JP2007232265A - Refrigeration unit - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To prevent deterioration of a heating capacity when heat amount of cooling heat exchangers exceed a necessary heat amount of an indoor heat exchanger. <P>SOLUTION: The refrigeration unit 1 is provided with a coolant circuit 1E connecting a compressor 2, an outdoor heat exchanger 4, an expansion mechanism, the indoor heat exchanger 41 for air-conditioning the indoors, and the cooling heat exchangers 45, 51 for cooling a chamber interior. The coolant circuit 1E is provided with a discharge side three-way valve 101 varying flow rates of a coolant distributed to the indoor heat exchanger 41 and the outdoor heat exchanger 4, of coolant discharged from the compressor 2. A distribution control part 82 is provided for controlling the discharge side three-way valve 101 to adjust the flow rates of the coolant distributed to the indoor heat exchanger 41 and the outdoor heat exchanger 4 such that a temperature difference between an indoor air temperature and a set indoor temperature becomes a predetermined value, during second heating/refrigeration operation using both the indoor heat exchanger 41 and the outdoor heat exchanger 4 as condensers. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

    The present invention relates to a refrigeration apparatus, and particularly relates to a refrigeration apparatus including an air conditioning heat exchanger and a cooling heat exchanger.

    Conventionally, a refrigeration apparatus that performs a refrigeration cycle is known, and is widely used as an air conditioner that cools and heats a room and a refrigerator such as a refrigerator that stores food. Some of these refrigeration apparatuses perform both air conditioning and refrigeration. For example, the refrigeration apparatus includes a plurality of use side heat exchangers such as an air conditioning heat exchanger and a cooling heat exchanger, and is installed in a convenience store. This refrigeration apparatus can perform both air conditioning in a store and cooling of a showcase, etc. by installing only one refrigeration apparatus (see, for example, Patent Documents 1 and 2).

In the conventional refrigeration apparatus, the amount of heat absorbed by a cooling heat exchanger such as a showcase can be effectively utilized by the air conditioning heat exchanger during heating of the air conditioning.
Japanese Patent No. 3253283 JP 2003-75022 A

    However, in the conventional refrigeration apparatus, when the amount of heat absorbed by the cooling heat exchanger exceeds the amount of heat necessary for the air conditioning heat exchanger, the discharge pressure of the compressor of the refrigerant circuit of the refrigeration apparatus becomes too high, so excess heat Need to be discharged. In such a case, conventionally, the refrigerant flow direction is switched by a four-way switching valve provided in the discharge pipe of the compressor, the refrigerant on the discharge side of the compressor is caused to flow to the heat source side heat exchanger, and excess heat is discharged. . At this time, since the refrigerant flow direction is simply switched by the four-way switching valve, the flow rate of the refrigerant flowing to the heat source side heat exchanger cannot be finely adjusted, and the discharge pressure of the compressor is lowered too much to lower the heating capacity. However, there was a problem that comfortable air conditioning could not be performed.

    The present invention has been made in view of the above points, and the object of the present invention is to provide a compressor discharge pressure when the amount of heat obtained by the cooling heat exchanger exceeds the amount of heat necessary for the air conditioning heat exchanger. It is to discharge the excess heat without lowering too much.

    In order to achieve the above object, the present invention provides a flow rate adjusting means that adjustably distributes the refrigerant discharged from the compressor (2) to the heat source side heat exchanger (4) and the air conditioning heat exchanger (41). (101, 104) and distribution control means (82) for controlling the distribution amount are provided.

    Specifically, the first invention relates to a compressor (2), a heat source side heat exchanger (4), an expansion mechanism (46, 52, 104), and an air conditioning heat exchanger (41) for air conditioning a room. ) And a cooling heat exchanger (45, 51) for cooling the inside of the refrigerator is a refrigeration apparatus including a refrigerant circuit (1E). In the refrigerant circuit (1E), the flow rate of the refrigerant discharged from the compressor (2) and distributed to the air conditioning heat exchanger (41) and the heat source side heat exchanger (4) is made variable. Flow rate adjusting means (101, 104) is provided. In addition, during the heat recovery operation in which both the air conditioning heat exchanger (41) and the heat source side heat exchanger (4) are condensers, the temperature difference between the indoor air temperature and the set indoor temperature becomes a predetermined value. Distributing control means (82) for controlling the flow rate adjusting means (101, 104) for adjusting the flow rate of the refrigerant distributed to the air conditioning heat exchanger (41) and the heat source side heat exchanger (4). ing.

    The second invention also includes a compressor (2), a heat source side heat exchanger (4), an expansion mechanism (46, 52, 104), and an air conditioning heat exchanger (41) for air conditioning the room. The refrigeration apparatus includes a refrigerant circuit (1E) connected to a cooling heat exchanger (45, 51) for cooling the inside of the refrigerator. In the refrigerant circuit (1E), the flow rate of the refrigerant discharged from the compressor (2) and distributed to the air conditioning heat exchanger (41) and the heat source side heat exchanger (4) is made variable. Flow rate adjusting means (101, 104) is provided. In addition, during the heat recovery operation in which both the air conditioning heat exchanger (41) and the heat source side heat exchanger (4) are condensers, the refrigerant circuit (1E) has a high pressure refrigerant pressure and the refrigerant circuit (1E) liquid The flow rate adjusting means (101, 104) is controlled to adjust the flow rate of the refrigerant distributed to the air conditioning heat exchanger (41) and the heat source side heat exchanger (4) so that the refrigerant temperature becomes a predetermined value. The distribution control means (82) is provided.

    That is, in the first and second inventions, the cooling heat exchanger (45, 51) absorbs the heat recovery operation in which both the air conditioning heat exchanger (41) and the heat source side heat exchanger (4) are condensers. When the amount of heat generated exceeds the amount of heat necessary for the air conditioning heat exchanger (41), the discharge pressure of the compressor (2) of the refrigerant circuit (1E) becomes too high, so that excess heat needs to be discharged. At this time, the flow rate adjusting means (101, 104) adjusts the compressor (2) according to the balance between the amount of heat absorbed by the cooling heat exchanger (45, 51) and the amount of heat necessary for the air conditioning heat exchanger (41). ) Is distributed to the air conditioning heat exchanger (41) and the heat source side heat exchanger (4) in an appropriate amount.

    In the first invention, the distribution control means (82) adjusts the flow rate of the refrigerant distributed to the air conditioning heat exchanger (41) and the heat source side heat exchanger (4) to set the indoor air temperature. The flow rate adjusting means (101, 104) is controlled so that the temperature difference from the room temperature becomes a predetermined value.

    In the second invention, the distribution control means (82) adjusts the flow rate of the refrigerant distributed to the air conditioning heat exchanger (41) and the heat source side heat exchanger (4) to adjust the refrigerant circuit (1E The flow rate adjusting means (101, 104) is controlled such that the high-pressure refrigerant pressure of (1) or the liquid refrigerant temperature of the refrigerant circuit (1E) becomes a predetermined value.

    Further, the third invention is the above-described first or second invention, in the heat recovery operation in which only the air conditioning heat exchanger (41) serves as a condenser, the air conditioning heat exchanger (41), and the heat source side heat exchanger. In the heat recovery operation in which both of (4) are condensers, the refrigerant circuit (45, 51) is adjusted so that the difference between the refrigerant temperature of the cooling heat exchanger (45, 51) and the set internal temperature becomes a predetermined value. 1E) capacity control means (81) for controlling the refrigeration capacity.

    In addition, the fourth invention is the above-described first or second invention, in the heat recovery operation in which only the air conditioning heat exchanger (41) serves as a condenser, the air conditioning heat exchanger (41), and the heat source side heat exchanger. When the heat recovery operation in which both of (4) are condensers, the temperature difference between the refrigerant pressure equivalent saturation temperature of the cooling heat exchanger (45, 51) and the set internal temperature becomes a predetermined value. A capacity control means (81) for controlling the refrigerating capacity of the refrigerant circuit (1E) is provided.

