JP2000065398A - Refrigerating cycle device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve the efficiency of a refrigerating cycle device of secondary refrigerant system. SOLUTION: In a refrigerating cycle device for effecting heat exchange between heat source side refrigerant and load side refrigerant through the first auxiliary heat exchanger 4 of a heat source side cycle A and the second auxiliary heat exchanger 7 of a load side cycle B, a load betector 10 for detecting the amount of loaded condition in a load side heat exchanger 8, quantity of state refrigerant detecting means 11, 15, 19-21 for detecting the quantity of state of heat source side refrigerant and/or the quantity of state of load side refrigerant as the quantity of state of the refrigerant, and control means 12-14, 16-18, 22-24 for controlling the operation of a compressor 1 and/or a pressure reducer 3 and/or the operation of a refrigerant transporting pump 6 through the control amount of the amount of loaded condition and the quantity of state of the refrigerant, are provided to determine the handling method of the amount of loaded condition and the quantity of state of the refrigerant as the control amount through the control means 12-14, 16-18, 22-24 in accordance with the quantity of state of the refrigerant.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a refrigeration cycle apparatus of a secondary refrigerant system type, and more particularly, to a secondary refrigerant system type using a flammable or toxic refrigerant which does not adversely affect the global environment. The present invention relates to a refrigeration cycle device.

[0002]

2. Description of the Related Art Compressors, heat source side heat exchangers, pressure reducers, load side heat exchangers, etc. are connected to electric (refrigeration) refrigerators, air conditioners, car air conditioners, refrigerated or frozen warehouses, showcases, and the like. Refrigeration cycle devices have been applied, and hydrocarbons containing fluorine atoms have been used as the refrigerant to be enclosed.

In particular, hydrocarbons (HCFCs, hydrochlorofluorocarbons) containing both fluorine and chlorine atoms have good performance, are nonflammable, and are nontoxic to the human body. In this case, there is no possibility of explosion or acute poisoning, so the refrigerant that has passed through the compressor and the heat source-side heat exchanger is transferred to the load-side heat exchanger (evaporator of an electric (refrigeration) refrigerator or indoor heat exchanger of an air conditioner). Refrigeration cycle devices of the direct expansion system type, which are directly introduced into the refrigeration cycle, have been widely used.

However, it has been revealed that HCFCs (hydrochlorofluorocarbons) have a chlorine atom and thus destroy the ozone layer when they are released into the atmosphere and reach the stratosphere. In recent years, its use has been banned or restricted worldwide.

[0005] Instead of these, HF containing no chlorine atom
Although C (hydrofluorocarbon) is being used, it does not have the property of destructing the ozone layer, but has a long greenhouse effect due to its long life in the atmosphere, and it is important in preventing global warming, which has recently become a problem. It is not always a satisfactory refrigerant.

[0006] Instead of the above-mentioned halogen-containing HCFCs and HFCs, they are strongly flammable but have an ozone depletion potential of zero and a global warming potential much higher than hydrocarbons containing halogen atoms. A refrigeration cycle device using a small hydrocarbon containing no halogen atoms as a refrigerant has been partially put into practical use as a refrigerator, and the possibility of developing a larger device has been studied.

[0007] A refrigerating cycle device of a secondary refrigerant system type using toxic ammonia is used in a part of a large freezing warehouse or the like.

[0008]

However, in equipment other than refrigerators, as the required amount of refrigerant to be charged increases, the possibility of explosion or acute poisoning in the event of leakage into a closed space increases. In order to avoid these problems, a refrigeration cycle device of a secondary refrigerant system type that introduces a safe load-side refrigerant (secondary refrigerant) into the load-side heat exchanger can be considered. As a result, the efficiency of the refrigeration cycle equipment decreases, and the power consumption increases. There is a problem that global warming is promoted by the increase in the amount.

Also, a compressor, a heat source side heat exchanger, a pressure reducer,
Compared with the direct expansion system type refrigeration cycle device mainly including the load side heat exchanger, the auxiliary heat exchanger that exchanges heat between the heat source side cycle and the load side cycle and the load side in the load side cycle There is also a problem that a cost increase is unavoidable in a refrigeration cycle device of a secondary refrigerant system type that requires a new refrigerant transport unit for circulating the refrigerant.

Further, a refrigeration cycle apparatus of a secondary refrigerant system using ammonia in a part of a large refrigeration warehouse or the like has only a single function of cooling or heating only in the load side heat exchanger. However, there is also a problem that it is not possible to operate efficiently by appropriately switching the cooling function and the heating function.

The present invention provides a secondary refrigerant system-type refrigeration cycle apparatus capable of improving efficiency and / or suppressing cost increase in consideration of the above-mentioned problems of the conventional secondary refrigerant system-type refrigeration cycle apparatus. The purpose is to provide.

[0012]

In order to solve the above-mentioned problems, a first invention (corresponding to the first invention) is provided.
Comprises a heat source side cycle having at least a compressor, a heat source side heat exchanger, a decompressor and a first auxiliary heat exchanger, and a load side cycle having at least refrigerant transfer means, a load side heat exchanger and a second auxiliary heat exchanger. In the refrigeration cycle apparatus, wherein the first auxiliary heat exchanger and the second auxiliary heat exchanger perform heat exchange between a heat source side refrigerant and a load side refrigerant, at least the heat source side cycle A heat-source-side heat exchanger, a heat-source-side flow switching unit that switches a flow direction of the heat-source-side refrigerant in the decompressor and the first auxiliary heat exchanger, and a load-side refrigerant in the second auxiliary heat exchanger. And a load-side flow switching means for switching a flow direction, wherein the load-side flow switching means is provided in the first auxiliary heat exchanger and the second auxiliary heat exchanger according to a state of the heat source side cycle. As exchange is performed more efficiently, a refrigeration cycle apparatus characterized by selecting and switching to the flow direction of the load-side refrigerant.

According to a second aspect of the present invention (corresponding to the second aspect of the present invention), the load-side flow switching means includes a path through which the heat source-side refrigerant and the load-side refrigerant exchange at least the heat. The refrigeration cycle apparatus according to the first aspect of the present invention is characterized in that the flow direction of the load-side refrigerant is selected and switched so that the whole or a part of the upper part flows in directions facing each other.

According to a third aspect of the present invention (corresponding to the third aspect of the present invention), the load-side heat exchanger is configured such that the load-side refrigerant flows in a direction facing a load object. The refrigeration cycle apparatus according to the first or second aspect of the present invention, wherein the direction of the flow of the load-side refrigerant in the load-side heat exchanger is not changed by the switching of the load-side flow switching means. .

A fourth aspect of the present invention (corresponding to the fourth aspect of the present invention) comprises a heat source side cycle having at least a compressor, a heat source side heat exchanger, a pressure reducer and a first auxiliary heat exchanger, and at least a refrigerant. And a load side cycle having a load side heat exchanger and a second auxiliary heat exchanger. In the first auxiliary heat exchanger and the second auxiliary heat exchanger, a heat source side refrigerant, a load side refrigerant, A load state quantity detecting means for detecting a load state quantity in the load side heat exchanger, and a state quantity of the heat source side refrigerant and / or a state of the load side refrigerant. A refrigerant state quantity detecting means for detecting an amount as a refrigerant state quantity; and operating the compressor and / or operating the pressure reducer and / or operating the refrigerant conveying means, using the load state quantity and the refrigerant state quantity as control amounts. operation Control means for controlling, wherein the control means determines how to treat the load state amount and the refrigerant state amount as the control amount according to the refrigerant state amount. is there.

According to a fifth aspect of the present invention (corresponding to the fifth aspect of the present invention), the refrigerant state quantity is set between the pressure reducing device on the side including the first auxiliary heat exchanger and the compressor. The pressure of the heat-source-side refrigerant at a predetermined position, and / or the degree of superheat or supercooling of the heat-source-side refrigerant at the first auxiliary heat exchanger outlet or the heat source-side heat exchanger outlet, and / or The temperature difference of the load-side refrigerant between the inlet side and the outlet side of the second auxiliary heat exchanger, wherein when the control means controls the operation of the compressor, the load state amount and the heat-source-side refrigerant The pressure as the control amount, and when the control means controls the operation of the pressure reducer, the load state amount;
And, when the degree of superheat or the degree of supercooling of the heat source side refrigerant is the control amount, and when the control means controls the operation of the refrigerant conveying means, the load state amount and the temperature of the load side refrigerant A refrigeration cycle apparatus according to a fourth aspect of the present invention, wherein the difference is the control amount.

