JP2008209075A - Air conditioner - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an air conditioner capable of being operated at an (optimum) operation point of high efficiency according to load of an use-side heat exchanger, and improving a coefficient of performance (COP) corresponding to energy consumption efficiency of the entire air conditioner. <P>SOLUTION: This air conditioner comprises a control means for controlling a rotational frequency of a compressor 2 to keep a temperature of a conveyed medium passing through an intermediate heat exchanger 6 constant in a heating operation, controlling openings of flow rate control valves 14 respectively disposed at a downstream side of the indoor heat exchangers 10 to keep the temperature of the conveyed medium passing through each of the indoor heat exchangers 10 constant, and further controlling a flow rate of the conveyed medium discharged from a conveyed medium driving device 9 and flowing into the intermediate heat exchanger 6 according to the total load of the indoor heat exchangers 10. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention pumps out the refrigerant by exchanging heat between the refrigerant in the primary cycle that circulates in the closed circuit while repeatedly changing the state of the gas phase / liquid phase, and the transport medium in the secondary cycle. The present invention relates to an air conditioner that transports and uses heat by a transport medium.

As an air conditioner that performs an air conditioning operation by enclosing a carrier medium in an indoor cycle (also referred to as a “secondary cycle” or a “use cycle”) and circulating the carrier medium in the indoor cycle, For example, there is one that heats or cools a transport medium by heat exchange with a refrigerant circulating in an outdoor cycle (also referred to as “primary side cycle” or “heat source side cycle”) (for example, Patent Document 1). reference).
Japanese Patent Laid-Open No. 9-79684

  However, in the air conditioner disclosed in Patent Document 1, only the pressure of the carrier medium enclosed in the heat carrier circuit is controlled, and the inlet temperature of the carrier medium driving device and the inlet of the use side heat exchanger are controlled. The temperature or outlet temperature is not controlled. Therefore, it is not possible to operate at an efficient (optimum) operating point according to the load on the use side heat exchanger, and the coefficient of performance (COP) corresponding to the energy consumption efficiency of the entire air conditioner There was a problem that would decrease.

  The present invention has been made in view of the above circumstances, and can be operated at an efficient (optimal) operating point according to the load of the use side heat exchanger, and the energy consumption of the entire air conditioner It aims at providing the air conditioner which can improve the coefficient of performance (COP) equivalent to efficiency.

In order to solve the above problems, the present invention employs the following means.
An air conditioner according to the present invention includes a compressor that compresses a refrigerant, an intermediate heat exchanger through which the refrigerant and a transport medium pass, a decompression unit that decompresses and expands the refrigerant to form a low-temperature and low-pressure refrigerant, and an interior Primary cycle of closed circuit comprising outdoor heat exchanger for exchanging heat between refrigerant passing through and outside air, transport medium driving device for circulating transport medium, intermediate heat exchanger, and transport medium passing inside A closed circuit secondary side cycle comprising a plurality of indoor heat exchangers for exchanging heat between the air blown into the room and a refrigerant circulating through the primary side cycle in the intermediate heat exchanger; An air conditioner that exchanges heat with a carrier medium that circulates through the secondary side cycle, and the compressor is configured so that the temperature of the carrier medium that has passed through the intermediate heat exchanger is kept constant during heating operation. Control the rotation speed And, while controlling the opening degree of the flow control valve respectively disposed on the downstream side of the indoor heat exchanger so that the temperature of the transport medium that has passed through each indoor heat exchanger is kept constant, Control means for controlling the flow rate of the transport medium discharged from the transport medium driving device and flowing into the intermediate heat exchanger according to the total load of the indoor heat exchanger.

  An air conditioner according to the present invention includes a compressor that compresses a refrigerant, an intermediate heat exchanger through which the refrigerant and a transport medium pass, a decompression unit that decompresses and expands the refrigerant to form a low-temperature and low-pressure refrigerant, and an interior Primary cycle of closed circuit comprising outdoor heat exchanger for exchanging heat between refrigerant passing through and outside air, transport medium driving device for circulating transport medium, intermediate heat exchanger, and transport medium passing inside A closed circuit secondary side cycle comprising a plurality of indoor heat exchangers for exchanging heat between the air blown into the room and a refrigerant circulating through the primary side cycle in the intermediate heat exchanger; An air conditioner that exchanges heat with a carrier medium that circulates through the secondary side cycle, and controls the number of rotations of the compressor so that the discharge pressure of the compressor is kept constant during heating operation. And each room heat exchange And controlling the opening degree of the flow control valve respectively arranged downstream of the indoor heat exchanger so that the temperature of the transport medium that has passed through the chamber is kept constant, and the load of the indoor heat exchanger Control means for controlling the flow rate of the transport medium discharged from the transport medium driving device and flowing into the intermediate heat exchanger according to the total is provided.

  An air conditioner according to the present invention includes a compressor that compresses a refrigerant, an intermediate heat exchanger through which the refrigerant and a transport medium pass, a decompression unit that decompresses and expands the refrigerant to form a low-temperature and low-pressure refrigerant, and an interior Primary cycle of closed circuit comprising outdoor heat exchanger for exchanging heat between refrigerant passing through and outside air, transport medium driving device for circulating transport medium, intermediate heat exchanger, and transport medium passing inside A closed circuit secondary side cycle comprising a plurality of indoor heat exchangers for exchanging heat between the air blown into the room and a refrigerant circulating through the primary side cycle in the intermediate heat exchanger; An air conditioner that exchanges heat with a carrier medium that circulates through the secondary side cycle, and during cooling operation, the degree of supercooling of the carrier medium that has passed through the intermediate heat exchanger is kept constant. Compressor speed And the degree of opening of the flow rate control valve disposed upstream of the indoor heat exchanger is controlled so that the degree of superheat of the transport medium that has passed through each indoor heat exchanger is kept constant. In addition, control means is provided for controlling the flow rate of the transport medium discharged from the transport medium driving device and flowing into the indoor heat exchanger according to the total load of the indoor heat exchanger.

  An air conditioner according to the present invention includes a compressor that compresses a refrigerant, an intermediate heat exchanger through which the refrigerant and a transport medium pass, a decompression unit that decompresses and expands the refrigerant to form a low-temperature and low-pressure refrigerant, and an interior Primary cycle of closed circuit comprising outdoor heat exchanger for exchanging heat between refrigerant passing through and outside air, transport medium driving device for circulating transport medium, intermediate heat exchanger, and transport medium passing inside And a closed-circuit secondary cycle comprising a single indoor heat exchanger for exchanging heat between the air blown into the room and a refrigerant circulating through the primary cycle in the intermediate heat exchanger An air conditioner that exchanges heat with a carrier medium that circulates through the secondary side cycle, and the compressor is configured so that the temperature of the carrier medium that has passed through the intermediate heat exchanger is kept constant during heating operation. Control the number of revolutions And control means for controlling the flow rate of the transport medium discharged from the transport medium driving device and flowing into the intermediate heat exchanger so that the temperature of the transport medium sucked into the transport medium driving device is kept constant. It has.

  An air conditioner according to the present invention includes a compressor that compresses a refrigerant, an intermediate heat exchanger through which the refrigerant and a transport medium pass, a decompression unit that decompresses and expands the refrigerant to form a low-temperature and low-pressure refrigerant, and an interior Primary cycle of closed circuit comprising outdoor heat exchanger for exchanging heat between refrigerant passing through and outside air, transport medium driving device for circulating transport medium, intermediate heat exchanger, and transport medium passing inside And a closed-circuit secondary cycle comprising a single indoor heat exchanger for exchanging heat between the air blown into the room and a refrigerant circulating through the primary cycle in the intermediate heat exchanger An air conditioner that exchanges heat with a carrier medium that circulates through the secondary side cycle, and controls the number of rotations of the compressor so that the discharge pressure of the compressor is kept constant during heating operation. And the carrier medium As the temperature of the transport medium which is sucked into the braking system is kept constant, and a control means for controlling the flow rate of the conveying medium flowing into the intermediate heat exchanger is discharged from the conveying medium driving device.

