CN110160290B - Air conditioning apparatus - Google Patents
Air conditioning apparatus Download PDFInfo
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- CN110160290B CN110160290B CN201811402219.9A CN201811402219A CN110160290B CN 110160290 B CN110160290 B CN 110160290B CN 201811402219 A CN201811402219 A CN 201811402219A CN 110160290 B CN110160290 B CN 110160290B
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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
- F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
- F25B43/006—Accumulators
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- Mechanical Engineering (AREA)
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- General Engineering & Computer Science (AREA)
- Air-Conditioning For Vehicles (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
The invention provides an air conditioning apparatus capable of suppressing the boiling of refrigerant in an accumulator. The air conditioning device is provided with: an indoor heat exchanger; an outdoor heat exchanger; a compressor which is mounted in a refrigerant circuit connecting the indoor heat exchanger and the outdoor heat exchanger, and compresses and discharges a sucked refrigerant; and an accumulator (33) which is attached to an upstream portion of the compressor of the refrigerant circuit, stores a liquid component of the refrigerant, and returns mainly a gas component of the refrigerant to a suction portion of the compressor. The accumulator (33) has a refrigerant storage section (71) for storing a liquid component of the refrigerant, a refrigerant inflow section for allowing the refrigerant to flow into the refrigerant storage section (71), a refrigerant outflow section for mainly returning a gas component of the refrigerant from the refrigerant storage section (71) to the compressor, and an agitation plate (72) for floating in the liquid refrigerant inside the refrigerant storage section (71).
Description
Technical Field
The present invention relates to an air conditioning apparatus.
Background
Many heat pump type air conditioning apparatuses used in vehicles and the like have a heating refrigerant circuit and a cooling refrigerant circuit, and share a compressor and an outdoor heat exchanger in both the refrigerant circuits. In addition, an accumulator may be provided upstream (suction side) of the compressor. The accumulator functions to accumulate a surplus liquid component of the refrigerant circulating in the refrigerant circuit and to return mainly a gas component of the refrigerant to a suction portion of the compressor. The accumulator disposed upstream of the compressor mainly functions during the heating operation, and a large amount of refrigerant is stored as liquid in the accumulator when the operation of the air-conditioning apparatus is stopped. (see, for example, Japanese patent laid-open publication No. 2017-20670 (hereinafter referred to as patent document 1)).
In the air-conditioning apparatus of patent document 1, an accumulator is connected to the suction side of the compressor, and most of the refrigerant is stored in the accumulator as a liquid during the operation stop. When the compressor is started from this state, the inside of the accumulator becomes a low pressure, and the liquid component of the refrigerant stored in the inside of the accumulator is gradually vaporized and sucked into the compressor.
However, the liquid component of the refrigerant stored in the accumulator is overheated (changes phase from liquid refrigerant to gas refrigerant at any time) at a portion below the liquid surface at the time of starting the compressor or the like, and is accumulated. Therefore, if the temperature of the refrigerant exceeds a certain degree of superheat, the refrigerant boils back, and in this case, it is considered that abnormal expansion noise is generated in the accumulator or the liquid refrigerant in the accumulator is sucked into the compressor. Further, when the liquid refrigerant is sucked into the compressor, a large load acts on the compressor, which is undesirable.
Disclosure of Invention
The present invention has been made in view of the above circumstances, and an object thereof is to provide an air-conditioning apparatus capable of suppressing the boiling-up of refrigerant in an accumulator.
The present invention adopts the following means to solve the above problems.
(1) An air conditioning apparatus according to an aspect of the present invention includes: an indoor heat exchanger for exchanging heat between the refrigerant passing through the indoor heat exchanger and air-conditioning air; an outdoor heat exchanger for exchanging heat between the refrigerant passing through the inside and outside air; a compressor that is attached to a refrigerant circuit connecting the indoor heat exchanger and the outdoor heat exchanger, and compresses and discharges a refrigerant sucked in; and an accumulator that is attached to an upstream portion of the compressor of the refrigerant circuit, stores a liquid component of the refrigerant, and returns mainly a gas component of the refrigerant to a suction portion of the compressor, wherein the accumulator includes: a refrigerant storage section that stores a liquid component of a refrigerant; a refrigerant inflow portion that causes a refrigerant to flow into the refrigerant storage portion; a refrigerant outflow portion that returns mainly a gas component of the refrigerant from the refrigerant storage portion to the compressor; and an agitating plate that floats in the liquid refrigerant inside the refrigerant storage unit.
