技术领域technical field
本发明涉及一种用于供热水器、热水供暖器或者空调器等的制冷循环装置。The invention relates to a refrigeration cycle device used for water heaters, hot water heaters or air conditioners.
背景技术Background technique
以往以来，已知有具备了压缩机、四通阀、室内换热器、室内侧节流装置、气液分离器、室外侧节流装置、室外换热器且能够对制冷和供暖进行切换的制冷循环装置。例如在专利文献1中公开了图9所示那样的制冷循环装置500。Conventionally, there are known air conditioners that are equipped with a compressor, a four-way valve, an indoor heat exchanger, an indoor throttle, an accumulator, an outdoor throttle, and an outdoor heat exchanger, and can switch between cooling and heating. Refrigeration cycle device. For example, Patent Document 1 discloses a refrigeration cycle device 500 as shown in FIG. 9 .
在该制冷循环装置500中，压缩机501经由四通阀532而与室内换热器512及室外换热器520连接，室内换热器512和室外换热器520经由室内侧节流装置514、气液分离器516及室外侧节流装置518而连接。另外，在气液分离器516与压缩机510之间设有将由气液分离器516分离后的中间压的气体制冷剂向压缩机510供给的喷射路径522。进而，为了将中间压控制为成为目标值，在制冷循环装置500中设有对制冷剂的冷凝温度及蒸发温度进行检测的换热温度传感器544、546和对气液分离器516内的制冷剂的温度即中间压温度进行检测的中间压温度传感器526。In this refrigeration cycle device 500, the compressor 501 is connected to the indoor heat exchanger 512 and the outdoor heat exchanger 520 through the four-way valve 532, and the indoor heat exchanger 512 and the outdoor heat exchanger 520 are connected through the indoor side throttle device 514, The gas-liquid separator 516 and the outdoor side throttling device 518 are connected. In addition, an injection path 522 for supplying intermediate-pressure gas refrigerant separated by the gas-liquid separator 516 to the compressor 510 is provided between the gas-liquid separator 516 and the compressor 510 . Furthermore, in order to control the intermediate pressure to a target value, the refrigeration cycle device 500 is provided with heat exchange temperature sensors 544 and 546 for detecting the condensation temperature and evaporation temperature of the refrigerant, and for monitoring the temperature of the refrigerant in the gas-liquid separator 516. The intermediate pressure temperature sensor 526 detects the temperature of the intermediate pressure.
关于如上所述构成的制冷循环装置500，以下对其动作进行说明。在进行供暖之际，从压缩机510喷出的制冷剂在通过四通阀532之后，在室内换热器512中进行换热，并通过室内侧节流装置514从高压减压为中间压。中间压的制冷剂在气液分离器516中被分离为气体制冷剂和液体制冷剂，中间压的气体制冷剂通过喷射路径522而向压缩机510供给。另一方面，中间压的液体制冷剂通过室外侧节流装置518而进一步地减压，减压后的低压的制冷剂在室外换热器520中进行换热，在通过了四通阀532之后，被吸入到压缩机510中。在进行制冷之际，从压缩机510喷出的制冷剂在通过四通阀532之后，在室外换热器520中进行换热，并通过室外侧节流装置518从高压减压为中间压。中间压的制冷剂在气液分离器516中被分离为气体制冷剂和液体制冷剂，中间压的气体制冷剂通过喷射路径522而向压缩机510供给。另一方面，中间压的液体制冷剂通过室内侧节流装置514而进一步地减压，减压后的低压的制冷剂在室内换热器512中进行换热，在通过了四通阀532之后，被吸入到压缩机510中。The operation of the refrigeration cycle apparatus 500 configured as described above will be described below. During heating, the refrigerant discharged from the compressor 510 passes through the four-way valve 532 , exchanges heat in the indoor heat exchanger 512 , and is decompressed from high pressure to intermediate pressure by the indoor expansion device 514 . The intermediate-pressure refrigerant is separated into gas refrigerant and liquid refrigerant in the gas-liquid separator 516 , and the intermediate-pressure gas refrigerant is supplied to the compressor 510 through the injection path 522 . On the other hand, the intermediate-pressure liquid refrigerant is further decompressed by the outdoor throttling device 518 , and the decompressed low-pressure refrigerant exchanges heat in the outdoor heat exchanger 520 , and after passing through the four-way valve 532 , is sucked into the compressor 510. During cooling, the refrigerant discharged from the compressor 510 passes through the four-way valve 532 , exchanges heat in the outdoor heat exchanger 520 , and is decompressed from high pressure to intermediate pressure by the outdoor throttle device 518 . The intermediate-pressure refrigerant is separated into gas refrigerant and liquid refrigerant in the gas-liquid separator 516 , and the intermediate-pressure gas refrigerant is supplied to the compressor 510 through the injection path 522 . On the other hand, the intermediate-pressure liquid refrigerant is further decompressed by the indoor throttling device 514 , and the decompressed low-pressure refrigerant exchanges heat in the indoor heat exchanger 512 , and after passing through the four-way valve 532 , is sucked into the compressor 510.
另外，在制冷循环装置500中，控制装置530根据由换热温度传感器544、546检测出的冷凝温度及蒸发温度来确定目标的中间压温度，并以使由中间压温度传感器526检测到的中间压温度成为目标的中间压温度的方式对位于气液分离器516的下游侧的节流装置(供暖时为室外侧节流装置516，而制冷时为室内侧节流装置514)的开度进行调整。In addition, in the refrigeration cycle device 500 , the control device 530 determines the target intermediate pressure temperature based on the condensation temperature and the evaporation temperature detected by the heat exchange temperature sensors 544 and 546 , and makes the intermediate pressure temperature detected by the intermediate pressure temperature sensor 526 The opening degree of the throttle device located on the downstream side of the gas-liquid separator 516 (the outdoor throttle device 516 for heating and the indoor throttle device 514 for cooling) is adjusted so that the pressure temperature becomes the target intermediate pressure temperature. Adjustment.
【先行技术文献】【Prior technical literature】
【专利文献】【Patent Literature】
【专利文献1】：日本专利第3317170号说明书[Patent Document 1]: Specification of Japanese Patent No. 3317170
【发明概要】【Invention Outline】
【发明所要解决的课题】【Problems to be solved by the invention】
但是，图9所示的制冷循环装置500存有进一步的效率改善的余地。However, there is room for further efficiency improvement in the refrigeration cycle device 500 shown in FIG. 9 .
发明内容Contents of the invention
本公开就是鉴于这样的状况而作出的，其目的在于，使制冷循环装置的效率提高。This disclosure was made in view of such a situation, and an object thereof is to improve the efficiency of the refrigeration cycle apparatus.
【用于解决课题的机构】【Institutions for problem solving】
本公开提供一种制冷循环装置，具备：制冷剂回路，其使制冷剂以依次通过压缩机、冷凝器、上游侧节流装置、气液分离器、下游侧节流装置及蒸发器的方式进行循环；喷射路径，其将由所述气液分离器分离后的气体制冷剂向所述压缩机供给；加热器，其设于所述喷射路径；中间压温度传感器，其对从所述制冷剂回路向所述喷射路径流入的制冷剂的温度即气液分离温度进行检测；过热度温度传感器，其对在所述喷射路径中由所述加热器加热后的制冷剂的温度即喷射温度进行检测；控制装置，其进行中间压控制运转，在该中间压控制运转中，在以使所述气液分离温度与所述喷射温度之间的温度差变得比规定值小的方式对所述上游侧节流装置和所述下游侧节流装置中的至少一方的开度进行调整之后，增大所述下游侧节流装置的开度，直至所述气液分离温度从此时的温度减小了规定温度。The present disclosure provides a refrigeration cycle device, which includes: a refrigerant circuit, which makes the refrigerant pass through a compressor, a condenser, an upstream throttling device, a gas-liquid separator, a downstream throttling device, and an evaporator. cycle; an injection path that supplies the gas refrigerant separated by the gas-liquid separator to the compressor; a heater that is provided in the injection path; an intermediate pressure temperature sensor that responds to the detecting the temperature of the refrigerant flowing into the injection path, that is, the gas-liquid separation temperature; and a superheat temperature sensor that detects the temperature of the refrigerant heated by the heater in the injection path, that is, the injection temperature; A control device that performs an intermediate pressure control operation in which the upstream side After adjusting the opening degree of at least one of the throttling device and the downstream side throttling device, increasing the opening degree of the downstream side throttling device until the gas-liquid separation temperature decreases by a predetermined value from the current temperature. temperature.
【发明效果】【Invention effect】
根据上述的结构，通过采用加热器及过热度温度传感器来确定气液分离温度的基准温度，并将比该基准温度低规定温度的温度设为气液分离温度的目标温度，由此能够消除中间压温度传感器的测定误差。由此，能够将中间压更高精度地控制为目的值，从而使制冷循环装置的效率提高。According to the above-mentioned structure, by using the heater and the superheat temperature sensor to determine the reference temperature of the gas-liquid separation temperature, and setting a temperature lower than the reference temperature by a predetermined temperature as the target temperature of the gas-liquid separation temperature, the intermediate temperature can be eliminated. The measurement error of the pressure and temperature sensor. As a result, the intermediate pressure can be controlled to a target value with higher precision, and the efficiency of the refrigeration cycle apparatus can be improved.
附图说明Description of drawings
图1是本发明的第一实施方式所涉及的制冷循环装置的结构图。FIG. 1 is a configuration diagram of a refrigeration cycle apparatus according to a first embodiment of the present invention.
图2是表示第一实施方式中的中间压控制运转的控制方法的流程图。FIG. 2 is a flowchart showing a control method of the intermediate pressure control operation in the first embodiment.
图3是表示第一实施方式中的上游侧节流装置及下游侧节流装置的开度的变化、以及喷出温度、喷射温度及气液分离温度的变化的曲线图。3 is a graph showing changes in the opening degrees of the upstream side throttling device and the downstream side throttling device, and changes in the discharge temperature, injection temperature, and gas-liquid separation temperature in the first embodiment.
图4是表示一变形例所涉及的加热器的图。FIG. 4 is a diagram showing a heater according to a modified example.
图5是另一变形例所涉及的制冷循环装置的结构图。Fig. 5 is a configuration diagram of a refrigeration cycle device according to another modified example.
图6是再一变形例所涉及的制冷循环装置的结构图。Fig. 6 is a configuration diagram of a refrigeration cycle device according to yet another modification.
图7是本发明的第二实施方式所涉及的制冷循环装置的结构图。Fig. 7 is a configuration diagram of a refrigeration cycle device according to a second embodiment of the present invention.
图8是表示第二实施方式中的中间压控制运转的控制方法的流程图。8 is a flowchart showing a control method of the intermediate pressure control operation in the second embodiment.
图9是现有的制冷循环装置的结构图。Fig. 9 is a structural diagram of a conventional refrigeration cycle device.
