JP2005241090A - Combination type air conditioning equipment and its operating method - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a combination type air conditioning equipment and its operating method capable of allowing an air conditioner and a refrigeration cycle device to sufficiently exercise their performances while sharing an outdoor machine and an air blower. <P>SOLUTION: In this air conditioning/refrigerating/freezing equipment (combination type air conditioning equipment) 1 comprising a refrigeration cycle device (refrigerating device 3 and freezing device 4) in addition to the air conditioner 2, refrigerant circuits 22, 32 of the refrigeration cycle device are divided into heat exchanging flow channels 22a, 32a where outdoor heat exchangers are mounted, and bypass flow channels 22b, 32b connected to a downstream side of the outdoor heat exchangers of the refrigerant circuits, at an upstream side of the outdoor heat exchangers 25, 35. The heat exchanging flow channels and the bypass flow channels are respectively connected through high-pressure control valves 27, 37, so that the refrigerant supply pressure to a downstream side of the high-pressure control valves can be kept in the refrigerant circuit. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a composite air conditioner and an operation method thereof.

For example, in large stores and convenience stores, in addition to air conditioning devices that heat or cool the stores, refrigeration devices that store or display drinking water or food in a refrigerated state, ice, ice cream, frozen foods, etc. A refrigeration cycle apparatus such as a refrigeration apparatus that stores or displays the above in a frozen state is provided.
Thus, for example, a combined air conditioning system described in Patent Document 1 described below is used in a store including an air conditioning apparatus and a refrigeration cycle apparatus.
This combined air conditioning system is configured to connect an air conditioner side indoor unit and a refrigerator side indoor unit to the same outdoor unit (outdoor unit) and operate with the same refrigerant circuit.

Japanese Patent Laid-Open No. 10-2629 (paragraph [0010] and FIG. 1)

  However, in the outdoor unit, the outside air is supplied to the air conditioner and the refrigeration cycle apparatus by the same blower. For this reason, the air volume of the air blower may not be appropriate for either the air conditioner or the refrigeration cycle apparatus.

For example, if the air flow of the blower is increased in order to increase the amount of heat exchange by the outdoor heat exchanger in the air conditioner, the air flow of the blower becomes too large for the refrigeration cycle device, and the outdoor of the refrigeration cycle device The heat exchange by the heat exchanger sometimes progressed too much.
In this case, in the refrigerant circuit of the refrigeration cycle apparatus, the refrigerant supply pressure to the downstream side of the outdoor heat exchanger decreases, and the refrigerant circulation in the refrigerant circuit is not smoothly performed. The capacity decreases, and the efficiency of the refrigeration cycle apparatus decreases.

  Specifically, in the winter season, the air conditioner must have a strong heating capability. However, because the outdoor air temperature is low, the air conditioner must be blown to evaporate the refrigerant in the outdoor heat exchanger (evaporator). It is necessary to increase the blast volume of the device. However, since the outside air temperature is low, if the amount of air blown from the blower is increased, the amount of air blown is too large for the refrigeration cycle device, and heat exchange by the outdoor heat exchanger of the refrigeration cycle device proceeds excessively, and the refrigeration cycle device This reduces the capacity of the refrigeration cycle apparatus and reduces the efficiency of the refrigeration cycle apparatus.

On the other hand, if the amount of air blown from the blower is set in accordance with the appropriate amount of heat exchange of the refrigeration cycle device, the air conditioner may have insufficient heat exchange by the outdoor heat exchanger.
In this case, the refrigerant pressure on the upstream side of the outdoor heat exchanger in the refrigerant circuit of the air conditioner is increased, which puts a burden on the compressor of the air conditioner and reduces the efficiency of the air conditioner. End up.

  Specifically, in the summer, the air conditioner is required to have a strong cooling capacity. However, because the outdoor temperature is high, the air conditioner must be blown to condense the refrigerant with the outdoor heat exchanger (condenser). It is necessary to increase the blast volume of the device. However, if the air flow rate of the air blower is set according to the appropriate heat exchange amount of the refrigeration cycle device, the air flow rate is too small for the air conditioner, and heat exchange by the outdoor heat exchanger of the air conditioner is not possible. It becomes insufficient and the efficiency of the air conditioner decreases.

In addition, during the heating operation of the air conditioner, the amount of heat exchange by the outdoor heat exchanger of the air conditioner is reduced or reduced in order to remove frost attached to the outdoor heat exchanger of the air conditioner and restore the heat exchange efficiency. Defrost operation may be performed to stop heat exchange.
However, at the time of defrosting operation, it is necessary to reduce the amount of air blown by the blower or to stop blowing. Thus, in the state which stopped the air blower, the heat exchange amount of the outdoor heat exchanger of a refrigerating cycle device is also reduced, and the condensation amount of the refrigerant | coolant by an outdoor heat exchanger reduces. For this reason, if the blower is stopped for a long time, the supply pressure of the refrigerant to the outdoor heat exchanger of the refrigeration cycle apparatus rises above the range suitable for efficient operation of the refrigeration cycle apparatus, and the refrigeration cycle The efficiency of the device is reduced.

  The present invention has been made in view of such circumstances, and is a composite type air that can fully exhibit the performances of the air conditioner and the refrigeration cycle apparatus while sharing the outdoor unit and the blower. It aims at providing harmony equipment and its operating method.

In order to solve the above problems, the composite air conditioning equipment and the operation method thereof according to the present invention employ the following means.
That is, the composite air conditioning equipment according to the present invention is a composite air conditioning equipment including an air conditioning apparatus and a refrigeration cycle apparatus in which refrigerant circuits including an outdoor heat exchanger and other components are independently provided. And a single outdoor unit in which the outdoor heat exchanger of each refrigerant circuit is housed, and a blower device that takes outside air into the outdoor unit and contacts the outdoor heat exchanger. The refrigerant circuit of the refrigeration cycle apparatus is connected upstream of the outdoor heat exchanger, to a heat exchange channel in which the outdoor heat exchanger is provided, and to a downstream side of the outdoor heat exchanger of the refrigerant circuit. The heat exchange channel and the bypass channel are connected via a high-pressure control valve, and the supply pressure of the refrigerant to the downstream side of the high-pressure control valve is maintained. Came to be And said that you are.

In addition to the air conditioner, this complex air conditioner has at least one refrigeration cycle apparatus such as a refrigeration apparatus or a refrigeration apparatus. Each of these air conditioners and refrigeration cycle apparatuses has a refrigerant circuit including an outdoor heat exchanger and other components, and each refrigerant circuit has an independent configuration.
The outdoor heat exchanger of each refrigerant circuit is installed in one outdoor unit, and by operating the air blower, it is brought into contact with the outside air taken into the outdoor unit by the air blower, Heat exchange is performed between the refrigerant flowing through the outside air and the outside air taken into the outdoor unit by the blower.

In this combined air conditioning system, the refrigerant circuit of the refrigeration cycle apparatus is provided with a high-pressure control valve at the junction of the heat exchange flow path in which the outdoor heat exchanger is provided and the bypass flow path that bypasses the outdoor heat exchanger. It has been.
When the pressure of the refrigerant flowing through the heat exchange channel decreases, the high pressure control valve reduces the amount of refrigerant flowing from the heat exchange channel to the downstream side or stops the refrigerant flow, The supply pressure of the refrigerant to the downstream side is maintained by increasing the circulation amount of the refrigerant from the bypass channel to the downstream side. Here, the high pressure control valve maximizes the amount of refrigerant flowing downstream from the heat exchange flow path when the refrigerant pressure flowing through the heat exchange flow path is within an appropriate range, The flow of the refrigerant from the bypass flow path to the downstream side is stopped.

In this refrigeration cycle apparatus for a combined air conditioning facility, when the refrigerant pressure in the heat exchange flow path falls below a preferred range due to excessive heat exchange in the outdoor heat exchanger, the high pressure control valve In the refrigerant circuit, the amount of refrigerant flowing from the heat exchange channel to the downstream side is reduced or the refrigerant flow is stopped, so that the refrigerant stays in the heat exchange channel.
As a result, the effective heat exchange area of the outdoor heat exchanger is reduced, so that the condensation of the refrigerant in the outdoor heat exchanger is difficult to proceed, and the excessive condensation of the refrigerant is suppressed.
On the other hand, since the flow rate of the refrigerant from the bypass flow path to the downstream side is increased by the high pressure control valve, the supply pressure of the refrigerant to the downstream side is maintained.

  In addition, when the refrigerant pressure in the heat exchange channel is within a preferable range, the amount of refrigerant flowing from the bypass channel to the downstream side is reduced or the refrigerant flow is stopped, while the heat exchange The amount of refrigerant flowing from the flow path to the downstream side is increased, and the supply pressure of the refrigerant to the downstream side is maintained.

Thus, in this combined air conditioning facility, the refrigerant supply pressure to the downstream side by the high-pressure control valve of the refrigeration cycle apparatus (refrigerant supply pressure to the member provided on the downstream side of the outdoor heat exchanger in the refrigerant circuit) Therefore, the performance of the refrigeration cycle apparatus is maintained regardless of the air volume of the air blower.
Thereby, in this combined type air conditioning facility, the performance of the refrigeration cycle apparatus can be maintained while the blower is operated in accordance with the operating conditions of the air conditioner and the performance of the air conditioner is sufficiently exhibited. .

  A combined air conditioning facility according to the present invention is a combined air conditioning facility including an air conditioner and a refrigeration cycle device in which refrigerant circuits including an outdoor heat exchanger and other components are independently provided. The outdoor heat exchanger of each refrigerant circuit is housed in one outdoor unit, and an air blower that takes outside air into the outdoor unit and contacts the outdoor heat exchanger. The refrigerant circuit of the cycle device is provided with a refrigeration cycle-side refrigerant pressure measuring device that measures the pressure of the refrigerant supplied to the outdoor heat exchanger, and the refrigerant circuit of the refrigeration cycle device includes the outdoor heat. The heat exchanger is branched on the upstream side of the exchanger into a heat exchange channel provided with the outdoor heat exchanger and a bypass channel connected to the downstream side of the outdoor heat exchanger of the refrigerant circuit, and the heat exchange In the flow path, A first flow rate control valve for adjusting the flow rate of the refrigerant flowing through the heat exchange flow path is provided downstream of the external heat exchanger, and the bypass flow path flows through the bypass flow path. A second flow rate control valve for adjusting the flow rate of the refrigerant is provided.

In addition to the air conditioner, this complex air conditioner has at least one refrigeration cycle apparatus such as a refrigeration apparatus or a refrigeration apparatus. Each of these air conditioners and refrigeration cycle apparatuses has a refrigerant circuit including an outdoor heat exchanger and other components, and each refrigerant circuit has an independent configuration.
The outdoor heat exchanger of each refrigerant circuit is installed in one outdoor unit, and by operating the air blower, it is brought into contact with the outside air taken into the outdoor unit by the air blower, Heat exchange is performed between the refrigerant flowing through the outside air and the outside air taken into the outdoor unit by the blower.

In this combined air conditioning facility, the refrigerant pressure supplied to the outdoor heat exchanger (refrigerant pressure in the outdoor heat exchanger) of the refrigerant circuit of the refrigeration cycle apparatus is measured by the refrigerant pressure measuring device on the refrigeration cycle side. ing.
The refrigerant circuit of the refrigeration cycle apparatus is provided with a first flow rate control valve on the downstream side of the outdoor heat exchanger in the heat exchange flow path. By operating this first flow rate control valve, The amount of refrigerant flowing to the downstream side can be controlled.
Further, the refrigerant circuit of the refrigeration cycle apparatus is provided with a second flow rate control valve in a bypass flow path that bypasses the outdoor heat exchanger. By operating this second flow rate control valve, the second flow rate control valve is downstream. The amount of refrigerant flowing to the side can be controlled.

In this combined air conditioning facility, the supply pressure of the refrigerant to the member provided on the downstream side of the outdoor heat exchanger in the refrigerant circuit is maintained by operating the first and second flow control valves of the refrigeration cycle apparatus. Therefore, the performance of the refrigeration cycle apparatus is maintained regardless of the amount of air blown by the blower.
Thereby, in this combined type air conditioning facility, the performance of the refrigeration cycle apparatus can be maintained while the blower is operated in accordance with the operating conditions of the air conditioner and the performance of the air conditioner is sufficiently exhibited. .

Hereinafter, the operation of this combined air conditioning facility will be described.
Here, in the refrigeration cycle apparatus, when the refrigerant pressure in the heat exchange flow path decreases due to excessive heat exchange in the outdoor heat exchanger, the pressure of the refrigerant supplied to the outdoor heat exchanger (Refrigerant pressure on the upstream side of the outdoor heat exchanger in the refrigerant circuit) also decreases. That is, in the refrigeration cycle apparatus, the supply pressure of the refrigerant to the downstream side of the heat exchange channel can be known based on the pressure of the refrigerant supplied to the outdoor heat exchanger.
Therefore, when the pressure of the refrigerant supplied to the outdoor heat exchanger falls below the preferable range, is the first flow control valve operated to reduce the refrigerant flow rate downstream from the heat exchange flow path? Or stop the flow of refrigerant.

As a result, since the refrigerant stays in the heat exchange flow path, the effective heat exchange area of the outdoor heat exchanger decreases, and it becomes difficult for the refrigerant to condense in the outdoor heat exchanger and excessive refrigerant condensation occurs. It can be suppressed.
In parallel with the operation of the first flow control valve, the second flow control valve is operated to increase the amount of refrigerant flowing from the bypass flow path to the downstream side, thereby supplying the refrigerant to the downstream side. Pressure is maintained.
Here, when the pressure of the refrigerant supplied to the outdoor heat exchanger in the refrigerant circuit of the refrigeration cycle apparatus is within a preferable range, the second flow rate control valve is operated to flow the refrigerant from the bypass flow path to the downstream side. While reducing the flow rate or stopping the flow of the refrigerant, operating the first flow control valve to increase the flow rate of the refrigerant from the heat exchange flow path to the downstream side, The refrigerant heat-exchanged by the heat exchanger is supplied at a sufficient pressure.

