal compressors.
일반적인 2단 원심압축기는 등엔트로피 효율과 전체 효율에 있어서 냉동능력이 50RT이상에서 유리하기 때문에 주로 대용량으로만 사용되어왔다. 그러나 현재 과거에는 불가능했던 소형인 10RT이하의 원심압축기는 기초과학의 발달과 가공기술 및 인버터기술의 발달로 상용화가 가능하게 되었다. 이러한 10RT이하의 2단 원심압축기는 윤활유를 사용하지 않으면서 약 36,000RPM 이상의 회전속도를 갖고 있다는 점과 인버터를 통해 모터의 속도를 제어한다는 점에서 대형의 2단 원심압축기와는 성능 및 제반특성을 측정하는 시스템이 다르다.The general two-stage centrifugal compressor has been mainly used in large capacity because its freezing capacity is more than 50RT in isentropic efficiency and overall efficiency. However, the compact centrifugal compressor below 10RT, which was impossible in the past, can be commercialized due to the development of basic science, processing technology and inverter technology. These two-stage centrifugal compressors of 10RT or less have performance and characteristics in comparison with large two-stage centrifugal compressors in that they have a rotation speed of about 36,000 RPM or more without using lubricant and control the speed of the motor through an inverter. The measuring system is different.
또, 일반적으로 상용화된 압축기(왕복동식, 회전식, 스크롤식)들은 압축과정에서 부품간의 접촉이 발생하는 접촉식이며, 이러한 접촉식의 압축기는 필연적으로 마찰구조에 따른 윤활유가 필요하다.In general, commercially available compressors (reciprocating type, rotary type, scroll type) are contact types in which contact between parts occurs in the compression process, and such contact type compressors inevitably require lubricating oil according to the friction structure.
이와 반하여 2단 원심압축기는 모터와 구동 연결된 임펠러가 모터의 회전력에 따라 작동유체에 운동에너지를 가하고 이러한 운동에너지를 디퓨져를 통해 압력에너지로 변환시키는 비접촉구조로써 그 동작조건이나 냉매에 따른 냉매회로 또는 냉동사이클이 다르며, 이 때문에 종래 압축기의 성능시험장치로는 적용이 어려울 뿐만 아니라 효과적인 성능 및 제반 압축기 특성들을 정확히 측정하거나 분석하는데 어려운 점이 많았다.On the contrary, the two-stage centrifugal compressor is a non-contact structure in which an impeller connected to the motor applies kinetic energy to the working fluid according to the rotational force of the motor and converts the kinetic energy into pressure energy through a diffuser. The refrigeration cycle is different, and therefore, it is difficult to apply the performance test apparatus of the conventional compressor, and it is difficult to accurately measure or analyze the effective performance and characteristics of all compressors.
또한 원심압축기의 특성상 압축률을 발생하기 위해서 2단 및 그이상의 압축과, 압축기의 설계구조 및 냉매특성에 따라 단단 및 2단이상의 팽창사이클로 구성되기 때문에 이러한 시스템에 기존 냉매압축기의 성능시험장치로는 적용이 어려운 것이었다.In addition, due to the characteristics of centrifugal compressors, two-stage and more compressions are used to generate a compression ratio, and the single-stage and two-stage expansion cycles are applied according to the compressor's design structure and refrigerant characteristics. This was difficult.
따라서, 원심압축기의 사이클을 변경시키거나 시스템에의 적용을 위한 시험에도 냉매회로의 변경이 용이하고, 시스템에 적절하게 적용시킬 수 있는 시험장치가 필요하다.Therefore, there is a need for a test apparatus that can be easily changed in the refrigerant circuit and can be appropriately applied to the system even in a test for changing the cycle of the centrifugal compressor or applying to the system.
그러나, 종래에는 이러한 2단 원심압축기의 성능을 측정하기 위한 장치가 전혀 제안된 바 없으므로 이러한 압축기의 성능측정 및 제반특성을 시험하는데 장애가 되는 문제점이 있었다.However, in the related art, since the device for measuring the performance of such a two-stage centrifugal compressor has not been proposed at all, there is a problem in that the performance measurement and various characteristics of the compressor are hindered.
