US20140290294A1 - Air heating unit of the air-conditioning - Google Patents
Air heating unit of the air-conditioning Download PDFInfo
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- US20140290294A1 US20140290294A1 US13/851,855 US201313851855A US2014290294A1 US 20140290294 A1 US20140290294 A1 US 20140290294A1 US 201313851855 A US201313851855 A US 201313851855A US 2014290294 A1 US2014290294 A1 US 2014290294A1
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- tube
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- temperature
- liquid refrigerant
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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
- F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
- F25B29/003—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously of the compression type system
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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
- F25B30/00—Heat pumps
- F25B30/02—Heat pumps of the compression type
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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
- F25B40/00—Subcoolers, desuperheaters or superheaters
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/37—Capillary tubes
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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
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/05—Compression system with heat exchange between particular parts of the system
- F25B2400/052—Compression system with heat exchange between particular parts of the system between the capillary tube and another part of the refrigeration cycle
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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
- F25B2600/00—Control issues
- F25B2600/11—Fan speed control
- F25B2600/111—Fan speed control of condenser fans
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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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2116—Temperatures of a condenser
- F25B2700/21163—Temperatures of a condenser of the refrigerant at the outlet of the condenser
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- 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
- the present invention relates to an air heating unit of the air-conditioning, and more particularly to the air heating unit of the air-conditioning has designed with no evaporator.
- Conventional air-conditioning equipment generally includes four basic item of device, respectively: an evaporator, a compressor, a condenser and a thermal expansion valve, and the four major item of device are connected sequentially with one another by a pipeline to define a refrigeration cycle.
- a low-pressure low-temperature refrigerant absorbs heat to produce a refrigeration effect in the evaporator.
- the high-pressure high-temperature gaseous refrigerant is discharged through a discharge line into the condenser for heat exchange to produce a heating effect.
- air passes through the condenser to increase the temperature of air, so that the high-pressure high-temperature gaseous refrigerant becomes liquid, and the high-pressure liquid refrigerant enters a thermal expansion device through a liquid line, and the thermal expansion device controls the flow of the refrigerant and disperses the liquid refrigerant into the evaporator in low pressure, low temperature mist refrigerant to absorb heat to provide a cooling effect in the evaporator and a heating effect in the condenser.
- the aforementioned air-conditioning equipment has a different name according to different functions, such as an air-conditioner, a heat pump, a refrigerator, and a dehumidifier, etc.
- the dehumidifier introduces air into the evaporator to dehumidify the air and lower the temperature, and then absorb heat from the condenser, so that the discharged air has a higher temperature and a lower enthalpy than the intake air, and thus the dehumidifier is considered as an air-conditioning equipment with the dehumidification and heating effect.
- the evaporator is a necessary device to evaporate the refrigerant into a low-pressure low-temperature gaseous refrigerant, a heat pump for example, in a low-temperature environment, the refrigerant in outdoor evaporator cannot absorb enough heat from the cold temperature environment, but is absorbed from compressor, and the crank case of the compressor will freeze, so cannot generate compression heat. Since the heat pump cannot function right in severe cold weather, therefore most of them require electric heating elements to produce an indoor heating effect. However, the high temperature of the electric heating elements causes an oxygen burning phenomenon, and thus requires improvements.
- One primary objective of the present invention is to provide an air heating unit of the air-conditioning that eliminates the device-evaporator, so that the operation of the air heating unit is not limited by cold weathers to provide the indoor heating effect in a severe cold weather.
- Another objective of the present invention is to provide an air heating unit of the air-conditioning, wherein the compression heat generated by the compressor is discharged through the condenser, the indoor air temperature is increased, and the indoor moisture is dehumidified, so that there is no longer any issue of the oxygen burning phenomenon.