    Further, the fifth invention is the above-described first or second invention, in the heat recovery operation in which only the air conditioning heat exchanger (41) serves as a condenser, the air conditioning heat exchanger (41), and the heat source side heat exchanger. In the heat recovery operation in which both of (4) are condensers, the refrigerant circuit is configured so that the difference between the intake air temperature of the cooling heat exchanger (45, 51) and the set internal temperature becomes a predetermined value. A capacity control means (81) for controlling the refrigerating capacity of (1E) is provided.

    That is, in the third to fifth inventions, since the low pressure refrigerant pressure of the cooling heat exchanger (45, 51) is important, the capacity control means (81) controls the refrigeration capacity of the refrigerant circuit (1E). To do.

    Specifically, in the third aspect of the invention, the capacity control means (81) causes the refrigerant circuit (1E) so that the difference between the refrigerant temperature of the cooling heat exchanger (45, 51) and the set internal temperature becomes a predetermined value. ) To control. For example, the refrigerant temperature Te of the cooling heat exchanger (45, 51) is set to be 10 ° lower than the set internal temperature Tset (Tset−Te = 10).

    In the fourth aspect of the invention, the capacity control means (81) causes the refrigerant circuit so that the temperature difference between the refrigerant pressure equivalent saturation temperature of the cooling heat exchanger (45, 51) and the set internal temperature becomes a predetermined value. Control (1E). For example, the saturation temperature corresponding to the refrigerant pressure Pe of the cooling heat exchanger (45, 51) is set to be 10 ° lower than the set internal temperature Tset (equivalent saturation temperature of Tset−Pe = 10).

    In the fifth aspect of the invention, the capacity control means (81) allows the refrigerant circuit (1E) so that the difference between the intake air temperature of the cooling heat exchanger (45, 51) and the set internal temperature becomes a predetermined value. ) For example, the intake air temperature Tr of the cooling heat exchanger (45, 51) is set to the set internal temperature Tset (Tset−Tr = 0).

    Further, a sixth invention is configured such that, in any one of the fourth to sixth inventions, the capacity control means (81) controls the capacity of the compressor (2).

    Further, according to a seventh invention, in any one of the fourth to sixth inventions, an auxiliary passage (90) for bypassing the refrigerant on the discharge side and the suction side of the compressor (2) is provided, The capacity control means (81) is configured to control the refrigerant flow rate in the auxiliary passage (90).

    Further, according to an eighth invention, in any one of the fourth to sixth inventions, the capacity control means (81) is configured such that the air volume of the cooling fan (47, 58) of the cooling heat exchanger (45, 51). Is configured to control.

    That is, in the sixth to eighth inventions, the refrigeration capacity of the refrigerant circuit (1E) is controlled by the capacity of the compressor (2), the amount of bypass refrigerant, or the air volume of the cooling fans (47, 58).

    Further, the ninth invention is the air conditioning heat exchanger (41) and the heat source side heat exchanger from the heat recovery operation in which only the air conditioning heat exchanger (41) is a condenser in the first or second invention. The auxiliary control means (83) for increasing the air volume of the air-conditioning fan (43) of the air-conditioning heat exchanger (41) is provided before switching to the heat recovery operation in which both of (4) are condensers.

    That is, in the ninth aspect of the invention, the air volume of the air conditioning fan (43) is increased when the heating capacity is excessive.

    The tenth invention is the air conditioning heat exchanger (41) and the heat source side heat exchanger from the heat recovery operation in which only the air conditioning heat exchanger (41) serves as a condenser in the first or second invention. The auxiliary control means (83) for operating the indoor ventilation fan is provided before switching to the heat recovery operation in which both of (4) become a condenser.

    In other words, in the tenth aspect of the invention, the ventilation fan is operated when the heating capacity is excessive.

    As described above, in the first and second inventions described above, the flow rate adjusting means (101) converts the refrigerant discharged from the compressor (2) into the air conditioning heat exchanger (41) and the heat source side heat exchanger (4 ) And adjusting the flow rate. For this reason, of the amount of heat absorbed by the cooling heat exchanger (45, 51) during the heat recovery operation, only the amount of heat necessary for the air conditioning heat exchanger (41) is supplied to the air conditioning heat exchanger (41), and the excess heat amount Can be discharged by the heat source side heat exchanger (4).

    Therefore, since the discharge refrigerant pressure of the compressor (2) is not lowered too much, comfortable air conditioning can be performed.

    Moreover, since the heat absorbed by the cooling heat exchanger (45, 51) can be recovered appropriately, the thermal efficiency can be significantly improved.

    In addition, since the refrigerant distribution amount between the air conditioning heat exchanger (41) and the heat source side heat exchanger (4) is controlled, the capacity of the air conditioning heat exchanger (41) can be finely adjusted, so it is more comfortable. Air conditioning can be performed.

    Moreover, since the said 3rd-8th invention controls the refrigerating capacity of the refrigerant circuit (1E) at the time of heat recovery operation, the low-pressure refrigerant pressure of the cooling heat exchanger (45, 51) is reliably maintained at a predetermined value. Therefore, the capability of the cooling heat exchanger (45, 51) can be surely exhibited.

    In the ninth and tenth aspects of the invention, the heat recovery operation in which only the air conditioning heat exchanger (41) serves as a condenser can be continued as much as possible.

    Hereinafter, embodiments of the present invention will be described with reference to the drawings.

Embodiment 1
As shown in FIG. 1, the refrigeration apparatus (1) according to the present embodiment is provided in a convenience store or a supermarket, and cools a showcase (not shown) that is in a warehouse and air-conditions in a store that is indoors. Is for.

    The refrigeration apparatus (1) includes an outdoor unit (1A), an indoor unit (1B), a refrigeration unit (1C), and a refrigeration unit (1D), and includes a refrigerant circuit (1E) that performs a vapor compression refrigeration cycle. ing. The refrigerant circuit (1E) includes a booster unit (1F). The refrigerant circuit (1E) includes a first system side circuit for refrigeration and freezing, and a second system side circuit for air conditioning. The refrigerant circuit (1E) is configured to switch between a cooling cycle and a heating cycle.

    The indoor unit (1B) is configured to perform switching between a cooling operation and a heating operation, and is installed in a sales floor, for example. The refrigeration unit (1C) is installed in a refrigerated showcase to cool the air in the showcase. The refrigeration unit (1D) is installed in a freezer showcase to cool the air in the showcase.

<Outdoor unit>
The outdoor unit (1A) includes an inverter compressor (2), a four-way switching valve (3A), a discharge side three-way switching valve (101) as a flow rate adjusting means, a suction side three-way switching valve (102), An outdoor heat exchanger (4), which is a heat source side heat exchanger, and an economizer heat exchanger (103) are provided.

    The inverter compressor (2) is constituted by, for example, a hermetic screw compressor, and the electric motor is inverter-controlled so that the capacity is variable stepwise or continuously. The discharge pipe (5) of the inverter compressor (2) is connected to the first port of the discharge side three-way switching valve (101). The operation capacity control of the inverter compressor (2) is always controlled so that the refrigerant pressure on the first system side circuit side is constant. During the heat recovery operation in which the indoor heat exchanger (41) and the outdoor heat exchanger (4) are condensers, the pressure in the indoor heat exchanger (41) is controlled to be constant. The inverter compressor (2) may be a scroll compressor.

