GB2555738A - Air conditioner - Google Patents

Air conditioner Download PDF

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Publication number
GB2555738A
GB2555738A GB1720060.1A GB201720060A GB2555738A GB 2555738 A GB2555738 A GB 2555738A GB 201720060 A GB201720060 A GB 201720060A GB 2555738 A GB2555738 A GB 2555738A
Authority
GB
United Kingdom
Prior art keywords
refrigerant
indoor
plate
rate control
flow rate
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
Application number
GB1720060.1A
Other versions
GB2555738B (en
GB2555738C (en
GB201720060D0 (en
GB2555738A9 (en
Inventor
Azuma Koji
Koge Hirofumi
Morimoto Osamu
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
Priority date (The priority date 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 date listed.)
Filing date
Publication date
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Publication of GB201720060D0 publication Critical patent/GB201720060D0/en
Publication of GB2555738A publication Critical patent/GB2555738A/en
Publication of GB2555738B publication Critical patent/GB2555738B/en
Publication of GB2555738A9 publication Critical patent/GB2555738A9/en
Application granted granted Critical
Publication of GB2555738C publication Critical patent/GB2555738C/en
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F25B41/00—Fluid-circulation arrangements
    • 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
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
    • F25B29/003—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously of the compression type system
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F25B41/22—Disposition of valves, e.g. of on-off valves or flow control valves between evaporator and 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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0062—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by spaced plates with inserted elements
    • F28D9/0068—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by spaced plates with inserted elements with means for changing flow direction of one heat exchange medium, e.g. using deflecting zones
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0062—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by spaced plates with inserted elements
    • F28D9/0075—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by spaced plates with inserted elements the plates having openings therein for circulation of the heat-exchange medium from one conduit to another
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0093—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F27/00—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus
    • F28F27/02—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus for controlling the distribution of heat-exchange media between different channels
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0231—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units with simultaneous cooling and heating
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0233—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel arrangements
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/025—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units
    • F25B2313/0253—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units in parallel arrangements
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/23—Separators
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/18—Optimization, e.g. high integration of refrigeration components
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles

Abstract

In an air conditioner according to the present invention, a second branching section and a heat exchange section are formed integrally by a multilayer plate in which a plurality of plate members are layered. The multilayer plate and a valve device of a first branching section are arranged side by side in the width direction within a housing.