具体实施方式detailed description
在图9所示的制冷循环装置500中，根据由三个温度传感器544、546、526检测的温度对从气液分离器516通过喷射路径522而向压缩机510供给的制冷剂的中间压进行控制，故温度传感器所具有的精度的偏差成为问题。在通常使用的温度传感器中，至少存在±1.5℃的测定误差。在如图9所示的制冷循环装置500那样使用多个温度传感器来进行控制的情况下，与温度传感器的个数相应地，测定误差也累积(若每一个为±1.5℃，则使用三个时为±4.5℃)。因此，实际控制的中间压从目标值背离，往往会导致制冷循环装置的效率降低。In the refrigeration cycle apparatus 500 shown in FIG. Control, so the deviation of the accuracy of the temperature sensor becomes a problem. In commonly used temperature sensors, there is at least a measurement error of ±1.5°C. In the case of using a plurality of temperature sensors for control as in the refrigeration cycle apparatus 500 shown in FIG. at ±4.5°C). Therefore, when the actually controlled intermediate pressure deviates from the target value, the efficiency of the refrigeration cycle device often decreases.
本公开的第一方式提供一种制冷循环装置，其中，具备：制冷剂回路，其使制冷剂以依次通过压缩机、冷凝器、上游侧节流装置、气液分离器、下游侧节流装置及蒸发器的方式进行循环；喷射路径，其将由所述气液分离器分离后的气体制冷剂向所述压缩机供给；加热器，其设于所述喷射路径；中间压温度传感器，其对从所述制冷剂回路向所述喷射路径流入的制冷剂的温度即气液分离温度进行检测；过热度温度传感器，其对在所述喷射路径中由所述加热器加热后的制冷剂的温度即喷射温度进行检测；控制装置，其进行中间压控制运转，在该中间压控制运转中，在以使所述气液分离温度与所述喷射温度之间的温度差变得比规定值小的方式对所述上游侧节流装置和所述下游侧节流装置中的至少一方的开度进行调整之后，增大所述下游侧节流装置的开度，直至所述气液分离温度从此时的温度减小了规定温度。A first aspect of the present disclosure provides a refrigeration cycle device including: a refrigerant circuit that allows the refrigerant to pass through a compressor, a condenser, an upstream-side throttling device, a gas-liquid separator, and a downstream-side throttling device in sequence. and the evaporator; the injection path, which supplies the gas refrigerant separated by the gas-liquid separator to the compressor; the heater, which is installed in the injection path; the intermediate pressure temperature sensor, which controls the detecting the gas-liquid separation temperature of the refrigerant flowing from the refrigerant circuit into the injection path; and a superheat temperature sensor for detecting the temperature of the refrigerant heated by the heater in the injection path That is, the injection temperature is detected; the control device performs an intermediate pressure control operation in which the temperature difference between the gas-liquid separation temperature and the injection temperature becomes smaller than a predetermined value After adjusting the opening degree of at least one of the upstream side throttling device and the downstream side throttling device, increase the opening degree of the downstream side throttling device until the gas-liquid separation temperature has changed from this point to The temperature is reduced by the specified temperature.
本公开的第二方式在第一方式的基础上，提供一种制冷循环装置，其中，还具备冷凝后温度传感器，该冷凝后温度传感器对从所述冷凝器流出的制冷剂的温度即冷凝侧出口温度进行检测，所述控制装置在所述中间压控制运转中，使用所述气液分离温度与所述喷射温度之间的温度差变得比规定值小时的所述气液分离温度及所述冷凝侧出口温度，对在稳定运转中使用的气液分离温度的计算式进行修正。A second aspect of the present disclosure provides a refrigeration cycle device based on the first aspect, further comprising a post-condensation temperature sensor that measures the temperature of the refrigerant flowing out of the condenser, that is, the temperature on the condensation side. The outlet temperature is detected, and the control device uses the gas-liquid separation temperature at which the temperature difference between the gas-liquid separation temperature and the injection temperature becomes smaller than a predetermined value and the Correct the calculation formula for the gas-liquid separation temperature used in stable operation based on the outlet temperature on the condensation side.
根据第二方式，在中间压控制运转中，能够使用气液分离温度与所述喷射温度之间的温度差变得比规定值小时的气液分离温度及冷凝侧出口温度，从而对在稳定运转中使用的气液分离温度的计算式进行修正。According to the second aspect, in the intermediate pressure control operation, it is possible to use the gas-liquid separation temperature and the outlet temperature on the condensation side at which the temperature difference between the gas-liquid separation temperature and the injection temperature becomes smaller than a predetermined value, so that it can be used in stable operation. Correct the calculation formula of gas-liquid separation temperature used in
本公开的第三方式在第二方式的基础上，提供一种制冷循环装置，其中，还具备蒸发前温度传感器，该蒸发前温度传感器对向所述蒸发器流入的制冷剂的温度即蒸发侧入口温度进行检测，所述控制装置在对稳定运转中使用的气液分离温度的计算式进行修正时，也使用所述气液分离温度与所述喷射温度之间的温度差变得比规定值小时的所述蒸发侧入口温度。A third aspect of the present disclosure provides a refrigeration cycle device based on the second aspect, further comprising a pre-evaporation temperature sensor that detects the temperature of the refrigerant flowing into the evaporator, that is, the evaporation side. The inlet temperature is detected, and when the control device corrects the calculation formula of the gas-liquid separation temperature used in steady operation, it also uses The evaporating side inlet temperature of hours.
根据第三方式，在中间压控制运转中，能够使用气液分离温度与所述喷射温度之间的温度差变得比规定值小时的气液分离温度、冷凝侧出口温度及蒸发侧入口温度，从而对在稳定运转中使用的气液分离温度的计算式进行修正。According to the third aspect, in the intermediate pressure control operation, the gas-liquid separation temperature, the condensation-side outlet temperature, and the evaporation-side inlet temperature at which the temperature difference between the gas-liquid separation temperature and the injection temperature becomes smaller than a predetermined value can be used, Accordingly, the calculation formula of the gas-liquid separation temperature used in the steady operation is corrected.
本公开的第四方式在第二方式或者第三方式的基础上，提供一种制冷循环装置，其中，所述控制装置使用在所述中间压控制运转中修正后的气液分离温度的计算式来进行稳定运转。A fourth aspect of the present disclosure provides the refrigeration cycle apparatus based on the second aspect or the third aspect, wherein the control device uses a calculation formula of the corrected gas-liquid separation temperature in the intermediate pressure control operation for stable operation.
根据第四方式，在稳定运转中能够进行还考虑了温度传感器的测定误差等的更高精度的中间压控制。According to the fourth aspect, it is possible to perform higher-accuracy intermediate pressure control that also takes into account the measurement error of the temperature sensor and the like during steady operation.
本公开的第五方式在第一～第四方式中的任一方式的基础上，提供一种制冷循环装置，其中，所述控制装置在起动运转时进行所述中间压控制运转。A fifth aspect of the present disclosure provides the refrigeration cycle apparatus in any one of the first to fourth aspects, wherein the control device performs the intermediate pressure control operation during start-up operation.
根据第五方式，制冷循环装置能够以最佳的状态从起动运转向稳定运转转移。According to the fifth aspect, the refrigeration cycle apparatus can shift from start-up operation to steady operation in an optimal state.
本公开的第六方式在第一～第五方式中的任一方式的基础上，提供一种制冷循环装置，其中，所述控制装置在稳定运转的中途进行所述中间压控制运转。A sixth aspect of the present disclosure provides the refrigeration cycle apparatus in any one of the first to fifth aspects, wherein the control device performs the intermediate pressure control operation during a steady operation.
根据第六方式，在稳定运转的中途也进行中间压控制运转，更高精度地将中间压控制为目的值。According to the sixth aspect, the intermediate pressure control operation is performed even in the middle of the steady operation, and the intermediate pressure is controlled to the target value with higher accuracy.
本公开的第七方式在第五方式的基础上，提供一种制冷循环装置，其中，还具备喷出温度传感器，该喷出温度传感器对从所述压缩机喷出的制冷剂的温度即喷出温度进行检测，所述控制装置以使所述喷出温度保持在目标的喷出温度附近的方式对所述上游侧节流装置的开度进行调整，并同时减小所述下游侧节流装置的开度，直至所述气液分离温度与所述喷射温度之间的温度差变得比规定值小，然后增大所述下游侧节流装置的开度。A seventh aspect of the present disclosure provides a refrigeration cycle device based on the fifth aspect, further comprising a discharge temperature sensor that measures the temperature of the refrigerant discharged from the compressor, that is, the discharge temperature sensor. The discharge temperature is detected, and the control device adjusts the opening degree of the upstream throttle device in such a manner that the discharge temperature is kept near the target discharge temperature, and at the same time reduces the downstream throttle. The opening degree of the device is increased until the temperature difference between the gas-liquid separation temperature and the injection temperature becomes smaller than a predetermined value, and then the opening degree of the downstream side throttling device is increased.
根据第七方式，通过利用上游侧节流装置对喷出温度进行控制，并利用下游侧节流装置对气液分离温度进行控制，由此能够实现简易的控制。According to the seventh aspect, simple control can be realized by controlling the discharge temperature with the upstream throttle device and controlling the gas-liquid separation temperature with the downstream throttle device.
本公开的第八方式在第一～第七方式中的任一方式的基础上，提供一种制冷循环装置，其中，所述制冷剂回路包括作为所述冷凝器及所述蒸发器发挥功能的室内换热器及室外换热器，并且包括作为所述上游侧节流装置及所述下游侧节流装置发挥功能的室内侧节流装置及室外侧节流装置，在所述制冷剂回路中设有对制冷剂的流动方向进行切换的四通阀。An eighth aspect of the present disclosure provides a refrigeration cycle device based on any one of the first to seventh aspects, wherein the refrigerant circuit includes a condenser that functions as the condenser and the evaporator An indoor heat exchanger and an outdoor heat exchanger, further including an indoor side throttling device and an outdoor side throttling device functioning as the upstream side throttling device and the downstream side throttling device, in the refrigerant circuit A four-way valve for switching the flow direction of the refrigerant is provided.
根据第八方式，实现了能够进行制冷和供暖的切换的制冷循环装置。According to the eighth aspect, a refrigeration cycle device capable of switching between cooling and heating is realized.
本公开的第九方式在第一～第八方式中的任一方式的基础上，提供一种制冷循环装置，其中，所述加热器为电热器。A ninth aspect of the present disclosure provides the refrigeration cycle device in any one of the first to eighth aspects, wherein the heater is an electric heater.
根据第九方式，电热器容易进行接通-切断控制，因此，能够仅仅在需要对在喷射路径中流动的制冷剂进行加热的情况下对在喷射路径中流动的制冷剂进行加热。According to the ninth aspect, the on-off control of the electric heater is easy, and therefore, the refrigerant flowing in the injection path can be heated only when it is necessary to heat the refrigerant flowing in the injection path.
本公开的第十方式在第一～第八方式中的任一方式的基础上，提供一种制冷循环装置，其中，所述加热器为对从所述压缩机排出的热量进行蓄积，且利用该蓄积的热量对制冷剂进行加热的蓄热单元。A tenth aspect of the present disclosure provides a refrigeration cycle device based on any one of the first to eighth aspects, wherein the heater stores heat discharged from the compressor and utilizes The stored heat heats the heat storage unit that heats the refrigerant.
根据第十方式，利用压缩机的废热而对在喷射路径中流动的制冷剂进行加热。According to the tenth aspect, the refrigerant flowing through the injection path is heated by waste heat of the compressor.
