AIR CONDITIONING APPARATUS

CROSS-REFERENCE TO RELATED APPLICATIONS

The present application claims the benefit of priority of Japanese Patent Applications No. 2011-216556 filed on Sep. 30, 2011, No. 2012-079427 filed on Mar. 30, 2012, and No. 2012-162230 filed on Jul. 23, 2012, which is incorporated herein by reference.

BACKGROUND

1. Field of the Invention

The invention relates to an air conditioning apparatus including multiple outdoor units and multiple indoor units connected by multiple refrigerant pipes and, more specifically, it relates to such air conditioning apparatus capable of preventing a shortage of refrigerant unit oil within a compressor.

2. Related Art

Conventionally, there is proposed an air conditioning apparatus in which multiple indoor units are parallel connected to at least one outdoor unit by multiple refrigerant pipes and the respective indoor units can execute a cooling operation and a heating operation. For example, the patent reference 1 discloses an air conditioning apparatus of a so called cooling and heating free operation type in which two indoor units are parallel connected to an outdoor unit including two outdoor heat exchangers by a high pressure gas pipe, a low pressure gas pipe and a liquid pipe, and the two indoor units can independently execute a heating operation and a cooling operation selectively.

In the above air conditioning apparatus, the number of outdoor heat exchangers equipped in the outdoor unit is selected according to the operation capacity required of the two indoor units. When the operation capacity required of the two indoor units is low, one of the outdoor heat exchangers is used and, when the required capacity is high, both heat exchangers are used.

When the above air conditioning apparatus is installed in a cold district, or when the open-air temperature is low (for example, it is 0° C. or lower), for example, in the early morning or in the middle of the night in winter, there is a fear that, while the air conditioning apparatus is not in operation, a state where a refrigerant is dissolved in the refrigerating machine oil of a compressor, namely, so-called refrigerant dissolution can occur within a compressor provided in the outdoor unit.

When, in the refrigerant dissolution state, the operation of the air conditioning apparatus is started and the compressor is actuated, the refrigerant dissolved in the refrigerating machine oil evaporates to a gas refrigerant. When this gas refrigerant is discharged to the outside of the compressor, it catches and takes out the refrigerating machine oil to the outside of the compressor, thereby causing a shortage of the refrigerating machine oil within the compressor. This raises a fear that the poor lubrication of the compressor can occur.

Therefore, in an ordinary air conditioning apparatus, the rotation number of the compressor in its start time is controlled to a given rotation number previously determined for warming the compressor and, while maintaining this rotation number, the compressor is driven on for a given period of time to thereby eliminate the refrigerant dissolution within the compressor.

That is, by executing the above start control, the refrigerant dissolution, which had occurred in the start time of the compressor before, is eliminated to restrict the amount of the refrigerating machine oil to be taken out to the outside of the compressor by the gas refrigerant, thereby preventing the poor lubrication of the compressor.

SUMMARY

However, in the air conditioning apparatus executing the above start control, since, in the start control execution, the compressor is driven on while maintaining its rotation number at the given number, the compressor internal pressure increases. The increased compressor internal pressure can cause the refrigerant dissolution.

One or more embodiments of the present invention aims at solving the above problem. Thus, it is an object of the invention to provide an air conditioning apparatus which, in its start time, even when a compressor is driven on at a given rotation number, can prevent the increased internal pressure of the compressor.

In attaining the above object, according to one embodiments of the present invention, there is provided an air conditioning apparatus, comprising: at least one outdoor unit including at least one compressor, at least two outdoor heat exchangers, flow passage switching devices connected to one end of each of the outdoor heat exchangers for switching the connection of the outdoor heat exchangers to the refrigerant discharge opening or refrigerant suction opening of the one or more compressors, outdoor expansion valves each connected to the other end of each of the outdoor heat exchangers for adjusting the refrigerant flow amount of the outdoor heat exchangers, and controller for executing the switching control of the flow passage switching devices and the valve opening rate control of the outdoor expansion valves; and, an indoor unit to be connected to the outdoor unit by at least two refrigerant pipes, wherein when a first given condition holds in the start operation of the outdoor unit, the controller executes first start control, in the first start control, the controller controls the flow passage switching devices corresponding to the one or more outdoor heat exchangers to allow it or them to function as an evaporator or evaporators, controls the flow passage switching devices corresponding to at least one of the other outdoor heat exchangers than one functioning as an evaporator to allow it or them to function as a condenser or condensers, and drives the one or more compressors at a predetermined rotation number.

Also, the controller, when a second given condition holds during execution of the first start control, the controller executes second start control following the first start control, in the second start control, the controller controls the flow passage switching devices corresponding to the outdoor heat exchangers to allow all of the outdoor heat exchangers used to function as condensers or evaporators, and continuously drives the one or more compressors at the same rotation number as in the first start control.

In attaining the above object, according to another embodiments of the present invention, there is provided an air conditioning apparatus, comprising: at least one outdoor unit including at least one compressor, at least two outdoor heat exchangers, flow passage switching devices connected to one end of each of the outdoor heat exchangers for switching the connection of the outdoor heat exchangers to the refrigerant discharge opening or refrigerant suction opening of the one or more compressors, outdoor expansion valves each connected to the other end of each of the outdoor heat exchangers for adjusting the refrigerant flow amount of the outdoor heat exchangers, open-air temperature detecting device for detecting open-air temperatures, and controller for executing the switching control of the flow passage switching devices and the valve opening rate control of the outdoor expansion valves; and, an indoor unit to be connected to the outdoor unit by at least two refrigerant pipes, wherein when a first given condition holds in the start operation of the outdoor unit, the controller executes start control including first start control, second start control and third start control, in the first start control, the controller controls the flow passage switching devices corresponding to the one or more outdoor heat exchangers to allow it or them to function as an evaporator or evaporators, controls the flow passage switching devices corresponding to at least one of the other outdoor heat exchangers than one functioning as an evaporator to allow it or them to function as a condenser or condensers, and drives the one or more compressors at a predetermined rotation number, in the second start control executed following the first start control, the controller drives the one or more compressors at a rotation number predetermined according to the open-air temperature detected by the open-air temperature detecting device reduced from the predetermined rotation number in the first start control, and in the third start control executed following the second start control, the controller controls the flow passage switching devices corresponding to the outdoor heat exchangers to allow all of the outdoor heat exchangers used to function as condensers or evaporators, and drives the one or more compressors at the rotation number returned to the same rotation number set in the first start control.

In attaining the above object, according to another embodiments of the present invention, there is provided an air conditioning apparatus, comprising: at least one outdoor unit including at least one compressor, at least two outdoor heat exchangers, flow passage switching devices connected to one end of each of the outdoor heat exchangers for switching the connection of the outdoor heat exchangers to the refrigerant discharge opening or refrigerant suction opening of the compressor, outdoor expansion valves each connected to the other end of each of the outdoor heat exchangers for adjusting the refrigerant flow amount of the outdoor heat exchangers, open-air temperature detecting device for detecting open-air temperatures, and controller for executing the switching control of the flow passage switching devices and the valve opening rate control of the outdoor expansion valves; and, an indoor unit to be connected to the outdoor unit by at least two refrigerant pipes, wherein the controller, when a first given condition holds in the start operation of the outdoor unit, executes start control including first start control, second start control and third start control, in the first start control, the controller controls the flow passage switching devices corresponding to the one or more outdoor heat exchangers to allow it or them to function as an evaporator or evaporators, controls the flow passage switching devices corresponding to at least one of the other outdoor heat exchangers than one functioning as an evaporator to allow it or them to function as a condenser or condensers, and drives the one or more compressors at a predetermined rotation number, in the second start control executed following the first start control, the controller drives the one or more compressors at a predetermined rotation number of the one or more compressors reduced from a given number of rotation in the first start control down to a predetermined rotation number according to the open-air temperature detected the one or more compressors at a rotation number predetermined according to the open-air temperature detected by the open-air temperature detecting device reduced from the predetermined rotation number in the first start control, and in the third start control executed following the second start control, the controller controls the flow passage switching devices corresponding to the outdoor heat exchangers to allow all of the outdoor heat exchangers used to function as condensers or evaporators, and to drive the one or more compressors at a rotation number maintained at the rotation number set in the second start control.

BRIEF DESCRIPTION OF DRAWINGS

FIG. 1 is a refrigerant circuit of an air conditioning apparatus according to an embodiment of the invention, explaining the flow of a refrigerant when executing a heating operation;

FIGS. 2A and 2B are schematic views of an outdoor unit in the embodiment of the invention;

FIG. 3 is a refrigerant circuit in the embodiment of the invention, showing the flow of a refrigerant when executing first start control;

FIG. 4 is a refrigerant circuit in the embodiment of the invention, showing the flow of a refrigerant when executing second start control;

FIG. 5 is a timing chart in the embodiment of the invention, showing the operations of the respective composing elements when executing the first and second start control;

FIG. 6 is a flow chart in the embodiment of the invention, showing processings to be executed by controller;

FIG. 7 is a timing chart in a second embodiment of the invention, showing the operations of the respective composing elements when executing first, second and third start control;

FIG. 8 is a rotation number table for use in execution of the second start control in the second embodiment;

FIG. 9 is a flow chart of processings to be executed by controller in the second embodiment;

FIG. 10 is a timing chart in the third embodiment of the invention, showing the operations of the respective composing elements when executing the first, second, and third start control; and

FIG. 11 is a flow chart of processings to be executed by controller in the third embodiment.

DETAILED DESCRIPTION

Hereinafter, description will be given below specifically of the mode for carrying out the invention with reference to the accompanying drawings. As an embodiment of this invention, there is taken an air conditioning apparatus of a so-called heating and cooling free operation type in which five indoor units are parallel connected to two outdoor units and the indoor units can independently execute a cooling operation and a heating operation selectively. Here, the invention is not limited to the following embodiments but can be modified variously without departing from the subject matter thereof.

Embodiment 1

As shown in FIG. 1, an air conditioning apparatus 1 of this embodiment includes two outdoor units 2a, 2b, five indoor units 8a-8e, five branch units 6a-6e, and turnout devices 70, 71, 72. The outdoor units 2a, 2b, five indoor units 8a-8e, five branch units 6a-6e, and turnout devices 70, 71, 72 are connected to their associated ones by a high pressure gas pipe 30, high pressure gas branch pipes 30a, 30b, a low pressure gas pipe 31, low pressure gas branch pipes 31a, 31b, a liquid pipe 32, and liquid branch pipes 32a, 32b, thereby constituting the refrigerant circuit of the air conditioning apparatus 1.

This air conditioning apparatus 1, according to the opened or closed states of various valves provided in the outdoor units 2a, 2b and branch units 6a-6e, can execute various operations such as a heating operation (all indoor units execute a heating operation), a heating-based operation (when the whole capacity required of the indoor units executing a heating operation exceeds the whole capacity required of the indoor units executing a cooling operation), a cooling operation (all indoor units execute a cooling operation), and a cooling-based operation (when the whole capacity required of the indoor units executing a cooling operation exceeds the whole capacity required of the indoor units executing a heating operation). In FIG. 1, description will be given of an example where, of these operations, the heating operation is executed.

FIG. 1 is a refrigerant circuit when all indoor units 8a-8e are executing the heating operation, and FIGS. 2A and 2B are schematic views of the outdoor units 2a, 2b. Firstly, the outdoors 2a, 2b will be described. Here, since the outdoors 2a, 2b are all the same in structure, in the following description, only the structure of the outdoor unit 2a will be described, while the specific description of the outdoor unit 2b is omitted.