    The gas side end (inverter compressor (2) side end) of the outdoor heat exchanger (4) is a pipe extending from the second port of the discharge side three-way switching valve (101) by the outdoor gas pipe (9). And a pipe connection extending from the second port of the four-way selector valve (3A). At the liquid side end of the outdoor heat exchanger (4), there is provided a heating expansion valve (104) consisting of an electric expansion valve whose opening degree can be adjusted. Further, the heating expansion valve (104) is connected to a liquid line. One end of a certain first liquid pipe (10a) and one end of the second liquid pipe (10b) are connected. In the heating expansion valve (104), the refrigerant is decompressed during heating when the outdoor heat exchanger (4) serves as an evaporator. The control is performed based on the suction heating degree of the inverter compressor (2) obtained by the suction temperature sensor (67) described later. The first liquid pipe (10a) is connected to the receiver (14) inlet. A first flow path (105) of the economizer heat exchanger (103) is connected to the second liquid pipe (10b).

    The outdoor heat exchanger (4) is, for example, a cross fin type fin-and-tube heat exchanger, and an outdoor fan (4F), which is a heat source fan, is disposed close to the outdoor heat exchanger (4).

    The suction pipe (6) of the inverter compressor (2) is connected to the first port of the suction side three-way switching valve (102). The third port of the suction side three-way switching valve (102) is connected to the low pressure gas pipe (15) via the closing valve (20).

    The first port of the four-way switching valve (3A) is connected to a pipe extending from the third port of the discharge side three-way switching valve (101) and a connection portion of a communication pipe (21) described later. A pipe extending from the third port of the four-way switching valve (3A) is connected to the second port of the suction side three-way switching valve (102). A communication gas pipe (17) is connected to a pipe extending from the fourth port of the four-way switching valve (3A) via a closing valve (20).

    The four-way switching valve (3A) includes a pipe extending from the third port of the discharge side three-way switching valve (101), a connection portion of the communication pipe (21) and the communication gas pipe (17), and an outdoor gas pipe. (9) and the ON state in which the connection portion of the pipe extending from the second port of the discharge side three-way switching valve (101) communicates with the pipe extending from the second port of the suction side three-way switching valve (102) (see the solid line in FIG. 2) And the pipe extending from the third port of the discharge side three-way switching valve (101) and the connection part of the communication pipe (21) and the outdoor gas pipe (9) communicate with each other, and the communication gas pipe (17) and the suction side three-way switching The valve (102) is configured to be switched to an OFF state (see a broken line in FIG. 2) in which a pipe extending from the second port communicates.

    The communication gas pipe (17), the low pressure gas pipe (15), and the connecting liquid pipe (19) are extended from the outdoor unit (1A) to the outside, and the shutoff valve (20) is provided in the outdoor unit (1A). Is provided.

    The economizer heat exchanger (103) includes a first channel (105) and a second channel (106). The pipe extending from one end of the first flow path (105) is connected to the outlet of the receiver (14), and the other end is connected to the connection portion of the pipe extending from the connection liquid pipe (19) and the inlet of the receiver (14). ing. One end of the second flow path (106) is connected to an intermediate pressure portion (not shown) of the inverter compressor (2) via a check valve (7), and the other end is an electric expansion valve for economizer (107). Is connected to a pipe connection extending from the inlet of the receiver (14) toward the connection liquid pipe (19). With this configuration, the liquid refrigerant that has come out from the outlet of the receiver (14) once passes through the first flow path (105) of the economizer heat exchanger (103), and then is electrically expanded for the economizer. After being depressurized by the valve (107) and being supercooled in a low pressure state by the refrigerant in the first flow path (105) while passing through the second flow path (106), the low pressure refrigerant is converted into the inverter compressor (2 ) Is led to an intermediate pressure part. The control of the economizer electric expansion valve (107) is performed in accordance with the degree of supercooling and the refrigerant temperature of the discharge pipe (5) of the inverter compressor (2). The check valve (7) prevents the refrigerant from flowing back from the intermediate pressure portion of the inverter compressor (2). The supercooled low-pressure refrigerant is guided to the intermediate pressure portion of the inverter compressor (2), thereby preventing the inverter compressor (2) from being overheated.

    Check valves (7) are respectively provided on the first liquid pipe (10a) side at the inlet of the receiver (14) and the first flow path (105) side of the economizer heat exchanger (103), The refrigerant is configured to flow only toward the inlet of the receiver (14). Further, a condensing pressure adjusting valve (108) is provided between the pipe extending from the inlet of the receiver (14) and the first flow path (105) side of the economizer heat exchanger (103). The condensation pressure regulating valve (108) prevents the refrigerant shortage in the first system side circuit when the outside air temperature is low during heating operation.

    A pipe extending from the first port of the four-way switching valve (3A) and a pipe connecting part extending from the third port of the discharge side three-way switching valve (101) and a connecting liquid pipe (19) extend from the connection liquid pipe (19) toward the receiver (14). A communication pipe (21) as an auxiliary line is connected between the pipes. The communication pipe (21) is provided with a spring check valve (109). The spring check valve (109) does not normally operate and is configured to prevent liquid leakage when each valve is closed when the receiver (14) is full of liquid refrigerant when operation is stopped. Yes.

<Indoor unit>
The indoor unit (1B) includes an indoor heat exchanger (41) and an indoor expansion valve (42) that is an expansion mechanism. A communication gas pipe (17) is connected to the gas side of the indoor heat exchanger (41). On the other hand, the second communication liquid pipe (12) is connected to the liquid side of the indoor heat exchanger (41) via the indoor expansion valve (42), and the second communication liquid pipe (12) is connected to the outdoor unit (1A). ) Is connected to the connecting liquid pipe (19). The indoor heat exchanger (41) is, for example, a cross fin type fin-and-tube heat exchanger, and an indoor fan (43), which is an air conditioning fan, is disposed close to the indoor heat exchanger (41). Further, although only one indoor unit (1B) is shown in FIG. 1, a plurality of indoor units (1B) may be connected in parallel to each other.

<Refrigerated unit>
The refrigeration unit (1C) includes a refrigeration heat exchanger (45) that is a cooling heat exchanger and a refrigeration expansion valve (46) that is an expansion mechanism. The liquid side of the refrigeration heat exchanger (45) is connected to the first communication liquid pipe (11) via a solenoid valve (7a) and a refrigeration expansion valve (46). On the other hand, a low-pressure gas pipe (15) is connected to the gas side of the refrigeration heat exchanger (45).

    The refrigeration heat exchanger (45) communicates with the third port of the suction side three-way switching valve (102) via the low pressure gas pipe (15), while the indoor heat exchanger (41) communicates during the cooling operation. It communicates with the second port of the suction side three-way switching valve (102) via the gas pipe (17). By adjusting the flow rate of the suction side three-way switching valve (102), the refrigerant pressure (evaporation pressure) of the refrigeration heat exchanger (45) becomes lower than the refrigerant pressure (evaporation pressure) of the indoor heat exchanger (41). As a result, the refrigerant evaporation temperature of the refrigeration heat exchanger (45) is, for example, −10 ° C., and the refrigerant evaporation temperature of the indoor heat exchanger (41) is, for example, + 5 ° C., so that the refrigerant circuit (1E) It forms a circuit for different temperature evaporation.

    The refrigeration expansion valve (46) is a temperature-sensitive expansion valve, and a temperature-sensitive cylinder is attached to the gas side of the refrigeration heat exchanger (45). The refrigeration heat exchanger (45) is, for example, a cross-fin type fin-and-tube heat exchanger, and a refrigeration fan (47), which is a cooling fan, is disposed close to the refrigeration heat exchanger (45).

<Refrigeration unit>
The refrigeration unit (1D) includes a refrigeration heat exchanger (51) that is a cooling heat exchanger and a refrigeration expansion valve (52) that is an expansion mechanism. On the liquid side of the refrigeration heat exchanger (51), a branch liquid pipe (13) branched from the first communication liquid pipe (11) is connected via a solenoid valve (7b) and a refrigeration expansion valve (52). .

