JP3300197B2 - Compression heat pump - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a compression heat pump, and more particularly to a two-stage heat exchanger in which first and second heat collecting heat exchangers for heating a flowing refrigerant by separate heat collecting sources are connected in series as evaporators. First and second compression heat pumps as heat sources and first and second cooling units for cooling the flowing refrigerant by individual heat radiation sources as condensers.
Compression heat pump of the two heat radiation sources connected in series with the heat radiation heat exchangers, and the first and second heat source heat exchangers for heating or cooling the flowing refrigerant by individual heat radiation sources are connected in series, The refrigerant is circulated in the order of a compressor-output heat exchanger-expansion means-first and second heat source heat exchangers in order to make the output heat exchanger function as a condenser, and heat the first and second heat source heat exchangers. A heat collection operation that makes the exchanger function as an evaporator as a heat collection heat exchanger;
The refrigerant is circulated in the order of the compressor, the series combination of the first and second heat source heat exchangers, the expansion means, and the output heat exchanger, so that the output heat exchanger functions as an evaporator, and the first and second heat source heats are emitted. The present invention relates to a compression heat pump of a two-source heat radiation source for switching an operation state and a heat radiation operation in which an exchanger functions as a condenser as a heat radiation heat exchanger.

[0002]

2. Description of the Related Art Conventionally, in a compression heat pump of this type connected in series, as shown in FIG. 8, a refrigerant to be evaporated having passed through an expansion means 4 flows in series (flow indicated by a solid arrow). The first and second heat sampling heat exchangers Ne1, Ne2,
Also, for each of the first and second radiating heat exchangers Nc1 and Nc2 that flow the refrigerant to be condensed discharged from the compressor 3 in series (the flow indicated by the dashed arrow), these heat exchangers are connected in series. (That is, a series set of Ne1 and Ne2 or a series set of Nc1 and Nc2) is simply interposed and connected in the circulation path of the refrigerant, and the first and second heat extraction heat exchangers are used. The order of serial flow of the refrigerant to Ne1 and Ne2, and the first and second radiating heat exchangers Nc1 and Nc
The order of the serial refrigerant flow for each of the two was fixed.

[0003] G1 and G2 are individual heat sources for the first and second heat exchangers Ne1 and Ne2, respectively, or individual heat sources for the first and second heat exchangers Nc2 and Nc1. Indicates a heat source.

[0004] In addition, a heat recovery operation in which the first and second heat source heat exchangers function as evaporators Ne1 and Ne2 by performing a reversal operation of the refrigerant circulation direction by a four-way valve or the like,
These first and second heat source heat exchangers are connected to a heat radiation heat exchanger Nc.
In the type in which the operation mode is switched to the heat dissipation operation in which the condenser functions as 1, Nc2 (that is, the type in which the flow indicated by the solid line and the flow indicated by the broken line in FIG. 8 are switched) is accompanied by the reversal of the refrigerant circulation direction. The order of serial flow of the refrigerant to the first and second heat source heat exchangers is reversed between the heat collection operation and the heat dissipation operation, but in the heat collection operation, the order of the refrigerant flow to the first and second heat collection heat exchangers Ne1 and Ne2 is changed. There is no change in that the order of the refrigerant serial flow is fixed, and the order of the refrigerant serial flow to the first and second heat radiation heat exchangers Nc1 and Nc2 is fixed in the heat dissipation operation.

[0005]

However, as a result of the research,
In the conventional compression heat pump in which the order of the refrigerant flowing in series is fixed as described above, the first and second heat collecting heat exchangers N
e1 and Ne2, respectively, the effect of raising the temperature of the refrigerant by the heat sources G1 and G2 (that is, the effect of further raising the temperature of the refrigerant that has become saturated vapor through the evaporation process by heating, in short,
In terms of the effect of obtaining the degree of superheat sh), in the series flow, the refrigerant temperature increasing effect of the used heat collecting source G1 in the heat collecting heat exchanger Ne1 located on the upstream side and the heat collecting heat exchanger located on the downstream side. The evaporating pressure pe and the evaporating temperature te of the refrigerant in the heat pump operation are different depending on the level relationship between the used heat source G2 and the refrigerant temperature increasing effect of Ne2.