As shown in FIGS. 1, 2A, and 2B, the outdoor unit 2a includes an electrical equipment box 100a made of a thin plate for storing therein various substrates such as a control substrate and a power source substrate, a compressor 21a, a first three-way valve 22a and a second three-way valve 23a serving as flow passage switching devices, a first outdoor heat exchanger 24a, a second outdoor heat exchanger 25a, an outdoor fan 26a, a fan motor 29a having an output shaft connected to the outdoor fan 26a for rotating the outdoor fan 26a, an accumulator 27a, an oil separator 28a, a first outdoor expansion valve 40a connected to the first outdoor heat exchanger 24a, a second outdoor expansion valve 41a connected to the second outdoor heat exchanger 25a, a hot gas bypass pipe 36a, a first electromagnetic valve 42a provided on the hot gas bypass pipe 36a, an oil return pipe 37a, a second electromagnetic valve 43a provided on the oil return pipe 37a, and closing valves 44a-46a. These elements constituting the outdoor unit 2a are disposed within the box body of the outdoor unit 2a constituted of a top plate 3a, a bottom plate 4a, a front panel 5a, a front support 7a, a left support 9aa, a right support 9ab and a fan guard 11a.

As shown in FIGS. 2A and 2B, the front panel 5a is a steel plate bent formed substantially in L-like shape when viewed from the upper surface of the outdoor unit 2a, while it is disposed to cover most of the box body front surface of the outdoor unit 2a and part of the front side of the left side surface thereof. The front support 7a, as shown in FIG. 2B, is made of a steel plate including a grille 7aa for sucking the open-air into the outdoor unit 2a, while the two end portions thereof are bent at a given angle (obtuse angle) and the respective bent portions are disposed to cover part of the front surface of the box body of the outdoor unit 2a and part of the front side of the right side surface thereof. The left support 9aa and right support 9ab are substantially the same in shape and are respectively a steel plate worked to have a substantially L-like shape. The left support 9aa is disposed at the back surface side left corner portion of the bottom plate 4a, while the right support 9ab is disposed at the back surface side right corner portion thereof.

The box body left side surface side of the outdoor unit 2a is opened up between the side end of the front panel 5a and left support 9aa to form a suction opening 13aa for sucking the open-air into the outdoor unit 2a, while a lattice-shaped protect member 12aa is disposed in the suction opening 13aa. Also, the box body back surface side of the outdoor unit 2a is opened up between the left support 9aa and right support 9ab to form a suction opening 13ab for sucking the open-air into the outdoor unit 2a, while a lattice-shaped protect member 12ab is disposed in the suction opening 13ab. The box body right side surface side of the outdoor unit 2a is opened up between the front support 7a and right support 9ab to form a suction opening 13ac for sucking the open-air into the outdoor unit 2a, while a lattice-shaped protect member 12ac is disposed in the suction opening 13ac. Here, the portions of the respective suction openings 13aa-13ac corresponding to the suction openings of the first and second outdoor heat exchangers 24a and 25a are exposed.

As shown in FIG. 2A, the top plate 3a is a substantially square-shaped steel plate, while its peripheral edge portion provides a flange bent downward substantially at right angles. The top plate 3a can be assembled by screws to the respective upper ends of the front panel 5a, front support 7a, left support 9aa and right support 9ab. The top plate 3a includes, at a position corresponding to the outdoor fan 26a disposed on the upper portion of the box body, a discharge opening 11a opened circularly and having its peripheral portion bent upward substantially at right angles for discharging the open-air sucked into the outdoor unit 2a to the outside by the outdoor fan 26a. On the upper end of the discharge opening 11a, there is provided a fan guard 14 so as to cover the upper end of the discharge opening 11a. Here, the fan motor 29a is fixed to the upper end of the first heat exchanger 24a by a fixing metal member 17a.

The bottom plate 4a is a substantially square-shaped steel plate, while its peripheral portion provides a flange bent upward substantially at right angles. As shown in FIG. 2A, the bottom plate 4a can be assembled by screws to the respective lower ends of the front panel 5a, front support 7a, left support 9aa and right support 9ab. Here, the bottom plate 4a includes, in the lower surface thereof, leg portions 15a extending in the right and left directions of the outdoor unit 2a for installing the outdoor unit 2a on the ground, on the roof floor of a building or the like.

The compressor 21a is a capacity variable compressor the operating capacity of which can be varied when it is driven by a motor (not shown) with its rotation number controllable by an inverter and, as shown in FIG. 2A, it is fixed to the bottom plate 4a. Also, as shown in FIG. 1, the discharge side of the compressor 21a is connected to the inflow side of the oil separator 28a by a refrigerant pipe, while the flow-out side of the oil separator 28a is connected to the closing valve 44a by an outdoor unit high pressure gas pipe 33a. The suction side of the compressor 21a is connected to the flow-out side of the accumulator 27a by a refrigerant pipe, while the inflow side of the accumulator 27a is connected to the closing valve 45a by an outdoor unit low pressure gas pipe 34a.

The first and second three-way valves 22a and 23a are valves for switching the flow directions of the refrigerant. The first three-way valves 22a has three ports a, b, c, while the second three-way valves 23a has three ports d, e, f. In the first three-way valve 22a, a refrigerant pipe connected to the port a is connected to the outdoor unit high pressure gas pipe 33a at a connecting point A. The port b and first outdoor heat exchanger 24a are connected together by a refrigerant pipe, while a refrigerant pipe connected to the port c is connected to the outdoor unit low pressure gas pipe 34a at a connecting point D.

In the second three-way valve 23a, a refrigerant pipe connected to the port d is connected at the connecting point A to the outdoor high pressure gas pipe 33a and the refrigerant pipe connected to the port a of the first three-way valve 22a. The port e and second outdoor heat exchanger 25a are connected together by a refrigerant pipe, while a refrigerant pipe connected to the port f is connected at a connecting point C to a refrigerant pipe connected to the port c of the first three-way valve 22a.

As shown in FIG. 2B, the first and second outdoor heat exchangers 24a and 25a are each formed to have a substantially U-like shape when viewed from their upper surfaces, while the surfaces thereof are respectively disposed opposed to the suction openings 13aa-13ac formed in the outdoor unit 2a. The right side end portions of the first and second outdoor heat exchangers 24a and 25a are bent along the grille 7aa side surface of the front support 7a. As shown in FIG. 2A, the second outdoor heat exchanger 25a is fixed to the bottom plate 4a and the lower end of the first outdoor heat exchangers 24a is fixed through a fixing metal member 16a to the upper end of the second outdoor heat exchanger 25a, whereby the first and second outdoor heat exchangers 24a and 25a are disposed vertically.

The first outdoor heat exchanger 24a includes a large number of fins 24aa made of aluminum material and multiple steel pipes 24ab for allowing a refrigerant to flow therein. Also, the second outdoor heat exchanger 25a, similarly to the first outdoor heat exchangers 24a, includes a large number of fins 25aa made of aluminum material and multiple steel pipes 25ab made of copper material for allowing a refrigerant to flow therein.

As shown in FIG. 1, one end of the first outdoor heat exchanger 24a, as described above, is connected to the port b of the first three-way valve 22a, with the other end connected through a refrigerant pipe to one port of the first outdoor expansion valve 40a. Here, the other port of the first outdoor expansion valve 40a is connected to the closing valve 46a by an outdoor unit liquid pipe 35a. And, one end of the second outdoor heat exchanger 25a, as described above, is connected to the port e of the second three-way valve 23a through a refrigerant pipe, with the other end connected through a refrigerant pipe to one port of the second outdoor expansion valve 41a. Here, the other port of the second outdoor expansion valve 41a is connected to the connecting point B of the outdoor unit liquid pipe 35a by a refrigerant pipe.

The inflow side of the accumulator 27a is connected to an outdoor unit low pressure gas pipe 34a, with the outflow side connected to the suction side of the compressor 21a by a refrigerant pipe. The accumulator 27a, on receiving a refrigerant, divides it to a gas refrigerant and a liquid refrigerant, and allows the compressor 21a to suck only the gas refrigerant therein.

The inflow side of the oil separator 28a is connected to the discharge side of the compressor 21a by a refrigerant pipe, with the outflow outside connected to the outdoor unit high pressure gas pipe 33a. In the oil separator 28a, the refrigerating machine oil of the compressor 21a contained in the refrigerant discharged from the compressor 21a is separated from the refrigerant. Here, the separated refrigerating machine oil is sucked into the compressor 21a through an oil return pipe 37a (to be described later).

One end of the hot gas bypass pipe 36a is connected to the outdoor unit high pressure gas pipe 33a at the connecting point E, with the other end connected to the outdoor unit low pressure gas pipe 34a at the connecting point F. The hot gas bypass pipe 36a includes the first electromagnetic valve 42a and, by opening or closing the first electromagnetic valve 42a, the hot gas bypass pipe 36a can be switched between a refrigerant flow state and a refrigerant non-flow state.

One end of the oil return pipe 37a is connected to the oil return port of the oil separator 28a, with the other end connected at the connecting point G to a refrigerant pipe connecting the suction side of the compressor 21a and the outflow side of the accumulator 27a. The oil return pipe 37a includes a second electromagnetic valve 43a and, by opening or closing the second electromagnetic valve 43a, the oil return pipe 37a can be switched between a refrigerant flow state and a refrigerant non-flow state.

Besides the above composing elements, the outdoor unit 2a includes various sensors. As shown in FIG. 1, the refrigerant pipe connecting the discharge side of the compressor 21a and the oil separator 28a includes thereon a high pressure sensor 50a for detecting the pressure of a refrigerant discharged from the compressor 21a and a discharge temperature sensor 53a for detecting the temperature of a refrigerant discharged from the compressor 21a. And, between the connecting point F of the outdoor unit low pressure gas pipe 34a and the inflow side of the accumulator 27a, there are interposed a low pressure sensor 51a for detecting the pressure of a refrigerant sucked into the compressor 21a, and a suction temperature sensor 54a for detecting the temperature of a refrigerant sucked into the compressor 21a. Also, between the connecting point B of the outdoor unit liquid pipe 32a and closing valve 46a, there are interposed an intermediate pressure sensor 52a for detecting the pressure of a refrigerant flowing in the outdoor unit liquid pipe 35a and a refrigerant temperature sensor 55a for detecting the temperature of a refrigerant flowing in the outdoor unit liquid pipe 35a.

The refrigerant pipe connecting the port b of the first three-way valve 22a and first outdoor heat exchanger 24a includes a first heat exchanger temperature sensor 56a for detecting the temperature of a refrigerant flowing out from or flowing into the first outdoor heat exchanger 24a. And, the refrigerant pipe connecting the port e of the second three-way valve 23a and second outdoor heat exchanger 25a includes a second heat exchanger temperature sensor 57a for detecting the temperature of a refrigerant flowing out from or flowing into the second outdoor heat exchanger 25a. Also, the outdoor unit 2a, in the vicinity of any one of the suction openings 13aa-13ac, includes an open-air temperature sensor 58a for detecting the temperature of the open-air flowing into the outdoor unit 2a, that is, the open-air temperature.

The outdoor unit 2a includes a controller 100a. The controller 100a is mounted on a control substrate (not shown) stored in the electric equipment box 10a and includes a CPU 110a, a memory portion 120a and a communication portion 130a. CPU 110a receives detection signals from the above-mentioned sensors of the outdoor unit 2a and control signals output from the indoor units 8a-8e through the communication portion 130a. CPU 110a, according to the received detection signals and control signals, carries out various kinds of control including the drive control of the compressor 21a, the switching control of the first and second three-way valves 22a and 23a, the rotation control of the fan motor 29a, and the valve opening rate control of the first and second outdoor expansion valves 40a and 41a.