With the above configuration, when the compressor is operated, the gas component of the refrigerant in the accumulator is sucked into the compressor through the refrigerant outflow portion, and the refrigerant existing on the upstream side of the accumulator flows into the refrigerant storage portion through the refrigerant inflow portion. At this time, the liquid component of the refrigerant stored in the refrigerant storage portion of the accumulator is gradually vaporized and sucked into the compressor.
When the refrigerant flows into the refrigerant storage portion from the refrigerant inflow portion, the liquid component of the refrigerant flows downward in the refrigerant storage portion, and the stirring plate is displaced upward and downward by the flow of the liquid component. The liquid component of the refrigerant in the refrigerant storage section is stirred by the displacement of the stirring plate. As a result, convection is generated in the refrigerant storage portion, and the liquid component of the refrigerant in the refrigerant storage portion is vaporized at an early stage without a high degree of superheat.
(2) In the aspect (1), the stirring plate may have a through hole penetrating the front and back.
In this case, when the agitating plate moves up and down in the refrigerant storage portion, the liquid component of the refrigerant in the refrigerant storage portion passes through the through hole provided in the agitating plate. Therefore, the refrigerant in the refrigerant reservoir is efficiently stirred.
(3) In addition to the aspect (1) or (2), the indoor heat exchanger may be a heat exchanger that exchanges heat between the refrigerant discharged from the compressor and air-conditioning air during the heating operation, the outdoor heat exchanger may be a heat exchanger that exchanges heat between the refrigerant that has passed through the inside of the indoor heat exchanger and outside air during the heating operation, and the refrigerant inflow portion of the accumulator may be connected to a downstream portion of the outdoor heat exchanger.
In this case, since a large amount of the refrigerant is stored in the refrigerant storage portion of the accumulator as a liquid when the compressor is stopped, displacement of the agitating plate in the refrigerant storage portion is particularly effective in suppressing the boiling-up of the refrigerant at the time of restarting the compressor.
According to the aspect of the present invention, the accumulator has the agitating plate floating in the refrigerant storage portion, and the agitating plate receives the flow of the refrigerant flowing into the refrigerant storage portion and displaces in the refrigerant, so that convection can be generated in the refrigerant storage portion. Therefore, according to the aspect of the present invention, the liquid component of the refrigerant in the refrigerant storage portion can be vaporized at an early stage without increasing the degree of superheat, and the boiling-up of the refrigerant can be suppressed.
Drawings
Fig. 1 is a configuration diagram of an air-conditioning apparatus according to an embodiment of the present invention.
Fig. 2 is a longitudinal sectional view of a reservoir according to an embodiment of the present invention.
Fig. 3 is a perspective view of a stirring plate according to an embodiment of the present invention.
Fig. 4 is a configuration diagram of an air-conditioning apparatus according to an embodiment of the present invention.
Fig. 5 is a configuration diagram of an air-conditioning apparatus according to an embodiment of the present invention.
Detailed Description
Hereinafter, an embodiment of the present invention will be described with reference to the drawings.
Fig. 1 is a configuration diagram of an air-conditioning apparatus 10 according to the present embodiment.
The air-conditioning apparatus 10 of the present embodiment is mounted on an electric vehicle or the like that does not include an engine (internal combustion engine) as a drive source of the vehicle, and performs a heating operation using a heat pump cycle. The air-conditioning apparatus 10 includes an air-conditioning unit 11, a heat pump cycle 12 in which a refrigerant can circulate, and a control device 13.
The air conditioning unit 11 includes a duct 51 through which air-conditioned air flows, a blower 52 housed in the duct 51, an evaporator 53 (an indoor heat exchanger for cooling), an air mix door 54, an indoor heat exchanger 55 for heating, and a heater core 56.
The duct 51 has an air intake port 57 located on the upstream side in the flow direction of the conditioned air, and an air outlet port 58 located on the downstream side. The blower 52, the evaporator 53, the air mix door 54, the indoor heat exchanger 55 for heating, and the heater core 56 are arranged in this order from the upstream side to the downstream side in the air-conditioning air flow direction.
The blower 52 is driven by a drive voltage applied by control of the controller 13, for example, and sends out the conditioned air (at least one of the internal air and the external air) taken into the duct 51 through the air intake port 57 to the downstream side.