  An air conditioner according to the present invention includes a compressor that compresses a refrigerant, an intermediate heat exchanger through which the refrigerant and a transport medium pass, a decompression unit that decompresses and expands the refrigerant to form a low-temperature and low-pressure refrigerant, and an interior Primary cycle of closed circuit comprising outdoor heat exchanger for exchanging heat between refrigerant passing through and outside air, transport medium driving device for circulating transport medium, intermediate heat exchanger, and transport medium passing inside And a closed-circuit secondary cycle comprising a single indoor heat exchanger for exchanging heat between the air blown into the room and a refrigerant circulating through the primary cycle in the intermediate heat exchanger An air conditioner that exchanges heat with a carrier medium that circulates through the secondary side cycle, and during cooling operation, the degree of supercooling of the carrier medium that has passed through the intermediate heat exchanger is kept constant. Control compressor speed And the flow rate of the transport medium discharged from the transport medium driving device and flowing into the indoor heat exchanger is controlled so that the degree of superheat of the transport medium flowing into the intermediate heat exchanger is kept constant. Control means are provided.

The air conditioner according to the present invention can be operated at an efficient (optimum) operating point according to the load of the indoor heat exchanger during heating operation or cooling operation, and the entire air conditioner Can increase (improve) the coefficient of performance (COP) equivalent to the energy consumption efficiency.
In addition, since the carrier medium sucked into the carrier medium driving device can be kept in a liquid phase state, and the efficiency of the carrier medium driving device can be increased (improved), it corresponds to the energy consumption efficiency of the entire air conditioner. The coefficient of performance (COP) can be further increased (improved).

  In the air conditioner, it is more preferable that the secondary cycle is provided with a four-way valve that switches a flow path of the transport medium discharged from the transport medium driving device in accordance with an operation mode.

  According to such an air conditioner, in accordance with the operation mode, the flow direction of the refrigerant circulating in the primary cycle and the flow direction of the carrier medium circulating in the secondary cycle are reversed (opposite flow). Therefore, the heat exchange efficiency in the intermediate heat exchanger can be further increased (improved), and the coefficient of performance (COP) corresponding to the energy consumption efficiency of the entire air conditioner can be further increased (improved). .

  In the air conditioner, it is more preferable that the transport medium driving device is configured to be able to rotate forward and backward, and the rotation direction is selected according to the operation mode and the discharge direction is reversed.

  According to such an air conditioner, the flow direction of the transport medium circulating in the secondary cycle can be reversed (reverse direction) simply by changing the rotation direction of the transport medium driving device. The (cycle) configuration of the side cycle can be simplified (simplified), and the manufacturing cost can be reduced.

  In the air conditioner, it is more preferable that a carbon dioxide refrigerant is used as the carrier medium.

  According to such an air conditioner, carbon dioxide refrigerant, which is one of natural refrigerants, is used as a carrier medium. Carbon dioxide is a non-toxic, non-flammable material and is very advantageous in that it is easy to handle and has excellent safety because it does not destroy the ozone layer.

  According to the present invention, it is possible to operate at an efficient (optimum) operating point according to the load on the use side heat exchanger, and to obtain a coefficient of performance (COP) corresponding to the energy consumption efficiency of the entire air conditioner. There is an effect that it can be improved.

Hereinafter, embodiments of the present invention will be described with reference to the drawings. FIG. 1 is a schematic configuration diagram of an air conditioner according to a first embodiment of the present invention, FIG. 2 is a flowchart for explaining rotation speed control of the compressor shown in FIG. 1, and FIG. 3 is a first diagram shown in FIG. FIG. 4 is a graph showing the relationship between the opening of the first flow control valve shown in FIG. 1 and the full load of the indoor cycle.
As shown in FIG. 1, the air conditioner 1 has a compressor 2, a four-way valve 3, an outdoor heat exchanger 4, an expansion valve (decompression means) 5, an intermediate heat exchanger 6, and a pipe 7 as main elements. The outer cycle 8 includes the intermediate heat exchanger 6, the carrier medium driving device 9, the indoor heat exchanger 10, and the indoor cycle 12 having the piping 11 as main elements.

The compressor 2 sucks and compresses a low-temperature / low-pressure gaseous refrigerant (for example, HCFC refrigerant (R22), HFC refrigerant (R407C or R410A), HC refrigerant (propane or isobutane), etc.) It is a refrigerant.
The four-way valve 3 is provided on the downstream side of the compressor 2 and switches the flow path of the refrigerant discharged from the compressor 2 between the cooling operation and the heating operation. During the heating operation (solid arrow in the figure) When the refrigerant is circulated in the direction indicated by), a flow path from the compressor 2 toward the intermediate heat exchanger 6 is formed, while on the other hand, during cooling operation (when the refrigerant is circulated in the direction indicated by the broken line arrow in the figure) Is configured to form a flow path from the compressor 2 toward the outdoor heat exchanger 4.

The outdoor heat exchanger 4 functions as a condenser that condenses and liquefies high-temperature and high-pressure gaseous refrigerant during cooling operation and dissipates heat to the outside air, and conversely evaporates low-temperature and low-pressure liquid refrigerant during heating operation and takes heat from the outside air. It functions as an evaporator.
The expansion valve 5 depressurizes and expands the refrigerant that passes through it to form a low-temperature and low-pressure refrigerant.

The intermediate heat exchanger (also referred to as “inter-refrigerant heat exchanger”) 6 allows heat to be transferred between the refrigerant circulating in the outdoor cycle 8 and the transport medium circulating in the indoor cycle 12. During the heating operation, the transport medium circulating in the indoor cycle 12 is heated by the refrigerant circulating in the outdoor cycle 8, and during the cooling operation, the transport medium circulating in the indoor cycle 12 is cooled by the refrigerant circulating in the outdoor cycle 8. It has come to be.
The pipe 7 connects the compressor 2, the four-way valve 3, the outdoor heat exchanger 4, the expansion valve 5, and the intermediate heat exchanger 6, and allows the refrigerant to circulate between these components. Thus, an outdoor cycle (also referred to as “primary side cycle” or “heat source side cycle”) 8 is formed.

The carrier medium driving device 9 is a pressure feeding unit such as a screw-type liquid pump or a compressor, and circulates a carrier medium (for example, carbon dioxide (CO ₂ ) refrigerant) in the indoor cycle 12. It is something to be made.
The indoor heat exchanger 10 performs heat exchange between the transport medium passing through the inside and the air blown into the room, and functions as a so-called evaporator during cooling operation and as a so-called gas cooler during heating operation. .

The pipe 11 connects the intermediate heat exchanger 6, the transfer medium driving device 9, and the indoor heat exchanger 10, and enables the transfer medium to circulate between these components, thereby enabling an indoor cycle ( (Also referred to as “secondary cycle” or “use cycle”) 12 is formed.
Further, a bypass pipe 11a that connects the vicinity of the suction port (a position indicated by a symbol F in FIG. 1) and the vicinity of the discharge port (a position indicated by a symbol A in FIG. 1) of the transport medium driving device 9 is connected to the pipe 11. The first flow rate control valve 13 is provided in the middle of the bypass pipe 11a. The bypass pipe 11a and the first flow rate control valve 13 are configured so that a part of the transport medium discharged from the transport medium driving device 9 toward the intermediate heat exchanger 6 does not pass through the intermediate heat exchanger 6, and the transport medium driving device. 9 is returned to the suction port side and is again sucked into the transport medium driving device 9, and is returned to the suction port side of the transport medium driving device 9 by adjusting the opening of the first flow rate control valve 13. The flow rate of the transported medium can be adjusted.
Furthermore, the pipe 11 connected to the outlet side of each indoor heat exchanger 10 is provided with a second flow rate control valve 14, and by adjusting the opening degree of each second flow rate control valve 14, The flow rate of the transfer medium from the indoor heat exchanger 10 toward the transfer medium driving device 9, that is, the flow rate of the transfer medium passing through each indoor heat exchanger 10 can be adjusted.

