U.S. patent application number 12/673902 was filed with the patent office on 2011-01-27 for air conditioning-hot water supply combined system.
This patent application is currently assigned to MITSUBISHI ELECTRIC CORPORATION. Invention is credited to Satoshi Akagi, Junichi Kameyama, Kousuke Tanaka, Hironori Yabuuchi, Kouji Yamashita.
Application Number | 20110016897 12/673902 |
Document ID | / |
Family ID | 40951839 |
Filed Date | 2011-01-27 |
United States Patent
Application |
20110016897 |
Kind Code |
A1 |
Akagi; Satoshi ; et
al. |
January 27, 2011 |
AIR CONDITIONING-HOT WATER SUPPLY COMBINED SYSTEM
Abstract
There is provided a heat pump apparatus bringing heating water
to a high temperature by connecting one or a plurality of load-side
units to one heat source-side unit. The air conditioning-hot water
supply combined system (heat pump apparatus) includes a heat
source-side unit equipped with an air conditioning compressor, a
four-way valve, and an outdoor heat exchanger; and the load-side
units equipped with an air conditioning throttle, an indoor heat
exchanger, a second compressor, a second load-side heat exchanger,
and a second flow rate control unit. Here, a main circuit is
configured by sequentially connecting the air conditioning
compressor, the four-way valve, the outdoor heat exchanger, the air
conditioning throttle, and the indoor heat exchanger, using a
high-pressure side connection piping and a low-pressure side
connection piping. On the other hand, a load-side refrigerant
circuit is configured by sequentially connecting the second
compressor, a second load-side heat exchanger second load-side heat
exchanger, the second flow rate control unit, and the indoor heat
exchanger using a load-side refrigerant piping.
Inventors: |
Akagi; Satoshi; (Tokyo,
JP) ; Yamashita; Kouji; (Tokyo, JP) ; Tanaka;
Kousuke; (Tokyo, JP) ; Kameyama; Junichi;
(Tokyo, JP) ; Yabuuchi; Hironori; (Tokyo,
JP) |
Correspondence
Address: |
BUCHANAN, INGERSOLL & ROONEY PC
POST OFFICE BOX 1404
ALEXANDRIA
VA
22313-1404
US
|
Assignee: |
MITSUBISHI ELECTRIC
CORPORATION
Chiyoda-ku
JP
|
Family ID: |
40951839 |
Appl. No.: |
12/673902 |
Filed: |
February 4, 2008 |
PCT Filed: |
February 4, 2008 |
PCT NO: |
PCT/JP2008/051722 |
371 Date: |
February 17, 2010 |
Current U.S.
Class: |
62/161 ;
62/513 |
Current CPC
Class: |
F25B 29/003 20130101;
F25B 40/00 20130101; F25B 2339/047 20130101; F25B 7/00 20130101;
F25B 13/00 20130101; F25B 2313/02741 20130101; F24D 3/18 20130101;
F24D 17/02 20130101; F25B 2400/23 20130101; Y02B 30/12 20130101;
F25B 2400/13 20130101; F25B 2313/0231 20130101; F25B 2313/0272
20130101 |
Class at
Publication: |
62/161 ;
62/513 |
International
Class: |
F25D 29/00 20060101
F25D029/00 |
Claims
1. An air conditioning-hot water supply combined system,
comprising: an air conditioning refrigeration cycle that circulates
an air conditioning refrigerant in a first refrigerant circuit
where an air conditioning compressor, flow path changeover means,
an outdoor heat exchanger, an indoor heat exchanger, and air
conditioning throttle means are connected in series, and where a
refrigerant-refrigerant heat exchanger and hot water supply heat
source throttle means are connected in series and in parallel to
said indoor heat exchanger and said air conditioning throttle
means; and a hot water supply refrigeration cycle that circulates a
hot water supply refrigerant in a second refrigerant circuit where
a hot water supply compressor, a heat medium-refrigerant heat
exchanger, hot water supply throttle means, and said
refrigerant-refrigerant heat exchanger are connected in series,
wherein said air conditioning refrigeration cycle and said hot
water supply refrigeration cycle are connected so that said air
conditioning refrigerant and said hot water supply refrigerant
exchange heat in said refrigerant-refrigerant heat exchanger.
2. The air conditioning-hot water supply combined system of claim
1, further comprising: hot water supply control means that has hot
water supply communication means for communicating information by
wire or by radio, and that controls an operation of the hot water
supply refrigeration cycle in response to a state of said hot water
supply refrigeration cycle; and air conditioning control means that
has air conditioning communication means for communicating
information by wire or by radio, and that controls an operation of
the air conditioning refrigeration cycle in response to a state of
said air conditioning refrigeration cycle, wherein said hot water
supply control means and said air conditioning control means
cooperatively control the operation of said hot water supply
refrigeration cycle and the operation of said air conditioning
refrigeration cycle by said hot water supply communication means
and said air conditioning communication means communicating with
each other.
3. The air conditioning-hot water supply combined system of claim
2, further comprising: at least one out of pressure detection means
for detecting a pressure on a high-pressure side and temperature
detection means for detecting a condensation temperature, in said
hot water supply refrigeration cycle and at least one out of
pressure detection means for detecting a pressure on a low-pressure
side and temperature detection means for detecting an evaporation
temperature, in said hot water supply refrigeration cycle, wherein
said hot water supply control means and said air conditioning
control means cooperatively control the operation of said hot water
supply refrigeration cycle and the operation of said air
conditioning refrigeration cycle by intercommunicating detection
information from each detection means.
4. The air conditioning-hot water supply combined system of claim
2, wherein said hot water supply control means calculates a
compression ratio of said hot water supply compressor from
detection information obtained by each detection means, and
controls said hot water supply throttle means so that a calculation
result of the compression ratio falls within a predetermined
range.
5. The air conditioning-hot water supply combined system of claim
4, wherein said hot water supply control means controls said hot
water supply heat source throttle means on the basis of said
calculation result.
6. The air conditioning-hot water supply combined system of claim
2, further comprising: heat medium temperature detection means for
detecting a temperature of a heat medium at an outlet side of said
heat medium-refrigerant heat exchanger, wherein, on the basis of
information from said heat medium temperature detection means, said
hot water supply control means controls said hot water supply
compressor so that the temperature of the heat medium at the outlet
side of said heat medium-refrigerant heat exchanger approaches a
predetermined target value.
7. The air conditioning-hot water supply combined system of claim
2, wherein, on the basis of at least one of a pressure on a
high-pressure side, a condensation temperature, and a temperature
at a position from an outlet of said hot water supply compressor to
an inlet of the heat medium-refrigerant heat exchanger, said hot
water supply control means estimates a temperature of a heat medium
at an outlet side of said heat medium-refrigerant heat exchanger,
and controls said hot water supply compressor so that an estimated
value of the temperature of the heat medium approaches a
predetermined target value.
8. The air conditioning-hot water supply combined system of claim
2, wherein an upper limit value of frequency of said hot water
supply compressor is changed on the basis of a temperature of a
heat medium at an outlet side of said heat medium-refrigerant heat
exchanger.
9. The air conditioning-hot water supply combined system of claim
2, wherein, only when said indoor heat exchanger is operating, an
upper limit value of frequency of said hot water supply compressor
is changed on the basis of a temperature of a heat medium at an
outlet side of said heat medium-refrigerant heat exchanger.
10. The air conditioning-hot water supply combined system of claim
2, wherein said hot water supply compressor is controlled so that a
heat exchange amount in said outdoor heat exchanger falls within a
predetermined range.
11. The air conditioning-hot water supply combined system of claim
1, further comprising: a hot water supply water circulation cycle,
in which a water circulation pump, said heat medium-refrigerant
heat exchanger, and a hot water storage tank are connected in
series, and in which water is circulated as a heat medium, wherein
said hot water supply refrigerant and said water exchange heat in
said heat medium-refrigerant heat exchanger to heat said water.
12. The air conditioning-hot water supply combined system of claim
1, wherein each device constituting said hot water supply
refrigeration cycle is accommodated in the same cabinet.
13. The air conditioning-hot water supply combined system of claim
1, wherein, for said hot water supply refrigerant, a refrigerant
having a critical temperature of 60.degree. C. or more is
adopted.
14. The air conditioning-hot water supply combined system of claim
3, wherein said hot water supply control means calculates a
compression ratio of said hot water supply compressor from
detection information obtained by each detection means, and
controls said hot water supply throttle means so that a calculation
result of the compression ratio falls within a predetermined
range.
15. The air conditioning-hot water supply combined system of claim
14, wherein said hot water supply control means controls said hot
water supply heat source throttle means on the basis of said
calculation result.
16. The air conditioning-hot water supply combined system of claim
3, further comprising: heat medium temperature detection means for
detecting a temperature of a heat medium at an outlet side of said
heat medium-refrigerant heat exchanger, wherein, on the basis of
information from said heat medium temperature detection means, said
hot water supply control means controls said hot water supply
compressor so that the temperature of the heat medium at the outlet
side of said heat medium-refrigerant heat exchanger approaches a
predetermined target value.
17. The air conditioning-hot water supply combined system of claim
3, wherein, on the basis of at least one of a pressure on a
high-pressure side, a condensation temperature, and a temperature
at a position from an outlet of said hot water supply compressor to
an inlet of the heat medium-refrigerant heat exchanger, said hot
water supply control means estimates a temperature of a heat medium
at an outlet side of said heat medium-refrigerant heat exchanger,
and controls said hot water supply compressor so that an estimated
value of the temperature of the heat medium approaches a
predetermined target value.
18. The air conditioning-hot water supply combined system of claim
3, wherein an upper limit value of frequency of said hot water
supply compressor is changed on the basis of a temperature of a
heat medium at an outlet side of said heat medium-refrigerant heat
exchanger.
19. The air conditioning-hot water supply combined system of claim
3, wherein, only when said indoor heat exchanger is operating, an
upper limit value of frequency of said hot water supply compressor
is changed on the basis of a temperature of a heat medium at an
outlet side of said heat medium-refrigerant heat exchanger.
20. The air conditioning-hot water supply combined system of claim
3, wherein said hot water supply compressor is controlled so that a
heat exchange amount in said outdoor heat exchanger falls within a
predetermined range.
Description
TECHNICAL FIELD
[0001] The present invention relates to an air conditioning-hot
water supply combined system equipped with a heat pump cycle and
capable of concurrently providing a cooling load, a heating load,
and a hot water supply load. More specifically, the present
invention pertains to an air conditioning-hot water supply combined
system that implements energy saving while concurrently satisfying
a demand for supplying a high temperature hot water.
BACKGROUND ART
[0002] Hitherto, there is air conditioning-hot water supply
combined system capable of concurrently providing a cooling load, a
heating load, and a hot water supply load by a unitary
refrigeration cycle. As such, there is proposed a multifunctional
heat pump system that is constituted of a refrigerant circuit
configured that is provided with a compressor, and connected with
an outdoor heat exchanger, an indoor heat exchanger, a cold heat
storage tank, and a hot water supply heat exchanger, and that makes
up a refrigeration cycle enabling individual operations of cooling,
heating, hot water supply, heat storage, and cold storage, as well
as enabling a combined operation thereof, by switching the
refrigerant flow to the respective heat exchangers (refer to, for
example, Patent Document 1).