The evaporator 53 exchanges heat between the low-pressure refrigerant flowing into the interior and the air-conditioning air (air flowing through the duct 51) passing around, and cools the air-conditioning air passing around the evaporator 53 by absorbing heat when the refrigerant evaporates.
The heating indoor heat exchanger 55 can radiate heat from the high-temperature and high-pressure refrigerant passing through the inside thereof, thereby heating the air-conditioning air passing through the periphery of the heating indoor heat exchanger 55.
The heater core 56 is disposed downstream of the indoor heat exchanger 55 for heating in the duct 51. The heater core 56 is connected to an electric water heater 62 and a water pump 63 via a pipe 61. The heater core 56 circulates water between it and the electric water heater 62 by the operation of the water pump 63. The water heated by the water heating electric heater 62 is supplied to the heater core 56, thereby heating the air-conditioning air passing around the heater core 56.
The air mix door 54 can be rotated by a drive mechanism, not shown, which is driven by control of the control device 13. Specifically, the air mix door 54 is rotated between a heating position (see fig. 4) in which a ventilation path (heating path) to the indoor heat exchanger 55 for heating and the heater core 56 is opened and a cooling position (see fig. 5) in which a ventilation path (cooling path) bypassing the heating path is opened in the duct 51.
The heat pump cycle 12 includes, for example, the evaporator 53 and the indoor heat exchanger 55 for heating, the compressor 21, the expansion valve 22 for heating, the bypass valve 23, the outdoor heat exchanger 24, the receiver tank 25, the refrigeration valve 26, the sub-condenser 27, the check valve 28, the expansion valve 29 for cooling, the auxiliary heat exchanger 31 for cooling, the heating valve 32, the accumulator 33, the dehumidification valve 34, and the evaporation capacity control valve 35, and the above-described components are connected via refrigerant flow paths.
The suction portion of the compressor 21 is connected to the accumulator 33, and the discharge portion is connected to the indoor heat exchanger 55 for heating. The compressor 21 is driven by the driving force of the driving mechanism driven by the control of the control device 13, mainly sucks the gas component of the refrigerant from the accumulator 33, compresses the refrigerant, and discharges the compressed refrigerant as a high-temperature and high-pressure refrigerant to the side of the above-described indoor heat exchanger 55 for heating.
The expansion valve 22 for heating is a so-called throttle valve, and expands the refrigerant discharged from the indoor heat exchanger 55 for heating, and then discharges the refrigerant as a low-temperature, low-pressure, vapor-liquid 2-phase (rich liquid phase) spray-like refrigerant to the outdoor heat exchanger 24.
A path from the discharge portion of the compressor 21 to the heating expansion valve 22 via the heating indoor heat exchanger 55 is the high-pressure side main path 41.
The bypass valve 23 is provided in the cooling bypass passage 42 connected to the outdoor heat exchanger 24 while bypassing the heating expansion valve 22 of the high-pressure side main passage 41, at the downstream portion of the heating indoor heat exchanger 55, and is controlled to open and close by the control device 13. The bypass valve 23 is closed during the heating operation, and is opened during the cooling operation.
Thus, during the heating operation, the refrigerant flowing out of the indoor heat exchanger 55 for heating passes through the expansion valve 22 for heating and flows into the outdoor heat exchanger 24 in a low-temperature and low-pressure state. On the other hand, when the cooling operation is performed, the refrigerant flowing out of the indoor heat exchanger 55 for heating flows into the outdoor heat exchanger 24 in a high temperature state by the bypass valve 23.
The outdoor heat exchanger 24 exchanges heat between the refrigerant flowing into the interior and the outdoor atmosphere. A fan 24a capable of blowing air toward the outdoor heat exchanger 24 is disposed in front of the outdoor heat exchanger 24. The fan 24a is driven under the control of the control device 13.
When the heating operation is performed, the outdoor heat exchanger 24 can absorb heat from the outdoor atmosphere by the low-temperature and low-pressure refrigerant passing through the inside thereof, and can vaporize the refrigerant by absorbing heat from the outdoor atmosphere. On the other hand, when the cooling operation is performed, the outdoor heat exchanger 24 can radiate heat to the outdoor atmosphere by the high-temperature refrigerant passing through the inside, and can cool the refrigerant by, for example, radiation to the outdoor atmosphere and blowing by the fan 24 a.