If any one of the heat sources G1 and G2 changes state due to various causes (for example, a temperature change or a flow rate change of the heat source), the heat change of the upstream side causes the heat change of the upstream side. The height relationship between the refrigerant temperature increasing effect of the used heat collecting source G1 in the exchanger Ne1 and the refrigerant temperature increasing effect of the used heat collecting source G2 in the downstream heat collecting heat exchanger Ne2 changes, and the evaporation pressure in the heat pump operation changes. It has been found that the pe and the evaporating temperature te change, which may cause a decrease in the coefficient of performance cop due to a decrease in the evaporating pressure pe and the evaporating temperature te.

Similarly, with respect to the heat radiating source, the cooling temperature of the refrigerant by the heat radiating sources G2 and G1 used in each of the first and second heat radiating heat exchangers Nc1 and Nc2 (that is, the refrigerant becomes a saturated liquid through a condensation process). In view of the effect of lowering the temperature of the refrigerant by cooling, that is, the effect of obtaining the degree of supercooling sc), the refrigerant generated by the heat radiation source G2 used in the heat radiation heat exchanger Nc1 located on the upstream side in the serial flow. The condensation pressure pc and the condensation temperature t of the refrigerant in the heat pump operation depend on the height relationship between the temperature lowering effect and the refrigerant temperature lowering effect of the heat radiation source G1 used in the heat radiation heat exchanger Nc2 located on the downstream side.
c will be different.

When any one of the heat sources G2 and G1 undergoes a situation change (for example, a temperature change or a flow rate change of the heat source) due to various causes, the heat radiation heat exchange on the upstream side is caused by the situation change of these heat sources. The relationship between the temperature drop of the refrigerant by the used heat source G2 in the heat exchanger Nc1 and the temperature drop of the refrigerant by the used heat source G1 in the downstream heat exchanger Nc2 changes, and the condensing pressure pc and the condensing temperature in the heat pump operation are changed. It has been found that tc changes, which may cause a decrease in the coefficient of performance cop due to an increase in the condensing pressure pc and the condensing temperature tc.

[0009] In view of the above circumstances, an object of the present invention is to enable the maximum high coefficient of performance operation under the current situation regardless of the change in the situation of each heat collecting source and each heat radiating source. The object is to simplify the improved configuration to achieve the above. An additional object of the present invention is to prevent a decrease in the coefficient of performance due to the deterioration of the condition of one of the heat collection source and the heat radiation source.

[0010]

Means for Solving the Problems [First characteristic configuration] A first characteristic configuration of the present invention (characteristic configuration of the first aspect of the present invention) relates to a compression heat pump, and is used as an evaporator through a separate heat source. In the configuration in which the first and second heat collecting heat exchangers for heating the flowing refrigerant are connected in series, the outlet flow path of the expansion means is connected to one end and the other end of the series set of the first and second heat collecting heat exchangers. A first flow path switching means which is alternatively connected to the first and second heat collecting heat exchangers, and a suction flow path of the compressor which is alternatively connected to one end and the other end of the series set of the first and second heat collecting heat exchangers. Second
Flow-switching means, the first and second heat-collecting heat exchangers, a high-efficiency heat-collecting heat exchanger in which the refrigerant temperature-raising effect by the used heat-collecting source is higher than the other, and Determining means for determining a low-effect heat-exchanger in which the refrigerant temperature raising effect is lower than the other; and, based on the determination result of the determining means, the evaporating refrigerant passing through the expansion means is subjected to the low-temperature heating. from adopting heat exchanger effects as flowing in the order of adoption heat exchanger of the high effect, only setting the control means for controlling switching the first and second channel switching means, said determination hand
Stage determines the low and high effect heat harvesting heat exchangers
At the same time, there is a difference
And determining configuration whether a constant differential above, the control hand
The stage determines the refrigerant of both heat exchangers based on the determination result.
When the difference in the heating effect is equal to or greater than the set difference, the low effect is taken.
As a configuration to stop the supply of heat source to the heat exchanger
There is to be.

