Patent Grant
8418494
The present invention relates to an air conditioning apparatus using a refrigeration cycle, more particularly to an arrangement of a distributor and the like installed for distributing refrigerant and refrigerator oil when a plurality of heat source apparatuses (heat source side units) are provided.
An air conditioning apparatus is provided that can individually arbitrarily perform cooling and heating operations. (For example, refer to Patent Document 1) In such an air conditioning apparatus, a refrigerant flows in the same direction in a plurality of refrigerant piping from a heat source apparatus to a plurality of indoor units (load side units). That is, a high-pressure refrigerant is output from the heat source apparatus and a low-pressure refrigerant returns to the heat source apparatus. Thereby, there is one heat source apparatus and since the refrigerant returns to the heat source apparatus always through a single piping from a plurality of indoor units, the refrigerant returns to the heat source apparatus in the proper quantity. In addition, hereinafter high or low pressure is not specified in relation to a reference pressure but represented as a relative pressure by such as pressurization by a compressor 11 and a refrigerator pass control by each throttle device. Further, it is the same for high and low temperatures.
The refrigerant oil discharged from the compressor in the heat source apparatus returns through the indoor unit to the heat source apparatus, however, since such refrigerator oil all returns to a single heat source apparatus, problems such as a depletion of the refrigerator oil hardly occur.
For example, when there are many indoor units and much more capability is required for the heat source apparatus side, air conditioning is performed by pipe-connecting a plurality of heat source apparatuses. Thereby, for example, a plurality of heat source apparatuses are connected in parallel, the refrigerant in each heat source apparatus is joined to be supplied to the indoor unit side, and the refrigerant and refrigerator oil from the indoor unit side are branched to be distributed to each heat source apparatus. Then, it is necessary to distribute them to each heat source apparatus with an appropriate amount in accordance with an operation condition thereof.
In the case when the refrigerant is in a gas-liquid two-phase condition and the refrigerator oil is mixed and included in a gas refrigerant, a liquid refrigerant and refrigerator oil are not necessarily divided according to the same ratio as a distribution ratio of the gas refrigerant. Especially under such a condition that a gas flow rate falls, a liquid becomes a laminar flow to flow along an inner surface of piping and be subjected to gravity and centrifugal forces. Therefore, it is not easy to determine the degree of distribution of liquids. When a liquid distribution rate changes dependent on such as an installation status of distribution means and the like, it is possible that some heat source apparatuses may run short of the refrigerant and return amount of the refrigerator oil. Nevertheless, installation of distribution means has been subjected to, for example, convenience of arrangement of a plurality of heat source apparatuses at an installation site.
In order to solve the above problems, the purpose of the present invention is to provide an air conditioning apparatus capable of effectively distributing the refrigerant and refrigerator oil into a plurality of heat source apparatuses.
An air conditioning apparatus according to the present invention includes a plurality of heat source apparatuses having a heat source apparatus side heat exchanger and a compressor, one or more indoor units having a flow rate control device and an indoor unit side heat exchanger, at least two main pipes for pipe-connecting between a plurality of heat source apparatuses and one or more indoor units, a tubular distributor for branching a refrigerant from a main pipe flowing from an inlet into a plurality of outlets to distribute into a plurality of heat source apparatuses, and connection piping for connecting a plurality of heat source apparatuses and the distributor respectively and fixedly disposes the distributor against one heat source apparatus among the plurality of heat source apparatuses at a predetermined position in a predetermined direction.
According to the present invention, since a distributor for distributing a refrigerant to a plurality of heat source apparatuses is fixedly disposed at a predetermined position against one heat source apparatus, a stable refrigerant distribution can be performed according to a predetermined supposed distribution by the arrangement in consideration of the effect of gravity and each heat source apparatus (especially one heat source apparatus).
As shown in
Between the heat source apparatus 10A and the relay 30 connect a set of a first main pipe 100, a distributor 50, and a first connection piping 500A and the set of a second main pipe 200, a merger 51, and a second connection piping 600A. In the same way, between the heat source apparatus 10B and the relay 30 connect a set of the first main pipe 100, the distributor 50, and the first connection piping 500B and the set of the second main pipe 200, the merger 51, and the second connection piping 600B. Then, in the set of the first main pipe 100, distributor 50, and first connection piping 500, a low-pressure refrigerant flows from the relay 30 side to the heat source apparatus 10 side. In the set of the second main pipe 200, the merger 51, and the second connection piping 600, a high-pressure refrigerant flows from the heat source apparatus 10 side to the relay 30 side.
Here, in the present embodiment, for example, it is provided that the distributor 50 is installed inside the heat source apparatus 10A, that is tubular distribution means having one inlet and a plurality of outlets. Because of this, the first connection piping 500A is inside the heat source apparatus A. The relation among the distributor 50, the first connection piping 500A, and the heat source apparatus A will be described later. On the other hand, as for the tubular merger 51 having a plurality of inlets and one outlet, the installation varies according to where heat source apparatuses 10A and 10B are installed. Therefore, basically, the merger 51 is installed outside the heat source apparatus 10 and the refrigerant flowing in the second connection piping 600A and 600B are made to be joined to flow into the second main pipe 200. Here, in the air conditioning apparatus according to the present embodiment, a diameter of the first main pipe 100 is larger than that of the second main pipe 200.
On the other hand, the relay 30 and the indoor unit 20a are connected by the second branched pipe 400a and the first branched pipe 300a. In the same way, the relay 30 and indoor unit 20b are connected by the second branched pipe 400b and the first branched pipe 300b, and the relay 30 and indoor unit C are connected by the second branched pipe 400c and the first branched pipe 300c. Through a piping connection by the first main pipe 100, second main pipe 200, second branched pipe 400 (400a, 400b, and 400c) and first branched pipe 300 (300a, 300b, and 300c), the refrigerant circulates among the heat source apparatuses 10A and 10B, relay 30, indoor unit 20a, 20b, and 20c to configure a refrigerant circuit.
