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KR20090069694A - Multi-roach type throttling valve-equipment multistage compression type compressor - Google Patents

Multi-roach type throttling valve-equipment multistage compression type compressor Download PDF

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KR20090069694A
KR20090069694A KR1020070137441A KR20070137441A KR20090069694A KR 20090069694 A KR20090069694 A KR 20090069694A KR 1020070137441 A KR1020070137441 A KR 1020070137441A KR 20070137441 A KR20070137441 A KR 20070137441A KR 20090069694 A KR20090069694 A KR 20090069694A
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South Korea
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refrigerant
condenser
evaporator
valve
throttling valve
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KR1020070137441A
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Korean (ko)
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정봉철
류구영
정일권
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주식회사 신성엔지니어링
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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
    • F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
    • F25B1/053—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type of turbine type
    • 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
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0401—Refrigeration circuit bypassing means for the compressor
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers
    • 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
    • F25B2600/2507—Flow-diverting valves

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  • 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)

Abstract

본 발명은 다단 압축방식 터보냉동기에 관련한 것으로서, 다단 압축기, 응축기, 제1 교축밸브, 이코노마이저, 제2 교축밸브 및 증발기를 순차적으로 액관 및 가스관으로 되는 배관에 의해 연통 가능하게 라인연결되는 주 냉매회로와, 상기 주 냉매회로의 응축기로부터 교축밸브로 유동하는 액관 내의 냉매의 일부를 제1 교축밸브 및 이코노마이저를 경유하여 상기 다단 압축기로 토출시키는 주입로를 구비하는 다단 압축방식 터보냉동기에 있어서, 상기 주입로에는 상기 응축기와 증발기의 차압이 설정 압력 이하로 떨어질 경우, 폐쇄되어 상기 주 냉매회로로만 냉매를 유동토록 하여 액냉매의 압축기로의 유입을 차단하도록 폐쇄 작동되는 제1 전자밸브가 개재되도록 구성하며, 2단 이상의 압축방식을 적용하는 열교환기 및 이코노마이저(Economizer)에서 전부하 상태에 최적 설계된 고정형 오리피스가 설계온도 이하의 냉각수 온도 상태 또는 부분부하 상태에서 교축효율이 떨어지는 문제를 해결하기 위해, 2로형 순환 교축장치를 적용함으로써 냉동부하에 따라 상응하는 최적의 냉매 순환량을 증발기에 공급함으로써 냉동능력을 향상시킬 수 있도록 하였다.The present invention relates to a multi-stage compression type turbocooler, wherein the multi-stage compressor, the condenser, the first throttling valve, the economizer, the second throttling valve, and the evaporator are connected in series by a pipe consisting of a liquid pipe and a gas pipe. And an injection path for discharging a part of the refrigerant in the liquid pipe flowing from the condenser of the main refrigerant circuit to the throttling valve to the multistage compressor via a first throttling valve and an economizer, wherein the injection is performed. When the differential pressure of the condenser and the evaporator drops below a set pressure, the furnace is closed so that the refrigerant flows only into the main refrigerant circuit so that the first solenoid valve is closed to block the inflow of the liquid refrigerant into the compressor. In heat exchangers and economizers that use two or more stages of compression In order to solve the problem that the fixed orifice designed optimally for the load condition has a low throttling efficiency at the coolant temperature or the partial load below the design temperature, the two-way circulating throttling device is applied to the corresponding optimum refrigerant circulation according to the refrigeration load. It was possible to improve the freezing capacity by supplying the

Description

다로형 교축밸브-구비 다단 압축방식 터보냉동기{CENTRIFUGAL CHILLER HAVING MULTI WAY THROTTLE APPARATUS}Multi-rotor throttling valve-equipment multi-stage compression type turbo freezer {CENTRIFUGAL CHILLER HAVING MULTI WAY THROTTLE APPARATUS}

본 발명은 터보 냉동기의 다로형 교축장치에 관한 것으로, 특히, 2단 이상의 압축방식을 적용하는 냉동사이클의 교축조절이 용이한 터보 냉동기의 다로형 교축밸브를 구비한 다단 압축방식 터보냉동기에 관한 것이다.The present invention relates to a multi-rotor throttling device of a turbo-cooler, and more particularly, to a multi-stage compression turbo-cooler having a multi-role throttling valve of a turbo-freezer that is easy to adjust the throttling of a refrigeration cycle to which two or more compression systems are applied. .

