WO2021118153A1 - Dispositif de régulation de débit de fluide frigorigène circulant de pompe à chaleur à circuit de fluide frigorigène, et pompe à chaleur permettant de réguler efficacement le débit de fluide frigorigène circulant au moyen de ce dernier - Google Patents

Dispositif de régulation de débit de fluide frigorigène circulant de pompe à chaleur à circuit de fluide frigorigène, et pompe à chaleur permettant de réguler efficacement le débit de fluide frigorigène circulant au moyen de ce dernier Download PDF

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Publication number
WO2021118153A1
WO2021118153A1 PCT/KR2020/017455 KR2020017455W WO2021118153A1 WO 2021118153 A1 WO2021118153 A1 WO 2021118153A1 KR 2020017455 W KR2020017455 W KR 2020017455W WO 2021118153 A1 WO2021118153 A1 WO 2021118153A1
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Prior art keywords
refrigerant
temperature
compressor
flow
space
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PCT/KR2020/017455
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English (en)
Korean (ko)
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최창균
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최창균
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Publication of WO2021118153A1 publication Critical patent/WO2021118153A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B30/00—Heat pumps
    • F25B30/02—Heat pumps of the compression 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F25B41/34—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators
    • F25B41/35—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators by rotary motors, e.g. by stepping motors
    • 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
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/06—Details of flow restrictors or expansion valves
    • F25B2341/068—Expansion valves combined with a sensor
    • F25B2341/0683—Expansion valves combined with a sensor the sensor is disposed in the suction line and influenced by the temperature or the pressure of the suction gas
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion valves
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21151—Temperatures of a compressor or the drive means therefor at the suction side of the compressor
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