[0011] Second characterizing feature] second characterizing feature of the present invention (wherein the configuration of the invention according to claim 2) relates to the compression type heat pump, the cooling of the flowing coolant by a separate radiating sources as a condenser In the configuration in which the first and second radiating heat exchangers are connected in series, the inlet flow path of the expansion means is alternatively connected to one end and the other end of the series combination of the first and second radiating heat exchangers. A first passage switching means, and a second passage for selectively connecting a discharge passage of the compressor to one end and the other end of the series combination of the first and second heat radiation heat exchangers.
And a high-efficiency heat-dissipating heat exchanger in which the used heat-dissipating heat source has a higher temperature-decreasing effect than the other heat-dissipating heat exchanger, and the first and second heat-dissipating heat exchangers. Means for determining a low-efficiency radiating heat exchanger in a state lower than the other, and based on the determination result of the determining means, the condensing target refrigerant discharged from the compressor is replaced with the low-effect radiating heat exchanger. from vessel to turn in flow of radiator heat exchanger of the high effect, only setting the control means for controlling switching the first and second channel switching means, said determination hand
Stage determines the low and high effect radiating heat exchanger
At the same time, there is a difference in the cooling effect of these heat exchangers.
And determining configuration whether a constant differential above, the control hand
Based on the result of this determination, the stage
When the difference in the temperature lowering effect is equal to or greater than the set difference,
As a configuration to stop the supply of heat radiation source to the heat heat exchanger
There is to be.

[0012] Third, wherein Configuration of third characterizing feature of the present invention (wherein the configuration of the invention according to claim 3) relates to the compression type heat pump, the heating or cooling the flowing coolant by a separate Toho heat source The first and second heat source heat exchangers are connected in series, and the refrigerant is compressed by a compressor, an output heat exchanger,
The expansion means and the first and second heat source heat exchangers are circulated in this order to make the output heat exchanger function as a condenser, and the first and second heat source heat exchangers are used for heat exchange. Heating operation to function as an evaporator as a device, the compressor, a series set of the first and second heat source heat exchangers, the expansion means,
Circulating the output heat exchanger in order, causing the output heat exchanger to function as an evaporator, and causing the first and second heat source heat exchangers to function as condenser heat exchangers. The first and second heat source heat exchangers include a circulation direction switching means for switching a state, and a flow path serving as an outlet flow path of the expansion means in the heat collecting operation and serving as an inlet flow path of the expansion means in the heat radiation operation. A first flow path switching means which is alternatively connected to one end and the other end of the series set; a suction flow path of the compressor in a heat collecting operation; and a discharge flow path of the compressor in a heat dissipation operation. A second flow path switching means for selectively connecting a flow path to be connected to one end and the other end of the series combination of the first and second heat source heat exchangers; With respect to the second heat source heat exchanger, the effect of increasing the refrigerant temperature by the used heat radiation source is higher than that of the other. A heat source heat exchanger that becomes a high-efficiency heat-collecting heat exchanger in situations where the heat-source heat exchanger becomes a low-efficiency heat-collecting heat exchanger when the effect of the used heat-collecting and radiating source is lower than the other. And in the heat dissipation operation, the first
And the second heat source heat exchanger, the heat source heat exchanger to be a high-efficiency heat radiation heat exchanger in a situation where the refrigerant cooling effect by the used heat radiation source is higher than the other, and the refrigerant temperature cooling effect by the used heat radiation source is higher than the other. Determination means for determining a heat source heat exchanger to be a low-efficiency heat radiation heat exchanger in a low situation, and based on the determination result of the determination means, in the heat collecting operation, the refrigerant to be evaporated that has passed through the expansion means, Condensate discharged from the compressor so as to flow in order from the heat source heat exchanger that becomes the low-effect heat-exchange heat exchanger to the heat-source heat exchanger that becomes the high-effect heat-exchange heat exchanger, and in the heat dissipation operation. In each of the heat-collecting operation and the heat-dissipation operation, the target refrigerant flows in the order from the heat-source heat exchanger that becomes the low-effect heat-radiation heat exchanger to the heat-source heat exchanger that becomes the high-effect heat-radiation heat exchanger. Switching control of the first and second flow path switching means Setting a control means that only, the determination unit
Is the low- and high-effect heat-exchange heat exchanger
Heat source heat exchanger to be used
The difference in the temperature rise effect of the heat source heat exchanger as a heat exchanger is set.
It is determined whether or not the difference is greater than or equal to, and in the heat dissipation operation,
A heat source heat exchanger that becomes a low-effect and high-effect heat-radiating heat exchanger
The heat source heat as a heat exchanger
Check whether the difference in refrigerant cooling effect of the exchanger is equal to or greater than the set difference.
The control means is configured to make a determination based on the determination result.
Therefore, in the heat recovery operation, the effect of increasing the refrigerant temperature of both heat source heat exchangers is considered.
When the difference is greater than or equal to the set difference, the low-efficiency heat collecting heat exchanger
Supply of the heat radiation source to the heat source heat exchanger
On the other hand, in the heat dissipation operation, there is a difference in the refrigerant cooling effect of both heat source heat exchangers.
When the difference is equal to or larger than the set difference, the low-efficiency heat-radiating heat exchanger is used.
To stop the supply of the heat radiation source to the heat source heat exchanger.
It is in that.