Description

(54) Title of the Invention: Air conditioner Abstract Title: Air conditioner (57) In an air conditioner according to the present invention, a second branching section and a heat exchange section are formed integrally by a multilayer plate in which a plurality of plate members are layered. The multilayer plate and a valve device of a first branching section are arranged side by side in the width direction within a housing.
[08]
Figure GB2555738A_D0001
(a)
200
Figure GB2555738A_D0002
SO 10,12
Cb)
AA Back surface BB Front surface CC Side surface σ>
Figure GB2555738A_D0003
OGS
LL v
2/9 πρ ο rio. Ζ
220
Figure GB2555738A_D0004
221 240 231 ί
242
3/9
FIG. 3
Figure GB2555738A_D0005
Figure GB2555738A_D0006
co t?)
Figure GB2555738A_D0007
fcS Sk OOS ίό
Figure GB2555738A_D0008
200
Figure GB2555738A_D0009
{
200'
L
Figure GB2555738A_D0010
I }
LL
8/9
FIG. 8
Figure GB2555738A_D0011
FRONT
SURFACE
SIDE SURFACE (a) (b)
FI A ib. y f ’ BACK......
|_ SURFACE 2Q0 LAMINATING DIRECTION <-
Figure GB2555738A_D0012
TO FIRST
CONNECTION PI BE 6
FROM GAS-LiQUID SEPARATION DEVICE 12
TO INDOOR UNIT ¢WIDTH DIRECTION OF CASING
9/9
Figure GB2555738A_D0013
200
Figure GB2555738A_D0014
242
FROM SECOND CONNECTION PIPE 7
DESCRIPTION
Title of Invention
AIR-CONDITIONING APPARATUS AND RELAY UNIT
Technical Field [0001]
The present invention relates to an air-conditioning apparatus including a refrigerant circuit and having a structure configured to supply one or both of heating energy and cooling energy generated by a heat source unit to a plurality of loads. Background Art [0002]
In a related art, there has been proposed an air-conditioning apparatus, which includes a heat source unit including a compressor, a switching valve, and a heat source unit-side heat exchanger, a plurality of indoor units each including an indoorside heat exchanger and an indoor-side flow rate control device, and a relay unit being interposed between the heat source unit and the plurality of indoor units and configured to switch a flow of refrigerant fed from the heat source unit to the indoor units, and is configured to perform a cooling operation, a heating operation, or a simultaneous cooling and heating operation (for example, see Patent Literature 1). [0003]
In the air-conditioning apparatus disclosed in Patent Literature 1, the relay unit includes a first branch portion, a second branch portion, a gas-liquid separation device, a heat exchange portion, a plurality of flow rate control devices, and flow passage pipes connecting those components, and the components are accommodated in a casing. Further, the first branch portion includes a plurality of valve devices configured to switch flow paths of refrigerant. The second branch portion includes two check valves for one indoor unit, and has a configuration of forming a refrigerant path in accordance with a direction of refrigerant flowing through the indoor-side heat exchanger of the indoor unit.
Citation List
Patent Literature [0004]
Patent Literature 1: International Publication WO 2013/094174 A Summary of Invention Technical Problem [0005]
With regard to a relay unit of an air-conditioning apparatus, downsizing has been desired. However, in the air-conditioning apparatus disclosed in Patent Literature 1, the casing of the relay unit accommodates, for example, the plurality of valve devices, the plurality of check valves, the gas-liquid separation device, the heat exchange portion, the plurality of flow rate control devices, and the flow passage pipes connecting those components. Therefore, even when the check valves are formed into block valves in consideration of downsizing, there is a limit of reduction in size. Further, a flow passage pipe connecting the second branch portion, which includes the plurality of check valves, and the heat exchanger to each other is required, with the result that a pipe configuration in the casing of the relay unit is complicated.
[0006]
The present invention has been made to solve the above-mentioned problems, and has an object to provide an air-conditioning apparatus capable of achieving downsizing and downweighting of the relay unit, and cost reduction.
Solution to Problem [0007]
According to one embodiment of the present invention, there is provided an airconditioning apparatus, including: a heat source unit including a compressor, a switching valve, and a heat source unit-side heat exchanger; a plurality of indoor units each including an indoor-side heat exchanger, and an indoor-side flow rate control device, the heat source unit and the plurality of indoor units being connected to each other by a first connection pipe and a second connection pipe, the air-conditioning apparatus being configured to perform a cooling operation, a heating operation, or a simultaneous cooling and heating operation by feeding the refrigerant from the heat source unit to the plurality of indoor units; and a relay unit, which is interposed between the heat source unit and the plurality of indoor units, and is configured to switch a flow of the refrigerant fed from the heat source unit to the plurality of indoor units, the relay unit including: a first branch portion including a valve device configured to switch and connect one of an outlet and an inlet for the refrigerant in the indoor-side heat exchanger of each of the plurality of indoor units to the first connection pipe or the second connection pipe; a second branch portion having one end connected to the second connection pipe side and an other end divided into a plurality of branches and connected to an other of the outlet and the inlet for the refrigerant in the indoor-side heat exchanger of the each of the plurality of indoor units through intermediation of the indoor-side flow rate control device; a bypass flow passage for connecting the second branch portion and the first connection pipe to each other through intermediation of the bypass flow rate control device; a heat exchange portion configured to perform heat exchange between the bypass flow passage, which extends between the bypass flow rate control device and the first connection pipe, and the second branch portion; and a casing for accommodating the first branch portion, the second branch portion, the bypass flow passage, and the heat exchange portion, the second branch portion and the heat exchange portion being integrally formed of a laminated plate including a plurality of plate-shaped members which are laminated on one another, the laminated plate and the valve device of the first branch portion being arranged next to each other in a width direction in the casing.
Advantageous Effects of Invention [0008]
With the air-conditioning apparatus according to one embodiment of the present invention, the second branch portion and the heat exchange portion are integrally formed of the laminated plate including the plurality of plate-shaped members which are laminated on one another, and the laminated plate and the valve device of the first branch portion are arranged next to each other in the width direction in the casing. Therefore, the relay unit can be downsized.
Brief Description of Drawings [0009] [Fig. 1] Fig. 1 is an overall configuration diagram for mainly illustrating a 5 refrigerant system of an air-conditioning apparatus according to an embodiment of the present invention.
[Fig. 2] Fig. 2 is an exploded perspective view of a laminated plate 200 in the air-conditioning apparatus 100 according to the embodiment of the present invention.
[Fig. 3] Fig. 3 is a diagram for illustrating details of the laminated plate 200 in 10 the air-conditioning apparatus 100 according to the embodiment of the present invention.
[Fig. 4] Fig 4 is a diagram for illustrating an operation state of a cooling operation in the air-conditioning apparatus according to the embodiment of the present invention.
[Fig. 5] Fig. 5 is a diagram for illustrating an operation state of a heating operation in the air-conditioning apparatus according to the embodiment of the present invention.
[Fig. 6] Fig. 6 is a diagram for illustrating an operation state of a cooling main operation in the air-conditioning apparatus according to the embodiment of the present invention.
[Fig. 7] Fig. 7 is a diagram for illustrating an operation state of a heating main operation in the air-conditioning apparatus according to the embodiment of the present invention.
[Figs. 8(a) and 8(b)] Figs. 8(a) and 8(b) are views for schematically illustrating a 25 component arrangement in a relay unit E of the air-conditioning apparatus according to the embodiment of the present invention.
[Fig. 9] Fig. 9 is a perspective view for schematically illustrating positions of openings of the laminated plate 200 in the air-conditioning apparatus 100 according to the embodiment of the present invention.
[Fig. 10] Fig. 10 is a perspective view for schematically illustrating a positional relationship between a position of an opening 230 of the laminated plate 200 and a position of a gas-liquid separation device 12 in the air-conditioning apparatus 100 according to the embodiment of the present invention.
Description of Embodiments [0010]
Now, description is made of an embodiment of the present invention with reference to the drawings. In the drawings referred to below including Fig. 1, the size relationship between components may be different from the reality in some cases. Further, in the drawings referred to below including Fig. 1, the same or corresponding parts are represented by the same reference symbols, and the same applies hereinafter throughout the specification. Further, the forms of the constituent elements described herein are only examples, and the present invention is not limited to the forms thus described.
[0011]
Fig. 1 is an overall configuration diagram for mainly illustrating a refrigerant system of an air-conditioning apparatus 100 according to the embodiment of the present invention.
As illustrated in Fig. 1, the air-conditioning apparatus 100 includes a heat source unit A, indoor units B, C, and D (hereinafter each simply referred to as indoor unit unless otherwise mentioned), and a relay unit E, which are connected to each other.
The heat source unit A has a function of supplying heating energy or cooling energy to the indoor units.
As described later, the indoor units are connected to each other in parallel, and have the same configuration. Each indoor unit has a function of performing airconditioning of a space to be air-conditioned such as an indoor space by heating energy or cooling energy supplied from the heat source unit A.
The relay unit E is interposed between the heat source unit A and the indoor units, and has a function of switching the flow of refrigerant supplied from the heat source unit A in response to a request from the indoor units.
[0012]
A four-way switching valve 2 of the heat source unit A and the relay unit E are connected to each other by a thick first connection pipe 6. Indoor-side heat exchangers 5 of the indoor units and the relay unit E are connected to each other by first connection pipes 6b, 6c, and 6d on the indoor unit side, which correspond to the first connection pipe 6.
A heat source unit-side heat exchanger 3 of the heat source unit A and the relay unit E are connected to each other by a second connection pipe 7 which is thinner than the first connection pipe 6. The indoor-side heat exchangers 5 of the indoor units and the relay unit E are connected to each other by the first connection pipe 6, and are also connected to each other by second connection pipes 7b, 7c, and 7d on the indoor unit side, which correspond to the second connection pipe 7.
[0013] (Heat Source Unit A)
The heat source unit A includes a compressor 1 with variable capacity, the four-way switching valve 2 configured to switch a flow direction of the refrigerant in the heat source unit A, the heat source unit-side heat exchanger 3 that functions as an evaporator or condenser (radiator), an accumulator 4 that is connected to a suction side of the compressor 1 through the four-way switching valve 2, and a heat source unit-side switching valve 40 configured to limit the flow direction of the refrigerant. The four-way switching valve 2 corresponds to the switching valve of the present invention. However, the switching valve may include a combination of valves such as a two-way valve and a three-way valve, instead of the four-way switching valve.
[0014]