According to a sixth aspect of the present invention (corresponding to the sixth aspect of the present invention), the refrigerant state quantity detecting means measures the degree of superheat at the discharge side of the compressor, so that the heat source side refrigerant is measured. The refrigeration cycle apparatus according to a fifth aspect of the present invention, wherein the superheat degree is detected.

According to a seventh aspect of the present invention (corresponding to the seventh aspect of the present invention), when the refrigerant state quantity is not within a first predetermined range, the control means gives priority to the load state quantity. do it,
The refrigerant state quantity is controlled so as to fall within the first range, and when the refrigerant state quantity is within a second range including the first range, the refrigerant state quantity is prioritized over the refrigerant state quantity. Control so that the load state quantity falls within a predetermined load range,
When the refrigerant state quantity is within the first range and is not within the second range, control that sets the refrigerant state quantity as a control amount, and control that sets the load state amount as a control amount, A refrigeration cycle apparatus according to any one of the fourth to sixth aspects of the present invention, wherein each of the refrigeration cycle apparatuses is weighted according to the refrigerant state quantity.

An eighth aspect of the present invention (corresponding to the eighth aspect of the present invention) comprises a heat source side cycle having at least a compressor, a heat source side heat exchanger, a pressure reducer and a first auxiliary heat exchanger, and at least a refrigerant. And a load side cycle having a load side heat exchanger and a second auxiliary heat exchanger. In the first auxiliary heat exchanger and the second auxiliary heat exchanger, a heat source side refrigerant, a load side refrigerant, In a refrigeration cycle apparatus that performs heat exchange between the second auxiliary heat exchanger, a refrigerant state quantity detecting unit that detects a temperature difference of the load-side refrigerant between an inlet side and an outlet side of the second auxiliary heat exchanger, Control means for controlling the operation of the refrigerant transport means as a control amount.

A ninth aspect of the present invention (corresponding to the ninth aspect of the present invention) is characterized in that the refrigerant transfer means is disposed on a path on an outlet side of the load side heat exchanger. First
It is a refrigeration cycle apparatus of any one of the present invention.

According to a tenth aspect of the present invention (corresponding to the tenth aspect of the present invention), the heat source side refrigerant is mainly composed of a flammable or toxic refrigerant. A refrigeration cycle apparatus according to any one of the present invention.

[0022]

Embodiments of the present invention will be described below with reference to the drawings.

(First Embodiment) First, the first embodiment of the present invention will be described.
An embodiment will be described with reference to the drawings. FIG. 1 is a schematic configuration diagram illustrating a refrigeration cycle device according to a first embodiment of the present invention. In FIG. 1, 1 is a compressor, 2 is a heat source side heat exchanger, 3 is a decompressor, 4 is a first auxiliary heat exchanger, and these are connected to form a heat source side cycle A. Also, a four-way valve 5 capable of reversing the refrigerant flow direction of the heat source side cycle A (corresponding to the heat source side flow switching means of the present invention)
And a flammable or toxic refrigerant (for example, propane) is sealed as a heat source side refrigerant. 6 is a refrigerant transfer pump (corresponding to the refrigerant transfer means of the present invention), 7 is a second auxiliary heat exchanger, 8 is a load side heat exchanger, and these are connected to form a load side cycle B. I have. Further, a four-way valve 9 for switching the inlet and outlet of the second auxiliary heat exchanger 7 (corresponding to the load-side flow path switching means of the present invention)
And a nonflammable or low-toxic refrigerant (for example, water) is sealed as a load-side refrigerant. Here, heat is exchanged between the first auxiliary heat exchanger 4 and the second auxiliary heat exchanger 7, and the solid arrows in the figure indicate the refrigerant flow when the cooling operation is performed by the load side heat exchanger 8. , Dotted arrows indicate the flow of the refrigerant when the heating action is performed.

Next, the operation of the refrigeration cycle apparatus according to the present embodiment will be described.

First, when the cooling operation is performed by the load side heat exchanger 8, the four-way valves 5 and 9 are respectively set as shown by the solid lines. In the heat source side cycle A, the heat source side refrigerant compressed by the compressor 1 has a high temperature and a high pressure, is guided to the heat source side heat exchanger 2 through the four-way valve 5, and is cooled by a heat source such as outside air or a river to be a high pressure liquid. The refrigerant is introduced into the decompressor 3 and decompressed to become a low-temperature and low-pressure two-phase refrigerant.
Will be introduced. The first auxiliary heat exchanger 4 exchanges heat with the second auxiliary heat exchanger 7, that is, absorbs heat from the load-side refrigerant flowing through the second auxiliary heat exchanger 7 to evaporate and evaporates, and passes through the four-way valve 5 to recompress the compressor. Inhaled into 1. In the load side cycle B, the load side refrigerant is supplied by the refrigerant transfer pump 6 to the four-way valve 9.
And is introduced into the second auxiliary heat exchanger 7. In the second auxiliary heat exchanger 7, the heat is absorbed by the heat source-side refrigerant in the first auxiliary heat exchanger 4 to be cooled to a low temperature, and is introduced into the load-side heat exchanger 8 via the four-way valve 9. Load side heat exchanger 8
Then, heat is absorbed from the load object (for example, indoor air for air conditioning, indoor air for refrigeration, and freezing use, etc.), and the load object is cooled down to near normal temperature, and then introduced into the refrigerant transport pump 6 again.

As described above, when the refrigeration cycle apparatus according to the present embodiment performs a cooling operation, the amount of heat absorbed from the load target in the load side heat exchanger 8 is transferred to the second auxiliary heat exchanger 7 and the first Through the heat exchange with the auxiliary heat exchanger 4, the heat is exhausted to the heat source by the heat source side heat exchanger 2. The flow of the load side refrigerant in the second auxiliary heat exchanger 7 and the first auxiliary heat exchanger 4 By making the heat source side refrigerant flow in the counter flow, heat exchange is performed efficiently, and the efficiency of the refrigeration cycle device is improved.

The load-side heat exchanger 8 is connected to the load-side refrigerant flow and the load object (eg, room air for air-conditioning, air inside the refrigerator for refrigeration, and refrigeration applications, etc.). The flow direction of the load-side refrigerant in the load-side heat exchanger 8 is not changed by switching the four-way valve 9, so that heat exchange can be performed efficiently. This is to improve the efficiency of the refrigeration cycle apparatus.

Further, by providing the refrigerant transfer pump 6 at the outlet side of the load-side heat exchanger 8, the load-side refrigerant flowing through the refrigerant transfer pump 6 is supplied from the second auxiliary heat exchanger 7 outlet to the load-side heat exchanger 8 inlet. Since the temperature of the refrigerant transfer pump 6 is closer to room temperature than that of the load side refrigerant, the use condition of the refrigerant transfer pump 6 is not strict, and a special material and configuration are not required, thereby suppressing an increase in cost.

On the other hand, when the heating operation is performed by the load side heat exchanger 8, the four-way valves 5 and 9 are set as indicated by dotted lines. In the heat source side cycle A, the heat source side refrigerant compressed by the compressor 1 has a high temperature and a high pressure, is guided to the first auxiliary heat exchanger 4 through the four-way valve 5, and exchanges heat with the second auxiliary heat exchanger 7. That is, heat is released to the load-side refrigerant flowing through the second auxiliary heat exchanger 7 and condensed and liquefied to become a high-pressure liquid refrigerant.
And is reduced in pressure to become a low-temperature low-pressure two-phase refrigerant, and is introduced into the heat source side heat exchanger 2. The heat source side heat exchanger 2 absorbs heat from a heat source such as outside air or a river to evaporate and gasify it.
Is drawn into the compressor 1 again. In the load side cycle B, the load side refrigerant is introduced into the second auxiliary heat exchanger 7 via the four-way valve 9 by the refrigerant transfer pump 6. In the second auxiliary heat exchanger 7, it is heated to a high temperature by being radiated from the heat source side refrigerant in the first auxiliary heat exchanger 4, and is introduced into the load side heat exchanger 8 via the four-way valve 9. In the load side heat exchanger 8, heat is radiated (that is, heats the load target) to a load target (for example, indoor air in the case of air conditioning, hot water supply in the case of hot water supply), the temperature becomes close to normal temperature, and is introduced again into the refrigerant transport pump 6. You.