[0003] Furthermore, there is an air conditioning-hot water supply
combined systems capable of concurrently providing a
high-temperature hot water supply and an indoor air conditioning
function by a binary refrigeration cycle. As such, there is
proposed a heat pump type hot water supply apparatus including: a
lower-stage side refrigerant circuit, in which a first compressor,
a refrigerant distributor, a first heat exchanger, a second heat
exchanger, a first throttle device, an outdoor heat exchanger, a
four-way valve, and the above-described first compressor are
connected in this order, from the refrigerant distributor, the
four-way valve, an indoor heat exchanger, and a second throttle
device are infixed in this order to be connected between the second
heat exchanger and the first throttle device, and a first
refrigerant is made to flow, a higher-stage side refrigerant
circuit, in which a second compressor, a condenser, a third
throttle device, the first heat exchanger, and the second
compressor are connected in this order, and a second refrigerant is
made to flow, and a hot water supply path through which the second
heat exchanger and the condenser are connected in this order, and
hot water supply water is made to flow. (refer to, for example,
Patent Document 2)
[0004] Moreover, there is proposed an air-conditioning hot-water
supply system including: an air conditioner having an air
conditioning refrigerant circuit to which a compressor, an outdoor
heat exchanger, an expansion mechanism, and an indoor heat
exchanger are connected, and a unit type hot water supplier having
a hot water supply refrigerant circuit configured by sequentially
connecting a compressor, a first heat exchanger, an expansion
mechanism, and a second heat exchanger, and being filled with
carbon dioxide refrigerant, wherein the first heat exchanger is
connected to a hot water circuit for hot water supply for
generating hot water from water and water in the hot water circuit
for hot water supply and the carbon dioxide refrigerant are
configured to be heat-exchangeable, and the second heat exchanger
includes a heat radiating portion connected in parallel to an
indoor heat exchanger in a refrigerant circuit for air conditioning
and a heat absorbing portion connected to the hot water supply
refrigerant circuit, and constituted by a cascade heat exchanger,
in which heat exchange is performed between the refrigerant in the
lower-stage side refrigerant circuit and the carbon dioxide
refrigerant (refer to, for example, Patent Document 3).
[0005] [Patent Document 1] Japanese Unexamined Patent Application
Publication No. 11-270920 (pp. 3 to 4; FIG. 1)
[0006] [Patent Document 2] Japanese Unexamined Patent Application
Publication No. 4-263758 (pp. 2 to 3; FIG. 1)
[0007] [Patent Document 3] Japanese Unexamined Patent Application
Publication No. 2004-132647 (pp. 6 to 8; FIG. 1)
DISCLOSURE OF INVENTION
Problems to be Solved by the Invention
[0008] A multifunctional heat pump system set forth in Patent
Document 1 is intended to concurrently provide a cooling load, a
heating load, and a hot water supply load by a unitary
refrigeration cycle, i.e., one refrigeration cycle. However, in
such a system, the temperature in a heat radiation process wherein
water is heated and the temperature in a heat radiation process
wherein air heating is performed becomes approximately the same,
causing a problem that it is impossible to cover a high-temperature
hot water supply load, or that the temperature in the heat
radiation process of an indoor unit performing heating operation
also needs to be elevated, which results in a significant reduction
in COP (coefficient of performance).
[0009] The heat pump type hot water supply apparatus set forth in
Patent Document 2 is intended to concurrently provide a cooling
load, a heating load, and a hot water supply load by a binary
refrigeration cycle, i.e., two refrigeration cycles. However, in
such a system, the refrigerant circuit performing air conditioning
by the indoor unit and the refrigerant circuit performing hot water
supply are handled differently from each other. This posed a
problem that a hot water supplying function cannot be added simply
as an alternative for the indoor unit, thereby making it impossible
to easily introduce this system into existing air conditioners.
[0010] The air-conditioning hot-water supply system set forth in
Patent Document 3 is intended to concurrently provide a cooling
load, a heating load, and a hot water supply load by a binary
refrigeration cycle, or two refrigeration cycles. Although such a
system is operable to concurrently provide the heating load and the
hot water supply load, but is not configured to be able to provide
the heating load and the hot water supply load concurrently with
the cooling load. This raised an issue that an energy-saving
operation in which exhaust heat from one side is utilized as a heat
source on the other side, is not feasible.
[0011] The present invention is made to solve the above-described
problems. An object of the present invention is to provide an air
conditioning-hot water supply combined system that makes energy
saving feasible while concurrently providing a cooling load, a
heating load, and a high-temperature hot water supply load. Another
object of the present invention is to provide an air
conditioning-hot water supply combined system capable of being
easily introduced into existing air conditioners.
Means for Solving the Problems
[0012] The air conditioning-hot water supply combined system
according to the present invention includes: an air conditioning
refrigeration cycle that circulates an air conditioning refrigerant
in a first refrigerant circuit in which an air conditioning
compressor, flow path changeover means, an outdoor heat exchanger,
an indoor heat exchanger, and air conditioning throttle means are
connected in series, and a refrigerant-refrigerant heat exchanger
and hot water supply heat source throttle means are connected in
series to be connected to the indoor heat exchanger and air
conditioning throttle means in parallel; and a hot water supply
refrigeration cycle that circulates a hot water supply refrigerant
in a second refrigerant circuit in which a hot water supply
compressor, a heat medium-refrigerant heat exchanger, hot water
supply throttle means, and the refrigerant-refrigerant heat
exchanger are connected in series, wherein the air conditioning
refrigeration cycle and the hot water supply refrigeration cycle
are connected so that the air conditioning refrigerant and the hot
water supply refrigerant exchange heat therebetween by the
refrigerant-refrigerant heat exchanger.
ADVANTAGES
[0013] According to the air conditioning-hot water supply combined
system according to the present invention, since heat that is
discharged in the air is collected and reused for hot water supply
while concurrently providing a cooling load, a heating load, and a
high-temperature hot water supply load, it is possible to
significantly increase system COP to thereby realize energy
saving.
BRIEF DESCRIPTION OF DRAWINGS
[0014] FIG. 1 is a refrigerant circuit diagram showing a
refrigerant circuit configuration of an air conditioning-hot water
supply combined system according to Embodiment 1 of the present
invention.
[0015] FIG. 2 is a Mollier diagram showing refrigerant states of an
air conditioning refrigeration cycle at the time of a cooling-based
operation.
[0016] FIG. 3 is a refrigerant circuit diagram showing a
refrigerant circuit configuration of the air conditioning-hot water
supply combined system according to Embodiment 1.
[0017] FIG. 4 is a Mollier diagram showing refrigerant states in an
air conditioning refrigeration cycle at the time of a heating-based
operation.
[0018] FIG. 5 is a refrigerant circuit diagram showing a
refrigerant circuit configuration of the air conditioning-hot water
supply combined system according to Embodiment 2 of the present
invention.
[0019] FIG. 6 is a refrigerant circuit diagram showing a
refrigerant circuit configuration of the air conditioning-hot water
supply combined system according to Embodiment 2.
[0020] FIG. 7 is a refrigerant circuit diagram showing a
refrigerant circuit configuration of the air conditioning-hot water
supply combined system according to Embodiment 3 of the present
invention.
[0021] FIG. 8 is a refrigerant circuit diagram showing a
refrigerant circuit configuration of the air conditioning-hot water
supply combined system according to Embodiment 4 of the present
invention.
REFERENCE NUMERALS
[0022] 1 air conditioning refrigeration cycle [0023] 1a air
conditioning refrigeration cycle [0024] 2 hot water supply
refrigeration cycle [0025] 3 hot water supply water circulation
cycle [0026] 21 hot water supply compressor [0027] 22 hot water
supply throttle means [0028] 23 hot water supply low-pressure side
pressure detecting means [0029] 24 hot water supply high-pressure
side pressure detection means [0030] 25 hot water supply control
means [0031] 26 hot water supply communication means [0032] 27 hot
water supply calculation means [0033] 28 hot water supply storage
means [0034] 31 water circulation pump [0035] 32 hot water storage
tank [0036] 33 hot water delivery temperature detection means
[0037] 41 refrigerant-refrigerant heat exchanger [0038] 51 heat
medium-refrigerant heat exchanger [0039] 100 air conditioning-hot
water supply combined system [0040] 100a air conditioning-hot water
supply combined system [0041] 100b air conditioning-hot water
supply combined system [0042] 100c air conditioning-hot water
supply combined system [0043] 101 air conditioning compressor
[0044] 102 four-way valve [0045] 103 outdoor heat exchanger [0046]
104 accumulator [0047] 105a check valve [0048] 105b check valve
[0049] 105c check valve [0050] 105d check valve [0051] 105e check
valve [0052] 106 high-pressure Side connection piping [0053] 107
low-pressure side connection piping [0054] 108 gas-liquid separator
[0055] 109 first distribution portion [0056] 109a valve means
[0057] 109b valve moans [0058] 110 second distribution portion
[0059] 110a check valve [0060] 110b check valve [0061] 111 first
internal heat exchanger [0062] 112 first relay unit throttle means
[0063] 113 second internal heat exchanger [0064] 114 second relay
unit throttle means [0065] 115 first meeting portion [0066] 116
second meeting portion [0067] 117 air conditioning throttle means
[0068] 118 indoor heat exchanger [0069] 119 hot water supply heat
source throttle means [0070] 120 air conditioning control means
[0071] 121 air conditioning communication means [0072] 122 air
conditioning calculation means [0073] 123 air conditioning storage
means [0074] 124 first heat source unit throttle means [0075] 125
air conditioning suction gas piping [0076] 126 air conditioning
suction gas piping [0077] 127 air conditioning liquid piping [0078]
128 second heat source unit throttle means [0079] 130 first
connection piping [0080] 131 second connection piping [0081] 132
connection piping [0082] 133 connection piping [0083] 133a
connection piping [0084] 133b connection piping [0085] 134
connection piping [0086] 134a connection piping [0087] 134b
connection piping [0088] 135 connection piping [0089] 135a
connection piping [0090] 135b connection piping [0091] 136
connection piping [0092] 136a connection piping [0093] 136b
connection piping [0094] 140 discharge-side piping [0095] 140a
discharge-side piping [0096] 140b discharge-side piping [0097] 141
bypass pipe [0098] 200 hot power supply refrigeration cycle cabinet
[0099] 201 connection valve [0100] 202 connection valve [0101] 203
connection valve [0102] 204 connection valve [0103] 205 connection
valve [0104] 206 connection valve [0105] 207 connection valve
[0106] 208 connection valve [0107] .LAMBDA. heat source unit [0108]
A.sub.2 heat source unit [0109] B cooling indoor unit [0110] C
heating indoor unit [0111] D hot water supply heat source circuit
[0112] E relay unit [0113] E.sub.2 relay unit
BEST MODES FOR CARRYING OUT THE INVENTION
[0114] Hereinafter, embodiments according to the present invention
will be described with reference to the drawings.