本公开的第十一方式在第一～第八方式中的任一方式的基础上，提供一种制冷循环装置，其中，所述加热器为包括第一换热部和第二换热部的换热器，在所述喷射路径中流动的制冷剂导入所述第一换热部，在所述制冷剂回路中流动且与所述气液分离温度相比为高温的制冷剂导入所述第二换热部，在所述换热器中，所述第二换热部对所述第一换热部进行加热。An eleventh aspect of the present disclosure provides a refrigeration cycle device based on any one of the first to eighth aspects, wherein the heater includes a first heat exchange unit and a second heat exchange unit. In a heat exchanger, the refrigerant flowing through the injection path is introduced into the first heat exchange part, and the refrigerant flowing through the refrigerant circuit and having a higher temperature than the gas-liquid separation temperature is introduced into the second heat exchanger. Two heat exchange parts, in the heat exchanger, the second heat exchange part heats the first heat exchange part.
根据第十一方式，利用在制冷剂回路中流动的制冷剂所具有的热量，来对在喷射路径中流动的制冷剂进行加热。According to the eleventh aspect, the refrigerant flowing through the injection path is heated by the heat of the refrigerant flowing through the refrigerant circuit.
本公开的第十二方式在第十一方式的基础上，提供一种制冷循环装置，其中，向所述第二换热部引导在所述压缩机与所述冷凝器之间流动的制冷剂。A twelfth aspect of the present disclosure provides the refrigeration cycle device based on the eleventh aspect, wherein the refrigerant flowing between the compressor and the condenser is guided to the second heat exchange unit. .
根据第十二方式，利用在制冷剂回路中流动的为比较高温的制冷剂所具有的热量，来对在喷射路径中流动的制冷剂进行加热。According to the twelfth aspect, the heat of the relatively high-temperature refrigerant flowing in the refrigerant circuit is used to heat the refrigerant flowing through the injection path.
本公开的第十三方式在第十一方式的基础上，提供一种制冷循环装置，其中，向所述第二换热部引导在所述冷凝器与所述上游侧节流装置之间流动的制冷剂。A thirteenth aspect of the present disclosure provides the refrigeration cycle device based on the eleventh aspect, wherein the flow between the condenser and the upstream expansion device is guided to the second heat exchange unit. of refrigerant.
根据第十三方式，利用在制冷剂回路中流动的制冷剂所具有的热量，来对在喷射路径22中流动的制冷剂进行加热。另外，制冷剂回路的冷凝器出口侧的制冷剂的过冷却度升高，故制冷循环装置的能力得以提高。According to the thirteenth aspect, the refrigerant flowing through the injection path 22 is heated by the heat of the refrigerant flowing through the refrigerant circuit. In addition, since the degree of subcooling of the refrigerant on the outlet side of the condenser of the refrigerant circuit increases, the performance of the refrigeration cycle device can be improved.
以下，关于本发明的实施方式，边参考附图边进行详细的说明。需要说明的是，以下的说明是关于本发明的一例的说明，本发明并非通过这些内容而被限定。Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. In addition, the following description is description about an example of this invention, and this invention is not limited by these content.
(第一实施方式)(first embodiment)
图1表示本公开的第一实施方式所涉及的制冷循环装置100。该制冷循环装置100具备使制冷剂循环的制冷剂回路1和控制装置30。FIG. 1 shows a refrigeration cycle apparatus 100 according to a first embodiment of the present disclosure. This refrigeration cycle device 100 includes a refrigerant circuit 1 for circulating a refrigerant, and a control device 30 .
制冷剂回路1包括压缩机10、四通阀32、室内换热器12、室内侧节流装置14、气液分离器16、室外侧节流装置18及室外换热器20。四通阀32的四个口通过制冷剂配管而与压缩机10的吸入口及喷出口以及室内换热器12及室外换热器20连接。另外，室内换热器12、室内侧节流装置14、气液分离器16、室外侧节流装置18及室外换热器20通过制冷剂配管而串联连接。The refrigerant circuit 1 includes a compressor 10 , a four-way valve 32 , an indoor heat exchanger 12 , an indoor throttling device 14 , a gas-liquid separator 16 , an outdoor throttling device 18 and an outdoor heat exchanger 20 . The four ports of the four-way valve 32 are connected to the suction port and the discharge port of the compressor 10 and the indoor heat exchanger 12 and the outdoor heat exchanger 20 through refrigerant piping. In addition, the indoor heat exchanger 12 , the indoor side expansion device 14 , the gas-liquid separator 16 , the outdoor side expansion device 18 , and the outdoor heat exchanger 20 are connected in series through refrigerant piping.
四通阀32将制冷剂的流动方向在供暖时切换为由实线箭头所示的第一方向，在制冷时切换为由虚线箭头所示的第二方向。在第一方向上，压缩机10的喷出口与室内换热器12连接，压缩机10的吸入口与室外换热器20连接。在第二方向上，压缩机10的喷出口与室外换热器20连接，压缩机10的吸入口与室外换热器12连接。即，在制冷剂回路1中循环的制冷剂在供暖时依次通过压缩机10、室内换热器12、室内侧节流装置14、气液分离器16、室外侧节流装置18及室外换热器20，在制冷时依次通过压缩机10、室外换热器20、室外侧节流装置18、气液分离器16、室内侧节流装置14及室内换热器12。The four-way valve 32 switches the flow direction of the refrigerant to a first direction indicated by solid arrows during heating, and to a second direction indicated by dotted arrows during cooling. In the first direction, the discharge port of the compressor 10 is connected to the indoor heat exchanger 12 , and the suction port of the compressor 10 is connected to the outdoor heat exchanger 20 . In the second direction, the discharge port of the compressor 10 is connected to the outdoor heat exchanger 20 , and the suction port of the compressor 10 is connected to the outdoor heat exchanger 12 . That is, the refrigerant circulating in the refrigerant circuit 1 sequentially passes through the compressor 10, the indoor heat exchanger 12, the indoor side throttling device 14, the gas-liquid separator 16, the outdoor side throttling device 18 and the outdoor heat exchanger during heating. The device 20 passes through the compressor 10, the outdoor heat exchanger 20, the outdoor side throttling device 18, the gas-liquid separator 16, the indoor side throttling device 14 and the indoor heat exchanger 12 in sequence during cooling.
室内换热器12在供暖时作为冷凝器发挥功能，在制冷时作为蒸发器发挥功能。另一方面，室外换热器20在供暖时作为蒸发器发挥功能，在供暖时作为冷凝器发挥功能。The indoor heat exchanger 12 functions as a condenser during heating and as an evaporator during cooling. On the other hand, the outdoor heat exchanger 20 functions as an evaporator during heating, and functions as a condenser during heating.
作为室内侧节流装置14及室外侧节流装置18，例如采用能够调整开度的电动膨胀阀。控制装置30向室内侧节流装置14及室外侧节流装置18输送控制信号，并对它们的开度进行调整。As the indoor side throttle device 14 and the outdoor side throttle device 18 , for example, an electric expansion valve whose opening can be adjusted is used. The control device 30 sends control signals to the indoor side throttle device 14 and the outdoor side throttle device 18 to adjust their opening degrees.
另外，在气液分离器16与压缩机10之间设有将由气液分离器16分离的中间压的气体制冷剂向压缩机10供给的喷射路径22。喷射路径22例如由一端与气液分离器16的气体层侧连结，且另一端与在压缩过程中向压缩机10的压缩室开口的中间压吸入口连结的制冷剂配管构成。在喷射路径22的中途设有加热器24，在喷射路径22中流动的中间压气体制冷剂被加热之后向压缩机10喷射。In addition, an injection path 22 for supplying the intermediate-pressure gas refrigerant separated by the gas-liquid separator 16 to the compressor 10 is provided between the gas-liquid separator 16 and the compressor 10 . The injection path 22 is constituted by, for example, a refrigerant pipe having one end connected to the gas layer side of the gas-liquid separator 16 and the other end connected to an intermediate pressure suction port opening to the compression chamber of the compressor 10 during compression. A heater 24 is provided in the middle of the injection path 22 , and the intermediate-pressure gas refrigerant flowing through the injection path 22 is heated and injected toward the compressor 10 .
作为加热器24，例如可以采用加热装置(heater)、即电热器。作为电热器，可举出电阻加热器、感应加热器等。加热器24并非必须始终对在喷射路径22中流动的制冷剂进行加热，例如也可以通过电热器的接通-切断控制，仅仅在后述的中间压控制运转之际对在喷射路径22中流动的制冷剂进行加热。As the heater 24, for example, a heater, that is, an electric heater can be used. As an electric heater, a resistance heater, an induction heater, etc. are mentioned. The heater 24 does not always have to heat the refrigerant flowing in the injection path 22. For example, the refrigerant flowing in the injection path 22 may be heated only during the intermediate pressure control operation described later by the on-off control of the electric heater. refrigerant for heating.
进而，在制冷循环装置100中设有：对从压缩机10喷出的制冷剂的温度即喷出温度Td进行检测的喷出温度传感器34；对室外温度To进行检测的室外温度传感器36；对室内温度Ti进行检测的室内温度传感器38；对从制冷剂回路1向喷射路径22流入的制冷剂的温度即气液分离温度Tm进行检测的中间压温度传感器26；对在喷射路径22中由加热器24加热后的制冷剂的温度即喷射温度Tinj进行检测的过热度温度传感器28。控制装置30主要根据由各种温度传感器检测的温度，对室内侧节流装置14及室外侧节流装置18的开度以及压缩机10的转速进行控制。Further, the refrigeration cycle apparatus 100 is provided with: a discharge temperature sensor 34 for detecting the temperature of the refrigerant discharged from the compressor 10, that is, a discharge temperature Td; an outdoor temperature sensor 36 for detecting the outdoor temperature To; The indoor temperature sensor 38 for detecting the indoor temperature Ti; the intermediate pressure temperature sensor 26 for detecting the gas-liquid separation temperature Tm, which is the temperature of the refrigerant flowing from the refrigerant circuit 1 into the injection path 22; The superheat temperature sensor 28 detects the injection temperature Tinj which is the temperature of the refrigerant heated by the radiator 24 . The control device 30 controls the opening degrees of the indoor-side throttle device 14 and the outdoor-side throttle device 18 and the rotational speed of the compressor 10 mainly based on temperatures detected by various temperature sensors.
需要说明的是，中间压温度传感器26既可以设置在气液分离器16上，也可以设置在构成喷射路径22的制冷剂配管的比加热器24更靠上游侧的位置。或者，中间压温度传感器26也可以设置在将气液分离器16与室内侧节流装置14连接的制冷剂配管上或者将气液分离器16与室外侧节流装置18连接的制冷剂配管上。过热度温度传感器28设置在构成喷射路径22的制冷剂配管的比加热器24更靠下游侧的位置。The intermediate pressure temperature sensor 26 may be installed on the gas-liquid separator 16 , or may be installed on the upstream side of the heater 24 in the refrigerant piping constituting the injection path 22 . Alternatively, the intermediate pressure temperature sensor 26 may also be installed on the refrigerant piping connecting the gas-liquid separator 16 and the indoor side throttling device 14 or on the refrigerant piping connecting the gas-liquid separator 16 and the outdoor side throttling device 18 . The superheat temperature sensor 28 is provided on the downstream side of the heater 24 in the refrigerant piping constituting the injection path 22 .
接着，对制冷循环装置100的动作进行说明。Next, the operation of the refrigeration cycle apparatus 100 will be described.
