EP2647925A2 - Refrigeration cycle apparatus - Google Patents
Refrigeration cycle apparatus Download PDFInfo
- Publication number
- EP2647925A2 EP2647925A2 EP13166592.9A EP13166592A EP2647925A2 EP 2647925 A2 EP2647925 A2 EP 2647925A2 EP 13166592 A EP13166592 A EP 13166592A EP 2647925 A2 EP2647925 A2 EP 2647925A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- temperature
- refrigerant
- detection means
- heat exchanger
- outlet
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 238000005057 refrigeration Methods 0.000 title description 21
- 238000001514 detection method Methods 0.000 claims abstract description 156
- 239000003507 refrigerant Substances 0.000 claims abstract description 130
- 230000006837 decompression Effects 0.000 claims abstract description 23
- 239000006096 absorbing agent Substances 0.000 claims abstract description 22
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 103
- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical compound O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 claims description 9
- 229910002092 carbon dioxide Inorganic materials 0.000 claims description 5
- 239000001569 carbon dioxide Substances 0.000 claims description 4
- 238000010586 diagram Methods 0.000 description 16
- 238000010438 heat treatment Methods 0.000 description 14
- 230000007423 decrease Effects 0.000 description 10
- 239000012530 fluid Substances 0.000 description 5
- 230000000694 effects Effects 0.000 description 3
- 238000001704 evaporation Methods 0.000 description 3
- 239000007788 liquid Substances 0.000 description 3
- 230000008020 evaporation Effects 0.000 description 2
- 230000002159 abnormal effect Effects 0.000 description 1
- 238000009529 body temperature measurement Methods 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 230000017525 heat dissipation Effects 0.000 description 1
- 238000004513 sizing Methods 0.000 description 1
Images
Classifications
-
- 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
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
- F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
-
- 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
- F25B2309/00—Gas cycle refrigeration machines
- F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
- F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
-
- 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
- F25B2339/00—Details of evaporators; Details of condensers
- F25B2339/04—Details of condensers
- F25B2339/047—Water-cooled condensers
-
- 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
- F25B2341/063—Feed forward 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
- F25B2600/00—Control issues
- F25B2600/17—Control issues by controlling the pressure of the condenser
-
- 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
- F25B2700/19—Pressures
- F25B2700/193—Pressures of the compressor
- F25B2700/1933—Suction pressures
-
- 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
- F25B2700/2102—Temperatures at the outlet of the gas cooler
-
- 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
-
- 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
- F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2116—Temperatures of a condenser
- F25B2700/21161—Temperatures of a condenser of the fluid heated by the condenser
-
- 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
- F25B2700/2117—Temperatures of an evaporator
- F25B2700/21174—Temperatures of an evaporator of the refrigerant at the inlet of the evaporator
-
- 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
Definitions
- the present invention relates to a refrigeration cycle apparatus using an internal heat exchanger, more particularly to a refrigerant control for stably securing performance.
- a hot water supply apparatus is proposed as a built-in refrigeration cycle apparatus such as:
- a water heater is also proposed such as: a water heater for heating a hot water supply fluid in a supercritical heat pump cycle where a refrigerant pressure in a high pressure side becomes equal to or more than the critical pressure of the refrigerant comprising:
- the present invention is made to solve the above problems in the prior art.
- the object is to obtain a refrigeration cycle apparatus capable of stably achieving efficient operation conditions by controlling operation values based on standard conditions of the radiator and outlet conditions of the radiator to be a target value.
- the refrigeration cycle apparatus includes at least a compressor, a radiator, decompression means capable of changing an open degree, a heat absorber, an internal heat exchanger that performs heat exchange between a refrigerant at an outlet of the radiator and the refrigerant at the outlet of the heat absorber.
- the refrigeration cycle apparatus is characterized in that at least first refrigerant conditions detection means for detecting standard conditions of the radiator and second refrigerant conditions detection means for detecting refrigerant conditions between an outlet of the radiator and a high-pressure side inlet of an internal heat exchanger are provided, and an opening degree of decompression means is controlled so that a calculation value calculated based on an output of the first refrigerant conditions detection means and the output of the second refrigerant conditions detection means becomes a target value.
- the expansion valve opening degree is controlled so that the COP becomes maximum based on standard conditions of the radiator and refrigerant conditions of the radiator outlet part, so that a refrigerant cycle apparatus capable of stably achieving efficient operation can be obtained.
- Fig. 1 shows a configuration diagram of the refrigerant cycle apparatus according to the present embodiment.
- the refrigerant cycle apparatus according to the present embodiment is a hot water supply apparatus using carbon dioxide (hereinafter, CO 2 ) as a refrigerant, composed of a heat source apparatus 50, a hot water storage apparatus 60, and a controller 40 for controlling these.
- CO 2 carbon dioxide
- the present embodiment shows an example of the hot water supply apparatus, however, it is not limited thereto.
- the apparatus may be an air conditioner.
- the refrigerant is not limited to carbon dioxide but an HFC refrigerant may be used.
- the heat source apparatus 50 is composed of a compressor 1 for compressing the refrigerant, a radiator 2 (hereinafter, referred to “water heat exchanger") for taking out heat of a high-temperature high-pressure refrigerant compressed in the compressor 1, an internal heat exchanger 5 for further cooling the refrigerant output from the water heat exchanger 2, a decompressor 3 (hereinafter, referred to “expansion valve”) that decompresses the refrigerant and whose opening degree can be changed, an heat-absorber 4 (hereinafter, referred to “evaporator”) for evaporating the refrigerant decompressed in the expansion valve 3, and an internal heat exchanger 5 for further heating the refrigerant flowed out of the evaporator 4.
- a compressor 1 for compressing the refrigerant
- a radiator 2 hereinafter, referred to "water heat exchanger”
- water heat exchanger 5 for taking out heat of a high-temperature high-pressure refrigerant compressed in the compressor 1
- the internal heat exchanger 5 is a heat exchanger that heat-exchanges the refrigerant at an outlet of the water heat exchanger 2 with the refrigerant at the outlet of the evaporator 4.
- a blower 29 is provided for sending air on an outer surface of the evaporator 4.
- first temperature detection means 30 for detecting a discharge temperature of the compressor 1
- second temperature detection means 31 for detecting an outlet temperature of the water heat exchanger 2
- fifth temperature detection means 32 for detecting an inlet refrigerant temperature of the evaporator 4
- sixth temperature detection means 33 for detecting a suction temperature of the compressor 1.
- the first temperature detection means 30 and the second temperature detection means 31 correspond to a first refrigerant conditions detection means and second refrigerant conditions detection means respectively in an example of control in Fig. 7 to be described later.
- a hot water storage apparatus 60 is connected with the water heat exchanger 2, which is a radiator, via piping, being composed of a heat source side pump 20, a hot water storage tank 21, a use side pump 22, and on-off valves 23, 24, 25.
- on-off valves 23, 24, 25 may be a simple valve only for switching operation or an opening variable valve.
- the on-off valves 23, 25 are closed, the on-off valve 24 is opened, and circulation heating operation is performed in which low-temperature hot water in the hot water storage tank 21 is re-boiled.
- the on-off valves 23, 24 are closed, the on-off valve 25 is opened, the use side pump 22 starts operation to transfer stored hot water to the use side.
- third temperature detection means 41 is attached for detecting an inlet temperature of a medium (water) to be heated.
- fourth temperature detection means 42 is attached for detecting the outlet temperature of the medium (water) to be heated.
- a controller 40 performs calculation using detected values from first temperature detection means 30, second temperature detection means 31, fifth temperature detection means 32, sixth temperature detection means 33, third temperature detection means 41, and fourth temperature detection means 42 to control an opening degree of the expansion valve 3, a rotation speed of the compressor 1, and the rotation speed of the hot water supply side pump 20, respectively.
- Fig. 2 is a P-h diagram describing cycle conditions during hot water storage operation in the refrigeration cycle apparatus shown in Fig. 1 .
- solid lines denote refrigerant conditions at a certain expansion valve opening degree and A, B, C, D, and E denote refrigerant conditions in the hot water storage operation.
- A high-temperature high-pressure refrigerant
- the refrigerant heats supplied water while dissipating heat to water circulating the hot water storage circuit to decrease the own temperature.
- a refrigerant (B) flowed out of the water heat exchanger 2 dissipates heat in the internal heat exchanger 5 to further decrease (C) the temperature, being decompressed (D) by the expansion valve 3 to turn into a low-temperature low-pressure refrigerant.
- the low-temperature low-pressure refrigerant absorbs heat from the air in the evaporator 4 to evaporate (E).
- the refrigerant flowed out of the evaporator 4 is heated in the internal heat exchanger 5 to turn into a gas (F) and sucked by the compressor 1 to form a refrigeration cycle.
- the expansion valve 3 is controlled so that a suction superheat degree of the compressor 1 becomes a target value (for example, 5 to 10 °C).
- a target value for example, 5 to 10 °C.
- an evaporation temperature (ET) is estimated
- a suction superheat degree SHs is calculated by the following formula using a detection value (Ts) of sixth temperature detection means 33 detecting a suction temperature of the compressor 1.
- Ts T S - ET
- An example is given in which an evaporation temperature (ET) is estimated based on the detection value of the fifth temperature detection means 32, however, it is not limited thereto.