In
A heat source apparatus side heat exchanger 13 (13A and 13B) has, for example, a pipe for passing the refrigerant and a fin for increasing a heat transfer area of the refrigerant passing the pipe and the air (outdoor air) to perform heat exchange between the refrigerant and the air. For example, at the time of heating and heating-dominant operations, the heat source apparatus side heat exchanger 13 functions as an evaporator to evaporate the refrigerant into a gas. On the contrary, when in the cooling and cooling-dominant operations, the heat exchanger 13 functions as a condenser to condense the refrigerant into a liquid. For example, at the time of the cooling-dominant operation, the heat exchanger 13 is adjusted to condense the refrigerant up to a state of a two-phase region (gas liquid two-phase refrigerant) of a liquid and a gas. In the neighborhood of the heat source apparatus side heat exchanger 15, a heat source apparatus side fan (not shown) is provided for efficiently performing heat exchange between the refrigerant and the air. An accumulator 14 (14A and 14B) accumulates an excessive refrigerant in the refrigerant circuit.
There are provided a first check valve 15-1, second check valve 15-2, third check valve 15-3, and fourth check valve 15-4. Each check valve makes a circulation path of the refrigerant that varies dependent on the cooling or heating operation fixed according to each operation and prevent the refrigerant to flow backward in the other paths. The first check valve 15-1 (15-1A and 15-1B) is located between the heat source side heat exchanger 13 and the second main pipe 200 to allow a refrigerant circulation only in the direction from the heat source side heat exchanger 13 to the second main pipe 200. The second check valve 15-2 (15-2A and 15-2B) is located between the four-way switching valve 12 and the first main pipe 100 to be mentioned later to allow a refrigerant circulation only in the direction from the first main pipe 100 to the four-way switching valve 12. The third check valve 15-3 (15-3A and 15-3B) is located between the four-way switching valve 12 and the second main pipe 200 to allow a refrigerant circulation only in the direction from the four-way switching valve 12 to the second main pipe 200. The fourth check valve 15-4 (15-4A and 15-4B) is located between the heat source apparatus side heat exchanger 13 and the first main pipe 100 to allow a refrigerant circulation only in the direction from the first main pipe 100 to the heat source apparatus side heat exchanger 13. A first manual opening and closing valve 16-1 (16-1A and 16-1B) and a second manual opening and closing valve 16-2 (16-2A and 16-2B) are in a closed state, for example, at the time of shipment. Then, they are opened at the installation and made to circulate the refrigerant. Therefore, when operating the sir conditioning apparatus 1, they are usually in the open state.
The relay 30 in the present embodiment is composed of a first branched part 31, second branched part 36, gas-liquid separator 41, and relay supercooled portion 42. The first branched part 31 has a first opening and closing valve 34 (34a, 34b, and 34c), second opening and closing valve 35 (35a, 35b, and 35c), and association parts 32 and 33.
One ends of the first opening and closing valve 34 and the second opening and closing valve 35 are connected with the first branched pipe 300 respectively. Then, the other end of the first opening and closing valve 34 is collectively connected by the association part 32 to connect with the first main pipe 100. Further, the other end of the second opening and closing valve 35 is collectively connected by the association part 33 to connect with the second main pipe 200 through the gas liquid separator 41. When flowing in the refrigerant from the indoor unit 20 to the first main pipe 100, the first opening and closing valve 34 is opened and the second opening and closing valve 35 is closed. When flowing in the refrigerant from the second main pipe 200 to the indoor unit 20 through the gas-liquid separator 41, the first opening and closing valve 34 is closed and the second opening and closing valve 35 is opened.
A second branched part 36 has a first relay check valve 39 (39a, 39b, and 39c), second relay check valve 40 (40a, 40b, and 40c), and association parts 37 and 38. The first relay check valve 39 and the second relay check valve 40 are in a reverse parallel relation and each end is connected with the second branched pipe, respectively. The other end of the first relay check valve 39 is collectively connected by the association part 37. In the same way, the other end of the second relay check valve 40 is collectively connected by the association part 38. When the refrigerant flows from the indoor unit 20 side to the relay supercooled portion 42 side, the flow passes the first relay check valve 39 and the association part 37. When the refrigerant flows from the relay supercooled portion 42 side to the indoor unit 20 side, the flow passes the second relay check valve 40 and the association part 38.
A gas-liquid separator 41 separates the refrigerant flowing from the second main pipe 200 into a gas refrigerant and a liquid refrigerant. A gas phase part (not shown) from which a gas refrigerant flows out is connected with the first branched part 31 (association part 33). When the second opening and closing valve 35 is open, the gas refrigerant flows into the indoor unit 20 side. On the other hand, the liquid phase part (not shown) from which the liquid refrigerant flows out is connected with the second branched part 36 through the relay supercooled portion 42.
The relay supercooled portion 42 has a first flow rate control device 43, bypass piping 44, second flow rate control device 45, second heat exchange part 46, and first heat exchange part 47. The relay supercooled portion 42 is provided in order to overcool the liquid refrigerant, for example, at the time of the cooling operation to supply it to the heat source apparatus 10. The refrigerant and the like used for overcooling is made to flow into the main pipe 100. The first flow rate control device 43 adjusts a refrigerant flow amount (a refrigerant amount flowing per unit time) flowing from the gas liquid separator 41 to the second branched part 36 through the first heat exchange part 47 and second heat exchange part 47. A bypass piping 47 connects the second branched part 36 with the main pipe 100 through the first heat exchange part 47 and the second heat exchange part 46. The second flow rate control device 45 adjusts the refrigerant flow amount passing through the bypass piping 44. The second heat exchange part 46 performs heat exchange between the refrigerant at the downstream part of the second flow rate control device 45 flowing through the bypass piping 44 and the refrigerant flowing from the first flow rate control device 43 to the association part 38 of the second branched part 36. On the other hand, the first heat exchange part 47 performs heat exchange between the refrigerant flowing at the downstream part of the bypass piping 44 and the second heat exchange part 46 and the refrigerant flowing from the gas-liquid separator 41 to the first flow rate control device 43.