일반적으로, 대규모의 공기 조절용으로 사용하는 터보 냉동기의 경우에는 임펠러를 회전시켜 생기는 기체의 원심력을 이용하여 기체를 압송하는 방식의 터보 압축기를 사용하여 냉매를 압축하는 것으로서, 효율 향상을 위하여 다단 압축방식을 적용하는데 도 1에 도시한 바와 같은 감압장치를 사용하여 냉매의 압력을 조절하게 된다.In general, in the case of a turbo-cooler used for large-scale air conditioning, the refrigerant is compressed by using a turbo compressor of a method of pumping gas by using centrifugal force of the gas generated by rotating the impeller. The pressure of the refrigerant is adjusted by using a pressure reducing device as shown in FIG. 1.

도 1은 종래의 2단 압축 터보 냉동기의 구성을 나타낸 개략도로서, 인렛가이드 베인(1a)을 통하여 흡입되는 저온저압의 냉매를 고온 고압의 기체로 압축시키는 압축기(1)와, 냉각탑에서 유입되는 냉각수에 의해 압축기(1)로부터 토출되는 고온 고압의 냉매가스를 응축시키는 응축기(2)와, 응축된 냉매를 감압하여 팽창시키는 제1 교축밸브(5)가 내장된 교축장치와, 냉매파이프를 통해서 제1 교축밸브(5)를 지 난 냉매에서 발생한 냉매 가스를 분리하는 이코노마이저(Economizer)(4), 이코노마이저(4)를 통과한 냉매를 다시 감압하여 팽창시키는 제2 교축밸브(6)와 냉매파이프를 통해 제2 교축밸브(6)로부터 보내진 냉매를 증발시키는 증발기(3)로 이루어져 있다.1 is a schematic view showing a configuration of a conventional two-stage compressed turbo refrigerator, comprising a compressor (1) for compressing a low temperature low pressure refrigerant sucked through an inlet guide vane (1a) into a gas of high temperature and high pressure, and cooling water flowing from a cooling tower A condenser (2) for condensing the high temperature and high pressure refrigerant gas discharged from the compressor (1), a first throttling valve (5) for decompressing and expanding the condensed refrigerant, and a refrigerant pipe through the refrigerant pipe. 1) the second throttle valve 6 and the refrigerant pipe which decompress and expand the refrigerant passing through the economizer 4 for separating the refrigerant gas generated from the refrigerant passing through the throttle valve 5 and the economizer 4 again. It consists of an evaporator (3) for evaporating the refrigerant sent from the second throttling valve (6).

상기 증발기(3)로 유입된 냉매는 냉수와 열교환되는 과정에서 냉수를 냉각시키도록 되어 있는데, 증발기(3) 내에는 습증기를 제거하기 위한 엘리미네이터(7, eliminator)가 설치되어 있다. 이에 따라, 증발기(3)내에서 증발된 냉매가 지니고 있는 습증기는 냉매가 엘리미네이터(7)를 통과하는 과정에서 제거된다.The refrigerant introduced into the evaporator (3) is to cool the cold water in the process of heat exchange with the cold water, the evaporator (3) is provided with an eliminator (7, eliminator) for removing the wet steam. Accordingly, the wet steam of the refrigerant evaporated in the evaporator 3 is removed in the process of passing the refrigerant through the eliminator 7.