Thus, in this composite air conditioning facility, by performing the above operation, the supply pressure of the refrigerant to the member provided on the downstream side of the outdoor heat exchanger in the refrigerant circuit of the refrigeration cycle apparatus can be maintained. Therefore, the performance of the refrigeration cycle apparatus is maintained regardless of the amount of air blown by the blower.
Thereby, in this combined type air conditioning facility, the performance of the refrigeration cycle apparatus can be maintained while the blower is operated in accordance with the operating conditions of the air conditioner and the performance of the air conditioner is sufficiently exhibited. .
Moreover, since the above-mentioned operation / effect can be obtained without using an expensive high-pressure control valve, the equipment cost can be reduced.

  The composite air conditioning equipment is provided with a control device that controls the opening degree of each of the first and second flow rate control valves based on the measurement value of the refrigerant pressure measuring device on the refrigeration cycle side. When the measured value of the refrigerant pressure measuring device on the refrigeration cycle side is lower than the lower reference value, the opening of the second flow control valve is increased while the opening of the first flow control valve is reduced. It may be said.

In the composite air conditioning equipment configured as described above, the opening degrees of the first and second flow rate control valves are automatically controlled by the control device, so that the refrigeration cycle device is always operated under optimum conditions. be able to.
Here, the lower limit side reference value, which is a criterion for control of the first and second flow control valves by the control device, is a value that allows the refrigeration cycle device to always operate under optimum conditions. The value is obtained by an experimental method or an analytical method based on the configuration of the refrigeration cycle apparatus.

  A combined air conditioning facility according to the present invention is a combined air conditioning facility including an air conditioner and a refrigeration cycle device in which refrigerant circuits including an outdoor heat exchanger and other components are independently provided. One outdoor unit in which the outdoor heat exchanger of each refrigerant circuit is housed, a blower device that takes outside air into the outdoor unit and contacts the outdoor heat exchanger, and the outdoor of the refrigeration cycle apparatus A refrigeration cycle side pressure measuring device that measures the pressure of the refrigerant supplied to the heat exchanger, and a low pressure that measures the pressure of the refrigerant that has passed through the outdoor heat exchanger of the air conditioner when the heating cycle of the air conditioner is formed A side pressure measuring device, and a control device for controlling the operation of the blower device based on the measured values of the refrigeration cycle side pressure measuring device and the low pressure side pressure measuring device, When the heating cycle of the air conditioner is formed, the control device has a measurement value of the low pressure side pressure measuring device within a range where an efficient heating operation of the air conditioner is performed and a measurement of the refrigeration cycle side pressure measuring device. It is the structure which controls the ventilation volume of the said air blower so that a value may become in the range where the efficient driving | operation of the said refrigerating-cycle apparatus is performed.

The combined air conditioning equipment configured as described above has at least one refrigeration cycle apparatus such as a refrigeration apparatus or a refrigeration apparatus in addition to the air conditioning apparatus. Each of these air conditioners and refrigeration cycle apparatuses has a refrigerant circuit including an outdoor heat exchanger and other components, and each refrigerant circuit has an independent configuration.
The outdoor heat exchanger of each refrigerant circuit is installed in one outdoor unit, and by operating the air blower, it is brought into contact with the outside air taken into the outdoor unit by the air blower, Heat exchange is performed between the refrigerant flowing through the outside air and the outside air taken into the outdoor unit by the blower. The amount of heat exchange by the outdoor heat exchanger of each refrigerant circuit increases in proportion to the amount of air blown by the blower.

In this complex air conditioning facility, the operation of the blower is controlled by the control device.
The control device is configured to control the operation of the blower based on the measured values of the refrigeration cycle side pressure measurement device and the low pressure side pressure measurement device of the air conditioner.
Specifically, during the heating operation of the air conditioner, the control device determines that the measured value of the low pressure side pressure measurement device is within the range where the efficient heating operation of the air conditioner is performed and the measurement of the refrigeration cycle side pressure measurement device. The air flow rate of the air blower is controlled so that the value falls within a range where the refrigeration cycle device is efficiently operated.

Thereby, in this composite type air conditioning equipment, it is possible to perform efficient operation for both the air conditioning apparatus and the refrigeration cycle apparatus.
In addition, in this air conditioning equipment, it is not necessary to change the piping structure, make it complicated, or provide various valves in order to obtain the above-mentioned effects. The composite air conditioning facility of the present invention can be configured with a slight change to the facility.

Here, the range of the supply pressure of the refrigerant to the outdoor heat exchanger of the refrigeration cycle apparatus required for operating the refrigeration cycle apparatus efficiently depends on the configuration of the refrigeration cycle apparatus, by an experimental method or an analytical method. Can be sought.
Similarly, the pressure range of the refrigerant supplied to the outdoor heat exchanger of the air conditioner in a state where the air conditioner is performing efficient heating operation depends on the experimental method or analytical It can be determined by each method.

  In this combined air conditioner, the air conditioner has a high pressure side pressure measuring device that measures the pressure of the refrigerant supplied to the outdoor heat exchanger of the air conditioner when forming a cooling cycle of the air conditioner. When the cooling cycle of the air conditioner is formed, the measured value of the high pressure side pressure measuring device is within the range where the air conditioning device is efficiently cooled and the measured value of the refrigeration cycle side pressure measuring device is You may be set as the structure which controls the ventilation volume of the said air blower so that it may become in the range where the efficient driving | operation of a refrigerating-cycle apparatus is performed.

  In this case, during the cooling operation of the air conditioner, the control device determines that the measured value of the high pressure side pressure measuring device is within the range where the efficient cooling operation of the air conditioner is performed and the measurement of the refrigeration cycle side pressure measuring device. The air flow rate of the air blower is controlled so that the value is within a range where the refrigeration cycle device is efficiently operated.

Thereby, in this composite type air conditioning equipment, it is possible to perform efficient operation for both the air conditioning apparatus and the refrigeration cycle apparatus.
Here, the pressure range of the refrigerant supplied to the outdoor heat exchanger of the air conditioner in a state where the air conditioner is performing an efficient cooling operation depends on an experimental method or an analytical method from the configuration of the air conditioner. It can be determined by each method.

  A combined air conditioning facility according to the present invention is a combined air conditioning facility including an air conditioner and a refrigeration cycle device in which refrigerant circuits including an outdoor heat exchanger and other components are independently provided. One outdoor unit in which the outdoor heat exchanger of each refrigerant circuit is housed, a blower device that takes outside air into the outdoor unit and contacts the outdoor heat exchanger, and the outdoor of the refrigeration cycle apparatus A refrigeration cycle side pressure measuring device that measures the pressure of the refrigerant supplied to the heat exchanger, and the pressure of the refrigerant supplied to the outdoor heat exchanger of the air conditioner when the cooling cycle of the air conditioner is formed A high pressure side pressure measuring device, and a control device for controlling the operation of the blower based on the measured values of the refrigeration cycle side pressure measuring device and the high pressure side pressure measuring device, When the cooling cycle of the air conditioner is formed, the control device is configured such that the measured value of the high pressure side pressure measuring device is within a range where an efficient cooling operation of the air conditioner is performed and the measurement of the refrigeration cycle side pressure measuring device is performed. It is the structure which controls the ventilation volume of the said air blower so that a value may become in the range where the efficient driving | operation of the said refrigerating-cycle apparatus is performed.

The combined air conditioning equipment configured as described above has at least one refrigeration cycle apparatus such as a refrigeration apparatus or a refrigeration apparatus in addition to the air conditioning apparatus. Each of these air conditioners and refrigeration cycle apparatuses has a refrigerant circuit including an outdoor heat exchanger and other components, and each refrigerant circuit has an independent configuration.
The outdoor heat exchanger of each refrigerant circuit is installed in one outdoor unit, and by operating the air blower, it is brought into contact with the outside air taken into the outdoor unit by the air blower, Heat exchange is performed between the refrigerant flowing through the outside air and the outside air taken into the outdoor unit by the blower. The amount of heat exchange by the outdoor heat exchanger of each refrigerant circuit increases in proportion to the amount of air blown by the blower.

In this complex air conditioning facility, the operation of the blower is controlled by the control device.
The control device is configured to control the operation of the blower based on the measured values of the refrigeration cycle side pressure measurement device and the high pressure side pressure measurement device of the air conditioner.

  Specifically, the control device, during the cooling operation of the air conditioner, the measurement value of the high pressure side pressure measurement device is within the range where the efficient cooling operation of the air conditioner is performed and the measurement of the refrigeration cycle side pressure measurement device. The air flow rate of the air blower is controlled so that the value is within a range where the refrigeration cycle device is efficiently operated.

Thereby, in this composite type air conditioning equipment, it is possible to perform efficient operation for both the air conditioning apparatus and the refrigeration cycle apparatus.
In addition, in this air conditioning equipment, it is not necessary to change the piping structure, make it complicated, or provide various valves in order to obtain the above-mentioned effects. The composite air conditioning facility of the present invention can be configured with a slight change to the facility.

Here, the range of the supply pressure of the refrigerant to the outdoor heat exchanger of the refrigeration cycle apparatus required for operating the refrigeration cycle apparatus efficiently depends on the configuration of the refrigeration cycle apparatus, by an experimental method or an analytical method. Can be sought.
Similarly, the pressure range of the refrigerant supplied to the outdoor heat exchanger of the air conditioner in a state where the air conditioner is performing efficient cooling operation is determined based on the configuration of the air conditioner by an experimental method or analytical method. It can be determined by each method.

  In this combined type air conditioning equipment, the control device stops the blower device during the defrost operation of the air conditioning device, and then the measured value of the refrigeration cycle side pressure measuring device is the upper limit side reference value of the refrigeration cycle device. When the value exceeds the value, the operation of the blower may be resumed.

Even in this combined air conditioner, during the defrost operation of the air conditioner, the air blower is stopped, the amount of heat exchange of the outdoor heat exchanger of the air conditioner is reduced, and the high temperature supplied to the outdoor heat exchanger is reduced. The frost attached to the outdoor heat exchanger is heated and melted by the refrigerant.
In this combined type air conditioner, after the air conditioner shifts to the defrost operation and the blower stops, if the measured value of the refrigeration cycle side pressure measuring device exceeds the upper limit side reference value, the control device The operation of the blower is resumed, and the amount of heat exchange by the outdoor heat exchanger of the refrigeration cycle apparatus is recovered.
As a result, the refrigerant supply pressure to the outdoor heat exchanger of the refrigeration cycle apparatus is always kept within the allowable range even when the air conditioner is shifted to the defrost operation, which reduces the efficiency of the refrigeration cycle apparatus. Can be prevented.
Here, the permissible range (upper limit side reference value) of the measurement value of the refrigeration cycle side pressure measuring device is a value that allows the refrigeration cycle device to always operate under optimum conditions, and this value is the refrigeration cycle device. Based on the configuration of the above, it is obtained by an experimental method or an analytical method.

  A combined air conditioning facility according to the present invention is a combined air conditioning facility including an air conditioner and a refrigeration cycle device in which refrigerant circuits including an outdoor heat exchanger and other components are independently provided. One outdoor unit in which the outdoor heat exchanger of each refrigerant circuit is housed, a blower device that takes outside air into the outdoor unit and makes contact with each outdoor heat exchanger, and controls the operation of the blower device And a refrigeration cycle side pressure measuring device for measuring the pressure of the refrigerant supplied to the outdoor heat exchanger of the refrigeration cycle apparatus, the control apparatus defrosting the air conditioner Sometimes, the blower is stopped, and then the operation of the blower is restarted when the measured value of the refrigeration cycle side pressure measuring device exceeds the upper reference value.

  Even in this combined air conditioner, during the defrost operation of the air conditioner, the air blower is stopped, the amount of heat exchange of the outdoor heat exchanger of the air conditioner is reduced, and the high temperature supplied to the outdoor heat exchanger is reduced. The frost attached to the outdoor heat exchanger is heated and melted by the refrigerant.

In this combined type air conditioner, after the air conditioner shifts to the defrost operation and the blower stops, if the measured value of the refrigeration cycle side pressure measuring device exceeds the upper limit side reference value, the control device The operation of the blower is resumed, and the amount of heat exchange by the outdoor heat exchanger of the refrigeration cycle apparatus is recovered.
As a result, the refrigerant supply pressure to the outdoor heat exchanger of the refrigeration cycle apparatus is always kept within the allowable range even when the air conditioner is shifted to the defrost operation, which reduces the efficiency of the refrigeration cycle apparatus. Can be prevented.
Here, the allowable range of the measurement value of the refrigeration cycle side pressure measuring device is a value that can always operate the refrigeration cycle device under optimum conditions, and this value is based on the configuration of the refrigeration cycle device, Required by experimental or analytical methods.

  A combined air conditioning facility according to the present invention is a combined air conditioning facility including an air conditioner and a refrigeration cycle device in which refrigerant circuits including an outdoor heat exchanger and other components are independently provided. The outdoor heat exchanger of each refrigerant circuit is housed in one outdoor unit, and an air blower that takes outside air into the outdoor unit and contacts the outdoor heat exchanger. The outdoor heat exchanger of the cycle device is divided into a plurality of heat exchanger units, and the refrigerant circuit of the refrigeration cycle device is allowed to allow refrigerant to flow to at least one of the heat exchange units. And a valve for performing regulation.

The composite air conditioning equipment configured as described above can increase the number of heat exchange units that circulate the refrigerant among the heat exchange units constituting the heat exchanger of the refrigeration cycle apparatus by opening the valve. By closing the valve, the effective heat exchange area of the outdoor heat exchanger can be reduced.
And reducing the effective heat exchange area of an outdoor heat exchanger by operating a valve and reducing the number of heat exchange units which distribute | circulate a refrigerant | coolant among the heat exchange units which comprise the heat exchanger of a refrigerating-cycle apparatus. Can do.
Further, by operating the valve, the effective heat exchange area of the outdoor heat exchanger is increased by increasing the number of heat exchange units through which the refrigerant flows among the heat exchange units constituting the heat exchanger of the refrigeration cycle apparatus. be able to.