The heat source unit-side heat exchanger 3 includes a first heat source unitside heat exchanger 41, a second heat source unit-side heat exchanger 42, a heat source unit-side bypass passage 43, a first solenoid on-off valve 44, a second solenoid on-off valve 45, a third solenoid on-off valve 46, a fourth solenoid on-off valve 47, and a fifth solenoid on-off valve 48. In the heat source unit-side heat exchanger 3, there is provided a heat source unit-side fan 20 configured to control a heat exchange capacity of the heat source unit-side heat exchanger 3.
[0015]
The first heat source unit-side heat exchanger 41 and the second heat source unit-side heat exchanger 42 have an equal heat transfer area, and are connected to each other in parallel.
The heat source unit-side bypass passage 43 is connected to the first heat source unit-side heat exchanger 41 and the second heat source unit-side heat exchanger 42 in parallel.
The first solenoid on-off valve 44 is provided at one end of the first heat source unit-side heat exchanger 41 on a side of connection to the four-way switching valve 2.
The second solenoid on-off valve 45 is provided at an other end of the first heat source unit-side heat exchanger 41.
The third solenoid on-off valve 46 is provided at one end of the second heat source unit-side heat exchanger 42 on a side of connection to the four-way switching valve 2.
The fourth solenoid on-off valve 47 is provided at an other end of the second heat source unit-side heat exchanger 42.
The fifth solenoid on-off valve 48 is provided in the middle of the heat source unit-side bypass passage 43.
[0016]
The heat source unit-side switching valve 40 includes a third check valve 32, a fourth check valve 33, a fifth check valve 34, and a sixth check valve 35.
The third check valve 32 is provided in the middle of a pipe coupling the heat source unit-side heat exchanger 3 and the second connection pipe 7 to each other, and allows a flow of refrigerant only in a direction from the heat source unit-side heat exchanger 3 to the second connection pipe 7.
The fourth check valve 33 is provided in the middle of a pipe coupling the fourway switching valve 2 of the heat source unit A and the first connection pipe 6 to each other, and allows a flow of refrigerant only in a direction from the first connection pipe to the four-way switching valve 2.
The fifth check valve 34 is provided in the middle of a pipe coupling the fourway switching valve 2 of the heat source unit A and the second connection pipe 7 to each other, and allows a flow of refrigerant only in a direction from the four-way switching valve 2 to the second connection pipe 7.
The sixth check valve 35 is provided in the middle of a pipe coupling the heat source unit-side heat exchanger 3 and the first connection pipe 6 to each other, and allows a flow of refrigerant only in a direction from the first connection pipe 6 to the heat source unit-side heat exchanger 3.
[0017] (Indoor Units)
The indoor units each include the indoor-side heat exchanger 5 and first flow rate control device (indoor-side flow rate control device) 9. The indoor-side heat exchanger 5 functions as a condenser (radiator) or an evaporator. The first flow rate control device 9 is controlled in accordance with the superheating amount on an outlet side of the indoor-side heat exchanger 5 during cooling, and is controlled in accordance with subcooling amounts on the outlet side of the indoor-side heat exchanger 5 during heating.
[0018] (Relay Unit E)
In the relay unit E, there are provided a first branch portion 10, a second branch portion 11, a gas-liquid separation device 12, a second flow rate control device 13, a first bypass flow passage 14, a third flow rate control device 15, and heat exchange portions (first heat exchange portion 19 and second heat exchange portion 16).
[0019]
The first branch portion 10 has a function of switchably connecting the first connection pipes 6b, 6c, and 6d on the indoor unit side and the first connection pipe 6 side or the second connection pipe 7 side.
The first branch portion 10 includes fourth flow rate control devices (branch8 side flow rate control devices) 55 that are connected to the respective first connection pipes 6b, 6c, and 6d on the indoor unit side and to the first connection pipe 6, and solenoid valves 31 as valve devices that are connected to the respective first connection pipes 6b, 6c, and 6d on the indoor unit side and to the first connection pipe 6 side.
[0020]
The second branch portion 11 has one end connected to the second connection pipe 7 side and an other end dividing into a plurality of branches to be connected to the second connection pipes 7b, 7c, and 7d on the indoor unit side.
Further, the second branch portion 11 and the heat exchange portions (first heat exchange portion 19 and second heat exchange portion 16) are integrally formed of a laminated plate 200 including a plurality of laminated plate-shaped members.
[0021]
Now, with reference to Fig. 2 and Fig. 3, description is made of a detailed configuration of the laminated plate 200.
Fig. 2 is an exploded perspective view of the laminated plate 200 in the airconditioning apparatus 100 according to the embodiment of the present invention.
Fig. 3 is a diagram for illustrating details of the laminated plate 200 in the airconditioning apparatus 100 according to the embodiment of the present invention.
In the laminated plate 200, a plurality of plates (plate-shaped members) are laminated and joined by brazing or other methods so as to be integrally formed into, for example, a cuboidal shape.
In the laminated plate 200, between an outer surface plate 201 and an outer surface plate 207, there are provided low-pressure plates 202 and 206 and a highpressure plate 204, which are laminated while sandwiching heat exchange plates 203 and 205. That is, in the laminated plate 200, there are provided the outer surface plate 201, the low-pressure plate 202, the heat exchange plate 203, the high-pressure plate 204, the heat exchange plate 205, the low-pressure plate 206, and the outer surface plate 207, which are laminated in the stated order.
In this embodiment, as one example, description is made of a case in which the two low-pressure plates 202 and 206 and the one high-pressure plate 204 are provided. However, the present invention is not limited to this configuration.
For example, three low-pressure plates and two high-pressure plates may be laminated while sandwiching heat exchange plates. That is, it is only necessary that a relationship in which the number of low-pressure plates is larger than the number of high-pressure plates by one be satisfied.
[0022]
The low-pressure plates 202 and 206 have low-pressure flow passages 210 being refrigerant flow passages. The low-pressure flow passages 210 communicate between an opening 220 of the outer surface plate 201 and to an opening 221 of the outer surface plate 207. That is, the refrigerant having flowed in through the opening 221 of the outer surface plate 207 passes through the low-pressure flow passage 210 and flows out through the opening 220 of the outer surface plate 201.
The high-pressure plate 204 has a high-pressure flow passage 211 being a refrigerant flow passage. The high-pressure flow passage 211 communicates between an opening 230 of the outer surface plate 201 and to an opening 231 of the outer surface plate 207. That is, the refrigerant having flowed in through the opening 230 of the outer surface plate 201 passes through the high-pressure flow passage 211 and flows out through the opening 231 of the outer surface plate 207.
[0023]
The high-pressure plate 204 and the low-pressure plates 202 and 206 are laminated while sandwiching the heat exchange plates 203 and 205.
The high-pressure flow passage 211 and the low-pressure flow passage 210 construct the first heat exchange portion 19, and the refrigerant flowing through the high-pressure flow passage 211 and the refrigerant flowing through the low-pressure flow passage 210 exchange heat through intermediation of the heat exchange plates 203 and 205.
[0024]
Further, the high-pressure plate 204 has a branch flow passage 212 being a refrigerant flow passage. The branching flow passage 212 has one end communicating with an opening 240 of the outer surface plate 207 and an other end dividing into a plurality of branches and communicating with openings 241 of the outer surface plate 201. The branching flow passage 212 constructs the second branch portion 11.
Further, the high-pressure plate 204 has a second bypass flow passage 51 having one end connected to the branching flow passage 212 (opening 240 of outer surface plate 207) and an other end communicating with an opening 242 of the outer surface plate 207.
The number of branches of the branching flow passage 212 illustrated in Fig. 2 is one example, and the openings 241 are formed in accordance with the number of branches of the branching flow passage 212.
[0025]
The branching flow passage 212 and the low-pressure flow passage 210 construct the second heat exchange portion 16, and the refrigerant flowing through the branching flow passage 212 and the refrigerant flowing through the low-pressure flow passage 210 exchange heat through intermediation of the heat exchange plates 203 and 205.
[0026]
As described above, in the laminated plate 200, the plurality of plate-shaped members are laminated, and the second branch portion 11, the first heat exchange portion 19, and the second heat exchange portion 16 are integrally formed.
[0027]
Fig. 1 is referred back.
The gas-liquid separation device 12 has an inlet for the refrigerant connected to the second connection pipe 7, and has a function of separating the refrigerant in a two-phase gas-liquid state into a gas phase and a liquid phase. In the gas-liquid separation device 12, an outlet for gas-phase part is connected to the solenoid valve 31 of the first branch portion 10, and an outlet for liquid-phase part is connected to the high-pressure flow passage 211 (first heat exchange portion 19) of the laminated plate 200.
The second flow rate control device 13 has one end connected to the gas-liquid separation device 12 through intermediation of the high-pressure flow passage 211 (first heat exchange portion 19) of the laminated plate 200, and an other end connected to the branching flow passage 212 (second branch portion 11) of the laminated plate 200. The second flow rate control device 13 is constructed by, for example, an electric expansion valve which is openable and closable.
[0028]
The third flow rate control device (bypass flow rate control device) 15 has one end connected to the low-pressure flow passage 210 of the laminated plate 200 through intermediation of the first bypass flow passage 14, and an other end connected to the branching flow passage 212 (second branch portion 11) of the laminated plate 200 through intermediation of the second bypass flow passage 51. The third flow rate control device 15 is constructed by, for example, an electric expansion valve which is openable and closable.
[0029] (Measurement Devices)
The relay unit E includes a first pressure detection unit 25, a second pressure detection unit 26, and a third pressure detection unit 56, which are each constructed by, for example, a pressure sensor.
The first pressure detection unit 25 is provided between the first branch portion 10 and the second flow rate control device 13 on the second connection pipe 7, and is configured to detect a pressure of refrigerant.
The second pressure detection unit 26 is provided between the second flow rate control device 13 and the first flow rate control device 9, and is configured to detect a pressure of refrigerant.
The third pressure detection unit 56 is provided at a position where the first connection pipe 6 and the first bypass flow passage 14 are connected, and is configured to detect a pressure of refrigerant.
[0030]
In the heat source unit A, there is provided a fourth pressure detection unit 18 which is constructed by, for example, a pressure sensor. The fourth pressure detection unit 18 is provided in the middle of a pipe connecting the four-way switching valve 2 and a discharge portion of the compressor 1 to each other, and is configured to detect a pressure of refrigerant.
[0031]
The indoor unit includes a first temperature detection unit 53 and a second temperature detection unit 54, which are each constructed by, for example, a temperature sensor.
The first temperature detection unit 53 is provided in the indoor unit on the first branch portion 10 side, and is configured to detect a temperature of the refrigerant.
The second temperature detection unit 54 is provided in the indoor unit on the second branch portion 11 side, and is configured to detect a temperature of the refrigerant.