A first pressure detector 60 and a second pressure detector 61 are attached to the relay 30. The first pressure detector 60 is attached to the piping which connects the first flow rate control device 43 and the gas-liquid separator 41. The second pressure detector 61 is attached to the piping which connects the first flow rate control device 43 and the second branched part 36.
Next, descriptions will be given to the configuration of the indoor unit 20 (20a, 20b, and 20c). The indoor unit 20 includes an indoor unit side heat exchanger 21 and an indoor unit side flow rate control device 22a adjacently connected in series with the indoor unit side heat exchanger 21. The indoor unit side heat exchanger 21 serves as an evaporator in the cooling operation and as a condenser in the heating operation like the above mentioned heat source apparatus side heat exchanger 13 to perform heat exchange between the air and the refrigerant in the air conditioning object space. The indoor unit side flow rate control device 22 functions as a pressure reducing valve and expansion valve to adjust the pressure of the refrigerant passing the indoor unit side heat exchanger 21. Here, the indoor unit side flow rate control device 22 according to the present embodiment is composed of an electronic expansion valve capable of changing an opening degree, for example. Then, at the time of the cooling operation, based on a degree of superheat at a refrigerant outlet side of the indoor unit side heat exchanger 21, an opening and closing status (opening degree) of the indoor unit side flow rate control device 22 is controlled. At the time of the heating operation, based on the degree of supercooling degree at the refrigerant outlet side (here, the second branched pipe 400), the opening and closing status (opening degree) of the indoor unit side flow rate control device 22 is controlled.
The air conditioning apparatus of the present embodiment that is configured as the above can perform operation of any of the four forms as mentioned the above: all cooling operation, all heating operation, cooling-dominant operation, and heating-dominant operation. Here, the heat source apparatus side heat exchanger 13 of the heat source apparatus 10 functions as a condenser at the time of the all cooling operation and cooling-dominant operation and functions as an evaporator at the time of the all heating operation and heating-dominant operation.
Next, descriptions will be given to the all cooling operation based on
A gas liquid separator 41 separates the refrigerant flowing into the relay 30 into a gas refrigerant and a liquid refrigerant. Here, in the all cooling operation, the refrigerant flowing into the relay 30 is the liquid refrigerant, almost no gas refrigerant basically. At the time of the heating operation, in the first branched part 31, the first opening and closing valve 34 (34a, 34b, and 34c) is opened and the second opening and closing valve 35 (35a, 35b, and 35c) is closed. Therefore, no gas refrigerant flows in the indoor unit 20 (20a, 20b, and 20c) side. On the other hand, the liquid refrigerant passes through the second heat exchange part 46 and first flow rate control device 43 and part of it flows into the second branched part 36. The refrigerant flowed into the second branched part 36 branched into the indoor units 20a, 20b, and 20c through an association part 37, first relay check valves 39a, 39b, and 39c, and second branched pipes 400a, 400b, and 400c.
In the indoor units 20a, 20b, and 20c, the liquid refrigerant flowing from the second branched pipes 400a, 400b, and 400c are subjected to an opening adjustment by the indoor unit side flow rate control devices 22a, 22b, and 22c to be pressure-adjusted. Here, as mentioned before, the opening adjustment by the indoor unit side flow rate control devices 22 is performed based on the degree of superheat of each indoor unit side heat exchanger 21 at the refrigerant outlet side. Through the opening adjustment of each indoor unit side flow rate control device 22a, 22b, and 22c, the refrigerant turned into a low-pressure gas-liquid two-phase refrigerant or low-pressure liquid refrigerant flows into the indoor unit side heat exchangers 21a, 21b, and 21c, respectively. The low-pressure gas-liquid two-phase refrigerant or low-pressure liquid refrigerant evaporates through the heat exchange between the indoor air to be an air conditioning object space while passing through the indoor unit side heat exchangers 21a, 21b, and 21c, respectively. Then, it turns into a low-pressure gas refrigerant to flow into the first branched pipes 300a, 300b, and 300c, respectively. Thereby, it cools the indoor air through the heat exchange to perform the cooling operation in the room. Here, the gas refrigerant is employed, however, in some cases, it may not be completely gasified in the indoor unit side heat exchangers 21a, 21b, and 21c and gas-liquid two-phase refrigerant flows, for example, when the air conditioning load (heat amount required by the indoor unit, hereinafter, referred to as a load) in each indoor unit 20 is small and when a transient operation is performed. The low-pressure gas refrigerant or gas-liquid two-phase refrigerant (low-pressure refrigerant) flowing from the first branched pipes 300a, 300b, and 300c flow into the first main pipe 100 through first opening and closing valves 34a, 34b, and 34c and association part 32.
A distributor 50 divides the low-pressure refrigerant flowing in the first main pipe 100 into the refrigerant to flow into the heat source apparatus 10A side and the refrigerant to flow into the heat source apparatus 10B side. The refrigerant to flow into the heat source apparatus 10A side flows into the heat source apparatus 10A through the first connection piping 500A. Then, the refrigerant circulates by returning to the compressor 11A again through the second check valve 15-2A, four-way switching valve 12A, and accumulator 14A. The refrigerant to flow into the heat source apparatus 10B flows into the heat source apparatus 10B side through the first connection piping 500B as well. Then, the refrigerant returns back to the compressor 11B through the second check valve 15-2B, four-way switching valve 12B, and accumulator 14B of the heat source apparatus 10B. This is a circulation path of the refrigerant at the time of the all, cooling operation.
Here, descriptions will be given to the refrigerant flow in the relay supercooled portion 42. As mentioned before, the liquid refrigerant divided by the gas-liquid separator partly flows into the second branched part 36 by way of the second heat exchange part 46 and the first flow rate control device 43. On the other hand, the refrigerant which does not flow into the second branched part 36 side passes through the bypass piping 14. Then, by adjusting the opening of the second flow rate control device 45, the refrigerant passes through the second heat exchange part 46 and the first heat exchange part 47 to supercool the refrigerant flowing into the second branched part 36 and flow into the first main pipe 100 as a low-pressure refrigerant. By supercooling the refrigerant, it is possible to reduce a enthalpy at the refrigerant inlet side (here, the second branched pipe 400 side) and increase the heat exchange amount with the air in the indoor unit side heat exchangers 21a, 21b, and 21c. Here, when the opening of the second flow rate control device 45 becomes large to increase the refrigerant amount (the refrigerant used for supercooling) flowing through the bypass piping 14, some refrigerant cannot be evaporated. In such a case, the gas-liquid two-phase refrigerant flows into the distributor 50 through the first main pipe 100. In addition, the above holds not only for the configuration of the air conditioning apparatus 1 of the present embodiment. The same situations occur in the air conditioning apparatus having a configuration such that a circuit bypassing a high-pressure liquid refrigerant with a low-pressure side is externally provided to a plurality of heat source apparatuses and a bypassed flow flows into the inlet side of the distribution part (the distributor 20 in the present embodiment) for example.