    The refrigeration expansion valve (52) is a temperature-sensitive expansion valve, and a temperature-sensitive cylinder is attached to the gas side of the refrigeration heat exchanger (51). The refrigeration heat exchanger (51) is, for example, a cross-fin type fin-and-tube heat exchanger, and a refrigeration fan (58) that is a cooling fan is disposed close to the refrigeration heat exchanger (51).

<Booster unit>
The booster unit (1F) includes a booster compressor (53) and a supercooling heat exchanger (210).

    The booster compressor (53) is configured to supply refrigerant to and from the inverter compressor (2) so that the refrigerant evaporation temperature of the refrigeration heat exchanger (51) is lower than the refrigerant evaporation temperature of the refrigeration heat exchanger (45). The stage is compressed. The refrigerant evaporation temperature of the refrigeration heat exchanger (51) is set to, for example, −40 ° C.

    The gas side of the refrigeration heat exchanger (51) and the suction side of the booster compressor (53) are connected by a connection gas pipe (54). A branch gas pipe (16) branched from the low pressure gas pipe (15) is connected to the discharge side of the booster compressor (53). The branch gas pipe (16) is provided with a check valve (7) and an oil separator (55). An oil return pipe (57) having a capillary tube is connected between the oil separator (55) and the connection gas pipe (54).

    The connection gas pipe (54) on the suction side of the booster compressor (53) and the downstream side of the check valve (7) of the branch gas pipe (16) on the discharge side of the booster compressor (53) A bypass pipe (59) having a check valve (7) is connected between them. The bypass pipe (59) is configured so that the refrigerant flows by bypassing the booster compressor (53) when the booster compressor (53) is stopped due to a failure or the like.

    The supercooling heat exchanger (210) is a so-called plate heat exchanger. A plurality of first flow paths (211) and a plurality of second flow paths (212) are formed in the supercooling heat exchanger (210). A third communication liquid pipe (18) branches from the first communication liquid pipe (11). The first flow path (211) of the supercooling heat exchanger (210) constitutes a part of the first communication liquid pipe (11). The second channel (212) constitutes a part of the third communication liquid pipe (18).

    A supercooling expansion valve (223) is provided between the branch point of the third communication liquid pipe (18) with the first communication liquid pipe (11) and the second flow path (212). The supercooling expansion valve (223) is a temperature-sensitive expansion valve, and a temperature-sensitive cylinder is attached to the opposite side of the second flow path (212).

    The supercooling heat exchanger (210) includes a refrigerant that flows through the first channel (211) and a refrigeration that flows through the second channel (212) when the expansion valve (223) for supercooling is opened. Heat exchange is performed with the refrigerant in the device (10). The refrigerant that is supercooled through the first flow path (211) flows through the first communication liquid pipe (11) to the refrigeration heat exchanger (45) and the refrigeration heat exchanger (51). ing.

<Control system>
The refrigerant circuit (1E) is provided with various sensors and various switches. In the vicinity of the third port of the discharge side three-way switching valve (101) of the outdoor unit (1A), a high pressure sensor (61) for detecting a high pressure refrigerant pressure is provided. The inverter compressor (2) is provided with a discharge temperature sensor (62) for detecting the high-pressure refrigerant temperature.

    Near the suction pipe (6) of the inverter compressor (2), a low pressure sensor (65, 66) for detecting the low pressure refrigerant pressure and a suction temperature sensor (67) for detecting the low pressure refrigerant temperature are provided. ing.

    The outdoor unit (1A) is provided with an outdoor air temperature sensor (70) for detecting the outdoor air temperature.

    The indoor heat exchanger (41) is provided with an indoor heat exchange sensor (71) for detecting a condensation temperature or an evaporation temperature which is a refrigerant temperature in the indoor heat exchanger (41), and the gas refrigerant temperature is set on the gas side. A gas temperature sensor (72) for detection is provided. The indoor unit (1B) is provided with a room temperature sensor (73) for detecting the indoor air temperature.

    The refrigeration unit (1C) is provided with a refrigeration temperature sensor (74) for detecting the internal temperature in the refrigeration showcase. The refrigeration unit (1D) is provided with a refrigeration temperature sensor (75) for detecting the internal temperature in the showcase for refrigeration. That is, the refrigeration temperature sensor (74) and the refrigeration temperature sensor (75) are configured to detect the intake air temperature of the refrigeration heat exchanger (45) and the refrigeration heat exchanger (51).

    Output signals from the various sensors and switches are input to the controller (80) (shown only in FIG. 1). The controller (80) is configured to control the capacity of the inverter compressor (2).

    The controller (80) is configured to control the operation of the refrigerant circuit (1E) and switch between the cooling operation, the refrigeration operation, the cooling refrigeration operation, the heating operation, and the first to third heating refrigeration operations. Has been.

    Under the control of the controller (80), when the outdoor heat exchanger (4) is an evaporator, the discharge side three-way switching valve (101) is completely closed at the second port, and the refrigerant is supplied to the third port side. Everything flows. On the other hand, when the indoor heat exchanger (41) during the heating operation becomes a condenser and when the thermostat is off, the third port side is completely closed, and all the refrigerant flows to the second port side.

    Under the control of the controller (80), the third port of the suction side three-way switching valve (102) is always closed when the first system side circuit is not used, that is, when only the indoor unit (1B) is operated.

    The controller (80) includes a capacity control unit (81) that is a capacity control unit of the refrigerant circuit (1E), a distribution control unit (82) that is a refrigerant distribution control unit, and an auxiliary control unit. And an auxiliary control unit (83).

    The distribution control unit (82) detects the indoor air temperature detected by the room temperature sensor (73) during the second heating / freezing operation in which both the indoor heat exchanger (41) and the outdoor heat exchanger (4) are condensers. The flow rate of the refrigerant distributed to the indoor heat exchanger (41) and the outdoor heat exchanger (4) is adjusted so that the difference between the temperature and the set room temperature becomes a predetermined value (set value 0) set in advance. Therefore, PID control is performed on the opening amounts of the second port and the third port of the discharge side three-way switching valve (101).

    Specifically, as shown in FIG. 6, when the indoor air temperature Tr, the set indoor temperature Tset, and the differential temperature are equal to or lower than a preset value 1, the distribution control unit (82) is configured to discharge the three-way switching valve on the discharge side. The second port of (101) is fully closed, all the refrigerant discharged from the inverter compressor (2) flows to the indoor heat exchanger (41), and the first heating and refrigeration operation is performed. Further, when the indoor air temperature Tr, the set indoor temperature Tset, and the differential temperature are equal to or higher than a preset set value 2, the second port of the discharge side three-way switching valve (101) is opened, and the inverter compressor (2) The discharged refrigerant is distributed to the indoor heat exchanger (41) and the outdoor heat exchanger (4) through the second port and the third port.

    When the second port of the discharge side three-way switching valve (101) is opened, the distribution control unit (82) is configured so that the indoor air temperature Tr, the set indoor temperature Tset, and the differential temperature become the set value 0. PID control is performed on the opening amounts of the second port and the third port of the three-way switching valve (101).

    The capacity control unit (81) includes the indoor heat exchanger (41) and the outdoor heat exchanger (4) during the heat recovery operation (first heating and refrigeration operation) in which only the indoor heat exchanger (41) serves as a condenser. So that the difference between the refrigerant temperature of the refrigeration heat exchanger (45) and the set internal temperature becomes a predetermined value at the time of heat recovery operation (second heating / refrigeration operation) in which both of them become condensers The refrigerant capacity of the refrigerant circuit (1E) is controlled by controlling the capacity of the compressor (2). Specifically, the capacity control unit (81) causes the refrigerant temperature Te of the refrigeration heat exchanger (45) to be 10 ° lower than the set internal temperature Tset (Tset−Te = 10).