In other words, the first temperature detection unit 53 and the second temperature detection unit 54 are provided at both ends of the indoor-side heat exchanger 5. The second temperature detection unit 54 is connected on the first flow rate control device 9 side, whereas the first temperature detection unit 53 is connected to the other end.
[0032]
The air-conditioning apparatus 100 includes a controller 70, which is constructed by, for example, a microcomputer. The controller 70 integrally controls the entire system of the air-conditioning apparatus 100. Specifically, the controller 70 controls a driving frequency of the compressor 1, a rotation speed of each of the heat source unit-side fan 20 and a fan provided in the indoor-side heat exchanger 5, switching of the four-way switching valve 2, opening and closing of each solenoid valve, an opening degree of each expansion device, and other conditions. In other words, based on information detected by the temperature detection unit and the pressure detection unit as described above and an instruction from a remote controller (not shown), the controller 70 controls respective actuators (driving components for the compressor 1, the four-way switching valve 2, each solenoid valve (first solenoid on-off valve 44 to fifth solenoid on-off valve 48 and solenoid valve 31), each expansion device (first flow rate control device 9, second flow rate control device 13, third flow rate control device 15, and fourth flow rate control device 55) and other devices).
[0033]
A type of the refrigerant to be filled in the air-conditioning apparatus 100 is not particularly limited, and, for example, there may be used any of a natural refrigerant such as carbon dioxide (CO2), a hydrocarbon, and helium, an alternative refrigerant that does not contain chlorine, such as HFC410A, HFC407C (zeotropic refrigerant mixture in which HFC-R32/R125/R134a are mixed at a ratio of 23/25/52 wt%), and HFC404A, and a fluorocarbon refrigerant such as R22 and R134a used for existing products
An example of the case where the heat source unit-side heat exchanger 3 and the indoor-side heat exchanger 5 exchange heat between the refrigerant and air has been described, but the heat may also be exchanged between the refrigerant and a heat medium other than air, for example, water and brine.
[0034]
In addition, this embodiment describes an example of the case where the airconditioning apparatus 100 includes one heat source unit A, but the present invention is not limited thereto. The air-conditioning apparatus 100 may include two or more heat source units A. Further, description is made of an example of the case where the air-conditioning apparatus 100 includes three indoor units, but the present invention is not limited thereto. The air-conditioning apparatus 100 may include four or more indoor units. The controller 70 may be installed in any one of the heat source unit A, the indoor unit, and the relay unit E, and may also be installed in all of the heat source unit A, the indoor unit, and the relay unit E. In addition, the controller 70 may also be installed separately from the heat source unit A, the indoor unit, and the relay unit E. In addition, in the case of constructing the controller 70 with a plurality of components, the components only need to be communicably connected to each other by wired or wireless connection.
[0035] (Operation)
Next, description is made of an operation of the air-conditioning apparatus 100 [0036] [Cooling Operation]
Fig 4 is a diagram for illustrating an operation state of a cooling operation in the air-conditioning apparatus according to the embodiment of the present invention.
With reference to Fig. 4, description is made of an operation state for a cooling only operation. In Fig. 4, a state where the cooling operation is performed by all of the indoor units B, C, and D is exemplified.
[0037]
As illustrated in Fig. 4, high-temperature and high-pressure refrigerant gas discharged from the compressor 1 passes through the four-way switching valve 2, and, in the heat source unit-side heat exchanger 3, exchanges heat with air sent by the heat source unit-side fan 20 with variable air-sending amount, to thereby be condensed and liquefied. After that, this refrigerant sequentially passes through the third check valve 32, the second connection pipe 7, and the gas-liquid separation device 12, and then passes through the first heat exchange portion 19 of the laminated plate 200 and the second flow rate control device 13. At this time, an opening degree of the second flow rate control device 13 is controlled to be fully opened.
[0038]
The refrigerant having passed through the second flow rate control device 13 branches in the second branch portion 11, passes through the second connection pipes 7b, 7c, and 7d on the indoor unit side, and flows into the indoor units B, C, and D.
Then, the refrigerant having flowed into each of the indoor units B, C, and D is decompressed into low-pressure refrigerant by the first flow rate control device 9 that is controlled in accordance with the outlet superheating amount of each indoor-side heat exchanger 5. The decompressed refrigerant flows into the indoor-side heat exchanger 5, and exchanges heat with indoor air in the indoor-side heat exchanger 5 to be evaporated and gasified, thereby cooling the indoor space.
Then, the refrigerant in this gas state is sucked by the compressor 1 after passing through the first connection pipes 6b, 6c, and 6d on the indoor unit side, the fourth flow rate control devices 55 in the first branch portion 10, the first connection pipe 6, the fourth check valve 33, and through the four-way switching valve 2 and the accumulator 4 in the heat source unit. In this way, the circulation cycle is constructed to perform the cooling operation.
[0039]
At this time, each solenoid valve 31 in the first branch portion 10 is controlled to be closed. Further, the refrigerant naturally flows into the third check valve 32 and the fourth check valve 33, because the first connection pipe 6 is at low pressure and the second connection pipe 7 is at high pressure.
In addition, the opening degree of the fourth flow rate control device 55 is controlled based on the state of the refrigerant, which is obtained by the detection information from the third pressure detection unit 56.
[0040]
Further, in this circulation cycle, part of the refrigerant having passed through the second flow rate control device 13 passes through the second bypass flow passage 51 formed in the laminated plate 200 and flows into the third flow rate control device 15.
Then, the refrigerant having flowed into the third flow rate control device 15 is decompressed into low-pressure refrigerant, and thereafter passes through the first bypass flow passage 14 and flows into the second heat exchange portion 16 of the laminated plate 200. The low-pressure refrigerant having flowed into the second heat exchange portion 16 exchanges heat with the high-pressure refrigerant having flowed from the second flow rate control device 13 into the second branch portion 11 (branching flow passage 212).
Further, in the first heat exchange portion 19, the low-pressure refrigerant having passed through the second heat exchange portion 16 exchanges heat with the refrigerant before flowing into the second flow rate control device 13, to thereby be evaporated. The low-pressure refrigerant having evaporated enters the first connection pipe 6 and the fourth check valve 33, and passes through the four-way switching valve 2 and the accumulator 4 in the heat source unit to be sucked by the compressor 1.
[0041]
Meanwhile, the refrigerant having flowed out from the gas-liquid separation device 12 is cooled by exchanging heat in the first heat exchange portion 19 and the second heat exchange portion 16 with the refrigerant having been decompressed into the low-pressure refrigerant by the third flow rate control device 15, to thereby be subcooled. Then, the refrigerant flows into the indoor units B, C, and D for cooling through the second branch portion 11.
The capacity of the compressor 1 with variable capacity and the air-sending amount of the heat source unit-side fan 20 are adjusted so that the evaporating temperature of the indoor unit and the condensing temperature of the heat source unit-side heat exchanger 3 reach predetermined target temperatures, thereby being capable of obtaining target cooling capacity in each indoor unit. The condensing temperature of the heat source unit-side heat exchanger 3 can be obtained as saturation temperature for the pressure detected by the fourth pressure detection unit 18.
[0042] [Heating Operation]
Fig 5 is a diagram for illustrating an operation state of a heating operation in the air-conditioning apparatus according to the embodiment of the present invention.
With reference to Fig. 5, description is made of an operation state for a heating only operation. In Fig. 5, a state where the heating operation is performed by all of the indoor units B, C, and D is exemplified.
[0043]
As illustrated in Fig. 5, the high-temperature and high-pressure refrigerant gas discharged from the compressor 1 passes sequentially through the four-way switching valve 2, the fifth check valve 34, the second connection pipe 7, the gasliquid separation device 12, the solenoid valves 31 in the first branch portion 10, and the first connection pipes 6b, 6c, and 6d on the indoor unit side, and flows into the indoor units B, C, and D. The refrigerant having flowed into each of the indoor units B, C, and D exchanges heat with indoor air to be condensed and liquefied, thereby heating the indoor space. Then, the refrigerant in this state is controlled in accordance with the outlet subcooling amount of each indoor-side heat exchanger 5, and passes through the first flow rate control device 9.
[0044]
The refrigerant having passed through the first flow rate control device 9 flows from the second connection pipes 7b, 7c, and 7d on the indoor unit side into the second branch portion 11 of the laminated plate 200. At this time, the opening degree of the second flow rate control device 13 is controlled to be fully opened, and the refrigerant having flowed into the second branch portion 11 is led to the second bypass flow passage 51 and flows into the third flow rate control device 15. The refrigerant having flowed into the third flow rate control device 15 is decompressed into low-pressure two-phase gas-liquid refrigerant.
[0045]
Then, the refrigerant having flowed into the third flow rate control device 15 is decompressed into low-pressure refrigerant, and thereafter passes through the first bypass flow passage 14 and flows into the second heat exchange portion 16 of the laminated plate 200. In the second heat exchange portion 16, the low-pressure refrigerant exchanges heat with the high-pressure refrigerant having flowed from the second flow rate control device 13 into the second branch portion 11 (branching flow passage 212).
The low-pressure refrigerant having flowed out from the second heat exchange portion 16 passes through first heat exchange portion 19, and flows through the first connection pipe 6 into the sixth check valve 35 and the heat source unit-side heat exchanger 3 in the heat source unit A. Then, the low-pressure refrigerant exchanges heat in the heat source unit A with air sent by the heat source unit-side fan 20 with variable air-sending amount, to thereby be evaporated. The refrigerant in the gas state resulting from the evaporation is sucked by the compressor 1 after passing through the four-way switching valve 2 and the accumulator 4. In this way, the circulation cycle is constructed to perform the heating operation.
[0046]
At this time, each solenoid valve 31 is controlled to be opened. In addition, the fourth flow rate control device 55 is closed.
[0047]
In addition, in the circulation cycle, the refrigerant naturally flows into the fifth check valve 34 and the sixth check valve 35, because the first connection pipe 6 is at low pressure and the second connection pipe 7 is at high pressure.
The capacity of the compressor 1 with variable capacity and the air-sending amount of the heat source unit-side fan 20 are adjusted so that the condensing temperature of the indoor unit and the evaporating temperature of the heat source unit-side heat exchanger 3 reach predetermined target temperatures, thereby being capable of obtaining target heating capacity in each indoor unit.
[0048] [Cooling Main Operation]
Fig. 6 is a diagram for illustrating an operation state of a cooling main operation in the air-conditioning apparatus according to the embodiment of the present invention.