The gas-liquid separator 41 separates the refrigerant flowed into the relay 30 into a gas refrigerant and a liquid refrigerant. The gas refrigerant flowed into the relay 30 flows into the relay 30 flows into the first branched part 31. Here, in the first branched part 31, the first opening and closing valve 34 (34a, 34b, and 34c) is closed and second opening and closing valve 35 (35a, 35b, and 35c) is opened. Therefore, the refrigerant flowed into the first branched part 31 is branched to all indoor units 20a, 20b, and 20c through the association part 33, second opening and closing valves 35a, 35b, and 35c, and first branched pipes 300a, 300b, and 300c.
In the indoor units 20a, 20b, and 20c, indoor unit side flow rate control devices 22a, 22b, and 22c adjust opening degree, respectively. Thus, regarding the refrigerant flowing from the first branched pipes 300a, 300b, and 300c, the pressure of the refrigerant flowing in the indoor unit side heat exchangers 21a, 21b, and 21c is adjusted, respectively. The high-pressure gas refrigerant is condensed through the heat exchange to turn into a liquid refrigerant while passing through the indoor unit side heat exchangers 21a, 21b, and 21c to pass through the indoor unit side flow rate control devices 22a, 22b, and 22c. Then, the indoor air is heated through the heat exchange and heating operation is performed in the room. The refrigerant passing through the indoor unit side flow rate control devices 22a, 22b, and 22c turns into a low-pressure gas-liquid two-phase refrigerant or low-pressure liquid refrigerant to flow into the association part 38 through the second branched pipes 400a, 400b, and 400c and second relay check valves 40a, 40b, and 40c. Then, the refrigerant passes through the second heat exchange section 46 and first heat exchange part 46 to flow into the first main pipe 100. Then, by adjusting the opening of the second flow rate control device 45, the low-pressure gas-liquid two-phase refrigerant flows into the first main pipe 100.
The distributor 20 divides the low-pressure refrigerant flowing in the first main pipe 100 into the refrigerant to flow into the heat source apparatus 10A side and the refrigerant to flow into the heat source apparatus 10B side. The refrigerant flowing at the heat source apparatus 10A side flows into the heat source apparatus 10A through the first connection piping 500A and passes through the fourth check valve 15-4A of the heat source apparatus 10A to flow into the heat source apparatus side heat exchanger 13A. While passing the heat source apparatus side heat exchanger 13A, the refrigerant evaporates to become a gas refrigerant through the heat exchange with the air. Then, the refrigerant returns to the compressor 11A again through the four-way switching valve 12A and accumulator 14A to circulate by being discharged as described before. The same is true for the refrigerant flowing into the heat source apparatus 10B side. The above is a circulation path of the refrigerant at the time of the all cooling operation.
Here, descriptions are given provided that in the above-mentioned all cooling operation and all heating operation, all indoor units 20a, 20b, and 20c perform operation, however, for example, part of the indoor units may perform or stop operation. When part of the indoor units 20 stops and the load is small for the entire air conditioning apparatus, either the compressor 11A or 11B of the heat source apparatuses 10A and 10B may be stopped.
Descriptions will be omitted for the refrigerant flow in the cooling operation by the indoor units 20a and 20b because they are the same as the flow in the all cooling operation explained using
In the indoor unit 20c, the indoor unit side flow rate control device 22c adjusts the opening and regarding the refrigerant flowing from the first branched pipe 300c, pressure adjustment is performed for the refrigerant flowing in the indoor unit side heat exchanger 21c. Then, the high-pressure gas refrigerant is condensed into a liquid refrigerant while passing in the indoor unit side heat exchanger 21c to pass through the indoor unit side flow rate control device 22c. Thereby, the indoor air is heated through the heat exchange and heating operation is performed in the room. The liquid refrigerant passing the indoor unit side flow rate control device 22c turns into a low-pressure liquid refrigerant to flow into the association part 38 through the second branched pipe 400c and second relay check valve 40c. Thereafter, the refrigerant passes a branched part to the first flow rate control device 15 and through the second heat exchanger part 46 to merge with the refrigerant at a downstream that flows from the gas liquid separator 41 and passes the second flow rate control device 13. Then, the refrigerant flows into the indoor units 20a and 20b to turn into the refrigerant for the cooling operation.
As mentioned above, in the cooling-dominant operation, the heat source apparatus side heat exchanger 13A of the heat source apparatus 10A and the heat source apparatus side heat exchanger 13B of the heat source apparatus 10B become condensers. The refrigerant passing through the indoor unit 20 (here, the indoor unit 20c) in the heating operation is used for the refrigerant for the indoor unit 20 (here, the indoor units 20a and 20b) in the cooling operation. However, the loads in the indoor units 20a and 20b are small, so that when the refrigerant flowing in the indoor units 20a and 20b is suppressed, the opening of the first flow rate control device 15 is increased. Thus, the refrigerant passing through the indoor unit 20c to flow into the association part 38 can be made to pass through the second heat exchange part 46 and the first heat exchange part 47 and bypassed to flow into the first main pipe 100. Then, through the first main pipe 100, a gas-liquid two-phase refrigerant flows into the distributor 50.