[0013]

[Operation] [Operation of the first characteristic configuration] That is, the refrigerant temperature increasing effect by the heat collecting source used in the upstream heat collecting heat exchanger and the refrigerant temperature increasing by the used heat collecting source in the downstream heat collecting heat exchanger. As a result of studying that the evaporation pressure pe and the evaporation temperature te of the refrigerant in the heat pump operation are different due to the height relationship with the effect, the refrigerant temperature increase effect by the heat source used in the downstream heat extraction heat exchanger is increased. It has been found that when the refrigerant heat-up effect is higher than that of the heat-collecting source used in the heat-collecting heat exchanger on the side, a heat pump operation with a higher evaporation pressure pe and evaporation temperature te is possible as compared to the opposite case.

That is, in the type in which the refrigerant to be evaporated that has passed through the expansion means flows in series to the first and second heat-collecting heat exchangers, a constant evaporation pressure pe is obtained at the downstream heat-collecting heat exchanger. Performing the evaporation of the refrigerant under the evaporation temperature te to reach the saturated vapor of the refrigerant, and subsequently increasing the refrigerant temperature from the evaporation temperature te to obtain the degree of superheat sh. On the other hand, in the upstream heat sampling heat exchanger,
Since the refrigerant is only evaporated to a certain degree of dryness x under the same evaporation pressure pe and evaporation temperature te as that of the downstream heat sampling heat exchanger, such a serial flow type is used. Appropriate degree of superheat for heat pump operation
Is different depending on the refrigerant temperature increasing effect (effect of obtaining the degree of superheat sh) by the heat collecting source used in the downstream heat collecting heat exchanger.

Regarding the downstream heat collecting heat exchanger, in the operation of maintaining the evaporation pressure pe and the evaporation temperature te constant, the refrigerant temperature increasing effect by the heat collecting source used in the downstream heat collecting heat exchanger. In the case where a constant degree of superheat sh is obtained, as is understood from the fact that the obtained superheat degree sh increases as the refrigerant temperature increasing effect increases, the downstream heat sampling heat exchanger The higher the refrigerant temperature raising effect of the heat collection source used, the higher the refrigerant temperature at the outlet of the heat collection heat exchanger (that is, the higher the refrigerant temperature by the degree of superheat sh from the evaporation temperature te (the sensible heat The more the exchange can be performed), the higher the evaporating pressure pe and the evaporating temperature te may be.
From this, when the refrigerant temperature increasing effect by the used heat source in the downstream heat collecting heat exchanger is higher than the refrigerant temperature increasing effect by the used heat collecting source in the upstream heat collecting heat exchanger, the reverse is true. Operation with a higher evaporation pressure pe and higher evaporation temperature te than in the case is possible.