With reference to Fig. 6, description is made of an operation state of the cooling main operation being a simultaneous cooling and heating operation in which a cooling operation capacity is larger than a heating operation capacity. In Fig. 6, the cooling main operation in a case where there are a cooling request from each of the indoor units B and C and a heating request from the indoor unit D is exemplified. [0049]
As illustrated in Fig. 6, the high-temperature and high-pressure refrigerant gas discharged from the compressor 1 flows into the heat source unit-side heat exchanger 3 through the four-way switching valve 2, and exchanges heat in the fourway switching valve 2 with air sent by the heat source unit-side fan 20 with variable air-sending amount, thereby being brought into a two-phase high-temperature and high-pressure state.
[0050]
The capacity of the compressor 1 with variable capacity and the air-sending amount of the heat source unit-side fan 20 are adjusted so that the evaporating temperature and the condensing temperature of the indoor unit reach predetermined target temperatures. In addition, the heat transfer area is adjusted by opening and closing the first solenoid on-off valve 44, the second solenoid on-off valve 45, the third solenoid on-off valve 46, and the fourth solenoid on-off valve 47 at both ends of the first heat source unit-side heat exchanger 41 and the second heat source unit-side heat exchanger 42. In addition, by opening and closing the fifth solenoid on-off valve 48 in the heat source unit-side bypass passage 43, a flow rate of the refrigerant having flowed in the first heat source unit-side heat exchanger 41 and the second heat source unit-side heat exchanger 42 is controlled. In this way, it is possible to obtain a freely-selected heat exchange amount in the heat source unit-side heat exchanger 3, and to obtain target heating capacity or cooling capacity in each indoor unit.
[0051]
Subsequently, the refrigerant in the two-phase high-temperature and highpressure state is sent to the gas-liquid separation device 12 in the relay unit E through the third check valve 32 and the second connection pipe 7, and is separated into gas-state refrigerant and liquid-state refrigerant.
Then, the gas-state refrigerant separated by the gas-liquid separation device 12 passes sequentially through the solenoid valve 31 in the first branch portion 10 and the first connection pipe 6d on the indoor unit side, and flows into the indoor unit D for heating. Then, the gas-state refrigerant exchanges heat with indoor air by the indoor-side heat exchanger 5 to be condensed and liquefied, thereby heating the indoor space. Further, the refrigerant, which flows out of the indoor-side heat exchanger 5, passes through the first flow rate control device 9 that is controlled in accordance with the outlet subcooling amount of the indoor-side heat exchanger 5 in the indoor unit D to be decompressed to a small extent, and flows into the second branch portion 11. The refrigerant having flowed into the second branch portion 11 merges with the refrigerant having passed through the second flow rate control device 13, and part of the refrigerant is led to the second bypass flow passage 51.
[0052]
Meanwhile, the liquid refrigerant having been separated in the gas-liquid separation device 12 is cooled by exchanging heat with the refrigerant having been decompressed into the low-pressure refrigerant in the first heat exchange portion 19, and flows into the second flow rate control device 13. The second flow rate control device 13 is controlled in accordance with a pressure detected by the first pressure detection unit 25 and a pressure detected by the second pressure detection unit 26. The refrigerant having passed through the second flow rate control device 13 flows into the second branch portion 11 and merges with the refrigerant having passed through the indoor unit D for heating. After that, the refrigerant flows into the second heat exchange portion 16 and is cooled in the second heat exchange portion 16. [0053]
Then, the refrigerant having been cooled by the second heat exchange portion 16 passes through the second connection pipes 7b and 7c on the indoor unit side, and flows into the indoor units B and C for cooling. The refrigerant having flowed into each of the indoor units B and C enters the first flow rate control device 9 that is controlled in accordance with the outlet superheating amount of the indoor-side heat exchanger 5 in each of the indoor units B and C to be decompressed, and then enters the indoor-side heat exchanger 5 and exchanges heat to be evaporated into a gas state, thereby cooling the indoor space. Subsequently, the refrigerant flows into the first connection pipe 6 through the fourth flow rate control device 55.
[0054]
Part of the refrigerant having passed from second branch portion 11 through the second bypass flow passage 51 flows into the third flow rate control device 15. The third flow rate control device 15 is controlled so that a difference between the pressure detected by the first pressure detection unit 25 and the pressure detected by the second pressure detection unit 26 falls within a predetermined range.
The refrigerant having flowed into the third flow rate control device 15 is decompressed into low-pressure refrigerant, and thereafter passes through the first bypass flow passage 14 and flows into the second heat exchange portion 16 of the laminated plate 200. The low-pressure refrigerant having flowed into the second heat exchange portion 16 exchanges heat with the high-pressure refrigerant having flowed from the second flow rate control device 13 into the second branch portion 11 (branching flow passage 212).
[0055]
Further, the low-pressure refrigerant having passed through the second heat exchange portion 16 is evaporated by exchanging heat with the refrigerant before flowing into the second flow rate control device 13 in the first heat exchange portion 19. The evaporated low-pressure refrigerant flows into the first connection pipe 6 and merges with the refrigerant having passed through the indoor units B and C.
The refrigerant having merged in the first connection pipe 6 passes through the fourth check valve 33, the four-way switching valve 2, and the accumulator 4 in the heat source unit A and is sucked into the compressor 1. The circulation cycle is constructed in such a manner to perform the cooling main operation.
[0056]
At this time, the solenoid valves 31 connected to the indoor units B and C are controlled to be closed, and the solenoid valve 31 connected to the indoor unit D is controlled to be opened.
In addition, the fourth flow rate control devices 55 connected to the indoor units B and C are opened, and the fourth flow rate control device 55 connected to the indoor unit D is closed.
[0057]
In addition, the refrigerant naturally flows into the third check valve 32 and the fourth check valve 33, because the first connection pipe 6 is at low pressure and the second connection pipe 7 is at high pressure.
[0058] [Heating Main Operation]
Fig. 7 is a diagram for illustrating an operation state of a heating main operation in the air-conditioning apparatus according to the embodiment of the present invention.
With reference to Fig. 7, description is made of an operation state of the heating main operation being a simultaneous cooling and heating operation in which the heating operation capacity is larger than the cooling operation capacity. In Fig. 7, the heating main operation in a case where there are the heating request from each of the indoor units B and C and the cooling request from the indoor unit D is exemplified.
[0059]
As illustrated in Fig. 7, the high-temperature and high-pressure refrigerant gas discharged from the compressor 1 is sent to the relay unit E through the four-way switching valve 2, the fifth check valve 34, and the second connection pipe 7, and passes through the gas-liquid separation device 12. The refrigerant having passed through the gas-liquid separation device 12 passes sequentially through the solenoid valves 31 in the first branch portion 10 and the first connection pipes 6b and 6c on the indoor unit side, and flows into the indoor units B and C for heating. Then, the refrigerant exchanges heat with indoor air in each indoor-side heat exchanger 5 to be condensed and liquefied, thereby heating the indoor space. The refrigerant thus condensed and liquefied is controlled in accordance with the outlet subcooling amount of the indoor-side heat exchanger 5 in each of the indoor units B and C, and passes through the first flow rate control device 9 to be decompressed to a small extent. Then, the refrigerant flows into the second branch portion 11. Part of the refrigerant having flowed into the second branch portion 11 is led to the second bypass flow passage 51.
[0060]
Remainder of the refrigerant having flowed into the second branch portion 11 flows out from the second branch portion 11, passes through the second connection pipe 7d on the indoor unit side, and enters the indoor unit D for cooling. Then, the refrigerant after entering the indoor unit D enters the first flow rate control device 9 that is controlled in accordance with the outlet superheating amount of the indoor-side heat exchanger 5 to be decompressed, and subsequently enters the indoor-side heat exchanger 5 and exchanges heat to be evaporated into a gas state, thereby cooling the indoor space. Then, the refrigerant flows into the first connection pipe 6 through the fourth flow rate control device 55.
[0061]
Meanwhile, part of the refrigerant having passed from second branch portion 11 through the second bypass flow passage 51 flows into the third flow rate control device 15. The third flow rate control device 15 is controlled so that the difference between the pressure detected by the first pressure detection unit 25 and the pressure detected by the second pressure detection unit 26 falls within a predetermined range.
The refrigerant having flowed into the third flow rate control device 15 is decompressed into low-pressure refrigerant, and thereafter passes through the first bypass flow passage 14 and flows into the second heat exchange portion 16 of the laminated plate 200. The low-pressure refrigerant having flowed into the second heat exchange portion 16 is evaporated by exchanging heat with the refrigerant having flowed from the indoor units B and C into the second branch portion 11 (branching flow passage 212) and with the refrigerant having flowed from the second branch portion 11 into the indoor unit D for cooling.
[0062]
Then, the low-pressure refrigerant having passed through the second heat exchange portion 16 flows into the first connection pipe 6 and merges with the refrigerant having passed through the indoor unit D. The refrigerant having merged in the first connection pipe 6 flows into the sixth check valve 35 and the heat source unit-side heat exchanger 3 in the heat source unit A. The refrigerant having flowed into the heat source unit-side heat exchanger 3 exchanges heat with air sent by the heat source unit-side fan 20 with variable air-sending amount, to thereby be evaporated into a gas state.
[0063]
The capacity of the compressor 1 with variable capacity and the air-sending amount of the heat source unit-side fan 20 are adjusted so that the evaporating temperature of the indoor unit D with a request for cooling and the condensing temperature of each of the indoor units B and C with a request for heating fall within predetermined target temperatures. In addition, the heat transfer area is adjusted by opening and closing the first solenoid on-off valve 44, the second solenoid on-off valve 45, the third solenoid on-off valve 46, and the fourth solenoid on-off valve 47 at both ends of the first heat source unit-side heat exchanger 41 and the second heat source unit-side heat exchanger 42. In addition, by opening and closing the fifth solenoid on-off valve 48 in the heat source unit-side bypass passage 43, the flow rate of the refrigerant flowing in the first heat source unit-side heat exchanger 41 and the second heat source unit-side heat exchanger 42 is controlled. In this way, it is possible to obtain a freely-selected heat exchange amount in the heat source unitside heat exchanger 3, and to obtain target heating capacity or cooling capacity in each indoor unit. Then, the refrigerant is sucked by the compressor 1 after passing through the four-way switching valve 2 and the accumulator 4 in the heat source unit A. In this way, the circulation cycle is constructed to perform the heating main operation.
[0064]