As described above, when the refrigeration cycle apparatus according to the present embodiment performs a heating operation, the amount of heat absorbed from the heat source in the heat source side heat exchanger 2 is converted into the second auxiliary heat exchanger 7.
The load target is heated by the load-side heat exchanger 8 through heat exchange between the first auxiliary heat exchanger 4 and the first auxiliary heat exchanger 4. The flow of the load-side refrigerant in the second auxiliary heat exchanger 7 and the first auxiliary heat By causing the flow of the heat source side refrigerant in the exchanger 4 to flow in the opposite direction, heat exchange is performed efficiently, and the efficiency of the refrigeration cycle apparatus is improved.

Further, as described above, the load-side heat exchanger 8 causes the flow of the load-side refrigerant and the flow of the load object (for example, room air in the case of air conditioning, hot water in the case of hot water supply) to be counter-flowed. Since the direction of the flow of the load-side refrigerant in the load-side heat exchanger 8 is not changed by switching the four-way valve 9, heat is efficiently exchanged and the efficiency of the refrigeration cycle device is improved. It is.

Further, by providing the refrigerant transfer pump 6 on the outlet side of the load side heat exchanger 8, the load side refrigerant flowing through the refrigerant transfer pump 6 is supplied from the second auxiliary heat exchanger 7 outlet to the load side heat exchanger 8 inlet. Since the temperature of the refrigerant transfer pump 6 is closer to room temperature than that of the load side refrigerant, the use condition of the refrigerant transfer pump 6 is not strict, and a special material and configuration are not required, thereby suppressing an increase in cost.

As described above, in the refrigeration cycle apparatus according to the present embodiment as shown in FIG. 1, the heat source side refrigerant flow in the first auxiliary heat exchanger 4 and the load side refrigerant in the second auxiliary heat exchanger 7 Counterflow with the refrigerant flow and counterflow between the load-side refrigerant flow in the load-side heat exchanger 8 and the flow of the load target can be performed both during the cooling operation and during the heating operation, thereby improving the efficiency of the refrigeration cycle device. Can be realized. Further, during both the cooling operation and the heating operation, the load-side refrigerant flowing through the refrigerant transfer pump 6 is discharged from the second auxiliary heat exchanger 7 to the load-side heat exchanger 8.
Since the temperature is closer to room temperature than the load-side refrigerant between the inlets, the use conditions of the refrigerant transport pump 6 are not strict, and a special material and configuration are not required, thereby suppressing an increase in cost.

When the first auxiliary heat exchanger 4 and the second auxiliary heat exchanger 7 are integrated plate heat exchangers or stacked heat exchangers, the heat source side cycle A and the load side cycle B A plate-type heat exchanger or a stacked heat exchanger is installed so that the amount of refrigerant to be sealed can be reduced and the heat source side refrigerant flow in the first auxiliary heat exchanger 4 flows upward during the cooling operation and flows downward during the heating operation. If the load-side refrigerant flow in the second auxiliary heat exchanger 7 is made to flow counter-currently so as to flow downward during the cooling operation and to flow upward during the heating operation, the refrigerant efficiently evaporates in the first auxiliary heat exchanger 4. Alternatively, condensation is performed, and the efficiency of the refrigeration cycle device is further improved.

In this embodiment, the flow of the load-side refrigerant in the second auxiliary heat exchanger 7 and the flow of the heat-source-side refrigerant in the first auxiliary heat exchanger 4 are defined on a path through which heat is exchanged. Although the description has been made assuming that the flow is counter-flowed as a whole, the flow is not limited to this. It may be made to flow in the direction in which it does. In short, the heat exchange in the first auxiliary heat exchanger and the second auxiliary heat exchanger is more efficient depending on the state of the heat source side cycle (for example, the flow direction of the heat source side refrigerant in the first auxiliary heat exchanger). The load-side flow switching means of the present invention may be any one that selects and switches the flow direction of the load-side refrigerant in the second auxiliary heat exchanger. When the cooling operation is performed in the load side heat exchanger 8, the first auxiliary heat exchanger 4 acts as an evaporator, but the heat source side refrigerant usually becomes a superheated gas at the outlet of the first auxiliary heat exchanger 4, and Since the temperature becomes higher than the temperature of the heat source side refrigerant at the inlet of the first auxiliary heat exchanger 4, the heat source side refrigerant at the inlet of the first auxiliary heat exchanger 4 and the load side of the second auxiliary heat exchanger 7 as described above. What is necessary is just to set the load side flow path switching means (four-way valve 9) so that the refrigerant and the refrigerant are caused to flow in opposite directions. However, for example, when the flow rate of the heat-source-side refrigerant is very large, the pressure loss in the first auxiliary heat exchanger 4 becomes large, that is, the vaporization due to the pressure loss becomes more downstream in the first auxiliary heat exchanger 4. The temperature of the heat-source-side refrigerant at the outlet of the first auxiliary heat exchanger 4 is reduced by the first auxiliary heat exchanger 4.
Since the temperature is lower than the heat source side refrigerant temperature at the inlet, the heat source side refrigerant flow in the first auxiliary heat exchanger 4 and the second auxiliary heat exchanger 7
In some cases, the heat exchange can be performed more efficiently by setting the load-side flow path switching means (four-way valve 9) so that the load-side refrigerant in the inside flows in parallel. In short, cycle A on the heat source side
(For example, the flow direction of the heat-source-side refrigerant in the first auxiliary heat exchanger 4, the temperature at the inlet and the outlet, etc.)
In order that the heat exchange in the first auxiliary heat exchanger 4 and the second auxiliary heat exchanger 7 is performed more efficiently, the load-side flow path switching means (four-way valve 9) of the present invention is provided with the second auxiliary heat exchanger. What is necessary is just to select and switch the flow direction of the load-side refrigerant in the vessel 7. Further, as described in the present embodiment, the flow of the load-side refrigerant in the second auxiliary heat exchanger 7 and the flow of the first auxiliary heat exchanger 4
By setting the load-side flow switching means (four-way valve 9) so as to make the heat source-side refrigerant flow in the inside counter-flow, the efficiency of the refrigeration cycle device during normal operation is improved and the heat source-side refrigerant is newly added. (1) A simple refrigeration cycle apparatus that does not require a means for detecting a temperature state at the inlet and the outlet of the auxiliary heat exchanger 4 can be realized, that is, efficiency can be effectively improved while suppressing cost increase.

The location where the refrigerant transfer pump 6 is provided is on the outlet side of the load-side heat exchanger 8, but is not limited to the vicinity of the outlet side of the load-side heat exchanger 8, and is not limited thereto. The same effect as described above can be obtained between the four-way valves 9.

(Second Embodiment) Next, a second embodiment of the present invention will be described.
An embodiment will be described with reference to the drawings. In the present embodiment, components that are not particularly described are the same as those in the first embodiment, and components that are assigned the same reference numerals as those in the first embodiment are the same as those in the first embodiment unless otherwise described. It has the same function as that of the first embodiment.

FIG. 2 is a schematic configuration diagram showing a refrigeration cycle apparatus according to a second embodiment of the present invention. The refrigeration cycle apparatus shown in FIG. 2 is configured to perform a cooling operation (endothermic operation) in the load-side heat exchanger 8, and a solid arrow in the drawing indicates a refrigerant flow, and a wavy arrow indicates a signal flow. The refrigeration cycle apparatus according to the present embodiment is different from the refrigeration cycle apparatus shown in FIG. 2 in that the flow of the heat-source-side refrigerant in the heat-source-side cycle A is reversed by replacing the compressor 1 with the load. A configuration (not shown) in which a heating action (radiation action) is performed by the side heat exchanger 8, and a cooling action / heating action can be switched by inserting a four-way valve as shown in FIG. 1 ( (Not shown). Therefore, in the following description, the case where the heating operation is performed by the load side heat exchanger 8 in addition to the case where the cooling operation is performed by the load side heat exchanger 8 corresponding to the configuration of FIG. 2 will be described. The load side heat exchanger 8
In the case where the heating action is performed, as described in the first embodiment, by switching the flow direction of the load-side refrigerant in the second auxiliary heat exchanger 7, a more efficient refrigeration cycle apparatus can be obtained. Become.