- the present invention provides an air heating unit of the air-conditioning, comprising: a compressor, with a discharge end coupled to a first link tube line provided for high-pressure high-temperature gaseous refrigerant and oil; a thermal compensation device, having an inner tube, a mid tube and an outer tube of different diameters, the mid tube being sheathed with the outer tube therein, and the inner tube being sheathed with the mid tube therein to form a tri-tubing structure of thermal compensation device, and an output end of the first link tube line being coupled to the inner and outer tubes, for facilitating the high-pressure high-temperature gaseous refrigerant charged into the inner and outer tubes, and an output end of the inner and outer tubes being coupled to a second link tube line for flowing the high-pressure high-temperature gaseous refrigerant and oil; an air cooled condenser, including an internal condenser coil installed therein and having an intake end coupled to an output end of the second link tube line, a fan installed
- FIG. 1 is a schematic view illustrating the pipeline layout of an air heating unit of the air-conditioning to the present invention
- FIG. 2 is a schematic view illustrating the refrigerant flowing direction of an air heating unit of the air-conditioning to the present invention.
- FIG. 3 is a cross-sectional view of a thermal compensation device to the present invention.
- the air heating unit comprises a compressor 1 , a thermal compensation device 2 , an air cooled condenser 3 , and four link tube lines 4 , 5 , 6 , 7 .
- the compressor 1 is a prior art, such as an electric motor, e.g. used as a motive power to facilitate a low-pressure low-temperature gaseous refrigerant such as the 134 A refrigerant and a lubricating oil (hereinafter referred to as “oil”) contained in the compressor 1 is compressed into a high-pressure high-temperature gaseous refrigerant.
- a low-pressure low-temperature gaseous refrigerant such as the 134 A refrigerant and a lubricating oil (hereinafter referred to as “oil”) contained in the compressor 1 is compressed into a high-pressure high-temperature gaseous refrigerant.
- the gaseous refrigerant and oil at approximately 107 Celsius degree moves (in a direction as indicated by the arrows in the figures) from a discharge end 11 of the compressor 1 into the first link tube line 4 .
- an intake end of the first link tube line 4 is coupled to the discharge end 11 of the compressor 1
- the thermal compensation device 2 is a tri-tubing structure formed by sheathing an inner tube 21 into a mid tube 22 , and the mid tube 22 into an outer tube 23 .
- the inner tube 21 , the mid tube 22 and the outer tube 23 are made of metal such as copper or a copper alloy and have different diameters such as 3 ⁇ 8′′, 1 ⁇ 2′′ and 3 ⁇ 4′′ inches respectively.
- Intake and output ends of the inner tube 21 and the outer tube 23 are coupled to a double-fork shunt tube 24 and a manifold tube 25 respectively to branch the aforementioned high-pressure high-temperature gaseous refrigerant and oil by the shunt tube 24 to enter and flow in the inner tube 21 and the outer tube 23 , so that the high-pressure high-temperature gaseous refrigerant in the inner tube 21 and the outer tube 23 flows respectively through a condenser 3 back to the mid tube 22 to compensate heat with the fast-flowing high-pressure intermediate-temperature liquid refrigerant, so as to perform a heat transfer to the liquid refrigerant.
- the high-temperature gaseous refrigerant collected by the manifold tube 25 flows towards a second link tube line 5 , and the temperature of the high-temperature gaseous refrigerant flowing in the second link tube line 5 drops slightly to approximately 103 Celsius degree.
- An intake end of second link tube line 5 is coupled to the manifold tube 25 , and an output end of the second link tube line 5 is coupled to the bottom inlet of air cooled condenser 3 and the condenser coil 31 are in series connection to provide the high-temperature gaseous refrigerant and oil to enter.
- a conventional fan 32 is provided and the condenser coil 31 is surrounded by a plurality of heat dissipation fins (prior art, not shown in the present invention) to achieve the heat dissipate and condensed effects, so that the high-pressure high-temperature gaseous refrigerant saturated in the condenser coil 31 is cooled to change its state into liquid with high-pressure intermediate-temperature containing bubbles of super heat, and the condensed liquid refrigerant and oil flow out from the output end of condenser coil 31 at the top of the condenser 3 and discharged into a third link tube line 6 . Since the liquid refrigerant charged to the condenser coil 31 is full saturated and satisfied, the heat saturation effect can be achieved effectively.