在供暖时，通过四通阀32将制冷剂的流动方向切换为由实线箭头所示的第一方向。在这种状态下，由压缩机10压缩后的制冷剂从压缩机10喷出之后被向室内换热器12引导。被导向室内换热器12的制冷剂在此向室内空气散热之后，被向室内侧节流装置14引导。被导向室内侧节流装置14的制冷剂在室内侧节流装置14中被减压，成为具有冷凝压力与蒸发压力的中间的压力的中间压制冷剂而被向气液分离器16引导。被导向气液分离器16的中间压制冷剂在气液分离器16中被分离，中间压制冷剂之中的液体制冷剂被向室外侧节流装置18引导，气体制冷剂向喷射路径22流入。被导向室外侧节流装置18的中间压液体制冷剂在室外侧节流装置18中被减压，并被向室外换热器20引导，之后，从室外空气吸热，然后返回压缩机10。向喷射路径22流入的中间压气体制冷剂由加热器24加热之后，被向压缩机10喷射。During heating, the flow direction of the refrigerant is switched by the four-way valve 32 to the first direction indicated by the solid arrow. In this state, the refrigerant compressed by the compressor 10 is discharged from the compressor 10 and then guided to the indoor heat exchanger 12 . The refrigerant guided to the indoor heat exchanger 12 radiates heat to the indoor air, and then is guided to the indoor expansion device 14 . The refrigerant guided to the indoor expansion device 14 is decompressed in the indoor expansion device 14 to become an intermediate-pressure refrigerant having a pressure intermediate between the condensation pressure and the evaporation pressure, and is guided to the gas-liquid separator 16 . The intermediate-pressure refrigerant guided to the gas-liquid separator 16 is separated in the gas-liquid separator 16 , and the liquid refrigerant in the intermediate-pressure refrigerant is guided to the outdoor throttle device 18 , and the gas refrigerant flows into the injection path 22 . . The intermediate-pressure liquid refrigerant guided to the outdoor side expansion device 18 is decompressed in the outdoor side expansion device 18 , guided to the outdoor heat exchanger 20 , absorbs heat from the outdoor air, and returns to the compressor 10 . The intermediate-pressure gas refrigerant flowing into the injection path 22 is injected into the compressor 10 after being heated by the heater 24 .
在制冷时，通过四通阀32将制冷剂的流动方向切换为由虚线箭头所示的第二方向。在这种状态下，由压缩机10压缩后的制冷剂从压缩机10喷出之后被向室外换热器20引导。被导向室外换热器20的制冷剂在此向室外空气散热之后，被向室外侧节流装置18引导。被导向室外侧节流装置18的制冷剂在室外侧节流装置18中被减压，成为具有冷凝压力与蒸发压力的中间的压力的中间压制冷剂而被向气液分离器16引导。被导向气液分离器16的中间压制冷剂在气液分离器16中被分离，中间压制冷剂之中的液体制冷剂被向室内侧节流装置14引导，气体制冷剂向喷射路径22流入。被导向室内侧节流装置14的中间压液体制冷剂在室内侧节流装置14中被减压，并被向室内换热器12引导，之后，从室内空气吸热，然后返回压缩机10。向喷射路径22流入的中间压气体制冷剂由加热器24加热之后，被向压缩机10喷射。During cooling, the four-way valve 32 switches the flow direction of the refrigerant to the second direction indicated by the dotted arrow. In this state, the refrigerant compressed by the compressor 10 is discharged from the compressor 10 and then guided to the outdoor heat exchanger 20 . The refrigerant guided to the outdoor heat exchanger 20 is guided to the outdoor side expansion device 18 after dissipating heat to the outdoor air. The refrigerant guided to the outdoor side expansion device 18 is decompressed in the outdoor side expansion device 18 , becomes an intermediate pressure refrigerant having a pressure intermediate between the condensation pressure and the evaporation pressure, and is guided to the gas-liquid separator 16 . The intermediate-pressure refrigerant guided to the gas-liquid separator 16 is separated in the gas-liquid separator 16 , and the liquid refrigerant in the intermediate-pressure refrigerant is guided to the indoor expansion device 14 , and the gas refrigerant flows into the injection path 22 . . The intermediate-pressure liquid refrigerant guided to the indoor expansion device 14 is decompressed in the indoor expansion device 14 , guided to the indoor heat exchanger 12 , absorbs heat from the indoor air, and returns to the compressor 10 . The intermediate-pressure gas refrigerant flowing into the injection path 22 is injected into the compressor 10 after being heated by the heater 24 .
在供暖时和制冷时，制冷剂回路1中的制冷剂的流动方向不同，但在喷射路径22中制冷剂向相同方向流动，因此作为控制中间压的方法在供暖时和制冷时可以采用同样的方法。以下之中，将供暖时的室内换热器12及制冷时的室外换热器20称为冷凝器，将供暖时的室外换热器20及制冷时的室内换热器12称为蒸发器，将供暖时的室内侧节流装置14及制冷时的室外侧节流装置18称为上游侧节流装置，将供暖时的室外侧节流装置18及制冷时的室内侧节流装置14称为下游侧节流装置，而不对供暖时和制冷时加以区分地进行说明。The flow direction of the refrigerant in the refrigerant circuit 1 is different during heating and cooling, but the refrigerant flows in the same direction in the injection path 22. Therefore, the same method of controlling the intermediate pressure can be used for heating and cooling. method. In the following, the indoor heat exchanger 12 during heating and the outdoor heat exchanger 20 during cooling are referred to as condensers, and the outdoor heat exchanger 20 during heating and the indoor heat exchanger 12 during cooling are referred to as evaporators, The indoor throttle device 14 for heating and the outdoor throttle device 18 for cooling are called upstream throttle devices, and the outdoor throttle device 18 for heating and the indoor throttle device 14 for cooling are called upstream throttle devices. The downstream side throttling device will be described without distinguishing between heating and cooling.
在本实施方式中，控制装置30在起动运转之际进行中间压控制运转。所谓“中间压控制运转”是指，在以使由中间压温度传感器26所检测的气液分离温度Tm与由过热度温度传感器28所检测的喷射温度Tinj之间的温度差变得比规定值ΔTi小的方式对上游侧节流装置和下游侧节流装置中的至少一方的开度进行调整之后，增大下游侧节流装置的开度，直至气液分离温度Tm从此时的温度减小了规定温度ΔTm的运转。以下，参考图2的流程图详细地说明控制装置30所进行的中间压控制运转。In the present embodiment, the control device 30 performs the intermediate pressure control operation during the startup operation. The term "intermediate pressure control operation" means that the temperature difference between the gas-liquid separation temperature Tm detected by the intermediate pressure temperature sensor 26 and the injection temperature Tinj detected by the superheat temperature sensor 28 becomes smaller than a predetermined value. ΔTi is small. After adjusting the opening degree of at least one of the upstream side throttling device and the downstream side throttling device, increase the opening degree of the downstream side throttling device until the gas-liquid separation temperature Tm decreases from the current temperature. Operation at a specified temperature ΔTm. Hereinafter, the intermediate pressure control operation performed by the control device 30 will be described in detail with reference to the flowchart of FIG. 2 .
首先，控制装置30以使由喷出温度传感器34所检测的喷出温度Td保持在目标的喷出温度TD附近的方式对上游侧节流装置的开度进行调整，同时减小下游侧节流装置的开度，直至气液分离温度Tm与喷射温度Tinj之间的温度差变得比规定值ΔTi小。First, the control device 30 adjusts the opening degree of the upstream throttle device so that the discharge temperature Td detected by the discharge temperature sensor 34 is kept close to the target discharge temperature TD, and at the same time reduces the downstream throttle. The opening degree of the device is adjusted until the temperature difference between the gas-liquid separation temperature Tm and the injection temperature Tinj becomes smaller than a predetermined value ΔTi.
具体而言，控制装置30利用室外温度传感器36对室外温度To进行检测，并且利用室内温度传感器38对室内温度Ti进行检测(步骤S1)。接着，控制装置30根据检测出的室外温度To及室内温度Ti，来确定目标的喷出温度TD(步骤S2)。然后，控制装置30利用喷出温度传感器34对喷出温度Td进行检测(步骤S3)，并将其与目标的喷出温度Td之差和预先确定的允许值ΔTd(例如，1.5℃)进行比较(步骤S4)。Specifically, the control device 30 detects the outdoor temperature To by the outdoor temperature sensor 36, and detects the indoor temperature Ti by the indoor temperature sensor 38 (step S1). Next, the control device 30 determines a target discharge temperature TD based on the detected outdoor temperature To and indoor temperature Ti (step S2). Then, the control device 30 detects the discharge temperature Td using the discharge temperature sensor 34 (step S3), and compares the difference between the discharge temperature Td and the target discharge temperature Td with a predetermined allowable value ΔTd (for example, 1.5°C). (step S4).
在检测出的喷出温度Td与目标的喷出温度TD之差为容许值ΔTd以上的情况下(步骤S4中为否)，控制装置30对上游侧节流装置的开度进行调整(步骤S5)。具体而言，控制装置30在检测出的喷出温度Td比目标的喷出温度TD低时减小上游侧节流装置的开度，而在检测出的喷出温度Td比目标的喷出温度TD高时增大上游侧节流装置的开度。步骤S5之后，返回步骤S1。通过反复进行步骤S1～S5，使实际的喷出温度Td接近目标的喷出温度TD的固定温度以内。其结果是，如果检测出的喷出温度Td与目标的喷出温度TD之差小于容许值ΔTd(步骤S4中为是)，则进入步骤S6。When the difference between the detected discharge temperature Td and the target discharge temperature TD is equal to or greater than the allowable value ΔTd (No in step S4), the control device 30 adjusts the opening degree of the upstream throttle device (step S5 ). Specifically, the control device 30 reduces the opening degree of the upstream throttle device when the detected discharge temperature Td is lower than the target discharge temperature TD, and reduces the opening degree of the upstream throttle device when the detected discharge temperature Td is lower than the target discharge temperature TD. When TD is high, increase the opening degree of the throttle device on the upstream side. After step S5, return to step S1. By repeating steps S1 to S5, the actual discharge temperature Td is brought within a fixed temperature close to the target discharge temperature TD. As a result, if the difference between the detected discharge temperature Td and the target discharge temperature TD is smaller than the allowable value ΔTd (YES in step S4 ), the process proceeds to step S6 .
在步骤S6中，控制装置30利用中间压温度传感器26对中间压制冷剂的气液分离温度Tm进行检测，并且利用过热度温度传感器28对通过了加热器24之后的制冷剂的喷射温度Tinj进行检测(步骤S6)。接着，控制装置30判定气液分离温度Tm与喷射温度Tinj之间的温度差是否小于预先确定的规定值ΔTi(例如，3℃)(步骤S7)。In step S6, the control device 30 uses the intermediate pressure temperature sensor 26 to detect the gas-liquid separation temperature Tm of the intermediate pressure refrigerant, and uses the superheat temperature sensor 28 to measure the injection temperature Tinj of the refrigerant after passing through the heater 24. Detection (step S6). Next, the control device 30 determines whether the temperature difference between the gas-liquid separation temperature Tm and the injection temperature Tinj is smaller than a predetermined value ΔTi (for example, 3° C.) (step S7 ).