    The auxiliary control unit (83) includes an indoor heat exchanger (41) and an outdoor heat exchanger (4) during a heat recovery operation (during the first heating / refrigeration operation) in which only the indoor heat exchanger (41) serves as a condenser. ) Increase the air volume of the indoor fan (43) of the indoor heat exchanger (41) before switching to the heat recovery operation (second heating / refrigeration operation) in which both of them become condensers.

-Driving action-
Next, only the heating mode in which the characteristics of the present invention appear will be described among the above-described operation operations performed by the refrigeration apparatus (1).

    The heating mode is switched to any one of the heating operation, the first heating / freezing operation, the second heating / freezing operation, and the third heating / freezing operation under the control of the controller (80).

<Heating operation>
This heating operation is an operation for heating only the indoor unit (1B). Further, the four-way switching valve (3A) switches to the ON state as shown by the solid line in FIG. The second port of the discharge side three-way switching valve (101) is closed. The third port of the suction side three-way switching valve (102) is closed. Furthermore, the solenoid valve (7a) of the refrigeration unit (1C) and the solenoid valve (7b) of the refrigeration unit (1D) are closed.

    In this state, the refrigerant discharged from the inverter compressor (2) passes through the third port of the discharge side three-way switching valve (101), passes through the four-way switching valve (3A), the communication gas pipe (17), and the indoor heat. It flows into the exchanger (41) and condenses. The condensed liquid refrigerant flows through the second communication liquid pipe (12) and then flows into the receiver (14). Thereafter, the liquid refrigerant flows through the heating expansion valve (104) to the outdoor heat exchanger (4) and evaporates. The evaporated gas refrigerant returns from the outdoor gas pipe (9) to the inverter compressor (2) through the four-way switching valve (3A) and the suction side three-way switching valve (102). This circulation is repeated to heat the inside of the store.

    The opening degree of the heating expansion valve (104) is superheat controlled by the pressure equivalent saturation temperature based on the low pressure sensor (65, 66) and the temperature detected by the suction temperature sensor (67). The opening degree of the indoor expansion valve (42) is supercooled based on the temperature detected by the indoor heat exchange sensor (71). The opening control of the heating expansion valve (104) and the indoor expansion valve (42) is the same in the heating mode hereinafter.

<First heating / freezing operation>
The first heating / freezing operation is an operation for heating the indoor unit (1B) and cooling the refrigeration unit (1C) and the refrigeration unit (1D) without using the outdoor heat exchanger (4).

    As shown by the solid line in FIG. 3, the four-way selector valve (3A) is switched to the ON state. The second port of the suction side three-way switching valve (102) is open. Further, the solenoid valve (7a) of the refrigeration unit (1C) and the solenoid valve (7b) of the refrigeration unit (1D) are opened, while the heating expansion valve (104) is closed.

    Further, as a feature of the present invention, the first heating and refrigeration operation is a case where the indoor air temperature Tr, the set indoor temperature Tset, and the differential temperature are equal to or lower than a preset set value 1 as shown in FIG. Therefore, the distribution control unit (82) fully closes the second port of the discharge side three-way switching valve (101).

    In this state, the refrigerant discharged from the inverter compressor (2) is all sent to the third port side in the discharge side three-way switching valve (101). This refrigerant flows from the four-way selector valve (3A) through the communication gas pipe (17) to the indoor heat exchanger (41) and condenses. The condensed liquid refrigerant flows from the second communication liquid pipe (12) to the first communication liquid pipe (11).

    Part of the liquid refrigerant flowing through the first communication liquid pipe (11) flows through the refrigeration expansion valve (46) to the refrigeration heat exchanger (45) and evaporates. The other liquid refrigerant flowing through the first communication liquid pipe (11) flows through the branch liquid pipe (13), passes through the refrigeration expansion valve (52), flows into the refrigeration heat exchanger (51), and evaporates. The gas refrigerant evaporated in the refrigeration heat exchanger (51) is sucked into the booster compressor (53), compressed, and discharged to the branch gas pipe (16).

    The gas refrigerant evaporated in the refrigeration heat exchanger (45) and the gas refrigerant discharged from the booster compressor (53) are merged in the low-pressure gas pipe (15) and returned to the inverter compressor (2). This circulation is repeated to heat the interior of the store, and at the same time, cool the interior of the refrigerator, which is a showcase for refrigeration and a showcase for freezing. That is, the cooling capacity (evaporation heat amount) of the refrigeration unit (1C) and the refrigeration unit (1D) balances the heating capacity (condensation heat amount) of the indoor unit (1B), and 100% heat recovery is performed.

    The opening degree of the refrigeration expansion valve (46) and the refrigeration expansion valve (52) is superheat controlled by a temperature sensing cylinder and is the same in each operation hereinafter.

    In the first heating / refrigeration operation, the capacity control unit (81) is configured so that the difference between the refrigerant temperature of the refrigeration heat exchanger (45) and the set internal temperature becomes a predetermined value. ) To control the refrigerating capacity of the refrigerant circuit (1E). Specifically, the capacity control unit (81) controls the capacity of the inverter compressor (2) so that the refrigerant temperature Te of the refrigeration heat exchanger (45) is 10 ° lower than the set internal temperature Tset. (Tset−Te = 10).

    Further, as a feature of the present invention, as shown in FIG. 6, the first heating / freezing operation is performed when the indoor air temperature Tr, the set indoor temperature Tset, and the differential temperature are equal to or higher than a preset set value 2, as shown in FIG. (82) opens the second port of the discharge side three-way switching valve (101) and switches to the second heating / freezing operation, but the auxiliary control unit (83) starts the second heating / freezing operation from the time of the first heating / freezing operation. Before switching to operation, the air volume of the indoor fan (43) of the indoor heat exchanger (41) is increased. As a result, the first heating / freezing operation is continued as much as possible.

<Second heating and freezing operation>
This second heating / freezing operation is an overheating operation of heating in which the heating capacity of the indoor unit (1B) is excessive during the first heating / freezing operation.

    As shown in FIG. 4, the second heating / freezing operation is a heat recovery operation when the heating capacity is excessive during the first heating / freezing operation.

    As a feature of the present invention, the second heating and refrigeration operation is a case where the indoor air temperature Tr, the set indoor temperature Tset, and the differential temperature are equal to or higher than a preset set value 2 as shown in FIG. Accordingly, the distribution control unit (82) performs PID control on the opening amounts of the second port and the third port of the discharge side three-way switching valve (101).

    Specifically, as shown in FIG. 6, when the indoor air temperature Tr, the set indoor temperature Tset, and the temperature difference are equal to or lower than a preset set value 1, the distribution control unit (82) is configured to discharge the three-way switching valve on the discharge side. The second port of (101) is fully closed, and all the refrigerant discharged from the inverter compressor (2) is caused to flow into the indoor heat exchanger (41), so that the first heating / freezing operation is performed. The distribution control unit (82) opens the second port of the discharge side three-way switching valve (101) when the indoor air temperature Tr, the set indoor temperature Tset, and the differential temperature are equal to or higher than a preset set value 2. The refrigerant discharged from the inverter compressor (2) is distributed to the indoor heat exchanger (41) and the outdoor heat exchanger (4) through the second port and the third port, and the second heating / refrigeration operation is performed.

    In the second heating / refrigeration operation, when the second port of the discharge side three-way switching valve (101) is opened, the distribution control unit (82) sets the indoor air temperature Tr, the set indoor temperature Tset, and the differential temperature. The opening amounts of the second port and the third port of the discharge side three-way switching valve (101) are PID controlled so that the value becomes zero.

    That is, only the refrigerant having a flow rate capable of giving the necessary heat of condensation in the indoor heat exchanger (41) flows through the third port to the indoor heat exchanger (41) and is condensed. The condensed liquid refrigerant flows into the first communication liquid pipe (11) through the second communication liquid pipe (12).