- the third link tube line 6 is attached with a thermostat sensor 61 , such that if the temperature of the liquid refrigerant passing through the third link tube line 6 detected by the thermostat sensor 61 reaches a predetermined limitation of temperature such as 75 Celsius degree, the fan 32 will be turned on immediately to blow air to the condenser 3 to dissipate the heat of the condenser 3 and turn the air passing through the condenser 3 into hot air for the indoor heating purpose. If the temperature of the liquid refrigerant passing through third link tube line 6 detected by the thermostat sensor 61 is lower than the predetermined thermostat temperature such as 75 Celsius degree, the fan 32 will be turned off immediately to stop blowing air to the condenser 3 . The control with the predetermined temperature of the thermostat sensor 61 keeps the fan 32 to blow air to the condenser 3 intermittently and turn the air passing through the condenser 3 into hot air to achieve an indoor heating effect.
- a predetermined limitation of temperature such as 75 Celsius degree
- the gaseous refrigerant enters from the bottom inlet of the condenser 3 and condensed into liquid refrigerant then flows out from the outlet in top of the condenser 3 , and such arrangement has the following advantage.
- the high-temperature gaseous refrigerant is impacted and mixed with the intermediate-temperature liquid refrigerant in the condenser coil 31 , so that the liquid refrigerant receives the heat of the super heat of gaseous refrigerant to expedite the liquefaction of the gaseous refrigerant, and a large quantity of liquefied refrigerant can be saturated and satisfied in the condenser coil 31 to achieve a heat saturation effect effectively.
- third link tube line 6 is coupled to the mid tube 22 of the thermal compensation device 2 , such that the intermediate-temperature liquid refrigerant, oil and bubbles of super heat flowing into third link tube line 6 flows towards the mid tube 22 . Since the diameters (or sizes) of the mid tube 22 and the inner tube 21 is 1 ⁇ 2′′ and 3 ⁇ 8′′ inches respectively, therefore the gap in between is very small so as to leave a capillary gap and achieve a kind of capillary tube effect.
- the intermediate-temperature liquid refrigerant flowing in the mid tube 22 perform heat transfer with the high-temperature gaseous refrigerant flowing in the inner tube 21 and the outer tube 23 , so that the liquid refrigerant is expanded by heat gain, and thus bubbles of super heat are blocked outside the inlet capillary gap 26 between the mid tube 22 and the inner tube 21 to achieve the flow restrained effect similar to an expansion valve or a capillary tube.
- the liquid refrigerant and oil are not containing any bubbles of super heat flowing out from the output end of the mid tube 22 enters into a fourth link tube line 7 . Since the fourth link tube line 7 has a diameter greater than the outlet capillary gap 27 between the mid tube 22 and the inner tube 21 , therefore when the intermediate-temperature liquid refrigerant are not containing bubbles of super heat enters and flows into fourth link tube line 7 , the pressure is depressed at once and the temperature is lowered to form a low-pressure intermediate-temperature unsaturated liquid refrigerant flowing, and measurements shows that the temperature of the liquid refrigerant of fourth link tube line 7 is 68 Celsius degree.
- fourth line tube line 7 is coupled to a conventional liquid-gas separator 8 accomplished with the compressor 1 , and the internal diameter of the liquid-gas separator 8 is greater than fourth link tube line 7 for many times.
- suitable temperature such as a liquid refrigerant at approximately 38 Celsius degree. This temperature will not lower as the refrigeration effect like the lubricating oil passing through the evaporator does, such that the lubricating oil is in a sticky form which is unfavorable for the lubrication of the compressor.
- the present invention has the following advantages.
- the high-temperature gaseous refrigerant flowing in the inner and outer tubes of the thermal compensation device transfers heat with the intermediate-temperature liquid refrigerant flowing in the mid tube, so that the liquid refrigerant flowing into the inlet of capillary gap between the mid tube and the inner tube is heated up to expand to achieve the flow restrained effect, and the inlet of capillary gap can stop bubbles of super heat from entering, and suppress the amount of liquid refrigerant to pass through. Therefore, a limited quantity of refrigerant can be sucked into the compressor at a low pressure without having the lubricating oil to return cooled.