상기 증발기(3)에서 저압의 냉매액이 냉수와 열교환후 증발한 냉매가스는 증발기(3) 상단에 설치된 엘리미네이터(7)와 인렛가이드 베인(1a, Inlet Guide Vane)을 통해 압축기(1)로 흡입되어 1단 임펠러와 1단 디퓨져에서 1차로 압축이 된 후 이코노마이져(4)에서 이코노마이저 상단에 설치된 엘리미네이터(8)를 통과한 냉매가스와 혼합하여 과열도가 낮추어진 냉매가 2단 임펠러와 2단 디퓨져를 통과하면서 고온 고압의 과열냉매가스로 압축되어 응축기(2)로 보내진다.The refrigerant gas evaporated after heat exchange with cold water of the low pressure refrigerant liquid in the evaporator 3 is carried out through the eliminator 7 and the inlet guide vane 1a (Inlet Guide Vane) installed on the evaporator 3. Refrigerant is first compressed in the first stage impeller and the first stage diffuser and then mixed with the refrigerant gas passing through the eliminator (8) installed at the top of the economizer in the economizer (4). While passing through the stage impeller and the second stage diffuser, it is compressed into superheated refrigerant gas of high temperature and high pressure and sent to the condenser (2).

여기에서, 상기 응축기(2)로 보내진 과열 냉매가스는 냉각수와의 열교환을 통해 포화냉매가스 상태에서 포화 냉매액 상태로 응축된다. 응축된 냉매액은 제1 교축밸브(5)를 지나 이코노마이저(4)로 들어가는데 제1교축밸브(5)를 지나면서 발생한 냉매가스는 압축기측의 2단 임펠러 쪽으로 가게되고 나머지 냉매액은 제2교축밸브(6)를 지나 다시 증발기(3)로 돌아가 증발하는 과정의 순환을 계속하게 된다. Here, the superheated refrigerant gas sent to the condenser 2 is condensed from the saturated refrigerant gas state to the saturated refrigerant liquid state through heat exchange with the cooling water. The condensed refrigerant liquid enters the economizer (4) after passing through the first throttling valve (5). The refrigerant gas generated after passing through the first throttling valve (5) is directed to the second stage impeller on the compressor side. After the valve 6 is returned to the evaporator 3 to continue the cycle of evaporation.

그러나, 실외온도의 변화, 부하의 변동 등의 영향으로 냉각수 온도가 과도히 낮아지거나, 부분부하 운전이 과하게 진행될 경우 증발기(3)와 응축기(2)의 압력차이가 설계 상태를 벗어나 줄어들게 되고 이코노마이저(4)로 들어가는 냉매의 2상 상태 또한 설계영역을 벗어나게 되는데 이 경우 이코노마이저(4) 상부에 엘리미네이터(8)가 있음에도 불구하고 냉매액이 압축기(1)로 흡입되면서 액압축현상이 발생하게 된다. 아울러 증발기(3)와 응축기(2)의 압력차가 줄어들게 되면서 응축기(2) 증발기로(3) 흐르는 냉매의 양 또한 급격히 줄면서 증발기 저압상태가 발생함으로써, 냉동능력이 저하되거나 운전 불능상태가 될 수 있는 단점을 내포하고 있었다.However, if the coolant temperature is excessively lowered or the partial load operation is excessively affected by the change in the outdoor temperature or the load, the pressure difference between the evaporator 3 and the condenser 2 is reduced from the design state and the economizer ( The two-phase state of the refrigerant entering the 4) also goes out of the design range. In this case, despite the eliminator 8 above the economizer 4, the refrigerant liquid is sucked into the compressor 1 and a liquid compression phenomenon occurs. . In addition, as the pressure difference between the evaporator 3 and the condenser 2 decreases, the amount of refrigerant flowing to the condenser 2 evaporator 3 also decreases rapidly, resulting in a low pressure of the evaporator, which may lower the freezing capacity or render it inoperable. It had some drawbacks.

본 발명은 상기한 바와 같은 문제점을 해결하기 위한 것으로서, 본 발명의 목적은 증발기와 응축기의 차압이 과도하게 줄었을 때, 이코노마이저와 압축기 사이의 액냉매가 압축기로 흡입되는 것을 차단하여, 액압축을 방지하고, 아울러 냉매의 순환량 변화에 따른 증발기 저압상태를 방지할 수 있는 다로형 교축밸브-구비 다단 압축방식 터보냉동기를 제공하는 데 있다.The present invention is to solve the above problems, an object of the present invention is to prevent the liquid refrigerant between the economizer and the compressor to be sucked into the compressor when the pressure difference between the evaporator and the condenser is excessively reduced, thereby reducing the liquid compression The present invention provides a multi-role throttling valve-equipped multi-stage compression type turbocooler capable of preventing and preventing an evaporator low pressure state caused by a change in circulation amount of a refrigerant.