At this time, the solenoid valves 31 connected to the indoor units B and C are controlled to be opened, and the solenoid valve 31 connected to the indoor unit D is controlled to be closed. In addition, the fourth flow rate control devices 55 connected to the indoor units B and C are closed, and the fourth flow rate control device 55 connected to the indoor unit D is opened.
In addition, the refrigerant naturally flows into the fifth check valve 34 and the sixth check valve 35, because the first connection pipe 6 is at low pressure and the second connection pipe 7 is at high pressure. At this time, the second flow rate control device 13 is closed.
[0065] [Arrangement Configuration in Relay Unit E]
Figs. 8(a) and 8(b) are views for schematically illustrating a component arrangement in the relay unit E of the air-conditioning apparatus according to the embodiment of the present invention.
With reference to Figs. 8(a) and 8(b), description is made of an arrangement relationship of components provided in the relay unit E. Fig. 8(a) is a plan view of the relay unit E, and Fig. 8(b) is a side view of the relay unit E.
In Figs. 8(a) and 8(b), the second flow rate control device 13 and the third flow rate control device 15 are illustrated as actuators 80.
[0066]
As illustrated in Fig. 8(a), the laminated plate 200, the first branch portion 10 (valve device), the gas-liquid separation device 12, and the actuators 80 are arranged so as not to overlap each other in plan view. Further, as illustrated in Fig. 8(b), the laminated plate 200, the first branch portion 10 (valve device), and the actuators 80 are arranged next to each other in a width direction in the casing of the relay unit E. [0067]
As described above, the air-conditioning apparatus 100 according to the embodiment of the present invention includes the laminated plate 200 integrally formed of the second branch portion 11 and the heat exchange portions (first heat exchange portion 19 and second heat exchange portion 16). Therefore, downsizing is achieved while avoiding complication of the pipe configuration in the relay unit E. [0068]
Further, the laminated plate 200, the first branch portion 10 (valve device), the gas-liquid separation device 12, and the actuators 80 are arranged so as not to overlap in plan view, thereby being capable of achieving downsizing particularly in a height direction of the casing. Therefore, such a configuration is effective in a case in which the relay unit E is provided at a location involving a restriction in the height direction.
Further, the laminated plate 200, the first branching portion 10 (valve device), and the actuators 80 are arranged next to each other in the width direction in the casing of the relay unit E, thereby being capable of shortening the flow passage pipe, thereby achieving further downsizing and downweighting of the relay unit E, and reducing the manufacturing cost.
[0069] [Positions of Openings of Laminated Plate 200]
Fig. 9 is a perspective view for schematically illustrating positions of the openings of the laminated plate 200 in the air-conditioning apparatus 100 according to the embodiment of the present invention.
As illustrated in Fig. 9, the plurality of plates (plate-shaped members) of the laminated plate are arranged so that a laminating direction thereof becomes the width direction of the casing of the relay unit E. The openings 220, 221,230, 231, 240,
241, and 242 (hereinafter simply referred to as openings unless otherwise distinguished) of the laminated plate 200 are formed at an end portion of a side surface in the width direction. For example, when the laminated plate 200 is formed into a rectangular shape, the openings are arranged next to each other along each side of the laminated plate 200.
[0070]
Through formation of the openings of the laminated plate 200 in the side surface as described above, the connection pipe (flow passage pipe) with functional components such as the first branch portion 10 arranged on the side-surface side of the laminated plate 200 can be shortened, thereby being capable of achieving downsizing while avoiding complication of the pipe configuration in the relay unit E.
Further, through formation of the openings of the laminated plate 200 at the end portion, the functional components such as the first branch portion 10 can be arranged on the side-surface side of the laminated plate 200 without interference with, for examples, pipes connected to the openings.
[0071]
Further, as illustrated in Fig. 9, the openings 241 to which the indoor-side heat exchangers 5 of the indoor units are connected are formed at the lower end portion on the front surface side of the casing of the relay unit E.
Therefore, the second connection pipes 7b, 7c, and 7d connecting the indoorside heat exchangers 5 of the indoor units and the relay unit E to each other can be shortened in the casing of the relay unit E, thereby being capable of achieving downsizing while avoiding complication of the pipe configuration in the casing of the relay unit E. Further, the interference of the second connection pipes 7b, 7c, and 7d with functional components in the casing of the relay unit E can be reduced.
[0072]
Further, as illustrated in Fig. 9, the second flow rate control device 13 and the third flow rate control device 15 are arranged closer to the back surface side than the laminated plate 200 in the casing of the relay unit E.
The relay unit E is often provided at a location involving a restriction in installation space, such as a back of a ceiling. Therefore, at the time of maintenance, an operator often places his or her body into an inspection hole communicating with an installation space, to thereby perform a unit maintenance for the relay unit E. However, the front surface side of the relay unit E is highly dominated by pipes connected to the indoor unit, and hence it is preferred that the maintenance be performed from the back surface side of the relay unit E.
In view of such a circumstance, the actuators 80, such as the second flow rate control device 13 and the third flow rate control device 15, are arranged on the back surface side of the casing of the relay unit E. Therefore, the maintenance of the actuators 80 can be performed from the back surface side of the relay unit E.
[0073]
Further, as illustrated in Fig. 9, in the laminated plate 200, the opening 231 and the opening 240 to which the second flow rate control device 13 is connected and the opening 221 and the opening 242 to which the third flow rate control device 15 is connected are formed on the back surface side of the casing of the relay unit E.
Therefore, the flow passage pipe connecting the second flow rate control device 13 to the opening 231 and the opening 240 and the flow passage pipe connecting the third flow rate control device 15 to the opening 221 and the opening 242 can be shortened. Therefore, downsizing can be achieved while avoiding complication of the pipe configuration in the relay unit E.
[0074]
Further, as illustrated in Fig. 9, the opening 231 and the opening 240 to which the second flow rate control device 13 is connected are formed along the same side of the laminated plate 200. Further, the opening 221 and the opening 241 to which the third flow rate control device 15 is connected are formed along the same side of the laminated plate 200.
Therefore, the flow passage pipe connecting the second flow rate control device 13 to the opening 231 and the opening 240 can be arranged along the side of the laminated plate 200, thereby being capable of increasing a space for arranging the actuators 80, such as the second flow rate control device 13 and the third flow rate control device 15 on the side surface of the laminated plate 200. Further, the flow passage pipe can be linearly arranged, thereby being capable of shortening the flow passage pipe. Therefore, downsizing can be achieved while avoiding complication of the pipe configuration in the relay unit E.
[0075]
Fig. 10 is a perspective view for schematically illustrating a positional relationship between the position of the opening 230 of the laminated plate 200 and the gas-liquid separation device 12 in the air-conditioning apparatus 100 according to the embodiment of the present invention. In Fig. 10, illustration of some openings is omitted.
As illustrated in Fig. 10, the gas-liquid separation device 12 separates the refrigerant, which has flowed in through the inlet 121, into the gas phase and the liquid phase, and then causes the refrigerant in the liquid-phase state to flow out through the outlet 122 for the liquid-phase part and causes the refrigerant in the gas29 phase state to flow out through the outlet 123 for the gas-phase part.
The gas-liquid separation device 12 and the laminated plate 200 are arranged next to each other in the width direction in the casing of the relay unit E. Further, the opening 230 of the laminated plate 200 to which the outlet 122 for the liquid-phase part in the gas-liquid separation device 12 is connected is formed at a position closer to the outlet 122 for the liquid-phase part as compared to the inlet 121 for the refrigerant in the gas-liquid separation device 12. For example, as illustrated in Fig. 10, the opening 230 is arranged at a position closer to the side surface on a side opposite to the side surface on the inlet 121 side of the gas-liquid separation device 12, that is, the side surface to which the second connection pipe 7 is connected.
With such an arrangement, the flow passage pipe connecting the outlet 122 for the liquid-phase part of the gas-liquid separation device 12 and the opening 230 of the laminated plate 200 can be shortened. Therefore, downsizing can be achieved while avoiding complication of the pipe configuration in the relay unit E.
[0076]
There is employed a structure in which the sensors such as the first pressure detection unit 25 and the second pressure detection unit 26 and the actuators such as the second flow rate control device 13 and the third flow rate control device 15 are directly inserted to the laminated plate 200, thereby being capable of omitting the connection pipes and achieving further downsizing and downweighting of the relay unit E.
[0077]
When the laminated plate 200 is made of aluminum, and other components such as the flow passage pipes connected to the laminated plate 200 are also made of aluminum, corrosion-prevention measures can be reduced.
There is a tendency that a pipe using aluminum is increased in wall thickness to secure strength, and there is difficulty in handling such as bending. However, application of the above-mentioned arrangement relationship of the components can shorten the flow passage pipes and deal with the arrangement of connection with straight pipes.
Reference Signs List [0078] compressor 2 four-way switching valve 3 heat source unit-side heat exchanger 4 accumulator 5 indoor-side heat exchanger 6 first connection pipe 6b first connection pipe 6c first connection pipe 6d first connection pipe 7 second connection pipe 7b second connection pipe 7c second connection pipe 7d second connection pipe 9 first flow rate control device 10 first branch portion 11 second branch portion 12 gas-liquid separation device 13 second flow rate control device 14 first bypass flow passage 15 third flow rate control device 16 second heat exchange portion 18 fourth pressure detection unit 19 first heat exchange portion 20 heat source unit-side fan 22 opening 25 first pressure detection unit26 second pressure detection unit 31 solenoid valve32 third check valve 33 fourth check valve 34 fifth check valve 35 sixth check valve 40 heat source unit-side switching valve41 first heat source unit-side heat exchanger 42 second heat source unit-side heat exchanger 43 heat source unit-side bypass passage 44 first solenoid on-off valve 45 second solenoid on-off valve 46 third solenoid on-off valve 47 fourth solenoid on-off valve48 fifth solenoid onoff valve 51 second bypass flow passage 53 first temperature detection unit 54 second temperature detection unit third pressure detection unit
100 air-conditioning apparatus
200 laminated plate 201 outer surface plate 202 low-pressure plate
203 heat exchange plate 204 high-pressure plate205 heat exchange plate 206 low-pressure plate 207 outer surface plate 210 low-pressure flow passage 211 high-pressure flow passage 212 branching flow passage fourth flow rate control device controller 80 actuators
121 inlet 122 outlet 123 outlet
220 opening 240 opening B indoor unit
221 opening 241 opening C indoor unit
230 opening 242 opening D indoor unit
231 opening A heat source unit E relay unit