- the present invention eliminates the use of the evaporator or flow restrained device, such that the compressor is the only heat generate device in the air heating unit of the air-conditioning.
- the air heating unit of the air-conditioning does not have evaporator, so that its indoor application is not limited by weathers, even in a severe cold weather outdoor.
- this air heating unit of the present invention is one of the innovative greatest designs of this sort.
Abstract
The present invention relates to an air heating unit of the air-conditioning including a compressor, a thermal compensation device and an air cooled condenser connected sequentially with one another by pipeline to define a refrigeration cycle. A high-temperature gaseous refrigerant flowing in inner and outer tubes of the thermal compensation device performs transfers heat with an intermediate-temperature liquid refrigerant flowing in mid tube, so that temperature of a liquid refrigerant flowing in a capillary gap between mid and inner tubes is increased to achieve liquid expand and flow restrained effects. The capillary gap can block bubbles of super heat from entering and suppress the liquid refrigerant from flowing through. Thus, a limited amount of liquid refrigerant can be sucked into the compressor at a low pressure without having lubricating oil to be turned cold. This air heating unit eliminates the use of evaporators other than in a conventional refrigeration system.
Description
- The present invention relates to an air heating unit of the air-conditioning, and more particularly to the air heating unit of the air-conditioning has designed with no evaporator.
- Conventional air-conditioning equipment generally includes four basic item of device, respectively: an evaporator, a compressor, a condenser and a thermal expansion valve, and the four major item of device are connected sequentially with one another by a pipeline to define a refrigeration cycle.
- According to the operation principle of the conventional air-conditioning equipment, a low-pressure low-temperature refrigerant absorbs heat to produce a refrigeration effect in the evaporator. In other words, air blows through the evaporator to lower the temperature of air, and the refrigerant is evaporated to form a low-pressure low-temperature gaseous refrigerant, and then sucked back to the compressor through a suction line and discharged to become a high-pressure and high-temperature gaseous.
- The high-pressure high-temperature gaseous refrigerant is discharged through a discharge line into the condenser for heat exchange to produce a heating effect. In other words, air passes through the condenser to increase the temperature of air, so that the high-pressure high-temperature gaseous refrigerant becomes liquid, and the high-pressure liquid refrigerant enters a thermal expansion device through a liquid line, and the thermal expansion device controls the flow of the refrigerant and disperses the liquid refrigerant into the evaporator in low pressure, low temperature mist refrigerant to absorb heat to provide a cooling effect in the evaporator and a heating effect in the condenser.
- The aforementioned air-conditioning equipment has a different name according to different functions, such as an air-conditioner, a heat pump, a refrigerator, and a dehumidifier, etc. For example, the dehumidifier introduces air into the evaporator to dehumidify the air and lower the temperature, and then absorb heat from the condenser, so that the discharged air has a higher temperature and a lower enthalpy than the intake air, and thus the dehumidifier is considered as an air-conditioning equipment with the dehumidification and heating effect.
- In view of the aforementioned air-conditioning equipments, the evaporator is a necessary device to evaporate the refrigerant into a low-pressure low-temperature gaseous refrigerant, a heat pump for example, in a low-temperature environment, the refrigerant in outdoor evaporator cannot absorb enough heat from the cold temperature environment, but is absorbed from compressor, and the crank case of the compressor will freeze, so cannot generate compression heat. Since the heat pump cannot function right in severe cold weather, therefore most of them require electric heating elements to produce an indoor heating effect. However, the high temperature of the electric heating elements causes an oxygen burning phenomenon, and thus requires improvements.
- One primary objective of the present invention is to provide an air heating unit of the air-conditioning that eliminates the device-evaporator, so that the operation of the air heating unit is not limited by cold weathers to provide the indoor heating effect in a severe cold weather.
- Another objective of the present invention is to provide an air heating unit of the air-conditioning, wherein the compression heat generated by the compressor is discharged through the condenser, the indoor air temperature is increased, and the indoor moisture is dehumidified, so that there is no longer any issue of the oxygen burning phenomenon.