Definitions

  • Refrigerant circuit that absorbs heat from the atmosphere and evaporates refrigerant in spite of wide climate change from very low sub-zero temperature to zero temperature, cools with evaporation heat, and heats with condensation heat obtained by compressing and condensing evaporated refrigerant vapor It's about heat pumps.
  • electric vehicles that operate with electric motors do not have waste heat from combustion reaction, so they must be heated in winter with the condensation heat of the refrigerant and must have a refrigerant circuit heat pump that cools them with the evaporation heat of the refrigerant in the summer.
  • the refrigerant vapor flowing inside the evaporator pipe flows into the compressor sealing case in a saturated evaporation state and is generated due to the current flowing in the rotor and stator windings of the driving motor provided inside the compressor sealing case Absorbs all heat generated by the operation of the compressor inside the compressor sealing case, such as heat generated by the compressor and friction heat generated by the operation of the compressor, and evaporates, and the evaporated refrigerant vapor maintains a temperature lower than the atmospheric temperature, so there is no heat lost to the atmosphere, and the specific volume is When it is sucked into the compressor in the lowest complete gaseous state, the heat pump efficiency of the refrigerant circuit heat pump can be maintained at its best. From this point of view, it is about the technology to control the flow rate of the refrigerant circulating in the refrigerant circuit.
  • the conventional refrigerant circuit heat pump has an outdoor unit and an indoor unit, and the flow direction of the refrigerant between the outdoor unit and the indoor unit is opposite according to heating and cooling.
  • the refrigerant condensed in the outdoor unit 103 passes through the check valve 104 and the refrigerant vapor sucked into the compressor from the “constant temperature expansion valve 106” becomes overheated. to regulate
  • the refrigerant condensed in the indoor unit 108 passes through the check valve 107 and flows into the outdoor unit 103 to maintain the refrigerant vapor sucked into the compressor from the “constant temperature expansion valve 105” in an overheated state. Adjust the flow.
  • the temperature of the indoor space where people reside is maintained at 20-25°C, but the climate temperature of the atmosphere varies greatly depending on the season and region, from -40°C or less to 40°C or more.
  • the space 201 (referred to as a temperature-sensitive space) acting by temperature is separated and partitioned by a diaphragm 202, and the same evaporation pressure as the refrigerant used is applied to the space acting by the temperature of the refrigerant suction vapor of the compressor.
  • the saturated vapor pressure of the internal material expanded inside the temperature-sensitive bulb 211 by receiving the heat of the refrigerant vapor sucked into the compressor is conducted to maintain the saturated vapor state by filling the to the direction in which the air gap with the toilet seat 206 increases (the direction in which the valve opens), and the refrigerant gas pressure in the exhaust gas space 203 or the pressure of the refrigerant flowing inside the compressor suction pipe that is applied through the equalization pipe.
  • the pressure added with the elastic force of the spring 208 moves the body 207 of the expansion valve upward and acts in the direction in which the air gap of the toilet seat 206 decreases (the direction in which the valve is closed).
  • the adiabatic expansion refrigerant absorbs the heat of evaporation from the outside as it passes through the evaporation pipe, and the evaporated refrigerant vapor passes through the compressor suction line and conducts heat from the refrigerant vapor sucked into the compressor and evaporates.
  • the evaporation pressure (1) of the material inside a temperature-sensitive bulb acts as a force to open the valve.
  • the force (2+3) which is the pressure of the refrigerant vapor (2) plus the elastic force of the spring (3), acts as a force to close the valve.
  • the opening degree of the valve is determined according to the balance between the force to open the valve and the force to close the valve.
  • the refrigerant vapor pressure sucked into the compressor flows into the pressure2 by subtracting the elastic force3 of the spring from the saturated evaporation pressure corresponding to the temperature of the refrigerant vapor sucked into the compressor sealing case.
  • the pressure corresponding to the elastic force of the spring becomes the pressure obtained by superheating the refrigerant vapor.
  • the evaporation pressure of the refrigerant which changes according to the temperature, does not increase in proportion to the temperature.
  • the pressure change is low, and when the temperature rises, the pressure change is high.
  • the overheating temperature is obtained by the constant elastic force of the spring, so the overheating temperature 1 of the refrigerant vapor sucked into the compressor at temperature 1 is less than the overheating temperature 2 of the refrigerant steam sucked into the compressor at temperature 2.