Now, when the air conditioner 1 comprised as mentioned above is set to heating operation mode, the compressor 2 is the exit temperature in the exit vicinity of the intermediate heat exchanger 6 (position shown with the code | symbol C in FIG. 1). Is controlled in accordance with a flowchart shown in FIG. 2 on the basis of a signal from a temperature detection means (not shown) arranged in the vicinity of the outlet of the intermediate heat exchanger 6.
That is, when the “temperature at C” detected by the temperature detection means is higher than the “target temperature” set in advance as a target, the rotational speed of the compressor 2 is decreased, and when it is lower, the compressor 2 is increased so that the outlet temperature in the vicinity of the outlet of the intermediate heat exchanger 6 is kept constant.

Further, the second flow rate control valve 14 is disposed in the vicinity of the outlet of the indoor heat exchanger 10 so as to keep the outlet temperature in the vicinity of the outlet of the indoor heat exchanger 10 (position indicated by symbol E in FIG. 1) constant. This is an on-off valve whose opening degree is controlled according to a flowchart shown in FIG. 3 based on a signal from a temperature detection means (not shown).
That is, when the “temperature at E” detected by the temperature detection means is higher than the “target temperature” set in advance as a target, the opening of the second flow control valve 14 is reduced, and when it is lower, The opening degree of the second flow rate control valve 14 is increased, and the outlet temperature in the vicinity of the outlet of the indoor heat exchanger 10 is kept constant.

Furthermore, the first flow control valve 13 is an on-off valve whose opening degree is controlled according to the total load of the indoor cycle 12 (that is, the total load of the indoor heat exchanger 10). The opening degree is adjusted along the solid line in FIG.
That is, when the full load of the indoor cycle 12 is minimum, the opening of the first flow control valve 13 is fully opened, and when the maximum load is maximum, the opening of the first flow control valve 13 is fully closed, and The opening degree of the first flow control valve 13 is linearly changed according to the full load of the indoor cycle 12.

According to the air conditioner 1 according to the present embodiment, during the heating operation, the rotation speed of the compressor 2 is controlled so that the outlet temperature in the vicinity of the outlet of the intermediate heat exchanger 6 is kept constant, and the indoor heat exchanger The opening degree of the second flow rate control valve 14 is controlled so that the outlet temperature in the vicinity of the outlet number 10 is kept constant, and the opening degree of the first flow rate control valve 13 is controlled according to the full load of the indoor cycle 12. Therefore, it is possible to operate at an efficient (optimum) operating point according to the load of each indoor heat exchanger 10, and a coefficient of performance corresponding to the energy consumption efficiency of the entire air conditioner 1 ( COP) can be increased (improved).
Further, since the carrier medium sucked into the carrier medium driving device 9 can be kept in a liquid phase state, and the efficiency of the carrier medium driving device 9 can be increased (improved), the energy consumption efficiency of the entire air conditioner 1 is improved. The coefficient of performance (COP) equivalent to can be further increased (improved).

A second embodiment of an air conditioner according to the present invention will be described with reference to FIGS. FIG. 5 is a schematic configuration diagram of an air conditioner according to a second embodiment of the present invention, and FIG. 6 is a graph showing the relationship between the rotation speed of the carrier medium driving device shown in FIG. 5 and the full load of the indoor cycle. is there.
In the air conditioner 21 according to the present embodiment, the bypass pipe 11a and the first flow rate control valve 13 are omitted, and the rotation speed of the transport medium driving device 9 is controlled according to the full load of the indoor cycle 12. It differs from that of the first embodiment described above. Since other components are the same as those of the first embodiment described above, description of these components is omitted here.
In addition, the same code | symbol is attached | subjected to the member same as 1st Embodiment mentioned above.

Now, when the air conditioner 21 comprised like this embodiment is set to heating operation mode, the compressor 2 is in the exit vicinity (position shown with the code | symbol C in FIG. 1) of the intermediate heat exchanger 6. FIG. In order to keep the outlet temperature constant, the rotational speed is controlled according to a flowchart shown in FIG. 2 based on a signal from a temperature detection means (not shown) arranged near the outlet of the intermediate heat exchanger 6. .
That is, when the “temperature at C” detected by the temperature detection means is higher than the “target temperature” set in advance as a target, the rotational speed of the compressor 2 is decreased, and when it is lower, the compressor 2 is increased so that the outlet temperature in the vicinity of the outlet of the intermediate heat exchanger 6 is kept constant.

Further, the second flow rate control valve 14 is disposed in the vicinity of the outlet of the indoor heat exchanger 10 so as to keep the outlet temperature in the vicinity of the outlet of the indoor heat exchanger 10 (position indicated by symbol E in FIG. 1) constant. This is an on-off valve whose opening degree is controlled according to a flowchart shown in FIG. 3 based on a signal from a temperature detection means (not shown).
That is, when the “temperature at E” detected by the temperature detection means is higher than the “target temperature” set in advance as a target, the opening of the second flow control valve 14 is reduced, and when it is lower, The opening degree of the second flow rate control valve 14 is increased, and the outlet temperature in the vicinity of the outlet of the indoor heat exchanger 10 is kept constant.

Further, the rotation speed of the transport medium driving device 9 is controlled (inverter control) according to the total load of the indoor cycle 12 (that is, the total load of the indoor heat exchanger 10). Specifically, the rotational speed is adjusted along the solid line in FIG.
That is, when the total load of the indoor cycle 12 is zero, the rotation speed of the transport medium driving device 9 is zero (zero), and when the maximum load is maximum, the rotation speed of the transport medium driving device 9 is maximum. In addition, the rotational speed of the transport medium driving device 9 is linearly changed according to the total load of the indoor cycle 12.

According to the air conditioner 21 according to the present embodiment, the bypass pipe 11a and the first flow rate control valve 13 that are required in the first embodiment can be eliminated, so that the configuration of the indoor cycle 12 is simplified. Thus, the air conditioner 21 as a whole can be reduced in size and the manufacturing cost can be reduced.
Other functions and effects are the same as those of the above-described first embodiment, and thus description thereof is omitted here.

A third embodiment of the air conditioner according to the present invention will be described with reference to FIGS. FIG. 7 is a schematic configuration diagram of an air conditioner according to a third embodiment of the present invention, and FIG. 8 is a flowchart for explaining the rotational speed control of the compressor shown in FIG.
In the air conditioner 31 according to the present embodiment, the rotational speed of the compressor 2 is controlled so as to keep the discharge pressure in the vicinity of the discharge port of the compressor 2 (the position indicated by the symbol G in FIG. 7) constant. This differs from that of the first embodiment described above. Since other components are the same as those of the first embodiment described above, description of these components is omitted here.
In addition, the same code | symbol is attached | subjected to the member same as 1st Embodiment mentioned above.

When the air conditioner 31 configured as in the present embodiment is set to the heating operation mode, the compressor 2 has a constant discharge pressure in the vicinity of the discharge port (the position indicated by the symbol G in FIG. 7). Therefore, based on a signal from a pressure detection means (not shown) arranged in the vicinity of the discharge port of the compressor 2, the rotational speed is controlled according to the flowchart shown in FIG.
That is, when the “pressure at G” detected by the pressure detection means is higher than the “target pressure” preset as a target, the rotational speed of the compressor 2 is reduced, and when it is lower, the compressor 2 is increased so that the discharge pressure in the vicinity of the discharge port of the compressor 2 is kept constant.