By adjusting the effective heat exchange area of the outdoor heat exchanger in this way, the amount of heat exchange by the outdoor heat exchanger of the refrigeration cycle apparatus can be controlled independently of the amount of air blown by the air blower. The refrigerant pressure in the outdoor heat exchanger of the refrigeration cycle apparatus can be maintained regardless of the blast volume of the apparatus.
Thus, the performance of the refrigeration cycle apparatus can be maintained while the blower is operated in accordance with the operating conditions of the air conditioner and the performance of the air conditioner is sufficiently exhibited.

  In this combined type air conditioning facility, a refrigeration cycle side refrigerant pressure measuring device that measures a pressure of refrigerant supplied to the outdoor heat exchanger in the refrigerant circuit of the refrigeration cycle device, and a refrigeration cycle side pressure measuring device A control device that controls the operation of the valve based on the measured value, and the control device is configured to control the valve when the measured value of the refrigeration cycle side pressure measuring device falls below a lower reference value. May be configured to reduce the number of heat exchange units through which the refrigerant flows in the heat exchange unit.

In the combined air conditioning equipment configured as described above, the opening and closing of the valve is automatically controlled by the control device, so that the refrigeration cycle device can always be operated under optimum conditions.
Here, the lower limit side reference value, which is a determination criterion for control of the valve by the control device, is a value that allows the refrigeration cycle device to always operate under optimum conditions, and this value is the value of the refrigeration cycle device. Based on the configuration, it can be determined by experimental or analytical methods.

  An operating method of a combined air conditioning facility according to the present invention is the operating method of the combined air conditioning facility according to claim 2, wherein the first, based on the measurement value of the refrigeration cycle side refrigerant pressure measuring device, When the opening value of the second flow rate control valve is controlled, and the measured value of the refrigeration cycle side refrigerant pressure measurement device falls below the lower limit side reference value, the opening amount of the first flow rate control valve is reduced. The opening degree of the second flow rate control valve is increased.

In this method of operating a combined air-conditioning facility, the refrigeration cycle apparatus can always be operated under optimum conditions by appropriately controlling the opening degrees of the first and second flow rate control valves.
Here, the lower limit side reference value, which is a criterion for control of the first and second flow control valves, is a value that can always operate the refrigeration cycle apparatus under optimum conditions. Based on the configuration of the refrigeration cycle apparatus, it is obtained by an experimental method or an analytical method.

  An operation method of a combined air conditioning facility according to the present invention includes an air conditioner and a refrigeration cycle device in which refrigerant circuits including an outdoor heat exchanger and other components are provided independently, and each of the refrigerant circuits. A method of operating a combined air conditioner comprising: one outdoor unit in which the outdoor heat exchanger is housed; and a blower that takes outside air into the outdoor unit and contacts the outdoor heat exchanger. A refrigeration cycle side pressure measuring device that measures the pressure of the refrigerant supplied to the outdoor heat exchanger of the refrigeration cycle device, and the outdoor heat exchanger of the air conditioner when passing through the heating cycle of the air conditioner A low-pressure side pressure measuring device for measuring the pressure of the refrigerant, and when the heating cycle of the air-conditioning apparatus is formed, the measured value of the low-pressure-side pressure measuring device is an efficient heating of the air-conditioning device The amount of air blown by the air blower is controlled so that the measured value of the pressure measuring device on the refrigeration cycle side is within the range where efficient operation of the refrigeration cycle device is performed. To do.

In this method of operating a combined air conditioner, during the heating operation of the air conditioner, the measured value of the low pressure side pressure measuring device is within the range where the efficient heating operation of the air conditioner is performed and the refrigeration cycle side pressure measuring device Is controlled so that the measured value falls within a range where the refrigeration cycle apparatus is efficiently operated.
Thereby, in this operating method of the complex type air conditioning equipment, both the air conditioning apparatus and the refrigeration cycle apparatus can be efficiently operated.

Here, the range of the supply pressure of the refrigerant to the outdoor heat exchanger of the refrigeration cycle apparatus required for operating the refrigeration cycle apparatus efficiently depends on the configuration of the refrigeration cycle apparatus, by an experimental method or an analytical method. Can be sought.
Similarly, the pressure range of the refrigerant supplied to the outdoor heat exchanger of the air conditioner in a state where the air conditioner is performing efficient heating operation depends on the experimental method or analytical It can be determined by each method.

  An operation method of a combined air conditioning facility according to the present invention includes an air conditioner and a refrigeration cycle device in which refrigerant circuits including an outdoor heat exchanger and other components are provided independently, and each of the refrigerant circuits. A method of operating a combined air conditioner comprising: one outdoor unit in which the outdoor heat exchanger is housed; and a blower that takes outside air into the outdoor unit and contacts the outdoor heat exchanger. A refrigeration cycle side pressure measuring device that measures the pressure of the refrigerant supplied to the outdoor heat exchanger of the refrigeration cycle device, and a cooling cycle of the air conditioner that is supplied to the outdoor heat exchanger of the air conditioner A high-pressure side pressure measuring device for measuring the pressure of the refrigerant to be cooled, and when the cooling cycle of the air-conditioning apparatus is formed, the measured value of the high-pressure-side pressure measuring device is an effective cooling of the air-conditioning apparatus. The amount of air blown by the blower is controlled so that the measured value of the pressure measuring device on the refrigeration cycle side is within the range in which the operation is performed and the range in which the efficient operation of the refrigeration cycle device is performed. To do.

In this method of operating a combined air conditioner, during the cooling operation of the air conditioner, the measured value of the high pressure side pressure measuring device is within the range where the efficient cooling operation of the air conditioner is performed, and the refrigeration cycle side pressure measuring device Is controlled so that the measured value falls within a range where the refrigeration cycle apparatus is efficiently operated.
Thereby, in this composite type air conditioning equipment, it is possible to perform efficient operation for both the air conditioning apparatus and the refrigeration cycle apparatus.

Here, the range of the supply pressure of the refrigerant to the outdoor heat exchanger of the refrigeration cycle apparatus required for operating the refrigeration cycle apparatus efficiently depends on the configuration of the refrigeration cycle apparatus, by an experimental method or an analytical method. Can be sought.
Similarly, the pressure range of the refrigerant supplied to the outdoor heat exchanger of the air conditioner in a state where the air conditioner is performing efficient cooling operation is determined based on the configuration of the air conditioner by an experimental method or analytical method. It can be determined by each method.

  An operation method of a combined air conditioning facility according to the present invention includes an air conditioner and a refrigeration cycle device in which refrigerant circuits including an outdoor heat exchanger and other components are provided independently, and each of the refrigerant circuits. A method of operating a combined air conditioner comprising: one outdoor unit in which the outdoor heat exchanger is housed; and a blower that takes outside air into the outdoor unit and contacts the outdoor heat exchanger. A refrigeration cycle side pressure measuring device that measures the pressure of the refrigerant supplied to the outdoor heat exchanger of the refrigeration cycle device, and stops the blower during defrost operation of the air conditioner, and then the refrigeration When the measured value of the cycle side pressure measuring device exceeds the upper limit side reference value, the operation of the blower is restarted.

In the operation method of this combined type air conditioning equipment, after the air conditioner shifts to the defrost operation and the blower stops, when the measured value of the refrigeration cycle side pressure measuring device exceeds the upper limit side reference value, The operation of the blower is resumed, and the heat exchange by the outdoor heat exchanger of the refrigeration cycle apparatus is resumed.
As a result, the refrigerant supply pressure to the outdoor heat exchanger of the refrigeration cycle apparatus is always kept within the allowable range even when the air conditioner is shifted to the defrost operation, which reduces the efficiency of the refrigeration cycle apparatus. Can be prevented.
Here, the permissible range (upper limit side reference value) of the measurement value of the refrigeration cycle side pressure measuring device is a value that allows the refrigeration cycle device to always operate under optimum conditions, and this value is the refrigeration cycle device. Based on the configuration of the above, it is obtained by an experimental method or an analytical method.

  A method for operating a combined air conditioning facility according to the present invention is the method for operating a combined air conditioning facility according to claim 9, wherein the refrigerant circuit of the refrigeration cycle apparatus is supplied to the outdoor heat exchanger. A refrigeration cycle side refrigerant pressure measuring device for measuring the refrigerant pressure is provided, and when the measured value of the refrigeration cycle side pressure measuring device falls below the lower limit side reference value, the valve is operated to Of these, the number of heat exchange units through which the refrigerant flows is reduced.

In this method of operating a combined air conditioning facility, the refrigeration cycle apparatus can always be operated under optimal conditions by appropriately controlling the opening and closing of the valves.
Here, the lower limit side reference value, which is a criterion for valve control, is a value that allows the refrigeration cycle apparatus to always operate under optimum conditions, and this value is based on the configuration of the refrigeration cycle apparatus. Thus, it is obtained by an experimental method or an analytical method.

  According to the combined air conditioning facility configured as described above and the operation method thereof, the outdoor unit and the air blower are configured in common, and the respective performances of the air conditioner and the refrigeration cycle apparatus are sufficiently exhibited. Can do.

Embodiments according to the present invention will be described below with reference to the drawings.
[First embodiment]
Hereinafter, a first embodiment of the present invention will be described with reference to FIGS. 1 to 4.
The air conditioning / refrigeration / refrigeration facility (combined air conditioning facility) 1 according to the present embodiment is applied to a store such as a large store or a convenience store as shown in FIG. An air conditioner 2 for performing cooling, a refrigeration apparatus (refrigeration cycle apparatus) 3 for storing or displaying drinking water or food in a refrigerated state, and a refrigeration apparatus for storing or displaying ice, ice cream, frozen food, or the like in a frozen state (Refrigeration cycle apparatus) 4 is provided.
Each of the air conditioner 2, the refrigeration apparatus 3, and the refrigeration apparatus 4 is independently provided with a refrigerant circuit including an outdoor heat exchanger and other components.

The air conditioner 2 has an indoor air conditioning unit 11 provided in the store. A refrigerant circuit 12 shown in FIG. 2 is connected to the indoor air conditioning unit 11.
The refrigerant circuit 12 selectively forms one of a heating cycle and a cooling cycle.
The refrigerant circuit 12 includes an indoor heat exchanger 13 provided in the indoor air conditioning unit 11 on the refrigerant flow path through which the refrigerant is circulated to exchange heat between the refrigerant and the store atmosphere, and a compressor that pressurizes the refrigerant. 14, an air conditioning outdoor heat exchanger 15 that performs heat exchange between the refrigerant and the outdoor atmosphere, and an electronic expansion valve (throttle resistor) 16 that expands the refrigerant to reduce the pressure are provided in this order. It is said that.

In the refrigerant circuit 12, the compressor 14 is connected to the indoor heat exchanger 13 and the air conditioning outdoor heat exchanger 15 via a four-way valve 17.
The four-way valve 17 controls the refrigerant discharge direction from the compressor 14 in the refrigerant flow path and the refrigerant supply direction to the compressor 14 in the refrigerant flow path, controls the flow of the refrigerant in the refrigerant flow path, and performs heating. One of the cycle and the cooling cycle is selectively formed.
As the electronic expansion valve 16, a cooling expansion valve 16a and a heating expansion valve 16b are provided, and the air conditioner 2 is configured to use these electronic expansion valves 16 in accordance with the operation mode.
In the refrigerant circuit 12, an accumulator 18 that removes the liquid refrigerant from the refrigerant flowing through the refrigerant circuit 12 and passes only the gaseous refrigerant is provided on the upstream side of the compressor 14.

As shown in FIG. 1, the refrigeration apparatus 3 includes a refrigerated showcase 21 that is provided in a store and stores and displays refrigerated objects. A refrigerant circuit 22 shown in FIG. 2 is connected to the refrigerated showcase 21.
The refrigerant circuit 22 forms a refrigeration cycle for cooling the atmosphere in the refrigerated showcase 21.
The refrigerant circuit 22 includes an indoor heat exchanger 23 that is provided in the refrigerated showcase 21 and exchanges heat between the refrigerant and the atmosphere in the refrigerated showcase 21 on a refrigerant flow path through which the refrigerant is circulated, and a refrigerant A compressor 24 that pressurizes the refrigerant, an outdoor heat exchanger 25 that performs heat exchange between the refrigerant and the outdoor atmosphere, and an expansion valve (throttle resistor) 26 that expands and cools the refrigerant. It is set as the structure.

In addition, the refrigerant circuit 22 is upstream of the refrigeration outdoor heat exchanger 25, and the heat exchange passage 22 a in which the refrigeration outdoor heat exchanger 25 is provided, and the refrigerant circuit 22 downstream of the refrigeration outdoor heat exchanger 25. It is branched to the bypass flow path 22b connected to the.
And the heat exchange flow path 22a and the bypass flow path 22b are connected via the 1st high pressure control valve 27, and the supply pressure of the refrigerant | coolant to a downstream is maintained.

The first high-pressure control valve 27 has a configuration in which a first chamber 27a to which the heat exchange channel 22a is connected and a second chamber 27b to which the bypass channel 22b is connected are connected.
A heat exchange channel 22a is connected to the first chamber 27a with the open end 22c facing the second chamber 27b.
The partition wall 27c that separates the first chamber 27a and the second chamber 27b is provided with a communication hole 27d that connects the first chamber 27a and the second chamber 27b at a position facing the opening end 22c. Yes.

A rod 28 is inserted into a portion of the wall portion constituting the second chamber 27b, facing the communication hole 27d so as to be substantially parallel to a straight line connecting the opening end 22c and the communication hole 27d.
The rod 28 is provided to be movable in the longitudinal direction with one end 28a positioned outside the second chamber 27b and the other end 28b positioned inside the first chamber 27a through the communication hole 27d. Here, in the insertion portion of the rod 28 in the second chamber 27b, the rod 28 and the wall portion of the second chamber 27b are sealed in an airtight and liquid tight manner while allowing the rod 28 to move by a sealing material (not shown). It has been stopped.