The refrigeration valve 26 is provided in the main cooling passage 43 connected to the downstream portion of the outdoor heat exchanger 24 in the refrigerant passage, and is controlled to open and close by the control device 13. The cooling valve 26 is in an open state during the cooling operation and is in a closed state during the heating operation.
The receiver tank 25 is provided on the upstream side of the refrigerant valve 26 in the main cooling passage 43. The receiver tank 25 stores the excess refrigerant of the refrigerant flowing into the main cooling passage 43 through the outdoor heat exchanger 24 during the cooling operation.
The sub-condenser 27 is provided on the downstream side of the receiver tank 25 in the cooling main passage 43, and performs heat exchange between the refrigerant flowing inside and the outdoor atmosphere.
The check valve 28 is provided on the downstream side of the sub-condenser 27 in the main cooling passage 43. The check valve 28 allows the refrigerant that has passed through the sub-condenser 27 to flow downstream during the cooling operation, and prevents the refrigerant from flowing back to a position upstream of the check valve 28 (on the sub-condenser 27 side) in the cooling main passage 43 during the dehumidification operation.
The expansion valve 29 for cooling is a so-called throttle valve, and is connected between the check valve 28 in the main passage 43 for cooling and the inlet of the evaporator 53. The expansion valve 29 for cooling expands the refrigerant having passed through the check valve 28 according to the valve opening degree controlled by the control device 13, and then discharges the refrigerant as a low-temperature, low-pressure, atomized refrigerant of a gas-liquid 2-phase (rich gas phase) to the evaporator 53.
The auxiliary heat exchanger 31 for cooling is disposed so as to straddle an upstream portion of the main passage 43 for cooling located upstream of the expansion valve 29 for cooling and a downstream portion of the main passage located downstream of the evaporator 53. The auxiliary heat exchanger 31 for cooling performs heat exchange between the upstream portion and the downstream portion described above during the cooling operation, and cools the refrigerant in the upstream portion before flowing into the evaporator 53.
The main passage 43 for cooling in the present embodiment is a passage connected from the downstream portion of the outdoor heat exchanger 24 to the accumulator 33 via the receiver tank 25, the cooling valve 26, the sub-condenser 27, the check valve 28, the auxiliary heat exchanger 31 for cooling, the expansion valve 29 for cooling, the evaporator 53, and the evaporation capacity control valve 35.
The heating valve 32 is provided in a heating bypass passage 44 that bypasses the cooling main passage 43 and connects the downstream portion of the outdoor heat exchanger 24 to the accumulator 33. The heating valve 32 is controlled to be opened and closed by the control device 13. The heating valve 32 is in an open state during the heating operation and in a closed state during the cooling operation.
The accumulator 33 is connected between the compressor 21 and a junction 46, and the junction 46 connects the downstream end of the cooling main passage 43 and the downstream end of the heating bypass passage 44. The accumulator 33 separates the refrigerant flowing in from the merging portion 46 into a gas and a liquid, stores the remaining liquid component (liquid phase) of the refrigerant therein, and mainly sucks the gas component (gas phase) of the refrigerant into the compressor 21.
Fig. 2 is a diagram showing a detailed structure of the inside of the reservoir 33. The internal structure of the reservoir 33 will be described in detail later.
The dehumidification valve 34 is provided in a dehumidification passage 48 that connects a portion of the cooling main passage 43 located downstream of the check valve 28 and a portion of the high-pressure side main passage 41 located downstream of the heating indoor heat exchanger 55, and is controlled to open and close by the control device 13. The dehumidification valve 34 is in an open state during the dehumidification operation, and is in a closed state during the other operations (cooling operation and heating operation).
The evaporation capacity control valve 35 is provided between the evaporator 53 and the auxiliary heat exchanger 31 for cooling in the main passage 43 for cooling, and is controlled to open and close by the control device 13. The evaporation capacity control valve 35 is controlled so that the opening degree is reduced at the time of the dehumidification operation as compared with the cooling operation.
Here, in the present embodiment, a heating refrigerant circuit in which a refrigerant circulates during a heating operation and a cooling refrigerant circuit in which a refrigerant circulates during a cooling operation are provided, and the compressor 21, the outdoor heat exchanger 24, and the accumulator 33 are shared by the two refrigerant circuits.