气液分离温度Tm与喷射温度Tinj之间的温度差为所喷射的气体制冷剂的过热度。现有技术中，在喷射路径22未设有加热器24，故所喷射的中间压气体制冷剂不会获取过热度。与其相对地，在本实施方式中，通过在喷射路径22设置加热器24，只要仅仅气体制冷剂在喷射路径22中流动，则通过了加热器24之后的中间压气体制冷剂可获取过热度。The temperature difference between the gas-liquid separation temperature Tm and the injection temperature Tinj is the degree of superheat of the injected gas refrigerant. In the prior art, the heater 24 is not provided in the injection path 22, so the injected intermediate-pressure gas refrigerant does not acquire superheat. On the other hand, in the present embodiment, by providing the heater 24 in the injection path 22 , as long as only the gas refrigerant flows through the injection path 22 , the intermediate-pressure gas refrigerant passing through the heater 24 can acquire superheat.
在步骤S7中为否的情况下、即在过热度获取了固定温度以上的情况下，控制装置30减小下游侧节流装置的开度(步骤S8)，而使气液分离温度Tm上升。步骤S8之后，返回步骤S1。控制装置30反复进行步骤S1～S8，直至在步骤S7中成为是。When NO in step S7, that is, when the degree of superheat is equal to or higher than the fixed temperature, the control device 30 reduces the opening of the downstream throttle device (step S8) to increase the gas-liquid separation temperature Tm. After step S8, return to step S1. The control device 30 repeats steps S1 to S8 until it becomes YES in step S7.
当减小下游侧节流装置的开度时，下游侧节流装置的前后的压力差变大，伴随于此，中间压变高。另外，所喷射的制冷剂的流量的比例也增加。当中间压上升时，气液分离器16内的中间压制冷剂的干燥度减少。如上所述，当继续减小下游侧节流装置的开度时，干燥度继续减少，所喷射的制冷剂的流量继续增加，故在某一阶段液体制冷剂流入喷射路径22。When the opening degree of the downstream side throttling device is reduced, the pressure difference between the front and rear of the downstream side throttling device increases, and the intermediate pressure increases accordingly. In addition, the ratio of the flow rate of the injected refrigerant also increases. When the intermediate pressure rises, the dryness of the intermediate-pressure refrigerant in the gas-liquid separator 16 decreases. As mentioned above, when the opening degree of the throttle device on the downstream side continues to decrease, the dryness continues to decrease, and the flow rate of injected refrigerant continues to increase, so the liquid refrigerant flows into the injection path 22 at a certain stage.
当液体制冷剂流入喷射路径22时，由加热器24对液体制冷剂进行加热而使其蒸发，故在此时的潜热的作用下，通过了加热器24之后的制冷剂的喷射温度Tinj急剧地降低。步骤S7为用于对喷射温度Tinj急剧地降低这一情况进行检测的步骤。When the liquid refrigerant flows into the injection path 22, the heater 24 heats the liquid refrigerant to evaporate, so due to the latent heat at this time, the injection temperature Tinj of the refrigerant after passing through the heater 24 sharply decreases. reduce. Step S7 is a step for detecting that the injection temperature Tinj has dropped sharply.
在步骤S7中为是的情况下、即在喷射温度Tinj急剧地降低而通过加热器24之后的气体制冷剂未能获取固定温度以上的过热度的情况下，控制装置30将此时的气液分离温度Tm记录为Tm0(步骤S9)。If the answer in step S7 is YES, that is, if the injection temperature Tinj drops sharply and the gas refrigerant after passing through the heater 24 fails to acquire a degree of superheat equal to or higher than a fixed temperature, the control device 30 converts the gas-liquid temperature at this time to The separation temperature Tm is recorded as Tm0 (step S9).
通过提高中间压力，能够减少在压缩机10中再次压缩的作功量，故能够减少压缩机10的电力消耗量。但是，当液体制冷剂开始向喷射路径22流动时，在蒸发器中流动的液体制冷剂的量也降低，蒸发能力降低，制冷循环的性能也降低。因而，为了在进行喷射的制冷循环装置100中获得较高的性能，需要将喷射路径22形成为仅仅有气体制冷剂流动的状态。因此，控制装置30确定目标的气液分离温度Tm1(步骤S10)。具体而言，控制装置30为了可靠地防止液体制冷剂向喷射路径22流入的情况，从处于通过加热器24之后的气体制冷剂无法获取固定温度以上的过热度的状态下的气液分离温度Tm0减去预先确定出的规定温度(例如，1℃)，由此来算出目标的气液分离温度Tm1。By increasing the intermediate pressure, the work amount of recompression in the compressor 10 can be reduced, so the power consumption of the compressor 10 can be reduced. However, when the liquid refrigerant starts to flow into the injection path 22, the amount of the liquid refrigerant flowing in the evaporator also decreases, the evaporation capacity decreases, and the performance of the refrigeration cycle also decreases. Therefore, in order to obtain high performance in the refrigeration cycle apparatus 100 that performs injection, it is necessary to form the injection path 22 in a state where only the gas refrigerant flows. Therefore, the control device 30 determines the target gas-liquid separation temperature Tm1 (step S10). Specifically, in order to reliably prevent liquid refrigerant from flowing into the injection path 22, the control device 30 sets the gas-liquid separation temperature Tm0 in a state where the gas refrigerant passing through the heater 24 cannot obtain a degree of superheat equal to or higher than a fixed temperature. The target gas-liquid separation temperature Tm1 is calculated by subtracting a predetermined temperature (for example, 1°C) determined in advance.
在步骤S10以后，再次对下游侧节流装置的开度进行调整而使中间压及气液分离温度Tm下降，从而成为在喷射路径22中仅仅有气体制冷剂流动的状态。具体而言，控制装置30利用中间压温度传感器26对中间压的气液分离温度Tm进行检测(步骤S11)，并将其与在步骤S10中确定出的目标的气液分离温度Tm1进行比较(步骤S12)。在检测出的气液分离温度Tm为目标的气液分离温度Tm1以上的情况下(步骤S12中为否)，增大下游侧节流装置的开度(步骤S13)，使中间压下降。在增大下游侧节流装置的开度而低于目标的气液分离温度Tm1时(步骤S12中为是)，向以保持目标的喷出温度、目标的气液分离温度的方式来进行控制的稳定运转转移(步骤S14)。After step S10 , the opening degree of the downstream expansion device is adjusted again to lower the intermediate pressure and the gas-liquid separation temperature Tm, so that only the gas refrigerant flows in the injection path 22 . Specifically, the control device 30 uses the intermediate pressure temperature sensor 26 to detect the gas-liquid separation temperature Tm of the intermediate pressure (step S11), and compares it with the target gas-liquid separation temperature Tm1 determined in step S10 ( Step S12). When the detected gas-liquid separation temperature Tm is equal to or higher than the target gas-liquid separation temperature Tm1 (NO in step S12), the opening degree of the downstream throttle device is increased (step S13) to lower the intermediate pressure. When the opening degree of the downstream side expansion device is increased to be lower than the target gas-liquid separation temperature Tm1 (YES in step S12), control is performed so as to maintain the target discharge temperature and the target gas-liquid separation temperature The steady-state operation transition (step S14).
在向稳定运转转移之后，控制装置30也利用中间压温度传感器26及喷出温度传感器34来对气液分离温度Tm及喷出温度Td进行检测，并以使它们不远离目标值的方式对上游侧节流装置及下游侧节流装置的开度进行调整。After shifting to the stable operation, the control device 30 also detects the gas-liquid separation temperature Tm and the discharge temperature Td by using the intermediate pressure temperature sensor 26 and the discharge temperature sensor 34, and controls the upstream temperature so that they do not deviate from the target value. Adjust the opening of the side throttle device and the downstream side throttle device.
气液分离温度Tm的控制通过下游侧节流装置的开度的调整来进行。具体而言，以使检测出的气液分离温度Tm距目标的气液分离温度Tm1成为固定温度ΔTms以内的方式对下游侧节流装置的开度进行调整。在气液分离温度Tm比Tm1-ΔTms低的情况下，减小下游侧节流装置的开度，使气液分离温度Tm上升，而使Tm接近Tm1。相反地，在气液分离温度Tm比Tm1+ΔTms高的情况下，增大下游侧节流装置的开度，使气液分离温度Tm下降，而使Tm接近Tm1。该调整的期间的下游侧节流装置的开度的调整量既可以为固定，也可以越接近目标值越减小开度的调整量。The control of the gas-liquid separation temperature Tm is performed by adjusting the opening degree of the downstream side throttle device. Specifically, the opening degree of the downstream side expansion device is adjusted so that the detected gas-liquid separation temperature Tm is within a fixed temperature ΔTms from the target gas-liquid separation temperature Tm1. When the gas-liquid separation temperature Tm is lower than Tm1-ΔTms, the opening degree of the downstream throttle device is reduced to raise the gas-liquid separation temperature Tm so that Tm approaches Tm1. Conversely, when the gas-liquid separation temperature Tm is higher than Tm1+ΔTms, the opening of the downstream throttle device is increased to lower the gas-liquid separation temperature Tm so that Tm approaches Tm1. During this adjustment period, the adjustment amount of the opening degree of the downstream throttle device may be constant, or the adjustment amount of the opening degree may be decreased as it approaches the target value.
喷出温度Td的控制通过上游侧节流装置的开度的调整来进行。具体而言，以使检测出的喷出温度Td距目标的喷出温度TD成为固定温度ΔTds以内的方式对上游侧节流装置的开度进行调整。在喷出温度Td比TD-ΔTds低的情况下，减小上游侧节流装置的开度，使喷出温度Td上升，而使Td接近TD。相反地，在喷出温度Td比Td+ΔTds高的情况下，增大上游侧节流装置的开度，使喷出温度Td下降，而使Td接近TD。该调整的期间的上游侧节流装置的开度的调整量既可以为固定，也可以越接近目标值越减小开度的调整量。The control of the discharge temperature Td is performed by adjusting the opening degree of the upstream throttle device. Specifically, the opening degree of the upstream side throttle device is adjusted so that the detected discharge temperature Td is within a fixed temperature ΔTds from the target discharge temperature TD. When the discharge temperature Td is lower than TD-ΔTds, the opening degree of the upstream throttle device is reduced to increase the discharge temperature Td so that Td approaches TD. Conversely, when the discharge temperature Td is higher than Td+ΔTds, the opening of the upstream throttle device is increased to lower the discharge temperature Td so that Td approaches TD. The adjustment amount of the opening degree of the upstream throttle device during this adjustment period may be constant, or the adjustment amount of the opening degree may be decreased as it approaches the target value.