- Pressure detection means (second pressure detection means) 51 (refer to Fig. 1 ) is installed between a low-pressure side outlet of the internal heat exchanger 5 and the inlet of the compressor 1, and from the detection value, a refrigerant saturation temperature may be obtained.
- a suction superheat degree control precedes other high efficiency operation control because a function to prevent liquid return of the compressor 1 precedes a function to efficiently operate the water heat exchanger 2 from the viewpoint of securing reliability of the equipment.
- Fig. 3 shows a refrigerant and water temperature distribution in the water heat exchanger 2.
- thick solid lines show a change in refrigerant temperature
- a thin solid lines denote a change in water temperature.
- ⁇ T1 denotes a temperature difference between the water heat exchanger inlet temperature and water outlet temperature
- ⁇ T2 denotes a temperature difference between the water heat exchanger outlet temperature and water inlet temperature.
- ⁇ Tp is a temperature difference at a pinch point where the temperature difference between a refrigerant and water in the water heat exchanger 2 becomes minimum.
- ⁇ T denotes a temperature difference between the water heat exchanger inlet temperature and the water heat exchanger outlet temperature.
- Fig. 5 shows changes in operation values obtained from the temperature of each part when the opening degree of the expansion valve 3 changes.
- the horizontal axis represents the opening degree (%) of the expansion valve 3
- the vertical axis represents the suction superheat degree, discharge temperature, temperature difference ⁇ T2 between the outlet temperature of the water heat exchanger and water inlet temperature, heating ability ratio, COP ratio.
- the heating ability ratio and COP ratio show a ratio when a maximum value against the expansion valve opening degree is set as 100%, respectively.
- changes in the suction superheat degree can be regarded as almost a constant value, so that it is understood that changes in the heating ability ratio and the COP ratio cannot be judged by the suction superheat degree.
- Fig. 6 shows changes in other operation values obtained from temperatures of each part when the opening degree of the expansion valve 3 is changed.
- the horizontal axis represents the opening degree (%) of the expansion valve 3.
- the vertical axis represents an outlet/inlet temperature difference ⁇ Thx of the internal heat exchanger, a temperature difference ⁇ T between a discharge temperature and an outlet temperature of the water heat exchanger, a total temperature difference ⁇ T of the above ⁇ T1 and ⁇ T2, heating ability, and a COP ratio, respectively.
- a total temperature difference ⁇ ⁇ T of the temperature difference ⁇ Ti between the water heat exchanger inlet temperature and water outlet temperature and the temperature difference ⁇ T2 between the water heat exchanger outlet temperature and water inlet temperature becomes a minimum.
- the control based on such an index has a physical meaning and being reasonable.
- high-precision temperature detection is required because change in temperature is small in the vicinity where the COP becomes a maximum compared with the temperature difference ⁇ T.
- a temperature difference ⁇ Tp at a pinch point is almost the same as that of ⁇ T2 between the water heat exchanger outlet temperature and water inlet temperature.
- FIG. 7 is a flowchart showing a control operation of the refrigeration cycle apparatus.
- the suction superheat degree (SHs) control of the compressor 1 precedes the temperature difference ⁇ T control for securing the heating ability.
- the expansion valve opening degree is increased until the suction superheat degree (SHs) converges.
- the temperature difference ⁇ T is made to converge at the target value.
- the temperature difference ⁇ T is made to converge at the target value.
- the expansion opening degree is increased and ⁇ T is made to converge.
- ⁇ Thx When using ⁇ Thx, internal heat exchanger outlet temperature detection means 52 is attached (refer to Fig. 1 ) between a high-pressure side outlet of the internal heat exchanger 5 and an inlet of the expansion valve 3, the temperature difference ⁇ Thx is obtained from a detection temperatures by the second temperature detection means 31 and the internal heat exchanger outlet temperature detection means 52.
- the expansion valve opening degree is made to be controlled so that the COP becomes maximum based on a temperature difference ⁇ T (or ⁇ ⁇ T, ⁇ T1 - ⁇ T2, ⁇ Thx) between the discharge temperature and the water heat exchanger outlet temperature, a high efficiency refrigeration cycle apparatus can be obtained.
- a refrigerant saturation temperature (ET) is obtained based on an output of the fifth temperature detection means 32 or pressure detection means, the suction superheat degree (SHs) is obtained by the detection temperature (Ts) of the sixth temperature detection means and the refrigerant saturation temperature (ET), and the expansion valve opening degree is controlled so that the suction superheat degree (SHs) becomes a target value, so that the superheat degree of the suction part of the compressor 1 is secured , liquid return to the compressor 1 can be prevented, and reliability can be secured.
- Ts detection temperature
- ET refrigerant saturation temperature
- the fifth temperature detection means 32 is provided between the expansion valve 3 and the evaporator 4, it can be disposed at any position between the inlet of the evaporator 4 and a low-pressure side inlet of the internal heat exchanger 5.
- the control of the superheat degree precedes the control of the above temperature differences. From this point, the reliability of the compressor 1 is secured.
- the radiator is composed of the water heat exchanger, so that a high efficiency hot water supply apparatus can be obtained.
- Fig. 8 is a drawing showing a configuration of the refrigeration cycle apparatus according to the present invention.
- a first pressure detection means 35 is provided in place of the first temperature detection means 30 for detecting the discharge temperature of the compressor 1. Based on the first pressure detection means 35, a virtual saturation temperature is obtained, which is a standard condition of the water heat exchanger 2.
- the pressure detection means 35 can be shared with a pressure sensor provided, for example, to prevent an abnormal rise in high pressure. Descriptions on an operation behavior will be omitted because they are the same as Embodiment 1.
- a virtual superheat degree of the water heat exchanger 2 outlet is calculated to control the refrigerant conditions thereof.
- a virtual saturation temperature is calculated as a standard condition of the water heat exchanger 2 and from the difference between a virtual saturation temperature Tsat and outlet temperature Tcount of the water heat exchanger 2 detected by the second temperature detection means 31, a virtual superheat degree SC is obtained from the following formula.
- SC Tsat - Tcount
- the opening degree of the expansion valve 3 is controlled in the same way as the flowchart of Fig. 7 so that the SC obtained by the above formula becomes a target value (SCm) whose efficiency is maximum.
- Fig. 9 is a diagram showing an operation behavior of the refrigeration cycle apparatus according to the present invention on a P-h diagram.
- the virtual saturation temperature can be freely defined by demonstrating a definition such as a pseudo critical temperature trajectory connecting flexion points of isothermal lines like a dashed line ⁇ and a vertical line like a dotted line ⁇ extended with an enthalpy at a critical point being a constant.
- a virtual saturation temperature should be selected under which the temperature difference becomes large in the vicinity of the maximum efficiency as mentioned above.
- the virtual saturation temperature can be obtained as an intersection of a constant pressure line with a pressure at a point B, which is a detection value by first pressure detection means 35 and the dashed line ⁇ , or as an intersection of a constant pressure line with a pressure at a point B, which is a detection value by first pressure detection means 35 and the dotted line ⁇ .
- first temperature detection means 30 in Fig. 1 can be omitted and low cost can be achieved.
- superheat degree of the outlet of the water heat exchanger 2 is controlled, therefore, control of the expansion valve can be applied as it is, which has been conventionally used.
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Chemical Kinetics & Catalysis (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Pump Type And Storage Water Heaters (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
- Air Conditioning Control Device (AREA)
Abstract
a compressor (1), a radiator (2), decompression means (3), a heat absorber (4), an internal heat exchanger (5) that performs heat exchange between a refrigerant at an outlet of said radiator and the refrigerant at an outlet of said heat absorber, wherein first temperature detection means (30) for detecting a refrigerant temperature between an outlet of the compressor (1) and an inlet of the radiator (2) and second temperature detection means (31) for detecting the refrigerant temperature between the outlet of the radiator (2) and a high-pressure side inlet of the internal heat exchanger (5) are provided, and
an opening degree of decompression means (3) is controlled so that a temperature difference (ΔT) between a detection temperature by the first temperature detection means (30) and the detection temperature by the second temperature detection means (31) becomes a target value.
Description
- The present invention relates to a refrigeration cycle apparatus using an internal heat exchanger, more particularly to a refrigerant control for stably securing performance.