Embodiment 1
[0115] FIG. 1 is a refrigerant circuit diagram showing a
refrigerant circuit configuration (especially, the refrigerant
circuit configuration at the time of the cooling-based operation)
of an air conditioning-hot water supply combined system 100
according to Embodiment 1 of the present invention. With reference
to FIG. 1, description is made of a refrigerant circuit
configuration of the air conditioning-hot water supply combined
system 100, especially the refrigerant circuit configuration at the
time of the cooling-based operation. The air conditioning-hot water
supply combined system 100 is installed in a building, a
condominium building or the like, and is operable to concurrently
provide a cooling load, a heating load, and a hot water supply load
by utilizing a refrigeration cycle (heat pump cycle) circulating a
refrigerant (air conditioning refrigerant). In the following
figures including FIG. 1, the size relationships among constituent
members may be different from actual ones.
[0116] In FIG. 1, in an air conditioning refrigeration cycle 1, the
load for a cooling indoor unit B is higher than the total of the
loads for a heating indoor unit C and a hot water supply heat
source circuit D. That is, FIG. 1 indicates the state of a cycle in
the case when an outdoor heat exchanger 103 functions as a radiator
(referred to a "cooling-based operation" for convenience). The air
conditioning-hot water supply combined system 100 according to
Embodiment 1 is configured by connecting an air conditioning
refrigeration cycle 1, a hot water supply refrigeration cycle 2,
and a hot water supply water circulation cycle 3 by connection
piping such as a high-pressure side connection piping 106 and a
lower-pressure side connection piping 107. It is configured that
the air conditioning refrigeration cycle 1 and the hot water supply
refrigeration cycle 2 exchange heat therebetween by a
refrigerant-refrigerant heat exchanger 41, and the hot water supply
refrigeration cycle 2 and the hot water supply water circulation
cycle 3 exchange heat therebetween by a heat medium-refrigerant
heat exchanger 51 without refrigerants and being mixed each
other.
[0117] [Air Conditioning Refrigeration Cycle 1]
[0118] The air conditioning refrigeration cycle 1 is constituted of
a heat source unit A, a cooling indoor unit B taking charge of a
cooling load, a heating indoor unit C taking charge of a heating
load, a hot water supply heat source circuit D serving as a heat
source for the hot water supply refrigeration cycle 2, and a relay
unit E. Among them, the cooling indoor unit B, the heating indoor
unit C, and the hot water supply heat source circuit D are
connected and installed so as to be in parallel to the heat source
unit A. The relay unit E disposed between the heat source unit A
and the cooling indoor unit B, the heating indoor unit C, and the
hot water supply heat source circuit D, is designed to cause the
cooling indoor unit B, the heating indoor unit C, and the hot water
supply heat source circuit D to exert their respective
functions.
[0119] [Heat Source Unit A]
[0120] The heat source unit A is configured by connecting an air
conditioning compressor 101, a four-way valve 102 serving as flow
path changeover means, an outdoor heat exchanger 103, and an
accumulator 104 in series. The heat source unit A has a function of
supplying cold heat to the cooling indoor unit B, the heating
indoor unit C, and the hot water supply heat source circuit D. In
the vicinity of the outdoor heat exchanger 103, there is preferably
provided an air blower such as a fan for supplying air to the
outdoor heat exchanger 103. In the heat source unit A, a
high-pressure side connection piping 106 and a lower-pressure side
connection piping 107 are connected by a first connection piping
130 and a second connection piping 131.
[0121] In the cooling-based operation, the connection portion
(hereinafter, simply referred to as a "connection portion a")
between the high-pressure side connection piping 106 and the first
connection piping 130 is located on the upstream side of the
connection portion (hereinafter, simply referred to as a
"connection portion b") between the high-pressure side connection
piping 106 and the second connection piping 131. On the other hand,
the connection portion (hereinafter, simply referred to as a
"connection portion c") between the low-pressure side connection
piping 107 and the first connection piping 130 is located on the
upstream side of the connection portion (hereinafter, simply
referred to as a "connection portion d") between the low-pressure
side connection piping 107 and the second connection piping
131.
[0122] In the first connection piping 130, there is provided a
check valve 105c permitting a flow of the air conditioning
refrigerant only in the direction from the low-pressure side
connection piping 107 toward the high-pressure side connection
piping 106. Likewise, in the second connection piping 131, there is
provided a cheek valve 105d allowing a flow of the air conditioning
refrigerant only in the direction from the low-pressure side
connection piping 107 toward the high-pressure side connection
piping 106. Moreover, between the connection portion a and the
connection portion b of the high-pressure side connection piping
106, there is provided a check valve 105a allowing a flow of the
air conditioning refrigerant only in a predetermined direction (the
direction from the heat source unit A toward the relay unit E). On
the other hand, between the "connection portion c" and the
connection portion d of the low-pressure side connection piping
107, there is provided a check valve 105b allowing a flow of the
air conditioning refrigerant only in a predetermined direction (the
direction from the relay unit E toward the heat source unit A).
[0123] The air conditioning compressor 101 is operative to suck-in
the air conditioning refrigerant and compress it into a
high-temperature and high-pressure state. Preferably, the air
conditioning compressor 101 is, for example, a type whose rotation
number is controlled by an inverter. The four-way valve 102 is
operative to changeover the flow of the air conditioning
refrigerant. The outdoor heat exchanger 103 functions as an
evaporator and a radiator (condenser), and exchanges heat between
the air supplied from an air blower (not shown) and the air
conditioning refrigerant, to thereby change the air conditioning
refrigerant to evaporated gas or condensation liquid. The
accumulator 104 is disposed between the four-way valve 102 and the
air conditioning compressor 101 in the cooling-based operation and
stores excessive air conditioning refrigerant. The accumulator 104
may be any container as long as it can store excessive air
conditioning refrigerant.
[0124] [Cooling Indoor Unit B and Heating Indoor Unit C]
[0125] In the cooling indoor unit B and the heating indoor unit C,
the air conditioning throttle means 117 and the indoor heat
exchanger 118 are serially connected and installed. A case is
illustrated by way of example, in which in the cooling indoor unit
B and the heating indoor unit C, two air conditioning throttle
means 117 and two indoor heat exchangers 118 are connected in
parallel and installed respectively. The cooling indoor unit B has
a function of receiving cold heat supply from the heat source unit
A and taking charge of a cooling load, while the heating indoor
unit C has a function of receiving cold heat supply from the heat
source unit A and taking charge of a heating load.
[0126] In short, a state is shown, in which the cooling indoor unit
B is determined by the relay unit E to take charge of a cooling
load, and the heating indoor unit C is determined thereby to take
charge of a heating load. In the vicinity of the indoor heat
exchanger 118 there may be provided an air blower such as a fan for
supplying air to the indoor heat exchanger 118. For convenience of
explanation, connection piping connected from the relay unit E to
the indoor heat exchanger 118 is referred to as a "connection
piping 133", and connection piping connected from the relay unit E
to the air conditioning throttle means 117 is referred to as a
"connection piping 134".
[0127] The air conditioning throttle means 117 functions as a
decompression valve and expansion valve, and decompresses the air
conditioning refrigerant to expand it. The air conditioning
throttle means 117 is preferably constituted by means whose degree
of opening is variably controllable, such as precise flow rate
control means by an electronic expansion valve and inexpensive
refrigerant flow rate regulating means such as a capillary, for
example. The indoor heat exchanger 118 functions as a radiator
(condenser) and an evaporator, and exchanges heat between the air
supplied from air blowing means (not shown) and the air
conditioning refrigerant, to thereby change the air conditioning
refrigerant to condensation liquid or evaporation. Here, the air
conditioning throttle means 117 and the indoor heat exchangers 118
are connected in series.
[0128] [Hot Water Supply Heat Source Circuit D]
[0129] The hot water supply heat source circuit D is configured by
connecting hot water supply heat source throttle means 119 and the
refrigerant-refrigerant heat exchanger 41 in series, and has a
function of supplying cold heat from the heat source unit A to the
hot water supply refrigeration cycle 2 via the
refrigerant-refrigerant heat exchanger 41. That is, the air
conditioning refrigeration cycle 1 and the hot water supply
refrigeration cycle 2 are cascade-connected in the
refrigerant-refrigerant heat exchanger 41. For convenience of
explanation, connection piping connecting from the relay unit E to
the refrigerant-refrigerant heat exchanger 41 is referred to as a
connection piping 135, and connection piping connecting from the
relay unit E to the hot water supply heat source throttle means 119
is referred to as a "connection piping 136".
[0130] As in the case of the air conditioning throttle means 117,
the hot water supply heat source throttle means 119 functions as a
decompression valve and an expansion valve, and decompresses the
air conditioning refrigerant to expand it. The hot water supply
heat source throttle means 119 is preferably constituted by means
whose degree of opening is variably controllable, such as precise
flow rate control means by an electronic expansion valve, and
inexpensive refrigerant flow rate regulating means such as a
capillary, for example. The refrigerant-refrigerant heat exchanger
41 functions as a radiator (condenser) and an evaporator, and
exchanges heat between the hot water supply refrigerant circulating
in the refrigeration cycle of the hot water supply refrigeration
cycle 2 and the air conditioning refrigerant circulating in the
refrigeration cycle of the air conditioning refrigeration cycle
1.
[0131] [Relay Unit E1]
[0132] The relay unit E has a function of connecting each of the
cooling indoor unit B, the heating indoor unit C, and the hot water
supply heat source circuit D to the heat source unit A. The relay
unit E also has a function of, determining whether the indoor heat
exchanger 118 and the refrigerant-refrigerant heat exchanger 41 to
be connected are to be a cooling unit (water cooler) or a heating
unit (water heater) by alternatively opening/closing any of the
valve means 109a and the valve means 109b of a first distribution
portion 109. The relay unit E is constituted of a gas-liquid
separator 108, the first distribution portion 109, a second
distribution portion 110, a first internal heat exchanger 111, a
first relay unit throttle means 112, a second internal heat
exchanger 113, and a second relay unit throttle means 114.
[0133] In the first distribution portion 109, the connection piping
133 and the connection piping 135 are branched into two. One
(connection piping 133b and connection piping 135b) is connected to
the low-pressure side connection piping 107, while the other
(connection piping 133a and connection piping 135a) is connected to
connection piping (referred to as connection piping 132, which is
connected with the gas-liquid separator 108. Furthermore, in the
first distribution portion 109, valve means 109a is provided with
connection piping 133a and connection piping 135a, and valve means
109b is provided with connection piping 133b and connection piping
135b.
[0134] In the second distribution portion 110, connection piping
134 and connection piping 136 are each branched into two. One
(connection piping 134a and connection piping 136a) is connected
with a first meeting portion 115, while the other (connection
piping 134b and connection piping 136b) is connected with a second
meeting portion 116. Furthermore, in the second distribution
portion 110, a check valve 110a is provided with connection piping
134a and connection piping 136a, and a check valve 110b is provided
with connection piping 134b and connection piping 136b,
respectively.
[0135] The first meeting portion 115 is connected between the
second distribution portion 110 and the gas-liquid separator 108
via the first relay unit throttle means 112 and the first internal
heat exchanger 111. The second meeting portion 116 branches into
two between the second distribution portion 110 and the second
internal heat exchanger 113. One of the branched portions is
connected to the first meeting portion 115 between the second
distribution portion 110 and the first relay unit throttle means
112 via second internal heat exchanger 113. The other of the
branched portions (a second meeting portion 116a) is connected to
the low-pressure side connection piping 107 via the second relay
unit throttle means 114, the second internal heat exchanger 113,
and the first internal heat exchanger 111.