The memory portion 120a is constituted of a ROM and a RAM and stores therein detection values corresponding to the control programs of the outdoor unit 2a and the detected signals from the sensors. The communication portion 130a is an interface for communication between the outdoor unit 2a and indoor units 8a-8e. Here, the electric equipment box 10a for storing the controller 100a therein, as shown in FIG. 2A, is disposed on the box body front surface side upper portion (substantially flush with the first outdoor heat exchanger 24a) of the outdoor unit 2a.

The outdoor unit 2b is the same in structure as the outdoor unit 2a and thus the final numbers of the reference numerals of the composing elements (devices and members) of the outdoor unit 2a are changed from a to b to thereby represent the composing elements of the outdoor unit 2b corresponding to those of the outdoor unit 2a. However, the connecting points among the first three-way valve, second three-way valve and refrigerant pipes are given different signs between the outdoor units 2a and 2b. Specifically, those of the first three-way valve 22b of the outdoor unit 2b corresponding to the ports a, b, c of the first three-way valve 22a of the outdoor unit 2a are designated ports by g, h, j respectively, while those of the second three-way valve 23b of the outdoor unit 2b corresponding to the ports d, e, f of the second three-way valve 23a of the outdoor unit 2a are designated ports k, m, n. Also, those of the outdoor units 2b corresponding to the connecting points A, B, C, D, E, F, G of the outdoor unit 2a are designated connecting points H, J, K, M, N, P, Q.

As shown in FIG. 1, in the refrigerant circuit during the heating operation, the three-way valves are switched such that the two outdoor heat exchangers provided on the outdoor units 2a, 2b can function as evaporators. Specifically, in the outdoor unit 2a, the first three-way valve 22a is switched to allow communication between the ports b and c, and the second three-way valve 23a is switched to allow communication between the ports e and f. Also, in the outdoor unit 2b, the first three-way valve 22b is switched to allow communication between the ports h and j, and the second three-way valve 23b is switched to allow communication between the ports m and n. Here, in FIG. 1, the relationship between the ports of the three-way valves in communication is shown by a solid line, whereas the relationship between the ports of the three-way valves not in communication is shown by a broken line (this applies similarly in the following refrigerant circuit diagrams (FIGS. 3 and 4)).

The five indoor units 8a-8e include indoor heat exchangers 81a-81e, indoor expansion valves 82a-82e and indoor fans 83a-83e. The indoor units 8a-8e are all the same in structure. Therefore, in the following description, only the structure of the indoor unit 8a will be described and thus the description of the remaining indoor units 8b-8e will be omitted.

One end of the indoor heat exchanger 81a is connected to one port of the indoor expansion valve 82a by a refrigerant pipe, with the other end connected to the branch unit 6a (to be discussed later) by a refrigerant pipe. The indoor heat exchanger 81a, in the cooling operation of the indoor unit 8a, functions as an evaporator and, in the heating operation, functions as a condenser.

One port of the indoor expansion valve 82a, as described above, is connected to the indoor heat exchanger 81a, with the other port connected to the liquid pipe 32. When the indoor heat exchanger 81a functions as an evaporator, the valve opening rate of the indoor expansion valve 82a is adjusted according to a cooling capacity required and, when the indoor heat exchanger 81a functions as a condenser, the valve opening rate is adjusted according to a heating capacity required.

The indoor fan 83a, as it is rotated by a fan motor (not shown), sucks the indoor air into the indoor unit 8a, exchanges heat between the indoor air and refrigerant in the indoor heat exchanger 81a, and then supplies the heat exchanged air into a room.

Besides the above composing elements, the indoor unit 8a includes various sensors. A refrigerant pipe on the indoor expansion valve 82a side of the indoor heat exchanger 81a includes a refrigerant temperature sensor 84a for detecting the temperature of the refrigerant, and a refrigerant pipe on the branch unit 6a side of the indoor heat exchanger 81a includes a refrigerant temperature sensor 85a for detecting the temperature of the refrigerant. Near the indoor air suction port (not shown) of the indoor unit 8a, there is provided an indoor air temperature sensor 86a for detecting the temperature of the indoor air flowing into the indoor unit 8a, that is, the indoor temperature.

Here, the indoor units 8b-8e are the same in structure as the indoor unit 8a. Thus, the numbers of the reference numerals given to the composing elements (devices and members) of the indoor unit 8a is changed from a to b, c, d and e to thereby designate the composing elements of the indoor units 8b-8e corresponding to those of the indoor unit 8a.

The air conditioning apparatus 1 includes five branch units 6a-6e corresponding to the five indoor units 8a-8e. The branch units 6a-6e include electromagnetic valves 61a-61e, electromagnetic valves 62a-62e, first branch pipes 63a-63e, and second branch pipes 64a-64e. Here, the branch units 6a-6e are all the same in structure. Therefore, in the following description, only the structure of the branch unit 6a will be described, while omitting the description of other branch units 6b-6e.

One end of the first branch pipe 63a is connected to the high pressure gas pipe 30, while one end of the second branch pipe 64a is connected to the low pressure gas pipe 31. The other end of the first branch pipe 63a is connected to the other end of the second branch pipe 64a, while this connecting portion is connected to the indoor heat exchanger 81a by a refrigerant pipe. The first branch pipe 63a includes the electromagnetic valve 61a, while the second branch pipe 64a includes the electromagnetic valve 62a. By opening or closing the electromagnetic valves 61a and 62a, the refrigerant flow passage in the refrigerant circuit can be switched such that the indoor heat exchanger 81a of the indoor unit 8a corresponding to the branch unit 6a can be connected to the discharge side (high pressure gas pipe 30 side) or suction side (low pressure gas pipe 31 side) of the compressor 21.

Here, the structures of the branch units 6b-6e, as described above, are the same as the branch unit 6a and thus the final numbers of numerals given to the composing elements (devices and members) of the branch unit 6a are changed from a to b, c, d and e to thereby designate the composing elements of the branch units 6b-6e.

While using FIG. 1, description will be given below of the connecting states of the above-mentioned outdoor units 2a, 2b, indoor units 8a-8e and branch units 6a-6e to the high pressure gas pipe 30, high pressure gas branch pipes 30a, 30b, low pressure gas pipe 31, low pressure gas branch pipes 31a, 31b, liquid pipe 32, liquid branch pipes 32a, 32b and turn-out devices 70, 71, 72. The one-side ends of the high pressure branch pipes 30a and 30b are connected to the closing valves 44a and 44b of the outdoor units 2a and 2b respectively, while the other-side ends of the high pressure branch pipes 30a and 30b are respectively connected to the turn-out device 70. One end of the high pressure gas pipe 30 is connected to the turn-out device 70, while the other end is branched and connected to the first branch pipes 63a-63e of the branch units 6a-6e.

The one-side ends of the low pressure gas branch pipes 31a and 31b are connected to the closing valves 45a and 45b of the outdoor units 2a and 2b respectively, with the other-side ends respectively connected to the turn-out device 71. One end of the low pressure gas pipe 31 is connected to the turn-out device 71, with the other end branched and connected to the second branch pipes 64a-64e of the branch units 6a-6e.

The one-side ends of the liquid branch pipes 32a and 32b are connected to the closing valves 46a and 46b of the outdoor units 2a and 2b, with the other-side ends connected to the turn-out device 72. One end of the liquid pipe 32 is connected to the turn-out device 72, with the other end branched and connected to refrigerant pipes connected to the indoor expansion valves 82a-82e of the indoor units 8a-8e.

The indoor heat exchangers 81a-81e of the indoor units 8a-8e are connected to the connecting portions between the first branch pipes 63a-63e and second branch pipes 64a-64b of the corresponding branch units 6a-6e by refrigerant pipes. This connection constitutes the refrigerant circuit of the air conditioning apparatus 1 and a refrigeration cycle can be formed when a refrigerant is poured into the refrigerant circuit.

Next, description will be given below of the operation of the air conditioning apparatus 1 of this embodiment with reference to FIG. 1. Here, in FIG. 1, when the respective heat exchangers provided in the outdoor units 2a, 2b and indoor units 8a-8e serve as condensers, they are shown as hatched, whereas, when they serve as evaporators, they are shown as reversed. Also, when the first electromagnetic valves 42a, 42b and second electromagnetic valves 43a, 43b provided on the outdoor units 2a, 2b and the electromagnetic valves 61a-61e and electromagnetic valves 62a-62e provided on the branch units 6a-6e are closed, they are shown as black, whereas, when opened, they are shown as reversed. And, arrows designate the flows of refrigerants.

As shown in FIG. 1, when both outdoor units 2a and 2b must be operated because all the indoor units 8a-8e are executing heating operations to thereby require a high operation capacity, in the outdoor unit 2a, the ports b and c of the first three-way valve 22a are switched into communication to thereby allow the first outdoor heat exchanger 24a to function as an evaporator, and the ports e and f of the second three-way valve 23a are switched into communication to thereby allow the second outdoor heat exchanger 25a to function as an evaporator. Also, in the outdoor unit 2b, the ports h and i of the first three-way valve 22b are switched into communication to thereby allow the first outdoor heat exchanger 24b to function as an evaporator, and the ports m and n of the second three-way valve 23b are switched into communication to thereby allow the second outdoor heat exchanger 25b to function as an evaporator. Here, the first electromagnetic valves 42a, 42b and second electromagnetic valves 43a, 43b of the outdoor units 2a, 2b are all closed, while the hot gas bypass pipes 36a, 36b and oil return pipes 37a, 37b are all shut.

In the indoor units 8a-8e, the electromagnetic valves 61a-61e of their corresponding branch units 6a-6e are opened to allow the refrigerant to flow in the first branch pipes 63a-63e and the electromagnetic valves 62a-62e are closed to shut the second branch pipes 64a-64e. Accordingly, the indoor heat exchangers 81a-81e of the indoor units 8a-8e are all allowed to function as condensers.

High pressure refrigerants discharged from the compressors 21a and 21b flow through the oil separators 28a and 28b in the outdoor high pressure gas pipes 33a and 33b, and flow through the closing valves 44a and 44b into the high pressure branch pipes 30a and 30b. The high pressure refrigerants having flown into the high pressure branch pipes 30a and 30b join together in the turn-out device 70, flow in the high pressure gas pipe 30, and flow from the high pressure pipe 30 into the branch units 6a-6e after they are branched.

The high pressure refrigerants having flown into the branch units 6a-6e flow in the first branch pipes 63a-63e with the electromagnetic valves 61a-61e opened, flow out from the branch units 6a-6e, and flow into the indoor units 8a-8e respectively corresponding to the branch units 6a-6e.

The high pressure refrigerants having flown into the indoor units 8a-8e flow into the indoor heat exchangers 81a-81e, and exchange heat with respect to the indoor air to thereby condense. The condensed refrigerants heat the indoor air, thereby heating the inside of a room with the indoor units 8a-8e installed. The high pressure refrigerants having flown out from the indoor heat exchangers 81a-81e pass through the indoor expansion valves 82a-82e, whereby the pressures thereof are reduced. The valve opening rates of the indoor expansion valves 82a-82e are determined according to the super-cooled degrees of the refrigerants in the refrigerant exits of the indoor heat exchangers 81a-81e. The refrigerant super-cooled degree can be found, for example, by subtracting the refrigerant temperature in the refrigerant exits of the indoor heat exchangers 81a-81e from a high pressure saturation temperature (corresponding to a condensation temperature within the indoor heat exchangers 81a-81e) calculated from pressures detected by the high pressure sensors 50a and 50b of the outdoor units 2a and 2b.