Descriptions will be omitted for the refrigerant flow in the heating operation by the indoor units 20a and 20b because they are the same as the flow in the all heating operation explained using
In the heating-dominant operation, the refrigerant output from the indoor unit (here, the indoor units 20a and 20b) in the heating operation flows in the indoor unit (here, the indoor units 20c) in the cooling operation. Therefore, when the indoor unit in the cooling operation stops, the amount of the gas-liquid two-phase refrigerant increases flowing in the bypass piping 44. To the contrary, when the load increases in the indoor unit in the cooling operation, the amount of the gas-liquid two-phase refrigerant flowing in the bypass piping 44 decreases. Therefore, while the refrigerant amount remains the same necessary for the indoor unit 20 in the heating operation, the heat exchange processing capability changes of the indoor unit heat exchanger 21 (evaporator) in the indoor unit 20 in the cooling operation. Then, capacities of the compressors 11A and 11B of the heat source apparatuses 10A and 10B become the same.
A discharged refrigerant flow amount (mass flow mount) and sucked refrigerant flow amount (mass flow mount) from each compressor 10 is the same. Therefore, when the load of the indoor unit 20 in the cooling operation under the heating-dominant operation changes, a dryness (density) of the low-pressure side refrigerant changes to keep a constant mass flow, that is a gas-liquid two-phase refrigerant flowing into the first main pipe 100 by way of the second flow rate control device 45. So that, the statuses of the refrigerant entering the distributor 50 varies from a high dryness state to a low dryness state even if it is a gas-liquid two-phase refrigerant. In any condition, since compressors 11A and 11B continue to perform driving, the refrigerant needs to be branched in the distributor 50.
As shown in
Two outlets of the distributor 50 and first connection piping 500A and 500B are connected respectively. Here, descriptions will be given to the shape of the first connection piping 500A. The first connection piping 500A of the present embodiment has a U-shaped bending part 501A for at one end part. In the case of an actual connection of the first connection piping 500A, the bending part 501A is made to be a reverse U-shaped and the first connection piping 500A is connected with the bending part 501A being the upper side than the inlet position of the distributor 50. The first connection piping 500B has the bending part 501B as well. Regarding at least the first connection piping 500A, the U-shaped bending part 502A is provided at the other end as well. The bending part 502A is connected so that it is made to be a lower side than the connection part with the first manual opening and closing valve 16-1A. By defining the shape of the first connection piping 500A in advance, it is possible to specify the piping length, position, and attachment direction to the manual opening and closing valve 16-1A (compressor 11A) to fixedly dispose the distributor 50 at a specified position.
Here, in the air conditioning apparatus 1 capable of performing a cooling-heating mixed, operation like the present embodiment, the first main pipe 100 serves as returning piping in which the refrigerant always returns from the indoor unit 20 to the heat source apparatus 10 side including the cooling-dominant operation and heating-dominant operation. Therefore, the refrigerant amount in the distributor 50 significantly changes in an order such that all cooling operation>cooling-dominant operation>heating-dominant operation, for example. Here, in the all cooling operation, a low-pressure gas or a high dryness gas refrigerant flows in the first main pipe 100. Then, since a refrigerant density is small, there is a tendency that the refrigerant flow becomes faster. The larger the refrigerant flow amount and the longer the piping length, slower the performance due to a friction loss. Therefore, in order to lower a pressure loss at the maximum refrigerant flow amount, a piping diameter of the main pipe 100 is made large to lower the flow rate of the refrigerant. That allows an inlet diameter in the distributor 50 to be large to lower the flow rate, as well. Here, a droplet (refrigerant, refrigerator oil) contained in the refrigerant is significantly subjected to the gravity when a gas flow rate is lowered. Especially, when there is a bending part in the piping, no homogeneous mass distribution is available in a cross section inside the piping due to a centrifugal force.
A specified position assuming the above is predetermined in the relation with the heat source apparatus 10A. In the air conditioning apparatus 1 having a plurality of the heat source apparatuses 10 like the heat source apparatuses 10A and 10B, specified members (the first connection piping 500A, in the present embodiment) for fixedly disposing the distributor 50 are prepared. Using the specified members, the distributor 50 is fixedly disposed so that its mounting position including its orientation becomes always fixed against the heat source apparatus 10A independent of the installation location of the heat source apparatuses 10A and 10B.
Thereby, it is possible to distribute the refrigerant amount flowing from the distributor 50 to the heat source apparatus 10A side in accordance with a predetermined assumption. (That is, the refrigerant flowing in another heat source apparatus 10B side becomes stable.) Since distribution based on a predetermined assumption is possible, for example, in the heat source apparatuses 10A and 10B, even when a slight difference in the distribution should occur, a product specification can be made in response thereto at the product development stage. For example, it is possible to correspond in such a way that a difference is provided in the refrigerant flow amount of the compressors 11A and 11B to change a return ratio of the liquid refrigerant.
It is considered that in the air conditioning apparatus 1 capable of performing a cooling-heating mixed operation, for example, when performing the cooling-dominant and heating-dominant operations in what is called an intermediate stage such as spring and autumn, the refrigerant flow amount returning to the distributor 50 becomes small. Then, since in the indoor unit 20 in the cooling operation the load becomes small, the refrigerant does not completely evaporate and turns into a gas-liquid two-phase refrigerant to flow in the first main pipe 100. As mentioned the above, by fixedly disposing the distributor 50, for example, it is possible to uniformly distribute the liquid refrigerant, leading to a proper distribution effect of the refrigerant. Especially in the air conditioning apparatus 1 capable of performing a cooling-heating mixed operation, the cooling operation frequently occurs in the intermediate stage. As a result, problems related to liquid distribution in the distributor 50 easily to happen, however, the fixedly disposed distributor may contribute toward solving the problems.
In the present embodiment, compressors 11A and 11B are a capacity-variable inverter compressor. When at least either of them is a capacity-variable compressor 11, the refrigerant flow amount significantly varies among a plurality of compressors 11. Even in such a case, it is possible to determine a specified position for the distributor 50 by adopting measures for the difference in the refrigerant flow amount at the product development stage. Further, by fixedly disposing the distributor 50 at the specified position, variation conditions of the liquid refrigerant distribution in accordance with the change in the refrigerant flow amount in the both compressors 11 can be stabilized. For example, by changing the piping diameter of the first connection piping 500A and 500B after the distributor 50, the distribution amount can be varied. In addition, the shape (length, diameter, and number of bending) of the first connection piping 500A provided inside the heat source apparatus 10A can be different from that of the first connection piping 500B. Thus, assuming the distribution amount of the liquid along with the distributor 50 is facilitated.