In FIG. 2, reference numeral 10 denotes a load detector (for example, a room temperature when the refrigeration cycle apparatus is used for air conditioning) at the load side heat exchanger 8 (the load state according to the present invention). 11 is a pressure detector (corresponding to the refrigerant state quantity detecting means of the present invention) for detecting the pressure of the first auxiliary heat exchanger 4, and 12 is a load state detected by the load detector 10. The first compressor controller 13 that determines the operating capacity of the compressor 1 so as to match the target load state (for example, the set temperature), the compressor controller 13 controls the compressor so that the pressure detected by the pressure detector 11 matches the target pressure. The second compressor controller 14 determines the operating capacity of the first compressor 14. The second compressor controller 14 determines the compressor operating capacity determined by the first compressor controller 12 according to the pressure detected by the pressure detector 11. 13 to determine the priority of the compressor operating capacity A third compressor controller for controlling the compressor operating capacity. The combination of the first compressor controller 12, the second compressor controller 13, and the third compressor controller 14 corresponds to the control means of the present invention.

Reference numeral 15 denotes a superheat / supercool degree detector (corresponding to the refrigerant state quantity detection means of the present invention) for detecting the degree of superheat at the outlet of the first auxiliary heat exchanger 4. 16 is the load detector 1
The first pressure reducer controller that determines the amount of pressure reduction in the pressure reducer 3 so that the load state detected at 0 matches the target load state, 1
Reference numeral 7 denotes a depressurizer 3 so that the degree of superheat or the degree of supercooling detected by the degree of superheat / degree of supercooling detector 15 matches the target degree of superheat.
A second decompressor controller 18 for determining the amount of decompression at the pressure reducing device 18 is a decompression determined by the first decompressor controller 16 according to the degree of superheat or the degree of supercooling detected by the superheat / supercool degree detector 15. The third pressure reducer controller controls the pressure reduction amount in the pressure reducer 3 by determining the priority of the pressure reduction amount of the pressure reducer and the pressure reduction amount determined by the second pressure reducer controller 17. In addition, the first decompressor controller 16,
The combination of the second pressure reducer controller 17 and the third pressure reducer controller 18 corresponds to the control means of the present invention.

When the superheat / supercool detector 15 performs the cooling operation in the load side heat exchanger 8 as shown in FIG. 2, the first auxiliary heat exchanger 4 functions as an evaporator. Therefore, when the heating operation is performed in the load-side heat exchanger 8, the first auxiliary heat exchanger 4 acts as a condenser, so that the supercooling degree is detected.

Reference numeral 19 denotes a second auxiliary heat exchanger inlet side temperature detector for detecting the temperature at the inlet side of the second auxiliary heat exchanger 7, and reference numeral 20 denotes a temperature at the outlet side of the second auxiliary heat exchanger 7. The second auxiliary heat exchanger outlet side temperature detector 21 detects the temperature detected by the second auxiliary heat exchanger inlet side temperature detector 19 and the second auxiliary heat exchanger outlet side temperature detector 20, respectively. A second auxiliary heat exchanger temperature difference calculator 22 for calculating a difference (hereinafter simply referred to as a temperature difference) 22 is provided at the refrigerant transfer pump 6 so that the load state detected by the load detector 10 matches the target load state. The first refrigerant transfer pump controller 23 for determining the refrigerant transfer amount is configured to transfer the refrigerant by the refrigerant transfer pump 6 such that the temperature difference calculated by the second auxiliary heat exchanger temperature difference calculator 21 matches the target temperature difference. The second refrigerant transfer pump controller for determining the amount, 24 is the second auxiliary heat The priority of the refrigerant transfer amount determined by the first refrigerant transfer pump controller 22 and the refrigerant transfer amount determined by the second refrigerant transfer pump controller 23 according to the temperature difference calculated by the exchanger temperature difference calculator 21 Is a third refrigerant transport pump controller that controls the amount of refrigerant transported by the refrigerant transport pump 6 by determining The second auxiliary heat exchanger inlet side temperature detector 1
9, the second auxiliary heat exchanger outlet side temperature detector 20 and the second auxiliary heat exchanger
The combination of the auxiliary heat exchanger temperature difference calculator 21 corresponds to the refrigerant state quantity detecting means of the present invention, and the first refrigerant transport pump controller 22, the second refrigerant transport pump controller 23, and the third
The combination of the refrigerant transport pump controller 24 corresponds to the control means of the present invention.

FIG. 3 is a flowchart showing a control procedure performed by the control means (third compressor controller 14) in the present embodiment. First, the pressure detected by the pressure detector 11 is compared with a first pressure threshold (for example, set based on the upper limit of the allowable use range of the compressor 1) (Step 101), and the pressure is larger than the first pressure threshold. In this case, the pressure membership value is set to 0 (step 102), and when the pressure is smaller than the first pressure threshold, a second pressure threshold smaller than the first pressure threshold (for example, the upper limit of the normal use range of the compressor 1 is also set). (Step 103) and the pressure detected by the pressure detector 11 are compared (Step 103). If the pressure is larger than the second pressure threshold, the pressure is monotonously continuous in a range from 0 to 1 according to the pressure. The pressure is substituted into the function f1 which makes the change, and a pressure membership value is set (step 104). If the pressure is smaller than the second pressure threshold, a third pressure threshold smaller than the second pressure threshold (for example, the compressor 1) Common use range of (Set based on the pressure limit) and the pressure detected by the pressure detector 11 (step 105). If the pressure is larger than the third pressure threshold, the pressure membership value is set to 1 (step 105). 1
06) When the pressure is smaller than the third pressure threshold, the fourth pressure threshold smaller than the third pressure threshold (for example, set based on the lower limit of the allowable use range of the compressor 1) and the pressure detected by the pressure detector 11 (Step 107), and when the pressure is larger than the fourth pressure threshold, 1 to 0 depending on the pressure.
The pressure is substituted into the function f2 which changes monotonously and continuously in the range up to and a pressure membership value is set (step 10).
8) If the pressure is smaller than the fourth pressure threshold, the pressure membership value is set to 0 (step 102). Then, the sum of the product of the operating capacity of the first compressor controller 12 and the pressure membership value and the product of the operating capacity of the second pressure controller 13 and the value obtained by subtracting the pressure membership value from 1 The compressor operation capacity is determined to control the compressor 1 (step 109), which is executed at regular time intervals.

That is, the range of the fourth pressure threshold to the first pressure threshold corresponds to the first range of the present invention, and the range of the third pressure threshold to the second pressure threshold corresponds to the second range of the present invention. It corresponds to the range.

When the cooling operation is performed by the load side heat exchanger 8, when the pressure detected by the pressure detector 11 (evaporation pressure / suction pressure) is determined to be larger than the first pressure threshold value in step 101, Alternatively, when it is determined in step 107 that the pressure is smaller than the fourth pressure threshold, the pressure is out of the allowable use range of the compressor 1 and the reliability of the compressor 1 is significantly impaired, or the efficiency is extremely low. Accordingly, in step 109, the operation capability of the second compressor controller 13 is given top priority, and when it is determined in step 101 that the pressure detected by the pressure detector 11 is larger than the first pressure threshold, the compressor 1 The operating capacity is increased to reduce the pressure, or if it is determined in step 107 that the pressure is smaller than the fourth pressure threshold, the operating capacity of the compressor 1 is reduced to increase the pressure. It is allowed to ensure the reliability of the compressor 1 kept within allowable operating range of the compressor 1 the pressure, or to improve the very low operating state of efficiency.