The intermediate pressure refrigerants having flown out from the indoor units 8a-8e flow into the liquid pipe 32, join together within the liquid pipe 32 and then flow into the turn-out device 72. The intermediate pressure refrigerants having branched and flown from the turn-out device 72 into the liquid branch pipes 32a and 32b flow through the closing valves 46a and 46b into the outdoor units 2a and 2b. The intermediate pressure refrigerants having flown into the outdoor units 2a and 2b flow in the outdoor unit liquid pipes 35a and 35b, branch at the connecting points B and J, and flow through the first outdoor expansion valves 40a, 40b and second outdoor expansion valves 41a, 41b, whereby the pressures thereof are reduced to provide low pressure refrigerants.

The valve opening rates of the first outdoor expansion valves 40a, 40b are determined according to the superheated degrees of the refrigerants in the refrigerant exits of the first outdoor heat exchangers 24a, 24b. Also, the valve opening rates of the second outdoor expansion valves 41a, 41b are determined according to the superheated degrees of the refrigerants in the refrigerant exits of the second outdoor heat exchangers 25a, 25b. The superheated degrees of the refrigerants can be found, for example, by subtracting low pressure saturation temperatures calculated from pressures detected by the low pressure sensors 51a, 51b of the outdoor units 2a, 2b (corresponding to evaporation temperatures within the first outdoor heat exchangers 24a, 24b and second outdoor heat exchangers 25a, 25b) from refrigerant temperatures in the refrigerant exits of the first outdoor heat exchangers 24a, 24b and second outdoor heat exchangers 25a, 25b detected by the first heat exchanger temperature sensors 56a, 56b and second heat exchanger temperature sensors 57a, 57b.

The low pressure refrigerants pressure reduced by the first outdoor expansion valves 40a, 40b and second outdoor expansion valves 41a, 41b flow into the first outdoor heat exchangers 24a, 24b and second outdoor heat exchangers 25a, 25b, where they exchange heat with respect to the open-air and are thus caused to evaporate. The low pressure refrigerants having flown out from the first outdoor heat exchangers 24a, 24b and second outdoor heat exchangers 25a, 25b flow through the first three-way valves 22a, 22b and second three-way valves 23a, 23b, join together at the connecting portions C and K, and are sucked through the connecting points F, P, accumulators 27a, 27b into the compressors 21a, 21b, where they are compressed again.

Next, while using FIGS. 1 to 5, description will be given below of the operation of the refrigerant circuit of the invention and the operation effects thereof with reference to the air conditioning apparatus 1 of this embodiment. Here, in the following description, there is taken an example in which the air conditioning apparatus 1 is actuated to start the heating operation described using FIG. 1 and, specifically, the indoor units 8a-8e and outdoor units 2a, 2b are all operated.

For example, when the air conditioning apparatus 1 is installed in a cold region, or when the open air temperature is low (for example, 0° C. or lower), for example, late at night or early in the morning in a winter season, there is a fear that, within the compressors 21a and 21b not in operation, there has occurred so called refrigerant dissolution where refrigerants are dissolved in the refrigerating machine oil of the compressors 21a, 21b. When the compressors 21a, 21b are started in this state, there is a fear that the refrigerant dissolved in the refrigerating machine oil can evaporate to provide a gas refrigerant and, when the gas refrigerant is discharged from the compressors 21a, 21b, it can catch and take out the refrigerating machine oil outside the compressors 21a, 21b, resulting in the shortage of the refrigerating machine oil within the compressors 21a, 21b.

In this embodiment, to solve the above problem, in the start time of the air conditioning apparatus 1, there are executed first start control mainly for removing the refrigerant dissolution within the compressors 21a and 21b to reduce the amount of the refrigerating machine oil that is discharged together with the refrigerant, and second start control mainly for shortening the rising time of the heating operation capacity. The first and second start control will be described below specifically.

[First Start Control]

According to an operation start instruction or a timer start instruction by a user, the air conditioning apparatus 1 starts a heating operation. On receiving the operation start instruction through the indoor units 8a-8e, CPUs 110a and 110b of the controllers 100a and 100b of the outdoor units 2a and 2b check whether a first given condition, namely, the start condition of a first start control holds or not; and, when it holds, they start the first start control. Here, the start condition of the first start control is, for example, a condition showing a fear that refrigerant dissolution has occurred within the compressors 21a and 21b because the open-air temperature is a given temperature (for example, 5° C.) or lower and the compressors 21a and 21b have been continuously not in operation for a given time (for example, an hour) or longer. Here, when the start condition of the first start control does not hold, CPUs 110a and 110b carry out such control of the outdoor units 2a and 2b as corresponds to the normal air conditioning control.

CPUs 110a and 110b, in the first start control, as shown in FIG. 5, execute the rotation number control of the compressors 21a, 21b, the function switching (evaporator/condenser switching) control of the first outdoor heat exchangers 24a, 24b and second outdoor heat exchangers 25a, 25b, the valve opening rate control of the first outdoor expansion valves 40a, 40b and second outdoor expansion valves 41a, 41b, and the opening and closing control of the first electromagnetic valves 42a, 42b and second electromagnetic valves 43a, 43b.

Specifically, as shown in FIG. 3, CPU 110a controls the first three-way valve 22a to bring the ports b and c into communication to thereby allow the first outdoor heat exchanger 24a to function as an evaporator, and controls the second three-way valve 23a to bring the ports d and e into communication to thereby allow the second outdoor heat exchanger 25a to function as a condenser. Also, CPU 110b controls the first three-way valve 22b to bring the ports h and j into communication to thereby allow the first outdoor heat exchanger 24b to function as an evaporator, and controls the second three-way valve 23b to bring the ports k and m into communication to thereby allow the second outdoor heat exchanger 25b to function as a condenser.

And, CPUs 110a and 110b maintain the compressors 21a, 21b at the start time rotation number which is a previously determined given rotation number. For example, as shown in FIG. 5, they start the compressors 21a, 21b at 70 rps and maintain this start time rotation number. When the compressors 21a, 21b start, as shown in FIG. 3, high pressure refrigerants discharged from the compressors 21a, 21b flow in the outdoor unit high pressure gas pipes 33a, 33b through oil separators 28a, 28b, and branch at the connecting points A and H into two refrigerants. One of them flows through the closing valves 44a, 44b into the indoor units 8a-8e, while the other flows through the second three-way valves 23a, 23b into the second outdoor heat exchangers 25a, 25b functioning as evaporators.

The high pressure refrigerant having flown into the second outdoor heat exchangers 25a, 25b exchanges heat with respect to the open-air to thereby condense and passes through the second outdoor expansion valves 41a, 41b fully opened by CPUs 110a, 110b as shown in FIG. 5, thereby being reduced in pressure. The intermediate pressure refrigerant having passed through the second outdoor expansion valves 41a, 41b joins the intermediate pressure refrigerant having flown from the indoor units 8a-8e at the connecting points B and J, and passes through the first outdoor expansion valves 40a, 40b opened at a given angle by CPUs 110a, 110b as shown in FIG. 5, thereby being reduced in pressure.

Here, the valve opening rates of the first outdoor expansion valves 40a, 40b are controlled by CPUs 110a, 110b according to the superheated degrees of the refrigerants in the refrigerant exits (existing on the first three-way valves 22a, 22b side) of the first outdoor heat exchangers 24a, 24b. The superheated degree of the refrigerant can be obtained, for example, by subtracting a low pressure saturation temperature (corresponding to an evaporation temperature within the first outdoor heat exchangers 24a, 24b calculated from pressure detected by the low pressure sensors 51a, 51b from the refrigerant temperature in the refrigerant exits of the first outdoor heat exchangers 24a, 24b detected by the first heat exchanger temperature sensors 56a, 56b.

The low pressure refrigerant having passed through the first outdoor expansion valves 40a, 40b exchanges heat with respect to the open-air in the first outdoor heat exchangers 24a, 24b to thereby evaporate, and is sucked through the first three-way valves 22a, 22b and accumulators 27a, 27b into the compressors 21a, 21b. Also, as shown in FIG. 5, CPUs 110a, 110b open the first electromagnetic valves 43a, 43b to thereby allow the refrigerant to flow in the hot gas bypass pipes 36a, 36b. Here, as shown in FIG. 5, the second electromagnetic valves 44a, 44b are set to open when the outdoor units 2a, 2b are not in operation and, also when executing the first start control, they maintain their open states, thereby allowing the refrigerant to flow in the oil return pipes 37a, 37b.

When there is a fear that refrigerant dissolution has occurred within the compressors 21a, 21b, in the start time of the air conditioning apparatus 1, preferably, by executing the start control to drive the compressors 21a, 21b at the rotation numbers that is the start time rotation numbers, namely, predetermined rotation numbers, the temperatures of the compressors 21a, 21b may be raised quickly to thereby quickly separate the refrigerant dissolved in the refrigerating machine oil from the refrigerating machine oil. Here, the start time rotation number, in consideration of the amount of discharge of the refrigerating machine oil increasing with the increased rotation number of the compressor, is set as a number as large as possible in the range where the discharge amount of the refrigerating machine oil is a given amount or less. However, when the compressors 21a, 21b are driven on at the start time rotation numbers, the internal pressures of the compressors 21a, 21b are caused to increase. This raises a fear that refrigerant dissolution cause by the increased pressure can occur within the compressors 21a, 21b.

On the other hand, in the first start control of the invention, when driving the compressor 21a, 21b with their rotation numbers maintained at the start time rotation numbers, one of the two outdoor heat exchangers, namely, the second outdoor heat exchanger 25a, 25b is allowed to function as a condenser, thereby being able to prevent the high pressure (the pressure on the discharge side of the compressor 21a, 21b) from increasing.

Also, when executing the first start control, the first electromagnetic valve 43a, 43b and second electromagnetic valve 44a, 44b are opened to thereby allow the refrigerant to flow in the hot gas bypass pipe 36a, 36b and oil return pipe 37a, 37b. Since the hot gas bypass pipe 36a, 36b bypasses the outdoor unit high pressure gas pipe 33a, 33b and outdoor unit low pressure gas pipe 34a, as shown by a broken arrow line in FIG. 3, the refrigerant flows from the connecting point E to F, or from the connecting point N to P to thereby prevent the high pressure (pressure on the discharge side of the compressor 21a, 21b) from increasing. Also, since the oil return pipe 37a, 37b bypasses the outdoor unit high pressure gas pipe 33a, 33b and outdoor unit low pressure gas pipe 34a through the oil separator 28a, 28b, as shown by a broken arrow line in FIG. 3, the refrigerant flows together with the refrigerating machine oil from the oil separator 28a, 28b to the compressor 21a, 21b to thereby prevent the high pressure (pressure on the discharge side of the compressor 21a, 21b) from increasing.

As described above, in the first start control, since CPU 110a, 110b control the second outdoor heat exchangers 25a, 25b to function as condensers and control the oil return pipes 37a, 37b to allow the refrigerants to flow therein, thereby being able to prevent the high pressure from increasing. Thus, even when the compressor 21a, 21b are driven on at the start time rotation numbers, the increased internal pressures of the compressor 21a, 21b can be prevented. This can prevent the occurrence of the refrigerant dissolution within the compressor 21a, 21b caused by the increased internal pressures of the compressor 21a, 21b.