본 발명의 목적은 2단 원심압축기의 성능 및 제반특성(온도특성, 압력특성, 소비전력, 전류 등)을 정확하게 측정할 수 있고 특히 흡입온도를 제어함과 동시에 응축압력을 변화시켜 압축률을 변경시킬 수 있으며, 원심압축기에서 사용하는 단단 또는 2단 이상의 압축은 물론 팽창사이클 조건에서도 시스템을 적용이 용이하고, 측정된 데이터를 분석하여 원심압축기나 냉매회로시스템을 개선시킴에 활용함으로써 연구개발의 효율을 크게 향상시킬 수 있도록 한 2단 원심압축기의 성능시험장치를 제공하는데 있다.An object of the present invention is to accurately measure the performance and overall characteristics (temperature characteristics, pressure characteristics, power consumption, current, etc.) of a two-stage centrifugal compressor, and in particular, to control the suction temperature and to change the compression ratio by changing the condensation pressure. It is easy to apply the system in the expansion cycle condition as well as the single stage or two stage compression of centrifugal compressor, and it is used to improve the centrifugal compressor or refrigerant circuit system by analyzing the measured data. It is to provide a performance test apparatus for a two-stage centrifugal compressor that can be greatly improved.
도 1은 본 발명에 따른 2단 원심압축기의 성능시험장치를 나타낸 개략도,1 is a schematic view showing a performance test apparatus of a two-stage centrifugal compressor according to the present invention;
도 2는 도 1의 성능시험장치에 온도계, 압력계, 유량계 등을 적용시킨 실시 예의 냉매회로도,2 is a refrigerant circuit diagram of an embodiment in which a thermometer, a pressure gauge, a flow meter, and the like are applied to the performance test apparatus of FIG. 1;
도 3은 본 발명의 2단압축/2단팽창 사이클을 나타낸 압력-엔탈피에 대한 그래프,Figure 3 is a graph of the pressure-enthalpy showing the two-stage compression / two-stage expansion cycle of the present invention,
도 4는 본 발명의 성능시험장치에 적용된 흡입온도제어기를 나타낸 단면도이다.4 is a cross-sectional view showing a suction temperature controller applied to the performance test apparatus of the present invention.
〈도면의 주요부분에 대한 부호설명〉<Code Description of Main Parts of Drawing>
11: 2단 원심압축기 12: 응축기11: two stage centrifugal compressor 12: condenser
13: 제1기액분리기 14: 제2기액분리기13: first gas-liquid separator 14: second gas-liquid separator
15: 흡입온도제어기 16: 유량계15: suction temperature controller 16: flow meter
17: 응축기 팬 B1∼B3: 제1 내지 제3 팽창밸브17: condenser fan B 1 to B 3 : first to third expansion valve
T1∼T11: 제1 내지 제11 온도계 P1∼P9: 제1 내지 제9 압력계T 1 -T 11 : 1st-11th thermometers P 1 -P 9 : 1st-9th pressure gauges
본 발명은 압축기시험사이클을 이루는 측정용 소형의 2단 원심압축기와 응축기 사이의 냉매라인에 마련되며 원심압축기의 1단압축부로 흡입되는 흡입냉매온도를 조절하는 흡입온도제어기; 상기 응축기의 출구측과 흡입온도제어기의 입구측의 냉매라인에 마련되며 2차에 걸쳐 기체 및 액체상태로 분리되도록 1차측에서 기체로 분리된 냉매는 2차측 액체냉매로 유입되고 1차측에서 액체로 분리된 냉매는 2차측 기체냉매로 유입되게 냉매라인을 통해 연결된 제1,제2기액분리기; 상기 응축기의 출구측과 제1기액분리기 입구측 사이의 냉매라인에 마련된 제1팽창밸브; 상기 제1기액분리기의 기체 및 액체출구측과 제2기액분리기의 입구측 사이의 분기냉매라인에 마련된 제2,제3팽창밸브가 구비됨을 특징으로 하는 2단 원심압축기의 성능시험장치에 있다.The present invention is provided in a refrigerant line between a small two-stage centrifugal compressor and a condenser for measuring constituting a compressor test cycle, the suction temperature controller for adjusting the suction refrigerant temperature sucked into the first stage of the centrifugal compressor; The refrigerant, which is provided in the refrigerant line at the outlet side of the condenser and the inlet side of the suction temperature controller, is separated into gas and liquid from the primary side to be separated into gas and liquid state over the secondary, and is introduced into the secondary liquid refrigerant and flows into the liquid from the primary side. The separated refrigerant is the first and second gas-liquid separator connected through the refrigerant line to flow into the secondary gas refrigerant; A first expansion valve provided in a refrigerant line between an outlet side of the condenser and an inlet side of the first gas liquid separator; And a second and third expansion valve provided in the branch refrigerant line between the gas and liquid outlet side of the first gas-liquid separator and the inlet side of the second gas-liquid separator.