따라서, 본 발명은 상기한 바와 같은 목적을 해결하기 위하여 안출된 것으로서, 다단 압축기, 응축기, 제1 교축밸브, 이코노마이저, 제2교축밸브 및 증발기를 순차적으로 액관 및 가스관으로 되는 배관에 의해 연통가능하게 라인연결되는 주 냉매회로와, 상기 주 냉매회로의 응축기로부터 주 교축밸브로 유동하는 액관 내의 냉매의 일부를 제1 교축밸브 및 이코노마이저를 경유하여 상기 다단 압축기로 토출 시키는 주입로를 구비하는 다단 압축방식 터보냉동기에 있어서, 상기 주입로에는 상기 응축기와 증발기의 차압이 설정 압력 이하로 떨어질 경우, 폐쇄되어 상기 주 냉매회로로만 냉매를 유동토록 하여 액냉매의 압축기로의 유입을 차단하도록 폐쇄 작동되는 제1 전자밸브가 개재되도록 구성된 것을 특징으로 한다.Accordingly, the present invention has been made in order to solve the above object, the multi-stage compressor, the condenser, the first throttling valve, the economizer, the second throttling valve and the evaporator in order to be able to communicate by a pipe consisting of a liquid pipe and a gas pipe sequentially. A multistage compression method including a main refrigerant circuit connected in a line and an injection path for discharging a part of the refrigerant in the liquid pipe flowing from the condenser of the main refrigerant circuit to the main throttling valve via the first throttling valve and the economizer; In the turbo chiller, when the differential pressure between the condenser and the evaporator drops below a set pressure in the injection path, the first operation is closed to shut off the inflow of the liquid refrigerant into the compressor by allowing the refrigerant to flow only into the main refrigerant circuit. It is characterized in that the solenoid valve is configured to be interposed.

또한, 본 발명에 의한 다로형 교축밸브-구비 다단 압축방식 터보냉동기는, 기존의 응축기(2)-이코노마이저(4)-증발기(3)로 이어지는 주 냉매회로(10) 이외에 별도로 응축기(2)와 증발기(3)를 직접 연결하는 직결로(30)를 설비하고 여기에 제3 교축밸브(9)를 설치하여, 응축기(2)와 증발기(3)의 차압에 따라 응동 개폐되는 제2 전자개폐밸브(33)를 설치하는 것을 특징으로 한다. In addition, the multi-rotor throttling valve-equipped multi-stage compression type turbocooler according to the present invention, in addition to the main refrigerant circuit (10) leading to the conventional condenser (2)-economizer (4)-evaporator (3) and condenser (2) and A second solenoid valve is installed to directly connect the evaporator (3) and the third throttle valve (9) is installed therein, which opens and closes in response to the pressure difference between the condenser (2) and the evaporator (3). (33) is provided.

또, 다음으로 본 발명에 의한 터보냉동기의 액압축 방지를 위해, 이코노마이저(4)와 압축기(1) 사이의 주입로(20)에 응축기(2)와 증발기(3)의 차압(P1-P2)에 따라 개폐되는 제1 전자개폐밸브(21)를 설치하는 것을 특징으로 한다.Further, in order to prevent the liquid compression of the turbocooler according to the present invention, the differential pressure (P1-P2) of the condenser 2 and the evaporator 3 in the injection path 20 between the economizer 4 and the compressor 1. It characterized in that the installation of the first electromagnetic opening and closing valve 21 is opened and closed.

상기한 바와 같은 본 발명의 다로형 교축밸브-구비 다단 압축방식 터보냉동기에 의하면, 냉각수의 저온운전이나, 저부하 운전시에 발생할 수 증발기 저압현상과 압축기에서의 액압축 현상을 원천 차단할 수 있도록 구성함으로써 저부하, 저온운전시에도 최적의 냉동사이클을 형성할 수 있는 효과가 있다.According to the multi-route throttling valve-equipped multistage compression type turbocooler of the present invention as described above, the low pressure operation of the coolant or the low load operation can prevent the low pressure operation of the evaporator and the liquid compression phenomenon in the compressor. As a result, an optimal refrigeration cycle can be formed even at low load and low temperature operation.