- To achieve the aforementioned objective, the present invention provides an air heating unit of the air-conditioning, comprising: a compressor, with a discharge end coupled to a first link tube line provided for high-pressure high-temperature gaseous refrigerant and oil; a thermal compensation device, having an inner tube, a mid tube and an outer tube of different diameters, the mid tube being sheathed with the outer tube therein, and the inner tube being sheathed with the mid tube therein to form a tri-tubing structure of thermal compensation device, and an output end of the first link tube line being coupled to the inner and outer tubes, for facilitating the high-pressure high-temperature gaseous refrigerant charged into the inner and outer tubes, and an output end of the inner and outer tubes being coupled to a second link tube line for flowing the high-pressure high-temperature gaseous refrigerant and oil; an air cooled condenser, including an internal condenser coil installed therein and having an intake end coupled to an output end of the second link tube line, a fan installed outside the air cooled condenser, such that the high-pressure high-temperature gaseous refrigerant entering into the condenser coil to change state to form a high-pressure intermediate-temperature liquid refrigerant by air blow, and the condensed liquid refrigerant and oil still containing bubbles of super heat inside output end of the condenser coil enter into a third link tube line, in which a thermostat sensor attached thereon for measuring and detecting the liquid refrigerant reaches a predetermined limitation of temperature to control the fan to be turned on or off, and the fan is operated in intermittently to blow air to the condenser for heating once; and the mid tube, having an intake end linked to the third link tube line and an output end coupled to a fourth link tube line respectively, such that the intermediate-temperature liquid refrigerant flowing and passing through mid tube performs a heat exchange respectively with the high-temperature gaseous refrigerant flowing in the inner tube and the outer tube, and the intermediate-temperature of liquid refrigerant is expanded by heat gain so do the pressure is increased, and the bubbles of super heat in the liquid refrigerant are blocked outside the inlet of capillary gap between the mid tube and the inner tube; the liquid refrigerant and oil containing no bubbles of super heat flowing out from the outlet of capillary gap between the mid tube and the inner tube flows and enters into the fourth link tube line, the high pressure is depressed at once and the temperature is lowered to become unsaturated liquid refrigerant flowing; and an output end of the fourth link tube line being coupled to a liquid-gas separator to disperse the unsaturated liquid refrigerant into it. In order to drop the pressure and the temperature again inside liquid-gas separator to form low-pressure suitable temperature, the low-pressure suitable temperature liquid refrigerant and oil are sucked from a suction end of the compressor to define a refrigeration cycle.
- The technical characteristics, contents, advantages and effects of the present invention will be apparent with the detailed description of a preferred embodiment accompanied with the illustration of related drawings as follows.
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FIG. 1 is a schematic view illustrating the pipeline layout of an air heating unit of the air-conditioning to the present invention; -
FIG. 2 is a schematic view illustrating the refrigerant flowing direction of an air heating unit of the air-conditioning to the present invention; and -
FIG. 3 is a cross-sectional view of a thermal compensation device to the present invention. - With reference to
FIG. 1 toFIG. 3 for the air heating unit of the air-conditioning in accordance with the present invention, the air heating unit comprises a compressor 1, athermal compensation device 2, an air cooledcondenser 3, and fourlink tube lines - The compressor 1 is a prior art, such as an electric motor, e.g. used as a motive power to facilitate a low-pressure low-temperature gaseous refrigerant such as the 134A refrigerant and a lubricating oil (hereinafter referred to as “oil”) contained in the compressor 1 is compressed into a high-pressure high-temperature gaseous refrigerant. For example, the gaseous refrigerant and oil at approximately 107 Celsius degree moves (in a direction as indicated by the arrows in the figures) from a
discharge end 11 of the compressor 1 into the firstlink tube line 4. Wherein, an intake end of the firstlink tube line 4 is coupled to thedischarge end 11 of the compressor 1, and an output end of the firstlink tube line 4 is coupled to a double-fork shunt tube 24 of athermal compensation device 2. - The