A valve body 28 c is provided at the other end 28 b of the rod 28.
The valve body 28c can move between a position where the open end 22c is closed and a position where the communication hole 27d is closed by moving the rod 28 in the longitudinal direction.
The pressure of the refrigerant flowing through the heat exchange flow path 22a acts on the valve body 28c as a force that presses the valve body 28c toward the communication hole 27d.

The first high-pressure control valve 27 includes a first urging member 29a that urges the valve body 28 toward the opening end 22c, and a second urging member that urges the valve body 28 toward the communication hole 27d. 29b.
That is, the valve body 28c is held at a position where the pressure of the refrigerant flowing through the heat exchange flow path 22a and the urging forces of the first and second urging members 29a and 29b are balanced.
Here, since the urging forces of the first and second urging members 29a and 29b are fixed as will be described later, the position of the valve body 28c is determined by the pressure of the refrigerant in the heat exchange flow path 22a. It changes depending on the degree of decline.

The first urging member 29a has a housing H provided on the one end 28a side of the rod 28 of the second chamber 27b so as to cover the one end 28a, and a sealed space S on the one end 28a side of the rod 28 that partitions the inside of the housing H. And a diaphragm D that receives the one end 28a.
The sealed space S is filled with a gas such as nitrogen gas, and the diaphragm D is pressed toward the second chamber 27b by the internal pressure of the sealed space S.
That is, the first urging member 29a urges the rod 28 toward the opening end 22c by the pressure of the gas filled in the sealed space S, and is thereby provided at the other end 28b of the rod 28. The valve body 28c is configured to be biased toward the opening end 22c.

  The second urging member 29b is, for example, provided in the first chamber 27a and directly urges the valve body 28c toward the communication hole 27d, and one end 28a of the rod 28 in the housing H. The second chamber 27b is provided between the second chamber 27b and urges the rod 28 to be pulled out from the second chamber 27b (ie, the valve body 28c provided on the rod 28 is urged toward the communication hole 27d). A coil spring 29d.

  In the refrigerant circuit 22, a receiver 30 for temporarily storing the refrigerant sent from the first high pressure control valve 27 is provided on the downstream side of the first high pressure control valve 27.

As shown in FIG. 1, the refrigeration apparatus 4 includes a refrigeration showcase 31 that is provided in a store and stores and displays objects to be frozen. A refrigerant circuit 32 shown in FIG. 2 is connected to the refrigeration showcase 31.
The refrigerant circuit 32 forms a refrigeration cycle for cooling the atmosphere in the refrigeration showcase 31.
The refrigerant circuit 32 includes an indoor heat exchanger 33 that is provided in the refrigeration showcase 31 and exchanges heat between the refrigerant and the atmosphere in the refrigeration showcase 31 on the refrigerant flow path through which the refrigerant circulates, A compressor 34 that pressurizes the refrigerant, an outdoor heat exchanger 35 that performs heat exchange between the refrigerant and the outdoor atmosphere, and an expansion valve (throttle resistor) 36 that expands and cools the refrigerant. It is set as the structure.

The refrigerant circuit 32 is upstream of the refrigeration outdoor heat exchanger 35, the heat exchange flow path 32 a provided with the refrigeration outdoor heat exchanger 35, and the refrigerant circuit 32 downstream of the refrigeration outdoor heat exchanger 35. And a bypass channel 32b connected to the.
And the heat exchange flow path 32a and the bypass flow path 32b are connected via the 2nd high voltage | pressure control valve 37, and the supply pressure of the refrigerant | coolant to a downstream is maintained.

The second high-pressure control valve 37 has substantially the same configuration as the first high-pressure control valve 27 shown in FIG. In the first high pressure control valve 27, the second high pressure control valve 37 is configured such that the heat exchange flow path 32a is connected to the first chamber 27a and the bypass flow path 32b is connected to the second chamber 27b. The open end 32c of the heat exchange channel 32a is opposed to the communication hole 27d of the partition wall 27c with the second chamber 27b.
In the second high-pressure control valve 37, the valve body 28c is pressed toward the communication hole 27d by the pressure of the refrigerant flowing in the heat exchange flow path 32a and the urging force of the second urging member 29c. The urging force of the urging member 29a is pressed toward the opening end 32c, and these forces are held at a balance position. That is, the position of the valve body 28c changes according to the degree of decrease in the refrigerant pressure in the heat exchange flow path 32a.

  In the refrigerant circuit 32, a receiver 40 that temporarily stores the refrigerant sent from the second high pressure control valve 37 is provided on the downstream side of the second high pressure control valve 37.

As shown in FIGS. 1 and 2, the air conditioning / refrigeration / refrigeration facility 1 includes an air conditioning outdoor heat exchanger 15, a refrigeration outdoor heat exchanger 25, and a refrigeration unit for each of the refrigerant circuits 12, 22, and 32. One outdoor unit 42 in which the outdoor heat exchanger 35 is accommodated is provided.
As shown in FIG. 2, the outdoor unit 42 takes outside air into the outdoor unit 42 and makes it contact the air conditioning outdoor heat exchanger 15, the refrigeration outdoor heat exchanger 25, and the freezing outdoor heat exchanger 35. A blower device 43 is provided.
In the outdoor unit 42, the outdoor heat exchanger 25 for refrigeration and the outdoor heat exchanger 35 for freezing are arranged close to the upstream side of the airflow generated by the blower device 43 with respect to the outdoor heat exchanger 15 for air conditioning. Yes.

Hereinafter, the operation of the air conditioning / refrigeration / refrigeration equipment configured as described above will be described.
In the air conditioner 2, during the heating operation, the refrigerant outlet of the compressor 14 is connected to the indoor heat exchanger 13 side of the refrigerant flow path by the four-way valve 17, and the refrigerant inlet of the compressor 14 is used for air conditioning of the refrigerant flow path. It is connected to the outdoor heat exchanger 15 side.
Thereby, the gaseous refrigerant pressurized to high temperature and high pressure by the compressor 14 is sent into the indoor heat exchanger 13, and heat exchange is performed between the high temperature and high pressure refrigerant and the indoor atmosphere.
As the refrigerant passes through the indoor heat exchanger 13, the indoor atmosphere is deprived of heat and condensed and liquefied, whereby the indoor atmosphere is heated. That is, the indoor heat exchanger 13 functions as a condenser that condenses and liquefies the gaseous refrigerant.

The refrigerant condensed and liquefied by the indoor heat exchanger 13 in this manner is decompressed by the heating expansion valve 16b provided on the downstream side of the indoor heat exchanger 13, and becomes a low-temperature and low-pressure two-phase refrigerant. This two-phase refrigerant is sent to the air conditioning outdoor heat exchanger 15 provided downstream of the heating expansion valve 16b, and heat exchange is performed with the outside air taken into the outdoor unit 42.
By passing through the outdoor heat exchanger 15 for air conditioning, the refrigerant takes heat from the outside air taken into the outdoor unit 42 and evaporates to become a low-temperature and low-pressure gaseous refrigerant. That is, the air conditioning outdoor heat exchanger 15 functions as an evaporator that heats and evaporates the liquid refrigerant.

Here, even if the air conditioning apparatus 2 has a constant circulation flow rate of the refrigerant in the refrigerant circuit 12 (during steady operation), the amount of air blown by the blower 43 (the amount of outside air taken into the outdoor unit 42). As the amount increases, the evaporation of the refrigerant by the outdoor heat exchanger 15 for air conditioning is promoted, and the heating capacity of the air conditioner 2 increases. On the contrary, the air conditioner 2 evaporates the refrigerant by the air-conditioning outdoor heat exchanger 15 as the amount of air blown by the blower 43 decreases even when the refrigerant circulation flow rate in the refrigerant circuit 12 is constant. It becomes difficult to break, and the heating capacity of the air conditioner 2 is reduced.
The gaseous refrigerant generated in this way is sent to the refrigerant inlet of the compressor 14 through the four-way valve 17, is again pressurized by the compressor 14, is sent to the indoor heat exchanger 13, and the above process is repeated.

On the other hand, during the cooling operation, the air conditioner 2 has the refrigerant outlet of the compressor 14 connected to the air conditioning outdoor heat exchanger 15 side of the refrigerant flow path by the four-way valve 17 and the refrigerant inlet of the compressor 14 is connected to the refrigerant flow path. To the indoor heat exchanger 13 side.
As a result, the gaseous refrigerant that has been pressurized by the compressor 14 to become high temperature and pressure is sent to the outdoor heat exchanger 15 for air conditioning, and heat exchange is performed with the outside air taken into the outdoor unit 42. .
By passing through the outdoor heat exchanger 15 for air conditioning, the refrigerant is condensed and liquefied by taking heat away from the outside air taken into the outdoor unit 42. That is, the air conditioning outdoor heat exchanger 15 functions as a condenser.
Here, even if the air conditioning apparatus 2 is a case where the circulation flow rate of the refrigerant in the refrigerant circuit 12 is constant, the refrigerant is condensed and liquefied by the air-conditioning outdoor heat exchanger 15 as the air blowing amount of the air blowing device 43 increases. Is promoted, and the cooling capacity of the air conditioner 2 is increased. On the contrary, in the air conditioner 2, even when the refrigerant circulation flow rate in the refrigerant circuit 12 is constant, the refrigerant is condensed and liquefied by the air conditioning outdoor heat exchanger 15 as the amount of air blown by the air blower 43 decreases. Is less likely to be performed, and the cooling capacity of the air conditioner 2 is reduced.

The liquid refrigerant generated in this manner is decompressed by the cooling expansion valve 16a provided on the downstream side of the air conditioning outdoor heat exchanger 15 to become a low-temperature and low-pressure two-phase refrigerant, and then the indoor heat exchanger 13. To exchange heat with the room atmosphere.
When the refrigerant passes through the indoor heat exchanger 13, it takes heat from the indoor atmosphere and evaporates, thereby cooling the indoor atmosphere. That is, the indoor heat exchanger 13 functions as an evaporator.
The gaseous refrigerant that has passed through the indoor heat exchanger 13 is sent to the refrigerant inlet of the compressor 14 through the four-way valve 17, is again pressurized by the compressor 14, and sent to the outdoor heat exchanger 15 for air conditioning, The above process is repeated.

  In the refrigeration apparatus 3, the gaseous refrigerant pressurized to high temperature and high pressure by the compressor 24 is sent to the outdoor heat exchanger 25 for refrigeration and exchanges heat with the outside air taken into the outdoor unit 42. Done. That is, the refrigeration outdoor heat exchanger 25 functions as a condenser.

The liquid refrigerant condensed and liquefied by the refrigeration outdoor heat exchanger 25 in this manner is depressurized by the expansion valve 26 provided on the downstream side of the refrigeration outdoor heat exchanger 25, and a low-temperature low-pressure two-phase refrigerant and Become.
This low-temperature and low-pressure two-phase refrigerant is sent to the indoor heat exchanger 23 to exchange heat with the atmosphere in the refrigerated showcase 21.
By passing through the indoor heat exchanger 23, the refrigerant takes heat from the atmosphere in the refrigerated showcase 21 and evaporates, whereby the atmosphere in the refrigerated showcase 21 is cooled. That is, the indoor heat exchanger 23 functions as an evaporator.
The gaseous refrigerant that has passed through the indoor heat exchanger 23 is sent to the refrigerant inlet of the compressor 24, is again pressurized by the compressor 24, is sent to the refrigeration outdoor heat exchanger 25, and the above process is repeated.

Here, even if the refrigerating apparatus 3 is a case where the circulation flow rate of the refrigerant in the refrigerant circuit 22 is constant, the refrigerant is condensed and liquefied by the refrigerating outdoor heat exchanger 25 as the amount of air blown by the blower 43 increases. Promoted and increased cooling capacity.
And if the ventilation volume of the air blower 43 increases too much, condensation of the refrigerant | coolant in the refrigeration outdoor heat exchanger 25 will advance too much, and the pressure of the refrigerant | coolant which distribute | circulates the inside of the heat exchange flow path 22a will fall.
In this air conditioning / refrigeration / refrigeration facility 1, when the pressure of the refrigerant flowing through the heat exchange flow path 22a decreases, the first high pressure control valve 27 reduces the flow of refrigerant from the heat exchange flow path 22a to the downstream side. While the circulation of the refrigerant is stopped, the circulation amount of the refrigerant from the bypass flow path 22b to the downstream side is increased.

Hereinafter, the control of the refrigerant flow rate from the heat exchange flow path 22a to the downstream side and the refrigerant flow rate from the bypass flow path 22b to the downstream side by the first high-pressure control valve 27 will be specifically described.
As described above, the position of the valve body 28 of the first high-pressure control valve 27 changes depending on the pressure of the refrigerant flowing in the heat exchange flow path 22a. And when the pressure of the refrigerant | coolant which distribute | circulates the inside of the heat exchange flow path 22a falls, the valve body 28 will be adjoined or closely_contact | adhered to the opening end 22c of the heat exchange flow path 22a, and the circulation of the refrigerant | coolant through the opening end 22c will be carried out. The amount is reduced or the flow of refrigerant is stopped.

In the present embodiment, when the pressure of the refrigerant flowing through the heat exchange flow path 22a is within a preferable range for operation of the refrigeration apparatus 3 (within a high operating efficiency), as shown in FIG. The valve body 28 of the high pressure control valve 27 is held at a position where the communication hole 27d is closed. This maximizes the amount of refrigerant flowing from the heat exchange flow path 22a to the downstream side, and restricts the flow of refrigerant from the bypass flow path 22b to the downstream side.
In this state, only the refrigerant that has undergone heat exchange by the refrigeration outdoor heat exchanger 25 is supplied to the downstream side of the refrigeration outdoor heat exchanger 25, and heat exchange by the refrigeration outdoor heat exchanger 25 is performed. The amount is maximized.