또, 상기 응축기(2)에서 증발기(3)로 가기 위해 응축기(2)를 빠져나오는 냉매는 포화액 또는 과냉액 상태이다. 이러한 냉매액이 응축기(2)에서 증발기(3)로 가는 사이의 배관에 제3 교축밸브(33)를 설치하고, 제3 교축밸브(33) 입구 냉매상 태가 응축된 포화액 냉매 또는 과냉 냉매액인 경우 목 면적비(제3 교축밸브(33)를 통과하는 유효 유동면적/배관유동면적)만 잘 정해주어 요망하는 압력강하(R134a 냉매용 터보냉동기의 경우 팽창부 압력강하는 약 7Mpa)를 얻을 수 있다.In addition, the refrigerant exiting the condenser 2 from the condenser 2 to the evaporator 3 is in a saturated or supercooled liquid state. Saturated liquid refrigerant or subcooled refrigerant liquid in which the third throttling valve 33 is installed in the pipe between the refrigerant liquid and the condenser 2 from the condenser 2 to the evaporator 3, and the inlet refrigerant state of the third throttle valve 33 is condensed. In this case, only the neck area ratio (effective flow area / pipe flow area passing through the third throttle valve 33) can be well defined to obtain the desired pressure drop (in the case of the R134a refrigerant turbocooler, the pressure drop of the expansion part is about 7 Mpa). have.

이하, 본 발명의 실시예를 첨부한 도면을 참조하면서 상세히 설명한다.Hereinafter, with reference to the accompanying drawings an embodiment of the present invention will be described in detail.

도 2는 본 발명에 따른 2단 압축터보 냉동기의 회로도이다. 2 is a circuit diagram of a two-stage compressed turbo freezer according to the present invention.

도 2에 도시된 바와 같이, 본 발명에 의한 다로형 교축밸브-구비 다단 압축방식 터보냉동기는, 다단 압축기(1), 응축기(2), 제1 교축밸브(5), 이코노마이저(4), 제2교축밸브(6) 및 증발기(3)를 순차적으로 액관 및 가스관으로 되는 배관에 의해 연통가능하게 라인연결되는 주 냉매회로(10)와, 상기 주 냉매회로(10)의 응축기(2)로부터 제1 교축밸브(5)로 유동하는 액관 내의 냉매의 일부를 제1 교축밸브(5) 및 이코노마이저(4)를 경유하여 상기 다단 압축기(1)의 중간압이 되는 지점으로 토출시키는 주입로(20)를 구비하고 있다.As shown in Fig. 2, the multi-rotor throttling valve-equipped multistage compression type turbocooler according to the present invention includes a multistage compressor (1), a condenser (2), a first throttling valve (5), an economizer (4), a first The second refrigerant valve 6 and the evaporator 3 are sequentially connected to the main refrigerant circuit 10 so as to be in communication with each other by a pipe consisting of a liquid pipe and a gas pipe, and from the condenser 2 of the main refrigerant circuit 10. Injection passage 20 for discharging a part of the refrigerant in the liquid pipe flowing through the first throttling valve 5 to the point where it becomes the intermediate pressure of the multistage compressor 1 via the first throttling valve 5 and the economizer 4. Equipped with.

또, 상기 주입로(20)에는 상기 응축기(2)와 증발기(3)의 차압(P1-P2)이 설정 압력 이하로 떨어질 경우, 폐쇄되어 상기 주 냉매회로(10)로만 냉매를 유동토록 하여 액냉매의 압축기(1)로의 유입을 차단하도록 폐쇄 작동되는 제1 전자개폐밸브(21)가 연통 가능하게 개재되어 있다.In addition, when the differential pressure P1-P2 of the condenser 2 and the evaporator 3 drops below a predetermined pressure, the injection path 20 is closed so that the refrigerant flows only to the main refrigerant circuit 10 so that the liquid flows. A first electromagnetic opening / closing valve 21 which is closed to block the inflow of the refrigerant to the compressor 1 is interposed so as to be communicable.