  • the isothermal section of the saturated steam inside the evaporator increases when the atmospheric temperature increases and decreases when the atmospheric temperature decreases.
  • the specific volume of refrigerant vapor sucked into the compressor increases as the ambient temperature decreases.
  • the specific volume of the refrigerant vapor sucked into the compressor is minimal due to minimal overheating, the compression efficiency of the compressor is maximized, and as the specific volume increases, the compression efficiency decreases.
  • the heat pump efficiency is lowered accordingly.
  • the refrigerant vapor sucked into the compressor is always changed by the constant elastic force of the spring 208 to change the expansion valve. This is because the number of gas molecules in a certain volume of gaseous refrigerant vapor sucked into the compressor does not decrease in proportion to the increase in temperature, but decreases as the temperature decreases and increases as the temperature increases. .
  • the "constant temperature expansion valve" of the conventional refrigerant circuit heat pump does not take into account the change in atmospheric temperature and always sets the pressure as low as the elastic force of the constant spring, so the overheating temperature of the evaporator is reduced to 3
  • the elastic force of the spring In order to set the temperature to °C, the elastic force of the spring must be set to 0.6 atm. At this time, the change in the overheating temperature that changes according to the outside air temperature is
  • ⁇ Atmospheric temperature is -40°C ⁇ -30°C, 8°C
  • the liquid refrigerant inside the evaporator needs to be evaporated at a temperature lower than the atmospheric temperature in order to receive heat from the atmosphere around the evaporator, and the refrigerant vapor flowing inside the conduit of the evaporator is in a saturated evaporation state. Maximum heat is conducted from the outside air when maintaining the isothermal temperature of
  • the means to solve the technical problem of the present invention is not using the elastic force of the spring to obtain the superheat of the refrigerant vapor sucked into the compressor as in the conventional constant temperature expansion valve, but according to the outside temperature according to FIG.
  • the circulating refrigerant of the refrigerant circuit heat pump which controls the current flowing through the solenoid coil 520 manufactured as shown in FIG. 6 to always keep the superheat of the refrigerant vapor sucked into the compressor to a minimum despite the high and low outdoor temperature. It is to provide a flow control device, and also to propose a heat pump capable of efficiently controlling the flow rate of circulating refrigerant by using the circulating refrigerant flow control device of the refrigerant circuit heat pump.
  • the latent heat contained in the refrigerant vapor flowing into the compressor sealing case is the same as all heat generated by the operation of the compressor inside the compressor sealing case, such as electrical resistance heat and frictional heat of the winding of the compressor driving motor.
  • the refrigerant temperature inside the compressor sealing case is heated to a temperature lower than the ambient temperature around the compressor sealing case, eliminating heat lost to the outside air, and controlling the flow rate of liquid refrigerant flowing into the evaporator to be sucked into the compressor with a minimum specific volume. It is a means to solve the technical problem of the present invention.
  • the power energy supplied for the operation of the compressor is absorbed into the circulating refrigerant without being lost to the atmosphere through the compressor sealing case, and is converted into heating heat, and the refrigerant that is sucked into the compressor As the vapor is sucked into the compressor with the minimum specific volume, the compression efficiency has the effect of improving the compression efficiency from the conventional compression curve 1 to the compression curve 2 as shown in FIG.
  • FIG. 1 Schematic diagram of a conventional refrigerant circuit heat pump
  • Figure 2 Configuration diagram of a conventional constant temperature expansion valve
  • FIG. 3 Schematic diagram of the principle of operation of a conventional constant temperature expansion valve
  • Figure 4 Superheat temperature distribution diagram of a conventional evaporator in which the degree of superheat of refrigerant vapor sucked into the compressor is changed according to the atmospheric temperature.
  • FIG. 5 Configuration diagram according to an embodiment of the flow control device according to the invention
  • Figure 6 Cross-sectional view of the flow control device for controlling the flow rate of the circulating refrigerant according to the invention
  • Figure 7 Standard diagram of the valve body and the valve seat in which the opening degree of the flow path is proportional to the displacement of the valve body of the flow control device according to the invention