또 본 발명은 상기 2단 원심압축기→응축기→제1,제2기액분리기→흡입온도제어기로 이어지는 냉매회로 각부위치의 냉매온도 및 압력과 유량을 측정할 수 있는 온도계, 압력계, 유량계가 구비됨을 특징으로 하는 2단 원심압축기의 성능시험장치에 있다.In another aspect, the present invention is characterized in that the two-stage centrifugal compressor → condenser → the first, second gas-liquid separator → suction temperature controller is provided with a thermometer, a pressure gauge, a flow meter for measuring the refrigerant temperature and pressure and flow rate at each position of the refrigerant circuit It is in the performance test apparatus of two stage centrifugal compressor.
이하, 본 발명의 이해를 돕기 위하여 첨부도면에 의거 구체적으로 설명한다.Hereinafter, the present invention will be described in detail with reference to the accompanying drawings.
도 1은 본 발명에 따른 원심압축기의 성능시험장치를 설명하기 위해 나타낸 냉매사이클회로이다.1 is a refrigerant cycle circuit shown to explain the performance test apparatus of the centrifugal compressor according to the present invention.
도면에 나타낸 바와 같이, 본 발명의 측정을 위한 소형의 2단 원심압축기(11)에는 하나의 사이클을 이루도록 응축기(12), 제1 내지 제3팽창밸브(B1∼B3), 제1,제2기액분리기(13,14) 및 흡입온도제어기(15)가 냉매라인(10)으로 연결되어 있다.As shown in the figure, the compact two-stage centrifugal compressor 11 for the measurement of the present invention comprises a condenser 12, first to third expansion valves B 1 to B 3 , first, The second gas liquid separators 13 and 14 and the suction temperature controller 15 are connected to the refrigerant line 10.
상기 2단 원심압축기(11)는 냉동능력이 10RT이하의 소형압축기로서, 그 전동부분 또한 윤활유 없이 고속 회전되게 마련되어 있으며, 상기 측정용 2단 원심압축기(11)의 입구부분인 냉매라인(10)에는 냉매의 흡입온도를 조절할 수 있는 흡입온도제어기(15)가 마련되어있다.The two-stage centrifugal compressor (11) is a compact compressor having a refrigeration capacity of 10 RT or less, and its transmission part is also provided to rotate at high speed without lubricating oil. The refrigerant line (10) is an inlet of the two-stage centrifugal compressor (11). The suction temperature controller 15 that can adjust the suction temperature of the refrigerant is provided.
상기 2단 원심압축기(11)는 각단의 효율이나, 모터냉각열량, 냉매유량, 마하수, 압축비, 레놀드수 등 성능에 미치는 인자들이 2단 원심압축기(11)의 흡입냉매온도에 지대한 영향을 주는 것이므로 시험목적에 따라 흡입온도를 변환시켜 가면서 성능변화를 특정하는 것이 중요하다.Since the two-stage centrifugal compressor (11) has a great influence on the suction refrigerant temperature of the two-stage centrifugal compressor (11) due to factors such as efficiency of each stage, performance of motor cooling heat, refrigerant flow rate, Mach number, compression ratio, and Lennold number. It is important to specify the performance change by changing the suction temperature according to the test purpose.
상기 흡입온도제어기(15)는 도 4와 같이 그 내부의 냉매라인(10)을 통해 2단 원심압축기(1)로 흡입되는 냉매흡입온도를 시험목적에 따라 변환시킬 수 있도록 밀폐용기 내부에 소정레벨만큼의 2차냉매(15b)가 채워져 있으며 상기 밀폐용기의 하부에는 2차냉매(15b)를 가열하는 히터(15a)가 마련되어 있고 상기 밀폐용기의 상부에는 2차냉매(15b)를 냉각시키는 냉각유닛(15c)이 마련되어 있다. 상기 흡입온도제어기(15)의 히터(15a)와 냉각유닛(15c)은 2차냉매(15b)를 가열하고 냉각하면서 설정흡입온도로 2단 원심압축기(11)의 흡입온도를 맞추게 된다.The suction temperature controller 15 has a predetermined level inside the sealed container so as to convert the refrigerant suction temperature sucked into the two-stage centrifugal compressor 1 through the refrigerant line 10 therein according to the test purpose as shown in FIG. As much as the secondary refrigerant 15b is filled, the lower portion of the sealed container is provided with a heater 15a for heating the secondary refrigerant 15b and the cooling unit for cooling the secondary refrigerant 15b in the upper portion of the sealed container. 15c is provided. The heater 15a and the cooling unit 15c of the suction temperature controller 15 adjust the suction temperature of the second stage centrifugal compressor 11 to the set suction temperature while heating and cooling the secondary refrigerant 15b.