또, 상기 응축기(2)와 증발기(3)의 사이에는, 상기 응축기(3)와 증발기(4)의 차압(P1-P2)이 과도하게 설정 압력 이하로 떨어질 경우, 개방되어 상기 제1 교축밸브(5)와 제2 교축밸브(6)를 경유하지 않고, 상기 주 냉매회로(10) 상의 증발기(4) 로 직결되어 냉매가 유동하도록 하여 증발기 저압현상을 규제하도록 개방 작동되는 제2 전자개폐밸브(31)가 개재되는 직결로(30)가 마련되어 있다.Further, between the condenser 2 and the evaporator 3, when the differential pressure P1-P2 of the condenser 3 and the evaporator 4 drops excessively below the set pressure, the first throttle valve is opened. The second solenoid valve which is directly opened to the evaporator 4 on the main refrigerant circuit 10 and opens to regulate the low pressure phenomenon of the evaporator without passing through the 5 and the second throttle valve 6. Direct connection path 30 through which 31 is provided is provided.

여기에서, 상기 제2 전자개폐밸브(31)는 응축기측 순환 파이프(2a)와 증발기측 순환 파이프(3a)를 설치하고 그 사이에 제3 교축밸브(33)와 조건에 따라 냉매유동라인을 폐쇄할 수 있는 전자제어밸브로 구성된다.Here, the second solenoid valve 31 is provided with a condenser side circulation pipe (2a) and the evaporator side circulation pipe (3a) between the third throttle valve 33 and close the refrigerant flow line according to the conditions It consists of an electronic control valve.

또, 액압축 방지를 위한 구성으로서의 상기 주입로(20) 상에 제1 전자개폐밸브(21)로 연동 가능하게 개재되어 있다.In addition, the first electromagnetic opening and closing valve 21 is interposed so as to be interlockable on the injection passage 20 as a configuration for preventing the liquid compression.

또, 상기 제3 교축밸브(33)는 냉각수 저온 또는 저부하 운전에 맞는 냉매 순환량에 해당하도록 설계하고, 제2 전자개폐밸브(31) 및 제1 전자개폐밸브(11)는 각각 해당 부하조건 또는 냉각수 온도에 따라 작동되도록 기계식 혹은 전자식으로 작동되도록 콘트롤러에 의해 제어되도록 구성되어 있다.In addition, the third throttling valve 33 is designed to correspond to the refrigerant circulation amount suitable for low temperature or low load operation of the coolant, and the second solenoid valve 31 and the first solenoid valve 11 respectively correspond to a corresponding load condition or It is configured to be controlled by the controller to operate mechanically or electronically to operate according to the coolant temperature.

다음에, 이와 같이 구성된 본 발명의 작용 및 효과를 설명한다.Next, the operation and effect of the present invention thus constructed will be described.

먼저, 상기 직결로(30)에서의 냉매 차단 기능을 수행하도록 작동할 조건(냉각수 저온 또는 저부하운전)이되어 상기 제2 전자개폐밸브(31)가 개방되면 기존의 응축기(2)-이코노마이저(4)-증발기(3)로 통과하는 냉매흐름에 부가적으로 작동하는 상기 직결로(30)를 통해 제3 교축밸브(33)를 경유하여 증발기(3)로 흐르게 되는 냉매흐름을 직접적으로 형성하여 증발기 저압현상을 방지하게 된다. First, when the second solenoid valve 31 is opened by a condition (cooling water low temperature or low load operation) to operate to perform the refrigerant blocking function in the direct connection 30, the existing condenser 2-economizer ( 4) directly forming the refrigerant flow flowing to the evaporator 3 via the third throttling valve 33 through the direct passage 30 which operates in addition to the refrigerant flow passing through the evaporator 3. It will prevent the evaporator low pressure phenomenon.

또, 제1 전자개폐밸브(21)가 작동할 조건(냉각수 저온 또는 저부하운전)이 되어 상기 제1 전자개폐밸브(21)가 폐쇄 작동되면, 상기 이코노마이저(4)에서 주입로(30)를 통과하여 제1 전자개폐밸브(11)를 지나 압축기(1)로 흐르게 되는 냉매순 환이 차단되게 되므로 저부하, 냉각수 저온상태에서 발생할 수 있는 액압축현상을 방지하게 되는 것이다.In addition, when the first solenoid valve 21 is operated under a condition (cold water low temperature or low load operation) to operate, the economizer 4 opens the injection passage 30. Since the refrigerant circulation that passes through the first solenoid valve 11 and flows to the compressor 1 is blocked, it is to prevent the liquid compression phenomenon that may occur in the low load, low temperature coolant.