In the above-described first start control, the second outdoor heat exchangers 25a, 25b are controlled to function as condensers, while the hot gas bypass pipe 36a, 36b and oil return pipe 37a, 37b are controlled to allow the refrigerant to flow therein. However, when, by controlling one of the pipes, the increased internal pressures of the compressor 21a, 21b due to the continuous driving of the compressor 21a, 21b at the start time rotation numbers can be prevented, only one of the pipes may also be controlled. Also, the hot gas bypass pipe 36a, 36b and oil return pipe 37a, 37b are controlled to allow the refrigerant to flow therein. However, when, by controlling only one of the pipes to allow the refrigerant to flow therein, the increased internal pressures of the compressor 21a, 21b due to the continuous driving of the compressor 21a, 21b at the start time rotation numbers can be prevented, only one of the pipes may also be controlled to allow the refrigerant to flow therein.

Also, in the first start control, of the two outdoor heat exchangers, the first outdoor heat exchanger 24a, 24b is controlled to function as an evaporator. As shown in FIGS. 2A and 2B, the first outdoor heat exchanger 24a, 24b is disposed nearer to the outdoor fan 26a, 26b than the second outdoor heat exchanger 25a, 25b.

When an outdoor heat exchanger functioning as an evaporator runs short of evaporation capacity, there is a fear that a liquid refrigerant having failed to evaporate fully in the outdoor heat exchanger can be sucked back into the compressor, that is, a so called liquid refrigerant back can occur. This raises a fear that, when the liquid refrigerant is compressed, the compressor can be damaged.

To prevent the above-mentioned liquid refrigerant back caused by the shortage of the evaporation capacity, in the first start control, the first outdoor heat exchanger 24a, 24b, which is disposed upwardly of the second outdoor heat exchanger 25a, 25b and is thereby nearer to the outdoor fan 26a, 26b than the heat exchanger 25a, 25b, is controlled to function as an evaporator. The nearer to the outdoor fan 26a, 26b the heat exchanger is, the more the passage amount of the open-air sucked into the outdoor units 2a, 2b is. Therefore, the evaporation capacity of the first outdoor heat exchanger 24a, 24b is higher than when the second outdoor heat exchanger 25a, 25b is used as an evaporator.

This can prevent the occurrence of the liquid refrigerant back caused by the short evaporation capacity of the first outdoor heat exchanger 24a, 24b functioning as an evaporator. Here, as described above, since the valve opening rate of the first outdoor expansion valve 40a, 40b corresponding to the first outdoor heat exchanger 24a, 24b functioning as an evaporator is controlled according to the superheated degree of the refrigerant in the refrigerant exit (existing on the first three-way valve 22a, 22b side), the higher evaporation capacity of the first outdoor heat exchanger 24a, 24b can be secured, thereby being able to prevent the occurrence of the liquid refrigerant back more effectively.

CPU 110a, 110b, during execution of the first start control, is checking whether a second given condition, namely, the end condition of the first start control holds or not. When it holds, CPU 110a or 110b ends the first start control and moves to the second start control to be explained next. Here, the first start control end condition is, for example, a condition which, when the discharge superheat degree of the compressor 21a, 21b after passage of a given time (for example, a minute) from the start of the first start control reaches a given temperature (for example, 8° C.), can restrict to some degree the refrigerating machine oil discharged together with the refrigerant from the compressor 21a, 21b. Here, to obtain the discharge superheat degree of the compressor 21a, 21b, a high pressure saturation temperature (corresponding to a condensation temperature within the second outdoor heat exchanger 25a, 25b) found from the pressure detected by the high pressure sensor 50a, 50b may be subtracted from a refrigerant temperature detected by the discharge temperature sensor 53a, 53b.

[Second Start Control]

CPU 110a, 110b starts the second start control following the first start control. As described above, since, in the first start control, the refrigerant dissolution in the compressor 21a, 21b has been eliminated to a certain degree to provide such refrigerating machine oil discharge amount as causes no interference with the lubrication of the compressor 21a, 21b, in the second start control, there are executed various kinds of control which reduce the refrigerant dissolution amount in the compressor 21a, 21b and shorten the rising time of the air conditioning capacity. Therefore, although, in the first start control, the two outdoor heat exchangers are structured different in function to thereby allow the evaporator and condenser to coexist in the outdoor unit, in the second start control, when an operation mode is a heating/heating-based operation, the two outdoor heat exchangers are both used to function as an evaporator and, for a cooling/cooling-based operation, both are used to function as a condenser.

In this embodiment, in order for the air conditioning apparatus 1 to carry out a heating operation, CPU 110a, 110b, in the second start control, as shown in FIG. 5, executes the control of the rotation number of the compressor 21a, 21b, the control of the function switching of the second outdoor heat exchanger 25a, 25b (switching from condenser to evaporator. The first outdoor heat exchanger 24a, 24b maintains this state because it is set to function as an evaporator in the first start control), the valve opening rate control of the first outdoor expansion valve 40a, 40b and second outdoor expansion valve 41a, 41b, and the opening/closing control of the first electromagnetic valve 42a, 42b and second electromagnetic valve 43a, 43b.

Specifically, CPUs 110a, 110b, as shown in FIG. 4, switch the second three-way valve 23a to bring the ports e and f into communication and the second three-way valve 23a to bring the ports m and n into communication, thereby allowing the second heat exchangers 25a, 25b to function as an evaporator. Also, CPUs 110a, 110b, as shown in FIG. 5, drive on the compressors 21a, 21b while maintaining 70 rps, namely, the start time rotation number, and maintain the opened states of the first electromagnetic valves 43a, 43b and second electromagnetic valves 44a, 44b, thereby allowing the refrigerant to flow in the hot gas bypass pipes 36a, 36b and oil return pipes 37a, 37b.

Also, CPUs 110a, 110b, as shown in FIG. 5, control the valve opening rates of the first outdoor expansion valves 40a, 40b according to the superheated degrees of the refrigerants in the refrigerant exits of the first outdoor heat exchangers 24a, 24b, and control the valve opening rates of the second outdoor expansion valves 41a, 41b according to the superheated degrees of the refrigerants in the refrigerant exits of the second outdoor heat exchangers 25a, 25b. Here, the refrigerant circuit shown in FIG. 4 during execution of the second start control is the same as the refrigerant circuit described in FIG. 1 except for the states (where the refrigerant flows/does not flow) of the hot gas bypass pipes 36a, 36b and oil return pipes 37a, 37b. Thus, the specific description of the flow of the refrigerant and the like is omitted here.

In the second start control, as described above, the second outdoor heat exchangers 25a, 25b having functioned as a condenser in the first start control are switched to function as an evaporator, while the compressors 21a, 21b are still driven on while maintaining 70 rps, or the start time rotation number. Since the compressors 21a, 21b have been heated in the first start control, even when the condenser is removed from the refrigerant circuit, there is reduced the amount of refrigerant dissolution due to the increased internal pressures of the compressors 21a, 21b caused by maintaining the start time rotation number. Therefore, in the second start control, since, while the first outdoor heat exchangers 24a, 24b and second outdoor heat exchangers 25a, 25b are both used as an evaporator, that is, according to a refrigerant circuit in a heating operation, the compressors 21a, 21b are driven with their rotation numbers maintained at 70 rps, the compressors 21a, 21b are heated to thereby be able to further reduce the refrigerant dissolution amount in the compressors 21a, 21b and also shorten the rising time of the heating operation capacity.

Also, when the second outdoor heat exchangers 25a, 25b having functioned as a condenser are switched to function as an evaporator, the high pressure increases transitionally, thereby raising a fear that the compression rates of the compressors 21a, 21b can increase. The increased compression rates can damage the compressors 21a, 21b. Thus, in the second start control, as shown in FIG. 5, the first electromagnetic valves 42a, 42b and second electromagnetic valves 43a, 43b, which have been opened in the first start control execution time, are remained opened for a given time (time necessary for the transitional increase in the high pressure to stop, for example, for two minute). This allows the refrigerant to flow in the hot gas bypass pipes 36a, 36b and oil return pipes 37a, 37b and thus the increase in the high pressure can be prevented. This can prevent the increased compression rates of the compressors 21a, 21b and thus can prevent them against damage.

In the second start control, since the second outdoor heat exchangers 25a, 25b are switched in function from a condenser to an evaporator, the first three-way valves 22a, 22b side portions of the second outdoor heat exchangers 25a, 25b are connected to the suction side portions of the compressors 21a, 21b respectively. Thus, liquid refrigerants, which stay in the second outdoor heat exchangers 25a, 25b functioning as a condenser and are not evaporated fully when the heat exchangers are switched to an evaporator, flow through the second three-way valves 23a, 23b and connecting points C, K into the outdoor unit low pressure gas pipes 34a, 34b.

In this state, for example, when the compressor 21b is stopping, the liquid refrigerant staying in the second outdoor heat exchanger 25b flows from the second three-way valve 23b through the connecting points K, M into the outdoor unit low pressure gas pipe 34b and then flows through the low pressure gas branch pipe 31b, turn-out device 71 and low pressure gas branch pipe 31a sequentially into the outdoor unit 2a. After then, the liquid refrigerant flows through the outdoor unit low pressure gas pipe 34a into the accumulator 27a via the connecting point F. Consequently, there is a fear that the refrigerants are concentrated in the outdoor unit 2a including the currently driven compressor 21a to thereby cause an overflow in the accumulator 27a.

Thus, in the second start control of the invention, all compressors having been driven in the first start control, in this embodiment, the compressors 21a, 21b are also continuously driven. Accordingly, when the second outdoor heat exchangers 25a, 2b are switched in function from a condenser to an evaporator, the liquid refrigerants staying in the second outdoor heat exchangers 25a, 2b are allowed to flow into their associated accumulators 27a, 27b. This can eliminate the inconvenience that the refrigerants can be concentrated in one of the outdoor units and thus an overflow can occur in the associated accumulator.

CPUs 110a, 110b, during execution of the second start control, are checking whether the end condition of the second start control holds or not. When the end condition holds, they end the second start control, that is, end the start control of the air conditioning apparatus 1 and transfer their control to the normal air-conditioning control. Here, the end condition of the second start control is a condition where the refrigerant dissolution within the compressors 21a, 21b is removed to thereby prevent the refrigerating machine oil from being discharged together with the refrigerant any more, for example, when the discharge superheated degrees of the compressors 21a, 21b after passage of a given time (for example, a minute) from the initiation of the second start control reach a given temperature (for example, 12° C.) or higher.

Next, description will be given below of the flow of processings to be executed by the air conditioning apparatus 1 of this embodiment with reference to a flow chart shown in FIG. 6. The flow chart of FIG. 6 shows the flow of processings relating to the first and second start control to be carried out when the air conditioning apparatus 1 starts its operation, wherein ST designates steps and a numeral following ST designates the step number. Here, in FIG. 6, description is given mainly of processings relating to the invention, while omitting the description of other ordinary processings such as the control of a refrigerant circuit corresponding to operation conditions such as temperatures and air amounts specified by a user. Also, since the processings relating to the first and second start control to be executed by CPUs 110a, 110b are the same, in the following description, description will be given of processings relating to the first and second start control to be executed by CPU 110a included in the controller 100a of the outdoor unit 2a.

On receiving an operation start instruction, CPU 110a checks whether the start condition of the first start control holds or not (ST1). When the condition holds (ST1-Yes), CPU 110a controls the first three-way valve 22a to allow the first outdoor heat exchanger 24a to function as an evaporator and controls the second three-way valve 23a to allow the second outdoor heat exchanger 25a to function as an evaporator (ST2).

Next, CPU 110a controls the compressor 21a to start at the start time rotation number, or, to be driven on at the start time rotation number (ST3).

Next, CPU 110a controls the valve opening rate of the first outdoor expansion valve 40a according to the refrigerant superheated degree in the refrigerant exit of the first outdoor heat exchanger 24a and opens the second outdoor expansion valve 41 fully (ST4).