- Conventionally, a hot water supply apparatus is proposed as a built-in refrigeration cycle apparatus such as:
- a hot water supply apparatus comprising a refrigeration cycle including a compressor, a hot water supply heat exchanger, an electronic expansion valve, and a heat source side heat exchanger whose heat source is an external air, and a hot water supply cycle including a hot water supply heat exchanger and a hot water supply tank,
- wherein since ability control means that uses an ability-variable type compressor and ability-controls the compressor in response to changes in external environment conditions of the heat source side heat exchanger is attached, expansion valve opening degree control means for controlling an opening degree of an electronic expansion valve so as to make a discharge temperature of a compressor to be a target value in response to changes in external environment conditions (an external temperature, for example) of the heat source side heat exchanger and rotation speed control means for controlling a rotation speed of the compressor to be a target value in response to changes in the external environment conditions of the heat source side heat exchanger are attached, an opening of the electronic expansion valve is controlled so as to make the discharge temperature of the compressor becomes a target value in response to changes in the external environment conditions (an external temperature, for example) of the heat source side heat exchanger, and the rotation speed of the compressor is controlled to be a target value in response to changes in the external environment conditions of the heat source side heat exchanger, an optimal operation condition can be obtained in which a hot water supply ability and a hot water supply load further match, and a coefficient of performance (COP) can be improved and down-sizing of elements such as an heat exchanger becomes possible. (For example, refer to Patent Document 1)
- A water heater is also proposed such as:
a water heater for heating a hot water supply fluid in a supercritical heat pump cycle where a refrigerant pressure in a high pressure side becomes equal to or more than the critical pressure of the refrigerant comprising: - a compressor,
- a radiator that performs heat exchange between a refrigerant discharged from the compressor and a hot water supply fluid and is configured so that a refrigerant flow and the hot water supply fluid flow opposes,
- a decompressor for decompressing the refrigerant flowing out of the radiator, and
- an evaporator that makes the refrigerant that flows out of the compressor evaporate, makes the refrigerant absorb a heat to discharge it into a suction side of the compressor,
- wherein a refrigerant pressure of a high-pressure side is controlled so that a temperature difference (ΔT) between the refrigerant that flows out of the radiator and the hot water supply fluid that flows therein becomes a predetermined temperature difference (ΔTo). (For example, refer to Patent Document 2) In this example of the prior art, a heat exchange efficiency of the radiator can be enhanced to improve efficiency of a heat pump.
-
- [Patent Document 1] Japanese Patent Gazette No.
601369 Fig. 1 ) - [Patent Document 2] Japanese Patent Gazette No.
3227651 Fig. 2 ) - Both of the above examples of the prior art control refrigerant conditions so that a discharge temperature of the compressor or a temperature difference (ΔT) between the refrigerant that flows out of the radiator and the hot water supply fluid that flows therein becomes a target value to achieve an efficient operation. However, there was a problem that in the vicinity where an efficiency (COP) of the refrigeration cycle becomes maximum, a control based only on an inlet side (the above discharge temperature) of the radiator or an outlet side (the above temperature difference ΔT) is difficult to achieve stable and efficient operation conditions because changes in the discharge temperature or the temperature difference ΔT are small. In addition, since an operation in which an internal heat exchanger exists in the refrigerant circuit is not considered, there was a problem that to control to achieve stable and efficient operation conditions is difficult.
- The present invention is made to solve the above problems in the prior art. The object is to obtain a refrigeration cycle apparatus capable of stably achieving efficient operation conditions by controlling operation values based on standard conditions of the radiator and outlet conditions of the radiator to be a target value.
- In order to solve the above problems, the refrigeration cycle apparatus according to the present invention includes at least a compressor, a radiator, decompression means capable of changing an open degree, a heat absorber, an internal heat exchanger that performs heat exchange between a refrigerant at an outlet of the radiator and the refrigerant at the outlet of the heat absorber. The refrigeration cycle apparatus is characterized in that at least first refrigerant conditions detection means for detecting standard conditions of the radiator and second refrigerant conditions detection means for detecting refrigerant conditions between an outlet of the radiator and a high-pressure side inlet of an internal heat exchanger are provided, and an opening degree of decompression means is controlled so that a calculation value calculated based on an output of the first refrigerant conditions detection means and the output of the second refrigerant conditions detection means becomes a target value.
- According to the present invention, the expansion valve opening degree is controlled so that the COP becomes maximum based on standard conditions of the radiator and refrigerant conditions of the radiator outlet part, so that a refrigerant cycle apparatus capable of stably achieving efficient operation can be obtained.
-
- [
Fig. 1] Fig. 1 is a diagram showing a configuration of a refrigeration cycle apparatus according toEmbodiment 1 of the present invention. - [
Fig. 2] Fig. 2 is a diagram showing an operation behavior on a P-h diagram according toEmbodiment 1 of the present invention. - [
Fig. 3] Fig. 3 is a diagram showing a temperature distribution of a refrigerant and water in a water heat exchanger according toEmbodiment 1 of the present invention. - [
Fig. 4] Fig. 4 is a diagram showing cycle conditions against an expansion valve opening degree according toEmbodiment 1 of the present invention. - [
Fig. 5] Fig. 5 is a diagram showing changes in each calculation value, heating ability, and COP against an expansion valve opening degree according toEmbodiment 1 of the present invention. - [
Fig. 6] Fig. 6 is a diagram showing changes in other calculation value, heating ability, and COP against an expansion valve opening degree according toEmbodiment 1 of the present invention. - [
Fig. 7] Fig. 7 is a diagram showing a control flowchart according toEmbodiment 1 of the present invention. - [
Fig. 8] Fig. 8 is a diagram showing a refrigeration cycle apparatus according toEmbodiment 2 of the present invention. - [
Fig. 9] Fig. 9 is a diagram showing an operation behavior on a P-h diagram according toEmbodiment 2 of the present invention. -
1 compressor 2 radiator (water heat exchanger) 3 expansion valve 4 heat absorber (evaporator) 5 internal heat exchanger 20 hot water supply side pump 21 hot water storage tank 22 use side pump 23, 24, 25 on-off valve 29 blower 30, 31, 32, 33, 41, 42, 52 temperature detection means 35, 51 pressure detection means 40 controller 50 heat source apparatus 60 hot water storage apparatus - Descriptions will be given to a refrigerant cycle apparatus by
Embodiment 1 according to the present invention.
Fig. 1 shows a configuration diagram of the refrigerant cycle apparatus according to the present embodiment. In the figure, the refrigerant cycle apparatus according to the present embodiment is a hot water supply apparatus using carbon dioxide (hereinafter, CO2) as a refrigerant, composed of aheat source apparatus 50, a hotwater storage apparatus 60, and acontroller 40 for controlling these. The present embodiment shows an example of the hot water supply apparatus, however, it is not limited thereto. The apparatus may be an air conditioner. In the same way, the refrigerant is not limited to carbon dioxide but an HFC refrigerant may be used. - The
heat source apparatus 50 is composed of acompressor 1 for compressing the refrigerant, a radiator 2 (hereinafter, referred to "water heat exchanger") for taking out heat of a high-temperature high-pressure refrigerant compressed in thecompressor 1, an internal heat exchanger 5 for further cooling the refrigerant output from thewater heat exchanger 2, a decompressor 3 (hereinafter, referred to "expansion valve") that decompresses the refrigerant and whose opening degree can be changed, an heat-absorber 4 (hereinafter, referred to "evaporator") for evaporating the refrigerant decompressed in theexpansion valve 3, and an internal heat exchanger 5 for further heating the refrigerant flowed out of theevaporator 4. That is, the internal heat exchanger 5 is a heat exchanger that heat-exchanges the refrigerant at an outlet of thewater heat exchanger 2 with the refrigerant at the outlet of theevaporator 4. Ablower 29 is provided for sending air on an outer surface of theevaporator 4. There are also provided first temperature detection means 30 for detecting a discharge temperature of thecompressor 1, second temperature detection means 31 for detecting an outlet temperature of thewater heat exchanger 2, fifth temperature detection means 32 for detecting an inlet refrigerant temperature of theevaporator 4, and sixth temperature detection means 33 for detecting a suction temperature of thecompressor 1. In addition, the first temperature detection means 30 and the second temperature detection means 31 correspond to a first refrigerant conditions detection means and second refrigerant conditions detection means respectively in an example of control inFig. 7 to be described later. - A hot
water storage apparatus 60 is connected with thewater heat exchanger 2, which is a radiator, via piping, being composed of a heatsource side pump 20, a hotwater storage tank 21, ause side pump 22, and on-offvalves valves water storage tank 21 drops, the on-offvalves valve 23 is opened, and hot water storage operation is performed in which supplied water is heated up to a predetermined temperature. When a heat dissipation loss is large and the temperature in the hotwater storage tank 21 decreases such as in winter, the on-offvalves valve 24 is opened, and circulation heating operation is performed in which low-temperature hot water in the hotwater storage tank 21 is re-boiled. At the time of using the hot water supply, the on-offvalves valve 25 is opened, theuse side pump 22 starts operation to transfer stored hot water to the use side. At an inlet side of thewater heat exchanger 2, third temperature detection means 41 is attached for detecting an inlet temperature of a medium (water) to be heated. At an outlet side of thewater heat exchanger 2, fourth temperature detection means 42 is attached for detecting the outlet temperature of the medium (water) to be heated. - A
controller 40 performs calculation using detected values from first temperature detection means 30, second temperature detection means 31, fifth temperature detection means 32, sixth temperature detection means 33, third temperature detection means 41, and fourth temperature detection means 42 to control an opening degree of theexpansion valve 3, a rotation speed of thecompressor 1, and the rotation speed of the hot watersupply side pump 20, respectively. -
Fig. 2 is a P-h diagram describing cycle conditions during hot water storage operation in the refrigeration cycle apparatus shown inFig. 1 . InFig. 2 , solid lines denote refrigerant conditions at a certain expansion valve opening degree and A, B, C, D, and E denote refrigerant conditions in the hot water storage operation. At the time of the hot water storage operation, a high-temperature high-pressure refrigerant (A) discharged from thecompressor 1 flows into thewater heat exchanger 2. In thewater heat exchanger 2, the refrigerant heats supplied water while dissipating heat to water circulating the hot water storage circuit to decrease the own temperature. A refrigerant (B) flowed out of thewater heat exchanger 2 dissipates heat in the internal heat exchanger 5 to further decrease (C) the temperature, being decompressed (D) by theexpansion valve 3 to turn into a low-temperature low-pressure refrigerant. The low-temperature low-pressure refrigerant absorbs heat from the air in theevaporator 4 to evaporate (E). The refrigerant flowed out of theevaporator 4 is heated in the internal heat exchanger 5 to turn into a gas (F) and sucked by thecompressor 1 to form a refrigeration cycle. - Here, the
expansion valve 3 is controlled so that a suction superheat degree of thecompressor 1 becomes a target value (for example, 5 to 10 °C). Specifically, based on a detection value of fifth temperature detection means 32 detecting an inlet refrigerant temperature of theevaporator 4, a temperature decrease amount due to a pressure loss in theevaporator 4 and the internal heat exchanger 5 is corrected, an evaporation temperature (ET) is estimated, a suction superheat degree SHs is calculated by the following formula using a detection value (Ts) of sixth temperature detection means 33 detecting a suction temperature of thecompressor 1.