The pressure detected by the pressure detector 11 (evaporation pressure / suction pressure) is determined to be smaller than the second pressure threshold value in step 103, and the third pressure value is determined in step 105.
When it is determined that the pressure is larger than the pressure threshold, the pressure is within the normal use range of the compressor 1 and there is no problem in the reliability of the compressor 1 or the efficiency is high. When the load state (for example, room temperature) detected by the load detector 10 is higher than the target load state (for example, set temperature), the first compressor controller 12 gives the compressor 1 Is determined in the increasing direction. As a result, the heat source-side refrigerant flow rate flowing in the first auxiliary heat exchanger 4 increases, and the amount of cooling by the first auxiliary heat exchanger 4 to the second auxiliary heat exchanger 7 increases,
The load cooling amount in the load side heat exchanger 8 increases, and the load state (for example, room temperature) can be made to match the target load state (for example, set temperature). Alternatively, when the load state (for example, room temperature) detected by the load detector 10 is lower than the target load state (for example, set temperature), the first compressor controller 12
Thus, the operating capacity of the compressor 1 is determined in the decreasing direction. As a result, the flow rate of the heat source side refrigerant flowing in the first auxiliary heat exchanger 4 decreases, and the second auxiliary heat exchanger 7
The amount of cooling to the load side decreases, the amount of load cooling in the load side heat exchanger 8 decreases, and the load state (for example, room temperature) can be matched with the target load state (for example, set temperature).

The pressure detected by the pressure detector 11 (evaporation pressure / suction pressure) is determined in step 103 to be larger than the second pressure threshold, or in step 107 to be larger than the fourth pressure threshold. In some cases, the pressure is within the allowable use range of the compressor 1 but outside the normal use range, and is in a state that is not very preferable from the viewpoint of the reliability of the compressor 1 or a state in which the efficiency is slightly low. Since the operating capacity of the compressor 1 by the first compressor controller 12 and the operating capacity of the compressor 1 by the second compressor controller 13 are mixed to control the compressor 1, the pressure is used in the normal operation of the compressor 1. The load state (for example, room temperature) can be made to match the target load state (for example, set temperature) while keeping within the use range or shifting to a state of high efficiency.

As described above, the first compressor controller 12, the second compressor controller 13, and the third compressor controller 14
The load state can be made to coincide with the target load state while maintaining a high efficiency state.

Also, when the heating operation is performed by the load side heat exchanger 8, the first compression is similarly performed based on the pressure detected by the pressure detector 11 (corresponding to the condensing pressure / the discharge pressure). The load state can be matched with the target load state while maintaining a high efficiency state by the machine controller 12, the second compressor controller 13, and the third compressor controller 14.

The pressure detector 11 has been described as detecting the pressure of the first auxiliary heat exchanger 4. However, the pressure detector 11 is not limited to this, and the pressure detector 11 extends from the pressure reducer 3 to the suction side of the compressor 1 during the cooling operation. The above-mentioned effects can be obtained by detecting the pressure in the path between the compressor 1 and the pressure in the path from the discharge side of the compressor 1 to the pressure reducer 3 during the heating operation.

FIG. 4 is a flowchart showing a control procedure performed by the control means (third decompressor controller 18) in the present embodiment when the cooling operation is performed in the load side heat exchanger 8. . First, the superheat degree detected by the superheat / supercool degree detector 15 is compared with the first superheat threshold value (step 201). When the superheat degree is larger than the first superheat threshold value, the superheat degree membership is determined. Set the value to 0 (Step 2
02), when the superheat degree is smaller than the first superheat degree threshold value, the second superheat degree threshold value smaller than the first superheat degree threshold value is compared with the superheat degree detected by the superheat / supercool degree detector 15 ( Step 203) If the superheat degree is larger than the second superheat degree threshold value, the superheat degree is substituted into a function f1 that changes monotonously and continuously in a range from 0 to 1 in accordance with the superheat degree, and the superheat degree membership. If the superheat degree is smaller than the second superheat degree threshold, a third superheat degree threshold smaller than the second superheat degree threshold and the superheat degree detected by the superheat / supercool degree detector 15 are set (step 204). (Step 205), and if the superheat is larger than the third superheat threshold, the superheat membership value is set to 1 (Step 206), and if the superheat is smaller than the third superheat threshold. Has a fourth superheat degree smaller than the third superheat threshold Makes a comparison between the value and the degree of superheating / subcooling detector 15 detected degree of superheat in (step 207),
When the superheat degree is larger than the fourth superheat degree threshold value, the superheat degree is substituted into a function f2 that changes monotonously and continuously in a range from 1 to 0 according to the superheat degree, and a superheat degree membership value is set. (Step 208) If the superheat is smaller than the fourth superheat threshold, the superheat membership value is set to 0 (Step 202). Then, the first decompressor controller 16
As the sum of the product of the decompressor depressurization amount and the superheat degree membership value by the pressure reducer and the value obtained by subtracting the superheat degree membership value from 1 by the depressurizer depressurization amount by the second depressurizer controller 17. The amount of pressure reduction is determined and the pressure reducer 3 is controlled (step 2).
09) is executed at regular time intervals.

In other words, the range from the fourth superheat threshold to the first superheat threshold corresponds to the first range of the present invention, and the range from the third superheat threshold to the second superheat threshold is This corresponds to the second range of the invention.

When the cooling operation is performed in the load side heat exchanger 8, the superheat degree detected by the superheat / supercool degree detector 15 (evaporator outlet superheat degree / compressor suction superheat degree) is determined in step 201. When it is determined that is smaller than the first superheat threshold in step 207, or when it is determined that it is smaller than the fourth superheat threshold in step 207, the efficiency of heat exchange in the first auxiliary heat exchanger is very low. Therefore, step 20
In step 9, the pressure reduction amount by the second pressure reducer controller 17 is given the highest priority. That is, when it is determined in step 201 that the degree of superheat detected by the degree of superheat / supercool degree detector 15 is larger than the first superheat degree threshold, the pressure reduction amount of the pressure reducer 3 is reduced to reduce the degree of superheat, or When it is determined in 207 that it is smaller than the fourth superheat degree threshold, the degree of pressure reduction of the pressure reducer 3 is increased to increase the degree of superheat, thereby improving the state in which the efficiency of heat exchange in the first auxiliary heat exchanger 4 is extremely low. I do.

Also, it is determined in step 203 that the superheat degree detected by the superheat / supercool detector 15 (evaporator exit superheat degree / compressor suction superheat degree) is smaller than the second superheat degree threshold value, and When it is determined in step 205 that it is larger than the third superheat degree threshold value, the efficiency of heat exchange in the first auxiliary heat exchanger 4 is high, and in step 209, the amount of pressure reduction by the first pressure reducer controller is reduced. First, when the load state (for example, room temperature) detected by the load detector 10 is higher than the target load state (for example, set temperature), the first pressure reducer controller 16 increases the pressure reduction amount of the pressure reducer 3 in the increasing direction. decide. As a result, the flow rate of the heat source-side refrigerant flowing in the first auxiliary heat exchanger 4 increases, the amount of cooling by the first auxiliary heat exchanger 4 to the second auxiliary heat exchanger 7 increases, and the load-side heat exchanger 8 , The load state (for example, room temperature) can be matched with the target load state (for example, set temperature). Alternatively, when the load state (for example, room temperature) detected by the load detector 10 is lower than the target load state (for example, set temperature), the first pressure reducer controller 16 determines the amount of pressure reduction of the pressure reducer 3 in a decreasing direction. As a result, the heat source-side refrigerant flow rate flowing in the first auxiliary heat exchanger 4 decreases, and the amount of cooling by the first auxiliary heat exchanger 4 to the second auxiliary heat exchanger 7 decreases,
The load cooling amount in the load-side heat exchanger 8 is reduced, and the load state (for example, room temperature) can be made to match the target load state (for example, set temperature).

In step 203, it is determined that the superheat degree detected by the superheat / supercool degree detector 15 (evaporator outlet superheat degree / compressor suction superheat degree) is larger than the second superheat degree threshold value, or If it is determined in step 207 that it is larger than the fourth superheat degree threshold value, the efficiency of heat exchange in the first auxiliary heat exchanger 4 is in a slightly low state. Since the pressure reduction amount of the first auxiliary heat exchanger 4 is controlled by controlling the pressure reduction device 3 by mixing the pressure reduction amount of the pressure reduction device 3 and the pressure reduction amount of the pressure reduction device 3 by the second pressure reduction device controller 17, the efficiency is high. While moving to the state,
The load state (for example, room temperature) can be matched with the target load state (for example, set temperature).