And when the pressure of the refrigerant | coolant which distribute | circulates the inside of the heat exchange flow path 22a falls below the range with preferable operation | movement of the refrigerator 3, the valve body 28 moves to the direction close | similar to the opening end 22c of the heat exchange flow path 22a. Be made. As a result, fluid resistance is generated in the refrigerant discharged from the opening end 22c, the amount of refrigerant flowing from the heat exchange flow path 22a to the downstream side is reduced, and the flow of refrigerant from the bypass flow path 22b to the downstream side is reduced. Permissible.
Furthermore, when the pressure of the refrigerant flowing through the heat exchange flow path 22a falls below the lower limit value of the allowable range of the refrigeration apparatus 3, the valve element 28 opens the heat exchange flow path 22a as shown in FIG. The end 22c is closed to restrict the refrigerant flow from the heat exchange flow path 22a to the downstream side, while the refrigerant flow amount from the bypass flow path 22b to the downstream side is maximized.
As described above, the refrigerant flow rate from the bypass flow path 22b to the downstream side is increased, so that the refrigerant supply pressure to the downstream side of the first high-pressure control valve 27 is maintained within an allowable range.

As described above, when the flow rate of the refrigerant from the heat exchange flow path 22a to the downstream side is reduced or the flow of the refrigerant is stopped, the refrigerant stays in the heat exchange flow path 22a. The effective heat exchange area of the exchanger 25 will decrease.
Thereby, since the condensation of the refrigerant in the outdoor heat exchanger 25 for refrigeration does not easily proceed, excessive condensation of the refrigerant is suppressed, and the pressure of the refrigerant flowing through the heat exchange flow path 22a is recovered.

  In the refrigeration apparatus 4, the gaseous refrigerant that has been pressurized by the compressor 34 to a high temperature and high pressure is sent to the refrigeration outdoor heat exchanger 35, and heat exchange is performed between the high temperature and high pressure refrigerant and the outdoor atmosphere. . That is, the freezing outdoor heat exchanger 35 functions as a condenser.

The liquid refrigerant condensed and liquefied by the refrigeration outdoor heat exchanger 35 in this manner is decompressed by the expansion valve 36 provided on the downstream side of the refrigeration outdoor heat exchanger 35, and the low-temperature and low-pressure two-phase refrigerant and Become.
The low-temperature and low-pressure two-phase refrigerant is sent to the indoor heat exchanger 33 and heat exchange is performed with the atmosphere in the refrigeration showcase 31.
By passing through the indoor heat exchanger 33, the refrigerant takes heat from the atmosphere in the refrigerated showcase 31 and evaporates, whereby the atmosphere in the refrigerated showcase 31 is cooled. That is, the indoor heat exchanger 33 functions as an evaporator.
The gaseous refrigerant that has passed through the indoor heat exchanger 33 is sent to the refrigerant inlet of the compressor 34, is again pressurized by the compressor 34, and sent to the outdoor heat exchanger 35 for refrigeration, and the above process is repeated. It is.

Here, in the refrigeration apparatus 4, even when the circulation flow rate of the refrigerant in the refrigerant circuit 32 is constant, the refrigerant is condensed and liquefied by the refrigeration outdoor heat exchanger 35 as the amount of air blown by the air blower 43 increases. Promoted and increased cooling capacity.
And if the ventilation volume of the air blower 43 increases too much, condensation of the refrigerant | coolant in the freezing outdoor heat exchanger 35 will advance too much, and the pressure of the refrigerant | coolant which distribute | circulates the inside of the heat exchange flow path 32a will fall.
In the present embodiment, when the pressure of the refrigerant flowing through the heat exchange channel 32a decreases, the second high-pressure control valve 37 reduces the amount of refrigerant flowing from the heat exchange channel 32a to the downstream side, or the refrigerant flows. While stopped, the amount of refrigerant flowing from the bypass flow path 32b to the downstream side is increased.

The second high-pressure control valve 37 operates in the same manner as the first control valve 27 in the refrigeration apparatus 3.
Specifically, when the pressure of the refrigerant flowing through the heat exchange flow path 32a is within a preferable range for operation of the refrigeration apparatus 4 (within a high operating efficiency), the valve of the second high pressure control valve 37 is used. The body 28 is held at a position that closes the communication hole 27d so that the amount of refrigerant flowing from the heat exchange flow path 32a to the downstream side is maximized, and the flow of refrigerant from the bypass flow path 32b to the downstream side is restricted. It has come to be.
In this state, only the refrigerant heat-exchanged by the freezing outdoor heat exchanger 35 is supplied to the downstream side of the freezing outdoor heat exchanger 35, and heat exchange by the freezing outdoor heat exchanger 35 is performed. The amount is maximized.

And when the pressure of the refrigerant | coolant which distribute | circulates the inside of the heat exchange flow path 32a falls below the range with preferable operation | movement of the refrigeration apparatus 3, the valve body 28 moves to the direction close | similar to the opening end 32c of the heat exchange flow path 32a. Be made. As a result, fluid resistance is generated in the refrigerant discharged from the open end 32c, the amount of refrigerant flowing from the heat exchange flow path 32a to the downstream side is reduced, and the flow of refrigerant from the bypass flow path 32b to the downstream side is reduced. Permissible.
Further, when the pressure of the refrigerant flowing through the heat exchange flow path 32a falls below the lower limit value of the allowable range of the refrigeration apparatus 4, the opening end 32c of the heat exchange flow path 32a is closed by the valve body 28 and heat is generated. While the flow of the refrigerant from the replacement flow path 32a to the downstream side is restricted, the flow amount of the refrigerant from the bypass flow path 32b to the downstream side is maximized.
As described above, the refrigerant flow rate from the bypass flow path 32b to the downstream side is increased, so that the refrigerant supply pressure to the downstream side of the second high-pressure control valve 37 is maintained within an allowable range.

As described above, when the circulation amount of the refrigerant from the heat exchange flow path 32a to the downstream side is reduced or the circulation of the refrigerant is stopped, the refrigerant stays in the heat exchange flow path 32a. The effective heat exchange area of the exchanger 35 will decrease.
Thereby, since the condensation of the refrigerant in the outdoor heat exchanger for freezing 35 is difficult to proceed, excessive condensation of the refrigerant is suppressed, and the pressure of the refrigerant flowing through the heat exchange flow path 32a is recovered.

Thus, in this air-conditioning / refrigeration / refrigeration facility 1, the refrigerant supply pressure (refrigerant circuit 22, 32, the refrigerant supply pressure to the downstream side of the refrigeration / freezing outdoor heat exchangers 25 and 35) is maintained, so that the performance of the refrigeration apparatus 3 and the refrigeration apparatus 4 is independent of the amount of air blown by the blower 43. Maintained.
Thereby, in this air-conditioning / refrigeration / refrigeration facility 1, the refrigeration apparatus 3 and the refrigeration apparatus are operated while the air blower 43 is operated in accordance with the operating conditions of the air conditioner 2 and the performance of the air conditioner 2 is sufficiently exhibited. 4 performance can be maintained.

Here, since the refrigerant circuits 12, 22, and 32 of the air conditioning apparatus 2, the refrigeration apparatus 3, and the refrigeration apparatus 4 are independent of each other, even if trouble occurs in any of the refrigerant circuits, the other refrigerant circuits are adversely affected. It is hard to give.
Further, in this air conditioning / refrigeration / refrigeration facility 1, it is only necessary to provide a bypass passage and a high-pressure control valve in the refrigerant circuits 22, 32 of the refrigeration apparatus 3 and the refrigeration apparatus 4, respectively. And the air conditioning / refrigeration / refrigeration equipment according to the present invention can be constructed by using the refrigeration apparatus almost as it is.

[Second Embodiment]
Next, a second embodiment of the present invention will be described with reference to FIG.
The air-conditioning / refrigeration / refrigeration facility 51 according to the present embodiment is partly changed in the configuration of the refrigerant circuit 22 of the refrigeration device 3 and the refrigerant circuit 32 of the refrigeration device 4 in the air-conditioning / refrigeration / refrigeration facility 1 shown in the first embodiment. This is the main feature.
Hereinafter, the same or similar members as those of the air conditioning / refrigeration / refrigeration facility 1 shown in the first embodiment are denoted by the same reference numerals, and detailed description thereof is omitted.

In the air conditioning / refrigeration / refrigeration facility 51, the refrigerant circuit 22 of the refrigeration apparatus 3 is provided with a refrigeration-side refrigerant pressure measurement device 52 that measures the pressure of the refrigerant supplied to the refrigeration outdoor heat exchanger 25. In the present embodiment, the refrigeration side refrigerant pressure measuring device 52 is provided between the compressor 24 and the refrigeration outdoor heat exchanger 25 in the refrigerant circuit 22.
The heat exchange flow path 22a of the refrigerant circuit 22 is provided with a first flow rate control valve 53 for adjusting the flow rate of the refrigerant flowing through the heat exchange flow path 22a on the downstream side of the refrigeration outdoor heat exchanger 25. .
The bypass flow path 22b of the refrigerant circuit 22 is provided with a second flow rate control valve 54 that adjusts the flow rate of the refrigerant flowing through the bypass flow path 22b.

In the air conditioning / refrigeration / refrigeration facility 51, the refrigerant circuit 32 of the refrigeration apparatus 4 is provided with a refrigeration-side refrigerant pressure measurement device 56 that measures the pressure of refrigerant supplied to the refrigeration outdoor heat exchanger 35. In the present embodiment, the refrigeration side refrigerant pressure measuring device 56 is provided between the compressor 34 and the refrigeration outdoor heat exchanger 35 in the refrigerant circuit 32.
The heat exchange flow path 32a of the refrigerant circuit 32 is provided with a first flow rate control valve 57 that adjusts the flow rate of the refrigerant flowing through the heat exchange flow path 32a on the downstream side of the outdoor heat exchanger 35 for refrigeration. .
The bypass flow path 32b of the refrigerant circuit 32 is provided with a second flow rate control valve 58 that adjusts the flow rate of the refrigerant flowing through the bypass flow path 32b.

  The air conditioning / refrigeration / refrigeration facility 51 controls the opening degree of the first and second flow rate control valves 53 and 54 of the refrigeration apparatus 3 based on the measurement value of the refrigeration side refrigerant pressure measurement apparatus 52, A control device 59 that controls the opening degree of each of the first and second flow rate control valves 57 and 58 of the refrigeration device 4 based on the measurement value of the refrigeration side refrigerant pressure measurement device 56 is provided.

  In the air conditioning / refrigeration / refrigeration facility 51 configured as described above, the opening degree of the first and second flow rate control valves 53 and 54 of the refrigeration apparatus 3 is controlled by the control device 59, whereby the first high pressure control valve is controlled. The same function as 27 is realized. Further, the opening degree of the first and second flow rate control valves 57 and 58 of the refrigeration apparatus 4 is controlled by the control device 59, thereby realizing the same function as the second high pressure control valve 37.

Hereinafter, the control of the opening degree of the first flow control valves 53 and 57 and the second flow control valves 54 and 58 by the control device 59 will be specifically described.
First, control of the first flow rate control valve 53 and the second flow rate control valve 54 of the refrigeration apparatus 3 by the control device 59 will be described.
Here, in the refrigeration apparatus 3, when the refrigerant pressure in the heat exchange flow path 22a is reduced due to excessive heat exchange in the refrigeration outdoor heat exchanger 25, the refrigeration outdoor heat exchanger 25 is used. The refrigerant pressure (refrigerant pressure upstream of the refrigeration outdoor heat exchanger 25 in the refrigerant circuit 22) also decreases.
That is, in the air conditioning / refrigeration / refrigeration facility 51, the measured value of the refrigeration side refrigerant pressure measuring device 52 (the pressure of the refrigerant supplied to the refrigeration outdoor heat exchanger 25) is the refrigerant pressure in the heat exchange flow path 22a. Proportionally almost identical.

  When the measured value of the refrigeration side refrigerant pressure measurement device 52 is within a preferable range for operation of the refrigeration device 3 (that is, when the refrigerant pressure in the heat exchange flow path 22a is within a preferable range), the control device 59 The second flow control valve 54 is operated to stop the refrigerant flow from the bypass flow path 22b to the downstream side, while the first flow control valve 53 is operated to flow the refrigerant from the heat exchange flow path 22a to the downstream side. Increase the distribution volume. Thereby, only the refrigerant heat-exchanged by the freezing outdoor heat exchanger 25 is supplied to the downstream side of the refrigerating outdoor heat exchanger 25 in the refrigerant circuit 22.

On the other hand, when the measured value of the refrigeration side refrigerant pressure measuring device 52 falls below a preferred range (that is, when the refrigerant pressure in the heat exchange flow path 22a falls below the preferred range), the control device 59 controls the first flow rate control. The valve 53 is operated to reduce the amount of refrigerant flowing from the heat exchange flow path 22a to the downstream side, or stop the refrigerant flow.
Thereby, since the refrigerant stays in the heat exchange flow path 22a, the effective heat exchange area of the refrigeration outdoor heat exchanger 25 is reduced, and the condensation of the refrigerant in the refrigeration outdoor heat exchanger 25 is difficult to proceed. The excessive condensation of the refrigerant is suppressed, and the pressure rises to compensate for the decrease in heat exchange capacity.
Further, in parallel with the operation of the first flow control valve 53, the control device 59 operates the second flow control valve 54 to increase the amount of refrigerant flowing from the bypass flow path 22b to the downstream side.
Thereby, the supply pressure of the refrigerant to the downstream side of the refrigeration outdoor heat exchanger 25 is maintained.

Next, control of the first flow rate control valve 57 and the second flow rate control valve 58 of the refrigeration apparatus 4 by the control device 59 will be described.
Here, in the refrigeration apparatus 4, when the refrigerant pressure in the heat exchange flow path 32a decreases due to excessive heat exchange in the refrigeration outdoor heat exchanger 35, the refrigeration outdoor heat exchanger 35 is used. The refrigerant pressure (refrigerant pressure on the upstream side of the refrigeration outdoor heat exchanger 35 in the refrigerant circuit 32) also decreases.
In other words, in this air conditioning / refrigeration / refrigeration facility 51, the measured value of the refrigeration side refrigerant pressure measuring device 56 (the pressure of the refrigerant supplied to the refrigeration outdoor heat exchanger 35) is the refrigerant pressure in the heat exchange channel 32a. Proportionally almost identical.