이와 같이 냉매의 흡입온도를 맞추는 과정은 냉매온도를 2단 원심압축기(11)의 1단압축부(11a) 입구측 냉매라인(10)에 설치된 온도센서(T1)로부터 현재의 온도를 측정하여 컨트롤러에서 설정값과 측정치를 비교하여 편차에 해당하는 출력신호를 송출하게 되고 이 출력신호를 받은 작동기(Actuator)에서 컨트롤러의 출력신호를 받아 히터전압을 조절하여 피드백제어를 반복함으로써 설정온도를 맞추게 된다.The process of adjusting the suction temperature of the refrigerant as described above by measuring the current temperature from the temperature sensor (T 1 ) installed in the refrigerant line 10 of the inlet side of the first stage 11a of the two-stage centrifugal compressor (11a). The controller compares the set value with the measured value and sends the output signal corresponding to the deviation. The actuator receives the output signal from the controller and adjusts the heater voltage to repeat the feedback control to set the set temperature. .
이렇게 시험목적에 맞도록 설정온도로 맞춰진 냉매는 2단 원심압축기(1)의 1단압축부(11a)측으로 유입되고, 모터(11b)를 냉각시킨 후 2단압축부(11c)의 입구로 유입되고, 2단 압축과정을 통해 2단압축부(11c) 출구측으로 보내지며. 2단압축부 (11c)의 출구측은 응축기(12)의 입구측과 연결되어 있다.Thus, the refrigerant adjusted to the set temperature to meet the test purpose flows into the first stage 11a of the two-stage centrifugal compressor 1, cools the motor 11b, and then flows into the inlet of the second stage 11c. It is sent to the outlet of the second stage compression section (11c) through a two stage compression process. The outlet side of the two-stage compression section 11c is connected to the inlet side of the condenser 12.
상기 응축기(12)는 시험조건에 맞춰 응축압력을 제어하기 위한 응축기 팬(17)이 마련되어 있고 이 응축기 팬(17)은 컨트롤러의 제어에 의해 구동됨으로써 공기를 강제적으로 통풍시켜 응축과정을 제어할 수 있으며, 상기 응축기 팬(17)의 조절은 응축기(12)의 후단에 설치된 디지털압력센서(P5)의 압력신호를 받아 응축기 팬(17)의 속도를 조절함으로써 응축압력을 조절 및 제어할 수 있게 된다.The condenser 12 is provided with a condenser fan 17 for controlling the condensation pressure in accordance with the test conditions, the condenser fan 17 is driven by the control of the controller to forcibly ventilate the air to control the condensation process The control of the condenser fan 17 receives the pressure signal of the digital pressure sensor P 5 installed at the rear end of the condenser 12 so as to control and control the condensation pressure by adjusting the speed of the condenser fan 17. do.
상기 응축기(12)의 출구측에는 제1기액분리기(13)의 입구측과 연결되어 있고 상기 응축기(12)의 출구측과 제1기액분리기(13) 입구측 사이에는 2단 팽창시 냉매유량을 조절하기 위한 제1팽창밸브(B1)가 연결되어 있다.The outlet side of the condenser 12 is connected to the inlet side of the first gas-liquid separator 13, and the refrigerant flow rate is adjusted during two stage expansion between the outlet side of the condenser 12 and the inlet side of the first gas-liquid separator 13. The first expansion valve B 1 is connected.