According to the air conditioner 31 according to the present embodiment, during the heating operation, the rotational speed of the compressor 2 is controlled so that the discharge pressure in the vicinity of the discharge port of the compressor 2 is kept constant, and the indoor heat exchanger 10 The opening degree of the second flow rate control valve 14 is controlled so as to keep the outlet temperature in the vicinity of the outlet of the engine at the same time, and the opening degree of the first flow rate control valve 13 is controlled according to the full load of the indoor cycle 12. Therefore, it is possible to operate at an efficient (optimal) operating point according to the load of each indoor heat exchanger 10, and a coefficient of performance (COP) corresponding to the energy consumption efficiency of the entire air conditioner 31 ) Can be increased (improved).
Further, since the carrier medium sucked into the carrier medium driving device 9 can be kept in a liquid phase state, and the efficiency of the carrier medium driving device 9 can be increased (improved), the energy consumption efficiency of the entire air conditioner 1 is improved. The coefficient of performance (COP) equivalent to can be further increased (improved).

A fourth embodiment of an air conditioner according to the present invention will be described with reference to FIG. FIG. 9 is a schematic configuration diagram of an air conditioner according to a fourth embodiment of the present invention.
In the air conditioner 41 according to the present embodiment, the bypass pipe 11a and the first flow rate control valve 13 are omitted, and the rotation speed of the transport medium driving device 9 is controlled according to the full load of the indoor cycle 12. It differs from that of the third embodiment described above. Since other components are the same as those of the third embodiment described above, description of these components is omitted here.
In addition, the same code | symbol is attached | subjected to the member same as 3rd Embodiment mentioned above.

When the air conditioner 41 configured as in the present embodiment is set to the heating operation mode, the compressor 2 has a constant discharge pressure in the vicinity of the discharge port (the position indicated by the symbol G in FIG. 9). Therefore, based on a signal from a pressure detection means (not shown) arranged in the vicinity of the discharge port of the compressor 2, the rotational speed is controlled according to the flowchart shown in FIG.
That is, when the “pressure at G” detected by the pressure detection means is higher than the “target pressure” preset as a target, the rotational speed of the compressor 2 is reduced, and when it is lower, the compressor 2 is increased so that the discharge pressure in the vicinity of the discharge port of the compressor 2 is kept constant.

Further, the second flow rate control valve 14 is disposed in the vicinity of the outlet of the indoor heat exchanger 10 so that the outlet temperature in the vicinity of the outlet of the indoor heat exchanger 10 (position indicated by symbol E in FIG. 9) is kept constant. This is an on-off valve whose opening degree is controlled according to a flowchart shown in FIG. 3 based on a signal from a temperature detection means (not shown).
That is, when the “temperature at E” detected by the temperature detection means is higher than the “target temperature” set in advance as a target, the opening of the second flow control valve 14 is reduced, and when it is lower, The opening degree of the second flow rate control valve 14 is increased, and the outlet temperature in the vicinity of the outlet of the indoor heat exchanger 10 is kept constant.

Further, the rotation speed of the transport medium driving device 9 is controlled (inverter control) according to the total load of the indoor cycle 12 (that is, the total load of the indoor heat exchanger 10). Specifically, the rotational speed is adjusted along the solid line in FIG.
That is, when the total load of the indoor cycle 12 is zero, the rotation speed of the transport medium driving device 9 is zero (zero), and when the maximum load is maximum, the rotation speed of the transport medium driving device 9 is maximum. In addition, the rotational speed of the transport medium driving device 9 is linearly changed according to the total load of the indoor cycle 12.

According to the air conditioner 41 according to the present embodiment, the bypass pipe 11a and the first flow control valve 13 that are required in the third embodiment can be eliminated, so that the configuration of the indoor cycle 12 is simplified. Thus, the air conditioner 41 as a whole can be reduced in size, and the manufacturing cost can be reduced.
Other functions and effects are the same as those of the above-described third embodiment, and thus description thereof is omitted here.

5th Embodiment of the air conditioner which concerns on this invention is described based on FIGS. 10-12. FIG. 10 is a schematic configuration diagram of an air conditioner according to a fifth embodiment of the present invention, FIG. 11 is a flowchart for explaining rotation speed control of the compressor shown in FIG. 10, and FIG. 12 is a second flow rate shown in FIG. It is a flowchart for demonstrating the opening degree control of a control valve.
Since the components of the air conditioner 51 according to the present embodiment are the same as those of the first embodiment and the third embodiment described above, description of these components is omitted here.
In addition, the same code | symbol is attached | subjected to the member same as 1st Embodiment and 3rd Embodiment mentioned above.

When the air conditioner 51 configured as in the present embodiment is set to the cooling operation mode, the compressor 2 is in the vicinity of the outlet of the intermediate heat exchanger 6 (the position indicated by the symbol B in FIG. 10). In order to keep the degree of supercooling constant, based on a signal from a supercooling degree detection means (not shown) arranged in the vicinity of the outlet of the intermediate heat exchanger 6, the rotational speed is controlled according to the flowchart shown in FIG. It has become.
That is, when the “supercooling degree in B” detected by the supercooling degree detection means is higher than the “target supercooling degree” set in advance as a target, the rotational speed of the compressor 2 is lowered and low. In this case, the number of rotations of the compressor 2 is increased, and the degree of supercooling in the vicinity of the outlet of the intermediate heat exchanger 6 is kept constant.

Further, the second flow rate control valve 14 is disposed in the vicinity of the outlet of the indoor heat exchanger 10 so that the degree of superheat in the vicinity of the outlet of the indoor heat exchanger 10 (position indicated by reference sign D in FIG. 10) is kept constant. This is an on-off valve whose opening degree is controlled according to a flowchart shown in FIG.
That is, when the “superheat degree at D” detected by the superheat degree detection means is higher than the “target superheat degree” set in advance as a target, the opening degree of the second flow control valve 14 is increased and low. In this case, the opening degree of the second flow rate control valve 14 is reduced, and the degree of superheat near the outlet of the indoor heat exchanger 10 is kept constant.

Furthermore, the first flow control valve 13 is an on-off valve whose opening degree is controlled according to the total load of the indoor cycle 12 (that is, the total load of the indoor heat exchanger 10). The opening degree is adjusted along the solid line in FIG.
That is, when the full load of the indoor cycle 12 is minimum, the opening of the first flow control valve 13 is fully opened, and when the maximum load is maximum, the opening of the first flow control valve 13 is fully closed, and The opening degree of the first flow control valve 13 is linearly changed according to the full load of the indoor cycle 12.

According to the air conditioner 51 according to the present embodiment, during the cooling operation, the rotational speed of the compressor 2 is controlled so that the degree of supercooling in the vicinity of the outlet of the intermediate heat exchanger 6 is kept constant, and indoor heat exchange is performed. The degree of opening of the second flow rate control valve 14 is controlled so that the degree of superheat in the vicinity of the outlet of the vessel 10 is kept constant, and the degree of opening of the first flow rate control valve 13 is set according to the full load of the indoor cycle 12. Since it is controlled, the coefficient of performance corresponding to the energy consumption efficiency of the entire air conditioner 51 can be operated at an efficient (optimum) operating point according to the load of each indoor heat exchanger 10. (COP) can be increased (improved).
In addition, since the transport medium sucked into the transport medium driving device 9 can be kept in a liquid phase state and the efficiency of the transport medium driving device 9 can be increased (improved), the energy consumption efficiency of the entire air conditioner 51 is improved. The coefficient of performance (COP) equivalent to can be further increased (improved).

A sixth embodiment of an air conditioner according to the present invention will be described with reference to FIG. FIG. 13 is a schematic configuration diagram of an air conditioner according to a sixth embodiment of the present invention.
In the air conditioner 61 according to the present embodiment, the bypass pipe 11a and the first flow rate control valve 13 are omitted, and the rotation speed of the transport medium driving device 9 is controlled according to the full load of the indoor cycle 12. It differs from that of the fifth embodiment described above. Since other components are the same as those of the fifth embodiment described above, description of these components is omitted here.
In addition, the same code | symbol is attached | subjected to the member same as 5th Embodiment mentioned above.