thermal compensation device 2 is a tri-tubing structure formed by sheathing aninner tube 21 into amid tube 22, and themid tube 22 into anouter tube 23. Wherein, theinner tube 21, themid tube 22 and theouter tube 23 are made of metal such as copper or a copper alloy and have different diameters such as ⅜″, ½″ and ¾″ inches respectively. Intake and output ends of theinner tube 21 and theouter tube 23 are coupled to a double-fork shunt tube 24 and amanifold tube 25 respectively to branch the aforementioned high-pressure high-temperature gaseous refrigerant and oil by theshunt tube 24 to enter and flow in theinner tube 21 and theouter tube 23, so that the high-pressure high-temperature gaseous refrigerant in theinner tube 21 and theouter tube 23 flows respectively through acondenser 3 back to themid tube 22 to compensate heat with the fast-flowing high-pressure intermediate-temperature liquid refrigerant, so as to perform a heat transfer to the liquid refrigerant. As such, the high-temperature gaseous refrigerant collected by themanifold tube 25 flows towards a second link tube line 5, and the temperature of the high-temperature gaseous refrigerant flowing in the second link tube line 5 drops slightly to approximately 103 Celsius degree. - An intake end of second link tube line 5 is coupled to the
manifold tube 25, and an output end of the second link tube line 5 is coupled to the bottom inlet of air cooledcondenser 3 and thecondenser coil 31 are in series connection to provide the high-temperature gaseous refrigerant and oil to enter. Aconventional fan 32 is provided and thecondenser coil 31 is surrounded by a plurality of heat dissipation fins (prior art, not shown in the present invention) to achieve the heat dissipate and condensed effects, so that the high-pressure high-temperature gaseous refrigerant saturated in thecondenser coil 31 is cooled to change its state into liquid with high-pressure intermediate-temperature containing bubbles of super heat, and the condensed liquid refrigerant and oil flow out from the output end ofcondenser coil 31 at the top of thecondenser 3 and discharged into a thirdlink tube line 6. Since the liquid refrigerant charged to thecondenser coil 31 is full saturated and satisfied, the heat saturation effect can be achieved effectively. - Wherein, the third
link tube line 6 is attached with athermostat sensor 61, such that if the temperature of the liquid refrigerant passing through the thirdlink tube line 6 detected by thethermostat sensor 61 reaches a predetermined limitation of temperature such as 75 Celsius degree, thefan 32 will be turned on immediately to blow air to thecondenser 3 to dissipate the heat of thecondenser 3 and turn the air passing through thecondenser 3 into hot air for the indoor heating purpose. If the temperature of the liquid refrigerant passing through thirdlink tube line 6 detected by thethermostat sensor 61 is lower than the predetermined thermostat temperature such as 75 Celsius degree, thefan 32 will be turned off immediately to stop blowing air to thecondenser 3. The control with the predetermined temperature of thethermostat sensor 61 keeps thefan 32 to blow air to thecondenser 3 intermittently and turn the air passing through thecondenser 3 into hot air to achieve an indoor heating effect. - In addition, the gaseous refrigerant enters from the bottom inlet of the
condenser 3 and condensed into liquid refrigerant then flows out from the outlet in top of thecondenser 3, and such arrangement has the following advantage. The high-temperature gaseous refrigerant is impacted and mixed with the intermediate-temperature liquid refrigerant in thecondenser coil 31, so that the liquid refrigerant receives the heat of the super heat of gaseous refrigerant to expedite the liquefaction of the gaseous refrigerant, and a large quantity of liquefied refrigerant can be saturated and satisfied in thecondenser coil 31 to achieve a heat saturation effect effectively. - An output end of third
link tube line 6 is coupled to themid tube 22 of thethermal compensation device 2, such that the intermediate-temperature liquid refrigerant, oil and bubbles of super heat flowing into thirdlink tube line 6 flows towards themid tube 22. Since the diameters (or sizes) of themid tube 22 and theinner tube 21 is ½″ and ⅜″ inches respectively, therefore the gap in between is very small so as to leave a capillary gap and achieve a kind of capillary tube effect. The intermediate-temperature liquid refrigerant flowing in themid tube 22 perform heat transfer with the high-temperature gaseous refrigerant flowing in theinner tube 21 and theouter tube 23, so that the liquid refrigerant is expanded by heat gain, and thus bubbles of super heat are blocked outside the inletcapillary gap 26 between themid tube 22 and theinner tube 21 to achieve the flow restrained effect similar to an expansion valve or a capillary tube. - The liquid refrigerant and oil are not containing any bubbles of super heat flowing out from the output end of the