The heating refrigerant circuit includes a high-pressure-side main passage 41 that connects the discharge portion of the compressor 21 to the upstream portion of the outdoor heat exchanger 24 via the indoor heat exchanger 55 for heating and the heating expansion valve 22, and a heating bypass passage 44 that bypasses the cooling main passage 43 and connects the downstream portion of the outdoor heat exchanger 24 to the accumulator 33. The cooling refrigerant circuit includes a cooling main passage 43 that connects the downstream portion of the outdoor heat exchanger 24 to the accumulator 33 via the cooling expansion valve 29 and the evaporator 53, and a passage that includes a part of the high-pressure side main passage 41 that passes through the heating indoor heat exchanger 55 and the cooling bypass passage 42, bypasses the heating expansion valve 22, and connects the discharge portion of the compressor 21 to the upstream portion of the outdoor heat exchanger 24.
In addition, although the refrigerant circuit including the heating refrigerant circuit and the cooling refrigerant circuit is filled with a refrigerant circulating therein, lubricating oil for lubricating sliding portions of devices in the circuit such as the compressor 21 is mixed in the refrigerant. In the heating operation in which the compressor 21 needs to be operated at a high rotation speed, an amount of lubricating oil sufficient to lubricate the compressor 21 during the heating operation is mixed into the refrigerant.
Next, the operation of the air-conditioning apparatus 10 will be described. Fig. 4 is an explanatory diagram illustrating an operation of the air-conditioning apparatus 10 during the heating operation, and fig. 5 is an explanatory diagram illustrating an operation of the air-conditioning apparatus 10 during the cooling operation. In the figure, the dashed-dotted line indicates a high-pressure state of the refrigerant, the solid line indicates a low-pressure state of the refrigerant, and the dashed line indicates a portion where the refrigerant does not flow.
(heating operation)
During the heating operation, as shown in fig. 4, the air mix door 54 is at the heating position at which the heating path is opened, and the heating valve 32 is in the open state. During the heating operation, the bypass valve 23, the refrigeration valve 26, the dehumidification valve 34, and the evaporation capacity control valve 35 are closed.
In this case, the high-temperature and high-pressure refrigerant discharged from the compressor 21 heats the air-conditioning air in the duct 51 by heat released in the indoor heat exchanger 55 for heating.
The refrigerant having passed through the indoor heat exchanger 55 for heating is expanded by the expansion valve 22 for heating to be in a spray form of a liquid-phase-rich gas-liquid 2 phase, and then absorbs heat from the outdoor atmosphere in the outdoor heat exchanger 24 to be in a spray form of a gas-phase-rich gas-liquid 2 phase. The refrigerant having passed through the outdoor heat exchanger 24 passes through the heating bypass passage 44 and the merging portion 46, and flows into the accumulator 33. The refrigerant flowing into the accumulator 33 is subjected to gas-liquid separation in the inside thereof, and the refrigerant (gas component of the refrigerant) in a gas phase is mainly sucked into the compressor 21.
At this time, the air-conditioning air flowing through the duct 51 of the air-conditioning unit 11 passes through the evaporator 53 and then passes through the indoor heat exchanger 55 and the heater core 56 for heating in the heating path. The conditioned air is heated when passing through the indoor heat exchanger 55 and the heater core 56 for heating, and then passes through the air outlet 58 to be supplied into the vehicle interior as heating air.
(Cooling operation)
During the cooling operation, as shown in fig. 5, the air mix door 54 is at a cooling position where the air-conditioning air having passed through the evaporator 53 passes through the cooling path, and the bypass valve 23, the refrigerant valve 26, and the evaporation capacity control valve 35 are in an open state. The heating expansion valve 22, the heating valve 32, and the dehumidification valve 34 are closed.
In this case, the high-temperature and high-pressure refrigerant discharged from the compressor 21 passes through the indoor heat exchanger 55 for heating and the bypass valve 23, releases heat to the outdoor atmosphere in the outdoor heat exchanger 24, and then flows into the main passage 43 for cooling. After the remainder of the refrigerant is collected in the receiver tank 25, the refrigerant releases heat again to the outdoor atmosphere in the sub-condenser 27. Thereafter, the refrigerant is expanded by the expansion valve 29 for cooling to be a spray of a gas-liquid 2 phase rich in a liquid phase, and then the air-conditioning air in the duct 51 is cooled by heat absorption in the evaporator 53.