Using the above formula, an opening degree of theexpansion valve 3 is controlled so that SHs becomes a target value. An example is given in which an evaporation temperature (ET) is estimated based on the detection value of the fifth temperature detection means 32, however, it is not limited thereto. Pressure detection means (second pressure detection means) 51 (refer toFig. 1 ) is installed between a low-pressure side outlet of the internal heat exchanger 5 and the inlet of thecompressor 1, and from the detection value, a refrigerant saturation temperature may be obtained. A suction superheat degree control precedes other high efficiency operation control because a function to prevent liquid return of thecompressor 1 precedes a function to efficiently operate thewater heat exchanger 2 from the viewpoint of securing reliability of the equipment. - Next, operation on the P-h diagram in the case when the opening degree of the
expansion valve 3 is made smaller is denoted by broken lines inFig. 2 . When the opening degree ofexpansion valve 3 is made smaller, the refrigerant flow amount flowing from theexpansion valve 3 to theevaporator 4 decreases and the suction superheat degree of thecompressor 1 temporarily increases. In addition, since the refrigerant shifts to a high pressure side, the pressure on the high pressure side increases and a discharge temperature becomes high. At the same time, a water heat exchanger output temperature decreases so that a temperature difference in the becomes constant. When the water heat exchanger output temperature decreases, a heat exchange amount in the internal heat exchanger 5 decreases, and as a result, the suction superheat degree becomes almost the same state as that of before the opening degree of theexpansion valve 3 is made smaller to indicate a constant value. That is, a change in opening degree of theexpansion valve 3 is absorbed by the heat exchange amount of the internal heat exchanger 5 (the heat exchange amount varies in response to the opening degree of the expansion valve 3) to make a change in the suction superheat degree small. Accordingly, control of the suction superheat degree of thecompressor 1 alone cannot secure heating ability in thewater heat exchanger 2 and efficiency is lowered. Therefore, new control is required in order to secure heating ability and improve operation efficiency. - Next, descriptions will be given to why a local maximal value occurs in performance (COP) using a temperature distribution in the water heat exchanger shown in
Fig. 3 .
Fig. 3 shows a refrigerant and water temperature distribution in thewater heat exchanger 2. In the figure, thick solid lines show a change in refrigerant temperature, and a thin solid lines denote a change in water temperature. Δ T1 denotes a temperature difference between the water heat exchanger inlet temperature and water outlet temperature, and ΔT2 denotes a temperature difference between the water heat exchanger outlet temperature and water inlet temperature. Δ Tp is a temperature difference at a pinch point where the temperature difference between a refrigerant and water in thewater heat exchanger 2 becomes minimum. Δ T denotes a temperature difference between the water heat exchanger inlet temperature and the water heat exchanger outlet temperature. As shown by a cycle state against the expansion valve opening degree inFig. 4 , when a discharge temperature is increased by decreasing theexpansion valve 3 opening degree, under a condition when heating ability in thewater heat exchanger 2 is almost constant, the outlet temperature of thewater heat exchanger 2 decreases so that an average temperature difference of the refrigerant and water in thewater heat exchanger 2 is maintained, and the temperature difference Δ Tp of pinch point also decreases. Further, as the refrigerant amount shifts to a high pressure side, a discharge pressure rises to increase an input and COP is lowered. To the contrary, when theexpansion valve 3 opening degree is made large and the discharge temperature is lowered, the outlet temperature of thewater heat exchanger 2 increases so that an average temperature difference between the refrigerant and water in thewater heat exchanger 2 is maintained. The temperature difference ΔTp at the pinch point also increases, however, a heating ability ratio becomes small and COP is lowered. Accordingly, as shown by broken lines in the figure, a suitable expansion opening degree exists that makes COP maximum. - Next,
Fig. 5 shows changes in operation values obtained from the temperature of each part when the opening degree of theexpansion valve 3 changes. InFig. 5 , the horizontal axis represents the opening degree (%) of theexpansion valve 3, and the vertical axis represents the suction superheat degree, discharge temperature, temperature difference Δ T2 between the outlet temperature of the water heat exchanger and water inlet temperature, heating ability ratio, COP ratio. The heating ability ratio and COP ratio show a ratio when a maximum value against the expansion valve opening degree is set as 100%, respectively. Against changes in the opening degree of theexpansion valve 3, changes in the suction superheat degree can be regarded as almost a constant value, so that it is understood that changes in the heating ability ratio and the COP ratio cannot be judged by the suction superheat degree. When controlling the COP to be maximum based on the temperature difference ΔT2 between the discharge temperature and the outlet temperature of the water heat exchanger and water inlet temperature, changes in the discharge temperature and temperature difference ΔT2 are small in the vicinity of the expansion valve opening degree when the COP reaches maximum as shown by a dotted line in the figure, so that it is found that a high accuracy temperature measurement is required for controlling COP to be maximum. - Next,
Fig. 6 shows changes in other operation values obtained from temperatures of each part when the opening degree of theexpansion valve 3 is changed. InFig. 6 , the horizontal axis represents the opening degree (%) of theexpansion valve 3. The vertical axis represents an outlet/inlet temperature difference ΔThx of the internal heat exchanger, a temperature difference ΔT between a discharge temperature and an outlet temperature of the water heat exchanger, a total temperature difference ΣΔT of the above ΔT1 and ΔT2, heating ability, and a COP ratio, respectively. Characteristics ofFig. 6 shows that operation can be performed in the vicinity where the COP becomes maximum by either controlling a heat exchange amount of the internal heat exchanger 5 based on the temperature difference ΔThx between the outlet and inlet of the internal heat exchanger or controlling the heat exchange amount of thewater heat exchanger 2 based on the total temperature difference ΣΔT of ΔT1 and ΔT2 of thewater heat exchanger 2. Further, the temperature difference ΔT between the discharge temperature and the outlet temperature of the water heat exchanger significantly changes in the vicinity of the expansion valve opening degree at which the COP becomes maximum, so that it is understood that a deviation from the maximum value of the COP could be controlled to be small based on the temperature difference ΔT. Here, only the case of the temperature difference ΔT is shown, however, the same effect can be expected by controlling based on the difference (ΔT1 - ΔT2) of the temperature differences ΔT1 and ΔT2.
Thus, it is possible to achieve an operation in the vicinity of the maximum efficiency by adopting a high-pressure side outlet temperature of the internal heat exchanger 5 for ΔThx, the discharge temperature for ΔT, and the discharge temperature and a water side outlet/inlet temperatures for ΣΔT. - As is understood from
Fig. 6 , a total temperature difference Σ ΔT of the temperature difference ΔTi between the water heat exchanger inlet temperature and water outlet temperature and the temperature difference ΔT2 between the water heat exchanger outlet temperature and water inlet temperature becomes a minimum. The control based on such an index has a physical meaning and being reasonable. However, high-precision temperature detection is required because change in temperature is small in the vicinity where the COP becomes a maximum compared with the temperature difference Δ T. Further, fromFig. 3 , it is considered that when the COP becomes a maximum value, a temperature difference ΔTp at a pinch point is almost the same as that of ΔT2 between the water heat exchanger outlet temperature and water inlet temperature. This is because a maximum performance is shown when two temperature differences that become minimum in thewater heat exchanger 2 become equal without being biased to either of them when considering characteristics of the heat exchanger. Accordingly, it is allowable to control theexpansion valve 3 so as to make ΔTp and ΔT2 to be equal. - Next, descriptions will be given to an example of a control operation of the refrigeration cycle apparatus of
Fig. 1 in which an expansion valve opening degree is controlled so as to make a suction superheat degree and the above temperature difference ΔT to converge at target values.
Fig. 7 is a flowchart showing a control operation of the refrigeration cycle apparatus. With the present invention, for the purpose of giving a priority to reliability of products, the suction superheat degree (SHs) control of thecompressor 1 precedes the temperature difference ΔT control for securing the heating ability.