Focusing on this, in the first characteristic configuration of the present invention, in the first and second heat collecting heat exchangers connected in series, the effect of the used heat collecting source on the temperature rise of the refrigerant is higher than the other. High-efficiency heat-exchanging heat exchangers and low-effect heat-exchanging heat exchangers in which the temperature rise effect of the used heat source is lower than the other are determined by an appropriate judgment method by detecting the heat source status. Means, and based on the result of the determination, the control means so that the refrigerant to be evaporated that has passed through the expansion means flows from the low-effect heat-exchange heat exchanger to the high-effect heat-exchange heat exchanger in order. By controlling the first and second flow path switching means to change the refrigerant flow order to the first and second heat collecting heat exchangers, the heat collecting heat exchanger in each heat collecting heat exchanger due to a change in the state of each heat collecting source. Regardless of the change in the refrigerant heating effect, the evaporation pressure pe, the highest possible operation of the evaporation temperature te, namely, to allow the highest possible operation of the coefficient of performance (cop).

On the other hand, the change of the flow order by the first and second flow path switching means is described in the first heat collecting heat exchanger 2A.
Is the above-mentioned high-efficiency heat exchanger (Fig. 2 (b)
, The first flow path switching means K1
Sets the outlet flow passage re of the expansion means 4 to the second heat extraction heat exchanger 2B in the series set of the first and second heat extraction heat exchangers 2A and 2B.
And the second flow path switching means K2 sets the suction flow path rc of the compressor 3 to
A, 2B, a switching state in which the refrigerant is connected to the end on the side of the first heat-exchanging heat exchanger 2A, whereby the refrigerant to be evaporated that has passed through the expansion means 4 is converted to the second heat-exchanging heat exchanger having a low effect. The heat is passed from the heat collecting heat exchanger 2B to the first heat collecting heat exchanger 2A, which is a highly effective heat collecting heat exchanger.

Conversely, when the second heat-exchange heat exchanger 2B is the above-mentioned high-efficiency heat-exchange heat exchanger (see the solid line arrow in FIG. 2A), the first flow path switching means K1 Is in a switching state in which the outlet channel re of the expansion means 4 is connected to the end of the series combination 2A, 2B on the side of the first heat-exchanger 2A, and the second channel switching means K2 is In the switching state, the suction flow passage rc of the heat exchanger 3 is connected to the end of the series combination 2A, 2B on the side of the second heat sampling heat exchanger 2B, whereby the refrigerant to be evaporated passing through the expansion means 4 is reduced. The heat is passed from the first heat-exchanger heat exchanger 2A, which is an effective heat-exchanger heat exchanger, to the second heat-collector heat exchanger 2B, which is a higher-effect heat-exchanger heat exchanger.

Further , as described above, the high-efficiency heat-exchange heat exchanger can be operated at the highest evaporating pressure pe and the highest evaporating temperature te by locating the high-efficiency heat-exchange heat exchanger downstream. If the heat-up effect of the refrigerant by the heat source used in the heat exchanger is too small compared to the heat-up effect by the heat source used in the high-effect heat exchanger, The operating temperature for the refrigerant is lower than the above-mentioned evaporation temperature te (that is, the used heat collecting source acts as a cooling source for the refrigerant to be evaporated), which results in a decrease in the coefficient of performance cop. .

Focusing on this, in the first characteristic configuration of the present invention, it is possible to judge low- and high-efficiency heat-exchanger heat exchangers and to determine the effect of increasing the refrigerant temperature by the heat-collecting source used in these heat-exchanger heat exchangers. The determination means determines whether or not the difference is equal to or greater than the set difference, and based on the determination result, when the difference between the refrigerant temperature increasing effects of the two heat collecting heat exchangers is equal to or greater than the set difference, the control means The supply of the heat source to the low-efficiency heat-exchange heat exchanger is stopped, and the heat pump is operated in a state in which only the high-efficiency heat-exchange heat exchanger functions as an evaporator. Avoid the situation where the heat collecting source used in the heat collecting heat exchanger acts as a cooling source for the refrigerant to be evaporated,
A decrease in the coefficient of performance cop due to the occurrence of such a situation is prevented.