The gas-rich gas-liquid 2-phase refrigerant having passed through the evaporator 53 exchanges heat in the auxiliary cooling heat exchanger 31 and flows into the accumulator 33. The gas-phase-rich refrigerant flowing into the accumulator 33 is subjected to gas-liquid separation in the inside thereof, and the refrigerant (gas component of the refrigerant) in a gas phase is mainly sucked into the compressor 21.
At this time, the air-conditioning air flowing through the duct 51 of the air-conditioning unit 11 is cooled while passing through the evaporator 53, and then bypasses the indoor heat exchanger 55 for heating to be supplied as cooling air from the air outlet 58 into the vehicle interior.
Next, the detailed configuration of the accumulator 33 used in the air-conditioning apparatus 10 according to the present embodiment will be described with reference to fig. 2 and 3.
The accumulator 33 is a cylindrical case 65 having a cylindrical shape, and an inlet-side connection port 66 connected to the cooling main passage 43 and the heating bypass passage 44 and an outlet-side connection port 67 connected to the suction portion of the compressor 21 are provided in an upper wall 65A of the case 65.
In the present embodiment, the inflow side connection port 66 constitutes a refrigerant inflow portion of the accumulator 33, and the outflow side connection port constitutes a refrigerant outflow portion of the accumulator 33.
A support wall 68 is attached to a position directly below the upper wall 65A in the housing 65 with a predetermined gap from the upper wall 65A. The support wall 68 is provided with an inlet port 68a, and the inlet port 68a introduces the refrigerant flowing from the inlet connection port 66 into a space below the support wall 68 in the casing 65.
In the present embodiment, a portion forming a space portion below the support wall 68 in the casing 65 constitutes the refrigerant storage portion 71 of the accumulator 33 that stores the liquid component of the refrigerant after gas-liquid separation.
An outflow pipe 69 is attached to the support wall 68, and an upper end of the outflow pipe 69 is connected to the outflow-side connection port 67 and a lower end thereof extends to a vicinity of the bottom wall in the housing 65. An end member 70 is attached to a lower end of the outlet pipe 69, and the end member 70 has a plurality of through holes 70a communicating the inside and outside of the outlet pipe 69. Further, a guide pipe 74 is disposed coaxially with the outflow pipe 69 on the radially outer side of the outflow pipe 69, and the diameter of the guide pipe 74 is larger than that of the outflow pipe 69. The lower end of the guide pipe 74 is fixed to the bottom surface inside the housing 65, and the upper end opens into a space portion directly below the support wall 68. The gas component of the refrigerant flowing into the space above the refrigerant reservoir 71 through the inflow connection port 66 and the introduction port 68a passes through the gap between the guide pipe 74 and the outflow pipe 69 and the through hole 70a of the end member 70 from the upper end of the guide pipe 74, passes through the inside of the outflow pipe 69 and the outflow connection port 67, and is sucked into the suction portion of the compressor 21.
A communication hole 75 is formed in the peripheral wall portion near the lower end of the guide pipe 74. In fig. 2, reference numeral 95 denotes a desiccant that is provided in the refrigerant storage portion 71 and dries moisture mixed in the refrigerant, and reference numeral L denotes a liquid component of the refrigerant stored in the refrigerant storage portion 71.
An agitation plate 72 is housed inside the refrigerant storage section 71, and the agitation plate 72 floats in the liquid refrigerant (liquid component L of the refrigerant) stored in the refrigerant storage section 71. The agitating plate 72 is formed of a raw material having a specific gravity smaller than that of the liquid refrigerant.
Fig. 3 is a perspective view of the agitating plate 72.
The stirring plate 72 is formed in a disk shape having an outer diameter smaller than the inner diameter of the refrigerant reservoir 71. An insertion hole 76 through which the guide pipe 74 passes is formed in the agitating plate 72. The insertion hole 76 is formed to have a diameter larger than the outer diameter of the guide pipe 74 so as not to hinder free displacement of the agitating plate 72 when the agitating plate 72 floats in the liquid refrigerant in the refrigerant storage portion 71. The stirring plate 72 is provided with a plurality of through holes 73 that penetrate the front and back thereof. When the stirring plate 72 floats in the liquid refrigerant in the refrigerant storage portion 71 and moves up and down, the through-holes 73 allow the refrigerant to pass through the inside thereof, thereby efficiently stirring the refrigerant stored in the refrigerant storage portion 71.
Next, the function of the storage 33 will be described.