mid tube 22 enters into a fourthlink tube line 7. Since the fourthlink tube line 7 has a diameter greater than the outletcapillary gap 27 between themid tube 22 and theinner tube 21, therefore when the intermediate-temperature liquid refrigerant are not containing bubbles of super heat enters and flows into fourthlink tube line 7, the pressure is depressed at once and the temperature is lowered to form a low-pressure intermediate-temperature unsaturated liquid refrigerant flowing, and measurements shows that the temperature of the liquid refrigerant of fourthlink tube line 7 is 68 Celsius degree. - An output end of fourth
line tube line 7 is coupled to a conventional liquid-gas separator 8 accomplished with the compressor 1, and the internal diameter of the liquid-gas separator 8 is greater than fourthlink tube line 7 for many times. After the unsaturated liquid refrigerant dispersed into the liquid-gas separator 8, the pressure and temperature are depressed again to a lower-pressure with suitable temperature such as a liquid refrigerant at approximately 38 Celsius degree. This temperature will not lower as the refrigeration effect like the lubricating oil passing through the evaporator does, such that the lubricating oil is in a sticky form which is unfavorable for the lubrication of the compressor. After the low-pressure suitable temperature liquid refrigerant and oil dispersed into the liquid-gas separator 8 is sucked by the suction power of thesuction end 12 of the compressor 1 and compressed to high-pressure high-temperature gaseous refrigerant discharged bydischarge end 11 into firstlink tube line 4 to define a refrigeration cycle. - In summation of the description above, the present invention has the following advantages. The high-temperature gaseous refrigerant flowing in the inner and outer tubes of the thermal compensation device transfers heat with the intermediate-temperature liquid refrigerant flowing in the mid tube, so that the liquid refrigerant flowing into the inlet of capillary gap between the mid tube and the inner tube is heated up to expand to achieve the flow restrained effect, and the inlet of capillary gap can stop bubbles of super heat from entering, and suppress the amount of liquid refrigerant to pass through. Therefore, a limited quantity of refrigerant can be sucked into the compressor at a low pressure without having the lubricating oil to return cooled. The present invention eliminates the use of the evaporator or flow restrained device, such that the compressor is the only heat generate device in the air heating unit of the air-conditioning. In addition, the air heating unit of the air-conditioning does not have evaporator, so that its indoor application is not limited by weathers, even in a severe cold weather outdoor. Obviously, this air heating unit of the present invention is one of the innovative greatest designs of this sort.
Claims (7)
1. An air heating unit of the air-conditioning, comprising:
a compressor, with a discharge end coupled to a first link tube line provided for a high-pressure high-temperature gaseous refrigerant and an oil to flow;
a thermal compensation device, having an inner tube, a mid tube and an outer tube of different diameters, said mid tube being sheathed with said outer tube therein, and said inner tube being sheathed with said mid tube therein to form a tri-tubing structure, and an output end of said first link tube line being coupled to said inner and outer tubes, for facilitating said high-pressure high-temperature gaseous refrigerant to flow and enter into said inner and outer tubes respectively, and an output end of said inner and outer tubes being coupled to a second link tube line for said high-pressure high-temperature gaseous refrigerant and said oil to flow;
an air cooled condenser, including an internal condenser coil installed in series therein and having an bottom inlet end coupled to an output end of said second link tube line, and a fan installed outside said air cooled condenser, such that said high-pressure high-temperature gaseous refrigerant charged into said condenser coil is cooled to change its state to form a high-pressure intermediate-temperature liquid refrigerant containing bubbles of super heat, and said condensed liquid refrigerant and oil flow out from the output end of said condenser coil and flow and enter into a third link tube line, and said third link tube line having a thermostat sensor attached thereon for measuring and detecting whether said liquid refrigerant passing through said third link tube line reaches