Next, CPU 110a controls opens the first electromagnetic valve 42a (ST5) to thereby allow the refrigerant to flow in the hot gas bypass 36a. Here, as described above, the second electromagnetic valve 43a has been opened since the stopping time of the outdoor unit 2a and CPU 110a maintains this state to allow the refrigerant to flow in the oil return pipe 37a.

Next, CPU 110a checks whether the end condition of the first start control holds or not (ST6). When not (ST6-No), CPU 110a returns the processing to ST2, where it continues the first start control.

When the end condition holds (ST-Yes), CPU 110a ends the first start control and moves to the second start control. CPU 110a checks whether an operation mode instructed by a user is a heating operation or a heating-based operation or not (ST7).

When it is a heating operation or a heating-based operation (ST7-Yes), CPU 110a switches the function of the second outdoor heat exchanger 25a from a condenser to an evaporator (ST8). Next, CPU 110a controls the valve opening rate of the first outdoor expansion valve 40a according to the refrigerant superheated degree in the refrigerant exit of the first outdoor heat exchanger 24a and controls the valve opening rate of the second outdoor expansion valve 41a according to the refrigerant superheated degree in the refrigerant exit of the second outdoor heat exchanger 25a (ST9).

Next, CPU 110a, after end of the first start control, starts a timer and checks whether a given time after end of the first start control, for example, two minutes have passed or not (ST10). When not (ST10-No), CPU 110a returns the processing to ST7.

When the given time has passed (ST10-Yes), CPU 110a closes the first and second electromagnetic valves 42a and 43a (ST11), thereby shutting the hot gas bypass pipe 36a and oil return pipe 37a.

Next, CPU 110a checks whether the end condition of the second start control holds or not (ST12). When not (ST12-No), CPU 110a drives on the compressor 21a at the start time rotation number (ST14) and returns the processing to ST12, where it continues the second start control. When the end condition holds (ST12-Yes), CPU 110a ends the second start control, namely, ends the start control of the air conditioning apparatus 1 and starts the normal air-conditioning control.

Here, when the start condition of the first start control does not hold in ST1 (ST1-No), CPU 110a does not execute the start control but starts the normal air-conditioning control.

Also, when the operation mode is not a heating operation or a heating-based operation (ST7-No), since the operation mode instructed by the user is a cooling operation or a cooling-based operation, CPU 110a switches the function of the first outdoor heat exchanger 24a from an evaporator to a condenser (ST12). Next, CPU 110a opens the first outdoor expansion valve 40a fully, or controls the valve opening rate thereof according to the refrigerant super-cooled degree in the refrigerant exit of the first outdoor heat exchanger 24a, and also opens the second outdoor expansion valve 41a fully, or controls the valve opening rate thereof according to the refrigerant super-cooled degree in the refrigerant exit of the second outdoor heat exchanger 25a (ST13). Then, CPU 110a advances the processing to ST10.

Embodiment 2

Next, description will be given below of a second embodiment of the air conditioning apparatus of the invention. Here, since the structure and running operation of the air conditioning apparatus and the start condition of start control to be executed when the air conditioning apparatus starts are the same as those of the first embodiment, the description thereof is omitted. This embodiment is different from the first embodiment in that, between the first and second start control of the first embodiment, there is inserted control to reduce the rotation number of the compressor.

Now, description will be given below of the operations of a refrigerant circuit of this embodiment and the operation effects thereof in the air conditioning apparatus 1 of this embodiment with reference to FIGS. 1 to 4, 7 and 8. Here, in the following description, similarly to the first embodiment, description will be given while taking an example where the air conditioning apparatus 1 starts its own operation and initiates the heating operation described with reference to FIG. 1 and the indoor units 8a-8e and outdoor units 2a, 2b are all operated.

In the first embodiment, in the case that the start control start condition (the start condition of the first start control) holds when the air conditioning apparatus 1 starts a heating operation, CPUs 110a, 110b execute the first start control and, following the end of the first start control, execute the second start control. When the control is switched from the first start control to the second start control, the second outdoor heat exchangers 25a, 25b functioning as condensers in the first start control are switched to function as evaporators. This removes the outdoor heat exchanger functioning as a condenser, thereby increasing the high pressure (the pressure on the discharge sides of the compressors 21a, 21b).

At the then time, when the open-air temperature is relatively high (for example, −9° C. or higher), since the second outdoor heat exchangers 25a, 25b functioning as condensers are switched to function as evaporators, the condensation capacity is reduced. This increases the high pressure and thus the operation loads of the compressors 21a, 21b, raising a fear that the discharge outputs of the compressors 21a, 21b can exceed the upper limit values thereof. This raises a fear that overload protection control to stop the compressors 21a, 21b to thereby prevent the increased discharge outputs can be executed.

In this embodiment, to solve the above problem, as shown in FIG. 7, when the air conditioning apparatus 1 starts its operation, there is carried out start control, including: first start control (the same control as the first start control in the first embodiment) to be executed mainly to eliminate the refrigerant dissolution within the compressors 21a, 21b to thereby reduce the amount of refrigerating machine oil to be discharged together with the refrigerant; second start control to be executed mainly to prevent an increase in the discharge pressures of the compressors 21a, 21b; and, third start control (the same control as the second start control in the first embodiment except for the control of the rotation numbers of the compressors 21a, 21b) to be executed mainly to shorten the rising time of the heating operation capacity.

Although description will be given below of the above-mentioned respective start control specifically, the description of the first start control is omitted because it is the same as the first start control in the first embodiment including the start and end conditions. Also, since the third start control is the same as the second start control in the first embodiment except for the rotation numbers (to be discussed later) of the compressors 21a, 21b, the description thereof is omitted. Further, in the following description, the lower limit rotation number in the rotation number range allowed in the compressors 21a, 21b is assumed to be 20 rps.

[Second Start Control]

When the end condition of the first start control holds, CPUs 110a, 110b start the second start control following the first start control. In the second start control, the rotation numbers of the compressors 21a, 21b are reduced at a given rate from 70 rps, namely, the rotation number (start time rotation number) during the first start control execution down to a rotation number X (rps) previously set according to the open-air temperatures, thereby reducing the discharge pressures of the compressors 21a, 21b.

In memory portions 120a, 120b respectively corresponding to CPU 110a, 110b, there is previously stored a rotation number table 200 shown in FIG. 8. The table 200 sets the rotation numbers X (rps) of the compressors 21a, 21b according to the then-time open-air temperatures T (° C.) when executing the second start control. In this table, by previously conducting tests and the like, it has been confirmed that, when the rotation numbers of the compressors 21a, 21b are reduced down to the rotation numbers X, the discharge pressures of the compressors 21a, 21b are prevented from exceeding their upper limit values at the corresponding open-air temperatures T.

In the rotation number table 200, the open-air temperatures T are divided by 1° C. between “−10° C. or lower” and “11° C. or higher”. The rotation numbers X are determined correspondingly to the open-air temperatures T. Specifically, when the open-air temperatures T are “−10° C. or lower”, since a fear of the discharge pressures of the compressors 21a, 21b exceeding their upper limit values is low, the rotation number X is set at “70 rps”, namely, the start time rotation number.

When the open-air temperatures T are higher than −10° C., there is a fear that the discharge pressures of the compressors 21a, 21b can exceed the upper limit values and, the higher the open-air temperatures T become, the higher the possibility of the discharge outputs exceeding the upper limit values becomes. Therefore, in the rotation number table 200, the higher the open-air temperatures T become, the lower the rotation numbers X become. For example, when the open-air temperature T is −5°, the rotation number X is 58 rps; for the open-air temperature T of 0° C., 46 rps; and, for the open-air temperature T of 5° C., 35 rps. For the open-air temperature T of 11° C. or higher, the rotation number X is 20 rps or the lower limit rotation number.

Next, description will be given below of the specific operations of the respective composing elements of the outdoor units 2a, 2b when executing the second start control. CPUs 110a, 110b, in the second start control, as shown in FIG. 7, execute the rotation number control of the compressors 21a, 21b, the function switching (evaporator/condenser switching) control of the first outdoor heat exchangers 24a, 24b and second outdoor heat exchangers 25a, 25b, the valve opening rate control of the first outdoor expansion valves 40a, 40b and second outdoor expansion valves 41a, 41b, and the opening/closing control of the first electromagnetic valves 42a, 42b and second electromagnetic valves 43a, 43b.

The above respective kinds of control included in the second start control are similar to those of the first start control except for the rotation number control of the compressors 21a, 21b. Therefore, the description thereof is omitted here and thus the rotation number control of the compressors 21a, 21b will be described below specifically. Here, the state of the refrigerant circuit of the air conditioning apparatus 1 when executing the second start control is similar to that of the first start control in the first embodiment, that is, the state shown in FIG. 3.

The memory portions 120a, 120b store therein in a time series manner the open-air temperatures detected at a given timing (for example, every two seconds) by the open-air temperature sensors 58a, 58b serving as the open-air temperature detecting devices provided in the respective outdoor units 2a, 2b. On starting the second start control, CPUs 110a, 110b import the finally stored open-air temperature T from the open-air temperatures stored in the memory portions 120a, 120b. CPUs 110a, 110b refer to the rotation number table 200 similarly stored in the memory portions 120a, 120b and extract from the rotation number table 200 the rotation number X corresponding to the imported open-air temperature T.

Next, CPUs 110a, 110b reduce the rotation number of the compressors 21a, 21b from the current rotation number, namely, 70 rps or the start time rotation number down to the extracted rotation number X at a predetermined given rate. For example, when the open-air temperature T is 0° C. and the given rate for reducing the rotation number is 2 rps/sec, since the rotation number table 200 shows that the rotation number X when the open-air temperature T is 0° C. is 46 rps, CPUs 110a, 110b reduce the rotation number of the compressors 21a, 21b down to 46 rps in twelve seconds ((70 rps−46 rps)/2 rps/sec=12 seconds). By reducing the rotation numbers of the compressors 21a, 21b in this manner, the discharge outputs of the compressors 21a, 21b are reduced.

CPUs 110a, 110b, during execution of the second start control, is checking whether the end condition of the second start control holds or not, and when the end condition holds, end the second start control and move to third start control to be described next. Here, the end condition of the second start control is, for example, whether a given time has passed since the start of the second start control or not. This given time is a previously determined in consideration of time necessary to reduce the rotation numbers of the compressors 21a, 21b down to the lower limit rotation number, 20 rps. For example, when a given rate for reducing the rotation number is above-mentioned 2 rps/1 sec, there is obtained (70 rps−20 rps)/2 rps=25 seconds.

Therefore, when time necessary to reduce the rotation numbers of the compressors 21a, 21b down to the rotation number X corresponding to the open-air temperature T is shorter than the given time (for example, 25 seconds), CPUs 110a, 110b, after reducing the rotation numbers of the compressors 21a, 21b down to the rotation number X, drive the compressors 21a, 21b while maintaining the rotation number X until the given time. For example, as described above, since the rotation number X is 46 rps when the open-air temperature T is 0° C. and thus 12 seconds are necessary to reduce the rotation number down to this rotation number, CPUs 110a, 110b drive the compressors 21a, 21b at 46 rps for the remaining thirteen seconds. Here, since, when the open-air temperature is −10° C. or lower, the rotation number X is 70 rps or the start time rotation number, CPUs 110a, 110b drive the compressors 21a, 21b for a given time (25 seconds) while maintaining 70 rps.