Claims (9)

  1. CLAIMS [Claim 1]
    An air-conditioning apparatus, comprising:
    a heat source unit comprising a compressor, a switching valve, and a heat source unit-side heat exchanger;
    a plurality of indoor units each comprising an indoor-side heat exchanger, and an indoor-side flow rate control device, the heat source unit and the plurality of indoor units being connected to each other by a first connection pipe and a second connection pipe, the air-conditioning apparatus being configured to perform a cooling operation, a heating operation, or a simultaneous cooling and heating operation by feeding refrigerant from the heat source unit to the plurality of indoor units; and a relay unit interposed between the heat source unit and the plurality of indoor units, and configured to switch a flow of the refrigerant fed from the heat source unit to the plurality of indoor units, the relay unit comprising a first branch portion comprising a valve device configured to connect one of an outlet and an inlet for the refrigerant in the indoor-side heat exchanger of each of the plurality of indoor units to the first connection pipe or the second connection pipe, a second branch portion having one end connected to the second connection pipe side and an other end divided into a plurality of branches and connected to an other of the outlet and the inlet for the refrigerant in the indoor-side heat exchanger of the each of the plurality of indoor units through intermediation of the indoor-side flow rate control device, a bypass flow passage for connecting the second branch portion and the first connection pipe to each other through intermediation of a bypass flow rate control device, a heat exchange portion configured to perform heat exchange between the bypass flow passage extending between the bypass flow rate control device and the first connection pipe, and the second branch portion, and a casing for accommodating the first branch portion, the second branch portion, the bypass flow passage, and the heat exchange portion, the second branch portion and the heat exchange portion being integrally formed of a laminated plate including a plurality of plate-shaped members laminated on one another, the laminated plate and the valve device of the first branch portion being arranged next to each other in a width direction in the casing.
  2. [Claim 2]
    The air-conditioning apparatus of claim 1, wherein the laminated plate, the valve device of the first branch portion, and the bypass flow rate control device of the bypass flow passage are arranged so as not to overlap each other in plan view.
  3. [Claim 3]
    The air-conditioning apparatus of claim 1 or 2, further comprising a flow passage pipe for forming a flow passage between the laminated plate and the first connection pipe, the second connection pipe, and the bypass flow rate control device, wherein the flow passage pipe and the laminated plate are directly connected to each other.
  4. [Claim 4]
    The air-conditioning apparatus of claim 3, wherein the laminated plate and the flow passage pipe are made of aluminum.
  5. [Claim 5]
    The air-conditioning apparatus of any one of claims 1 to 4, wherein the plurality of plate-shaped members of the laminated plate are arranged so that a laminating direction of the plurality of plate-shaped members is in the width direction of the casing, wherein the plurality of plate-shaped members comprise a plate-shaped member having a refrigerant flow passage and a plate-shaped member having a plurality of openings communicating with the refrigerant flow passage, and wherein the plurality of openings of the plate-shaped member are formed at an end portion of a side surface in the width direction.
  6. [Claim 6]
    The air-conditioning apparatus of claim 5, wherein, among from the plurality of openings of the plate-shaped member, an opening to which the indoor-side heat exchanger is connected is formed at a lower end portion on a front surface side of the casing.
  7. [Claim 7]
    The air-conditioning apparatus of claim 5 or 6, wherein the bypass flow rate control device is arranged on a back surface side with respect to the laminated plate in the casing, and wherein, among from the plurality of openings of the plate-shaped member, two openings to which the bypass flow rate control device is connected are formed on the back surface side of the casing.
  8. [Claim 8]
    The air-conditioning apparatus of claim 7, wherein, among from the plurality of openings of the plate-shaped member, the two openings to which the bypass flow rate control device is connected are formed along a same side of the plate-shaped member.
  9. [Claim 9]
    The air-conditioning apparatus of any one of claims 5 to 8, further comprising a gas-liquid separation device configured to separate the refrigerant into a gas phase and a liquid phase, wherein the gas-liquid separation device and the laminated plate are arranged next to each other in the width direction in the casing, wherein the gas-liquid separation device having an inlet for the refrigerant connected to the second connection pipe, an outlet for gas-phase part connected to the first branch portion, and an outlet for liquid-phase part connected to the second branch portion of the laminated plate, and wherein, in the laminated plate, among from the plurality of openings of the plate-shaped member, an opening to which the gas-liquid separation device is connected is formed at a position closer to the outlet for liquid-phase part as compared to the inlet of the gas-liquid separation device.
GB1720060.1A 2015-05-26 2015-05-26 Air conditioning apparatus and relay unit Expired - Fee Related GB2555738C (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2015/065135 WO2016189667A1 (en) 2015-05-26 2015-05-26 Air conditioner