    On the other hand, the remaining refrigerant discharged from the inverter compressor (2) is distributed to the outdoor gas pipe (9) side through the second port by the discharge side three-way switching valve (101). The refrigerant condenses in the outdoor heat exchanger (4). The condensed liquid refrigerant flows through the first liquid pipe (10a), then flows into the receiver (14), passes through the connection liquid pipe (19), and passes through the indoor heat exchanger (11) in the first communication liquid pipe (11). It merges with the refrigerant that passed through 41).

    Thereafter, a part of the liquid refrigerant flowing through the first communication liquid pipe (11) flows into the refrigeration heat exchanger (45) and evaporates. The other liquid refrigerant flowing through the first communication liquid pipe (11) flows to the refrigeration heat exchanger (51) and evaporates. The gas refrigerant evaporated in the refrigeration heat exchanger (45) and the gas refrigerant discharged from the booster compressor (53) after evaporating in the refrigeration heat exchanger (51) merge in the low-pressure gas pipe (15). Then, it returns to the inverter compressor (2) through the third port of the suction side three-way switching valve (102). This circulation is repeated to heat the interior of the store, and at the same time, cool the interior of the refrigerator, which is a showcase for refrigeration and a showcase for freezing. In other words, the cooling capacity (evaporation heat amount) of the refrigeration unit (1C) and refrigeration unit (1D) and the heating capacity (condensation heat amount) of the indoor unit (1B) are not balanced, and only the remaining condensation heat is transferred to the outdoor heat exchanger. Discharge to the outside in (4).

    Also in this second heating / refrigeration operation, the capacity control unit (81) also uses the inverter compressor (81) so that the difference between the refrigerant temperature of the refrigeration heat exchanger (45) and the set internal temperature becomes a predetermined value. The capacity of 2) is controlled to control the refrigerating capacity of the refrigerant circuit (1E). Specifically, the capacity control unit (81) controls the capacity of the inverter compressor (2) so that the refrigerant temperature Te of the refrigeration heat exchanger (45) is 10 ° lower than the set internal temperature Tset. (Tset−Te = 10).

<Third heating / freezing operation>
The third heating / freezing operation is a heating-deficient operation in which the heating capacity of the indoor unit (1B) is insufficient during the first heating / freezing operation. That is, the amount of heat of evaporation is insufficient.

    As shown by the solid line in FIG. 5, the four-way selector valve (3A) is switched to the ON state. The second port of the discharge side three-way switching valve (101) is closed. The suction side three-way switching valve (102) has the second port and the third port open. Furthermore, the solenoid valve (7a) of the refrigeration unit (1C) and the solenoid valve (7b) of the refrigeration unit (1D) are opened.

    Therefore, all of the refrigerant discharged from the inverter compressor (2) flows into the indoor heat exchanger (41) and condenses as in the first heating / refrigeration operation. The condensed liquid refrigerant flows through the second communication liquid pipe (12) to the first communication liquid pipe (11) and the receiver (14).

    Thereafter, a part of the liquid refrigerant flowing through the first communication liquid pipe (11) flows to the refrigeration heat exchanger (45) and evaporates. The other liquid refrigerant flowing through the first communication liquid pipe (11) flows to the refrigeration heat exchanger (51) and evaporates. The gas refrigerant evaporated in the refrigeration heat exchanger (45) and the gas refrigerant discharged from the booster compressor (53) after evaporating in the refrigeration heat exchanger (51) are combined and sucked in the low-pressure gas pipe (15). It returns to the inverter compressor (2) through the third port of the side three-way switching valve (102).

    On the other hand, the other liquid refrigerant flowing into the receiver (14) flows through the second liquid pipe (10b) through the heating expansion valve (104) to the outdoor heat exchanger (4) and evaporates. The evaporated gas refrigerant flows through the outdoor gas pipe (9) and returns to the inverter compressor (2) through the four-way switching valve (3A) and the suction side three-way switching valve (102).

    This circulation is repeated to heat the interior of the store, and at the same time, cool the interior of the refrigerator, which is a showcase for refrigeration and a showcase for freezing. In other words, the cooling capacity (evaporation heat amount) between the refrigeration unit (1C) and the refrigeration unit (1D) and the heating capacity (condensation heat amount) of the indoor unit (1B) are not balanced, and insufficient heat of evaporation is transferred to the outdoor heat exchanger. Get from (4).

-Effect of Embodiment 1-
As described above, according to the refrigeration apparatus (1) of the above embodiment, the three-way switching valve (101) causes the refrigerant discharged from the compressor (2) to be transferred to the indoor heat exchanger (82) by the distribution control unit (82). 41) and the outdoor heat exchanger (4) are adjusted and distributed. For this reason, only the amount of heat necessary for the indoor heat exchanger (41) out of the amount of heat absorbed by the refrigeration heat exchanger (45) and the refrigeration heat exchanger (51) during the second heating and refrigeration operation is converted into the indoor heat exchanger (41 ) And the excess heat can be discharged to the outside by the outdoor heat exchanger (4). Therefore, since the discharge pressure of the compressor (2) is not reduced too much, comfortable air conditioning can be performed, and the heat absorbed by the refrigeration heat exchanger (45) and the refrigeration heat exchanger (51) can be recovered appropriately. , The thermal efficiency can be significantly improved.

    In addition, since the refrigerant distribution amount between the indoor heat exchanger (41) and the outdoor heat exchanger (4) is controlled, the capacity of the indoor heat exchanger (41) can be finely adjusted. Air conditioning can be performed.

    Moreover, since the said capacity control part (81) controls the refrigerating capacity of the refrigerant circuit (1E) at the time of 1st heating refrigerating operation and 2nd heating refrigerating operation, a refrigerating heat exchanger (45) and refrigerating heat exchanger ( Since the low-pressure refrigerant pressure of 51) can be reliably maintained at a predetermined value, the capabilities of the refrigeration heat exchanger (45) and the refrigeration heat exchanger (51) can be reliably exhibited.

    In addition, the first heating and refrigeration operation in which only the indoor heat exchanger (41) serves as a condenser can be continued as much as possible by the auxiliary control unit (83).

<< Embodiment 2 >>
In this embodiment, the distribution control unit (82) of the first embodiment is based on the difference between the indoor air temperature and the set indoor temperature, and the distribution control unit (82) is a high-pressure refrigerant of the refrigerant circuit (1E). It is based on pressure.

    Specifically, the distribution control unit (82), as shown in FIG. 6, during the second heating and refrigeration operation in which both the indoor heat exchanger (41) and the outdoor heat exchanger (4) are condensers, The flow rate of the refrigerant distributed to the indoor heat exchanger (41) and the outdoor heat exchanger (4) is adjusted so that the high-pressure refrigerant temperature HP detected by the discharge temperature sensor (62) becomes a predetermined value (set value 0). In order to adjust, the opening amounts of the second port and the third port of the discharge side three-way switching valve (101) are PID controlled.

    Specifically, as shown in FIG. 6, when the high-pressure refrigerant temperature HP is equal to or lower than a preset set value 1, the distribution control unit (82) sets the second port of the discharge side three-way switching valve (101). All the refrigerant discharged from the inverter compressor (2) flows to the indoor heat exchanger (41), and the first heating / freezing operation is performed. Further, when the high-pressure refrigerant temperature HP is equal to or higher than a preset set value 2, the second port of the discharge side three-way switching valve (101) is opened, and the discharge refrigerant of the inverter compressor (2) is connected to the second port and the second port. It distributes with an indoor heat exchanger (41) and an outdoor heat exchanger (4) via 3 ports.