  • FIG. 9 schematic diagram showing the operating principle of the flow control device according to the invention
  • compression curve 1 Compression curve 1
  • compression curve 2 Compression curve 2
  • refrigerant outlet 206 toilet seat (Valve seat)
  • valve body 531 valve seat
  • the present invention provides a refrigerant flow during heating and cooling by 'one electronic flow control device' having four check valves (check valves 1 to 4) as shown in FIG. 5 .
  • check valves 1 to 4 check valves 1 to 4
  • the flow control device includes a temperature-sensitive bulb 510 that responds to the temperature of refrigerant vapor flowing inside the compressor suction pipe, and a pressure equalization space 516 connected to the compressor suction pipe by an equalizing pipe 517 and , a lower portion of the pressure equalization space 516 is partitioned by a diaphragm 515 and connected to the temperature-sensitive bulb 510 by a connecting capillary 512.
  • a diaphragm lower space 514 (referred to as a temperature-sensitive space);
  • the first inlet and outlet 532 are the inlet of the refrigerant during heating and the outlet of the refrigerant during cooling, the second inlet 533 which is the inlet of the refrigerant during cooling and the outlet of the refrigerant during heating, and the first inlet and outlet 532 ) or a fluid space 534 in which the refrigerant introduced into the second inlet and outlet 533 stays, a flow rate control space 540 connected to the lower part of the fluid space through a flow path, and the elevating and descending force of the diaphragm 515 and A variable body 530 that opens and closes the flow path by the magnetic force of a solenoid coil, a first check valve CV1 that enables a refrigerant flow from the first inlet and outlet 532 to the infusion space 534, and the flow rate control A second check valve (CV2) that enables a refrigerant flow from the space (540) to the first
  • the "one electronic flow control device” configured in this way includes a pressure equalization space 516 that responds to the pressure of refrigerant vapor flowing inside the compressor suction pipe path, and a temperature sensitive space 514 that responds to the temperature of refrigerant vapor flowing inside the compressor suction pipe path.
  • a solenoid coil 520 that generates a force in proportion to the strength of the flowing current
  • the flow control device is opened to increase the flow rate, and the inside of the compressor suction pipe path
  • the flow rate control device is closed.
  • the temperature-sensitive material of the temperature-sensitive bulb 510 which is in contact with the compressor suction pipe surface and responds to the temperature of refrigerant vapor sucked into the compressor sealing case, is converted into a refrigerant in the refrigerant circuit heat pump. It is the same refrigerant used,
  • the temperature sensitive bulb 510 is connected to the inlet 511, the diaphragm lower space 513, the connecting capillary 512, and the outlet 513 to form one temperature sensitive space, and the outlet 513 is a valve (Fig. is connected to a vacuum pump (not shown in the drawing) through a vacuum pump (not shown in the drawing), and the inlet 511 is connected to a refrigerant storage container (not shown in the drawing) through another valve (not shown). do.
  • the refrigerant inside the temperature sensitive bulb 510 installed in close contact with the external surface of the compressor suction pipe path is evaporated by receiving heat from the refrigerant vapor temperature flowing inside the suction pipe path, and saturated evaporation of the refrigerant inside the evaporated temperature sensitive bulb 510 .
  • the pressure pushes the diaphragm 515 upward from the lower part of the diaphragm 515 to act in a direction to open the variable body 530 connected to the diaphragm 515,
  • the pressure equalization space 516 above the diaphragm 515 is connected to the compressor suction line in which the temperature sensitive bulb 510 is located through the pressure equalization tube 517, the pressure of the refrigerant vapor sucked into the compressor is the pressure equalization tube ( 517) to push the diaphragm down from the upper part of the diaphragm 515 and act in a direction to close the variable body 530 connected to the diaphragm,
  • the magnetic force generated as the current flows in the solenoid coil 520 attracts the armature 521 connected to the variable body 530 of the flow control device according to the present invention to the center of the solenoid coil 520, so by this force It acts in a direction to close the flow path of the circulating refrigerant by pushing the variable body 530 downward.
  • the force to close the body of the flow control device and the force to open the body by the saturated evaporation pressure of the refrigerant evaporated inside the temperature-sensitive bulb 510 are balanced with each other.
  • the variable body 530 is stopped at a position forming