Firstly, when the suction superheat degree (SHs) is smaller than a target value (SHm) by a preset convergence range ΔSH or less (S101), the expansion valve opening degree is lowered until the suction superheat degree (SHs) converges. Thus, when the suction superheat degree (SHs) is secured, the temperature difference ΔT is made to converge at the target value. Specifically, when the temperature difference ΔT is smaller than a target value (ΔTm) by a preset convergence range δ T or less (S102), the expansion opening degree is lowered and ΔT is made to converge. Thus, lower limit values of the suction superheat degree (SHs) and the temperature difference ΔT can be suppressed.
Next, when the suction superheat degree (SHs) is larger than the target value (SHm) by a preset convergence range Δ SH or more (S103), the expansion valve opening degree is increased until the suction superheat degree (SHs) converges. Thus, when the suction superheat degree (SHs) is converged, the temperature difference ΔT is made to converge at the target value. Thus, when the suction superheat degree (SHs) is converged, the temperature difference ΔT is made to converge at the target value. Specifically, when the temperature difference ΔT is larger than the target value (ΔTm) by a preset convergence range δT or more (S104), the expansion opening degree is increased and ΔT is made to converge. Thus, upper limit values of the suction superheat degree (SHs) and the temperature difference ΔT can be suppressed. An example is shown in which a priority is given to control the suction superheat degree, however, it is not limited thereto when using a compressor which is resistant to liquid return. The same effect can be expected even when the priority order is exchanged. Through the above control, the suction superheat degree (SHs) and the temperature difference ΔT are converged at target values. - In the above, descriptions are given to an example in which the suction superheat degree (SHs) and the temperature difference ΔT are controlled to converge at target values (SHm, ΔTm), however, it is allowable that, in place of the temperature difference ΔT, a total temperature difference Σ ΔT of ΔT1 and ΔT2, a difference between ΔT1 and ΔT2 (ΔT1 - ΔT2), or ΔThx can be used to control them to converge at a target value, respectively. When using ΣΔT and (ΔT1 - Δ T2), they are obtained by calculating detection temperatures by the first temperature detection means 30, the second temperature detection means 31, the third temperature detection means 41, and the fourth temperature detection means 42. When using Δ Thx, internal heat exchanger outlet temperature detection means 52 is attached (refer to
Fig. 1 ) between a high-pressure side outlet of the internal heat exchanger 5 and an inlet of theexpansion valve 3, the temperature difference ΔThx is obtained from a detection temperatures by the second temperature detection means 31 and the internal heat exchanger outlet temperature detection means 52. - Since, in the present embodiment, in addition to suction superheat degree control of the compressor, the expansion valve opening degree is made to be controlled so that the COP becomes maximum based on a temperature difference ΔT (or Σ ΔT, ΔT1 - ΔT2, ΔThx) between the discharge temperature and the water heat exchanger outlet temperature, a high efficiency refrigeration cycle apparatus can be obtained.
A refrigerant saturation temperature (ET) is obtained based on an output of the fifth temperature detection means 32 or pressure detection means, the suction superheat degree (SHs) is obtained by the detection temperature (Ts) of the sixth temperature detection means and the refrigerant saturation temperature (ET), and the expansion valve opening degree is controlled so that the suction superheat degree (SHs) becomes a target value, so that the superheat degree of the suction part of thecompressor 1 is secured , liquid return to thecompressor 1 can be prevented, and reliability can be secured. In the example ofFig. 1 , descriptions are given to an example in which the fifth temperature detection means 32 is provided between theexpansion valve 3 and theevaporator 4, it can be disposed at any position between the inlet of theevaporator 4 and a low-pressure side inlet of the internal heat exchanger 5.
In the present embodiment, when controlling the superheat degree and the above temperature differences (ΔT, ΣΔT, ΔT1 - ΔT2, ΔThx), the control of the superheat degree precedes the control of the above temperature differences. From this point, the reliability of thecompressor 1 is secured.
In the present embodiment, the radiator is composed of the water heat exchanger, so that a high efficiency hot water supply apparatus can be obtained. - Descriptions will be given to a refrigeration cycle apparatus according to
Embodiment 2 of the present invention as follows.
Fig. 8 is a drawing showing a configuration of the refrigeration cycle apparatus according to the present invention. What is different fromEmbodiment 1 is that a first pressure detection means 35 is provided in place of the first temperature detection means 30 for detecting the discharge temperature of thecompressor 1. Based on the first pressure detection means 35, a virtual saturation temperature is obtained, which is a standard condition of thewater heat exchanger 2. The pressure detection means 35 can be shared with a pressure sensor provided, for example, to prevent an abnormal rise in high pressure. Descriptions on an operation behavior will be omitted because they are the same asEmbodiment 1. - In the present embodiment, like a conventional HFC refrigerant, a virtual superheat degree of the
water heat exchanger 2 outlet is calculated to control the refrigerant conditions thereof. Specifically, from first pressure detection means 35 provided in place of the first temperature detection means 30, a virtual saturation temperature is calculated as a standard condition of thewater heat exchanger 2 and from the difference between a virtual saturation temperature Tsat and outlet temperature Tcount of thewater heat exchanger 2 detected by the second temperature detection means 31, a virtual superheat degree SC is obtained from the following formula.
In the present embodiment, the opening degree of theexpansion valve 3 is controlled in the same way as the flowchart ofFig. 7 so that the SC obtained by the above formula becomes a target value (SCm) whose efficiency is maximum. - Here, how to obtain the virtual saturation temperature will be explained.
Fig. 9 is a diagram showing an operation behavior of the refrigeration cycle apparatus according to the present invention on a P-h diagram. The virtual saturation temperature can be freely defined by demonstrating a definition such as a pseudo critical temperature trajectory connecting flexion points of isothermal lines like a dashed line α and a vertical line like a dotted line β extended with an enthalpy at a critical point being a constant. However, in order to operate the refrigeration cycle apparatus stably and at the maximum efficiency, a virtual saturation temperature should be selected under which the temperature difference becomes large in the vicinity of the maximum efficiency as mentioned above. Then, the virtual saturation temperature can be obtained as an intersection of a constant pressure line with a pressure at a point B, which is a detection value by first pressure detection means 35 and the dashed line α, or as an intersection of a constant pressure line with a pressure at a point B, which is a detection value by first pressure detection means 35 and the dotted line β. - In the present embodiment, since the virtual saturation temperature is used in place of the discharge temperature of the
compressor 1, first temperature detection means 30 inFig. 1 can be omitted and low cost can be achieved. Like the conventional HFC refrigerant, superheat degree of the outlet of thewater heat exchanger 2 is controlled, therefore, control of the expansion valve can be applied as it is, which has been conventionally used.
Further Aspects of the invention comprise a refrigerant cycle apparatus comprising: - at least a compressor, a radiator, decompression means capable of changing an open degree, a heat absorber, an internal heat exchanger that performs heat exchange between a refrigerant at an outlet of said radiator and the refrigerant at an outlet of said heat absorber, wherein
- first refrigerant conditions detection means for detecting standard conditions of at least said radiator and second refrigerant conditions detection means for detecting refrigerant conditions between an outlet of said radiator and a high-pressure side inlet of said internal heat exchanger are provided, and
- an opening of said decompression means is controlled so that a calculation value calculated based on at least an output of said first refrigerant conditions detection means and the output of said second refrigerant conditions detection means becomes a target value.
- third temperature detection means for detecting an inlet temperature of a medium to be heated and fourth temperature detection means for detecting an outlet temperature of the medium to be heated, wherein
- the opening degree of said decompression means is controlled such that a calculation value calculated based on outputs of said first refrigerant condition detection means, said second refrigerant condition detection means, said third temperature detection means, and said fourth temperature detection means become a target value.
- at least a compressor, a radiator, decompression means capable of changing an open degree, a heat absorber, an internal heat exchanger that performs heat exchange between a refrigerant at an outlet of said radiator and the refrigerant at an outlet of said heat absorber, wherein
- first temperature detection means for detecting a refrigerant temperature between an outlet of said compressor and an inlet of said radiator and second temperature detection means for detecting the refrigerant temperature between an outlet of said radiator and a high-pressure side inlet of said internal heat exchanger are provided, and
- an opening degree of said decompression means is controlled such that a temperature difference (ΔT) between a detection temperature by said first temperature detection means and the detection temperature by said second temperature detection means becomes a target value.
- third temperature detection means for detecting an inlet temperature of a medium to be heated and fourth temperature detection means for detecting an outlet temperature of the medium to be heated, wherein
- the opening degree of said decompression means is controlled such that a calculation value calculated based on outputs of said first temperature detection means, said second temperature detection means, said third temperature detection means, and said fourth temperature detection means, instead of said temperature difference (ΔT), become a target value.
- at least a compressor, a radiator, decompression means capable of changing an open degree, a heat absorber, an internal heat exchanger that performs heat exchange between a refrigerant at an outlet of said radiator and the refrigerant at an outlet of said heat absorber, wherein
- first temperature detection means for detecting a refrigerant temperature between an outlet of said compressor and an inlet of said radiator and second temperature detection means for detecting the refrigerant temperature between the outlet of said radiator and a high-pressure side inlet of said internal heat exchanger, third temperature detection means for detecting an inlet temperature of a medium to be heated and fourth temperature detection means for detecting the outlet temperature of the medium to be heated are provided, and
- an opening degree of said decompression means is controlled such that a sum (ΣΔT) of a temperature difference (ΔT1) between a detection temperature by said first temperature detection means and the detection temperature by said fourth temperature detection means and the temperature difference (Δ T2) between the detection temperature by said second temperature detection means and the detection temperature by said third temperature detection means becomes a target value.