When the air conditioner 61 configured as in the present embodiment is set to the cooling operation mode, the compressor 2 is in the vicinity of the outlet of the intermediate heat exchanger 6 (the position indicated by symbol B in FIG. 13). In order to keep the degree of supercooling constant, based on a signal from a supercooling degree detection means (not shown) arranged in the vicinity of the outlet of the intermediate heat exchanger 6, the rotational speed is controlled according to the flowchart shown in FIG. It has become.
That is, when the “supercooling degree in B” detected by the supercooling degree detection means is higher than the “target supercooling degree” set in advance as a target, the rotational speed of the compressor 2 is lowered and low. In this case, the number of rotations of the compressor 2 is increased, and the degree of supercooling in the vicinity of the outlet of the intermediate heat exchanger 6 is kept constant.

Further, the second flow rate control valve 14 is disposed in the vicinity of the outlet of the indoor heat exchanger 10 so that the degree of superheat in the vicinity of the outlet of the indoor heat exchanger 10 (position indicated by reference sign D in FIG. 13) is kept constant. This is an on-off valve whose opening degree is controlled according to a flowchart shown in FIG.
That is, when the “superheat degree at D” detected by the superheat degree detection means is higher than the “target superheat degree” set in advance as a target, the opening degree of the second flow control valve 14 is increased and low. In this case, the opening degree of the second flow rate control valve 14 is reduced, and the degree of superheat near the outlet of the indoor heat exchanger 10 is kept constant.

Further, the rotation speed of the transport medium driving device 9 is controlled (inverter control) according to the total load of the indoor cycle 12 (that is, the total load of the indoor heat exchanger 10). Specifically, the rotational speed is adjusted along the solid line in FIG.
That is, when the total load of the indoor cycle 12 is zero, the rotation speed of the transport medium driving device 9 is zero (zero), and when the maximum load is maximum, the rotation speed of the transport medium driving device 9 is maximum. In addition, the rotational speed of the transport medium driving device 9 is linearly changed according to the total load of the indoor cycle 12.

According to the air conditioner 61 according to the present embodiment, the bypass pipe 11a and the first flow control valve 13 that are required in the fifth embodiment can be eliminated, so that the configuration of the indoor cycle 12 is simplified. Thus, the air conditioner 61 as a whole can be reduced in size, and the manufacturing cost can be reduced.
Other functions and effects are the same as those of the above-described fifth embodiment, and thus description thereof is omitted here.

In the first to sixth embodiments described above, the indoor cycle 12 has four positions at the positions shown in FIG. 14 (that is, in the middle of the pipe 11 that connects the transport medium driving device 9 and the indoor heat exchanger 10). More preferably, a valve 65 is incorporated.
By configuring the indoor cycle 12 in this way, the flow (circulation) direction of the carrier medium can be reversed between the heating operation and the cooling operation, so that the carrier medium driving device 9 can rotate in one direction. (The discharge direction and the suction direction are determined in one direction) can be adopted, and the manufacturing cost can be further reduced.
In addition, the flow direction of the refrigerant that circulates in the outdoor cycle 8 and the flow direction of the carrier medium that circulates in the indoor cycle 12 can be reversed (opposite flow) during heating operation and cooling operation. The heat exchange efficiency in the intermediate heat exchanger 6 can be further increased (improved), and the coefficient of performance (COP) corresponding to the energy consumption efficiency of the entire air conditioner can be further increased (improved).

A seventh embodiment of an air conditioner according to the present invention will be described with reference to FIGS. 15 to 17. FIG. 15 is a schematic configuration diagram of an air conditioner according to a seventh embodiment of the present invention, FIG. 16 is a flowchart for explaining the rotational speed control of the compressor shown in FIG. 15, and FIG. It is a flowchart for demonstrating the opening degree control of 1 flow control valve.
The air conditioner 71 according to the present embodiment is different from that of the first embodiment described above in that the indoor heat exchanger 10 is one and the second flow rate control valve 14 is omitted. Since other components are the same as those of the first embodiment described above, description of these components is omitted here.
In addition, the same code | symbol is attached | subjected to the member same as 1st Embodiment mentioned above.

Now, when the air conditioner 71 comprised like this embodiment is set to heating operation mode, the compressor 2 is in the exit vicinity (position shown with the code | symbol C in FIG. 15) of the intermediate heat exchanger 6. FIG. In order to keep the outlet temperature constant, the rotation speed is controlled according to a flowchart shown in FIG. 16 based on a signal from a temperature detection means (not shown) arranged in the vicinity of the outlet of the intermediate heat exchanger 6. .
That is, when the “temperature at C” detected by the temperature detection means is higher than the “target temperature” set in advance as a target, the rotational speed of the compressor 2 is decreased, and when it is lower, the compressor 2 is increased so that the outlet temperature in the vicinity of the outlet of the intermediate heat exchanger 6 is kept constant.

Further, the first flow rate control valve 13 is at the temperature of the transport medium sucked (inflowed) into the transport medium driving device 9 (that is, in the vicinity of the suction port of the transport medium driving device 9 (the position indicated by the symbol F in FIG. 15)). The vicinity of the inlet of the transport medium driving device 9 or the vicinity of the outlet of the indoor heat exchanger 10 so that the temperature or the vicinity of the outlet of the indoor heat exchanger 10 (the position indicated by symbol E in FIG. 15) is kept constant. This is an on-off valve whose opening degree is controlled according to the flowchart shown in FIG.
That is, when the “temperature at F (or E)” detected by the temperature detection means is higher than the “target temperature” preset as a target, the opening of the first flow control valve 13 is reduced, When it is low, the opening of the first flow rate control valve 13 is increased so that the temperature of the transport medium sucked into (inflows into) the transport medium driving device 9 is kept constant.

According to the air conditioner 71 according to this embodiment, during the heating operation, the rotation speed of the compressor 2 is controlled so as to keep the outlet temperature in the vicinity of the outlet of the intermediate heat exchanger 6 constant, and the carrier medium driving device Since the opening of the first flow rate control valve 13 is controlled so as to keep the temperature of the transport medium sucked into the air 9, the efficiency according to the load of the indoor heat exchanger 10 (optimum) It is possible to operate at the operating point, and to increase (improve) the coefficient of performance (COP) corresponding to the energy consumption efficiency of the entire air conditioner 71.
Further, since the carrier medium sucked into the carrier medium driving device 9 can be kept in a liquid phase state, and the efficiency of the carrier medium driving device 9 can be increased (improved), the energy consumption efficiency of the entire air conditioner 71 is improved. The coefficient of performance (COP) equivalent to can be further increased (improved).

An eighth embodiment of an air conditioner according to the present invention will be described with reference to FIGS. FIG. 18 is a schematic configuration diagram of an air conditioner according to an eighth embodiment of the present invention, and FIG. 19 is a flowchart for explaining the rotational speed control of the transport medium driving device shown in FIG.
In the air conditioner 81 according to the present embodiment, the bypass pipe 11a and the first flow rate control valve 13 are omitted, and the rotational speed of the transport medium driving device 9 determines the temperature of the transport medium sucked into the transport medium driving device 9. It differs from that of the seventh embodiment described above in that it is controlled so as to be kept constant. Since other components are the same as those of the seventh embodiment described above, description of these components is omitted here.
In addition, the same code | symbol is attached | subjected to the member same as 7th Embodiment mentioned above.

Now, when the air conditioner 71 comprised like this embodiment is set to heating operation mode, the compressor 2 is in the exit vicinity (position shown by the code | symbol C in FIG. 18) of the intermediate heat exchanger 6. FIG. In order to keep the outlet temperature constant, the rotation speed is controlled according to a flowchart shown in FIG. 16 based on a signal from a temperature detection means (not shown) arranged in the vicinity of the outlet of the intermediate heat exchanger 6. .
That is, when the “temperature at C” detected by the temperature detection means is higher than the “target temperature” set in advance as a target, the rotational speed of the compressor 2 is decreased, and when it is lower, the compressor 2 is increased so that the outlet temperature in the vicinity of the outlet of the intermediate heat exchanger 6 is kept constant.