a predetermined limitation of temperature to control said fan to be turned on or off, and said fan is operated intermittently to blow air to said condenser for heating purpose; and said mid tube, having an intake end and an output end coupled to said third link tube line and a fourth link tube line respectively, such that said intermediate-temperature liquid refrigerant flowing and passing said mid tube performs a heat transfer with said high-temperature gaseous refrigerant flowing in said inner tube and said outer tube, and said intermediate-temperature liquid refrigerant is expanded by heat gain, and said bubbles of super heat of said intermediate-temperature liquid refrigerant are blocked outside the inlet end of capillary gap between said mid tube and said inner tube; if said intermediate-temperature liquid refrigerant and oil containing no air bubbles flowing out from an outlet end of capillary gap between said mid tube and said inner tube flows and enters into said fourth link tube line, the pressure is depressed at once and the temperature is lowered to form a low-pressure intermediate-temperature unsaturated liquid refrigerant; and an output end of said fourth link tube line being coupled to a liquid-gas separator to disperse said low-pressure intermediate-temperature unsaturated liquid refrigerant and depress the pressure and lower the temperature again to form a low-pressure with suitable temperature liquid refrigerant, said low-pressure with suitable temperature liquid refrigerant and oil are sucked from a suction end of said compressor to define a refrigeration cycle.
2. The air heating unit of the air-conditioning according to claim 1 , wherein said inner tube, said mid tube and said outer tube are made of copper and have different diameters such as ⅜″, ½″ and ¾″ inches respectively.
3. The air heating unit of the air-conditioning according to claim 1 , wherein said first link tube line has a discharge end coupled to said inner and outer tubes through a shunt tube for facilitating said high-pressure high-temperature gaseous refrigerant and said oil to be delivered by said shunt tube to flow and enter into said inner tube and said outer tube respectively, and said second link tube line has an intake end coupled to said inner and outer tubes through a manifold tube for facilitating said high-pressure high-temperature gaseous refrigerant to be connected into said second link tube line.
4. The air heating unit of the air-conditioning according to claim 1 , wherein said condenser coil is connected in series, and said second link tube line is coupled to the intake end of said condenser coil at the bottom of said condenser, and said third link tube line is coupled to the output end of said condenser coil at the top of said condenser.
5. The air heating unit of the air-conditioning according to claim 1 , wherein said predetermined limitation of temperature is 75 Celsius degree.
6. The air heating unit of the air-conditioning according to claim 1 , wherein said fourth link tube line has a diameter greater than said outlet of capillary gap between said mid tube and said inner tube, and said liquid-gas separator has an internal diameter greater than the diameter of said fourth link tube line.
7. The air heating unit of the air-conditioning according to claim 1 , wherein said condenser coil is surrounded by a plurality of fins.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
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US13/851,855 US20140290294A1 (en) | 2013-03-27 | 2013-03-27 | Air heating unit of the air-conditioning |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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US13/851,855 US20140290294A1 (en) | 2013-03-27 | 2013-03-27 | Air heating unit of the air-conditioning |
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US20140290294A1 true US20140290294A1 (en) | 2014-10-02 |
Family
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US13/851,855 Abandoned US20140290294A1 (en) | 2013-03-27 | 2013-03-27 | Air heating unit of the air-conditioning |
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Cited By (4)
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CN107144068A (en) * | 2017-04-13 | 2017-09-08 | 滁州胜利电器有限公司 | A kind of liquid expanding temperature controller for commercial display cases |
CN107701399A (en) * | 2017-08-08 | 2018-02-16 | 江苏盈科汽车空调有限公司 | From heat exchange type vehicle-mounted air conditioner compressor |
DE102017110706A1 (en) * | 2017-05-17 | 2018-11-22 | Miele & Cie. Kg | Throttle device for a heat pump and heat pump with a throttle device |
CN113921948A (en) * | 2021-10-13 | 2022-01-11 | 华为数字能源技术有限公司 | Cabinet air conditioning system, cabinet air conditioning device and cabinet |
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