[0136] The gas-liquid separator 108 is operative to separate the
air conditioning refrigerant into a gas refrigerant and a liquid
refrigerant, and is provided with the high-pressure side connection
piping 106. One is connected to the valve means 109a in the first
distribution portion 109, and the other is connected to the second
distribution portion 110 via the first meeting portion 115. The
first distribution portion 109 has a function of allowing the air
conditioning refrigerant to flow into the indoor heat exchanger 118
and the refrigerant-refrigerant heat exchanger 41 by alternatively
opening/closing either of the valve means 109a or the valve means
109b. The second distribution portion 110 has a function of
permitting the flow of the air conditioning refrigerant into either
direction by the check valve 110a and the check valve 110b.
[0137] The first internal heat exchanger 111 is provided in the
first meeting portion 115 between the gas-liquid separator 108 and
the first relay unit throttle means 112, and performs heat exchange
between the air conditioning refrigerant passing through the first
meeting portion 115 and the air conditioning refrigerant passing
through the second meeting portion 116a, which is branched from the
second meeting portion 116. The first relay unit throttle means 112
is provided in the first meeting portion 115 between the first
internal heat exchanger 111 and the second distribution portion
110, and is operative to decompress the air conditioning
refrigerant to expand it. The first relay unit throttle means 112
is preferably constituted by means whose degree of opening is
variably controllable, such as precise flow rate control means by
an electronic expansion valve and inexpensive refrigerant flow rate
regulating means such as a capillary, for example.
[0138] The second internal heat exchanger 113 is provided in the
second meeting portion 116, and performs heat exchange between the
air conditioning refrigerant passing through the second meeting
portion 116 and the air conditioning refrigerant passing through
the second meeting portion 116a, which is branched from the second
meeting portion 116. The second relay unit throttle means 114 is
provided in the second meeting portion 116 between the second
internal heat exchanger 113 and the second distribution portion
110, and functions as a decompression valve and an expansion valve,
to decompress the air conditioning refrigerant and expand it. As in
the case of the first relay unit throttle means 112, the second
relay unit throttle means 114 is preferably constituted by means
whose degree of opening is variably controllable, such as precise
flow rate control means by an electronic expansion valve and
inexpensive refrigerant flow rate regulating means such as a
capillary, for example.
[0139] As described above, the air conditioning refrigeration cycle
1 makes up a first refrigerant circuit by connecting the air
conditioning compressor 101, the flow path changeover means 102,
the outdoor heat exchanger 103, the indoor heat exchanger 118, and
the air conditioning throttle means 117 in series, and connecting
the refrigerant-refrigerant heat exchanger 41 and the hot water
supply heat source throttle means 119 in series the indoor heat
exchanger 118 and air conditioning throttle means 117 being
connected in parallel thereto. By circulating the air conditioning
refrigerant in the above-described first refrigerant circuit, the
air conditioning refrigeration cycle 1 is established.
[0140] Here, the cooling-based Operation of the air conditioning
refrigeration cycle 1 will be described.
[0141] FIG. 2 is a Mollier diagram (P-H diagram) showing
refrigerant states of the air conditioning refrigeration cycle 1 at
the time of the cooling-based operation. With reference to FIGS. 1
and 2, description is made of operation of the air conditioning
refrigeration cycle 1 in the air conditioning-hot water supply
combined system 100. In FIG. 2, the vertical axis represents an
absolute pressure (MPa), and the horizontal axis represents a
specific enthalpy (kJ/kg). FIG. 2 indicates that: the air
conditioning refrigerant is in a gas-liquid two-phase state in the
portion enclosed by the saturated liquid line and the saturated
vapor line; it is in a liquid state on the left side of the
saturated liquid line; and it is in a gas state on the right side
of the saturated vapor line. Here, a case in which, in the air
conditioning refrigeration cycle 1, R410A is used as an air
conditioning refrigerant, is shown by way of example.
[0142] At first, the air conditioning refrigerant brought into a
high-temperature and high-pressure state by the air conditioning
compressor 101 is discharged from the air conditioning compressor
101, and flows into the outdoor heat exchanger 103 via the four-way
valve 102. In the outdoor heat exchanger 103, the air conditioning
refrigerant that flowed therein exchanges heat with outdoor air and
radiates heat. The air conditioning refrigerant that flowed out
from the outdoor heat exchanger 103 passes through the check valve
105a, and being introduced into the high-pressure side connection
piping 106, and reaches the gas-liquid separator 108 of the rely
unit E. The air conditioning refrigerant that flowed into the
gas-liquid separator 108 is separated into a gas-phase air
conditioning refrigerant and a liquid-phase air conditioning
refrigerant.
[0143] Saturated vapor (the gas-phased air conditioning
refrigerant) is distributed among circuits with the valve means
109a in the first distribution portion 109 being open. Here, the
saturated vapor is adapted to flow into the heating indoor unit C
and the hot water supply heat source circuit D. The air
conditioning refrigerant that flowed into the heating indoor unit C
radiates heat in the indoor heat exchangers 118 (that is, heats the
indoor air), being decompressed by the air conditioning throttle
means 117, and meets in the first meeting portion 115. On the other
hand, the air conditioning refrigerant that flowed into the hot
water supply heat source circuit D radiates heat in the
refrigerant-refrigerant heat exchanger 41 (that is, supplies heat
to the hot water supply refrigeration cycle 2), being decompressed
by the hot water supply heat source throttle means 119, and meets
the air conditioning refrigerant that flowed out from the heating
indoor unit C, at the first meeting portion 115.
[0144] On the other hand, the saturated liquid (the liquid-phase
air conditioning refrigerant) exchanges heat in the first internal
heat exchanger 111 with the air conditioning refrigerant that
expanded into a low-temperature and, low-pressure state by the
second relay unit throttle means 114, to thereby obtain a
supercooling degree. Then, the saturated liquid passes through the
first relay unit throttle means 112, and meets the refrigerant used
for air conditioning in the first meeting portion 115 (the air
conditioning refrigerant that flowed into the heating indoor unit C
and the hot water supply heat source circuit D, and that has
radiated heat in the indoor heat exchanger 118 and the
refrigerant-refrigerant heat exchanger 41). Thereafter, the air
conditioning refrigerant that met at the first meeting portion 115
exchanges heat with the air conditioning refrigerant that expanded
into a low-temperature and low-pressure state by the second relay
unit throttle means 114 to thereby obtain a supercooling degree in
the second internal heat exchanger 113. This air conditioning
refrigerant is distributed between the second meeting portion 116
side and the second relay unit throttle means 114 side.
[0145] The air conditioning refrigerant passing through the second
meeting portion 116 is distributed among circuits with the valve
means 109b being open. Here, the air conditioning refrigerant
passing through the second meeting portion 116 is adapted to flow
into the cooling indoor unit B. The air conditioning refrigerant
that flowed into the cooling indoor unit B is expanded into a
low-temperature and low-pressure state by the air conditioning
throttle means 117, evaporates in the indoor heat exchangers 118,
and meets in the lower pressure side connection piping 107 via the
valve means 109b. On the other hand, the air conditioning
refrigerant that passed through the second relay unit throttle
means 114 exchanges heat in the second internal heat exchanger 113
and the first internal heat exchanger 111 to thereby evaporate, and
meets the air conditioning refrigerant that flowed out from the
cooling indoor unit in the lower pressure side connection piping
107. Then, the air conditioning refrigerant that net in the lower
pressure side connection piping 107 is led to the four-way valve
102 through the check valve 105d, and returns to the air
conditioning compressor 101 via the accumulator 104.
[0146] Next, the heating-based operation of the air conditioning
refrigeration cycle 1 will be described.
[0147] FIG. 3 is a refrigerant circuit diagram showing a
refrigerant circuit configuration (especially, the refrigerant
circuit configuration at the time of the heating-based operation)
of the air conditioning-hot water supply combined system 100
according to Embodiment 1 of the present invention. FIG. 4 is a
Mollier diagram showing refrigerant states of the air conditioning
refrigeration cycle at the time of the heating-based operation.
With reference to FIGS. 3 and 4, description is made of the
heating-based operation of the air conditioning refrigeration cycle
1 in the air conditioning-hot water supply combined system 100.
[0148] In FIG. 3, in the air conditioning refrigeration cycle 1,
the load for the cooling indoor unit B is lower than the total of
the loads for the heating indoor unit C and the hot water supply
heat source circuit D. So that, a state of a cycle (referred to as
a "heat-based operation" for convenience) is shown in which an
outdoor heat exchanger 103 functions as an evaporator. In FIG. 4,
the vertical axis represents the absolute pressure (MPa), and the
horizontal axis represents the specific enthalpy (kJ/kg). It is
also indicated that the air conditioning refrigerant is in a
gas-liquid two-phase state in the portion enclosed by a saturated
liquid line and a saturated vapor line on the left side of the
saturated liquid line is in a liquid state, and on the right side
of the saturated vapor line is in a gas state. Here, a case is
shown by way of example, in which R410A is used in the air
conditioning refrigeration cycle 1 as an air conditioning
refrigerant.
[0149] First, the air conditioning refrigerant turned into a
high-temperature and high-pressure state by the air conditioning
compressor 101 is discharged from the air conditioning compressor
101, and after passing through the check valve 105c via the
four-way valve 102, it is led into the high pressure side
connection piping 106 to flow into the gas-liquid separator 108 of
the relay unit E in a superheated gas state. The air conditioning
refrigerant in the superheated gas state, flowed into the
gas-liquid separator 108 is distributed into circuits with the
valve means 109a of the first distribution portion 109 being open.
Here, the air conditioning refrigerant in the superheated gas state
is adapted to flow into the heating indoor unit C and the hot water
supply heat source circuit D.
[0150] The air conditioning refrigerant that flowed into the
heating indoor unit C radiates heat in the indoor heat exchangers
118 (that is, heats the indoor air), and being decompressed by the
air conditioning throttle means 117 to meet in the first meeting
portion 115. On the other hand, the air conditioning refrigerant
that flowed into the hot water supply heat source circuit D
radiates heat in the refrigerant-refrigerant heat exchanger 41
(that is, supplies heat to the hot water supply refrigeration cycle
2), and after being decompressed by the hot water supply heat
source throttle means 119 to meet the air conditioning refrigerant
flowed out from the heating indoor unit C in the first meeting
portion 115. Meanwhile, part of the air conditioning refrigerant in
a superheated gas state flowed into the gas-liquid separator 108
exchanges heat in the first internal heat exchanger 111 with the
air conditioning refrigerant that expanded into a low-temperature
and low-pressure state by the second relay unit throttle means 114,
to thereby obtain a supercooling degree.
[0151] Then, the part of the air conditioning refrigerant in the
superheated gas state passes through the first relay unit throttle
means 112, and meets the air conditioning refrigerant (the air
conditioning refrigerant that flowed into the heating indoor unit C
and the hot water supply heat source circuit D and radiated heat in
the indoor heat exchanger 118 and the refrigerant-refrigerant heat
exchanger 41) in the first meeting portion 115. Meanwhile, part of
the air conditioning refrigerant in the superheated gas state
passing through the first relay unit throttle means 112 may be
nulled out by totally closing the first relay unit throttle means
112. Thereafter, a supercooling degree can be obtained by
performing heat exchange with the air conditioning refrigerant that
expanded into a low-temperature and low-pressure state by the
second relay unit throttle means 114. This air conditioning
refrigerant is distributed into the second meeting portion 116 side
and the second relay unit throttle means 114 side.