- at least a compressor, a radiator, decompression means capable of changing an open degree, a heat absorber, an internal heat exchanger that performs heat exchange between a refrigerant at an outlet of said radiator and the refrigerant at an outlet of said heat absorber, wherein
- first temperature detection means for detecting a refrigerant temperature between an outlet of said compressor and an inlet of said radiator and second temperature detection means for detecting the refrigerant temperature between the outlet of said radiator and a high-pressure side inlet of said internal heat exchanger, third temperature detection means for detecting an inlet temperature of a medium to be heated and fourth temperature detection means for detecting an outlet temperature of the medium to be heated are provided, and
- an opening degree of said decompression means is controlled such that a difference (ΔT1 - ΔT2) between a second temperature difference (ΔT1) between a detection temperature by said first temperature detection means and the detection temperature by said fourth temperature detection means and a third temperature difference (ΔT2) between the detection temperature by said second temperature detection means and the detection temperature by said third temperature detection means becomes a target value.
- at least a compressor, a radiator, decompression means capable of changing an open degree, a heat absorber, an internal heat exchanger that performs heat exchange between a refrigerant at an outlet of said radiator and the refrigerant at an outlet of said heat absorber, wherein
- first pressure detection means for detecting a refrigeration pressure between at least an outlet of said compressor and an inlet of said decompression means and second temperature detection means for detecting a refrigeration temperature between the outlet of said radiator and a high-pressure side inlet of said internal heat exchanger are provided, and
- an opening degree of said decompression means is controlled such that a calculation value calculated based on a detection pressure by said first pressure detection means and a detection temperature by said second temperature detection means becomes a target value.
- at least a compressor, a radiator, decompression means capable of changing an open degree, a heat absorber, an internal heat exchanger that performs heat exchange between a refrigerant at an outlet of said radiator and the refrigerant at an outlet of said heat absorber, wherein
- second temperature detection means for detecting a refrigerant temperature between an outlet of said radiator and a high-pressure side inlet of said internal heat exchanger and internal heat exchanger outlet temperature detection means for detecting the refrigerant temperature between a high-pressure side outlet of said internal heat exchanger and an inlet of said compression means are provided, and
- an opening degree of said decompression means is controlled such that a temperature difference (ΔThx) between a detection temperature by said second temperature detection means and the detection temperature by said internal heat exchanger outlet temperature detection means becomes a target value.
sixth temperature detection means for detecting the refrigerant temperature between a low-pressure side outlet of said internal heat exchanger and an inlet of said compressor may be provided,
superheat degree of a compressor suction part may be calculated from a refrigerant saturation temperature at a detection point of said sixth temperature detection means and a detection temperature by said sixth temperature detection means, and
the opening degree of said decompression means may be controlled such that said superheat degree becomes the target value.
In said previously mentioned refrigerant cycle apparatus
second pressure detection means may be provided between the low-pressure side outlet of said internal heat exchanger and the inlet of said compressor and
said refrigerant saturation temperature may be calculated based on a detection value of said second pressure detection means.
In said refrigerant cycle apparatus fifth temperature detection means may be provided between the inlet of said heat absorber and the low-pressure side inlet of said internal heat exchanger and
said refrigerant saturation temperature may be calculated based on the detection temperature of said fifth temperature detection means.
In said refrigerant cycle apparatus a priority may be given to control said superheat degree over said temperature difference.
In any one of said previously mentioned refrigerant cycle apparatuses said radiator may be a heat exchanger that exchanges heat with water.
In any one of said previously mentioned refrigerant cycle apparatuses carbon dioxide may be used as a refrigerant.
Claims (7)
- A refrigerant cycle apparatus comprising:at least a compressor (1), a radiator (2), decompression means (3) capable of changing an open degree, a heat absorber (4), an internal heat exchanger (5) that performs heat exchange between a refrigerant at an outlet of the radiator (2) and the refrigerant at an outlet of the heat absorber (4), whereinfirst temperature detection means (30) for detecting a refrigerant temperature between an outlet of the compressor (1) and an inlet of the radiator (2) and second temperature detection means (31) for detecting the refrigerant temperature between the outlet of the radiator (2) and a high-pressure side inlet of the internal heat exchanger (5), third temperature detection means (41) for detecting an inlet temperature of a medium to be heated and fourth temperature detection means (42) for detecting an outlet temperature of the medium to be heated are provided, andan opening degree of the decompression means (3) is controlled such that a difference (ΔT1 - ΔT2) between a second temperature difference (ΔT1) between a detection temperature by the first temperature detection means (30) and the detection temperature by the fourth temperature detection means (42) and a third temperature difference (ΔT2) between the detection temperature by the second temperature detection means (31) and the detection temperature by the third temperature detection means (41) becomes a target value.
- The refrigerant cycle apparatus of claim 1, wherein
sixth temperature detection means (33) for detecting the refrigerant temperature between a low-pressure side outlet of the internal heat exchanger (5) and an inlet of the compressor (1) is provided,
superheat degree of a compressor suction part is calculated from a refrigerant saturation temperature at a detection point of the sixth temperature detection means (33) and a detection temperature by the sixth temperature detection means (33), and
the opening degree of the decompression means (3) is controlled such that the superheat degree becomes the target value. - The refrigerant cycle apparatus of claim 2, wherein
second pressure detection means (51) is provided between the low-pressure side outlet of the internal heat exchanger (5) and the inlet of the compressor (1) and
the refrigerant saturation temperature is calculated based on a detection value of the second pressure detection means (51). - The refrigerant cycle apparatus of claim 2, wherein
fifth temperature detection means (32) is provided between the inlet of the heat absorber (4) and the low-pressure side inlet of the internal heat exchanger (5) and
the refrigerant saturation temperature is calculated based on the detection temperature of the fifth temperature detection means (32). - The refrigerant cycle apparatus of any one of claims 2 to 4, wherein
a priority is given to control the superheat degree over the temperature difference. - The refrigerant cycle apparatus of any one of claims 1 to 5, wherein
the radiator (2) is a heat exchanger that exchanges heat with water. - The refrigerant cycle apparatus of any one of claims 1 to 6, wherein
carbon dioxide is used as a refrigerant.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2007310097A JP4948374B2 (en) | 2007-11-30 | 2007-11-30 | Refrigeration cycle equipment |
EP08855672.5A EP2196745B1 (en) | 2007-11-30 | 2008-11-20 | Refrigeration cycle device |
Related Parent Applications (3)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP08855672.5 Division | 2008-11-20 | ||
EP08855672.5A Division EP2196745B1 (en) | 2007-11-30 | 2008-11-20 | Refrigeration cycle device |
EP08855672.5A Division-Into EP2196745B1 (en) | 2007-11-30 | 2008-11-20 | Refrigeration cycle device |
Publications (3)
Publication Number | Publication Date |
---|---|
EP2647925A2 true EP2647925A2 (en) | 2013-10-09 |
EP2647925A3 EP2647925A3 (en) | 2015-08-05 |
EP2647925B1 EP2647925B1 (en) | 2016-12-21 |
Family
ID=40678426
Family Applications (5)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP13166596.0A Active EP2647928B1 (en) | 2007-11-30 | 2008-11-20 | Refrigeration cycle apparatus |
EP13166595.2A Active EP2647927B1 (en) | 2007-11-30 | 2008-11-20 | Refrigeration cycle apparatus |
EP13166593.7A Active EP2647926B1 (en) | 2007-11-30 | 2008-11-20 | Refrigeration cycle apparatus |
EP13166592.9A Active EP2647925B1 (en) | 2007-11-30 | 2008-11-20 | Refrigeration cycle apparatus |
EP08855672.5A Active EP2196745B1 (en) | 2007-11-30 | 2008-11-20 | Refrigeration cycle device |
Family Applications Before (3)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP13166596.0A Active EP2647928B1 (en) | 2007-11-30 | 2008-11-20 | Refrigeration cycle apparatus |