Further, the transport medium driving device 9 is at the temperature of the transport medium sucked (inflowed) into the transport medium driving device 9 (that is, in the vicinity of the suction port of the transport medium driving device 9 (the position indicated by the symbol F in FIG. 18)). The vicinity of the inlet of the transport medium driving device 9 or the vicinity of the outlet of the indoor heat exchanger 10 so that the temperature or the vicinity of the outlet of the indoor heat exchanger 10 (the temperature indicated by the symbol E in FIG. 18) is kept constant. The number of revolutions is controlled (inverter control) in accordance with a flowchart shown in FIG.
That is, when the “temperature at F (or E)” detected by the temperature detection means is higher than the “target temperature” set in advance as a target, the rotation speed of the transport medium driving device 9 is increased and low. In this case, the rotational speed of the transport medium driving device 9 is reduced, and the temperature of the transport medium sucked into the transport medium driving device 9 is kept constant.

According to the air conditioner 81 according to the present embodiment, the bypass pipe 11a and the first flow control valve 13 that are required in the seventh embodiment can be eliminated, so that the configuration of the indoor cycle 12 is simplified. Therefore, it is possible to reduce the size of the air conditioner 81 as a whole and to reduce the manufacturing cost.
Other functions and effects are the same as those of the above-described seventh embodiment, and thus description thereof is omitted here.

9th Embodiment of the air conditioner which concerns on this invention is described based on FIG. 20 and FIG. FIG. 20 is a schematic configuration diagram of an air conditioner according to a ninth embodiment of the present invention, and FIG. 21 is a flowchart for explaining the rotational speed control of the compressor shown in FIG.
In the air conditioner 91 according to the present embodiment, the rotational speed of the compressor 2 is controlled so as to keep the discharge pressure in the vicinity of the discharge port of the compressor 2 (the position indicated by the symbol G in FIG. 20) constant. This differs from that of the seventh embodiment described above. Since other components are the same as those of the seventh embodiment described above, description of these components is omitted here.
In addition, the same code | symbol is attached | subjected to the member same as 7th Embodiment mentioned above.

When the air conditioner 91 configured as in the present embodiment is set to the heating operation mode, the compressor 2 has a constant discharge pressure in the vicinity of the discharge port (the position indicated by the symbol G in FIG. 20). Therefore, based on a signal from a pressure detection means (not shown) arranged in the vicinity of the discharge port of the compressor 2, the rotation speed is controlled according to the flowchart shown in FIG.
That is, when the “pressure at G” detected by the pressure detection means is higher than the “target pressure” preset as a target, the rotational speed of the compressor 2 is reduced, and when it is lower, the compressor 2 is increased so that the discharge pressure in the vicinity of the discharge port of the compressor 2 is kept constant.

According to the air conditioner 91 according to the present embodiment, during the heating operation, the rotation speed of the compressor 2 is controlled so as to keep the discharge pressure in the vicinity of the discharge port of the compressor 2 constant, and the carrier medium driving device 9. Since the opening degree of the first flow rate control valve 13 is controlled so as to keep the temperature of the transport medium sucked into the chamber constant, it is efficient (optimal according to the load of the indoor heat exchanger 10). ) It can be operated at the operating point, and the coefficient of performance (COP) corresponding to the energy consumption efficiency of the entire air conditioner 91 can be increased (improved).
Further, since the transport medium sucked into the transport medium driving device 9 can be kept in a liquid phase state, and the efficiency of the transport medium driving device 9 can be increased (improved), the energy consumption efficiency of the entire air conditioner 91 is increased. The coefficient of performance (COP) equivalent to can be further increased (improved).

A tenth embodiment of an air conditioner according to the present invention will be described with reference to FIG. FIG. 22 is a schematic configuration diagram of an air conditioner according to a tenth embodiment of the present invention.
In the air conditioner 101 according to the present embodiment, the bypass pipe 11a and the first flow rate control valve 13 are omitted, and the rotational speed of the transport medium driving device 9 determines the temperature of the transport medium sucked into the transport medium driving device 9. It differs from that of the ninth embodiment described above in that it is controlled so as to be kept constant. Since other components are the same as those of the ninth embodiment described above, description of these components is omitted here.
In addition, the same code | symbol is attached | subjected to the member same as 9th Embodiment mentioned above.

Now, when the air conditioner 101 configured as in the present embodiment is set to the heating operation mode, the compressor 2 has a constant discharge pressure in the vicinity of the discharge port (the position indicated by the symbol G in FIG. 22). Therefore, based on a signal from a pressure detection means (not shown) arranged in the vicinity of the discharge port of the compressor 2, the rotation speed is controlled according to the flowchart shown in FIG.
That is, when the “pressure at G” detected by the pressure detection means is higher than the “target pressure” preset as a target, the rotational speed of the compressor 2 is reduced, and when it is lower, the compressor 2 is increased so that the discharge pressure in the vicinity of the discharge port of the compressor 2 is kept constant.

Further, the transport medium driving device 9 is at the temperature of the transport medium sucked (inflowed) into the transport medium driving device 9 (that is, in the vicinity of the suction port of the transport medium driving device 9 (the position indicated by the symbol F in FIG. 22)). From temperature detection means (not shown) disposed near the suction port of the transport medium driving device 9 so as to keep the temperature or the vicinity of the outlet of the indoor heat exchanger 10 (the temperature indicated by the symbol E in FIG. 22) constant. Based on this signal, the rotational speed is controlled according to the flowchart shown in FIG.
That is, when the “temperature at F (or E)” detected by the temperature detection means is higher than the “target temperature” set in advance as a target, the rotation speed of the transport medium driving device 9 is increased and low. In this case, the rotational speed of the transport medium driving device 9 is reduced, and the temperature of the transport medium sucked into the transport medium driving device 9 is kept constant.

According to the air conditioner 101 according to the present embodiment, the bypass pipe 11a and the first flow rate control valve 13 required in the ninth embodiment can be eliminated, and thus the configuration of the indoor cycle 12 is simplified. Thus, the air conditioner 101 as a whole can be reduced in size and the manufacturing cost can be reduced.
Other functions and effects are the same as those of the ninth embodiment described above, and a description thereof is omitted here.

11th Embodiment of the air conditioner which concerns on this invention is described based on FIG. 23 and FIG. FIG. 23 is a schematic configuration diagram of an air conditioner according to an eleventh embodiment of the present invention, and FIG. 24 is a flowchart for explaining the rotational speed control of the compressor shown in FIG.
Since the components of the air conditioner 111 according to this embodiment are the same as those of the seventh embodiment and the ninth embodiment described above, description of these components is omitted here.
In addition, the same code | symbol is attached | subjected to the member same as 7th Embodiment and 9th Embodiment mentioned above.

Now, when the air conditioner 111 comprised like this embodiment is set to the air_conditionaing | cooling operation mode, the compressor 2 is in the exit vicinity (position shown with the code | symbol B in FIG. 23) of the intermediate heat exchanger 6. In order to keep the degree of supercooling constant, based on a signal from a supercooling degree detection means (not shown) arranged in the vicinity of the outlet of the intermediate heat exchanger 6, the rotation speed is controlled according to the flowchart shown in FIG. It has become.
That is, when the “supercooling degree in B” detected by the supercooling degree detection means is higher than the “target supercooling degree” set in advance as a target, the rotational speed of the compressor 2 is lowered and low. In this case, the number of rotations of the compressor 2 is increased, and the degree of supercooling in the vicinity of the outlet of the intermediate heat exchanger 6 is kept constant.

The first flow rate control valve 13 is overheated in the vicinity of the inlet of the intermediate heat exchanger 6 (position indicated by symbol C in FIG. 23) or in the vicinity of the outlet of the indoor heat exchanger 10 (position indicated by symbol D in FIG. 23). Based on a signal from a superheat degree detection means (not shown) arranged near the inlet of the intermediate heat exchanger 6 or near the outlet of the indoor heat exchanger 10 so as to keep the temperature constant, the opening is opened according to the flowchart shown in FIG. An on-off valve whose degree is controlled.
That is, when the “superheat degree in D (or C)” detected by the superheat degree detection means is higher than the “target superheat degree” set in advance as a target, the opening degree of the first flow control valve 13 is increased. If it is increased and lower, the opening degree of the first flow control valve 13 is decreased so that the degree of superheat near the inlet of the intermediate heat exchanger 6 or the outlet of the indoor heat exchanger 10 is kept constant. It has become.