[Operation of the second characteristic configuration] In other words, the degree of the temperature drop of the refrigerant by the heat radiation source used in the upstream heat radiation heat exchanger and the degree of the refrigerant temperature decrease by the heat radiation source used in the downstream heat radiation heat exchanger are high and low. As a result of studying that the condensing pressure pc and the condensing temperature tc of the refrigerant in the heat pump operation are different depending on the relationship, the refrigerant cooling effect by the radiating source used in the radiating heat exchanger on the downstream side is reduced by the radiating heat exchanger on the upstream side. It has been found that when the cooling temperature of the refrigerant is higher than the cooling effect of the heat radiation source used, the operation at a lower condensing pressure pc and lower condensing temperature tc is possible as compared to the opposite case.

That is, in the type in which the refrigerant to be condensed discharged from the compressor flows in series to the first and second radiating heat exchangers, a constant condensing pressure pc and a constant condensing pressure are provided in the downstream radiating heat exchanger. The refrigerant condenses at the temperature tc to reach the saturated liquid, and the condensing temperature t
e to obtain the degree of supercooling sc by lowering the refrigerant temperature, whereas, on the other hand, in the heat radiation heat exchanger on the upstream side,
Under the same condensing pressure pc and condensing temperature tc as the heat radiation heat exchanger on the downstream side, a certain degree of wetness m (= 1−dryness x)
Since only the refrigerant is condensed up to this point, the condensing pressure pc, when obtaining an appropriate degree of supercooling sc in such a series flow heat pump operation,
The condensing temperature tc differs depending on the refrigerant temperature drop effect (effect of obtaining the degree of supercooling sc) by the heat radiation source used in the heat radiation heat exchanger on the downstream side.

In the operation of maintaining the condensing pressure pc and the condensing temperature tc constant, the effect of the heat radiation source used in the downstream heat radiating heat exchanger changes the refrigerant temperature drop effect. In the case where the constant supercooling degree sc is obtained, as can be understood from the fact that the obtained supercooling degree sc increases as the refrigerant temperature drop effect increases,
As the cooling temperature of the refrigerant by the heat radiation source used in the heat radiation heat exchanger on the downstream side is high, the refrigerant temperature at the outlet of the heat radiation heat exchanger can be lowered (that is, the degree of supercooling sc from the condensation temperature tc). The more the refrigerant temperature can be reduced (sensible heat exchange) more efficiently, the lower the condensing pressure pc and the condensing temperature tc may be. Therefore, the refrigerant temperature is reduced by the heat radiation source used in the downstream heat radiation heat exchanger. When the effect is higher than the cooling-down effect of the refrigerant by the heat radiation source used in the heat radiation heat exchanger on the upstream side, the operation in which the condensing pressure pc and the condensing temperature tc are lower than in the opposite case becomes possible.

Focusing on this, in the second characteristic configuration of the present invention, the first and second radiating heat exchangers connected in series have a high cooling effect in which the radiating source used has a higher refrigerant cooling effect than the other. The heat radiating heat exchanger, and a low-efficiency heat radiating heat exchanger in which the refrigerant cooling effect by the used heat radiating source is lower than the other is determined by the determining means using an appropriate determination method such as detection of the heat radiating source status. Then, based on the determination result, the control means controls the first and second flows to flow the refrigerant to be condensed discharged from the compressor in order from the low-efficiency heat radiation heat exchanger to the high-effect heat radiation heat exchanger. By controlling the path switching means to change the refrigerant flow order to the first and second heat radiating heat exchangers, regardless of the change in the refrigerant cooling effect in each heat radiating heat exchanger due to a change in the state of each heat radiating source, Condensation pressure under certain circumstances pc, as low as possible the operation of the condensation temperature tc, i.e., to allow the highest possible operation of the coefficient of performance (cop).