  When the measured value of the refrigeration-side refrigerant pressure measuring device 56 is within a preferable range for operation of the refrigeration device 4 (that is, when the refrigerant pressure in the heat exchange channel 32a is within a preferable range), the control device 59 The second flow control valve 58 is operated to stop the flow of refrigerant from the bypass flow path 32b to the downstream side, while the first flow control valve 57 is operated to flow the refrigerant from the heat exchange flow path 32a to the downstream side. Increase the distribution volume. Thereby, only the refrigerant heat-exchanged by the freezing outdoor heat exchanger 35 is supplied to the downstream side of the freezing outdoor heat exchanger 35 in the refrigerant circuit 32.

On the other hand, when the measured value of the refrigeration side refrigerant pressure measuring device 56 falls below a preferred range (that is, when the refrigerant pressure in the heat exchange flow path 32a falls below the preferred range), the control device 59 controls the first flow rate control. The valve 57 is operated to reduce the circulation amount of the refrigerant from the heat exchange flow path 32a to the downstream side or stop the circulation of the refrigerant.
Thereby, since the refrigerant stays in the heat exchange flow path 32a, the effective heat exchange area of the refrigeration outdoor heat exchanger 35 decreases, and the condensation of the refrigerant in the refrigeration outdoor heat exchanger 35 does not easily proceed. The excessive condensation of the refrigerant is suppressed, and the pressure rises to compensate for the decrease in heat exchange capacity.
Further, in parallel with the operation of the first flow rate control valve 57, the control device 59 operates the second flow rate control valve 58 to increase the amount of refrigerant flowing from the bypass flow path 32b to the downstream side.
Thereby, the supply pressure of the refrigerant to the downstream side of the freezing outdoor heat exchanger 35 is maintained.

As described above, in the air conditioning / refrigeration / refrigeration facility 1, the first and second flow rate control valves 53, 54, 57, and 58 are operated by the control device 59 as described above, so that the refrigeration device 3 and the refrigeration device are operated. In each of the four refrigerant circuits 22 and 32, the supply pressure of the refrigerant to the downstream side of the refrigeration and freezing outdoor heat exchangers 25 and 35 is maintained. 3 and the performance of the refrigeration apparatus 4 are maintained.
Thereby, in this air-conditioning / refrigeration / refrigeration facility 51, the air blower is operated in accordance with the operating conditions of the air conditioner, and the performance of the air conditioner 2 is sufficiently exhibited, while the refrigerator 3 and the freezer 4 Performance can be maintained.
Moreover, since the above-mentioned operation / effect can be obtained without using an expensive high-pressure control valve, the equipment cost can be reduced.

  Here, a reference value serving as a determination reference for controlling the first and second flow control valves 53 and 54 by the control device 59, and a determination reference for controlling the first and second flow control valves 57 and 58, The reference value is obtained by an experimental method or an analytical method based on the configuration of the refrigeration apparatus 3 and the refrigeration apparatus 4.

[Third embodiment]
Next, a third embodiment of the present invention will be described with reference to FIGS.
The air-conditioning / refrigeration / refrigeration facility 61 according to this embodiment is the same as the air-conditioning / refrigeration / refrigeration facility 1 shown in the first embodiment. The main feature is that a part of the configuration of each of the refrigerant circuits 32 is changed. Hereinafter, the same or similar members as those of the air conditioning / refrigeration / refrigeration facility 1 shown in the first embodiment are denoted by the same reference numerals, and detailed description thereof is omitted.

In this air conditioning / refrigeration / refrigeration facility 61, the refrigerant that has passed through the air-conditioning outdoor heat exchanger 15 during the heating cycle of the air-conditioning device 2 (by the air-conditioning outdoor heat exchanger 15) is connected to the refrigerant circuit 12 of the air-conditioning device 2. A low pressure side pressure measuring device 62 that measures the pressure of the refrigerant that has finished heat exchange, and a high pressure side pressure measurement that measures the pressure of the refrigerant supplied to the air conditioner outdoor heat exchanger 15 when the air conditioning device 2 forms a cooling cycle. A device 63 is provided.
In the present embodiment, the low-pressure side pressure measuring device 62 is provided between the four-way valve 17 and the accumulator 18 inlet in the refrigerant circuit 12, and the high-pressure side pressure measuring device 63 includes the compressor 14 outlet, the four-way valve 17, and the like. It is provided between.

In the air conditioning / refrigeration / refrigeration facility 61, the refrigerant circuit 22 of the refrigeration apparatus 3 is not branched into the heat exchange flow path 22a and the bypass flow path 22b, and the first high-pressure control valve 27 is not provided.
Instead, the refrigerant circuit 22 is provided with a refrigeration-side refrigerant pressure measuring device 52 that measures the pressure of the refrigerant supplied to the refrigeration outdoor heat exchanger 25. In the present embodiment, the refrigeration side refrigerant pressure measuring device 52 is provided between the compressor 24 and the refrigeration outdoor heat exchanger 25 in the refrigerant circuit 22.

In the air conditioning / refrigeration / refrigeration facility 61, the refrigerant circuit 32 of the refrigeration apparatus 4 is not branched into the heat exchange flow path 32a and the bypass flow path 32b, and the second high-pressure control valve 37 is not provided.
Instead, the refrigerant circuit 32 is provided with a refrigeration-side refrigerant pressure measuring device 56 that measures the pressure of the refrigerant supplied to the refrigeration outdoor heat exchanger 35. In the present embodiment, the refrigeration side refrigerant pressure measuring device 56 is provided between the compressor 34 and the refrigeration outdoor heat exchanger 35 in the refrigerant circuit 32.

  In the present embodiment, a DC fan motor that can linearly control the rotational speed of the fan (that is, the air flow rate) is used as the air blowing device 43 so that the air flow rate can be easily controlled.

  Further, the air conditioning / refrigeration / refrigeration facility 61 is based on the measured values of the refrigeration side refrigerant pressure measurement device 52, the refrigeration side refrigerant pressure measurement device 56, the low pressure side pressure measurement device 62, and the high pressure side pressure measurement device 63. A control device 64 that controls the operation of the blower device 43 in accordance with the operation mode of the air conditioner 2 is provided.

The control device 64 has an arithmetic device (not shown) and a storage device such as a memory.
The storage device includes information on the pressure range _PAH in which the air conditioner 2 can perform an efficient heating operation among the pressures of the refrigerant that has passed through the air conditioning outdoor heat exchanger 15 of the air conditioner 2, and this And the information on the amount of air blown by the blower 43 (in this embodiment, the number of rotations of the DC fan motor) is stored.
The storage device of the pressure of the refrigerant passing through the air conditioner outdoor heat exchanger 15 of the air conditioner 2, the pressure range P _AC of information that can be air conditioner 2 performs efficient cooling operation And the information of the ventilation volume of the air blower 43 corresponding to this is stored.

In addition, the storage device, among the pressure of the refrigerant supplied to the refrigerating outdoor heat exchanger 25 of the refrigeration unit 3, and the information of the pressure range P _C of the refrigerating apparatus 3 can perform efficient operation, which And the information on the air flow rate of the air blower 43 corresponding to the above are stored.
The storage device of the pressure of the refrigerant supplied to the refrigerating outdoor heat exchanger 35 of the refrigeration apparatus 4, the information of the pressure range P _F refrigerating apparatus 4 can perform efficient operation, which And the information on the air flow rate of the air blower 43 corresponding to the above are stored.

  The arithmetic unit calculates the optimum air flow rate of the blower device 43 at the present time based on the information stored in the storage device, and the calculation result, the refrigeration side refrigerant pressure measurement device 52, and the refrigeration side refrigerant pressure measurement. Based on the measured values of the device 56, the low-pressure side pressure measurement device 62, and the high-pressure side pressure measurement device 63, the operation of the blower device 43 is controlled so that the blown air amount is always optimum.

During the operation of the air conditioning / refrigeration / refrigeration facility 61, the air conditioning apparatus 2, the refrigeration apparatus 3, and the refrigeration apparatus 4 are circulated in the refrigerant circuits 12, 22, and 32 so as to satisfy the required capacities. Is maintained.
While the air conditioning / refrigeration / refrigeration facility 61 is in operation, the air volume of the air blower 43 is controlled by the controller 64.
The control device 64 calculates the blowing amount of the blowing device 43 in which each of the air conditioning device 2, the refrigeration device 3, and the refrigeration device 4 is efficiently operated, and based on this calculation result, the blowing amount is always optimal. The operation of the blower 43 is controlled so as to be.

Hereinafter, the calculation method of the optimal ventilation volume of the air blower 43 by the control apparatus 64 is demonstrated.
First, the calculation method of the ventilation volume of the air blower 43 at the time of the heating operation of the air conditioning apparatus 2 is demonstrated.
Here, in Fig.7 (a), the rotation speed R of the DC fan motor which is the pressure of the refrigerant | coolant which passed the outdoor heat exchanger 15 for an air conditioning at the time of the heating cycle formation of the air conditioning apparatus 2 and the air blower 43 (of the air blower 43) is shown. The solid line shows the relationship with the air flow).
Similarly, in FIG. 7A, the relationship between the pressure of the refrigerant supplied to the refrigeration outdoor heat exchanger 25 of the refrigeration apparatus 3 and the rotation speed R of the blower 43 is indicated by a one-dot chain line. A relationship between the pressure of the refrigerant supplied to the outdoor heat exchanger 35 and the rotational speed R of the blower 43 is indicated by a two-dot chain line.

The control device 64 is configured such that the pressure of the refrigerant that has passed through the air-conditioning outdoor heat exchanger 15 of the air conditioner 2 falls within a suitable pressure range _PAH , and the refrigerant supplied to the refrigerating outdoor heat exchanger 25 of the refrigerating device 3 pressure becomes preferable range P _C, and calculates the engine speed range R _H blower 43 the pressure of the refrigerant supplied to the refrigerating outdoor heat exchanger 35 of the refrigeration apparatus 4 is a preferable range in the P _F .
And by controlling the operation of the air blower 43 so that the rotational speed of the blower 43 is located within the rotational speed range _RH , the performance of each of the air conditioner 2, the refrigeration device 3, and the refrigeration device 4 is sufficient. To show.

Next, the calculation method of the ventilation volume of the air blower 43 at the time of the air_conditionaing | cooling operation of the air conditioning apparatus 2 is demonstrated.
Here, in FIG.7 (b), the solid line shows the relationship between the pressure of the refrigerant | coolant supplied to the outdoor heat exchanger 15 for an air conditioning at the time of the air_conditioning | cooling cycle formation of the air conditioning apparatus 2, and the rotation speed R of the air blower 43. FIG.
Similarly, in FIG. 7B, the relationship between the pressure of the refrigerant supplied to the refrigeration outdoor heat exchanger 25 of the refrigeration apparatus 3 and the rotational speed R of the blower 43 is shown by a one-dot chain line. A relationship between the pressure of the refrigerant supplied to the outdoor heat exchanger 35 and the rotational speed R of the blower 43 is indicated by a two-dot chain line.

The control device 64 is configured so that the pressure of the refrigerant supplied to the air conditioning outdoor heat exchanger 15 of the air conditioner 2 is within a suitable pressure range _PAC , and the refrigerant supplied to the refrigeration outdoor heat exchanger 25 of the refrigeration device 3. pressure becomes preferable range P _C of, and calculates the engine speed range R _C blower 43 the pressure of the refrigerant supplied to the refrigerating outdoor heat exchanger 35 of the refrigeration apparatus 4 is a preferable range in the P _F To do.
And by controlling the operation of the blower device 43 so that the rotational speed of the blower device 43 is located within the rotational speed range _RC , the performance of each of the air conditioner 2, the refrigeration device 3, and the refrigeration device 4 is sufficient. Let it show.

Next, the control of the blower device 43 by the control device 64 during the defrost operation of the air conditioner 2 will be described.
The control device 64 stops the blowing by the blowing device 43 during the defrost operation.
As a result, the heat exchange amount of the air conditioning outdoor heat exchanger 15 of the air conditioner 2 is reduced, and frost attached to the air conditioning outdoor heat exchanger 15 by the high-temperature refrigerant supplied to the air conditioning outdoor heat exchanger 15 is reduced. It is heated and melted.
Here, in the outdoor unit 42, the refrigeration outdoor heat exchanger 25 and the refrigeration outdoor heat exchanger 35 are disposed close to the air conditioning outdoor heat exchanger 15.
Thereby, since the outdoor heat exchanger 15 for an air conditioning is overheated also with the heat | fever discharged | emitted from the outdoor heat exchanger 25 for refrigeration, and the outdoor heat exchanger 35 for freezing, defrosting is performed more efficiently.

In the state where the blower 43 is stopped in this manner, the heat exchange amount by the refrigeration outdoor heat exchanger 25 is reduced, and the refrigerant condensation amount is reduced. The refrigerant pressure on the upstream side of the exchanger 25 increases.
Similarly, in the state where the blower 43 is stopped, the heat exchange amount by the refrigeration outdoor heat exchanger 35 decreases and the refrigerant condensation amount decreases, so that the refrigeration outdoor heat in the refrigerant circuit 32 of the refrigeration device 4. The refrigerant pressure on the upstream side of the exchanger 35 increases.
For this reason, if the time which has stopped the air blower 43 is long, the efficiency of the refrigerator 3 and the freezing apparatus 4 will fall.

Controller 64, after stopping the blowing by the blower 43 proceeds to defrost operation, or measurements of refrigerating side refrigerant pressure measuring device 52 exceeds a suitable pressure range P _C above or freezing side refrigerant pressure If the measured value of the measuring device 56 exceeds a suitable pressure range P _F above, it resumes the operation of the blower 43.

  Thereby, since the heat exchange amount by the outdoor heat exchanger 25 for refrigeration and the heat exchange amount by the outdoor heat exchanger 35 for freezing are recovered | restored, even if the air conditioning apparatus 2 is transfering to defrost operation, the refrigeration apparatus 3 and A reduction in efficiency of the refrigeration apparatus 4 is prevented.