이상에서 살펴본 바와 같이 본 발명은 2단 이상의 압축방식을 적용하는 열교환기 및 이코노마이저(Economizer)에서 전부하 상태에 최적 설계된 고정형 오리피스가 설계온도 이하의 냉각수 온도 상태 또는 부분부하 상태에서 교축효율이 떨어지는 문제를 해결하기 위해, 2로형 순환 교축장치를 적용함으로써 냉동부하에 따라 상응하는 최적의 냉매 순환량을 증발기에 공급함으로써 냉동능력을 향상시킬 수 있다는 매우 뛰어난 효과를 도모할 수 있게 되는 것이다.As described above, the present invention provides a problem that the fixed orifice optimally designed for a full load state in a heat exchanger and an economizer to which two or more compression methods are applied has a drop in throttling efficiency at a coolant temperature below a design temperature or a partial load state. In order to solve the problem, by applying the two-way circulation throttling device it is possible to achieve a very excellent effect that can improve the freezing capacity by supplying the optimum amount of refrigerant circulation according to the refrigeration load to the evaporator.

이상의 설명은 본 발명의 기술 사상을 예시적으로 설명한 것에 불과한 것으로서, 본 발명이 속하는 기술 분야에서 통상의 지식을 가진 자라면 본 발명의 본질적인 특성에서 벗어나지 않는 범위에서 다양한 수정 및 변형이 가능할 것이다. 따라서, 본 발명에 개시된 실시예들은 본 발명의 기술 사상을 한정하기 위한 것이 아니라 설명하기 위한 것이고, 이러한 실시예에 의하여 본 발명의 기술 사상의 범위가 한정되는 것은 아니다. 본 발명의 보호 범위는 아래 청구범위에 의하여 해석되어야 하며, 그와 동등한 범위 내에 있는 모든 기술 사상은 본 발명의 권리범위에 포함되는 것으로 해석되어야 할 것이다.The above description is merely illustrative of the technical idea of the present invention, and those skilled in the art to which the present invention pertains may make various modifications and changes without departing from the essential characteristics of the present invention. Therefore, the embodiments disclosed in the present invention are not intended to limit the technical idea of the present invention but to describe the present invention, and the scope of the technical idea of the present invention is not limited by these embodiments. The scope of protection of the present invention should be interpreted by the following claims, and all technical ideas within the scope equivalent thereto should be construed as being included in the scope of the present invention.

도1은 일반적인 2단 압축 터보 냉동기의 회로 계통도,1 is a circuit schematic diagram of a typical two-stage compressed turbo freezer;

도2는 본 발명에 따른 2단 압축 터보냉동기의 회로 계통도.Figure 2 is a circuit system diagram of a two stage compression turbocooler according to the present invention.

<도면의 주요부분에 대한 부호의 설명><Description of the symbols for the main parts of the drawings>

1 : 압축기 2 : 응축기  1: compressor 2: condenser

3 : 증발기 4 : 이코노마이저  3: evaporator 4: economizer

5 : 제1 교축밸브 6 : 제2 교축밸브  5: first throttling valve 6: second throttling valve

7 : 증발기측 엘리미네이터 8 : 이코노마이저측 엘리미네이터  7: Evaporator side eliminator 8: Economizer side eliminator

10 : 주 냉매회로 20 : 주입로 10: main refrigerant circuit 20: injection furnace

21 : 제1 전자개폐밸브 30 : 직결로 21: first solenoid valve 30: direct connection

31 : 제2 전자개폐밸브 33 : 제3 교축밸브 31: second solenoid valve 33: third throttle valve

Claims (2)