[0152] The air conditioning refrigerant passing through the second
meeting portion 116 is distributed into circuits with the valve
means 109b opened. Here, the air conditioning refrigerant passing
through the second meeting portion 116 is adapted to flow into the
cooling indoor unit B. The air conditioning refrigerant that flowed
into the cooling indoor unit B is expanded into a low-temperature
and low-pressure state by the air conditioning throttle means 117,
evaporates in the indoor heat exchangers 118, and meets in the low
pressure side connection piping 107 via the valve means 109b. The
air conditioning refrigerant that passed through the second relay
unit throttle means 114 exchanges heat in the second internal heat
exchanger 113 and the first internal heat exchanger 111 to
evaporate, and meets the air conditioning refrigerant that flowed
out of the cooling indoor unit B in the low pressure side
connection piping 107. Then, the air conditioning refrigerant that
met in the low pressure side connection piping 107 is led to the
outdoor heat exchanger 103 through the check valve 105d, evaporates
a remaining liquid refrigerant depending upon an operating
condition, and returns to the air conditioning compressor 101 via
the four-way valve 102 and the accumulator 104.
[0153] [Hot Water Supply Refrigeration Cycle 2]
[0154] With reference to FIGS. 1 and 3, the hot water supply
refrigeration cycle 2 is described. The operation of the hot water
supply refrigeration cycle 2 does not differ irrespective of the
operating state of the air conditioning refrigeration cycle 1,
i.e., irrespective of whether the air conditioning refrigeration
cycle 1 is performing the cooling-based operation or the
heating-based operation. As shown in FIGS. 1 and 3, the hot water
supply refrigeration cycle 2 is constituted of the hot water supply
compressor 21, the heat medium-refrigerant heat exchanger 51, the
hot water supply throttle means 22, and the refrigerant-refrigerant
heat exchanger 41. That is, the hot water supply refrigeration
cycle 2 makes up the second refrigerant circuit by connecting the
hot water supply compressor 21, the heat medium-refrigerant heat
exchanger 51, the hot water supply throttle means 22, and the
refrigerant-refrigerant heat exchanger 41 in series, and by
circulating the hot water supply refrigerant in the above-described
second refrigerant circuit, the hot water supply refrigeration
cycle 2 is established.
[0155] The hot water supply compressor 21 sucks-in a hot water
supply refrigerant and compresses it into a high-temperature and
high-pressure state. The hot water supply compressor 21 is
preferably a type of which rotation speed is controlled by an
inverter. The heat medium-refrigerant heat exchanger 51 exchanges
heat between water (heat medium) circulating in the hot water
supply water circulation cycle 3 and the hot water supply
refrigerant circulating in the hot water supply refrigeration cycle
2. The hot water supply throttle means 22 functions as a
decompression valve and an expansion valve, and decompresses the
hot water supply refrigerant to expand it. The hot water supply
throttle means 22 is preferably constituted by means of which the
degree of opening is variably controllable, such as precise flow
rate control means by an electronic expansion valve, for example,
and inexpensive refrigerant flow rate regulating means such as a
capillary. The refrigerant-refrigerant heat exchanger 41 exchanges
heat between the hot water supply refrigerant circulating in the
hot water supply refrigeration cycle 2 and the air conditioning
refrigerant circulating in the air conditioning refrigeration cycle
1.
[0156] Here, the operation of the hot water supply refrigeration
cycle 2 will be described.
[0157] In FIGS. 2 and 4, Mollier diagrams (P-H diagrams) are
illustrated showing refrigerant states in an hot water supply
refrigeration cycle 2 at the times of cooling-based operation and
the heating-based operation, respectively. With reference to FIGS.
1 to 4, description is made of operation of the hot water supply
refrigeration cycle 2 in the air conditioning-hot water supply
combined system 100. It is indicated that: the hot water supply
refrigerant is in a gas-liquid two-phase state in the portion
enclosed by a saturated liquid line and a saturated vapor line; on
the left side of the saturated liquid line is in a liquid state;
and on the right side of the saturated vapor line is in a gas
state. Here, a case wherein R134a is used as a hot water supply
refrigerant in the hot water supply refrigeration cycle 2 is shown
by way of example.
[0158] First, the hot water supply refrigerant brought into a
high-temperature and high-pressure state by the hot water supply
compressor 21 is discharged from the hot water supply compressor 21
and flows into the heat medium-refrigerant heat exchanger 51. In
the heat medium-refrigerant heat exchanger 51, the hot water supply
refrigerant therein heats the water circulating in the hot water
supply water circulation cycle 3, to thereby radiate heat. This hot
water supply refrigerant is expanded up to a temperature below the
outlet temperature of the refrigerant-refrigerant heat exchanger 41
in the hot water supply heat source circuit D of the air
conditioning refrigeration cycle 1 by the hot water supply throttle
means 22. The expanded hot water supply refrigerant receives heat
from the air conditioning refrigerant flowing in the hot water
supply heat source circuit D in the refrigerant-refrigerant heat
exchanger 41 to evaporate and returns to the hot water supply
compressor 21.
[0159] [Hot Water Supply Water Circulation Circle 3]
[0160] With reference to FIGS. 1 and 3, the hot water supply water
circulation cycle 3 will be described. The operation of the hot
water supply water circulation cycle 3 does not vary irrespective
of the operating state of the air conditioning refrigeration cycle
1, i.e., whether the air conditioning refrigeration cycle 1 is
performing the cooling-based operation or the heating-based
operation. As shown in FIGS. 1 and 3, the hot water supply water
circulation cycle 3 is constituted of a water circulation pump 31,
the heat medium-refrigerant heat exchanger 51, and a hot water
storage tank 32.
[0161] The water circulation pump 31 sucks in water stored in the
hot water storage tank 32, pressurizes the water, circulate it in
the hot water supply water circulation cycle 3. Preferably, the
water circulation pump 31 is, for example, a type whose rotation
number is controlled by an inverter. As described above, the heat
medium-refrigerant heat exchanger 51 exchanges heat between the
water (heat medium) circulating in the hot water supply water
circulation cycle 3 and the hot water supply refrigerant
circulating in the hot water supply refrigeration cycle 2. The hot
water storage tank 32 is used for storing the water heated by the
heat medium-refrigerant heat exchanger 51.
[0162] First, comparatively low temperature water that is stored in
the hot water storage tank 32 is drawn out by the water circulation
pump 31 from the bottom portion of the hot water storage tank 32,
and obtains a water head. The water that obtained the water head
flows into the heat medium-refrigerant heat exchanger 51, and
receives heat in the heat medium-refrigerant heat exchanger 51 from
the hot water supply refrigerant circulating in the hot water
supply refrigeration cycle 2. That is, the water flowed into the
heat medium-refrigerant heat exchanger 51 is boiled up by the hot
water supply refrigerant circulating in the hot water supply
refrigeration cycle 2 to rise its temperature. The boiled-up water
returns to a comparatively high temperature upper portion of the
hot water storage tank 32, being stored in the hot water storage
tank 32.
[0163] In Embodiment 1, as shown in FIGS. 1 and 3, the case where
the water in the hot Water storage tank 32 is directly heated by
the heat medium-refrigerant heat exchanger 51, is explained by way
of example. However, it is not limited thereto. One alternative
method is that by making the water passing through the water
circulation pump 31 and the heat medium-refrigerant heat exchanger
51 be a closed system independent of the water in the hot water
storage tank 32, making the piping pass through the hot water
storage tank 32, the water in the hot water storage tank 32 is
reheated. In this case, the medium within the closed system may
also be brine (antifreeze) or the like instead of water.
[0164] Furthermore, the check valve 105a, the check valve 105b, the
check valve 105c, the check valve 105d, the check valves 110a, and
the check valves 110b may be each constituted by valve means such
as a solenoid valve to more reliably perform a switchover between
refrigerant flow paths. Moreover, the air conditioning compressor
101 and the hot water supply compressor 21 may employ any of
various types such as a reciprocating type, a rotary type, a scroll
type, and a screw type. Besides, they are not limited to one whose
rotation number is variable, but may be one whose rotation number
is fixed.
[0165] The case in which the R410A is adopted for the air
conditioning refrigerant circulating in the air conditioning
refrigeration cycle 1, and the R134a is adopted for the hot water
supply refrigerant circulating in the hot water supply
refrigeration cycle 2, are explained by way of example. However,
kinds of the refrigerants are not particularly limited. For
example, any of natural refrigerant such as carbon dioxide
(CO.sub.2), hydrocarbon, and helium; alternative refrigerant
containing no chrome, such as HFC410A, HFC407C, HFC404A; and
fluorocarbon refrigerants, such as R22 or R134a, which are used in
existing products, may be adopted. While the air conditioning
refrigeration cycle 1 and the hot water supply refrigeration cycle
2 have an independent refrigerant circuit configuration, and the
refrigerants circulating may be of the same kind or mutually
different kinds. These refrigerants exchange heat therebetween in
the refrigerant-refrigerant heat exchanger 41 and the heat
medium-refrigerant heat exchanger 51 without being mixed with each
other.
[0166] In a case where a refrigerant having a low critical
temperature is used as a hot power supply refrigerant, when a
high-temperature hot water is supplied, the hot water supply
refrigerant in a heat radiating process in the heat
medium-refrigerant heat exchanger 51 is assumed to turn into a
supercritical state. However, in general, when the refrigerant in a
heat radiating process is in a supercritical state, the fluctuation
of the COP due to change in the radiator pressure and the radiator
outlet temperature is large. In order to perform an operation for
achieving a high COP, higher degree of control is desired.
Furthermore, typically, because the refrigerant having a low
critical temperature is high in saturated pressure with respect to
the same temperature, the wall of pipings and the compressor must
be made thicker correspondingly, which results in increase in
cost.
[0167] In view of the fact that a recommended temperature of water
stored in the hot water storage tank 32 is 60.degree. C. or above
in order to prevent the breeding of legionella bacteria or the
like, the target temperature of hot water is preferably 60.degree.
C. at a minimum. On the basis of the above, it is desirable to
adopt a refrigerant having a critical temperature of 60.degree. C.
at a minimum for the hot water supply refrigerant. When using such
a refrigerant as the hot water supply refrigerant for the hot water
supply refrigeration cycle 2, a higher COP would be obtained more
stably and at a lower cost.
[0168] In Embodiment 1, the case where the air conditioning
refrigerant exchanges heat with air in the outdoor heat exchanger
103, is illustrated by way of example, but the present invention is
not limited to this case. The air conditioning refrigerant may
exchange heat with water, a refrigerant, brine or the like.
Moreover, in Embodiment 1, as shown in FIGS. 1 and 3, the case
where the cooling indoor unit B and the heating indoor unit C are
each equipped with two or more indoor heat exchangers 118, is
shown, but the present invention is not limited to this case. For
example, in the case of the cooling-based operation shown in FIG.