[Third Start Control]

CPUs 110a, 110b start the third start control following the second start control. The execution of the first start control has relieved the refrigerant dissolution in the compressors 21a, 21b to a certain degree to thereby provide such amount of discharge of refrigerating machine oil as cannot interfere with the lubrication of the compressors 21a, 21b. Also, the execution of the second start control has reduced the discharge pressures of the compressors 21a, 21b. In the third start control, while decreasing the refrigerant dissolution amount in the compressors 21a, 21b and controlling the discharge pressures of the compressors 21a, 21b not to exceed the upper limit values thereof, there are executed various kinds of control for shortening the rising time of the air conditioning capacity.

Therefore, in the first and second start control, two outdoor heat exchangers are controlled to differ in function, whereby an evaporator and a condenser are intermingled within the outdoor unit. On the other hand, in the third start control, when the operation mode is a heating operation or a heating-based operation, both outdoor heat exchangers are controlled to function as evaporators and, for a cooling operation or a cooling-based operation, they are controlled to function as condensers.

Next, description will be given of the specific operations of the respective composing elements of the outdoor units 2a, 2a when executing the third start control. In this embodiment, in order for the air conditioning apparatus 1 to carry out a heating operation, CPU 110a, 110b, in the third start control, as shown in FIG. 7, execute the rotation number control of the compressors 21a, 21b, the function switching (switching from condenser to evaporator. Since the first outdoor heat exchangers 24a, 24b are controlled to function as evaporators in the first and second start control, they are maintained in state) control of the second outdoor heat exchangers 25a, 25b, the valve opening rate control of the first outdoor expansion valves 40a, 40b and second outdoor expansion valves 41a, 41b, and the opening/closing control of the first electromagnetic valves 42a, 42b and second electromagnetic valves 43a, 43b.

The above-mentioned kinds of control except for the rotation number control of the compressors 21a, 21b are similar to those of the second start control in the first embodiment including the end condition and, therefore, the description thereof is omitted here. Thus, the rotation number control of the compressors 21a, 21b will be described below specifically. Here, the state of the refrigerant circuit of the air conditioning apparatus 1 when executing the third start control is similar to the state for the second start control in the first embodiment, or, the state shown in FIG. 4.

CPUs 110a, 110b, when starting the third start control, execute the control to return the rotation numbers of the compressors 21a, 21b to 70 rps or the start time rotation number. Specifically, CPUs 110a, 110b increase gradually the rotation number of the compressors 21a, 21b up to 70 rps at a given rate and, after reaching 70 rps, drive on the compressors 21a, 21b until the end of the third start control while maintaining this rotation number (70 rps).

Here, a given rate, at which the rotation numbers of the compressors 21a, 21b are increased, is a rate so determined to be able to prevent the discharge outputs of the compressors 21a, 21b from exceeding their upper limit values when the rotation numbers of the compressors 21a, 21b are increased suddenly. For example, in the case that, when the given rate for increasing the rotation numbers of the compressors 21a, 21b is 10 rps/30 sec. and, in the second start control, the open-air temperature T is 7° C., the rotation numbers of the compressors 21a, 21b have been reduced down to the rotation number X: 30 rps corresponding to such open-air temperature T, time necessary for the rotation numbers of the compressors 21a, 21b to increase from 30 rps to 70 rps is 120 seconds ((70 rps−30 rps)/10 rps)×30 seconds=120 seconds).

As described above, by gradually increasing the rotation numbers of the compressors 21a, 21b up to 70 rps, the discharge outputs of the compressors 21a, 21b are prevented from exceeding their upper limit values. Here, as described above, the end condition of the third start control is the same as that of the second start control in the first embodiment. Thus, when the end condition of the third start control holds, CPU 110a, 110b end the start control of the air conditioning apparatus 1 and move to their normal air conditioning control.

Next, description will be given below of the flow of processings to be executed by the air conditioning apparatus 1 of this embodiment with reference to a flow chart shown in FIG. 9. The flow chart of FIG. 9 shows the flow of processings relating to the first control, second control and third start control to be executed when the air conditioning apparatus 1 starts its operation, while ST designates “step” and a numeral following ST a step number. Here, in FIG. 9, description is given mainly of processings relating to this invention and thus the description of other ordinary processings such as the control of the refrigerant circuit corresponding to the operation conditions such as a set temperature and air amount instructed by a user is omitted. Also, since the first, second and third start control to be executed by CPU 110a, 110b are the same, in the following description, description will be given of processings relating to the first, second and third start control to be executed by CPU 110a provided in the controller 100a of the outdoor unit 2a.

On receiving an operation start instruction, CPU 110a checks whether the start condition of the first start control holds or not (ST21). When it holds (ST21-Yes), CPU 110a controls the first three-way valve 22a to allow the first outdoor heat exchanger 24a to function as an evaporator and controls the second three-way valve 23a to allow the second outdoor heat exchanger 25a to function as an evaporator (ST22).

Next, CPU 110a controls the compressor 21a to start at the start time rotation number, or, to drive it on at the start time rotation number (ST23).

Next, CPU 110a opens the first electromagnetic valve 42a (ST25) to thereby allow the refrigerant to flow in the hot gas bypass 36a. Here, as described in the first embodiment, the second electromagnetic valve 43a has been opened since the stopping time of the outdoor unit 2a and CPU 110a maintains this state to allow the refrigerant to flow in the oil return pipe 37a.

Next, CPU 110a checks whether the end condition of the first start control holds or not (ST26). When not (ST26-No), CPU 110a returns the processing to ST22 and continues the first start control.

When the end condition holds (ST26-Yes), CPU 110a ends the first start control and moves to the second start control. CPU 110a imports, of open-air temperatures detected by the open-air temperature sensor 58a and stored in the memory portion 120a, the open-air temperature T finally stored from the memory portion 120a (ST27).

Next, CPU 110a checks whether the imported open-air temperature T is −10° C. or lower or not (ST28). When it is −10° C. or lower (ST28-Yes), since it is not necessary to reduce the rotation number of the compressor 21a (see the rotation number table 200 of FIG. 8), CPU 110a advances the processing to ST31.

When not (ST28-No), CPU 110a refers to the rotation table 200 stored in the memory portion 120a and extracts the rotation number X corresponding to the imported open-air temperature T (ST29). And, CPU 110a reduces the rotation number of the compressor 21a down to the extracted rotation number X (ST30).

Next, CPU 110a checks whether the end condition of the second start control holds or not (ST31). When not (ST31-No), CPU 110a returns the processing to ST27.

When it holds (ST31-Yes), CPU 110a ends the second start control and moves to the third start control. CPU 110a checks whether an operation mode instructed by a user is a heating operation or a heating-based operation or not (ST32).

When it is a heating operation or a heating-based operation (ST32-Yes), CPU 110a switches the second outdoor heat exchanger 25a functioning as a condenser to function as an evaporator (ST33). Next, CPU 110a controls the valve opening rate of the first outdoor expansion valve 40a according to the refrigerant superheated degree in the refrigerant exit of the first outdoor heat exchanger 24a and controls the valve opening rate of the second outdoor expansion valve 41a according to the refrigerant superheated degree in the refrigerant exit of the second outdoor heat exchanger 25a (ST34). Next, CPU 110a returns the rotation number of the compressor 21a to the start time rotation number and drives the compressor 21a (ST35).

Next, CPU 110a starts a time after end of the second start control and checks whether a given time, for example, two minutes have passed or not since the end of the second start control (ST36). When not (ST36-No), CPU 110a returns the processing to ST32.

When a given time has passed (ST36-Yes), CPU 110a closes the first and second electromagnetic valves 42a and 43a (ST37) to thereby prevent the refrigerant from flowing in the hot gas bypass 36a and oil return pipe 37a.

Next, CPU 110a checks whether the end condition of the third start control holds or not (ST38). When not (ST38-No), CPU 110a drives on the compressor 21a at the start time rotation number (ST41) and returns the processing to ST38, thereby continuing the third start control. When the end condition holds (ST38-Yes), CPU 110a ends the third start control or ends the start control of the air conditioning apparatus 1 and starts its normal air conditioning control.

Here, in ST21, when the start condition of the first start control does not hold (ST21-No), CPU 110a does not execute the start control but starts the normal air conditioning control.

Also, in ST32, when not (ST32-No), the operation mode instructed by the user is a cooling operation or a cooling-based operation and, therefore, CPU 110a switches the first outdoor heat exchanger 24a functioning as an evaporator to function as a condenser (ST39). Next, CPU 110a opens the first outdoor expansion valve 40a fully or controls the valve opening rate thereof according to the refrigerant superheated degree in the refrigerant exit of the first outdoor heat exchanger 24a, and opens the second outdoor expansion valve 41a fully or controls the valve opening rate thereof according to the refrigerant superheated degree in the refrigerant exit of the second outdoor heat exchanger 25a (ST40). And, CPU 110a advances the processing to ST35.

In the above-described embodiment, description has been given of a case where, after the second start control is executed for a given time, the processing is moved to the third start control. However, the processing may also be moved to the third start control immediately when the rotation numbers of the compressors 21a, 21b are reduced down to the rotation number X corresponding to the open-air temperature T. For example, as described above, it takes 12 seconds to reduce the rotation numbers of the compressors 21a, 21b down to 46 rps. When the rotation numbers of the compressors 21a, 21b are reduced down to 46 rps, CPUs 110a, 110b may stop the second start control in 12 seconds and immediately move to the third start control. Also, when the open-air temperature T is −10° C. or lower and thus the rotation numbers of the compressors 21a, 21b need not be reduced (when the start time rotation number or 70 rps is maintained), CPUs 110a, 110b may not execute the second start control but, immediately after stopping the first start control, may execute the third start control.

Embodiment 3

Next, description will be given below of a third embodiment of the air conditioning apparatus of the invention. Here, since the structure and running operation of the air conditioning apparatus and the start condition of start control to be executed when the air conditioning apparatus starts are the same as those of the first embodiment, the description thereof is omitted. The third embodiment is different from the first embodiment in that, between the first and second start control in the first embodiment, there is executed control to reduce the rotation numbers of the compressors and also in that, in the second start control, the compressors are driven at the reduced rotation numbers provided by the above control to be executed between the first and second start control in the first embodiment and, during execution of the second start control, the first and second electromagnetic valves are retained opened.

Now, description will be given below of the operations of a refrigerant circuit of this embodiment and the operation effects thereof in the air conditioning apparatus 1 of this embodiment with reference to FIGS. 1 to 4, 10 and 11. Here, in the following description, similarly to the first embodiment, description will be given while taking an example where the air conditioning apparatus 1 starts its own operation and initiates the heating operation described with reference to FIG. 1 and the indoor units 8a-8e and outdoor units 2a, 2b are all operated.

In this embodiment, to solve the above problems, as shown in FIG. 10, when starting the air conditioner 1, there is executed start control including: first start control (the same control as the first start control in the first embodiment) to be executed mainly for eliminating the refrigerant dissolution within the compressors 21a and 21b to thereby reduce the amount of refrigerating oil to be discharged together with the refrigerant; second start control to be executed mainly for preventing the discharge pressures of the compressors 21a and 21b from exceeding the upper limit values thereof; and, third start control (the same control in the second start control in the first embodiment, except for the control of the rotation numbers of the compressors 21a and 21b, and the opening/closing control of the first electromagnetic valves 42a, 42b and second electromagnetic valves 43a, 43b) to be executed mainly to prevent the discharge pressures of the compressors 21a and 21b from increasing suddenly and also to switch the function of the second outdoor heat exchangers 25a and 25b from the function of a condenser to that of an evaporator.

The above-mentioned start control will be described below specifically. However, since the first start control is the same as the first start control in the first embodiment including the start condition and end condition, the description thereof is omitted here. Also, the third start control is the same as the second start control in the first embodiment except for the control of the rotation numbers of the compressors 21a and 21b, and the opening/closing control of the first electromagnetic valves 42a, 42b and second electromagnetic valves 43a, 43b to be described later. Therefore, the description of the same part of this control is omitted here. And, the following description is given assuming that the lower limit rotation number in the rotation number range allowed for the compressors 21a and 21b is 20 rps.