또, 상기 제1팽창밸브(B1)와 연결된 제1기액분리기(13)에는 제1기액분리기 (13)의 기체 및 액체출구와 제각기 기체 및 액체입구가 분기냉매라인(10a,10b)에 의해 이어지는 제2기액분리기(14)가 연결되어 있고, 상기 제1,제2기액분리기(13,14) 사이의 분기냉매라인(10a,10b)에는 제2,제3팽창밸브(B2,B3)들이 설치되어 있다.In addition, in the first gas-liquid separator 13 connected to the first expansion valve B 1 , the gas and liquid outlets of the first gas-liquid separator 13 and the respective gas and liquid inlets are separated by branch refrigerant lines 10a and 10b. A second gas-liquid separator 14 is connected thereto, and second and third expansion valves B 2 and B 3 are connected to branch refrigerant lines 10a and 10b between the first and second gas-liquid separators 13 and 14. ) Are installed.
또, 상기 2단 원심압축기(11)→응축기(12)→제1 내지 제3팽창밸브(B1∼B3)→제1,제2기액분리기(13,14)→흡입온도제어기(15)로 이어지는 냉매회로의 각 부위에는 냉매온도 및 압력과 유량을 측정할 수 있도록 온도계(T1-T11), 압력계(P1-P9), 유량계(16)가 마련되어 있다.The two-stage centrifugal compressor (11) → condenser (12) → first to third expansion valves (B 1 to B 3 ) → first and second gas-liquid separators (13, 14) → suction temperature controller (15). In each portion of the refrigerant circuit, a thermometer T 1 -T 11 , a pressure gauge P 1 -P 9 , and a flow meter 16 are provided to measure the refrigerant temperature, pressure, and flow rate.
도 2는 본 발명의 2단 원심압축기의 성능시험장치에 필수적으로 설치되는 계측기까지 나타낸 냉매사이클회로이다.2 is a refrigerant cycle circuit showing a measuring instrument which is essentially installed in the performance test apparatus of the two-stage centrifugal compressor of the present invention.
여기에서는, 2단 원심압축기(11)의 1단압축부(11a) 입구측에는 제1온도계 (T1)와 제1 압력계(P1)가 설치되어 있고 상기 제1온도계(T1)를 통해 흡입온도제어가 이루어지며, 상기 2단 원심압축기(11)의 1단압축부(11a) 출구에는 제2온도계(T2) 및 제2압력계(P2)가 설치되어 있다.Here, the first thermometer (T 1 ) and the first pressure gauge (P 1 ) are provided at the inlet side of the first stage compression section (11a) of the two-stage centrifugal compressor (11) and sucked in through the first thermometer (T 1 ). Temperature control is performed, and a second thermometer (T 2 ) and a second pressure gauge (P 2 ) are installed at the outlet of the first stage compression unit (11a) of the two-stage centrifugal compressor (11).
또, 2단 원심압축기(11)의 압축부인 1단압축부(11a)의 출구와 2단압축부 (11c)의 입구사이에는 제3온도계(T3)와 제3압력계(P3)가 설치되어 있으며, 2단 원심압축기(11)의 2단압축부(11c) 출구와 응축기(2)사이에는 제4온도계(T4)와 제4압력계(P4)가 설치되어 있다.A third thermometer T 3 and a third pressure gauge P 3 are installed between the outlet of the first stage compressor 11a, which is the compression unit of the two stage centrifugal compressor 11, and the inlet of the two stage compressor 11c. A fourth thermometer T 4 and a fourth pressure gauge P 4 are provided between the outlet of the second stage compressor 11c of the two stage centrifugal compressor 11 and the condenser 2.
또, 상기 응축기(12)와 제1팽창밸브(B1) 사이에는 제5온도계(T5) 및 제5압력계(P5)가 설치되어 있고, 이때 제5압력계(P5)는 디지털센서가 부착된 컨트롤러를 통해 응축기 팬(17)의 속도를 제어할 수 있다. 상기 제1팽창밸브(B1)와 제1기액분리기 (13) 입구측 사이에는 제6온도계(T6) 및 제6압력계(P6)가 설치되어 있으며, 제2,제3 팽창밸브(B2,B3)의 출구와 제2 기액분리기(14)의 입구측 사이에는 제각기 제7,제8온도계(T7,T8)가 설치되어 있다.In addition, a fifth thermometer T 5 and a fifth pressure gauge P 5 are installed between the condenser 12 and the first expansion valve B 1 , wherein the fifth pressure gauge P 5 is a digital sensor. An attached controller can control the speed of the condenser fan 17. A sixth thermometer T 6 and a sixth pressure gauge P 6 are installed between the first expansion valve B 1 and the inlet side of the first gas-liquid separator 13, and the second and third expansion valves B 6 are provided. 2, a B 3) of the outlet and the second respectively, the seventh, eighth thermometer (T 7, T 8 between the inlet side of the gas-liquid separator 14) is provided.