  • the refrigerant vapor flowing into the "first inlet/outlet 532 which is an inlet in the case of heating and an outlet in the case of cooling," passes through the check valve 1 (CV1), and is a liquid refrigerant having a large specific gravity in the receiving space 534. is pooled downward, and the accumulated liquid refrigerant flows through the flow path (gap) between the valve body 530 and the valve seat 531 to the flow rate control space 540 .
  • the refrigerant vapor that has passed through the flow control space 540 passes through the check valve CV4, passes through the "second inlet and outlet 533", flows into the evaporator, absorbs heat from the atmosphere, evaporates, and is in an atomized state that has not yet evaporated. It flows into the compressor sealing case together with the refrigerant vapor.
  • the second inlet and outlet 533 corresponds to an inlet in the case of cooling and an outlet in the case of heating.
  • the latent heat contained in the refrigerant vapor in the atomized state flowing into the compressor sealing case causes the electric current to flow in the stator winding and the rotor winding as the motor driving the compressor is operated inside the case sealing the compressor, thereby reducing the electrical resistance heat and the compressor.
  • the flow rate of the liquid refrigerant flowing into the evaporator so that it absorbs all the mechanical frictional heat generated during operation and evaporates to a temperature lower than the ambient temperature and slightly overheated, and the current flowing through the solenoid coil 520 of the flow control device.
  • the flow path (gap) cross-sectional area between the body 530 and the toilet seat 531 is that of the body.
  • the opening degree of the flow path increases or decreases in proportion to the vertical movement distance of the body.
  • the flow control device configured in this way is placed between the outdoor unit and the indoor unit, and temperatures are sensed at six locations as follows.
  • T3 surface temperature of the refrigerant suction pipe between the "four sides" and the temperature sensitive bulb 510
  • T4 Pipe surface temperature at the point where the compressor suction pipe and the compressor sealing case meet
  • T5 Surface temperature of the refrigerant pipe at the outlet of the outdoor unit
  • T6 Surface temperature of the refrigerant pipe at the outlet of the indoor unit
  • the temperature signal detected by the six temperature sensors (T1 to T6) is input to the main controller 800 of the refrigerant circuit heat pump, and the driving power of the motor driving the compressor is the inverter (INV1) and the outdoor unit cooling blower (FM1). )
  • the driving power is supplied through the inverter INV2, and the driving power of the indoor unit cooling blower FM2 is supplied through the inverter INV3, respectively.
  • each inverter INV and the current value supplied to the solenoid coil 520 are calculated according to the temperature signals sensed by the six temperature sensors T1 to T6. 800) is provided.
  • the main controller 800 of the refrigerant circuit heat pump is
  • the physical properties of the refrigerant including the temperature, pressure, specific volume, state heat, and latent heat of the refrigerant, are stored in the form of software and receive the temperature signals from the six
  • the operating frequency of the inverter (INV1) that supplies power to the motor driving the compressor is set and commanded to the inverter (INV1).
  • ⁇ Controls the current flowing in the solenoid coil 520 of the flow control device that controls the flow rate of the refrigerant flowing into the evaporator.
  • Both the cooling load ( ⁇ ) and the heating load ( ⁇ ) increase or decrease in proportion to the difference between the outdoor temperature (T1) and the indoor temperature (T2).
  • the "latent heat of evaporation per unit mass" of the refrigerant increases as the temperature decreases and decreases as the temperature increases according to the change of the outside temperature.
  • the saturated evaporation pressure inside the temperature sensitive space 514 by heat conducted from the temperature of the refrigerant vapor sucked into the compressor acts as a force to open the flow path of the flow control device
  • the magnetic force acting on the armature 521 is added by controlling the current flowing through the solenoid coil 520 to compensate for the change in the force caused by the evaporation pressure of the refrigerant sucked into the compressor and the “latent heat of evaporation per unit mass” of the refrigerant. 'Resultant force' acts as a force to close the flow path of the flow control device,
  • the displacement of the body 530 of the flow control device according to the present invention is determined, and the opening degree of the flow path is adjusted according to the displacement of the body 530, so that the refrigerant flowing into the evaporator volume is automatically controlled.
  • Refrigerant vapor in a saturated state has a constant temperature when the pressure is constant. Therefore, since it is not possible to know the evaporation state (dry humidity) of the refrigerant vapor only by measuring the temperature in one place of the compressor suction pipe, the temperature sensitive bulb 510 attached to the middle of the compressor suction pipe connected from all sides to the compressor sealing case 110. Based on the position, temperature sensors T3 and T4 are attached to the front and rear ends of the compressor suction pipe, respectively, the difference between the two temperature values is measured, and the solenoid coil 520 according to the difference between the set temperature values.