如图1所示，气液分离器16配置在上游侧节流装置与下游侧节流装置之间，故气液分离温度Tm受到上游侧节流装置的开度的调整的很大影响。具体而言，当减小上游侧节流装置的开度时，上游侧节流装置前后的差压变大，伴随于此，中间压降低，气液分离温度Tm降低。相反地，当增大上游侧节流装置的开度时，上游侧节流装置前后的差压变小，伴随于此，中间压上升，气液分离温度Tm上升。如此，上游侧节流装置的开度的调整不仅对于喷出温度Td赋予影响，对于气液分离温度Tm也赋予影响。这种情况不局限于上游侧节流装置，而当进行下游侧节流装置的开度的调整时，向蒸发器流动的制冷剂的量变化，压缩机10的吸入状态变化，故下游侧节流装置的开度的调整不仅对于气液分离温度Tm赋予影响，对于喷出温度Td也赋予影响。As shown in FIG. 1 , the gas-liquid separator 16 is arranged between the upstream side throttle device and the downstream side throttle device, so the gas-liquid separation temperature Tm is greatly affected by the adjustment of the opening degree of the upstream side throttle device. Specifically, when the opening degree of the upstream side throttle device is reduced, the differential pressure across the upstream side throttle device increases, the intermediate pressure decreases accordingly, and the gas-liquid separation temperature Tm decreases. Conversely, when the opening degree of the upstream throttle device is increased, the differential pressure across the upstream side throttle device decreases, and the intermediate pressure increases accordingly, thereby increasing the gas-liquid separation temperature Tm. In this manner, the adjustment of the opening degree of the upstream throttle device affects not only the discharge temperature Td but also the gas-liquid separation temperature Tm. This is not limited to the upstream side throttling device, but when the opening of the downstream side throttling device is adjusted, the amount of refrigerant flowing to the evaporator changes, and the suction state of the compressor 10 changes, so the downstream side throttle The adjustment of the opening of the flow device affects not only the gas-liquid separation temperature Tm but also the discharge temperature Td.
如此，上游侧节流装置及下游侧节流装置各自的开度调整分别对喷出温度Td及气液分离温度Tm赋予影响，不过，当利用上游侧节流装置来控制喷出温度Td，而利用下游侧节流装置来控制气液分离温度Tm这样的使各个节流装置分别具有作用地进行控制时，能够实现更加简易的控制。In this way, the opening adjustments of the upstream side throttling device and the downstream side throttling device each have an influence on the discharge temperature Td and the gas-liquid separation temperature Tm. However, when the upstream side throttling device is used to control the discharge temperature Td, When the gas-liquid separation temperature Tm is controlled by the downstream side throttling means, when each throttling means functions individually, control can be performed more easily.
图3示出了在上述的中间压控制运转中，上游侧节流装置及下游侧节流装置的开度以及喷出温度Td、喷射温度Tinj及气液分离温度Tm如何变化的情况。如图3所示，在本实施方式中，首先，将上游侧节流装置的开度逐渐地减小，而喷出温度Td逐渐地上升。接着，将下游侧节流装置的开度减小，直至喷射温度Tinj急剧地降低，然后将下游侧节流装置的开度增大。3 shows how the opening degrees of the upstream side throttle device and the downstream side throttle device, the discharge temperature Td, the injection temperature Tinj, and the gas-liquid separation temperature Tm change during the above-mentioned intermediate pressure control operation. As shown in FIG. 3 , in the present embodiment, first, the opening degree of the upstream throttle device is gradually reduced, and the discharge temperature Td is gradually increased. Next, the opening degree of the downstream side throttle device is decreased until the injection temperature Tinj drops sharply, and then the opening degree of the downstream side throttle device is increased.
在以上说明的中间压控制运转中，采用加热器24及过热度温度传感器28来确定气液分离温度Tm的基准温度Tm0，并将比该基准温度Tm0低规定温度ΔTm的温度设为气液分离温度的目标温度Tm1，由此能够消除中间压温度传感器26的测定误差。由此，能够将中间压更高精度地控制为目的值，从而能够使制冷循环装置100的效率提高。In the above-described intermediate pressure control operation, the heater 24 and the superheat temperature sensor 28 are used to determine the reference temperature Tm0 of the gas-liquid separation temperature Tm, and a temperature lower than the reference temperature Tm0 by a predetermined temperature ΔTm is used as the gas-liquid separation temperature. The target temperature Tm1 of the temperature can thereby eliminate the measurement error of the intermediate pressure temperature sensor 26 . Thereby, the intermediate pressure can be controlled to the target value with higher precision, and the efficiency of the refrigeration cycle apparatus 100 can be improved.
另外，在本实施方式中，在起动运转之际进行中间压控制运转，因此能够以最佳的状态从起动运转向稳定运转转移。In addition, in the present embodiment, the intermediate pressure control operation is performed during the startup operation, so that the transition from the startup operation to the steady operation can be performed in an optimal state.
<变形例><Modification>
在所述实施方式中，在起动运转之际进行了中间压控制运转。因此，以使气液分离温度Tm与喷射温度Tinj之间的温度差变得比规定值小的方式对上游侧节流装置和下游侧节流装置这双方的开度进行调整。但是，控制装置30也可以在稳定运转的中途进行中间压控制运转。在这种情况下，也可以以使气液分离温度Tm与喷射温度Tinj之间的温度差变得比规定值小的方式对上游侧节流装置和下游侧节流装置中的任一方的开度进行调整。In the above-described embodiment, the intermediate pressure control operation is performed during the start-up operation. Therefore, the opening degrees of both the upstream side throttling device and the downstream side throttling device are adjusted so that the temperature difference between the gas-liquid separation temperature Tm and the injection temperature Tinj becomes smaller than a predetermined value. However, the control device 30 may perform the intermediate pressure control operation in the middle of the steady operation. In this case, either the upstream side throttling device or the downstream side throttling device may be opened so that the temperature difference between the gas-liquid separation temperature Tm and the injection temperature Tinj becomes smaller than a predetermined value. degree to adjust.
在稳定运转的中途进行中间压控制运转时的流程图与图2完全相同。即，在稳定运转中满足了某些判定条件时进入步骤S1即可。例如，可以在外气温度变化、循环条件变化较大时等进入步骤S1，也可以根据用户侧的要求的变化而进入步骤S1。或者是，也可以根据自运转开始起的经过时间而进入步骤S1。The flow chart when the intermediate pressure control operation is performed in the middle of the steady operation is exactly the same as that in FIG. 2 . That is, what is necessary is just to progress to step S1 when certain determination conditions are satisfied during steady operation. For example, the process may proceed to step S1 when the outside air temperature changes or the circulation conditions change greatly, or may proceed to step S1 according to changes in the user's request. Alternatively, the process may proceed to step S1 based on the elapsed time from the start of the operation.
在所述实施方式中，作为加热器24使用了电热器。但是，加热器24并不局限于电热器等从制冷剂回路1的外部对制冷剂施加热量的机构。例如，也可以通过使构成喷射路径22的制冷剂配管的一部分与比中间压的制冷剂(气液分离温度)温度高的高温的压缩机10的密闭容器或者喷出配管等直接性或者间接性地接触，由此制冷剂回路1的一部分构成加热器24。以下，对加热器24的变形例进行详细的说明。需要说明的是，以下所示的变形例除了特别说明的情况以外，均与所述实施方式同样地构成。In the above embodiment, an electric heater is used as the heater 24 . However, the heater 24 is not limited to a mechanism that applies heat to the refrigerant from the outside of the refrigerant circuit 1, such as an electric heater. For example, a part of the refrigerant piping constituting the injection path 22 may be directly or indirectly connected to a closed container or a discharge piping of the high-temperature compressor 10 having a temperature higher than that of the intermediate-pressure refrigerant (gas-liquid separation temperature). ground contact, whereby a part of the refrigerant circuit 1 constitutes the heater 24 . Hereinafter, modifications of the heater 24 will be described in detail. In addition, the modification examples shown below are configured in the same manner as the above-mentioned embodiment except for the case where it is particularly described.
图4表示作为加热器24的一变形例的加热器24A。加热器24A为对从压缩机10排出的热量进行蓄积，并利用该蓄积的热量来对在喷射路径22中流动的制冷剂进行加热的蓄热单元。具体而言，加热器24A具有：以将压缩机10包入的方式配置的蓄热件50；在蓄热件50的内部蜿蜒通过的蜿蜒管52。蜿蜒管52构成喷射路径22的一部分。因而，从气液分离器16向喷射路径22流入的制冷剂通过在蜿蜒管52中流动而被加热。进而，通过了蜿蜒管52的制冷剂被向压缩机10喷射。由此，能够利用压缩机10的废热，来对在喷射路径22中流动的制冷剂进行加热。由于无需为了对在喷射路径22中流动的制冷剂进行加热而设置独立的电热器，故能够实现制冷循环装置的节省电力化。FIG. 4 shows a heater 24A as a modified example of the heater 24 . The heater 24A is a thermal storage unit that stores heat discharged from the compressor 10 and uses the stored heat to heat the refrigerant flowing through the injection path 22 . Specifically, heater 24A has: thermal storage material 50 disposed so as to enclose compressor 10 ; and meandering pipe 52 meandering through the inside of thermal storage material 50 . The serpentine tube 52 forms part of the injection path 22 . Therefore, the refrigerant flowing into the injection path 22 from the gas-liquid separator 16 is heated by flowing through the serpentine tube 52 . Furthermore, the refrigerant that has passed through the serpentine tube 52 is injected toward the compressor 10 . Thereby, the refrigerant flowing through the injection path 22 can be heated by waste heat of the compressor 10 . Since it is not necessary to provide a separate electric heater for heating the refrigerant flowing through the injection path 22, power saving of the refrigeration cycle apparatus can be realized.
图5表示具备作为加热器24的另一变形例的加热器24B的制冷循环装置100A。加热器24B为具有对在喷射路径22中流动的制冷剂进行引导的第一换热部60及从制冷剂回路1分支而对在制冷剂回路1中流动的制冷剂进行引导的第二换热部62的换热器。第一换热部60也为喷射路径22的一部分。被导向第二换热部62的制冷剂的温度比气液分离温度高。第二换热部62同冷凝器12与上游侧节流装置14之间的制冷剂回路1连接。详细而言，第二换热部62具有同冷凝器12与上游侧节流装置14之间的制冷剂回路1连接的一端和在比该一端更靠下游侧处同冷凝器12与上游侧节流装置14之间的制冷剂回路1连接的另一端。由此，向第二换热部62引导在冷凝器12与上游侧节流装置14之间流动的制冷剂。另外，第二换热部62配置成对第一换热部60进行加热。由此，对在喷射路径22中流动的制冷剂进行加热。因而，能够利用在制冷剂回路1中流动的制冷剂所具有的热量，来对在喷射路径22中流动的制冷剂进行加热。无需为了对在喷射路径22中流动的制冷剂进行加热而设置独立的电热器，故能够实现制冷循环装置的节省电力化。另外，能够提高制冷剂回路1的冷凝器12的出口侧的制冷剂的过冷却度，故能够实现制冷能力得以提高的制冷循环装置100A。FIG. 5 shows a refrigeration cycle apparatus 100A including a heater 24B as another modified example of the heater 24 . The heater 24B has a first heat exchange part 60 that guides the refrigerant flowing through the injection path 22 and a second heat exchange part that guides the refrigerant flowing through the refrigerant circuit 1 branched from the refrigerant circuit 1 . Section 62 of the heat exchanger. The first heat exchange portion 60 is also a part of the injection path 22 . The temperature of the refrigerant guided to the second heat exchange unit 62 is higher than the gas-liquid separation temperature. The second heat exchange unit 62 is connected to the refrigerant circuit 1 between the condenser 12 and the upstream expansion device 14 . In detail, the second heat exchange unit 62 has one end connected to the refrigerant circuit 1 between the condenser 12 and the upstream side expansion device 14 and connected to the condenser 12 and the upstream side throttle on the downstream side of the one end. The other end of the refrigerant circuit 1 connection between flow device 14. As a result, the refrigerant flowing between the condenser 12 and the upstream expansion device 14 is guided to the second heat exchange unit 62 . In addition, the second heat exchange part 62 is configured to heat the first heat exchange part 60 . As a result, the refrigerant flowing through the injection path 22 is heated. Therefore, the refrigerant flowing through the injection path 22 can be heated by utilizing the heat of the refrigerant flowing through the refrigerant circuit 1 . Since it is not necessary to provide a separate electric heater for heating the refrigerant flowing through the injection path 22, power saving of the refrigeration cycle apparatus can be realized. In addition, since the degree of subcooling of the refrigerant on the outlet side of the condenser 12 of the refrigerant circuit 1 can be increased, it is possible to realize the refrigeration cycle apparatus 100A with improved refrigeration capacity.