1, the number of the indoor heat exchangers 118 in the cooling
indoor unit B may be one, and the number of the indoor heat
exchangers 118 in the heating indoor unit C may be zero or one.
Moreover, for example, in the case of the heating-based operation
shown in FIG. 3, the number of the indoor heat exchangers 118 in
the cooling indoor unit B and the heating indoor unit C may be zero
or one.
[0169] The capacity of the indoor heat exchanger 118 in each of the
cooling indoor unit B and the heating indoor unit C is not
particularly restricted. The capacities of the respective indoor
heat exchangers 118 may be different from each other, or may be the
same. Furthermore, the case where in the air conditioning
refrigeration cycle 1, excessive refrigerant is stored by the
accumulator 104, but the present invention is not limited to this
case. Upon removing the accumulator 104, excessive refrigerant may
also be stored in heat exchangers serving as radiators in the air
conditioning refrigeration cycle 1 (i.e., the outdoor heat
exchanger 103, the indoor heat exchanger 118, the
refrigerant-refrigerant heat exchanger 41, or the like).
[0170] In the air conditioning-hot water supply combined system 100
according to Embodiment 1, since the hot water supply load system
is constituted by a binary cycle (the air conditioning
refrigeration cycle 1 and the hot water supply refrigeration cycle
2), when serving a demand for high-temperature hot water supply
(for example, hot water of 80.degree. C. or above), it suffices
only to set the temperature of the radiator (heat
medium-refrigerant heat exchanger 51) in the hot water supply
refrigeration cycle 2 to a high temperature (for example,
condensation temperature 85.degree. C.). Accordingly, when there is
a demand for a heating load besides the demand for the hot water
supply, it is allowable not to increase the condensation
temperature (for example, 50.degree. C.) of the heating indoor unit
C, which allows reduction in energy consumption.
[0171] Furthermore, for example, when there is a demand for
high-temperature hot water supply during an air conditioning
cooling operation in summer, it is necessary to address the hot
water supply demand using a boiler or the like conventionally.
However, in the air conditioning-hot water supply combined system
100 according to Embodiment 1, since heat discharged in the air is
collected and reused for hot water supply, the system COP is
significantly enhanced, leading to energy saving. Although one
example of the present invention is explained above on the basis of
the air conditioning-hot water supply combined system 100 according
to Embodiment 1, the air conditioning refrigeration cycle 1
introducible into the air conditioning-hot water supply combined
system 100 that produces effects of the present invention is not
restricted to this example. As long as an arrangement capable of
concurrently supplying a cooling function and a heating function,
any arrangement may be adopted. For example, an arrangement shown
in Embodiment 2 of the present invention as described below may be
used.
Embodiment 2
[0172] FIG. 5 is a refrigerant circuit diagram showing a
refrigerant circuit configuration (especially, the refrigerant
circuit configuration at the time of the cooling-based operation)
in an air conditioning-hot water supply combined system 100a
according to Embodiment 2 of the present invention. With reference
to FIG. 5, description is made of a refrigerant circuit
configuration of the air conditioning-hot water supply combined
system 100a, especially the refrigerant circuit configuration at
the time of the cooling-based operation. The air conditioning-hot
water supply combined system 100a is installed in a building, a
condominium building or the like, and is operable to concurrently
provide a cooling load, a heating load, and a hot water supply load
by utilizing a refrigeration cycle circulating a refrigerant (air
conditioning refrigerant). Here, the description of Embodiment 2 is
focused on its differences from the above-described Embodiment 1.
The same parts as those in Embodiment 1 are designated by the same
symbols, and description thereof is omitted.
[0173] As shown in FIG. 5, the air conditioning-hot water supply
combined system 100a according to Embodiment 2 is characterized in
that the heat source unit A.sub.2 and the relay unit E.sub.2 in an
air conditioning refrigeration cycle 1a are configured differently
from the heat source unit A and the relay unit E in the air
conditioning refrigeration cycle 1 of the air conditioning-hot
water supply combined system 100 according to Embodiment 1.
Configurations other than the heat source unit A.sub.2 and the
relay unit E.sub.2 (that is, the cooling indoor unit B, the heating
indoor unit C, the hot water supply heat source circuit D, the hot
water supply refrigeration cycle 2, and the hot water supply water
circulation cycle 3) are configured to be similar to Embodiment
1.
[0174] [Heat Source Unit A.sub.2]
[0175] The heat source unit A.sub.2 is constituted of the air
conditioning compressor 101, the four-way valve 102, the outdoor
heat exchanger 103, the first heat source unit throttle means 124,
and the accumulator 104. As in the case of the heat source unit A,
the heat source unit A.sub.2 has a function of supplying cold heat
to the cooling indoor unit B, the heating indoor unit C, and the
hot water supply heat source circuit D. The discharge-side piping
140 connected to the air conditioning compressor 101 branches
between the air conditioning compressor 101 and the four-way valve
102. One (discharge-side piping 140a) is connected to the four-way
valve 102, and the other (discharge-side piping 140b) is connected
to the air conditioning discharged gas piping 125.
[0176] Moreover, in the heat source unit A.sub.2, there is provided
a bypass piping 141 for connecting the connection piping between
the four-way valve 102 and the outdoor heat exchanger 103 with a
connection piping serving as another refrigerant flow path of the
four-way valve 102 (a refrigerant flow path where the four-way
valve 102 and the outdoor heat exchanger 103 are not directly
connected). That is, the bypass piping 141 is provided for directly
connecting the four-way valve 102 and the outdoor heat exchanger
103. In the bypass piping 141, a second heat source unit throttle
means 128 and the check valve 105e are arranged from the upstream
side of the flow of the air conditioning refrigerant.
[0177] The first heat source unit throttle means 124 and the second
heat source unit throttle means 128 function as a decompression
valve or an expansion valve, and decompresses the air conditioning
refrigerant to expand it. The first heat source unit throttle means
124 and the second heat source unit throttle means 128 is
preferably constituted by means whose degree of opening is variably
controllable, such as precise flow rate control means by an
electronic expansion valve and inexpensive refrigerant flow rate
regulating means such as a capillary for example. The check valve
105a permits the flow of air conditioning refrigerant only in a
predetermined direction (the direction from the four-way valve 102
toward the outdoor heat exchanger 103).
[0178] [Relay Unit E.sub.2]
[0179] The relay unit E.sub.2 has a function of connecting the
cooling indoor unit B, the heating indoor unit C, and the hot water
supply heat source circuit D to the heat source unit A.sub.2,
respectively. The relay unit E.sub.2 also has a function of
alternatively opening/closing either of the valve means 109a and
the valve means 109b in the first distribution portion 109, and
thereby determining whether the indoor heat exchanger 118 and the
refrigerant-refrigerant, heat exchanger 41 to be connected are the
cooling unit (water cooler) or the heating unit (water heater). The
relay unit E.sub.2 differs from the relay unit E according to
Embodiment 1 in that it is provided with only the first
distribution portion 109, and not provided with the gas-liquid
separator 108, the second distribution portion 110, the first
internal heat exchanger 111, the first relay unit throttle means
112, the second internal heat exchanger 113, and the second relay
unit throttle means 114.
[0180] In the first distribution portion 109, the connection piping
133 and the connection piping 135 are branched into two. One (the
connection piping 133b and the connection piping 135b) is connected
to the air conditioning discharged gas piping 125, and other (the
connection piping 133a and the connection piping 135a) is connected
to the air conditioning suction gas piping 126. In the relay unit
E.sub.2, since there is provided no second distribution portion
110, neither of the connection piping 134 and the connection piping
136 are branched, and they are connected to an air conditioning
liquid piping 127.
[0181] Here, the cooling-based operation of the air conditioning
refrigeration cycle 1a will be described.
[0182] First, a part of the air conditioning refrigerant turned
into a high-temperature and high-pressure state by the air
conditioning compressor 101 is led to the air conditioning
discharged gas piping 125 and flows into the relay unit E2, while
the other part is led to the four-way valve 102. The air
conditioning refrigerant led to the air conditioning discharged gas
piping 125 is distributed into circuits with the valve means 109b
being opened. Here, the air conditioning refrigerant is adapted to
flow into the heating indoor unit C and the hot water supply heat
source circuit D. The air conditioning refrigerant flowed into the
heating indoor unit C radiates heat in the indoor heat exchanger
118, decompressed by the air conditioning throttle means 117, and
meets in the air conditioning liquid piping 127. On the other hand,
the air conditioning refrigerant flowed into the hot water supply
heat source circuit D radiates heat in the refrigerant-refrigerant
heat exchanger 41, decompressed by the hot water supply heat source
throttle means 119, and meets with the air conditioning refrigerant
flowed out from the heating indoor unit C in the air conditioning
liquid piping 127.
[0183] Meanwhile, the air conditioning refrigerant led to the
four-way valve 102 flows into the outdoor heat exchanger 103 via
the four-way valve 102. In the outdoor heat exchanger 103, the air
conditioning refrigerant flowed therein exchanges heat with outdoor
air and radiates heat. The air conditioning refrigerant flowed out
from the outdoor heat exchanger 103 is decompressed by the first
heat source unit throttle means 124 and meets in the air
conditioning liquid piping 127. The air conditioning refrigerant
that met in the air conditioning liquid piping 127 is distributed
to circuits with the valve means 109a opened. Here, the air
conditioning refrigerant is adapted to flow into the cooling indoor
unit B. The air conditioning refrigerant flowed into the cooling
indoor unit B is expanded into a low-temperature and low-pressure
state by the air conditioning throttle means 117, evaporates in the
indoor heat exchanger 118, and meets in the air conditioning
suction gas piping 126 via the valve means 109a. Part of the air
conditioning refrigerant that met in the air conditioning suction
gas piping 126 returns to the air conditioning compressor 101 via
the accumulator 104, while the other part is led to the bypass
piping 141.
[0184] Next, the heating-based operation of the air conditioning
refrigeration cycle 1a will be described.
[0185] FIG. 6 is a refrigerant circuit diagram showing a
refrigerant circuit configuration (especially, the refrigerant
circuit configuration at the time of the heating-based operation)
in the air conditioning-hot water supply combined system 100a
according to Embodiment 2 of the present invention. With reference
to FIG. 6, description is made of the heating-based operation of
the air conditioning refrigeration cycle 1a in the air
conditioning-hot water supply combined system 100a. First, most
part the air conditioning refrigerant turned into a
high-temperature and high-pressure state is led to the air
conditioning discharged gas piping 125, and distributed to circuits
with the valve means 109b opened. Here, the air conditioning
refrigerant is adapted to flow into the heating indoor unit C and
the hot water supply heat source circuit D.
[0186] The air conditioning refrigerant flowed into the heating
indoor unit C radiates heat in the indoor heat exchanger 118, being
decompressed by the air conditioning throttle means 117, and meets
in the air conditioning liquid piping 127. On the other hand, the
air conditioning refrigerant flowed into the hot water supply heat
source circuit D radiates heat in the refrigerant-refrigerant heat
exchanger 41, being decompressed by the hot water supply heat
source throttle means 119, and meets with the air conditioning
refrigerant flowed out from the heating indoor unit C in the air
conditioning liquid piping 127. The air conditioning refrigerant
met in the air conditioning liquid piping 127 is distributed to
circuits with the valve means 109a opened and circuits led to the
outdoor heat exchanger 103. Here, the air conditioning refrigerant
is adapted to flow into the cooling indoor unit B and the outdoor
heat exchanger 103.