EP13166595.2A Active EP2647927B1 (en) | 2007-11-30 | 2008-11-20 | Refrigeration cycle apparatus |
EP13166593.7A Active EP2647926B1 (en) | 2007-11-30 | 2008-11-20 | Refrigeration cycle apparatus |
Family Applications After (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP08855672.5A Active EP2196745B1 (en) | 2007-11-30 | 2008-11-20 | Refrigeration cycle device |
Country Status (7)
Country | Link |
---|---|
US (1) | US20100205987A1 (en) |
EP (5) | EP2647928B1 (en) |
JP (1) | JP4948374B2 (en) |
CN (2) | CN101842645B (en) |
DK (5) | DK2647928T3 (en) |
ES (5) | ES2823758T3 (en) |
WO (1) | WO2009069524A1 (en) |
Families Citing this family (34)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP5330915B2 (en) * | 2009-07-22 | 2013-10-30 | 株式会社前川製作所 | Dual refrigeration cycle apparatus and control method thereof |
JP5689079B2 (en) * | 2010-02-12 | 2015-03-25 | 三菱電機株式会社 | Refrigeration cycle equipment |
JP5558937B2 (en) * | 2010-06-30 | 2014-07-23 | 株式会社コロナ | Heat pump type water heater |
RU2535271C1 (en) * | 2010-10-15 | 2014-12-10 | Тосиба Кэрриер Корпорейшн | Heat source |
CN103635761A (en) * | 2011-08-04 | 2014-03-12 | 三菱电机株式会社 | Refrigeration device |
KR20130041640A (en) * | 2011-10-17 | 2013-04-25 | 엘지전자 주식회사 | Air conditioner and control method of the same |
ES2632004T3 (en) | 2011-10-25 | 2017-09-07 | Lg Electronics Inc. | Air conditioning and its operation procedure |
WO2013080244A1 (en) * | 2011-11-29 | 2013-06-06 | 三菱電機株式会社 | Refrigerating/air-conditioning device |
JP5875396B2 (en) * | 2012-02-10 | 2016-03-02 | 三菱重工業株式会社 | Heat pump control device, heat pump, and heat pump control method |
JP5861577B2 (en) * | 2012-07-05 | 2016-02-16 | 株式会社デンソー | Water heater |
JP5831423B2 (en) * | 2012-10-08 | 2015-12-09 | 株式会社デンソー | Refrigeration cycle equipment |
WO2014102940A1 (en) * | 2012-12-26 | 2014-07-03 | 三菱電機株式会社 | Refrigeration cycle device and method for controlling refrigeration cycle device |
DE102013001455A1 (en) * | 2013-01-28 | 2014-08-14 | Hochschule für angewandte Wissenschaften München | Arrangement and method for supplying heat to a building |
JP6080939B2 (en) * | 2013-02-19 | 2017-02-15 | 三菱電機株式会社 | Air conditioner |
DE102013210175A1 (en) | 2013-05-31 | 2014-12-18 | Siemens Aktiengesellschaft | Heat pump for use of environmentally friendly refrigerants |
US10605498B2 (en) * | 2014-01-23 | 2020-03-31 | Mitsubishi Electric Corporation | Heat pump apparatus |
JP5874754B2 (en) * | 2014-01-31 | 2016-03-02 | ダイキン工業株式会社 | Refrigeration equipment |
WO2015136595A1 (en) * | 2014-03-10 | 2015-09-17 | 三菱電機株式会社 | Heat pump system |
ES2883599T3 (en) * | 2014-10-09 | 2021-12-09 | Carrier Corp | Internal liquid suction heat exchanger |
US10473354B2 (en) * | 2014-12-05 | 2019-11-12 | Mitsubishi Electric Corporation | Air-conditioning apparatus |
JP6456139B2 (en) * | 2014-12-26 | 2019-01-23 | 株式会社前川製作所 | Refrigeration or air conditioner and control method thereof |
WO2017049258A1 (en) * | 2015-09-18 | 2017-03-23 | Carrier Corporation | System and method of freeze protection for a chiller |
JP2017088137A (en) * | 2015-11-17 | 2017-05-25 | 株式会社ヴァレオジャパン | Refrigeration cycle of vehicular air conditioner and vehicle mounted with the same |
JP6745657B2 (en) * | 2016-06-29 | 2020-08-26 | リンナイ株式会社 | Hot water supply system |
WO2018163345A1 (en) * | 2017-03-09 | 2018-09-13 | 三菱電機株式会社 | Heat pump hot water supply device |
WO2020075238A1 (en) * | 2018-10-10 | 2020-04-16 | 三菱電機株式会社 | Plate heat exchanger and heat pump device |
CN111854206B (en) * | 2019-04-28 | 2022-01-25 | 青岛海尔智能技术研发有限公司 | Refrigerator equipment, refrigerating system and control method of refrigerating system |
AT522875B1 (en) * | 2019-10-30 | 2021-03-15 | Lambda Waermepumpen Gmbh | Method for controlling an expansion valve |
DE102020115274A1 (en) | 2020-06-09 | 2021-12-09 | Stiebel Eltron Gmbh & Co. Kg | Method for operating a compression refrigeration system |
JP7014988B1 (en) * | 2020-12-02 | 2022-02-02 | ダイキン工業株式会社 | Refrigeration equipment |
JPWO2022162819A1 (en) * | 2021-01-28 | 2022-08-04 | ||
DE102021127213A1 (en) | 2021-10-20 | 2023-04-20 | Lauda Dr. R. Wobser Gmbh & Co. Kg | Refrigeration system and method for operating a refrigeration system |
CN114234450B (en) * | 2021-12-24 | 2023-09-08 | 山东雅士股份有限公司 | Variable frequency CO 2 Control method of water heater unit |
DE102022118670A1 (en) * | 2022-07-26 | 2024-02-01 | Lauda Dr. R. Wobser Gmbh & Co. Kg | Process cooling unit and method for controlling a process cooling unit |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP3227651B2 (en) | 1998-11-18 | 2001-11-12 | 株式会社デンソー | Water heater |
JP3601369B2 (en) | 1999-09-03 | 2004-12-15 | ダイキン工業株式会社 | Water heater |
Family Cites Families (30)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH05106922A (en) * | 1991-10-18 | 1993-04-27 | Hitachi Ltd | Control system for refrigerating equipment |
US5457965A (en) * | 1994-04-11 | 1995-10-17 | Ford Motor Company | Low refrigerant charge detection system |
EP0685692B1 (en) * | 1994-05-30 | 2004-06-09 | Mitsubishi Denki Kabushiki Kaisha | Refrigerant circulating system |
JPH0966736A (en) * | 1995-06-23 | 1997-03-11 | Denso Corp | Air conditioner for vehicle |
US5704219A (en) * | 1995-08-01 | 1998-01-06 | Nippondenso Co., Ltd. | Air conditioning apparatus |
JPH11108485A (en) * | 1997-09-30 | 1999-04-23 | Matsushita Electric Ind Co Ltd | Method for controlling air conditioner and outlet temperature of refrigerant heater |
JP2001235239A (en) * | 2000-02-23 | 2001-08-31 | Seiko Seiki Co Ltd | Supercritical vapor compressing cycle system |
US6430949B2 (en) * | 2000-04-19 | 2002-08-13 | Denso Corporation | Heat-pump water heater |
JP3737381B2 (en) * | 2000-06-05 | 2006-01-18 | 株式会社デンソー | Water heater |
JP4538919B2 (en) * | 2000-08-08 | 2010-09-08 | 三菱電機株式会社 | Indoor multi air conditioner |
JP2003176957A (en) * | 2001-10-03 | 2003-06-27 | Denso Corp | Refrigerating cycle device |
US7076964B2 (en) * | 2001-10-03 | 2006-07-18 | Denso Corporation | Super-critical refrigerant cycle system and water heater using the same |
JP3737414B2 (en) * | 2001-11-05 | 2006-01-18 | 株式会社デンソー | Water heater |
TWI263025B (en) * | 2002-01-24 | 2006-10-01 | Daikin Ind Ltd | Freezing device |
JP2004061061A (en) * | 2002-07-31 | 2004-02-26 | Matsushita Electric Ind Co Ltd | Freezing cycle device and its operation method |
US7000413B2 (en) * | 2003-06-26 | 2006-02-21 | Carrier Corporation | Control of refrigeration system to optimize coefficient of performance |
JP3915770B2 (en) * | 2003-10-31 | 2007-05-16 | 松下電器産業株式会社 | Heat pump water heater |
JP2005156030A (en) * | 2003-11-26 | 2005-06-16 | Hitachi Home & Life Solutions Inc | Heat pump apparatus |
JP4269323B2 (en) * | 2004-03-29 | 2009-05-27 | 三菱電機株式会社 | Heat pump water heater |
CN100494829C (en) * | 2004-05-20 | 2009-06-03 | 上海交通大学 | Efficient refrigerating system with high-dryness two-phase state evaporator outlet refrigerant |
EP1777471A1 (en) * | 2004-07-12 | 2007-04-25 | Denso Corporation | Heat pump-type hot-water supply device |
JP2006077998A (en) * | 2004-09-07 | 2006-03-23 | Matsushita Electric Ind Co Ltd | Refrigerating cycle device, and control method |
JP4459776B2 (en) * | 2004-10-18 | 2010-04-28 | 三菱電機株式会社 | Heat pump device and outdoor unit of heat pump device |
JP4670329B2 (en) * | 2004-11-29 | 2011-04-13 | 三菱電機株式会社 | Refrigeration air conditioner, operation control method of refrigeration air conditioner, refrigerant amount control method of refrigeration air conditioner |
US8096141B2 (en) * | 2005-01-25 | 2012-01-17 | Trane International Inc. | Superheat control by pressure ratio |
CN1862151A (en) * | 2005-05-12 | 2006-11-15 | 乐金电子(天津)电器有限公司 | Air conditioner for regenerative cooling circulation system |
JP2007093100A (en) * | 2005-09-28 | 2007-04-12 | Mitsubishi Electric Corp | Control method of heat pump water heater, and heat pump water heater |
EP1813887B1 (en) * | 2006-01-31 | 2009-05-06 | Sanyo Electric Co., Ltd. | Air conditioning device |
JP4613916B2 (en) * | 2006-03-17 | 2011-01-19 | 三菱電機株式会社 | Heat pump water heater |
JP4569508B2 (en) * | 2006-03-31 | 2010-10-27 | 株式会社デンソー | Expansion valves used in supercritical and refrigeration cycles |
-
2007
- 2007-11-30 JP JP2007310097A patent/JP4948374B2/en active Active
-
2008
- 2008-11-20 ES ES13166595T patent/ES2823758T3/en active Active
- 2008-11-20 DK DK13166596.0T patent/DK2647928T3/en active
- 2008-11-20 DK DK08855672.5T patent/DK2196745T3/en active
- 2008-11-20 DK DK13166592.9T patent/DK2647925T3/en active
- 2008-11-20 ES ES13166593T patent/ES2700938T3/en active Active
- 2008-11-20 WO PCT/JP2008/071069 patent/WO2009069524A1/en active Application Filing
- 2008-11-20 EP EP13166596.0A patent/EP2647928B1/en active Active
- 2008-11-20 CN CN2008801141141A patent/CN101842645B/en active Active
- 2008-11-20 EP EP13166595.2A patent/EP2647927B1/en active Active
- 2008-11-20 ES ES13166596.0T patent/ES2605462T3/en active Active
- 2008-11-20 US US12/738,924 patent/US20100205987A1/en not_active Abandoned
- 2008-11-20 EP EP13166593.7A patent/EP2647926B1/en active Active
- 2008-11-20 EP EP13166592.9A patent/EP2647925B1/en active Active
- 2008-11-20 EP EP08855672.5A patent/EP2196745B1/en active Active
- 2008-11-20 DK DK13166593.7T patent/DK2647926T3/en active
- 2008-11-20 CN CN201110289736.1A patent/CN102425872B/en active Active
- 2008-11-20 ES ES13166592.9T patent/ES2611980T3/en active Active
- 2008-11-20 DK DK13166595.2T patent/DK2647927T3/en active
- 2008-11-20 ES ES08855672.5T patent/ES2650233T3/en active Active