加热器24B为例如由内管及与内管同心的外管构成的双层管式换热器。在这种情况下，内管的内部相当于第一换热部60及第二换热部62中的任一方。另外，形成在外管的内周面与内管的外周面之间的空间相当于第一换热部60及第二换热部62的另一方。另外，通过例如使作为第一换热部60的配管和作为第二换热部62的配管接触地配置，由此也可以构成加热器24B。除此之外，第二换热部62只要能够对第一换热部60进行加热，则加热器24B的结构无特别限定。The heater 24B is, for example, a double-tube heat exchanger composed of an inner tube and an outer tube concentric with the inner tube. In this case, the inside of the inner pipe corresponds to either one of the first heat exchange portion 60 and the second heat exchange portion 62 . In addition, the space formed between the inner peripheral surface of the outer tube and the outer peripheral surface of the inner tube corresponds to the other of the first heat exchange part 60 and the second heat exchange part 62 . In addition, the heater 24B can also be configured by, for example, arranging the piping as the first heat exchange part 60 and the piping as the second heat exchange part 62 so as to be in contact with each other. Besides, as long as the second heat exchange part 62 can heat the first heat exchange part 60, the structure of the heater 24B is not particularly limited.
阀64设置在第二换热部62的上游侧。另外，在制冷剂回路1中，在连接有第二换热部62的一端的位置和连接有第二换热部62的另一端的位置之间设有阀66。阀64、66为例如能够调整开度的电动阀。通过对阀64、66的开闭进行控制而能够对在喷射路径22中流动的制冷剂的加热进行控制。例如，也可以以使仅仅在中间压控制运转之际对在喷射路径22中流动的制冷剂进行加热的方式对阀64、66的开闭进行控制。需要说明的是，阀64、66可以省略。另外，第二换热部62也可以为从制冷剂回路1不分支的形态。换而言之，第二换热部62也可以由冷凝器12与上游侧节流装置14之间的制冷剂回路1的一部分来构成。The valve 64 is provided on the upstream side of the second heat exchange part 62 . In addition, in the refrigerant circuit 1 , a valve 66 is provided between a position where one end of the second heat exchange portion 62 is connected and a position where the other end of the second heat exchange portion 62 is connected. The valves 64 and 66 are, for example, electric valves whose openings can be adjusted. By controlling the opening and closing of the valves 64 and 66 , heating of the refrigerant flowing through the injection path 22 can be controlled. For example, the opening and closing of the valves 64 and 66 may be controlled so as to heat the refrigerant flowing through the injection path 22 only during the intermediate pressure control operation. It should be noted that the valves 64 and 66 can be omitted. In addition, the second heat exchange unit 62 may not branch from the refrigerant circuit 1 . In other words, the second heat exchange unit 62 may be constituted by a part of the refrigerant circuit 1 between the condenser 12 and the upstream expansion device 14 .
图6表示具备作为加热器24的再一变形例的加热器24C的制冷循环装置100B。加热器24C为具有对在喷射路径22中流动的制冷剂进行引导的第一换热部70及从制冷剂回路1分支并对在制冷剂回路1中流动的制冷剂进行引导的第二换热部72的换热器。第一换热部70也为喷射路径22的一部分。第二换热部72同压缩机10与冷凝器12之间的制冷剂回路1连接。详细而言，第二换热部72具有同压缩机10与冷凝器12之间的制冷剂回路1连接的一端和在比该一端更靠下游侧处同压缩机10与冷凝器12之间的制冷剂回路1连接的另一端。由此，向第二换热部72引导在制冷剂回路1中流动的制冷剂之中为比较高温的、在压缩机10与冷凝器12之间流动的制冷剂。被导向第二换热部72的制冷剂的温度比气液分离温度高。另外，第二换热部72配置成对第一换热部70进行加热。由此，对在喷射路径22中流动的制冷剂进行加热。因而，能够利用在制冷剂回路1中流动的制冷剂之中为比较高温的制冷剂所具有的热量，来对在喷射路径22中流动的制冷剂进行加热。由于无需为了对在喷射路径22中流动的制冷剂进行加热而设置独立的电热器，故能够实现制冷循环装置的节省电力化。FIG. 6 shows a refrigeration cycle apparatus 100B including a heater 24C as still another modified example of the heater 24 . The heater 24C has a first heat exchange unit 70 that guides the refrigerant flowing in the injection path 22 and a second heat exchange unit that branches from the refrigerant circuit 1 and guides the refrigerant flowing in the refrigerant circuit 1 . Section 72 of the heat exchanger. The first heat exchange portion 70 is also a part of the injection path 22 . The second heat exchange unit 72 is connected to the refrigerant circuit 1 between the compressor 10 and the condenser 12 . Specifically, the second heat exchange unit 72 has one end connected to the refrigerant circuit 1 between the compressor 10 and the condenser 12 and a connection between the compressor 10 and the condenser 12 on the downstream side of the one end. The other end of the refrigerant circuit 1 connection. Thereby, among the refrigerants flowing in the refrigerant circuit 1 , relatively high-temperature refrigerant flowing between the compressor 10 and the condenser 12 is guided to the second heat exchange unit 72 . The temperature of the refrigerant guided to the second heat exchange unit 72 is higher than the gas-liquid separation temperature. In addition, the second heat exchange part 72 is configured to heat the first heat exchange part 70 . As a result, the refrigerant flowing through the injection path 22 is heated. Therefore, it is possible to heat the refrigerant flowing through the injection path 22 by utilizing the heat of relatively high-temperature refrigerant among the refrigerants flowing through the refrigerant circuit 1 . Since it is not necessary to provide a separate electric heater for heating the refrigerant flowing through the injection path 22, power saving of the refrigeration cycle apparatus can be realized.
第一换热部70及第二换热部72由与加热器24B的第一换热部60及第二换热部62同样的结构来构成。另外，例如能够调整开度的电动阀也可以设置在第二换热部72的上游侧、以及连接有第二换热部72的一端的位置与连接有第二换热部72的另一端的位置之间的制冷剂回路1上。第二换热部72也可以为从制冷剂回路1不分支的形态。换而言之，第二换热部72也可以由压缩机10与冷凝器12之间的制冷剂回路1的一部分构成。The first heat exchange part 70 and the second heat exchange part 72 are configured with the same structure as the first heat exchange part 60 and the second heat exchange part 62 of the heater 24B. In addition, for example, an electric valve capable of adjusting the opening degree may also be provided on the upstream side of the second heat exchange part 72 and between the position where one end of the second heat exchange part 72 is connected and the position where the other end of the second heat exchange part 72 is connected. between locations on refrigerant circuit 1. The second heat exchange unit 72 may not branch from the refrigerant circuit 1 . In other words, the second heat exchange unit 72 may be constituted by a part of the refrigerant circuit 1 between the compressor 10 and the condenser 12 .
(第二实施方式)(second embodiment)
图7表示本发明的第二实施方式所涉及的制冷循环装置200。需要说明的是，在本实施方式中，对于与第一实施方式相同的结构标以相同符号，而省略其说明。FIG. 7 shows a refrigeration cycle apparatus 200 according to a second embodiment of the present invention. In addition, in this embodiment, the same code|symbol is attached|subjected to the same structure as 1st Embodiment, and the description is abbreviate|omitted.
在本实施方式中，在制冷剂回路1中的室内换热器12与室内侧节流装置14之间设有室内换热器侧温度传感器40，而在室外侧节流装置18与室外换热器20之间设有室外换热器侧温度传感器42。需要说明的是，本实施方式的制冷循环装置200的动作与第一实施方式的制冷循环装置100的动作相同。In this embodiment, an indoor heat exchanger side temperature sensor 40 is provided between the indoor heat exchanger 12 and the indoor side throttling device 14 in the refrigerant circuit 1, and the outdoor side throttling device 18 exchanges heat with the outdoor. An outdoor heat exchanger side temperature sensor 42 is provided between the heat exchangers 20 . It should be noted that the operation of the refrigeration cycle device 200 in this embodiment is the same as that of the refrigeration cycle device 100 in the first embodiment.
在供暖时，室内换热器侧温度传感器40对从室内换热器(冷凝器)12流出的制冷剂的温度即冷凝侧出口温度Tc进行检测，室外换热器侧温度传感器42对向室外换热器(蒸发器)20流入的制冷剂的温度即蒸发侧入口温度Te进行检测。在制冷时，室外换热器侧温度传感器42对从室外换热器(冷凝器)20流出的制冷剂的温度即冷凝侧出口温度Tc进行检测，室内换热器侧温度传感器40对向室内换热器(蒸发器)12流入的制冷剂的温度即蒸发侧入口温度Te进行检测。以下，将供暖时的室内换热器侧温度传感器40及制冷时的室外换热器侧温度传感器42称为冷凝后温度传感器，将供暖时的室外换热器侧温度传感器42及制冷时的室内换热器侧温度传感器40称为蒸发前温度传感器，与第一实施方式同样地不对供暖时和制冷时加以区分地进行说明。During heating, the indoor heat exchanger side temperature sensor 40 detects the temperature of the refrigerant flowing out of the indoor heat exchanger (condenser) 12, that is, the outlet temperature Tc on the condensation side, and the outdoor heat exchanger side temperature sensor 42 is directed toward the outdoor. The temperature of the refrigerant flowing into the heater (evaporator) 20 , that is, the evaporation side inlet temperature Te is detected. During cooling, the outdoor heat exchanger side temperature sensor 42 detects the temperature of the refrigerant flowing out of the outdoor heat exchanger (condenser) 20, that is, the condensation side outlet temperature Tc, and the indoor heat exchanger side temperature sensor 40 is directed toward the indoor heat exchanger. The temperature of the refrigerant flowing into the heater (evaporator) 12, that is, the evaporation side inlet temperature Te is detected. Hereinafter, the indoor heat exchanger side temperature sensor 40 during heating and the outdoor heat exchanger side temperature sensor 42 during cooling are referred to as post-condensation temperature sensors, and the outdoor heat exchanger side temperature sensor 42 during heating and the indoor heat exchanger side temperature sensor 42 during cooling are referred to as post-condensation temperature sensors. The heat exchanger side temperature sensor 40 is referred to as a pre-evaporation temperature sensor, and will be described without distinguishing between heating and cooling as in the first embodiment.