    The distribution control unit (82) is configured to switch the first three-way switching valve (101) so that the high-pressure refrigerant temperature HP becomes a set value 0 when the second port of the three-way switching valve (101) is opened. PID control is performed on the opening amounts of the second port and the third port. Other configurations, operations, and effects such as the capability control unit (81) are the same as those in the first embodiment.

<< Embodiment 3 >>
In this embodiment, the distribution control unit (82) of the first embodiment is based on the difference between the indoor air temperature and the set indoor temperature, and the distribution control unit (82) is a liquid refrigerant of the refrigerant circuit (1E). It is based on temperature.

    Specifically, the distribution control unit (82), as shown in FIG. 6, during the second heating and refrigeration operation in which both the indoor heat exchanger (41) and the outdoor heat exchanger (4) are condensers, Distributing to the indoor heat exchanger (41) and the outdoor heat exchanger (4) so that the liquid refrigerant temperature TL (indoor condensation temperature) detected by the indoor heat exchange sensor (71) becomes a predetermined value (set value 0). In order to adjust the flow rate of the refrigerant, the opening amount of the second port and the third port of the discharge side three-way switching valve (101) is PID controlled.

    Specifically, as shown in FIG. 6, when the liquid refrigerant temperature TL is equal to or lower than a preset set value 1, the distribution control unit (82) turns on the second port of the discharge side three-way switching valve (101). All the refrigerant discharged from the inverter compressor (2) flows to the indoor heat exchanger (41), and the first heating / freezing operation is performed. Further, when the liquid refrigerant temperature TL is equal to or higher than a preset set value 2, the second port of the discharge side three-way switching valve (101) is opened, and the discharge refrigerant of the inverter compressor (2) is connected to the second port and the second port. It distributes with an indoor heat exchanger (41) and an outdoor heat exchanger (4) via 3 ports.

    When the second port of the discharge side three-way switching valve (101) is opened, the distribution control unit (82) sets the first value of the discharge side three-way switching valve (101) so that the liquid refrigerant temperature TL becomes the set value 0. PID control is performed on the opening amounts of the second port and the third port. Other configurations, operations, and effects such as the capability control unit (81) are the same as those in the first embodiment.

<< Embodiment 4 >>
In the present embodiment, instead of the capability control unit (81) of the first embodiment controlling the inverter compressor (2) based on the refrigerant temperature of the refrigeration heat exchanger (45), the capability control unit (81 ) Is configured to control the inverter compressor (2) based on the equivalent saturation temperature of the refrigerant pressure Pe of the refrigeration heat exchanger (45).

    Specifically, the capacity control unit (81) includes both the indoor heat exchanger (41) and the outdoor heat exchanger (4) during the first heating / refrigeration operation in which only the indoor heat exchanger (41) serves as a condenser. The inverter compressor is configured so that a difference temperature between the equivalent saturation temperature of the refrigerant pressure Pe of the refrigeration heat exchanger (45) and the set internal temperature becomes a predetermined value during the second heating / refrigeration operation in which the is a condenser. The capacity of (2) is controlled to control the refrigerating capacity of the refrigerant circuit (1E). Specifically, the capacity controller (81) causes the equivalent saturation temperature of the refrigerant pressure Pe of the refrigeration heat exchanger (45) to be 10 ° lower than the set internal temperature Tset (equivalent saturation temperature of Tset-Pe). = 10). Other configurations, operations, and effects such as the distribution control unit (82) are the same as those in the first embodiment.

<< Embodiment 5 >>
In the present embodiment, instead of the capability control unit (81) of the first embodiment controlling the inverter compressor (2) based on the refrigerant temperature of the refrigeration heat exchanger (45), the capability control unit (81 ) Is configured to control the inverter compressor (2) based on the intake air temperature of the refrigeration heat exchanger (45).

    Specifically, the capacity control unit (81) includes both the indoor heat exchanger (41) and the outdoor heat exchanger (4) during the first heating / refrigeration operation in which only the indoor heat exchanger (41) serves as a condenser. Of the inverter compressor (2) so that the difference between the intake air temperature of the refrigeration heat exchanger (45) and the set internal temperature becomes a predetermined value during the second heating / refrigeration operation in which the is a condenser. The refrigerating capacity of the refrigerant circuit (1E) is controlled by controlling the capacity. Specifically, the capacity control unit (81) causes the intake air temperature Tr of the refrigeration heat exchanger (45) to be the set internal temperature Tset (equivalent saturation temperature of Tset−Pe = 0). Other configurations, operations, and effects such as the distribution control unit (82) are the same as those in the first embodiment.

Embodiment 6
In this embodiment, instead of the capacity control unit (81) of the first embodiment controlling the capacity of the inverter compressor (2), the capacity control unit (81) is refrigerated by the refrigeration heat exchanger (45). The fan (47) and the refrigeration fan (58) of the refrigeration heat exchanger (51) are configured to control the air volume.

    Specifically, the capacity control unit (81) controls the air volume of the refrigeration fan (47) of the refrigeration heat exchanger (45) and the refrigeration fan (58) of the refrigeration heat exchanger (51) to control the refrigerant circuit (1E). The refrigeration heat exchanger (45) and the refrigeration heat exchanger (51) exhibit a predetermined cooling capacity. Other configurations, operations, and effects such as the distribution control unit (82) are the same as those in the first embodiment.

<< Embodiment 7 >>
In this embodiment, instead of the capacity control unit (81) of the first embodiment controlling the capacity of the inverter compressor (2), the capacity control unit (81) is connected to the discharge side of the inverter compressor (2). And the suction side are bypassed.

    In this embodiment, as shown in FIG. 7, an auxiliary passage (90) is connected between the discharge pipe (5) and the suction pipe (6) of the inverter compressor (2). The auxiliary passage (90) is provided with a variable opening auxiliary valve (91) as an opening / closing mechanism. And the said capability suppression part is comprised so that the opening degree of an auxiliary valve (91) may be adjusted and the refrigerant | coolant flow rate of an auxiliary channel | path (90) may be controlled. Other configurations, operations, and effects such as the distribution control unit (82) are the same as those in the first embodiment.

Embodiment 8
In this embodiment, the flow rate adjusting means of the first embodiment is constituted by a discharge side three-way switching valve (101), and the flow rate adjusting means is constituted by a motor valve having a variable opening.

    Specifically, in the present embodiment, as shown in FIG. 8, the discharge pipe (5) of the inverter compressor (2) is branched, and the discharge pipe (5) of the inverter compressor (2) and the four-way switching valve. The first solenoid valve (101a) is installed in the pipe connecting the first port of (3A), and the discharge pipe (5) of the inverter compressor (2) and the gas side end of the outdoor heat exchanger (4) A second solenoid valve (101b) is provided in the connecting pipe. The distribution control unit (82) performs PID control on the opening amounts of the first electromagnetic valve (101a) and the second electromagnetic valve (101b), and the refrigerant discharged from the inverter compressor (2) is transferred to the indoor heat exchanger ( 41) and outdoor heat exchanger (4). Other configurations, operations, and effects such as the capability control unit (81) are the same as those in the first embodiment.

<< Other Embodiments >>
This invention is good also as following structures about the said Embodiments 1-7.

    That is, in the above embodiment, the flow rate adjusting means is configured so that the discharge side three-way switching valve (101) can adjust the flow rate, but a three-way switching valve (101) having a simple structure without a flow rate adjusting function may be used. In this case, the flow rate adjusting means is composed of the three-way switching valve (101) and the heating expansion valve (104), and the heating expansion valve (104) connected to the downstream end during the heat recovery operation. By adjusting the degree of opening, the refrigerant discharged from the compressor (2) may be distributed in an appropriate amount to the indoor heat exchanger (41) and the outdoor heat exchanger (4). In this case, a four-way switching valve having a simple structure without a flow rate adjusting function may be used as the flow rate adjusting means, and in either case, an efficient refrigeration apparatus (1) can be obtained as in the above embodiment.