  • the current flowing in the solenoid coil 520 is reduced to increase the refrigerant flow flowing through the flow control device, and when the difference in the temperature value between the two places is small, the solenoid coil By increasing the current flowing through the 520, the flow rate of the refrigerant flowing through the flow control device is decreased.
  • the increase or decrease of the current flowing through the solenoid coil 520 is determined by the difference between the temperature values T3 and T4 at the two places, and the difference between the temperature values T3 and T4 at the two places.
  • the evaporator absorbs heat from the outside air and changes depending on the evaporation state (dry humidity) of the evaporated refrigerant vapor.
  • T3 when the temperature of T3 receives the heat of evaporation from outside air and absorbs the latent heat of evaporation of the refrigerant vapor flowing inside the evaporator pipe, a constant saturated evaporation temperature is always maintained, while the compressor sealing case 110 and the refrigerant vapor are introduced into the suction pipe.
  • the temperature (T4) at the junction of the compressor is the resistance heat caused by the current generated by the flow of current in the armature winding and the stator winding of the motor driving the compressor, mechanical friction heat generated by the operation of the compressor, and heat conducted from outside air, the compressor It is the temperature that is changed by the heat conducted by the refrigerant vapor flowing into the sealing case.
  • the temperature T3 is the saturated evaporation temperature of the refrigerant vapor evaporated by conducting heat from the outside air in the evaporator
  • the temperature T4 is the heat generated by the operation of the compressor in the compressor sealing case, which is conducted from the compressor sealing case 110. is the temperature
  • the refrigerant flow rate is adjusted according to the value of the temperature difference (T4-T3) between the two places, the amount of refrigerant particles in the liquid phase that has not evaporated contained in the refrigerant vapor flowing into the compressor sealing case 110 is controlled. It is possible to control the degree of superheat of the refrigerant vapor sucked into the compressor from the inside.
  • the noise generated when the compressor is operating is caused by particles of incompressible liquid contained in the refrigerant vapor, and the power supplied to the compressor driving motor changes according to the specific volume of the refrigerant vapor. Therefore, if the value of the temperature difference (T4-T3) between the two places is changed during operation, the noise and the power supplied to the compressor change at the same time.
  • the refrigerant vapor sucked into the compressor is the refrigerant vapor in an ideal gas state without latent heat, and the specific volume is the minimum.
  • the value of the temperature difference (T4-T3) between the two places at this moment is approximately 2°C or less, and the superheated temperature of the refrigerant vapor sucked into the compressor is 2°C or more. Since the temperature (T3, T4) of the two places is simultaneously changed as the outside air temperature is changed after being sucked in, the value of the temperature difference (T4-T3) between the two places does not change.
  • the current flowing through the solenoid coil 520 is controlled according to the change of the outside temperature to control the refrigerant flow rate flowing into the evaporator.
  • the changed refrigerant flow rate is always absorbed by the compressor by absorbing all the heat generated by the operation of the compressor inside the compressor sealing case.
  • the temperature of the refrigerant sucked into the furnace is lower than the outside temperature, and the refrigerant vapor is a superheated gas with no latent heat and is sucked into the compressor with the smallest specific volume, so that the compression efficiency of the compressor can be maintained at its best.
  • temperature sensors T3 and T4 are attached to the front and rear ends of the compressor suction line, respectively, to measure the temperature of the two places, respectively, and By controlling the current flowing in the solenoid coil 520 of the flow control device according to the value of the temperature difference (T4-T3) of the two places, the value of the temperature difference (T4-T3) of the two places can be kept constant,
  • the flow rate of the refrigerant flowing into the compressor sealing case is controlled despite the change in the latent heat of the refrigerant that is changed according to the change in the outside temperature to control the compressor sealing case.
  • T4-T3 the temperature difference between the two places