다단 압축기, 응축기, 제1 교축밸브, 이코노마이저, 제2 교축밸브 및 증발기를 순차적으로 액관 및 가스관으로 되는 배관에 의해 연통가능하게 라인연결되는 주 냉매회로와, 상기 주 냉매회로의 응축기로부터 주 교축밸브로 유동하는 액관 내의 냉매의 일부를 제1 교축밸브 및 이코노마이저를 경유하여 상기 다단 압축기로 토출시키는 주입로를 구비하는 다단 압축방식 터보냉동기에 있어서,A main refrigerant circuit which is connected in series with a multistage compressor, a condenser, a first throttling valve, an economizer, a second throttling valve, and an evaporator in series by a pipe consisting of a liquid pipe and a gas pipe, and a main throttle valve from the condenser of the main refrigerant circuit. In the multi-stage compression type turbocooler having an injection path for discharging a portion of the refrigerant in the liquid pipe flowing to the multi-stage compressor via the first throttling valve and the economizer, 상기 주입로에는 상기 응축기와 증발기의 차압이 설정 압력 이하로 떨어질 경우, 패쇄되어 상기 주 냉매회로로만 냉매를 유동토록 하여 액냉매의 압축기로의 유입을 차단하도록 폐쇄 작동되는 제1 전자밸브가 개재된 것을 특징으로 하는 다단 압축방식 터보냉동기.When the differential pressure of the condenser and the evaporator drops below the set pressure, the injection path is interposed with a first solenoid valve which is closed so that the refrigerant flows only into the main refrigerant circuit to block the inflow of the liquid refrigerant into the compressor. Multi-stage compression type turbo chiller, characterized in that. 제 1 항에 있어서,The method of claim 1, 상기 응축기와 증발기의 사이에는, 상기 응축기와 증발기의 차압이 과도하게 설정 압력 이하로 떨어질 경우, 개방되어 상기 제1 교축밸브와 제2 교축밸브를 경유하지 않고, 상기 주 냉매회로로 직결되어 냉매가 유동하도록 하여 증발기 저압현상을 규제하도록 개방 작동되는 제2 전자개폐밸브가 개재되는 직결로가 마련된 것을 특징으로 하는 다단 압축방식 터보냉동기.Between the condenser and the evaporator, when the differential pressure between the condenser and the evaporator drops excessively below a set pressure, the condenser and the evaporator are opened and connected directly to the main refrigerant circuit without passing through the first and second throttling valves, thereby allowing the refrigerant to flow. A multistage compression type turbo freezer, characterized in that a direct connection is provided through which a second electromagnetic opening and closing valve is opened to regulate the evaporator low pressure phenomenon.
KR1020070137441A 2007-12-26 2007-12-26 Multi-roach type throttling valve-equipment multistage compression type compressor Ceased KR20090069694A (en)

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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101155701B1 (en) * 2010-02-25 2012-06-12 엘지전자 주식회사 Economizer with fluid velocity reduction apparatus and multi-stage compressing refrigeration apparatus having the same
KR20150072168A (en) * 2013-12-19 2015-06-29 엘지전자 주식회사 Variable expansion device, economizer and turbo chiller comprising the same
CN109099607A (en) * 2017-06-21 2018-12-28 浙江盾安人工环境股份有限公司 Centrifugal refrigerating machines and its control method
CN111076439A (en) * 2019-12-11 2020-04-28 珠海格力电器股份有限公司 Air supply structure, centrifugal chiller and air conditioner
CN116037625A (en) * 2022-12-26 2023-05-02 江苏辛普森新能源有限公司 Heat pump type kitchen waste treatment equipment

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101155701B1 (en) * 2010-02-25 2012-06-12 엘지전자 주식회사 Economizer with fluid velocity reduction apparatus and multi-stage compressing refrigeration apparatus having the same
KR20150072168A (en) * 2013-12-19 2015-06-29 엘지전자 주식회사 Variable expansion device, economizer and turbo chiller comprising the same
CN109099607A (en) * 2017-06-21 2018-12-28 浙江盾安人工环境股份有限公司 Centrifugal refrigerating machines and its control method
CN111076439A (en) * 2019-12-11 2020-04-28 珠海格力电器股份有限公司 Air supply structure, centrifugal chiller and air conditioner
CN116037625A (en) * 2022-12-26 2023-05-02 江苏辛普森新能源有限公司 Heat pump type kitchen waste treatment equipment

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