As described above, the first pressure reducer controller 16, the second pressure reducer controller 17, and the third pressure reducer controller 18
The load state can be made to coincide with the target load state while maintaining the state of high heat exchange efficiency of the first auxiliary heat exchanger 4 (that is, the operating state of the refrigeration cycle device with high efficiency).

When the heating operation is performed in the load side heat exchanger 8, the first auxiliary heat exchanger 4 operates as a condenser. Therefore, if the degree of superheat during the cooling operation is replaced with the degree of supercooling, In this case, the control procedure performed by the control means (third depressurizer controller 18) in the present embodiment is as shown in FIG. 5, and the first depressurizer controller 1
6. The second decompressor controller 17 and the third decompressor controller 18 maintain a state in which the first auxiliary heat exchanger 4 has a high heat exchange efficiency (that is, an operation state in which the refrigeration cycle device has a high efficiency). The load state can be made to match the target load state.

When the superheat / supercool detector 15 is arranged at the outlet of the heat source side heat exchanger 2 and not at the position shown in FIG. Detects the degree of supercooling at the same position, or detects the degree of superheating at the same position when the load side heat exchanger 8 performs heating, and performs control similar to that shown in FIGS. , The same effect can be obtained.

Further, when it is difficult for the refrigeration cycle apparatus to detect the degree of superheat at the outlet of the heat source side heat exchanger 2, a discharge superheat degree / supercool degree detector for detecting the degree of superheat at the discharge side of the compressor 1 ( (Not shown), the heat source side heat exchanger 2
Estimate the state of the refrigerant at the outlet (such as the degree of superheat or the degree of dryness in the gas-liquid mixed state) (for example, when the discharge superheat is large, the superheat degree at the outlet of the heat source side heat exchanger 2 is large, When it is small, the degree of superheat at the outlet of the heat source side heat exchanger 2 can be small or the degree of dryness can be small in a gas-liquid mixed state, etc.).
It is also possible to substitute for

FIG. 6 is a flowchart showing a control procedure performed by the control means (third refrigerant transport pump controller 24) in the present embodiment. First, the temperature difference calculated by the second auxiliary heat exchanger temperature difference calculator 21 is compared with the first temperature difference threshold (step 401), and when the temperature difference is larger than the first temperature difference threshold, the temperature difference is calculated. The membership value is set to 0 (step 402), and if the temperature difference is smaller than the first temperature difference threshold, the temperature difference is compared with a second temperature difference threshold smaller than the first temperature difference threshold (step 403). If the temperature difference is larger than the second temperature difference threshold value, the temperature difference is substituted into a function f1 that changes monotonously and continuously in a range from 0 to 1 according to the temperature difference, and the temperature difference membership value is set. If the temperature difference is smaller than the second temperature difference threshold (step 404), the third temperature difference threshold smaller than the second temperature difference threshold is compared with the temperature difference (step 405), and the temperature difference is set to the second temperature difference threshold. 3 If the difference is larger than the temperature difference threshold, Set Bashippu value to 1 (step 406), when the temperature difference is smaller than the third temperature difference threshold, it compares the temperature difference and the third temperature difference threshold smaller than the fourth temperature difference threshold (Step 4
07) If the temperature difference is larger than the fourth temperature difference threshold, the temperature difference is substituted into a function f2 that changes monotonously and continuously in the range from 1 to 0 according to the temperature difference, and the temperature difference membership is obtained. A value is set (step 408), and if the temperature difference is smaller than the fourth temperature difference threshold, the temperature difference membership value is set to 0 (step 402). Then, the product of the load-side refrigerant transfer amount and the temperature difference membership value by the first refrigerant transfer pump controller 22 and the load-side refrigerant transfer amount by the second refrigerant transfer pump controller 23 and the temperature difference membership value from 1 The load-side refrigerant transfer amount is determined as the sum of the product amount with the value obtained by subtracting the value, and the refrigerant transfer pump 6 is controlled (step 40).
9) It is executed at regular time intervals.

That is, the range from the fourth temperature difference threshold to the first temperature difference threshold corresponds to the first range of the present invention, and the range from the third temperature difference threshold to the second temperature difference threshold is This corresponds to the second range of the invention.

When the cooling operation is performed by the load side heat exchanger 8, if it is determined in step 401 that the temperature difference is larger than the first temperature difference threshold value, as shown in FIG. The load-side refrigerant transfer amount is too small, the efficiency of heat exchange between the first auxiliary heat exchanger 4 and the second auxiliary heat exchanger 7 is low, and the second auxiliary heat exchanger 7 outlet side (low temperature side) In order to perform heat exchange with the first auxiliary heat exchanger 4,
Since the temperature of the auxiliary heat exchanger 4 has to be lowered, the efficiency of the heat source side cycle is reduced. Alternatively, when it is determined in step 407 that the temperature difference is smaller than the fourth temperature difference threshold value, the load-side refrigerant transfer amount in the refrigerant transfer pump 6 is excessive, that is, the operation state is such that the efficiency of the refrigerant transfer pump 6 is low. At 409, the load-side refrigerant transfer amount by the second refrigerant transfer pump controller 23 is given top priority. That is, the second auxiliary heat exchanger temperature difference calculator 21
When it is determined in step 401 that the temperature difference calculated in step 401 is larger than the first temperature difference threshold, the load-side refrigerant transfer amount of the refrigerant transfer pump 6 is increased to reduce the second auxiliary heat exchanger temperature difference, and In a state where the efficiency of heat exchange between the auxiliary heat exchanger 4 and the second auxiliary heat exchanger 7 is high, the cycle efficiency on the heat source side is shifted to a high state, or it is determined that the temperature difference is smaller than the fourth temperature difference threshold value in step 407. When this is done, the load-side refrigerant transfer amount of the refrigerant transfer pump 6 can be reduced, and the operation of the refrigerant transfer pump 6 can be shifted to a highly efficient operation state.

The temperature difference calculated by the second auxiliary heat exchanger temperature difference calculator 21 is determined in step 403 to be smaller than the second temperature difference threshold, and in step 405 to be larger than the third temperature difference threshold. The load-side refrigerant transfer amount in the refrigerant transfer pump 6 is substantially appropriate, the heat exchange efficiency between the first auxiliary heat exchanger 4 and the second auxiliary heat exchanger 7 is high, and the heat source side Since the efficiency of the cycle is high and the operation state of the refrigerant transfer pump 6 is high,
In step 409, the load-side refrigerant transfer amount by the first refrigerant transfer pump controller 22 is given top priority. That is, when the load state (for example, room temperature) detected by the load detector 10 is higher than the target load state (for example, the set temperature), the first refrigerant transfer pump controller 22 increases the load-side refrigerant transfer amount of the refrigerant transfer pump 6. Determine the direction. As a result, the flow rate of the load-side refrigerant flowing in the second auxiliary heat exchanger 7 increases, the amount of cooling from the first auxiliary heat exchanger 4 to the second auxiliary heat exchanger 7 increases, and the load-side heat exchanger 8, the load cooling amount increases, and the load state (for example, room temperature) is changed to the target load state (for example, set temperature).
Can be matched. Alternatively, when the load state (for example, room temperature) detected by the load detector 10 is lower than the target load state (for example, set temperature), the first refrigerant transfer pump controller 22 decreases the load-side refrigerant transfer amount of the refrigerant transfer pump 6. Determine the direction. As a result, the flow rate of the load-side refrigerant flowing through the second auxiliary heat exchanger 4 decreases, the amount of cooling from the first auxiliary heat exchanger 4 to the second auxiliary heat exchanger 7 decreases, and the load-side heat exchanger 8, the load cooling amount is reduced, and the load state (for example, room temperature) can be matched with the target load state (for example, set temperature).