控制装置30进行与第一实施方式大致同样的中间压控制运转，但此时，使用气液分离温度Tm与喷射温度Tinj之间的温度差变得比规定值ΔTi小时的气液分离温度Tm、冷凝侧出口温度Tc及蒸发侧入口温度Te，来对在稳定运转中使用的气液分离温度的计算式进行修正。以下，参考图8的流程图详细地说明控制装置30所进行的中间压控制运转。The control device 30 performs the intermediate pressure control operation substantially the same as in the first embodiment, but at this time, the gas-liquid separation temperature Tm at which the temperature difference between the gas-liquid separation temperature Tm and the injection temperature Tinj becomes smaller than a predetermined value ΔTi is used. The condensing side outlet temperature Tc and the evaporating side inlet temperature Te are used to correct the calculation formula for the gas-liquid separation temperature used in stable operation. Hereinafter, the intermediate pressure control operation performed by the control device 30 will be described in detail with reference to the flowchart of FIG. 8 .
图8所示的流程图将图2所示的流程图的步骤S9变更为步骤S21～S23，其他的步骤S1～S8、S10～S14与第一实施方式相同。因此，以下，以本实施方式独自的步骤S21～S23为中心进行说明。In the flowchart shown in FIG. 8 , step S9 in the flowchart shown in FIG. 2 is changed to steps S21 to S23 , and other steps S1 to S8 and S10 to S14 are the same as those in the first embodiment. Therefore, the following description will focus on steps S21 to S23 unique to this embodiment.
在步骤S7中，控制装置30在判定为由中间压温度传感器26检测出的气液分离温度Tm与由过热度温度传感器28检测出的喷射温度Tinj之间的温度差比预先确定的规定值ΔTi小时，利用冷凝后温度传感器对冷凝侧出口温度Tc进行检测，并且利用蒸发前温度传感器对蒸发侧入口温度Te进行检测(步骤S21)。接着，控制装置30将在步骤S7中成为是时的气液分离温度Tm记录为Tm0，并且将在步骤S21中检测出的冷凝侧出口温度Tc及蒸发侧入口温度Te分别存储为Tc0及Te0(步骤S22)。然后，控制装置30使用存储的Tm0、Tc0、Te0，对在稳定运转中使用的气液分离温度的计算式进行修正(步骤S23)。In step S7, the control device 30 determines that the temperature difference between the gas-liquid separation temperature Tm detected by the intermediate pressure temperature sensor 26 and the injection temperature Tinj detected by the superheat temperature sensor 28 is smaller than a predetermined value ΔTi. After condensing, the outlet temperature Tc of the condensing side is detected by the temperature sensor after condensation, and the inlet temperature Te of the evaporating side is detected by the temperature sensor before evaporating (step S21). Next, the control device 30 records the gas-liquid separation temperature Tm when YES in step S7 as Tm0, and stores the condensation side outlet temperature Tc and the evaporation side inlet temperature Te detected in step S21 as Tc0 and Te0 ( Step S22). Then, the control device 30 corrects the calculation formula of the gas-liquid separation temperature used in the steady operation by using the stored Tm0, Tc0, and Te0 (step S23).
在此，所谓“在稳定运转中使用的气液分离温度的计算式”，为用于根据冷凝侧出口温度Tc及蒸发侧入口温度Te或者仅根据冷凝侧出口温度Tc来推定气液分离温度的计算式，例如如以下的式(1)来表示。Here, the "calculation formula for the gas-liquid separation temperature used in steady operation" is a formula for estimating the gas-liquid separation temperature from the condensation side outlet temperature Tc and the evaporation side inlet temperature Te or only from the condensation side outlet temperature Tc. The calculation formula is represented, for example, by the following formula (1).
Tm2＝αTc+β···(1)Tm2=αTc+β···(1)
需要说明的是，在使用式(1)的情况下、换而言之在仅仅根据冷凝侧出口温度来推定气液分离温度的情况下，在步骤S21中无需利用蒸发前温度传感器来检测蒸发侧入口温度Te。即，能够仅仅使用Tm0和Tc0来对气液分离温度的计算式进行修正。以下，为了易于理解说明，假定使用式(1)来进行说明。It should be noted that, in the case of using formula (1), in other words, in the case of estimating the gas-liquid separation temperature only based on the outlet temperature of the condensation side, it is not necessary to use the pre-evaporation temperature sensor to detect the temperature of the evaporation side in step S21. Inlet temperature Te. That is, the calculation formula of the gas-liquid separation temperature can be corrected using only Tm0 and Tc0. Hereinafter, for the sake of easy understanding of the description, it will be described assuming that Equation (1) is used.
在步骤S23中，控制装置30将在步骤S22中存储的Tc0代入式(1)，算出推定温度Tm2。控制装置30将算出的推定温度Tm2与在步骤S22中存储的Tm0进行比较，以其差作为中间压温度传感器26及冷凝后温度传感器的测定误差而被消除的方式对气液分离温度的计算式进行改写。例如，在Tm0相对于Tm2较大的情况下，在计算式中加上作为修正值的其差量(Tm0-Tm2)，在Tm0相对于Tm2较小的情况下，在计算式中减去作为修正值的其差量(Tm2-Tm0)。或者是，对上述的式(1)中的系数α、β进行变更。In step S23, the control apparatus 30 substitutes Tc0 memorize|stored in step S22 into Formula (1), and calculates estimated temperature Tm2. The control device 30 compares the calculated estimated temperature Tm2 with the Tm0 stored in step S22, and calculates the gas-liquid separation temperature in such a manner that the difference is eliminated as a measurement error of the intermediate pressure temperature sensor 26 and the post-condensation temperature sensor. to rewrite. For example, when Tm0 is larger than Tm2, add the difference (Tm0-Tm2) as a correction value to the calculation formula, and in the case where Tm0 is smaller than Tm2, subtract it from the calculation formula. The difference (Tm2-Tm0) of the correction value. Alternatively, the coefficients α and β in the above-mentioned formula (1) are changed.
然后，控制装置30经过步骤S10～S13，向稳定运转转移(步骤814)。在稳定运转中，控制装置30使用在中间压控制运转中修正后的气液分离温度的计算式来进行稳定运转。具体而言，控制装置30利用中间压温度传感器26、喷出温度传感器34、冷凝后温度传感器及蒸发前温度传感器来检测气液分离温度Tm、喷出温度Td、冷凝侧出口温度Tc、蒸发侧入口温度Te，并以使它们不远离目标值的方式对上游侧节流装置及下游侧节流装置的开度进行调整。Then, the control device 30 proceeds to the steady operation through steps S10 to S13 (step 814 ). In the steady operation, the control device 30 performs the steady operation using the calculation formula of the gas-liquid separation temperature corrected in the intermediate pressure control operation. Specifically, the control device 30 uses the intermediate pressure temperature sensor 26, the discharge temperature sensor 34, the post-condensation temperature sensor, and the pre-evaporation temperature sensor to detect the gas-liquid separation temperature Tm, the discharge temperature Td, the condensation side outlet temperature Tc, and the evaporation side temperature sensor. The inlet temperature Te is adjusted so that the openings of the upstream side throttle device and the downstream side throttle device are adjusted so that they do not deviate from the target value.
在第一实施方式中，目标的气液分离温度Tm1为固定，但在本实施方式中，将使用在步骤S23中修正了的气液分离温度的计算式算出的推定温度Tm2设定为目标的气液分离温度。喷出温度Td及气液分离温度Tm的控制与第一实施方式同样地，通过上游侧节流装置及下游侧节流装置的开度的调整来进行。In the first embodiment, the target gas-liquid separation temperature Tm1 is fixed, but in this embodiment, the estimated temperature Tm2 calculated using the calculation formula of the gas-liquid separation temperature corrected in step S23 is set as the target value. Gas-liquid separation temperature. The control of the discharge temperature Td and the gas-liquid separation temperature Tm is performed by adjusting the opening degrees of the upstream side throttling device and the downstream side throttling device, as in the first embodiment.
如此，在中间压控制运转中，对根据其他的温度计测点推定气液分离温度Tm的计算式进行修正，并将该修正后的计算式在稳定运转中使用，由此在稳定运转中也能够实现还考虑了温度传感器的测定误差等的更高精度的中间压控制。In this way, in the intermediate pressure control operation, by correcting the calculation formula for estimating the gas-liquid separation temperature Tm from other temperature measurement points, and using the corrected calculation formula in the steady operation, it is possible to Higher-precision intermediate pressure control that also takes into account measurement errors of the temperature sensor and the like is realized.
<变形例><Modification>
需要说明的是，在图8所示的流程图中，检测冷凝侧出口温度Tc及蒸发侧入口温度Te的步骤S21配置在步骤S7之后，但也可以将步骤S21配置在步骤S6与步骤S7之间，并且之后配置根据冷凝侧出口温度Tc及蒸发侧入口温度Te来确定目标的气液分离温度Tm3的步骤，在步骤S8中，在检测出的气液分离温度Tm与目标的气液分离温度Tm3之差较大时增大开度的调整量，而在其差较小时减小开度的调整量。It should be noted that, in the flowchart shown in FIG. 8 , the step S21 of detecting the outlet temperature Tc of the condensation side and the inlet temperature Te of the evaporation side is arranged after the step S7, but the step S21 can also be arranged between the steps S6 and S7. , and then configure the step of determining the target gas-liquid separation temperature Tm3 according to the condensation side outlet temperature Tc and the evaporation side inlet temperature Te. In step S8, the detected gas-liquid separation temperature Tm and the target gas-liquid separation temperature The adjustment amount of the opening degree is increased when the difference of Tm3 is large, and the adjustment amount of the opening degree is decreased when the difference is small.
另外，在步骤S10中，在确定目标的气液分离温度Tm1之际，也可以代替使用Tm0，而使用通过在步骤S23中修正后的计算式所获得的推定温度Tm2。In step S10, when determining the target gas-liquid separation temperature Tm1, instead of using Tm0, estimated temperature Tm2 obtained by the calculation formula corrected in step S23 may be used.
另外，第二实施方式的加热器24也能够进行与第一实施方式的变形例同样的变更。In addition, the heater 24 of the second embodiment can also be changed in the same way as the modified example of the first embodiment.
(其他的实施方式)(other embodiments)
需要说明的是，在所述实施方式中，在制冷剂回路1中设有四通阀32，而能够实现制冷和供暖的切换，但本发明的制冷循环装置也可以为制冷专用或者供暖专用。It should be noted that, in the above-described embodiment, the four-way valve 32 is provided in the refrigerant circuit 1 to realize switching between cooling and heating, but the refrigeration cycle device of the present invention may also be dedicated to cooling or heating.
【工业方面可利用性】【Industrial availability】
本发明的制冷循环装置可以作为供热水器、热水供暖器、制冷或者空调设备等的热泵装置来利用。The refrigerating cycle device of the present invention can be used as a heat pump device such as a water heater, a hot water heater, or refrigeration or air-conditioning equipment.
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2011148794 | 2011-07-05 | ||
| JP2011-148794 | 2011-07-05 | ||
| PCT/JP2012/004313WO2013005424A1 (en) | 2011-07-05 | 2012-07-03 | Refrigeration cycle device |
| Publication Number | Publication Date |
|---|---|
| CN103348197A CN103348197A (en) | 2013-10-09 |
| CN103348197Btrue CN103348197B (en) | 2016-02-10 |
| Application Number | Title | Priority Date | Filing Date |
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| CN201280007707.4AExpired - Fee RelatedCN103348197B (en) | 2011-07-05 | 2012-07-03 | Refrigerating circulatory device |
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