According to the air conditioner 111 according to the present embodiment, during the cooling operation, the rotational speed of the compressor 2 is controlled so that the degree of supercooling in the vicinity of the outlet of the intermediate heat exchanger 6 is kept constant, and the intermediate heat exchange is performed. Since the opening degree of the first flow rate control valve 13 is controlled so that the degree of superheat in the vicinity of the inlet of the heat exchanger 6 or in the vicinity of the outlet of the indoor heat exchanger 10 is kept constant, the load on the indoor heat exchanger 10 It is possible to operate at an efficient (optimal) operating point according to the above, and to increase (improve) the coefficient of performance (COP) corresponding to the energy consumption efficiency of the entire air conditioner 111.
Further, since the transport medium sucked into the transport medium driving device 9 can be kept in a liquid phase state, and the efficiency of the transport medium driving device 9 can be increased (improved), the energy consumption efficiency of the entire air conditioner 111 is improved. The coefficient of performance (COP) equivalent to can be further increased (improved).

A twelfth embodiment of an air conditioner according to the present invention will be described with reference to FIG. FIG. 25 is a schematic configuration diagram of an air conditioner according to a twelfth embodiment of the present invention.
In the air conditioner 121 according to this embodiment, the bypass pipe 11a and the first flow rate control valve 13 are omitted, and the rotation speed of the transport medium driving device 9 keeps the degree of superheat of the transport medium flowing into the intermediate heat exchanger 6 constant. It is different from that of the eleventh embodiment described above in that it is controlled so as to maintain the above. Since other components are the same as those of the eleventh embodiment described above, description of these components is omitted here.
In addition, the same code | symbol is attached | subjected to the member same as 11th Embodiment mentioned above.

Now, when the air conditioner 121 configured as in the present embodiment is set to the cooling operation mode, the compressor 2 is in the vicinity of the outlet of the intermediate heat exchanger 6 (the position indicated by the symbol B in FIG. 25). In order to keep the degree of supercooling constant, based on a signal from a supercooling degree detection means (not shown) arranged in the vicinity of the outlet of the intermediate heat exchanger 6, the rotation speed is controlled according to the flowchart shown in FIG. It has become.
That is, when the “supercooling degree in B” detected by the supercooling degree detection means is higher than the “target supercooling degree” set in advance as a target, the rotational speed of the compressor 2 is lowered and low. In this case, the number of rotations of the compressor 2 is increased, and the degree of supercooling in the vicinity of the outlet of the intermediate heat exchanger 6 is kept constant.

Further, the transport medium driving device 9 has a degree of superheat in the vicinity of the inlet of the intermediate heat exchanger 6 (a position indicated by a symbol C in FIG. 25) or in the vicinity of the outlet of the indoor heat exchanger 10 (a position indicated by a symbol D in FIG. 25). Is controlled based on a signal from a superheat degree detection means (not shown) arranged near the inlet of the intermediate heat exchanger 6 or near the outlet of the indoor heat exchanger 10 (inverter control). Is done.
That is, when the “superheat degree in C (or D)” detected by the superheat degree detection means is higher than the “target superheat degree” set in advance as a target, the rotation speed of the transport medium driving device 9 increases. If it is low, the rotational speed of the transport medium driving device 9 is reduced so that the degree of superheat near the inlet of the intermediate heat exchanger 6 or the outlet of the indoor heat exchanger 10 is kept constant. It has become.

According to the air conditioner 121 according to the present embodiment, the bypass pipe 11a and the first flow control valve 13 that are required in the eleventh embodiment can be eliminated, so that the configuration of the indoor cycle 12 is simplified. Thus, the air conditioner 121 as a whole can be reduced in size, and the manufacturing cost can be reduced.
Other functions and effects are the same as those of the above-described eleventh embodiment, and a description thereof is omitted here.

Note that in the seventh to twelfth embodiments described above, the four-way operation is performed at the position shown in FIG. 26 of the indoor cycle 12 (that is, in the middle of the pipe 11 communicating the transport medium driving device 9 and the indoor heat exchanger 10). More preferably, a valve 125 is incorporated.
By configuring the indoor cycle 12 in this way, the flow (circulation) direction of the carrier medium can be reversed between the heating operation and the cooling operation, so that the carrier medium driving device 9 can rotate in one direction. (The discharge direction and the suction direction are determined in one direction) can be adopted, and the manufacturing cost can be further reduced.
In addition, the flow direction of the refrigerant that circulates in the outdoor cycle 8 and the flow direction of the carrier medium that circulates in the indoor cycle 12 can be reversed (opposite flow) during heating operation and cooling operation. The heat exchange efficiency in the intermediate heat exchanger 6 can be further increased (improved), and the coefficient of performance (COP) corresponding to the energy consumption efficiency of the entire air conditioner can be further increased (improved).

  In the above-described embodiment, the example in which the heat transfer system according to the present invention is applied to an air conditioner has been described. However, the heat transfer system according to the present invention is not only applicable to an air conditioner. It can also be applied to other than air conditioners.

  In the above-described embodiment, the pressure of the carrier medium circulating in the indoor cycle 12 is pressurized to the supercritical region during heating and is reduced to a critical pressure or lower during cooling.

1 is a schematic configuration diagram of an air conditioner according to a first embodiment of the present invention. It is a flowchart for demonstrating the rotation speed control of the compressor shown in FIG. It is a flowchart for demonstrating the opening degree control of the 2nd flow control valve shown in FIG. It is a graph which shows the relationship between the opening degree of the 1st flow control valve shown in FIG. 1, and the full load of an indoor cycle. It is a schematic block diagram of the air conditioner which concerns on 2nd Embodiment of this invention. It is a graph which shows the relationship between the rotation speed of the conveyance medium drive device shown in FIG. 5, and the full load of an indoor cycle. It is a schematic block diagram of the air conditioner which concerns on 3rd Embodiment of this invention. It is a flowchart for demonstrating rotation speed control of the compressor shown in FIG. It is a schematic block diagram of the air conditioner which concerns on 4th Embodiment of this invention. It is a schematic block diagram of the air conditioner which concerns on 5th Embodiment of this invention. It is a flowchart for demonstrating the rotation speed control of the compressor shown in FIG. It is a flowchart for demonstrating the opening degree control of the 2nd flow control valve shown in FIG. It is a schematic block diagram of the air conditioner which concerns on 6th Embodiment of this invention. It is a schematic block diagram which shows other embodiment of the air conditioner which concerns on this invention. It is a schematic block diagram of the air conditioner which concerns on 7th Embodiment of this invention. It is a flowchart for demonstrating rotation speed control of the compressor shown in FIG. It is a flowchart for demonstrating the opening degree control of the 1st flow control valve shown in FIG. It is a schematic block diagram of the air conditioner which concerns on 8th Embodiment of this invention. It is a flowchart for demonstrating rotation speed control of the conveyance medium drive device shown in FIG. It is a schematic block diagram of the air conditioner which concerns on 9th Embodiment of this invention. It is a flowchart for demonstrating rotation speed control of the compressor shown in FIG. It is a schematic block diagram of the air conditioner which concerns on 10th Embodiment of this invention. It is a schematic block diagram of the air conditioner which concerns on 11th Embodiment of this invention. It is a flowchart for demonstrating rotation speed control of the compressor shown in FIG. It is a schematic block diagram of the air conditioner which concerns on 12th Embodiment of this invention. It is a schematic block diagram which shows another embodiment of the air conditioner which concerns on this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Air conditioner 2 Compressor 4 Outdoor heat exchanger 5 Expansion valve (pressure reduction means)
6 Intermediate heat exchanger 8 Outdoor cycle (primary cycle)
9 Conveying medium driving device 10 Indoor heat exchanger 12 Indoor cycle (secondary cycle)
14 Second flow control valve (flow control valve)
DESCRIPTION OF SYMBOLS 21 Air conditioner 31 Air conditioner 41 Air conditioner 51 Air conditioner 61 Air conditioner 65 Four way valve 71 Air conditioner 81 Air conditioner 91 Air conditioner 101 Air conditioner 111 Air conditioner 121 Air conditioner 125 Four way valve