In step 403, it is determined that the temperature difference calculated by the second auxiliary heat exchanger temperature difference calculator 21 is larger than the second temperature difference threshold, or it is determined in step 407 that it is larger than the fourth temperature difference threshold. In this case, the efficiency of the heat exchange between the first auxiliary heat exchanger 4 and the second auxiliary heat exchanger 7 is slightly lower, or the operation of the refrigerant transfer pump 6 is slightly lower. Then, since the load-side refrigerant transfer amount by the first refrigerant transfer pump controller 22 and the load-side refrigerant transfer amount by the second refrigerant transfer pump controller 23 are mixed to control the refrigerant transfer pump 6, the first auxiliary heat exchange A load state (for example, room temperature) is set while shifting to a state in which the heat exchange between the heat exchanger 4 and the second auxiliary heat exchanger 7 is highly efficient, or shifting to a highly efficient operation state of the refrigerant transfer pump 6. It can be matched to a load state (e.g., the set temperature).

As described above, the first refrigerant transfer pump controller 22, the second refrigerant transfer pump controller 23, and the third refrigerant transfer pump controller 24 increase the efficiency of heat exchange of the second auxiliary heat exchanger 7. The load state can be matched with the target load state while maintaining the state and the operation state of the refrigerant transport pump 6 with high efficiency (that is, the operation state of the refrigeration cycle device with high efficiency).

When the heating operation is performed in the load side heat exchanger 8, the first refrigerant transfer pump controller 2
2. The second refrigerant transfer pump controller 23 and the third refrigerant transfer pump controller 24 control the second auxiliary heat exchanger 7 in a state in which the heat exchange efficiency is high and the refrigerant transfer pump 6 in an efficient operation state (ie, refrigeration). Highly efficient operation of cycle equipment)
Can be made to match the load state with the target load state.

As shown in FIG. 2, the second auxiliary heat exchanger inlet-side temperature detector 19 is located near the second auxiliary heat exchanger inlet, and the second auxiliary heat exchanger outlet-side temperature detector 20 is connected to the second auxiliary heat exchanger. Although it has been described that they are arranged in the vicinity of the outlet of the heat exchanger 7, the present invention is not limited to this, and the second auxiliary heat exchanger inlet-side temperature detector 19 is connected to the second auxiliary heat exchanger 8 through the outlet of the load-side heat exchanger 8. The second auxiliary heat exchanger outlet side temperature detector 20 detects the temperature in the path from the second auxiliary heat exchanger 7 to the load side heat exchanger 8 in the path from the second auxiliary heat exchanger 7 to the load side heat exchanger 8. Even if the temperature is detected, the temperature difference is substantially equal to the temperature difference near the inlet and the outlet near the second auxiliary heat exchanger 7,
The above effects can be obtained.

In the control procedure of each controller shown in FIGS. 3 to 6, it has been described that common functions f1 and f2 are used for each controller. However, the present invention is not limited to this. May be used. In short, the control of the present invention in which the refrigerant state quantity is the control amount and the control of the present invention in which the load state quantity is the control amount are performed by weighting each of them according to the refrigerant state quantity. I just need.

In the present embodiment, the pressure of the heat source side refrigerant at a predetermined position between the decompressor on the side including the first auxiliary heat exchanger and the compressor, the first auxiliary heat exchanger outlet or The degree of superheat or supercooling of the heat source side refrigerant at the heat source side heat exchanger outlet, the temperature difference of the load side refrigerant between the inlet side and the outlet side of the second auxiliary heat exchanger, and the refrigerant state quantity of the present invention, respectively. As described above, the control means of the present invention is provided for each refrigerant state quantity, but the present invention is not limited to this. For example, for any one of the refrigerant state quantities, or for two To provide a refrigeration cycle apparatus of a secondary refrigerant system type capable of improving efficiency and / or suppressing cost increase as compared with a conventional refrigeration cycle apparatus of a secondary refrigerant system, even if each of them has the control means of the present invention. Can .

Also, from the refrigeration cycle apparatus according to the present embodiment, the load detector 10, the pressure detector 11, the first compressor controller 12, the second compressor controller 13, the third compressor controller 14, Degree / subcooling degree detector 15, first pressure reducer controller 16, second pressure reducer controller 17, third pressure reducer controller 1
8, the function of each of the first refrigerant transfer pump controller 22 and the third refrigerant transfer pump controller 24 is omitted, and the second refrigerant transfer pump controller 23 directly controls the refrigerant transfer pump 6, Thus, a refrigeration cycle apparatus of the secondary refrigerant system type which can improve efficiency as compared with the refrigeration cycle apparatus of the secondary refrigerant system type can be provided.

In the first and second embodiments described above, propane is taken as an example of the heat source side refrigerant sealed in the heat source side cycle, and the ozone destruction ability and the global warming ability of the refrigerant itself are almost zero. However, it has been described that a highly efficient refrigeration cycle device can be realized. However, the present invention is not limited to this. For example, flammable or toxic substances (for example, other hydrocarbons (particularly hydrocarbons having 2 to 4 carbon atoms) Refrigeration cycle device in which a refrigerant mainly composed of (a) and ammonia) is sealed as a heat source side refrigerant in the heat source side cycle, and a high efficiency refrigeration cycle device can be realized while maintaining safety in the load side cycle. Is clear. In addition, carbon dioxide is generally non-toxic, but the operating pressure is high, so the same effect can be achieved in a refrigeration cycle device in which only the heat source side cycle is sealed as a heat source side refrigerant with emphasis on safety. It is obtained.

In the above-described first and second embodiments, the configuration in which only one load-side heat exchanger is used has been described. However, the present invention is not limited to this. For example, FIG. 1 or FIG. , Instead of the load side heat exchanger 8,
In a refrigeration cycle apparatus having a configuration in which a plurality of load-side heat exchangers are connected in parallel, the same effect as in the first and second embodiments can be obtained.

[0073]

As is apparent from the above description, the present invention can provide a refrigeration cycle apparatus of a secondary refrigerant system type capable of improving efficiency and / or suppressing cost increase.

That is, the present invention of claims 1 to 3
It is possible to provide a refrigeration cycle device of a secondary refrigerant system type capable of improving the heat exchange efficiency in the auxiliary heat exchanger and the second auxiliary heat exchanger.

Further, according to the third aspect of the present invention, in addition to the above effects, the efficiency of heat exchange in the load side heat exchanger can be improved.
A refrigeration cycle device of the secondary refrigerant system type can be provided.

According to the present invention, the operation of the compressor is controlled and / or the operation of the pressure reducer is controlled, and / or the operation of the refrigerant conveying means is controlled. By doing so, it is possible to provide a refrigeration cycle device of the secondary refrigerant system type capable of improving the efficiency of the entire refrigeration cycle device. Here, the reason that the efficiency can be improved by controlling the operation of the compressor is that the load state (for example, room temperature) is reduced while keeping the pressure within the normal use range of the compressor or shifting to a state of high efficiency. This is because it can be made to match the target load state (for example, the set temperature). The reason that the efficiency can be improved by controlling the operation of the pressure reducer is that the load state is maintained while maintaining the high heat exchange efficiency of the first auxiliary heat exchanger (that is, the high efficiency operation of the refrigeration cycle device). This is because the target load state can be matched. The efficiency can be improved by controlling the operation of the refrigerant transfer means because the second auxiliary heat exchanger has a high heat exchange efficiency or the refrigerant transfer pump has a high efficiency operation state (that is, the efficiency of the refrigeration cycle device is low). This is because the load state can be made to match the target load state while maintaining the high operation state).

Further, in addition to the above effects, the present invention of claim 6 can improve the efficiency by controlling the operation of the decompressor even when it is difficult to detect the degree of superheat at the heat source side heat exchanger outlet. A refrigeration cycle device of the secondary refrigerant system type can be provided.

The present invention according to claim 8 can provide a refrigeration cycle apparatus of the secondary refrigerant system type which can improve the efficiency of the entire refrigeration cycle apparatus by controlling the operation of the refrigerant conveying means. Here, the efficiency can be improved by controlling the operation of the refrigerant conveying means,
This is because it is possible to maintain a state in which the second auxiliary heat exchanger has a high heat exchange efficiency and an operation state in which the refrigerant transfer pump has a high efficiency (that is, an operation state in which the refrigeration cycle device has a high efficiency).