In the above descriptions, all the indoor units 20A are made to perform the cooling or heating operation, however, in some cases, only part of the indoor units 20 perform operation, for example. In such a case, since the load of the indoor unit 20 side is often small, all the heat source apparatuses 10 need not to be driven (the compressor 11 is driven), and sometimes part of them can be stopped. Therefore, it is considered that the heat source apparatus 10A (compressor 11A) is in operation and the heat source apparatus 10B (compressor 11B) is stopped. Basically, in many cases the load in the indoor unit 10 is small, there is a strong possibility that the refrigerant flowing through the main pipe 100 into the distributor 50 is a gas-liquid two-phase refrigerant. As mentioned the above, the liquid (liquid refrigerant) becomes a stratified flow flowing along the internal face of the piping to be subjected to gravity and centrifugal forces.
Typically, since the compressor 11B is stopped and no pressure related suction is generated at the first connection piping 500B side, no gas refrigerant flows. Here, in the air conditioning apparatus 1 according to the present embodiment, the distributor 50 is fixedly disposed so that the inlet is located at the lower side of the outlet. Accordingly, the liquid refrigerant turns into a stratified flow to flow along the internal face of the piping from downward to upward. The liquid refrigerant is heavier than the gas refrigerant, it has momentum. Therefore, there is a possibility that even if no gas refrigerant flows, the liquid refrigerant may try to flow into the first connection piping 500B side.
As mentioned the above, the first connection piping 500B according to the present embodiment extends further upward from the distributor 50, as mentioned before, to have a bending part 501B. As a result, the liquid refrigerant that tried to flow in the first connection piping 500B side is subjected to gravity, and rapidly stalls, falls downward to return back to the distributor 50. Therefore, it is possible to prevent the refrigerant to be supplied with the indoor unit 20 side from not returning back to the compressor 11 by that no refrigerant flows in the first connection piping 500B side. In addition, the first connection piping 500A also has a bending part 501A, however, since a force related to suction of the compressor 11A is exerted, the liquid refrigerant flows into the first connection piping 500A.
That holds to a case in which not only the liquid refrigerant but also the refrigerator oil flowed out of the compressor 11 returns back through each refrigerant piping, indoor unit 20, and the like. Therefore, no refrigerator oil flows toward the first connection piping 500B of the heat source apparatus 10 side that is not in operation, so that the compressor 11A in operation no longer becomes an oil-depleted state.
In the first main pipe 100, the refrigerant always flows in the direction from the indoor unit 20 side to the heat source apparatus 10 side. Therefore, when the refrigerant flow amount is small, especially the refrigerator oil cannot reach the distributor 50 while being carried by the flow, so that it is feared that the refrigerant may be accumulated before the distributor 50. An internal flow in the main pipe 100 will not be reversed, that is no refrigerant flows from the heat source apparatuses 10A and 10B side to the indoor unit 20 side. As a result, there is a possibility that the accumulated oil may continue to stay by the time when the refrigerant flow amount becomes larger. As for a method to return the accumulated oil, there is a method such that by deliberately increasing the refrigerant flow amount, the refrigerator oil is pushed out to pass the distributor 50, for example. Another method is that the liquid refrigerant having a low viscosity is made to flow from the indoor unit 20 side intentionally, and by dissolving the refrigerator oil into the liquid refrigerant to lower the viscosity, it becomes easier for the refrigerant oil to advance in the distributor 50. In any case, the droplet has to be separated upon reaching the distributor 50. By fixedly disposing the distributor 50 at a specified position, its posture can be fixed according to a predetermined manner. It is possible to keep the refrigerant flow amount for returning the refrigerator oil and liquid refrigerant amount to be returned at a minimum amount as assumed. Therefore, a stable air conditioning is possible without excessively changing the refrigeration cycle operation.
A distribution merger 52 functions as a merger for merging the refrigerant like the merger 51 at the time of the all cooling operation and cooling-dominant operation when the heat source apparatus side heat exchanger 13 functions as a condenser. At the time of the all heating operation and heating-dominant operation when the heat source apparatus side heat exchanger 13A functions as an evaporator, the distribution merger 52 functions as a distributor for distributing the refrigerant like the distributor 50. Here, it is not limited in particular, although, since the distribution merger 52 functions as a distributor as well, its shape can be the same as that of the distributor 50 described in Embodiment 1. The distribution merger 52 can be provided in the heat source apparatus 10A like the distributor 50. Here, it is provided in the heat source apparatus 10A. Therefore, a third connection piping 800A is provided in the heat source apparatus 10A as well. Its shape is predetermined like the first connection piping 500A. Thereby, the installation position of the distribution merger 52 in the heat source apparatus 10A is a fixed position (provision). On the other hand, the third connection piping 800B is connected to the manual opening and closing valve 15B inside the heat source apparatus 10B again after going out the heat source apparatus 10A once in order to connect to the distribution merger 52 in the heat source apparatus 10A.
A main high-pressure gas pipe 900 is connected to a branched pipe 700 (the manual opening and closing valve 16-3) through the merger 51 and the second connection piping 600 and the discharged gas refrigerant flows therein. In the present embodiment, the merger 51 is installed outside the heat source apparatuses 10A and 10B.
Next, descriptions will be given to the all cooling operation based on
The high-pressure refrigerant flowing into the heat source apparatus side heat exchanger 13A is condensed through the heat exchange while passing the heat source apparatus side heat exchanger 13A and turns into a high-pressure liquid refrigerant to flow into the third connection piping 800A through the flow rate control valve 19A. On the other hand, in the heat source apparatus 10B, the refrigerant flows in the third connection piping 800B in accordance with a similar flow. The refrigerant passing the third connection piping 800A and third connection piping 800B merges in the distribution merger 52 to be branched into the indoor units 20a, 20b, and 20c by way of the second main pipe 200.