Thus, in this air conditioning / refrigeration / refrigeration facility 61, the air conditioner 2, and the refrigeration apparatus 3 and the refrigeration apparatus 4 that are refrigeration cycle apparatuses can be efficiently operated.
Further, in this air conditioning / refrigeration / refrigeration facility 61, there is no need to change the piping structure or make it complicated, or to provide various valves in order to obtain the above-described effects. Therefore, the air conditioning shown in the first and second embodiments is not necessary.・ The equipment cost is reduced compared to the refrigeration / refrigeration facilities 1 and 51, and the air conditioning / refrigeration / refrigeration facility of the present invention can be configured by making a slight change to the existing air-conditioning / refrigeration / refrigeration facility. .

The information on the pressure ranges P _AH , P _AC , P _C , and P _{F and} the information on the amount of air blown from the blower 43 corresponding thereto are the air conditioner 2, the refrigerator 3, and the refrigerating device 4. It can be obtained by an experimental method or an analytical method based on the configuration of

  Here, the information on the pressure of the refrigerant that has passed through the air-conditioning outdoor heat exchanger 15 at the time of forming the heating cycle of the air conditioner 2 may be obtained using a technique other than that obtained by directly measuring with the low-pressure side pressure measuring device 62. Good. Similarly, the information on the pressure of the refrigerant supplied to the outdoor heat exchanger 15 for air conditioning when the cooling cycle of the air conditioner 2 is formed is obtained using a method other than that obtained by directly measuring with the high-pressure side pressure measuring device 63. (This also applies to the second embodiment and the fourth embodiment described later).

  For example, the relationship between the pressure of the refrigerant that has passed through the air-conditioning outdoor heat exchanger 15 and the temperature of the refrigerant evaporated by the air-conditioning outdoor heat exchanger 15 during the heating cycle of the air-conditioning apparatus 2 is as follows. It can be derived from the configuration of the refrigerant circuit 12. Therefore, as indicated by a two-dot chain line in FIG. 6, a temperature sensor 66 is provided in the air conditioning outdoor heat exchanger 15, and the control device 64 passes through the air conditioning outdoor heat exchanger 15 from the measured value of the temperature sensor 66. By adopting a configuration for calculating the pressure of the refrigerant, the same control as the control based on the measurement value of the low-pressure side pressure measuring device 62 described above can be performed.

  Similarly, the relationship between the pressure of the refrigerant supplied to the outdoor heat exchanger 15 for air conditioning when the cooling cycle of the air conditioner 2 is formed and the temperature of the refrigerant condensed by the outdoor heat exchanger 15 for air conditioning is It can be derived from the configuration of the refrigerant circuit 12 of the device 2. For this reason, the control device 64 is configured to calculate the pressure of the refrigerant supplied to the outdoor heat exchanger 15 for air conditioning from the measurement value of the temperature sensor 66, so that the measurement value of the high pressure side pressure measurement device 63 described above is obtained. Control similar to the control based on can be performed.

Here, since the temperature sensor 66 is generally provided in air conditioning, refrigeration, and refrigeration equipment, the low-pressure-side pressure measuring device 62, the high-pressure-side pressure are used when the temperature sensor 66 is configured to perform control. It is not necessary to install the measuring device 63, and the manufacturing cost of the air conditioning / refrigeration / refrigeration facility 61 can be reduced.
Further, the air-conditioning / refrigeration / refrigeration facility 61 is configured so that both the control using the low-pressure side pressure measurement device 62 and the high-pressure side pressure measurement device 63 and the control using the temperature sensor 66 can be switched. Thus, the control system can be made redundant.
That is, when the low pressure side pressure measuring device 62 or the high pressure side pressure measuring device 63 fails, control using the temperature sensor 66 is performed, and when the temperature sensor 66 fails, the low pressure side pressure measuring device 62 and the high pressure side pressure are controlled. By adopting a configuration that performs control using the measuring device 63, it is possible to prevent a reduction in operating rate due to a failure.

[Fourth embodiment]
Next, a fourth embodiment of the present invention will be described with reference to FIGS.
The air-conditioning / refrigeration / refrigeration equipment 71 according to the present embodiment has a part of the configuration of the refrigerant circuit 22 of the refrigeration apparatus 3 and the refrigerant circuit 32 of the refrigeration apparatus 4 in the air-conditioning / refrigeration / refrigeration equipment 61 shown in the third embodiment. The main feature is that it has been changed. Hereinafter, the same or same members as those of the air conditioning / refrigeration / refrigeration facility 61 shown in the third embodiment are denoted by the same reference numerals, and detailed description thereof is omitted.

In this air conditioning / refrigeration / refrigeration facility 71, the refrigeration outdoor heat exchanger 25 of the refrigeration apparatus 3 is divided into a plurality of heat exchanger units, and these heat exchange units are respectively parallel to the refrigerant circuit 22. It is connected.
Further, the refrigerant circuit 22 is provided with a valve for allowing and restricting the flow of the refrigerant to each of the heat exchanger units.
In this embodiment, as shown in FIGS. 8 and 9, the refrigeration outdoor heat exchanger 25 is configured such that the heat exchange units 25a, 25b, and 25c are adjacently arranged in this order from the top to the bottom. . As shown in FIG. 9, in the refrigerant circuit 22, a first electromagnetic valve 72 is provided on the outlet side of the heat exchange unit 25a, and a second electromagnetic valve 73 is provided on the outlet side of the heat exchange unit 25b. It has been.

Similarly, in this air conditioning / refrigeration / refrigeration facility 71, the freezing outdoor heat exchanger 35 of the refrigeration apparatus 4 is divided into a plurality of heat exchanger units, and these heat exchanging units are respectively connected to the refrigerant circuit 32. Connected in parallel.
Further, the refrigerant circuit 32 is provided with a valve for allowing and restricting the flow of the refrigerant to each of the heat exchanger units.
In this embodiment, as shown in FIG.8 and FIG.9, the outdoor heat exchanger 35 for freezing is set as the structure which arrange | positioned the heat exchange units 35a, 35b, and 35c adjacently in this order toward the bottom from the top. . As shown in FIG. 9, in the refrigerant circuit 32, a third electromagnetic valve 76 is provided on the outlet side of the heat exchange unit 35a, and a fourth electromagnetic valve 77 is provided on the outlet side of the heat exchange unit 35b. It has been.

Further, the air conditioning / refrigeration / refrigeration facility 71 includes first to fourth solenoid valves 72, 73, 76, based on the measured values of the refrigeration side refrigerant pressure measurement device 52 and the refrigeration side refrigerant pressure measurement device 56. A control device 78 for controlling the operation of 77 is provided.
In the air conditioning / refrigeration / refrigeration facility 71, the low pressure side pressure measuring device 62 and the high pressure side pressure measuring device 63 may be omitted.

Controller 78, when the measurement value of the refrigeration side refrigerant pressure measuring device 52 is below the preferred pressure range P _C, the first, by operating the second solenoid valve 72 and 73, the heat exchange unit 25a The number of heat exchange units through which the refrigerant is circulated is reduced one by one.
The control device 78 is configured to restrict the flow of the refrigerant in order from the heat exchange unit located above when the number of heat exchange units through which the refrigerant flows is reduced.

Further, the control unit 78, when the measurement value of the refrigeration side refrigerant pressure measuring device 56 is below the preferred pressure range P _F, the third, by operating the fourth solenoid valve 76 and 77, the heat exchange unit The number of heat exchange units for circulating the refrigerant among 35a to 35c is decreased one by one.
The control device 78 is configured to restrict the flow of the refrigerant in order from the heat exchange unit located above when the number of heat exchange units through which the refrigerant flows is reduced.

The control device 78 has an arithmetic device (not shown) and a storage device such as a memory.
The storage device of the pressure of the refrigerant supplied to the refrigerating outdoor heat exchanger 25 of the refrigeration unit 3, information of the pressure range P _C of the refrigerating apparatus 3 can perform efficient operation is stored .
The storage device of the pressure of the refrigerant supplied to the refrigerating outdoor heat exchanger 35 of the refrigeration apparatus 4, the information of the pressure range P _F refrigerating apparatus 4 can perform efficient operation is stored ing.

  Based on the information stored in the storage device and the measured values of the refrigeration-side refrigerant pressure measurement device 52 and the refrigeration-side refrigerant pressure measurement device 56, the arithmetic device is configured to perform first to fourth electromagnetic valves 72, 73, Each of 76 and 77 is opened and closed.

During the operation of the air conditioning / refrigeration / refrigeration facility 71, the air circulation device 2, the refrigeration device 3, and the refrigeration device 4 are circulated in the refrigerant circuits 12, 22, 32 so as to satisfy the required capacities. Is maintained.
Moreover, the operation | movement of the air blower 43 is controlled so that the ventilation volume requested | required of the outdoor heat exchanger 15 for an air conditioning of the air conditioning apparatus 2 is ensured.

And when the ventilation volume of the air blower 43 becomes excessive for the refrigeration outdoor heat exchanger 25 of the refrigeration apparatus 3, the condensation of the refrigerant by the refrigeration outdoor heat exchanger 25 proceeds excessively, and the refrigeration The pressure of the refrigerant supplied to the outdoor heat exchanger 25 decreases (the measured value of the refrigeration side refrigerant pressure measuring device 52 decreases).
Control device 78, the measured value is lowered in the refrigeration side refrigerant pressure measuring device 52, when it falls below the pressure range P _C, first, by closing the first solenoid valve 72, cold outdoor heat exchanger 25 Among them, the heat exchange by the heat exchange unit 25a located at the top is stopped, and the effective heat exchange area of the refrigeration outdoor heat exchange device 25 is reduced.
Then, when the measured value of the refrigerating side refrigerant pressure measuring device 52 in this state is below the pressure range P _C closes the second solenoid valve 73, of the refrigerating outdoor heat exchanger 25, located at the top The heat exchange not only by the heat exchange unit 25a to be performed but also by the heat exchange unit 25b located at the intermediate portion is stopped, and the effective heat exchange area of the refrigeration outdoor heat exchange device 25 is further reduced.
In this state, heat exchange is performed only by the heat exchange unit 25c located at the bottom of the outdoor heat exchanger 25 for refrigeration.

  In this air conditioning / refrigeration / refrigeration facility 71, the effective heat exchange area of the refrigeration outdoor heat exchanger 25 is adjusted in this way, so that the refrigeration device 3 outside the refrigeration room 3 independently of the air flow rate of the blower 43. Since the amount of heat exchange by the heat exchanger 25 can be controlled, the refrigerant pressure in the refrigeration outdoor heat exchanger 25 of the refrigeration apparatus 3 can be maintained regardless of the amount of blast of the blower 43.

Similarly, when the amount of air blown by the blower 43 is excessive for the freezing outdoor heat exchanger 35 of the freezing device 4, the condensation of the refrigerant by the freezing outdoor heat exchanger 35 proceeds excessively, The pressure of the refrigerant supplied to the freezing outdoor heat exchanger 35 decreases (the measured value of the freezing-side refrigerant pressure measuring device 56 decreases).
Control device 78, the measured value is lowered in the refrigeration side refrigerant pressure measuring device 56, when it falls below the pressure range P _F, first, by closing the third solenoid valve 76, the freezing outdoor heat exchanger 35 Among these, the heat exchange by the heat exchange unit 35a located at the top is stopped, and the effective heat exchange area of the outdoor heat exchange device 35 for freezing is reduced.
Then, when the measured value of the refrigeration side refrigerant pressure measuring device 56 also is below the pressure range P _F this state, by closing the fourth solenoid valve 77, of the frozen outdoor heat exchanger 35, located at the top The heat exchange not only by the heat exchange unit 35a to be performed but also by the heat exchange unit 35b located at the intermediate part is stopped, and the effective heat exchange area of the outdoor heat exchange device 35 for refrigeration is further reduced.
In this state, heat exchange is performed only by the heat exchange unit 35c located at the bottom of the outdoor heat exchanger 35 for freezing.

  In this air conditioning / refrigeration / refrigeration facility 71, the effective heat exchange area of the refrigeration outdoor heat exchanger 35 is adjusted in this way, so that the air flow of the blast device 43 is independent of the blast volume of the refrigeration device 3. Since the amount of heat exchange by the heat exchanger 35 can be controlled, the refrigerant pressure in the refrigeration outdoor heat exchanger 35 of the refrigeration apparatus 4 can be maintained regardless of the amount of blast of the blower 43.

  Thereby, in this air-conditioning / refrigeration / refrigeration facility 71, the refrigeration apparatus 3 and the refrigeration apparatus are operated while the air blower 43 is operated in accordance with the operating conditions of the air conditioner 2 and the performance of the air conditioner 2 is sufficiently exhibited. 4 performance can be maintained.

Here, in the outdoor unit 42 of the air-conditioning / refrigeration / refrigeration equipment 71, the refrigeration outdoor heat exchanger 25 and the refrigeration outdoor heat exchanger 35 are blown to the air-conditioning outdoor heat exchanger 15. Is located close to the upstream side of the airflow generated.
Thereby, the outdoor air heated by heat exchange by each of the refrigeration outdoor heat exchanger 25 and the freezing outdoor heat exchanger 35 heats the air conditioning outdoor heat exchanger 15 of the air conditioner 2.
That is, the refrigeration outdoor heat exchanger 25 and the refrigeration outdoor heat exchanger 35 act as drain heaters, so that it is difficult for frost to be generated in the air conditioning outdoor heat exchanger 15 during the heating operation of the air conditioner 2, and defrosting is also performed. The frost can be removed more efficiently during operation.
Here, in the outdoor heat exchanger 15 for air conditioning, since the liquid refrigerant stays, frost tends to be generated particularly in the lower part. In this air conditioning / refrigeration / refrigeration facility 71, the heat exchange unit of the refrigeration outdoor heat exchanger 25 and the heat exchange unit of the refrigeration outdoor heat exchanger 35 are configured to be stopped in order from above. Moreover, the heat exchange unit located in the lowest part is not stopped.
For this reason, in this air conditioning / refrigeration / refrigeration equipment 71, the lower part where the frost is likely to be generated in the air conditioning outdoor heat exchanger 15 is always the exhaust of the refrigeration outdoor heat exchanger 25 and the freezing outdoor heat exchanger 35, respectively. Since it is heated by heat, frost is less likely to be generated in the outdoor heat exchanger 15 for air conditioning during the heating operation of the air conditioner 2 regardless of the operating conditions of the refrigeration apparatus 3 and the refrigeration apparatus 4, and more efficient during defrost operation. Frost can be removed.