Further, the present invention of claim 9 provides the invention according to claims 1 to 8
In addition to the effects of the present invention, the use conditions of the refrigerant conveying means are not strict, and special materials and configurations are not required. Therefore, it is possible to provide a refrigeration cycle apparatus of a secondary refrigerant system type capable of suppressing cost increase.

The tenth aspect of the present invention relates to the first to fifth aspects.
9 In addition to the effects of the present invention, the impact on the global environment is small,
It is possible to provide a refrigeration cycle device of a secondary refrigerant system type capable of maintaining safety in a load side cycle.

[Brief description of the drawings]

FIG. 1 is a schematic configuration diagram illustrating a refrigeration cycle device according to a first embodiment of the present invention.

FIG. 2 is a schematic configuration diagram illustrating a refrigeration cycle device according to a second embodiment of the present invention.

FIG. 3 is a flowchart showing a control procedure performed by control means (a third compressor controller 14) according to a second embodiment of the present invention.

FIG. 4 is a flowchart showing a control procedure performed by a control unit (third pressure reducer controller 18) according to the second embodiment of the present invention in a case where a cooling operation is performed in the load side heat exchanger 8; It is.

FIG. 5 is a flowchart showing a control procedure performed by the control means (third pressure reducer controller 18) in the second embodiment of the present invention in the case where the heating operation is performed in the load side heat exchanger 8; It is.

FIG. 6 is a flowchart illustrating a control procedure performed by a control unit (a third refrigerant transport pump controller 24) according to the second embodiment of the present invention.

FIG. 7 is a schematic diagram illustrating a refrigerant transfer amount, a refrigerant transfer pump efficiency, and a second auxiliary heat exchanger temperature difference.

[Explanation of symbols]

 REFERENCE SIGNS LIST 1 compressor 2 heat source side heat exchanger 3 decompressor 4 first auxiliary heat exchanger 5 four-way valve 6 refrigerant transport pump 7 second auxiliary heat exchanger 8 load side heat exchanger 9 four-way valve 10 load detector 11 pressure detector 12 First compressor controller 13 Second compressor controller 14 Third compressor controller 15 Superheat / subcool degree detector 16 First decompressor controller 17 Second decompressor controller 18 Third decompressor control Device 19 Second auxiliary heat exchanger inlet side temperature detector 20 Second auxiliary heat exchanger outlet side temperature detector 21 Second auxiliary heat exchanger temperature difference calculator 22 First refrigerant transport pump controller 23 Second refrigerant transport pump Controller 24 Third refrigerant transfer pump controller A Heat source side cycle B Load side cycle

 ──────────────────────────────────────────────────続 き Continued on the front page (72) Inventor Noriho Okaza 1006 Kazuma Kadoma, Osaka Prefecture Inside Matsushita Electric Industrial Co., Ltd. F term (reference) 3L092 AA02 AA14 BA06 BA26 DA19 EA02 EA04 EA06 EA20 FA03 FA13 FA22 FA26

Claims (10)

[Claims] 1. A heat source side cycle having at least a compressor, a heat source side heat exchanger, a decompressor and a first auxiliary heat exchanger, and at least a refrigerant conveying means, a load side heat exchanger and a second auxiliary heat exchanger. A refrigeration cycle apparatus comprising: a load-side cycle, wherein the first auxiliary heat exchanger and the second auxiliary heat exchanger perform heat exchange between a heat-source-side refrigerant and a load-side refrigerant. At least the heat source side heat exchanger,
Heat-source-side flow switching means for switching a flow direction of the heat-source-side refrigerant in the decompressor and the first auxiliary heat exchanger; and a load side for switching a flow direction of the load-side refrigerant in the second auxiliary heat exchanger. Flow path switching means, wherein the load side flow path switching means is more efficient in heat exchange in the first auxiliary heat exchanger and the second auxiliary heat exchanger according to the state of the heat source side cycle. As is done in
A refrigeration cycle apparatus wherein the flow direction of the load-side refrigerant is selected and switched. 2. The load-side flow switching means, wherein the heat-source-side refrigerant and the load-side refrigerant flow at least in whole or in part on a path in which the heat exchange is performed, in such a direction as to face each other. The refrigeration cycle apparatus according to claim 1, wherein the flow direction is selected and switched. 3. The load-side heat exchanger is configured such that the load-side refrigerant flows in a direction facing a load target, and the load-side heat exchange is performed by switching of the load-side flow switching unit. 3. The refrigeration cycle apparatus according to claim 1, wherein the flow direction of the load-side refrigerant in the vessel does not change. 4. A heat source side cycle having at least a compressor, a heat source side heat exchanger, a decompressor and a first auxiliary heat exchanger, and at least a refrigerant conveying means, a load side heat exchanger and a second auxiliary heat exchanger. A refrigeration cycle apparatus including a load-side cycle, wherein the first auxiliary heat exchanger and the second auxiliary heat exchanger perform heat exchange between a heat source-side refrigerant and a load-side refrigerant. A load state quantity detecting means for detecting a load state quantity in the exchanger; a refrigerant state quantity detecting means for detecting a state quantity of the heat source side refrigerant and / or a state quantity of the load side refrigerant as a refrigerant state quantity; Control means for controlling the operation of the compressor and / or the operation of the pressure reducer and / or the operation of the refrigerant conveying means, using the state quantity and the refrigerant state quantity as control amounts, wherein the control means Depending on the refrigerant state quantity, the refrigeration cycle apparatus characterized by determining how to handle as the control amount of the load state quantity and the refrigerant state quantity. 5. The refrigerant state quantity may be a pressure of the heat-source-side refrigerant at a predetermined position between the pressure reducer on a side including the first auxiliary heat exchanger and the compressor, and / or A degree of superheating or supercooling of the heat source side refrigerant at a first auxiliary heat exchanger outlet or the heat source side heat exchanger outlet, and / or
Or the temperature difference of the load side refrigerant between the inlet side and the outlet side of the second auxiliary heat exchanger, and when the control means controls the operation of the compressor, the load state amount and the heat source When the pressure of the side refrigerant is the control amount, and the control means controls the operation of the pressure reducer, the load state amount, and the degree of superheat or the degree of supercooling of the heat source side refrigerant are controlled by the control. The refrigeration according to claim 4, wherein, when the control unit controls the operation of the refrigerant transport unit, the load state amount and the temperature difference of the load-side refrigerant are set as the control amount. Cycle equipment. 6. The refrigerant state quantity detecting means according to claim 5, wherein the degree of superheat of the heat source side refrigerant is detected by measuring a degree of superheat on a discharge side of the compressor. Refrigeration cycle equipment. 7. The control unit, when the refrigerant state quantity is not within a predetermined first range, prior to the load state quantity, such that the refrigerant state quantity falls within the first range. When the refrigerant state quantity is within a second range including the first range, control is performed such that the load state quantity falls within a predetermined load range in preference to the refrigerant state quantity. Performing, when the refrigerant state quantity is within the first range and not within the second range, control that sets the refrigerant state quantity as a control amount and control that sets the load state amount as a control amount The refrigerating cycle apparatus according to any one of claims 4 to 6, wherein the weighting is performed in accordance with the refrigerant state quantity. 8. A heat source side cycle having at least a compressor, a heat source side heat exchanger, a decompressor and a first auxiliary heat exchanger, and at least a refrigerant conveying means, a load side heat exchanger and a second auxiliary heat exchanger. A refrigeration cycle apparatus including a load-side cycle, wherein the first auxiliary heat exchanger and the second auxiliary heat exchanger perform heat exchange between a heat source-side refrigerant and a load-side refrigerant. A refrigerant state quantity detecting unit that detects a temperature difference of the load side refrigerant between an inlet side and an outlet side of a heat exchanger; and a control unit that controls operation of the refrigerant conveying unit using the temperature difference as a control amount. A refrigeration cycle device characterized by the above-mentioned. 9. The refrigeration cycle apparatus according to claim 1, wherein the refrigerant transfer means is disposed on a path on an outlet side of the load side heat exchanger. 10. The refrigeration cycle apparatus according to claim 1, wherein the heat-source-side refrigerant is mainly composed of a flammable or toxic refrigerant.