In the indoor units 20a, 20b, and 20c, the indoor unit side flow rate control devices 22a, 22b, and 22c adjust the pressure of the liquid refrigerant flowing from the second branched pipe 400a, 400b, and 400c by adjusting the opening, respectively. The opening adjustment of each indoor unit side flow rate control device 22 is performed based on a degree of superheat at a refrigerant outlet side of the indoor unit side heat exchanger 21. Through the opening adjustment by each indoor unit side flow rate control devices 22a, 22b, and 22c, the refrigerant turned into a low-pressure gas-liquid two-phase refrigerant or low-pressure liquid refrigerant flows into the indoor unit side heat exchangers 21a, 21b, and 21c, respectively. The low-pressure gas-liquid two-phase refrigerant or low-pressure liquid refrigerant evaporates through the heat exchange with the indoor air while passing the indoor unit side heat exchangers 21a, 21b, and 21c respectively to turn into a low-pressure gas refrigerant or gas-liquid two-phase refrigerant. Then, they flow into the first branched pipes 300a, 300b, and 300c, respectively. Then, it cools the indoor air through heat exchange to perform cooling operation in the room. At the time of the all cooling operation, all the first opening and closing valves are opened and all the second opening and closing valves 35 are closed in the first branched part 31. As a result, the low-pressure gas refrigerant or gas-liquid two-phase refrigerant (low-pressure refrigerant) flowing from the first branched pipes 300a, 300b, and 300c flows into the first main pipe 100 through the first opening and closing valves 34a, 34b, and 34c and the association part 32.
The distributor 50 divides the low-pressure refrigerant flowing in the main pipe 100 into the refrigerant flowing in the heat source apparatus 10A side and the refrigerant flowing in the heat source apparatus 10B side. The refrigerant flowing in the heat source apparatus 10A side circulates by flowing into the heat source apparatus 10A through the first connection piping 500A, passing the accumulator 14A of the heat source apparatus 10A, returning back to the compressor 11A, and being discharged as mentioned before. That makes a circulation path at the time of the cooling operation in a refrigerant main circuit. The refrigerant flowing into the heat source apparatus 10B flows into the heat source apparatus 10B through the first connection piping 500B to return back to the compressor 11B through the accumulator 14B of the heat source apparatus 10B in the same way.
Next, descriptions will be given to the all heating operation based on
In the heat source apparatus 10A, the compressor 11A compresses the sucked refrigerant to discharge a high-pressure gas refrigerant. The discharged refrigerant from the compressor 11A flows into the second connection piping 600A through the branched pipe 700A and electromagnetic opening and closing valve 18A. In the heat source apparatus 10B, there is a refrigerant flow into the second connection piping 600B. The refrigerants flowing in the second connection piping 600A and the second connection piping 600B are merged by the merger 51 to flow into the first branched part 31 by way of the main high-pressure gas pipe 900. In the all heating operation, all the first opening and closing valves 34 are dosed and all the second opening and closing valves 35 are opened in the first branched part 31. The refrigerant flowing into the first branched part 31 is branched into the indoor units 20a, 20b, and 20c through the association part 33, the second opening and dosing valves 35a, 35b, and 35c, and the first branched pipes 300a, 300b, and 300c.
In the indoor units 20a, 20b, and 20c, indoor unit side flow rate control devices 22a, 22b, and 22c perform opening control, and for the refrigerants flowing from the first branched pipes 300a, 300b, and 300c, respectively, pressure is adjusted when flowing in the indoor unit side heat exchanger 21. The high-pressure gas refrigerant is condensed through the heat exchange while passing the indoor unit side heat exchangers 21a, 21b, and 21c and turns into a high-pressure liquid refrigerant to pass indoor unit side flow rate control devices 22a, 22b, and 22c. Thereby, indoor air is heated by heat exchange and heating operation is performed in the room. The refrigerant passing the indoor unit side flow rate control devices 22a, 22b, and 22c turns into a low-pressure gas-liquid two-phase refrigerant or low-pressure liquid refrigerant to flow into the second main pipe 200 through the second branched pipes 400a, 400b, and 400c.
The distribution merger 52 divides the low-pressure refrigerant flowing in the second main pipe 200 into the refrigerant to flow in the heat source apparatus WA side and the refrigerant to flow in the heat source apparatus 10B side. The refrigerant flowing in the heat source apparatus 10A side flows into the heat source apparatus 10A through the third connection piping 800A. Then, the refrigerant circulates by passing the heat source apparatus side heat exchanger 13A, four-way switching valve 12A, accumulator 14A, returning back to the compressor 11A, and being discharged as mentioned the above. That is a circulation path at the time of the heating operation. Here, since the heat source apparatus side heat exchanger 13A functions as an evaporator in the all heating operation, the refrigerant gasifies through heat exchange. The refrigerant flows in the heat source apparatus 10B flows into the heat source apparatus 10B through the third connection piping 800B in the same way. Then, the refrigerant returns back to the compressor 11B by way of the heat source apparatus side heat exchanger 13B, four-way switching valve 12B, and accumulator 14B of the heat source apparatus 10B of the heat source apparatus 10B.
Here, in the present embodiment, descriptions are given provided that in the all cooling operation and all heating operation described above, all indoor units A, B, and C are in operation, however, some indoor units may be in operation while others are stopped. For example, when some indoor units are stopped and the load is small for the entire air conditioning apparatus, either of the compressor 11A or 11B of the heat source apparatus 10A or 10B may be stopped.
On the other hand, in the cooling-dominant operation, since unlike the all cooling operation, the gas refrigerant is supplied with the indoor unit (here, the indoor unit C) performing the heating operation, the electromagnetic opening and closing valve 18A is opened in the heat source apparatuses 10A. Thereby, part of the high-pressure gas refrigerant flows into the first branched part 31 through the branched pipe 700, second connection piping 600A, and merger 51. Here, when the load based on the heating operation is small, the electromagnetic opening and closing valve 18B of the heat source apparatuses 10B may be closed. On the other hand, when the load of the indoor unit 20 in the heating operation is large, the electromagnetic opening and closing valve 18B may be opened in the heat source apparatuses 10B as well and the high-pressure gas refrigerant may be supplied from the heat source apparatuses 10B side.