When the compressor 21 is stopped for a long time after the heating operation, the refrigerant in the refrigerant circuit is stored in the refrigerant storage portion 71 of the accumulator 33 in a liquefied state. Therefore, a large amount of the liquid component L of the refrigerant is stored in the refrigerant storage portion 71 of the accumulator 33.
When the compressor 21 is started from this state, the gas component of the refrigerant in the accumulator 33 is sucked into the suction portion of the compressor 21 through the outflow-side connection port 67, and the refrigerant existing in the heating bypass passage 44 flows into the refrigerant storage portion 71 through the inflow-side connection port 66. At this time, the pressure in the refrigerant storage portion 71 of the accumulator 33 becomes low, and the liquid component L of the refrigerant stored in the refrigerant storage portion 71 is gradually vaporized and sucked into the suction portion of the compressor 21.
When the refrigerant flows into the refrigerant storage portion 71 from the inflow-side connection port 66 of the accumulator 33, the liquid component L of the refrigerant flowing into the introduction port 68a in the case 65 from the inflow-side connection port 66 drips onto the liquid surface of the refrigerant in the refrigerant storage portion 71. At this time, the liquid level of the refrigerant in the refrigerant storage section 71 fluctuates due to the dropping of the liquid component L of the refrigerant, or the stirring plate 72 fluctuates vertically in the liquid refrigerant due to the dropping of the liquid component L directly onto the stirring plate 72. At this time, the liquid refrigerant in the refrigerant storage section 71 is stirred by the stirring plate 72. In particular, since the agitating plate 72 is provided with the plurality of through holes 73, the liquid refrigerant in the refrigerant storage section 71 is efficiently agitated by the liquid refrigerant passing through the through holes 73. Thereby, the liquid refrigerant in the refrigerant storage portion 71 is stirred by the stirring plate 72 and flows convectively in the refrigerant storage portion 71. As a result, the liquid refrigerant in the refrigerant storage portion 71 is vaporized at an early stage without increasing the degree of superheat, and the boiling of the refrigerant in the refrigerant storage portion 71 is suppressed.
As described above, in the air-conditioning apparatus 10 of the present embodiment, the agitating plate 72 of the accumulator 33 floats in the liquid refrigerant in the refrigerant storage section 71, and the agitating plate 72 moves up and down in the refrigerant due to the dropping of the refrigerant sucked from the inlet connection port 66. The vertical movement of the stirring plate 72 at this time stirs the liquid refrigerant in the refrigerant storage section 71. Therefore, when the air-conditioning apparatus 10 according to the present embodiment is used, the liquid refrigerant in the refrigerant storage portion 71 of the accumulator 33 can be vaporized at an early stage without a high degree of superheat, and the boiling of the refrigerant can be suppressed.
Therefore, when the air-conditioning apparatus 10 according to the present embodiment is used, the occurrence of abnormal expansion noise due to boiling-back can be suppressed. Further, the liquid refrigerant in the accumulator 33 can be prevented from being sucked into the compressor 21 by the boiling-up operation, and a large load can be applied to the compressor 21.
In particular, in the air-conditioning apparatus 10 of the present embodiment, the agitating plate 72 housed in the refrigerant storage portion 71 of the accumulator 33 is provided with a plurality of through holes 73 that penetrate the front and back. Therefore, when the stirring plate 72 fluctuates in the refrigerant, the liquid refrigerant in the refrigerant storage section 71 can be efficiently stirred.
In the air-conditioning apparatus 10 according to the present embodiment, since the stirring plate 72 having a relatively simple structure is simply housed in the refrigerant storage portion 71 of the accumulator 33, the rising of the product cost of the accumulator 33 can be suppressed, and the boiling-up of the refrigerant can be suppressed.
The present invention is not limited to the above-described embodiments, and various design changes can be made without departing from the scope of the present invention.
Claims (2)
1. An air conditioning apparatus is characterized by comprising:
an indoor heat exchanger for exchanging heat between the refrigerant passing through the indoor heat exchanger and air-conditioning air;
an outdoor heat exchanger for exchanging heat between the refrigerant passing through the inside and outside air;
a compressor that is attached to a refrigerant circuit connecting the indoor heat exchanger and the outdoor heat exchanger, and compresses and discharges a refrigerant sucked in; and
an accumulator installed at an upstream portion of the compressor of the refrigerant circuit, storing a liquid component of the refrigerant and returning mainly a gas component of the refrigerant to a suction portion of the compressor,
the reservoir has:
a refrigerant storage section that stores a liquid component of a refrigerant;
a refrigerant inflow portion that causes a refrigerant to flow into the refrigerant storage portion;
a refrigerant outflow portion that returns mainly a gas component of the refrigerant from the refrigerant storage portion to the compressor; and
an agitating plate that floats in the liquid refrigerant inside the refrigerant storage unit,
the stirring plate is provided with a through hole penetrating through the front and the back.