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air Conditioning Control Device (AREA)
  • Control Of Positive-Displacement Pumps (AREA)

Abstract

Dans les pompes à chaleur classiques, les sens d'écoulement de fluide frigorigène entre une unité extérieure et une unité intérieure pendant un chauffage et un refroidissement sont contraires l'un à l'autre. Ainsi, pour chaque cas, deux espaces de fluide, deux clapets anti-retour et deux vannes de détente à température constante sont prévus pour réguler la pression d'évaporation d'un fluide frigorigène. Dans ce cas, pour réguler une température de surchauffe, les vannes de détente à température constante commandent la force élastique d'un ressort (208) par rotation d'une vis (209), ce qui permet de réguler la température de surchauffe de vapeur de fluide frigorigène aspirée dans un compresseur. Cependant, tous les fluides frigorigènes ont des caractéristiques selon lesquelles une variation de pression en fonction d'une variation de température n'est pas constante, la variation de pression en fonction d'une variation de température est faible à basse température, et la variation de pression en fonction d'une variation de température est élevée à haute température. Pour surmonter les propriétés physiques de tels fluides frigorigènes, la présente invention concerne un moyen permettant d'augmenter au maximum l'efficacité de compression d'un compresseur en réduisant au minimum le volume spécifique de vapeur de fluide frigorigène aspirée dans le compresseur en maintenant en permanence une température de surchauffe constante en dépit d'une variation de la température d'air extérieur, et un appareil de mise en œuvre du moyen.
PCT/KR2020/017455 2019-12-11 2020-12-02 Dispositif de régulation de débit de fluide frigorigène circulant de pompe à chaleur à circuit de fluide frigorigène, et pompe à chaleur permettant de réguler efficacement le débit de fluide frigorigène circulant au moyen de ce dernier WO2021118153A1 (fr)

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KR10-2019-0164290 2019-12-11
KR1020190164290A KR102171577B1 (ko) 2019-12-11 2019-12-11 냉매회로 열펌프의 순환냉매 유량조절장치 및 이를 이용하여 순환냉매의 효율적 유량제어가 가능한 히트펌프

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WO2021118153A1 true WO2021118153A1 (fr) 2021-06-17

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KR102171577B1 (ko) * 2019-12-11 2020-10-29 최창균 냉매회로 열펌프의 순환냉매 유량조절장치 및 이를 이용하여 순환냉매의 효율적 유량제어가 가능한 히트펌프

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KR880003185U (ko) * 1986-07-08 1988-04-11 주식회사 금성사 광 픽업 구동장치
JP2004309081A (ja) * 2003-04-10 2004-11-04 Tgk Co Ltd 膨張弁およびその制御方法
JP2012082972A (ja) * 2010-10-06 2012-04-26 Tgk Co Ltd 膨張装置
JP2017026191A (ja) * 2015-07-17 2017-02-02 株式会社鷺宮製作所 温度膨張弁及び冷凍サイクル
US20190323748A1 (en) * 2016-05-11 2019-10-24 Danfoss A/S Insert for a thermostatic expansion valve, thermostatic expansion valve and method for assembling a thermostatic expansion valve
KR102171577B1 (ko) * 2019-12-11 2020-10-29 최창균 냉매회로 열펌프의 순환냉매 유량조절장치 및 이를 이용하여 순환냉매의 효율적 유량제어가 가능한 히트펌프

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KR880003185U (ko) * 1986-07-08 1988-04-11 주식회사 금성사 광 픽업 구동장치
JP2004309081A (ja) * 2003-04-10 2004-11-04 Tgk Co Ltd 膨張弁およびその制御方法
JP2012082972A (ja) * 2010-10-06 2012-04-26 Tgk Co Ltd 膨張装置
JP2017026191A (ja) * 2015-07-17 2017-02-02 株式会社鷺宮製作所 温度膨張弁及び冷凍サイクル
US20190323748A1 (en) * 2016-05-11 2019-10-24 Danfoss A/S Insert for a thermostatic expansion valve, thermostatic expansion valve and method for assembling a thermostatic expansion valve
KR102171577B1 (ko) * 2019-12-11 2020-10-29 최창균 냉매회로 열펌프의 순환냉매 유량조절장치 및 이를 이용하여 순환냉매의 효율적 유량제어가 가능한 히트펌프

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