Descriptions will be omitted for the refrigerant flow in the indoor units 20a and 20b in the cooling operation because it is the same as those in the all cooling operation explained using
In the indoor unit C, the indoor unit side flow rate control device 22c performs the opening adjustment and regarding the refrigerant flowing from the first branched pipe 300c, the pressure of the refrigerant is adjusted that flows in the indoor unit side heat exchanger 21c. Then, the high-pressure refrigerant is condensed and turns into a liquid refrigerant through heat exchange while passing the indoor unit side heat exchanger 21c to pass the indoor unit side flow rate control device 22c. Thereby, the indoor air is heated through heat exchange and the heating operation is performed in the room. The refrigerant passing the indoor unit side flow rate control device 22c turns into a little decompressed low-pressure refrigerant to pass the second branched pipe 400c. Then, the refrigerant merges with the refrigerant flowing in the second main pipe 200 and flows into the indoor units 20a and 20b to turn into a refrigerant for the cooling operation. As for the flow and operation of each means thereafter of the refrigerant for the cooling operation, descriptions will be omitted because they are the same as the flow of the all cooling operation explained using
As for the refrigerant flow in the heating operation of the indoor units 20b and 20c, descriptions will be omitted because it is the same as the flow of the all heating operation. Here, the indoor unit 20a performs the cooling operation, and since the refrigerant flow is different from the indoor units 20b and 20c in the heating operation, descriptions will be given focusing the flow. In the indoor units B and C, the refrigerant is condensed into a liquid refrigerant through the heat exchange while passing the indoor unit side heat exchangers 21a and 21b to flow into the second branched pipes 400b and 400c through the indoor unit side flow rate control devices 22a and 22b.
Most of the refrigerant flowing in the second branched pipes 400b and 400c passes through the second main pipe 200 to flow into the heat source apparatuses 10A and 10B through the distribution merger 52. Part of the refrigerant flows into the indoor, unit A by way of the second branched pipe 400a to turn into a refrigerant for the cooling operation. Through the heat exchange of the indoor unit side heat exchanger 21a of the indoor unit A, the gasified gas refrigerant or gas-liquid two-phase refrigerant flows into the first main pipe 100 through the first branched pipe 300a and opening and closing valve 8a. The distributor 50 distributes a low-pressure refrigerant flowing in the first main pipe 100. Each divided refrigerant by the distribution flows into the heat source apparatus 10 to return back to the compressor 11 through the accumulator 14 of the heat source apparatuses 10.
Here, the distributor 50 and a joining branch part 25 are provided to connect to the first connection piping 500A and third connection piping 800 A whose shapes are provided in advance. Therefore, the same effect as Embodiment 1 can be obtained.
In Embodiment 1, the distributor 50 is fixedly disposed inside the heat source apparatus 10A by the first connection piping 500A, however, it is not limited thereto. For example, the distributor 50 may be fixedly disposed at the heat source apparatus 10B side. It goes without saying that when only the location where the distributor 50 is fixedly disposed is specified, the same effect can be observed by fixing it in the heat source apparatus 10A through a fixing sheet metal 17A and the like.
The distributor 50 can be fixedly built-in inside the heat source apparatus 10A in advance to be shipped into the market. Thereby; there is an advantage that an installation time can be reduced on the site. On the other hand, when not built-in, it is necessary to install it on the site. However, no distributor is required when a device is composed of only one heat source apparatus 10A, the heat source apparatus can be shared between a device having a plurality of heat source apparatuses and a device having a single heat source apparatus, so that an installation-flexible product can be obtained.
In the embodiment above, descriptions are given to the air conditioning apparatus 1 in which a heat source apparatus 10A and heat source apparatus 10B are provided, however, the number of the heat source apparatus is not limited to two. It goes without saying that in a device configuration having three or more heat source apparatuses 10, by fixing the distributor 50 at a predetermined location in part of the heat source apparatuses 10, an effect is the same on a refrigerant distribution to the heat source apparatus.
Like the embodiment above, the present invention has a main pipe in which the refrigerant flows in one direction from the indoor unit 20 to the heat source apparatus 10 side, so that it is effective for a device where the refrigerant flow amount changes, however, it is not limited thereto. For example, the present invention is applicable to other refrigeration cycle such as a refrigeration device.
| Filing Document | Filing Date | Country | Kind | 371c Date |
|---|---|---|---|---|
| PCT/JP2007/068606 | 9/26/2007 | WO | 00 | 3/3/2010 |
| Publishing Document | Publishing Date | Country | Kind |
|---|---|---|---|
| WO2009/040889 | 4/2/2009 | WO | A |
| Number | Name | Date | Kind |
|---|---|---|---|
| 5156014 | Nakamura et al. | Oct 1992 | A |
| 5279131 | Urushihata et al. | Jan 1994 | A |
| Number | Date | Country |
|---|---|---|
| 7438191 | Oct 1991 | AU |
| 2 248 494 | Apr 1992 | GB |
| 0 453 271 | Oct 1991 | JP |
| 4-093561 | Mar 1992 | JP |
| 7-052045 | Jun 1995 | JP |
| 9-101070 | Apr 1997 | JP |
| Entry |
|---|
| Japanese Office Action (Notification of Reasons for Refusal) dated Mar. 21, 2012, issued in the corresponding Japanese Patent Application No. 2009-534080, and a English Translation thereof. (3 pages). |
| International Search Report of PCT/JP2007/068606 dated Jan. 8, 2008. |
| Office Action from Chinese Patent Office issued in corresponding Chinese Patent Application No. 200780100841.8 dated Mar. 30, 2011. |
| Office Action (Decision of Rejection) issued by the Japanese Patent Office on Dec. 25, 2012 in corresponding Japanese Patent Application No. 2009-534080, and an English translation thereof. |
| Number | Date | Country | |
|---|---|---|---|
| 20100199695 A1 | Aug 2010 | US |