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP3227651B2 (en) | 1998-11-18 | 2001-11-12 | 株式会社デンソー | Water heater |
JP3601369B2 (en) | 1999-09-03 | 2004-12-15 | ダイキン工業株式会社 | Water heater |
Also Published As
Publication number | Publication date |
---|---|
EP2647928A2 (en) | 2013-10-09 |
JP4948374B2 (en) | 2012-06-06 |
EP2647927A2 (en) | 2013-10-09 |
EP2647925B1 (en) | 2016-12-21 |
ES2611980T3 (en) | 2017-05-11 |
EP2647928B1 (en) | 2016-10-26 |
EP2647926A2 (en) | 2013-10-09 |
EP2196745B1 (en) | 2017-11-08 |
EP2196745A1 (en) | 2010-06-16 |
CN102425872A (en) | 2012-04-25 |
CN101842645A (en) | 2010-09-22 |
DK2647928T3 (en) | 2016-12-12 |
DK2196745T3 (en) | 2017-12-11 |
EP2647927B1 (en) | 2020-09-16 |
DK2647926T3 (en) | 2019-01-07 |
ES2700938T3 (en) | 2019-02-20 |
EP2647927A3 (en) | 2015-07-29 |
WO2009069524A1 (en) | 2009-06-04 |
EP2647926B1 (en) | 2018-10-24 |
CN101842645B (en) | 2012-11-28 |
ES2605462T3 (en) | 2017-03-14 |
US20100205987A1 (en) | 2010-08-19 |
EP2647926A3 (en) | 2015-07-29 |
JP2009133547A (en) | 2009-06-18 |
ES2823758T3 (en) | 2021-05-10 |
CN102425872B (en) | 2014-06-25 |
DK2647925T3 (en) | 2017-02-06 |
EP2647925A3 (en) | 2015-08-05 |
DK2647927T3 (en) | 2020-10-19 |
EP2647928A3 (en) | 2015-08-05 |
EP2196745A4 (en) | 2013-02-13 |
ES2650233T3 (en) | 2018-01-17 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP2196745B1 (en) | Refrigeration cycle device | |
US8353173B2 (en) | Refrigerating cycle apparatus and operation control method therefor | |
CN105157266B (en) | Operation of refrigerant vapor compression system | |
JP4337880B2 (en) | Heat pump water heater | |
JP5196452B2 (en) | Transcritical refrigerant vapor compression system with charge control | |
EP2631562B1 (en) | Heat pump-type air-warming device | |
US7490481B2 (en) | Vapor compression system startup method | |
US20100023166A1 (en) | Free-cooling limitation control for air conditioning systems | |
JP2010526985A (en) | Refrigerant vapor compression system with flash tank economizer | |
JP2011521194A (en) | Filling management in refrigerant vapor compression systems. | |
KR20100123729A (en) | Refrigeration device | |
EP1709373B1 (en) | Transcritical vapor compression optimization through maximization of heating capacity | |
US6568199B1 (en) | Method for optimizing coefficient of performance in a transcritical vapor compression system | |
JP4859480B2 (en) | Turbo chiller, control device thereof, and control method of turbo chiller | |
KR101296064B1 (en) | Air conditioner and control method thereof | |
JP2019060581A (en) | Refrigeration cycle device |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
17P | Request for examination filed |
Effective date: 20130506 |
|
AC | Divisional application: reference to earlier application |
Ref document number: 2196745 Country of ref document: EP Kind code of ref document: P |
|
AK | Designated contracting states |
Kind code of ref document: A2 Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MT NL NO PL PT RO SE SI SK TR |
|
PUAL | Search report despatched |
Free format text: ORIGINAL CODE: 0009013 |
|
AK | Designated contracting states |
Kind code of ref document: A3 Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MT NL NO PL PT RO SE SI SK TR |
|
RIC1 | Information provided on ipc code assigned before grant |
Ipc: F25B 1/00 20060101AFI20150702BHEP |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R079 Ref document number: 602008048082 Country of ref document: DE Free format text: PREVIOUS MAIN CLASS: F25B0009000000 Ipc: F25B0041060000 |
|
RIC1 | Information provided on ipc code assigned before grant |
Ipc: F25B 41/06 20060101AFI20160107BHEP Ipc: F25B 9/00 20060101ALI20160107BHEP |
|
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
INTG | Intention to grant announced |
Effective date: 20160630 |
|
GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
AC | Divisional application: reference to earlier application |
Ref document number: 2196745 Country of ref document: EP Kind code of ref document: P |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MT NL NO PL PT RO SE SI SK TR |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: FG4D |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: EP |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: FG4D |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: REF Ref document number: 855846 Country of ref document: AT Kind code of ref document: T Effective date: 20170115 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R096 Ref document number: 602008048082 Country of ref document: DE |
|
REG | Reference to a national code |
Ref country code: DK Ref legal event code: T3 Effective date: 20170202 |
|
REG | Reference to a national code |
Ref country code: SE Ref legal event code: TRGR |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LV Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161221 |
|
REG | Reference to a national code |
Ref country code: LT Ref legal event code: MG4D |
|
REG | Reference to a national code |
Ref country code: NL Ref legal event code: MP Effective date: 20161221 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161221 Ref country code: NO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170321 Ref country code: GR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170322 |
|
REG | Reference to a national code |
Ref country code: ES Ref legal event code: FG2A Ref document number: 2611980 Country of ref document: ES Kind code of ref document: T3 Effective date: 20170511 |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: MK05 Ref document number: 855846 Country of ref document: AT Kind code of ref document: T Effective date: 20161221 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: FI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161221 Ref country code: HR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161221 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: NL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161221 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: EE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161221 Ref country code: CZ Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161221 Ref country code: RO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161221 Ref country code: IS Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170421 Ref country code: SK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161221 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: AT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161221 Ref country code: BG Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170321 Ref country code: PT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170421 Ref country code: PL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161221 Ref country code: BE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161221 Ref country code: IT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161221 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R097 Ref document number: 602008048082 Country of ref document: DE |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 10 |
|
PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
26N | No opposition filed |
Effective date: 20170922 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161221 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MC Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161221 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LI Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20171130 Ref country code: CH Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20171130 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LU Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20171120 |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: MM4A |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20171120 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 11 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20171120 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R084 Ref document number: 602008048082 Country of ref document: DE |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: 746 Effective date: 20190122 |
|
REG | Reference to a national code |
Ref country code: ES Ref legal event code: GC2A Effective date: 20190416 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: HU Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO Effective date: 20081120 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: CY Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20161221 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: TR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161221 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R079 Ref document number: 602008048082 Country of ref document: DE Free format text: PREVIOUS MAIN CLASS: F25B0041060000 Ipc: F25B0041300000 |
|
P01 | Opt-out of the competence of the unified patent court (upc) registered |
Effective date: 20230512 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: GB Payment date: 20230928 Year of fee payment: 16 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: FR Payment date: 20230929 Year of fee payment: 16 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: ES Payment date: 20231201 Year of fee payment: 16 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: SE Payment date: 20231002 Year of fee payment: 16 Ref country code: DK Payment date: 20231116 Year of fee payment: 16 Ref country code: DE Payment date: 20230929 Year of fee payment: 16 |