Claims (9)

A compressor that compresses the refrigerant, an intermediate heat exchanger through which the refrigerant and the carrier medium pass, a decompression unit that decompresses and expands the refrigerant to form a low-temperature and low-pressure refrigerant, and heat exchange between the refrigerant that passes through the interior and the outside air A closed cycle primary cycle comprising an outdoor heat exchanger
A closed circuit comprising a transport medium driving device for circulating a transport medium, the intermediate heat exchanger, and a plurality of indoor heat exchangers for exchanging heat between the transport medium passing through the interior and air blown into the room. A secondary cycle,
In the intermediate heat exchanger, an air conditioner for exchanging heat between the refrigerant circulating in the primary side cycle and the transport medium circulating in the secondary side cycle,
During the heating operation, the rotation speed of the compressor is controlled so that the temperature of the transport medium that has passed through the intermediate heat exchanger is kept constant, and
While controlling the opening degree of the flow control valve respectively disposed on the downstream side of the indoor heat exchanger so that the temperature of the transport medium that has passed through each indoor heat exchanger is kept constant,
Air conditioning characterized by comprising control means for controlling the flow rate of the transport medium discharged from the transport medium driving device and flowing into the intermediate heat exchanger according to the total load of the indoor heat exchanger Machine. A compressor that compresses the refrigerant, an intermediate heat exchanger through which the refrigerant and the carrier medium pass, a decompression unit that decompresses and expands the refrigerant to form a low-temperature and low-pressure refrigerant, and heat exchange between the refrigerant that passes through the interior and the outside air A closed cycle primary cycle comprising an outdoor heat exchanger
A closed circuit comprising a transport medium driving device for circulating a transport medium, the intermediate heat exchanger, and a plurality of indoor heat exchangers for exchanging heat between the transport medium passing through the interior and air blown into the room. A secondary cycle,
In the intermediate heat exchanger, an air conditioner for exchanging heat between the refrigerant circulating in the primary side cycle and the transport medium circulating in the secondary side cycle,
During the heating operation, the rotation speed of the compressor is controlled so that the discharge pressure of the compressor is kept constant, and
While controlling the opening degree of the flow control valve respectively disposed on the downstream side of the indoor heat exchanger so that the temperature of the transport medium that has passed through each indoor heat exchanger is kept constant,
Air conditioning characterized by comprising control means for controlling the flow rate of the transport medium discharged from the transport medium driving device and flowing into the intermediate heat exchanger according to the total load of the indoor heat exchanger Machine. A compressor that compresses the refrigerant, an intermediate heat exchanger through which the refrigerant and the carrier medium pass, a decompression unit that decompresses and expands the refrigerant to form a low-temperature and low-pressure refrigerant, and heat exchange between the refrigerant that passes through the interior and the outside air A closed cycle primary cycle comprising an outdoor heat exchanger
A closed circuit comprising a transport medium driving device for circulating a transport medium, the intermediate heat exchanger, and a plurality of indoor heat exchangers for exchanging heat between the transport medium passing through the interior and air blown into the room. A secondary cycle,
In the intermediate heat exchanger, an air conditioner for exchanging heat between the refrigerant circulating in the primary side cycle and the transport medium circulating in the secondary side cycle,
During the cooling operation, the rotation speed of the compressor is controlled so that the degree of supercooling of the transport medium that has passed through the intermediate heat exchanger is kept constant, and
While controlling the opening degree of the flow control valve respectively disposed on the upstream side of the indoor heat exchanger so that the degree of superheat of the transport medium that has passed through each indoor heat exchanger is kept constant,
Air conditioning characterized by comprising control means for controlling the flow rate of the transport medium discharged from the transport medium driving device and flowing into the indoor heat exchanger according to the total load of the indoor heat exchanger Machine. A compressor that compresses the refrigerant, an intermediate heat exchanger through which the refrigerant and the carrier medium pass, a decompression unit that decompresses and expands the refrigerant to form a low-temperature and low-pressure refrigerant, and heat exchange between the refrigerant that passes through the interior and the outside air A closed cycle primary cycle comprising an outdoor heat exchanger
A closed circuit comprising a transport medium driving device for circulating a transport medium, the intermediate heat exchanger, and a single indoor heat exchanger for exchanging heat between the transport medium passing through the interior and air blown into the room. A secondary cycle,
In the intermediate heat exchanger, an air conditioner for exchanging heat between the refrigerant circulating in the primary side cycle and the transport medium circulating in the secondary side cycle,
During the heating operation, the rotation speed of the compressor is controlled so that the temperature of the transport medium that has passed through the intermediate heat exchanger is kept constant, and
Control means for controlling the flow rate of the transport medium discharged from the transport medium drive device and flowing into the intermediate heat exchanger so that the temperature of the transport medium sucked into the transport medium drive device is kept constant. An air conditioner characterized by A compressor that compresses the refrigerant, an intermediate heat exchanger through which the refrigerant and the carrier medium pass, a decompression unit that decompresses and expands the refrigerant to form a low-temperature and low-pressure refrigerant, and heat exchange between the refrigerant that passes through the interior and the outside air A closed cycle primary cycle comprising an outdoor heat exchanger
A closed circuit comprising a transport medium driving device for circulating a transport medium, the intermediate heat exchanger, and a single indoor heat exchanger for exchanging heat between the transport medium passing through the interior and air blown into the room. A secondary cycle,
In the intermediate heat exchanger, an air conditioner for exchanging heat between the refrigerant circulating in the primary side cycle and the transport medium circulating in the secondary side cycle,
During the heating operation, the rotation speed of the compressor is controlled so that the discharge pressure of the compressor is kept constant, and
Control means for controlling the flow rate of the transport medium discharged from the transport medium drive device and flowing into the intermediate heat exchanger so that the temperature of the transport medium sucked into the transport medium drive device is kept constant. An air conditioner characterized by A compressor that compresses the refrigerant, an intermediate heat exchanger through which the refrigerant and the carrier medium pass, a decompression unit that decompresses and expands the refrigerant to form a low-temperature and low-pressure refrigerant, and heat exchange between the refrigerant that passes through the interior and the outside air A closed cycle primary cycle comprising an outdoor heat exchanger
A closed circuit comprising a transport medium driving device for circulating a transport medium, the intermediate heat exchanger, and a single indoor heat exchanger for exchanging heat between the transport medium passing through the interior and air blown into the room. A secondary cycle,
In the intermediate heat exchanger, an air conditioner for exchanging heat between the refrigerant circulating in the primary side cycle and the transport medium circulating in the secondary side cycle,
During the cooling operation, the rotation speed of the compressor is controlled so that the degree of supercooling of the transport medium that has passed through the intermediate heat exchanger is kept constant, and
Control means for controlling the flow rate of the transport medium discharged from the transport medium driving device and flowing into the indoor heat exchanger so that the degree of superheat of the transport medium flowing into the intermediate heat exchanger is kept constant. An air conditioner characterized by   The four-way valve which switches the flow path of the conveyance medium discharged from the said conveyance medium drive device according to the operation mode in the said secondary side cycle is provided. Air conditioner as described in.   The transport medium driving device is configured to be rotatable forward and backward, and the rotation direction is selected according to the operation mode, and the discharge direction is reversed. The air conditioner according to one item.   The air conditioner according to any one of claims 1 to 8, wherein the carrier medium is a carbon dioxide refrigerant.

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