2. The air conditioning device according to claim 1,
the indoor heat exchanger is a heat exchanger for exchanging heat between the refrigerant discharged from the compressor and air-conditioning air during heating operation,
the outdoor heat exchanger is a heat exchanger for exchanging heat between the refrigerant passing through the indoor heat exchanger and the outside air during the heating operation,
a refrigerant inflow portion of the accumulator is connected to a downstream portion of the outdoor heat exchanger.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2018-026482 | 2018-02-16 | ||
| JP2018026482A JP7058514B2 (en) | 2018-02-16 | 2018-02-16 | Air conditioner |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN110160290A CN110160290A (en) | 2019-08-23 |
| CN110160290B true CN110160290B (en) | 2021-04-20 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201811402219.9A Active CN110160290B (en) | 2018-02-16 | 2018-11-22 | Air conditioning apparatus |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP7058514B2 (en) |
| CN (1) | CN110160290B (en) |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH094945A (en) * | 1995-04-17 | 1997-01-10 | Fuji Koki:Kk | Receiver dryer |
| CN1526994A (en) * | 2003-03-04 | 2004-09-08 | 东芝开利株式会社 | Air conditioning apparatus |
| JP2008032315A (en) * | 2006-07-28 | 2008-02-14 | Calsonic Kansei Corp | Accumulator |
| CN205843155U (en) * | 2016-07-27 | 2016-12-28 | 广东美的暖通设备有限公司 | Gas-liquid separator and the air-conditioning with it |
| JP2017058070A (en) * | 2015-09-16 | 2017-03-23 | 本田技研工業株式会社 | Air conditioner |
| CN106731919A (en) * | 2016-11-12 | 2017-05-31 | 佘小玲 | A kind of Liqiud-gas mixing device |
| CN107289689A (en) * | 2017-07-28 | 2017-10-24 | 安徽美芝精密制造有限公司 | reservoir and compressor |
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| JPH0536494Y2 (en) * | 1987-11-25 | 1993-09-16 | ||
| JPH03107668U (en) * | 1990-02-21 | 1991-11-06 | ||
| JP2586083Y2 (en) * | 1992-07-31 | 1998-12-02 | ダイキン工業株式会社 | Gas-liquid separator |
| JP3960534B2 (en) | 2002-07-31 | 2007-08-15 | 株式会社共立 | Wave tank of liquid tank |
| US20050081559A1 (en) | 2003-10-20 | 2005-04-21 | Mcgregor Ian A.N. | Accumulator with pickup tube |
| JP6507057B2 (en) | 2015-07-24 | 2019-04-24 | 株式会社不二工機 | accumulator |
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- 2018-02-16 JP JP2018026482A patent/JP7058514B2/en active Active
- 2018-11-22 CN CN201811402219.9A patent/CN110160290B/en active Active
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| JPH094945A (en) * | 1995-04-17 | 1997-01-10 | Fuji Koki:Kk | Receiver dryer |
| CN1526994A (en) * | 2003-03-04 | 2004-09-08 | 东芝开利株式会社 | Air conditioning apparatus |
| JP2008032315A (en) * | 2006-07-28 | 2008-02-14 | Calsonic Kansei Corp | Accumulator |
| JP2017058070A (en) * | 2015-09-16 | 2017-03-23 | 本田技研工業株式会社 | Air conditioner |
| CN205843155U (en) * | 2016-07-27 | 2016-12-28 | 广东美的暖通设备有限公司 | Gas-liquid separator and the air-conditioning with it |
| CN106731919A (en) * | 2016-11-12 | 2017-05-31 | 佘小玲 | A kind of Liqiud-gas mixing device |
| CN107289689A (en) * | 2017-07-28 | 2017-10-24 | 安徽美芝精密制造有限公司 | reservoir and compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| JP7058514B2 (en) | 2022-04-22 |
| CN110160290A (en) | 2019-08-23 |
| JP2019143835A (en) | 2019-08-29 |
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