    In the eighth embodiment, the heating expansion valve (104) may be applied as described above instead of the second electromagnetic valve (101b).

    Further, the capacity control unit (81) of the third to seventh embodiments may be applied to the second embodiment, and the distribution control unit (82) of the second embodiment or the third to third embodiments may be applied to the flow rate adjusting means of the eighth embodiment. 7 capability control unit (81) may be applied.

    Moreover, in the said Embodiment 1-8, an auxiliary | assistant control part (82) is an indoor heat exchanger (41) from the time of the heat recovery operation (at the time of 1st heating-freezing operation) from which only an indoor heat exchanger (41) becomes a condenser. ) And the outdoor heat exchanger (4) may be operated before switching to the heat recovery operation (second heating / refrigeration operation) in which the condenser becomes a condenser.

    As described above, the present invention is useful for a refrigeration apparatus including an air conditioning heat exchanger and a cooling heat exchanger used in a convenience store, a supermarket, and the like.

3 is a circuit diagram illustrating a refrigerant circuit of the refrigeration apparatus according to Embodiment 1. FIG. It is a refrigerant circuit figure which shows the refrigerant | coolant flow at the time of the heating operation of Embodiment 1. FIG. 3 is a refrigerant circuit diagram illustrating a refrigerant flow during a first heating / freezing operation of the first embodiment. It is a refrigerant circuit diagram which shows the refrigerant | coolant flow at the time of the 2nd heating refrigerating operation of Embodiment 1. It is a refrigerant circuit diagram which shows the refrigerant | coolant flow at the time of the 3rd heating refrigerating operation of Embodiment 1. 6 is an explanatory diagram illustrating a control operation of a distribution control unit according to the first embodiment. FIG. FIG. 10 is a refrigerant circuit diagram using an auxiliary passage according to a seventh embodiment. FIG. 10 is a refrigerant circuit diagram using the flow rate adjusting means of the eighth embodiment.

Explanation of symbols

1 Refrigeration equipment 1E Refrigerant circuit 2 Compressor 4 Outdoor heat exchanger (heat source side heat exchanger)
4F outdoor fan (heat source fan)
5 Discharge pipe 41 Indoor heat exchanger (air conditioning heat exchanger)
43 Indoor fans (air conditioning fans)
45 Refrigerated heat exchanger (cooling heat exchanger)
47 Refrigerated fan (cooling fan)
51 Refrigeration heat exchanger (cooling heat exchanger)
58 Refrigeration fan (cooling fan)
101 Three-way selector valve 104 Expansion valve 80 Controller (control means)
81 Ability control unit (ability control means)
82 Distribution control unit (distribution control means)
83 Auxiliary control unit (auxiliary control means)
90 Auxiliary passage 91 Auxiliary valve 101a, 101b Motorized valve

Claims (10)

Compressor (2), heat source side heat exchanger (4), expansion mechanism (46, 52, 104), air conditioning heat exchanger (41) for air conditioning the room, and cooling the interior A refrigeration apparatus comprising a refrigerant circuit (1E) connected to a cooling heat exchanger (45, 51),
A flow rate that is provided in the refrigerant circuit (1E) and that varies the flow rate of the refrigerant discharged from the compressor (2) and distributed to the air conditioning heat exchanger (41) and the heat source side heat exchanger (4). Adjusting means (101, 104);
During the heat recovery operation in which both the air conditioning heat exchanger (41) and the heat source side heat exchanger (4) are condensers, the air conditioning heat is adjusted so that the difference between the indoor air temperature and the set indoor temperature becomes a predetermined value. Distributing control means (82) for controlling the flow rate adjusting means (101, 104) for adjusting the flow rate of the refrigerant distributed to the exchanger (41) and the heat source side heat exchanger (4). A refrigeration apparatus characterized by that. Compressor (2), heat source side heat exchanger (4), expansion mechanism (46, 52, 104), air conditioning heat exchanger (41) for air conditioning the room, and cooling the interior A refrigeration apparatus comprising a refrigerant circuit (1E) connected to a cooling heat exchanger (45, 51),
A flow rate that is provided in the refrigerant circuit (1E) and that varies the flow rate of the refrigerant discharged from the compressor (2) and distributed to the air conditioning heat exchanger (41) and the heat source side heat exchanger (4). Adjusting means (101, 104);
During the heat recovery operation in which both the air conditioning heat exchanger (41) and the heat source side heat exchanger (4) are condensers, the high-pressure refrigerant pressure of the refrigerant circuit (1E) or the liquid refrigerant temperature of the refrigerant circuit (1E) Distribution for controlling the flow rate adjusting means (101, 104) in order to adjust the flow rate of refrigerant distributed to the air conditioning heat exchanger (41) and the heat source side heat exchanger (4) so that becomes a predetermined value. A refrigeration apparatus comprising a control means (82). In claim 1 or 2,
In the heat recovery operation in which only the air conditioning heat exchanger (41) is a condenser and in the heat recovery operation in which both the air conditioning heat exchanger (41) and the heat source side heat exchanger (4) are condensers, A capacity control means (81) is provided for controlling the refrigerating capacity of the refrigerant circuit (1E) so that the difference between the refrigerant temperature of the cooling heat exchanger (45, 51) and the set internal temperature becomes a predetermined value. A refrigeration apparatus characterized by that. In claim 1 or 2,
In the heat recovery operation in which only the air conditioning heat exchanger (41) is a condenser and in the heat recovery operation in which both the air conditioning heat exchanger (41) and the heat source side heat exchanger (4) are condensers, Capacity control means (81) for controlling the refrigerating capacity of the refrigerant circuit (1E) so that the difference between the refrigerant pressure equivalent saturation temperature of the cooling heat exchanger (45, 51) and the set internal temperature becomes a predetermined value. A refrigeration apparatus comprising the refrigeration apparatus. In claim 1 or 2,
In the heat recovery operation in which only the air conditioning heat exchanger (41) is a condenser and in the heat recovery operation in which both the air conditioning heat exchanger (41) and the heat source side heat exchanger (4) are condensers, A capacity control means (81) is provided for controlling the refrigerating capacity of the refrigerant circuit (1E) so that the difference between the intake air temperature of the cooling heat exchanger (45, 51) and the set internal temperature becomes a predetermined value. A refrigeration apparatus characterized by comprising: In any one of Claims 4-6,
The said capacity control means (81) is comprised so that the capacity | capacitance of a compressor (2) may be controlled, The freezing apparatus characterized by the above-mentioned. In any one of Claims 4-6,
An auxiliary passage (90) for bypassing the refrigerant on the discharge side and suction side of the compressor (2) is provided,
The said capacity control means (81) is comprised so that the refrigerant | coolant flow volume of an auxiliary | assistant channel | path (90) may be controlled, The freezing apparatus characterized by the above-mentioned. In any one of Claims 4-6,
The said capacity control means (81) is comprised so that the air volume of the cooling fan (47,58) of the said cooling heat exchanger (45,51) may be controlled, The freezing apparatus characterized by the above-mentioned. In claim 1 or 2,
Before switching from the heat recovery operation in which only the air conditioning heat exchanger (41) is a condenser to the heat recovery operation in which both the air conditioning heat exchanger (41) and the heat source side heat exchanger (4) are condensers, A refrigeration apparatus comprising auxiliary control means (83) for increasing the air volume of an air conditioning fan (43) of an air conditioning heat exchanger (41). In claim 1 or 2,
Before switching from the heat recovery operation in which only the air conditioning heat exchanger (41) is a condenser to the heat recovery operation in which both the air conditioning heat exchanger (41) and the heat source side heat exchanger (4) are condensers, A refrigeration apparatus comprising auxiliary control means (83) for operating an indoor ventilation fan.

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