또, 상기 제2기액분리기(14)의 출구와 2단 원심압축기(11)의 1단압축부(11a) 입구 사이에는 제9온도계(T9)와 제7압력계(P7)가 설치되어 있고, 제9온도계(T9), 제7압력계(P7)들과 제1온도계(T1), 제1압력계(P1)들 사이에는 유량계(16)가 설치되어 있으며, 이때 제1온도계(T1)의 디지털 신호를 흡입온도제어기(15)로 피드백하여 흡입온도를 제어하게된다.A ninth thermometer T 9 and a seventh pressure gauge P 7 are provided between the outlet of the second gas-liquid separator 14 and the inlet of the first stage compression section 11a of the two-stage centrifugal compressor 11. The flowmeter 16 is installed between the ninth thermometer (T 9 ), the seventh pressure gauge (P 7 ), the first thermometer (T 1 ), and the first pressure gauge (P 1 ), wherein the first thermometer ( The digital signal of T 1 ) is fed back to the suction temperature controller 15 to control the suction temperature.
이와 같이 구성된 본 발명은 도 1,2 및 도 4에 나타낸 바와 같이 성능을 측정하고자 하는 2단 원심압축기(11)를 성능시험장치에 설치하고 2단 원심압축기(11) 및 냉매회로상의 각 구성요소들을 구동시킨다.In the present invention configured as described above, the two-stage centrifugal compressor 11 to measure the performance as shown in FIGS. 1,2 and 4 is installed in the performance test apparatus, and the two-stage centrifugal compressor 11 and each component on the refrigerant circuit. Drive them.
상기 2단 원심압축기(11)에서는 압축된 기체가 응축기(12)를 통과하면서 액체상태로 되고, 이 액체상태의 냉매가 제1팽창밸브(B1)를 지나면서 액체상태와 기체상태를 갖는 혼합액으로 되며, 이러한 혼합액을 제1기액분리기(13)에서 액체상태와 기체상태로 분리하여 1차 팽창시킨다.In the two-stage centrifugal compressor (11), the compressed gas passes through the condenser (12) into a liquid state, and the mixed liquid having a liquid state and a gas state passes through the first expansion valve (B 1 ). The mixed solution is separated into a liquid state and a gaseous state in the first gas-liquid separator 13 to be first expanded.
즉, 제1팽창밸브(B1)를 통과한 냉매는 액체상태와 기체상태가 혼합된 상태이며, 제1기액분리기(13)에서 액체상태와 기체상태로 분리하여 제2,제3팽창밸브 (B2,B3)를 통하여 제2기액분리기(14)로 보내지며, 이 과정에서 2차 팽창이 이루어진다.That is, the refrigerant passing through the first expansion valve B 1 is in a liquid state and a gaseous state, and is separated into a liquid state and a gaseous state in the first gas-liquid separator 13 to form a second and third expansion valve ( B 2 , B 3 ) is sent to the second gas-liquid separator 14, in which secondary expansion occurs.
이와 같이 2단압축 2단팽창되는 본 발명의 성능시험장치가 구동되면 도 3과 같은 압력- 엔탈피 그래프를 얻는다.As such, when the performance test apparatus of the present invention in which the two-stage compression is expanded in two stages is obtained, a pressure-enthalpy graph as shown in FIG.
2단 원심압축기(11)의 성능을 측정하기 위해서는 본 발명의 냉매회로를 이루는 각 부품의 입구 또는 출구에 설치된 제1 내지 제11온도계(T1-T11)와 제1 내지 제9압력계(P1-P9)를 통하여 각 부위의 온도 및 압력을 측정한다.In order to measure the performance of the two-stage centrifugal compressor (11), the first to eleventh thermometer (T 1 -T 11 ) and the first to ninth pressure gauge (P) installed at the inlet or outlet of each component constituting the refrigerant circuit of the present invention. 1 -P 9 ) to measure the temperature and pressure of each site.
또, 유량계(16)에서는 해당부위의 유량을 측정하여 다른 측정값(압력과 온도)과 같이 압축기의 성능을 계산한다.In addition, the flowmeter 16 measures the flow rate of the corresponding portion and calculates the performance of the compressor like other measured values (pressure and temperature).