Publications (5)

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GB2555738A true GB2555738A (en) 2018-05-09
GB2555738B GB2555738B (en) 2020-09-02
GB2555738A9 GB2555738A9 (en) 2020-10-21
GB2555738C GB2555738C (en) 2020-11-11

Family

ID=57393854

Family Applications (1)

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Country Status (3)

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JP (1) JP6395930B2 (en)
GB (1) GB2555738C (en)
WO (1) WO2016189667A1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020227373A1 (en) * 2019-05-07 2020-11-12 Carrier Corporation Heat exchange apparatus

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0611203A (en) * 1992-06-25 1994-01-21 Mitsubishi Electric Corp Air conditioning apparatus
JP2000346488A (en) * 1999-05-31 2000-12-15 Mitsubishi Electric Corp Air conditioner
WO2014106901A1 (en) * 2013-01-07 2014-07-10 三菱電機株式会社 Air conditioner device

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0611203A (en) * 1992-06-25 1994-01-21 Mitsubishi Electric Corp Air conditioning apparatus
JP2000346488A (en) * 1999-05-31 2000-12-15 Mitsubishi Electric Corp Air conditioner
WO2014106901A1 (en) * 2013-01-07 2014-07-10 三菱電機株式会社 Air conditioner device

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020227373A1 (en) * 2019-05-07 2020-11-12 Carrier Corporation Heat exchange apparatus

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WO2016189667A1 (en) 2016-12-01
GB2555738B (en) 2020-09-02
JP6395930B2 (en) 2018-09-26
GB2555738C (en) 2020-11-11
GB201720060D0 (en) 2018-01-17
JPWO2016189667A1 (en) 2018-01-18
GB2555738A9 (en) 2020-10-21

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