[0187] The air conditioning refrigerant distributed into the
circuits whose valve means 109a is open, is expanded into a
low-temperature and low-pressure state by the air conditioning
throttle means 117, evaporates in the indoor heat exchanger 118,
and meets in the air conditioning suction gas piping 126. On the
other hand, the air conditioning refrigerant led into the outdoor
heat exchanger 103 is expanded into a low-temperature and
low-pressure state by the first heat source unit throttle means
124, evaporates in the indoor heat exchanger 103, being led into
the bypass piping 141, and meets with the discharged gas
refrigerant that has passed through the second heat source unit
throttle means 128 and the check valve 105a. This air conditioning
refrigerant meets with the air conditioning refrigerant that led
into the cooling indoor unit B via the four-way valve 102 in the
air conditioning suction gas piping 126. The air conditioning
refrigerant that met in the air conditioning suction gas piping 126
returns to the air conditioning compressor 101 via the accumulator
104.
[0188] The operation of the hot water supply refrigeration cycle 2
does not differ 4 irrespective of the operating state of the air
conditioning refrigeration cycle 1a, i.e., irrespective of whether
the air conditioning refrigeration cycle 1a is performing the
cooling-based operation or the heating-based operation. The
configuration and operation of the hot water supply refrigeration
cycle 2 is as explained in Embodiment 1. The operation of the hot
water supply water circulation cycle 3 does not differ by the
operating conditions of the air conditioning refrigeration cycle
1a, that is, whether in the cooling-based operation or in the
heating-based operation. Its configuration and operation is what is
described in Embodiment 1.
[0189] The check valve 105e may be constituted by valve means such
as a solenoid valve so as to more reliably perform switchover
between refrigerant flow paths. Moreover, the air conditioning
refrigerant circulating in the air conditioning refrigeration cycle
1a is not particularly limited in kinds. For example, as in the
case of Embodiment 1, the R410A may be used. Furthermore, any of
natural refrigerants may be adopted such as carbon dioxide
(CO.sub.2), hydrocarbon, and helium; alternative refrigerants
containing no chrome such as HFC410A, HFC407C, HFC401A; or
fluorocarbon refrigerants such as R22 or R134a, which is used in
existing products.
[0190] While the air conditioning refrigeration cycle 1a and the
hot water supply refrigeration cycle 2 have an independent
refrigerant circuit configuration, the circulating refrigerants may
be of the same kind or not. In either case, heat exchange is
performed in the refrigerant-refrigerant heat exchanger 41 and the
heat medium-refrigerant heat exchanger 51 without being mixed with
each other. Moreover, in Embodiment 2, as shown in FIGS. 5 and 6,
the case where the cooling indoor unit B and the heating indoor
unit C are equipped with two or more indoor heat exchangers 118 is
illustrated, but it is not limited thereto. For example, in the
case of the cooling-based operation shown in FIG. 5, the indoor
heat exchangers 118 in the cooling indoor unit B may be one, and
the indoor heat exchangers 118 in the heating indoor unit C may be
zero or one. Moreover, for example, in the case of the
heating-based operation shown in FIG. 6, the indoor heat exchangers
118 in the cooling indoor unit B and the heating indoor unit C may
be either zero or one.
[0191] In the air conditioning-hot water supply combined system
100a according to Embodiment 2, the hot water supply load system is
constituted by a binary cycle (the air conditioning refrigeration
cycle 1a and the hot water supply refrigeration cycle 2).
Therefore, when meeting a demand for high-temperature hot water
supply (for example, hot water of 80.degree. C. or above), it
suffices to set the temperature of the radiator (heat
medium-refrigerant heat exchanger 51) in the hot water supply
refrigeration cycle 2 to a high temperature (for example,
condensation temperature 85.degree. C.). Accordingly, when there is
a demand for a heating load besides the demand for the hot water
supply, there is no need to increase the condensation temperature
(for example, 50.degree. C.) of the heating indoor unit C, which
allows reduction in energy consumption.
Embodiment 3
[0192] FIG. 7 is a refrigerant circuit diagram showing a
refrigerant circuit configuration of an air conditioning-hot water
supply combined system 100b according to Embodiment 3 of the
present invention. With reference to FIG. 7, description is made of
the refrigerant circuit configuration of the air conditioning-hot
water supply combined system 100b. The air conditioning-hot water
supply combined system 100b is installed in a building, a
condominium building or the like, and is operable to concurrently
provide a cooling load, a heating load, and a hot water supply load
by utilizing a refrigeration cycle circulating a refrigerant (air
conditioning refrigerant). Here, the description of Embodiment 3 is
focused on its differences from the above-described Embodiments 1
and 2. The same parts as those in Embodiments 1 and 2 are
designated by the same symbols, and description thereof is
omitted.
[0193] In FIG. 7, the state of the four-way valve 102 in the
cooling-based operation is indicated by a solid line, and the state
thereof in the heating-based operation is indicated by a broken
line. Besides, in FIG. 7, the hot power supply refrigeration cycle
cabinet 200 is indicated by a chain line. That is, part of the air
conditioning refrigeration cycle 1, the hot water supply
refrigeration cycle 2, and part of the hot water supply water
circulation cycle 3 are accommodated in the hot power supply
refrigeration cycle cabinet 200. In addition, in order to allow the
mounting/demounting of the hot power supply refrigeration cycle
cabinet 200, connection valves are installed to the connection
portion between the air conditioning refrigeration cycle 1 and the
hot water supply refrigeration cycle 2, and the connection portion
between the hot water supply refrigeration cycle 2 and the hot
water supply water circulation cycle 3.
[0194] The connection portions between the air conditioning
refrigeration cycle 1 and the hot water supply refrigeration cycle
2, that is, the connection piping 135 and the connection piping 136
are provided with two connection valves (connection valve 201 and
connection valve 202, and connection valve 203 and connection valve
204). The connection valve 202 and the connection valve 203 are
installed inside the hot power supply refrigeration cycle cabinet
200, while the connection valve 201 and the connection valve 204
are installed outside the hot power supply refrigeration cycle
cabinet 200.
[0195] The connection portions between the hot water supply
refrigeration cycle 2 and the hot water supply water circulation
cycle 3, that is, a water piping connecting the heat
medium-refrigerant heat exchanger 51 and the hot water storage tank
32, and a water piping connecting the water circulation pump 31 and
the heat medium-refrigerant heat exchanger 51, respectively, have
two connection valves (connection valves 205 and 206; and
connection valves 207 and 208). The connection valves 206 and 207
are installed inside the hot power supply refrigeration cycle
cabinet 200, while the connection valves 205 and 208 are installed
outside the hot power supply refrigeration cycle cabinet 200.
[0196] That is, the air conditioning-hot water supply combined
system 100b according to Embodiment 3 differs in that the
mountable/demountable hot power supply refrigeration cycle cabinet
200 are provided in addition to the configuration of the air
conditioning-hot water supply combined system 100 according to
Embodiment 1. Configurations other than the hot power supply
refrigeration cycle cabinet 200, the connection valves 201 to 208,
(namely, the heat source unit A, the cooling indoor unit B, the
heating indoor unit C, the hot water supply heat source circuit D,
the relay unit E, the air conditioning refrigeration cycle 1, the
hot water supply refrigeration cycle 2, and the hot water supply
water circulation cycle 3) have configurations similar to those in
Embodiment 1.
[0197] By configuring the air conditioning-hot water supply
combined system 100b in this way, the air conditioning-hot water
supply combined system 100b according to the present invention can
be constituted as an alternate of a general-purpose indoor unit
(cooling indoor unit B, heating indoor unit C, or the like) for
general-purpose air conditioning refrigeration cycle. Therefore, it
is possible to suppress development investment for a
special-purpose air conditioning refrigeration cycle and to
constitute the air conditioning-hot water supply combined system
100b using existing air conditioning refrigerant cycles, to thereby
more easily achieve energy saving.
Embodiment 4
[0198] FIG. 8 is a refrigerant circuit diagram showing a
refrigerant circuit configuration of an air conditioning-hot water
supply combined system 100c according to Embodiment 4 of the
present invention. With reference to FIG. 8, description is made of
a refrigerant circuit configuration of the air conditioning-hot
water supply combined system 100c. The air conditioning-hot water
supply combined system 100c is installed in a building, a
condominium building or the like, and is operable to concurrently
provide a cooling load, a heating load, and a hot water supply load
by utilizing a refrigeration cycle circulating a refrigerant (air
conditioning refrigerant). Here, the description of Embodiment 4 is
focused on its differences from the above-described Embodiments 1
to 3. The same parts as those in Embodiments 1 to 3 are designated
by the same symbols, and description thereof is omitted.
[0199] In FIG. 8, the state of the four-way valve 102 in the
cooling-based operation is indicated by a solid line, and the state
thereof in the heating-based operation is indicated by a broken
line. As shown in FIG. 8, the air conditioning-hot water supply
combined system 100c according to Embodiment 4 is basically the
same as that air conditioning-hot water supply combined system 100
according to Embodiment 1, but differs in that a hot water supply
low-pressure side pressure detecting means 23, a hot water supply
higher-pressure side pressure detection means 24, a hot water
delivery temperature detection means (heat medium temperature
detection means) 33, the hot water supply control means 25, and an
air conditioning control means 120 are provided.
[0200] The hot water supply low-pressure side pressure detecting
means 23 is provided on the suction side of the hot water supply
compressor 21, and used for detecting the pressure of the air
conditioning refrigerant to be sucked into the hot water supply
compressor 21. The hot water supply high-pressure side pressure
detection means 24 is provided on the discharge side of the hot
water supply compressor 21, and used for detecting the pressure of
the air conditioning refrigerant discharged from the hot water
supply compressor 21. The hot water delivery temperature detection
means 33 is provided on the water outlet side of the heat
medium-refrigerant heat exchanger 51, and to detect the temperature
of water stored in the hot water storage tank 32 to be delivered.
Information detected by the hot water supply low-pressure side
pressure detecting means 23, the hot water supply higher-pressure
side pressure detection means 24, and the hot water delivery
temperature detection means 33 is outputted to the hot water supply
control means 25.
[0201] The hot water supply control means 25 is constituted of the
hot water supply communication means 26, hot water supply
calculation means 27, and hot water supply storage means 28. The
hot water supply control means 25 causes the hot water supply
storage means 28 to store at least one out of the ON/OFF state of
the hot water supply refrigeration cycle 2, that is detection
information from the above-described detection means, such as the
ON/OFF state of the hot water supply compressor 21, and its
frequency and discharge temperature; the high-pressure side
pressure, the low-pressure side pressure, the condensation
temperature, the evaporation temperature of the hot water supply
refrigerant circulating in the hot water supply refrigeration cycle
2; the entering water temperature, the delivery hot water
temperature of the heat medium-refrigerant heat exchanger 51; and
the degree of throttling of the hot water supply throttle means 22
and the hot water supply heat source throttle means 119 (the number
of pulses when an electronic expansion valve is used). On the basis
of stored information, the hot water supply calculation means 27
performs calculation and performs various kinds of control.