각단의 효율은 도 3과 같이 엔탈피를 구하여 계산한다.The efficiency of each stage is calculated by calculating the enthalpy as shown in FIG.
일례로, 2단 원심압축기(11)의 1단측 효율은 그 입구측의 온도와 압력(T1과 P1)을 측정한 값으로 엔탈피를 계산한 후, 등엔트로피로 계산한 값과 출구측에서 측정한 값의 계산치를 이용하여 구한다.For example, the first stage efficiency of the two-stage centrifugal compressor 11 is calculated by measuring the enthalpy of the inlet side and the temperature and pressure (T 1 and P 1 ), It calculates using calculated value of measured value.
1단의 비압축일은 입구측과 출구측의 엔탈피 차로 구한다.The uncompressed work in the first stage is obtained by the difference in enthalpy between the inlet and outlet sides.
L1= h1- h2[J/Kg]L 1 = h 1 -h 2 [J / Kg]
1단측의 압축일은 비압축일에 유량을 곱하여 구한다.The compression day at the first stage is obtained by multiplying the flow rate by the non-compression day.
N1= L1×G [W]N 1 = L 1 × G [W]
1단 임펠러의 비유량계수는 1단 임펠러의 직경과 입구의 온도 및 압력을 이용해서 계산한 밀도와 임펠러의 원주속도 U21을 이용하여 구한다.The specific flow coefficient of the first stage impeller is obtained using the density calculated from the diameter of the first stage impeller, the temperature and the pressure of the inlet, and the circumferential speed U 21 of the impeller.
이렇게 하여 2단 원심압축기(11)의 성능 및 제반특성(온도특성, 압력특성, 소비전력, 전류 등)을 정확하게 측정할 수 있으며, 이를 이용하여 2단 원심압축기 (11)와 냉매회로시스템의 최적작동조건을 찾을 수 있고 이러한 연구개발에 활용할 수 있는 것이다.In this way, the performance and overall characteristics (temperature characteristics, pressure characteristics, power consumption, current, etc.) of the two-stage centrifugal compressor 11 can be accurately measured, and the optimal performance of the two-stage centrifugal compressor 11 and the refrigerant circuit system is used. The operating conditions can be found and used for such research and development.
한편, 본 발명의 상기와 같은 실시 예에서는 2단 팽창과정을 통한 시험장치로 설계하고 있으나 2단 팽창의 경우와 마찬가지로 추가되는 팽창밸브와 기액분리기를 액체상태와 기체상태로 구분하여 연결되도록 증감시키면 3단 또는 1단의 팽창과정을 가지는 사이클에도 적용이 가능하게 된다.On the other hand, in the above embodiment of the present invention is designed as a test device through a two-stage expansion process, but as in the case of two-stage expansion, if the expansion valve and the gas-liquid separator is added to the liquid state and gaseous state is connected to increase and decrease It is also possible to apply to a cycle having a three-stage or one-stage expansion process.
이상에서 상세하게 설명한 바와 같이, 본 발명에 따른 2단 원심압축기의 성능시험장치는 압축기의 성능 및 제반특성(온도특성, 압력특성, 소비전력, 전류 등)을 정확하게 측정할 수 있고 특히 냉매흡입온도를 제어함과 동시에 응축압력을 변화시켜 압축률의 변경이 용이하게 되는 효과가 있다.As described in detail above, the performance test apparatus of the two-stage centrifugal compressor according to the present invention can accurately measure the performance and various characteristics (temperature characteristics, pressure characteristics, power consumption, current, etc.) of the compressor, and in particular, the refrigerant suction temperature. While controlling the effect of changing the condensation pressure at the same time it is easy to change the compression ratio.
또 본 발명은 원심압축기에서 사용하는 단단 또는 2단 이상의 압축은 물론 팽창사이클 조건에서도 시스템을 적용이 용이하고, 측정된 데이터를 분석하여 원심압축기나 냉매회로시스템을 개선하는데 활용함으로써 연구개발의 효율을 크게 향상시킬 수 있는 특유의 효과가 있다.In addition, the present invention is easy to apply the system in the expansion cycle conditions as well as the single stage or two or more stages of compression used in the centrifugal compressor, by analyzing the measured data to improve the centrifugal compressor or refrigerant circuit system to improve the efficiency of research and development There is a unique effect that can be greatly improved.
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