It is a perspective view showing an example of application of air-conditioning, refrigeration, and freezing equipment concerning a first embodiment of the present invention. It is a figure which shows the structure of the refrigerant circuit of the air conditioning / refrigeration / refrigeration equipment concerning 1st embodiment of this invention. It is a longitudinal cross-sectional view which shows the structure of the high pressure control valve used for the air-conditioning / refrigeration / refrigeration equipment according to the first embodiment of the present invention. It is a longitudinal cross-sectional view which shows the structure of the high pressure control valve used for the air-conditioning / refrigeration / refrigeration equipment according to the first embodiment of the present invention. It is a figure which shows the structure of the refrigerant circuit of the air conditioning / refrigeration / refrigeration equipment concerning 2nd embodiment of this invention. It is a figure which shows the structure of the refrigerant circuit of the air conditioning / refrigeration / refrigeration equipment concerning 3rd embodiment of this invention. It is a graph which shows the reference | standard conditions of control of the air blower by the control apparatus of the air conditioning / refrigeration / refrigeration equipment concerning 3rd embodiment of this invention. It is a figure which shows the structure of the air conditioning / refrigeration / refrigeration equipment concerning 4th embodiment of this invention. It is a figure which shows the structure of the refrigerant circuit of the air conditioning / refrigeration / refrigeration equipment concerning 4th embodiment of this invention.

Explanation of symbols

1,51,61,71 Air conditioning, refrigeration and refrigeration equipment (combined air conditioning equipment)
2 Air conditioning equipment 3 Refrigeration equipment (refrigeration cycle equipment)
4 Refrigeration equipment (refrigeration cycle equipment)
15 Air Conditioning Outdoor Heat Exchangers 22a and 32a Heat Exchange Channels 22b and 32b Bypass Channel 25 Refrigeration Outdoor Heat Exchangers 25a to 25c Heat Exchanger Units 27 and 37 First and Second High Pressure Control Valves 35 Refrigeration Outdoor Heat Exchanger 35a-35c Heat exchanger unit 42 Outdoor unit 43 Blower 52, 56 Refrigerating side, refrigeration side refrigerant pressure measuring device 53, 57 First flow control valve 54, 58 Second flow control valve 59, 64, 78 Control device 62 Low Pressure Side Pressure Measuring Device 63 High Pressure Side Pressure Measuring Device 72, 73, 76, 77 First to Fourth Solenoid Valves

Claims (15)

A combined air conditioner comprising an air conditioner and a refrigeration cycle apparatus in which refrigerant circuits including an outdoor heat exchanger and other components are independently provided,
One outdoor unit in which the outdoor heat exchanger of each refrigerant circuit is stored;
An air blower that takes outside air into the outdoor unit and makes contact with the outdoor heat exchangers,
The refrigerant circuit of the refrigeration cycle apparatus is connected to the upstream side of the outdoor heat exchanger, the heat exchange flow path in which the outdoor heat exchanger is provided, and the downstream side of the outdoor heat exchanger of the refrigerant circuit. Branched to the bypass channel,
The heat exchange channel and the bypass channel are connected via a high-pressure control valve, and the supply pressure of the refrigerant to the downstream side of the high-pressure control valve is maintained. Combined air conditioning equipment. A combined air conditioner comprising an air conditioner and a refrigeration cycle apparatus in which refrigerant circuits including an outdoor heat exchanger and other components are independently provided,
One outdoor unit in which the outdoor heat exchanger of each refrigerant circuit is stored;
An air blower that takes outside air into the outdoor unit and makes contact with the outdoor heat exchangers,
The refrigerant circuit of the refrigeration cycle apparatus is provided with a refrigeration cycle side refrigerant pressure measuring device that measures the pressure of the refrigerant supplied to the outdoor heat exchanger,
The refrigerant circuit of the refrigeration cycle apparatus is connected to the upstream side of the outdoor heat exchanger, the heat exchange flow path in which the outdoor heat exchanger is provided, and the downstream side of the outdoor heat exchanger of the refrigerant circuit. Branched to the bypass channel,
The heat exchange flow path is provided with a first flow rate control valve that adjusts the flow rate of the refrigerant flowing through the heat exchange flow path on the downstream side of the outdoor heat exchanger,
A combined air conditioning facility, wherein the bypass flow path is provided with a second flow rate control valve for adjusting a flow rate of the refrigerant flowing through the bypass flow path. A control device is provided for controlling the opening degree of each of the first and second flow rate control valves based on the measurement value of the refrigeration cycle side refrigerant pressure measurement device,
When the measured value of the refrigeration cycle side refrigerant pressure measuring device falls below the lower limit side reference value, the control device reduces the opening of the first flow control valve while opening the second flow control valve. The combined air-conditioning equipment according to claim 2, wherein: A combined air conditioner comprising an air conditioner and a refrigeration cycle apparatus in which refrigerant circuits including an outdoor heat exchanger and other components are independently provided,
One outdoor unit in which the outdoor heat exchanger of each refrigerant circuit is stored;
A blower for taking outside air into the outdoor unit and bringing it into contact with the outdoor heat exchangers;
A refrigeration cycle side pressure measuring device for measuring the pressure of refrigerant supplied to the outdoor heat exchanger of the refrigeration cycle device;
A low-pressure side pressure measuring device that measures the pressure of the refrigerant that has passed through the outdoor heat exchanger of the air-conditioning device when the heating cycle of the air-conditioning device is formed;
A control device that controls the operation of the blower based on the measured values of the refrigeration cycle side pressure measurement device and the low pressure side pressure measurement device,
When the heating cycle of the air conditioner is formed, the control device has a measurement value of the low pressure side pressure measuring device within a range where an efficient heating operation of the air conditioner is performed, and the refrigeration cycle side pressure measuring device A combined air-conditioning facility characterized in that the amount of air blown by the blower is controlled so that the measured value is within a range where the refrigeration cycle device is efficiently operated. A high-pressure side pressure measurement device that measures the pressure of the refrigerant supplied to the outdoor heat exchanger of the air-conditioning device when forming a cooling cycle of the air-conditioning device;
The control device, when forming a cooling cycle of the air conditioner, the measured value of the high pressure side pressure measuring device is within a range where an efficient cooling operation of the air conditioner is performed and the refrigeration cycle side pressure measuring device The combined air-conditioning equipment according to claim 4, wherein the air flow rate of the air blower is controlled so that the measured value is within a range where the refrigeration cycle device is efficiently operated. . A combined air conditioner comprising an air conditioner and a refrigeration cycle apparatus in which refrigerant circuits including an outdoor heat exchanger and other components are independently provided,
One outdoor unit in which the outdoor heat exchanger of each refrigerant circuit is stored;
A blower for taking outside air into the outdoor unit and bringing it into contact with the outdoor heat exchangers;
A refrigeration cycle side pressure measuring device for measuring the pressure of refrigerant supplied to the outdoor heat exchanger of the refrigeration cycle device;
A high-pressure side pressure measurement device that measures the pressure of the refrigerant supplied to the outdoor heat exchanger of the air-conditioning device when a cooling cycle of the air-conditioning device is formed;
A control device for controlling the operation of the blower device based on the measured values of the refrigeration cycle side pressure measurement device and the high pressure side pressure measurement device,
The control device, when forming a cooling cycle of the air conditioner, the measured value of the high pressure side pressure measuring device is within a range where an efficient cooling operation of the air conditioner is performed, and of the refrigeration cycle side pressure measuring device. A combined air-conditioning facility characterized in that the amount of air blown by the blower is controlled so that the measured value is within a range where the refrigeration cycle device is efficiently operated. The control device stops the air blower during defrost operation of the air conditioner,
After that, when the measured value of the refrigeration cycle side pressure measuring device exceeds the upper limit side reference value of the refrigeration cycle device, the operation of the blower device is restarted. The combined air conditioning equipment described in 1. A combined air conditioner comprising an air conditioner and a refrigeration cycle apparatus in which refrigerant circuits including an outdoor heat exchanger and other components are independently provided,
One outdoor unit in which the outdoor heat exchanger of each refrigerant circuit is stored;
A blower for taking outside air into the outdoor unit and bringing it into contact with the outdoor heat exchangers;
A control device for controlling the operation of the blower;
A refrigeration cycle side pressure measuring device for measuring the pressure of the refrigerant supplied to the outdoor heat exchanger of the refrigeration cycle device,
The control device stops the air blower during the defrost operation of the air conditioner,
After that, when the measured value of the refrigeration cycle side pressure measuring device exceeds the upper limit side reference value, the operation of the blower is restarted. A combined air conditioner comprising an air conditioner and a refrigeration cycle apparatus in which refrigerant circuits including an outdoor heat exchanger and other components are independently provided,
One outdoor unit in which the outdoor heat exchanger of each refrigerant circuit is stored;
An air blower that takes outside air into the outdoor unit and makes contact with the outdoor heat exchangers,
The outdoor heat exchanger of the refrigeration cycle apparatus is divided into a plurality of heat exchanger units,

A combined air-conditioning facility, wherein the refrigerant circuit of the refrigeration cycle apparatus is provided with a valve that allows and regulates the flow of refrigerant to at least one of the heat exchange units. A refrigeration cycle side refrigerant pressure measuring device for measuring a pressure of refrigerant supplied to the outdoor heat exchanger of the refrigerant circuit of the refrigeration cycle device;
A control device for controlling the operation of the valve based on the measurement value of the refrigeration cycle side pressure measurement device,
When the measured value of the refrigeration cycle side pressure measuring device falls below a lower limit side reference value, the control device operates the valve to count the number of heat exchange units that allow the refrigerant to circulate among the heat exchange units. The combined air-conditioning equipment according to claim 9, wherein the combined air-conditioning equipment is characterized in that A method for operating the combined air conditioning facility according to claim 2,
Based on the measured value of the refrigeration cycle side refrigerant pressure measuring device, the opening degree of each of the first and second flow rate control valves is controlled, and the measured value of the refrigeration cycle side refrigerant pressure measuring device falls below the lower limit side reference value. In this case, the operating method of the composite air conditioner, wherein the opening of the second flow control valve is increased while the opening of the first flow control valve is reduced. One outdoor unit that includes an air conditioner and a refrigeration cycle apparatus each independently provided with a refrigerant circuit including an outdoor heat exchanger and other components, and in which the outdoor heat exchanger of each refrigerant circuit is housed. A method of operating a combined air-conditioning facility having a fan and a blower that takes outside air into the outdoor unit and contacts the outdoor heat exchanger,
A refrigeration cycle side pressure measuring device for measuring the pressure of refrigerant supplied to the outdoor heat exchanger of the refrigeration cycle device;
A low pressure side pressure measuring device that measures the pressure of the refrigerant that has passed through the outdoor heat exchanger of the air conditioner during the heating cycle formation of the air conditioner;
At the time of forming the heating cycle of the air conditioner, the measured value of the low pressure side pressure measuring device is within a range where efficient heating operation of the air conditioner is performed, and the measured value of the refrigeration cycle side pressure measuring device is the refrigeration. A method of operating a combined air conditioner, characterized in that the amount of air blown from the blower is controlled to be within a range where efficient operation of the cycle device is performed. One outdoor unit that includes an air conditioner and a refrigeration cycle apparatus each independently provided with a refrigerant circuit including an outdoor heat exchanger and other components, and in which the outdoor heat exchanger of each refrigerant circuit is housed. A method of operating a combined air-conditioning facility having a fan and a blower that takes outside air into the outdoor unit and contacts the outdoor heat exchanger,
A refrigeration cycle side pressure measuring device for measuring the pressure of refrigerant supplied to the outdoor heat exchanger of the refrigeration cycle device;
A high-pressure side pressure measuring device that measures the pressure of the refrigerant supplied to the outdoor heat exchanger of the air conditioner when forming a cooling cycle of the air conditioner,
At the time of forming the cooling cycle of the air conditioner, the measured value of the high pressure side pressure measuring device is within the range where the efficient cooling operation of the air conditioner is performed, and the measured value of the refrigeration cycle side pressure measuring device is the refrigeration. A method of operating a combined air conditioner, characterized in that the air flow rate of the air blower is controlled to be within a range where an efficient operation of the cycle device is performed. One outdoor unit that includes an air conditioner and a refrigeration cycle apparatus each independently provided with a refrigerant circuit including an outdoor heat exchanger and other components, and in which the outdoor heat exchanger of each refrigerant circuit is housed. A method of operating a combined air-conditioning facility having a fan and a blower that takes outside air into the outdoor unit and contacts the outdoor heat exchanger,
A refrigeration cycle side pressure measuring device for measuring the pressure of the refrigerant supplied to the outdoor heat exchanger of the refrigeration cycle device,
During the defrost operation of the air conditioner, the blower is stopped,
After that, when the measured value of the refrigeration cycle side pressure measuring device exceeds the upper limit side reference value, the operation of the blower is restarted. A method of operating a combined air conditioning facility according to claim 9,
A refrigeration cycle side refrigerant pressure measuring device for measuring the pressure of the refrigerant supplied to the outdoor heat exchanger of the refrigerant circuit of the refrigeration cycle device is provided,
When the measured value of the refrigeration cycle side pressure measuring device falls below the lower limit side reference value, the valve is operated to reduce the number of heat exchange units through which the refrigerant flows in the heat exchange unit. A method of operating the combined air-conditioning equipment.

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