[Second Start Control]

Next, description will be given below of the specific operations of the respective composing elements of the outdoor units 2a, 2b when executing the second start control. CPUs 110a, 110b, in the second start control, as shown in FIG. 10, execute the rotation number control of the compressors 21a, 21b, the function switching (evaporator/condenser switching) control of the first outdoor heat exchangers 24a, 24b and second outdoor heat exchangers 25a, 25b, the valve opening rate control of the first outdoor expansion valves 40a, 40b and second outdoor expansion valves 41a, 41b, and the opening/closing control of the first electromagnetic valves 42a, 42b and second electromagnetic valves 43a, 43b.

[Third Start Control]

CPUs 110a, 110b start the third start control following the second start control. Due to execution of the first start control, the refrigerant dissolution within the compressors 21a and 21b has been eliminated to a certain degree, whereby the discharge amount of the refrigerating oil has become such amount as the refrigerating oil cannot interfere with the lubrication of the compressors 21a and 21b. Also, owing to execution of the second start control, the discharge pressures of the compressors 21a and 21b have been lowered. In the third start control, there is carried out various control in order to reduce the refrigerant dissolution within the compressors 21a and 21b and also to prevent the lowered durability of the compressors 21a and 21b caused when the discharge pressures of the compressors 21a and 21b are allowed to increase suddenly to thereby wear and deteriorate the sliding portions of the compressors 21a and 21b.

Here, in the first and second start control, the two outdoor heat exchangers are structured to differ in function from each other and the evaporator and condenser coexist within the outdoor unit. In the third start control, for the heating operation/heating-based operation, the two outdoor heat exchangers are both controlled to function as evaporators, or, for the cooling operation/cooling-based operation, the two outdoor heat exchangers are both controlled to function as condensers, thereby preparing transition to the normal operation.

Next, description will be given of the specific operations of the respective composing elements of the outdoor units 2a, 2a when executing the third start control. In this embodiment, in order for the air conditioning apparatus 1 to carry out a heating operation, CPU 110a, 110b, in the third start control, as shown in FIG. 10, execute the rotation number control of the compressors 21a, 21b, the function switching (switching from condenser to evaporator. Since the first outdoor heat exchangers 24a, 24b are controlled to function as evaporators in the first and second start control, they are maintained in state) control of the second outdoor heat exchangers 25a, 25b, the valve opening rate control of the first outdoor expansion valves 40a, 40b and second outdoor expansion valves 41a, 41b, and the opening/closing control of the first electromagnetic valves 42a, 42b and second electromagnetic valves 43a, 43b.

Of the above-mentioned control, other control than the control of the rotation number of the compressors 21a and 21b and the opening/closing control of the first electromagnetic valves 42a, 42b and second electromagnetic valves 43a, 43b is the same as the second start control in the first embodiment including the end condition. Therefore, the description thereof is omitted here and description will be given below specifically of the control of the rotation number of the compressors 21a and 21b and the opening/closing control of the first electromagnetic valves 42a, 42b and second electromagnetic valves 43a, 43b. Here, the state of the refrigerant circuit of the air conditioning apparatus 1 when executing the third start control is similar to the state for the second start control in the first embodiment, or, the state shown in FIG. 4.

CPUs 110a, 110b, after starting the third start control, as shown in FIG. 10, fix the rotation number of the compressors 21a and 21b to the rotation number X set in the second start control and drive the compressors 21a and 21b at this rotation number X until the third start control ends. Also, CPUs 110a, 110b retain the opened states of the first electromagnetic valves 42a, 42b and second electromagnetic valves 43a, 43b until the third start control ends.

In the second start control, since the rotation number of the compressors 21a and 21b is set to the rotation number X corresponding to the open-air temperature, the discharge pressures of the compressors 21a and 21b are prevented from exceeding their respective upper limit values when the second start control is switched to the third start control. However, in the third start control, the second outdoor heat exchangers 25a, 25b having functioned as condensers are switched to function as evaporators, thereby reducing the number of heat exchangers functioning as condensers. This raises a fear that the discharge pressures of the compressors 21a and 21b can increase suddenly. With such sudden increase in the discharge pressures of the compressors 21a and 21b, a large load is applied to the sliding portions of the compressors 21a and 21b. This raises a fear that the sliding portions can be worn and deteriorated to thereby lower the durability of the compressors 21a and 21b.

To solve the above problem, in the third start control, the rotation number of the compressors 21a and 21b is set to the rotation number X and the first electromagnetic valves 42a, 42b and second electromagnetic valves 43a, 43b are retained opened continuously from the first and second start control. This can prevent the discharge pressures of the compressors 21a and 21b from increasing suddenly, thereby being able to prevent the lowered durability of the compressors 21a and 21b.

Here, the end condition of the third start control is whether a given time (for example, 10 seconds) has passed since the start of the third start control or not. This given time is decided by taking into consideration the time necessary to switch the function of the second outdoor heat exchangers 25a, 25b from that of a condenser to that of an evaporator and the time necessary to slacken the increasing degree of the discharge pressures of the compressors 21a and 21b by executing the third start control when the discharge pressures of the compressors 21a and 21b are going to increase suddenly due to the reduced number of heat exchangers functioning as condensers. When the end condition of the third start control holds, CPUs 110a, 110b end the start control of the air conditioner 1 and moves to the normal air conditioning control.

Next, description will be given below of the flow of processings to be executed by the air conditioning apparatus 1 of this embodiment with reference to a flow chart shown in FIG. 11. The flow chart of FIG. 11 shows the flow of processings relating to the first control, second control and third start control to be executed when the air conditioning apparatus 1 starts its operation, while ST designates “step” and a numeral following ST a step number. Here, in FIG. 11, description is given mainly of processings relating to this invention and thus the description of other ordinary processings such as the control of the refrigerant circuit corresponding to the operation conditions such as a set temperature and air amount instructed by a user is omitted. Also, since the first, second and third start control to be executed by CPU 110a, 110b are the same, in the following description, description will be given of processings relating to the first, second and third start control to be executed by CPU 110a provided in the controller 100a of the outdoor unit 2a.

On receiving an operation start instruction, CPU 110a checks whether the start condition of the first start control holds or not (ST 121). When it holds (ST 121-Yes), CPU 110a controls the first three-way valve 22a to allow the first outdoor heat exchanger 24a to function as an evaporator and controls the second three-way valve 23a to allow the second outdoor heat exchanger 25a to function as an evaporator (ST 122).

Next, CPU 110a controls the compressor 21a to start at the start time rotation number, or, to drive it on at the start time rotation number (ST 123).

Next, CPU 110a opens the first electromagnetic valve 42a (ST 125) to thereby allow the refrigerant to flow in the hot gas bypass 36a. Here, as described in the first embodiment, the second electromagnetic valve 43a has been opened since the stopping time of the outdoor unit 2a and CPU 110a maintains this state to allow the refrigerant to flow in the oil return pipe 37a.

Next, CPU 110a checks whether the end condition of the first start control holds or not (ST 126). When not (ST 126-No), CPU 110a returns the processing to ST 122 and continues the first start control.

When the end condition holds (ST 126-Yes), CPU 110a ends the first start control and moves to the second start control. CPU 110a imports, of open-air temperatures detected by the open-air temperature sensor 58a and stored in the memory portion 120a, the open-air temperature T finally stored from the memory portion 120a (ST 127).

Next, CPU 110a checks whether the imported open-air temperature T is −10° C. or lower or not (ST 128). When it is −10° C. or lower (ST 128-Yes), since it is not necessary to reduce the rotation number of the compressor 21a (see the rotation number table 200 of FIG. 8), CPU 110a advances the processing to ST 131.

When not (ST 128-No), CPU 110a refers to the rotation table 200 stored in the memory portion 120a and extracts the rotation number X corresponding to the imported open-air temperature T (ST 129). And, CPU 110a reduces the rotation number of the compressor 21a down to the extracted rotation number X (ST 130).

Next, CPU 110a checks whether the end condition of the second start control holds or not (ST 131). When not (ST 131-No), CPU 110a returns the processing to (ST 127).

When it holds (ST 131-Yes), CPU 110a ends the second start control and moves to the third start control. CPU 110a checks whether an operation mode instructed by a user is a heating operation or a heating-based operation or not (ST 132).

When it is a heating operation or a heating-based operation (ST 132-Yes), CPU 110a switches the second outdoor heat exchanger 25a functioning as a condenser to function as an evaporator (ST 133). Next, CPU 110a controls the valve opening rate of the first outdoor expansion valve 40a according to the refrigerant superheated degree in the refrigerant exit of the first outdoor heat exchanger 24a and controls the valve opening rate of the second outdoor expansion valve 41a according to the refrigerant superheated degree in the refrigerant exit of the second outdoor heat exchanger 25a (ST 134).

Next, CPU 110a checks whether the end condition of the third start control holds or not (ST 135). When not (ST 135-No), CPU 110a drives the compressor 21a with the rotation number X maintained (ST 139) and returns the processing to ST 135.

When the end condition of the third start control holds (ST 135-Yes), CPU 110a closes the first electromagnetic valve 42a and second electromagnetic valve 43a (ST 136) to prevent a refrigerant from flowing in the hot gas bypass pipe 36a and oil return pipe 37a, thereby ending the third start control, that is, ending the start control of the air conditioner 1 and starting the normal air conditioning control.

Next, CPU 110a checks whether the end condition of the third start control holds or not (ST 138). When not (ST 138-No), CPU 110a drives on the compressor 21a at the start time rotation number (ST 141) and returns the processing to ST 138, thereby continuing the third start control. When the end condition holds (ST 138-Yes), CPU 110a ends the third start control or ends the start control of the air conditioning apparatus 1 and starts its normal air conditioning control.

Here, in ST 121, when the start condition of the first start control does not hold (ST 121-No), CPU 110a does not execute the start control but starts the normal air conditioning control.

Also, in ST 132, when not (ST 132-No), the operation mode instructed by the user is a cooling operation or a cooling-based operation and, therefore, CPU 110a switches the first outdoor heat exchanger 24a functioning as an evaporator to function as a condenser (ST 139). Next, CPU 110a opens the first outdoor expansion valve 40a fully or controls the valve opening rate thereof according to the refrigerant superheated degree in the refrigerant exit of the first outdoor heat exchanger 24a, and opens the second outdoor expansion valve 41a fully or controls the valve opening rate thereof according to the refrigerant superheated degree in the refrigerant exit of the second outdoor heat exchanger 25a (ST 140). And, CPU 110a advances the processing to (ST 135).

As described above, according the air conditioning apparatus of the invention, even when the compressors are driven on at a given rotation number in order to eliminate the refrigerant dissolution of the compressors early, by controlling part of the outdoor heat exchangers to function as a condenser, an increase in the discharge side (high pressure side) pressure of the compressor can be prevented. This can prevent the increased internal pressure of the compressor and thus can prevent the occurrence of refrigerant dissolution caused by the increased internal pressure of the compressor. Also, after end of the first start control, while the outdoor heat exchangers are all controlled to function as condensers or evaporators according to the operation mode of the normal air conditioning operation, the compressors are driven on at the same given rotation numbers as those in the first start control execution. This enables the air conditioning capacity to rise quickly.

Number	Date	Country	Kind
2011-216556	Sep 2011	JP	national
2012-079427	Mar 2012	JP	national
2012-162230	Jul 2012	JP	national

AIR CONDITIONING APPARATUS

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