[0202] The air conditioning control means 120 is constituted of the
air conditioning communication means 121, the air conditioning
calculation means 122, and the air conditioning storage means 123.
The air conditioning control means 120 and the hot water supply
control means 25 can perform control in cooperation with each other
by intercommunicating information via the hot water supply
communication means 26 of the hot water supply control means 25,
and the air conditioning communication means 121 of the air
conditioning control means 120. In this manner, by allowing the two
control means to intercommunicate, a higher-degree and more stable
energy-saving system can be constructed.
[0203] The air conditioning control means 120 causes the air
conditioning storage means 123 to store at least one out of the
ON/OFF state of the air conditioning refrigeration cycle 1, that is
detection information from the various detection means (not shown),
such as the ON/OFF state of the air conditioning compressor 101,
and its frequency and discharge temperature; the high-pressure side
pressure, the low-pressure side pressure, the condensation
temperature, the evaporation temperature of the air conditioning
refrigerant circulating in the air conditioning refrigeration cycle
1; the fan air volume, the inlet temperature, the outlet
temperature, the intake air temperature of the outdoor heat
exchanger 103; the changeover state of the four-way valve 102; the
degrees of throttling of the first relay unit throttle means 112,
the second relay unit throttle means 114, and the degree of
throttling of the air conditioning throttle means 117; the
changeover states of the valve means 109a and the valve means 109b;
and the fan air volume and indoor unit intake air temperature of
the cooling indoor unit B and the heating indoor unit C. On the
basis of stored information, the hot water supply control means 120
causes the air conditioning calculation means 122 performs
calculation and performs various kinds of control.
[0204] Concrete control behavior performed in this embodiment will
be described below.
[0205] For example, when the ON/OFF state of the air conditioning
compressor 101 is communicated from the air conditioning control
means 120 to the hot water supply control means 25, and in
synchronization with the ON/OFF timing of the hot water supply
compressor 21 is controlled, there is no need to perform a useless
operation of the hot water supply compressor 21, whereby energy
saving can be achieved. Furthermore, after the start-up of the air
conditioning compressor 101, by actuating the hot water supply
compressor 21 after waiting for the air conditioning refrigeration
cycle 1 to be stabilized, the hot water supply refrigerant in the
air conditioning refrigeration cycle 2 can sufficiently absorb heat
of the air conditioning refrigeration cycle 1 and evaporate when
passing through the refrigerant-refrigerant heat exchanger 41. This
allows the hot water supply refrigeration cycle 2 to stably
operate, thereby enhancing the reliability of system, and ensuring
energy saving.
[0206] When, because of failure of the air conditioning compressor
101 and excessively small load, an operation is once interrupted
and restarts, and when the hot water supply compressor 21 is
operating at a high frequency, if the hot water supply compressor
21 is not controlled to operate together with the air conditioning
compressor 101 and when the hot water supply compressor 21 is
operating at a high frequency, the low-pressure side pressure of
the hot water supply refrigeration cycle 2 may cause abnormal
lowering during the stoppage of the air conditioning compressor
101, thereby bringing about a large heat shock when the air
conditioning compressor 101 resumes its operation. This being the
case, when the air conditioning compressor 101 stops during
operation of the hot water supply compressor 21, for example, by
adding an item indicating that the low-pressure side pressure of
the hot water supply refrigeration cycle 2 is to fall within a
predetermined range, to a control target for the hot water supply
compressor 21, it is possible to prevent a large heat shock and
enhance the reliability of the system for longer time period, to
thereby ensure energy saving.
[0207] Furthermore, in the air conditioning-hot water supply
combined system 100c according to Embodiment 4, in a state where
water in the hot water storage tank 32 is at a low temperature, the
compression ratio of the hot water supply compressor 21 is prone to
become small, thereby causing a risk of stalling of the hot water
supply compressor 21. Therefore, on the basis of outputs of the hot
water supply lower-pressure side pressure detecting means 23 and
the hot water supply high-pressure side pressure detection means 24
of the hot water supply refrigeration cycle 2 stored by the hot
water supply control means 25, when the compression ratio of the
hot water supply compressor 21 calculated by the hot water supply
calculation means 27 falls below a predetermined range, the hot
water supply refrigeration cycle 2 is controlled in the direction
of increasing the compression ratio by throttling the hot water
supply throttle means 22, thereby allowing to enhance the
reliability of the system, and ensuring energy conservation.
[0208] Specifically, by connecting the hot water supply control
means 25 and the hot water supply throttle means 22 by wire or by
radio, a signal may be directly provided (for example, when the
electronic expansion valve is used, a signal for reducing the
pulses is sent). Alternatively, the hot water supply throttle means
22 may be indirectly throttled by increasing a supercooling degree
of the hot water supply refrigerant at the outlet of the heat
medium-refrigerant heat exchanger 51, or the superheating degree of
the hot water supply refrigerant at the outlet of the
refrigerant-refrigerant heat exchanger 41 that are assumed to be
control target values of the hot water supply throttle means 22 to
be larger than values when the compression ratio of the hot water
supply refrigeration cycle 2 is within a predetermined range.
[0209] Moreover, by providing the hot water supply heat source
throttle means 119 with a control signal for throttling, the
evaporation heat source of the hot water supply refrigeration cycle
2 decreases to thereby reduce the pressure on the low-pressure side
of the hot water supply refrigeration cycle 2, whereby the
compression ratio can be increased. Specifically, by connecting the
hot water supply control means 25 and the hot water supply heat
source throttle means 119 by wire or by radio, a signal may be
directly provided (for example, when the electronic expansion valve
is used, a signal for reducing the pulses is sent). Alternatively,
the hot water supply heat source throttle means 119 may be
indirectly throttled by increasing the supercooling degree of the
hot water supply refrigerant at the outlet of the
refrigerant-refrigerant heat exchanger 41, which is assumed to be
an control target value of the hot water supply heat source
throttle means 119 to be larger than the value when the compression
ratio of the hot water supply refrigeration cycle 2 is within a
predetermined range.
[0210] Here, the case in which the control of the hot water supply
heat source throttle means 119 is performed by connecting with the
hot water supply control means 25 by wire or by radio is
illustrated, but it is not limited thereto. The control may be
performed by connecting with the air conditioning control means
120. Furthermore, for example, by adhering temperature detection
means onto piping between the hot water supply throttle means 22
and the refrigerant-refrigerant heat exchanger 41 and detecting the
evaporation temperature, a saturated pressure calculated from the
output may be substituted for the hot water supply lower-pressure
side pressure detecting means 23. Moreover, although it is
difficult when the heat medium-refrigerant heat exchanger 51 is a
plate heat exchanger, however, if the condensation temperature is
detectable by the temperature detection means as in the case in
which in a double piping heat exchanger, a refrigerant is passed
through outside the hot water supply higher-pressure side pressure
detection means 24 can detect the condensation temperature by the
temperature detection means, and a saturated pressure calculated
from the output may be substituted.
[0211] Regarding the control of the hot water supply compressor 21,
because controlling the output of the hot water delivery
temperature detection means 33 as a target value directly follows
user's demand, there will be no useless operation, leading to
energy saving. However, for the piping on the water side of the
heat medium-refrigerant heat exchanger 51, stainless steel is
assumed to be adopted from the viewpoint of anticorrosion, so that,
in this case, in order to detect the delivery hot water
temperature, a method in which temperature detection means is
adhered to the outside of the piping of the delivery hot water
portion cannot be adopted. Therefore, it is necessary to directly
detect the water temperature inside the piping, which results in an
increase in cost, and poses an obstacle to the introduction of an
energy-saving system.
[0212] However, if the performance of the heat medium-refrigerant
heat exchanger 51 is known in advance, it is known that the hot
water delivery temperature can be estimated with some degree of
accuracy from the condensation temperature of the hot water supply
refrigerant that is exchanging heat with water. For example, it is
ascertained by a simulation that, in some combination, the
difference in the hot water delivery temperature and the
condensation temperature of the hot water supply refrigeration
cycle 2 is 6.degree. C., and that even if water circulation amount
is decreased by a factor of a quarter, the difference value is
reduced down to only 3.degree. C. Therefore, even if the hot water
delivery temperature is not directly measured, it is possible to
estimate the hot water delivery temperature with a certain degree
of accuracy on the basis of an output of the hot water supply
higher-pressure side pressure detection means 24 in the hot water
supply refrigeration cycle 2, and to treat the estimated value as a
control target value of the hot water supply compressor 21.
[0213] That is, on the basis of at least one value out of the
high-pressure side pressure of the hot water supply refrigeration
cycle 2, the condensation temperature, and a temperature at a
position from the outlet of the hot water supply compressor 21 to
the inlet of the heat medium-refrigerant heat exchanger 51, the hot
water supply control means 25 can estimate the temperature (hot
water delivery temperature) of a heat medium (here, water) at the
outlet of the heat medium-refrigerant heat exchanger 51, and can
control the hot water supply compressor 21 so that the
above-described estimated value approaches a predetermined target
value, thereby allowing the introduction of an energy-saving system
without increasing cost.
[0214] In a state in which the temperature of the water in the hot
water storage tank 32 is low, the heat change amount in the heat
medium-refrigerant heat exchanger 51 tends to increase, for
example, when the heating indoor unit C is in operation
concurrently, a necessary heating capability may not sometimes be
obtained on the side of heating indoor unit C.
[0215] In the system according to the present embodiment, for
example, in the case in which the temperature of the water in the
hot water storage tank 32 is low, by controlling the hot water
supply compressor 21 so as to reduce the upper limit of the
frequency, the heating capability of the heating indoor unit C can
be ensured, thereby allowing the realization of a stable
energy-saving system without impairing user's comfort.
[0216] Moreover, in this embodiment, when not a single heating
indoor unit C is operating, there is no need to concern about
capability deficiency of the heating indoor unit C, and therefore,
it is possible to perform control to inhibit reduction in the upper
limit of the frequency of the hot water supply compressor 21,
thereby allowing making the most of the capability of the system.
Here, the temperature of water in the hot water storage tank 32 may
be estimated using an entering water temperature or a leaving water
temperature.
[0217] The system according to this embodiment is a system in which
the air conditioning refrigeration cycle concurrently covers a
heating load and a cooling load to thereby reduce exhaust heat,
whereby energy saving is implemented. Here, the air conditioning
load such as a cooling load or a heating load depends upon a user's
real-time demand, whereas the hot water supply load can be covered
by the heat stored in the hot water storage tank 32. Therefore, a
system in which the air conditioning refrigeration cycle and a hot
water supplying refrigerant cycle intercommunicates as the present
embodiment, would be able to perform operation to minimize exhaust
heat by operating the hot water supply refrigeration cycle 2 in
synchronization with an operation of the cooling indoor unit B.
[0218] When attempting to minimize exhaust heat, by the air
conditioning refrigeration cycle and the hot water supplying
refrigeration cycle intercommunicating therebetween, performing
control so that the heat exchange amount in the outdoor heat
exchanger 103 in the air conditioning refrigeration cycle
decreases, allows an achievement of the minimization of exhaust
heat. For example, when the outdoor heat exchanger 103 is an air
heat exchanger, controlling the hot water supply compressor 21 to
reduce the fan wind amount enables implementation of the
minimization of exhaust heat.
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