On the other hand, the change of the flow order by the first and second flow path switching means is described in the first heat radiation heat exchanger 2A.
Is the above-mentioned high-efficiency heat-dissipating heat exchanger (Fig. 2 (a)
, The first flow path switching means K1
The first radiating heat exchanger 2A in the series set of the first and second radiating heat exchangers 2A and 2B is connected to the inlet passage re of the expansion means 4.
And the second flow path switching means K2 connects the discharge flow path rc of the compressor 3 to the series set 2
A, 2B, a switching state in which the refrigerant is condensed and connected to the end of the second heat radiation heat exchanger 2B on the side of the second heat radiation heat exchanger 2B. The heat is passed from the exchanger 2B to the first heat radiation heat exchanger 2A, which is a high-efficiency heat radiation heat exchanger, in that order.

Conversely, when the second heat radiation heat exchanger 2B is the above-mentioned high-efficiency heat radiation heat exchanger (see the broken arrow in FIG. 2B), the first flow path switching means K1 The inlet channel re of the expansion means 4 is switched to a state in which it is connected to the end of the series combination 2A, 2B on the side of the second radiating heat exchanger 2B, and the second channel switching means K2 is connected to the compressor 3. The first heat radiation heat exchanger 2 in the series combination 2A, 2B
A switching state is connected to the end on the side of A, whereby the refrigerant to be condensed discharged from the compressor 3 is exchanged with the high-efficiency heat radiation heat from the first heat-radiation heat exchanger 2A, which is a low-effect heat radiation heat exchanger. Flow through the second heat radiation heat exchanger 2B, which is a heat exchanger.

Further , as described above, by locating the high-efficiency radiating heat exchanger on the downstream side to enable the operation of the condensing pressure pc and the condensing temperature tc to be as low as possible, a low-efficiency radiating heat exchanger is required. If the cooling effect of the used heat radiation source is excessively small compared to the cooling effect of the heat radiation source used in the high-efficiency heat radiation heat exchanger, the low-effect heat radiation heat exchanger located on the upstream side will have an effect temperature on the refrigerant. A situation higher than the above-mentioned condensation temperature tc (that is, a situation in which the used heat radiation source acts as a heating source on the contrary to the refrigerant to be condensed) is caused, and this causes a decrease in the coefficient of performance cop.

Focusing on this, in the second characteristic configuration of the present invention, the difference between the cooling effect and the cooling effect of the heat radiating source used in these heat radiating heat exchangers is determined in addition to the judgment of the low and high effect radiating heat exchangers. The determining means determines whether or not the difference is equal to or greater than the set difference, and based on the determination result, when the difference between the refrigerant temperature lowering effects of both the heat radiating heat exchangers is equal to or greater than the set difference, the control means reduces the heat radiation heat of low effect. The heat pump operation is performed in a state where the heat radiation source supply to the heat exchanger is stopped and only the high-efficiency heat radiation heat exchanger is made to function as a condenser, thereby using the heat radiation heat exchanger with a low effect as described above. Avoid situations where the heat radiation source acts as a heating source for the refrigerant to be condensed,
A decrease in the coefficient of performance cop due to the occurrence of such a situation is prevented.

[Operation of Third Characteristic Configuration] In the third characteristic configuration, the first and second heat source heat exchangers function as evaporators as heat-collecting heat exchangers to perform heat-collecting operations on individual heat-collecting / radiating sources. A heat collecting operation in which the output heat exchanger functions as a condenser to heat the object to be heated, and conversely, the first and second heat source heat exchangers function as condenser heat exchangers to individually collect heat. While applying heat radiation to the heat radiation source,
A radiating operation in which the output heat exchanger functions as an evaporator to perform a cooling operation on the object to be cooled is alternatively performed by switching the refrigerant circulation direction.

In the heat collecting operation in which the first and second heat source heat exchangers are used as the heat collecting heat exchangers, similarly to the first characteristic configuration, the refrigerant temperature increasing effect by the used heat collecting and radiating source is higher than that of the other. A heat source heat exchanger that is a high-efficiency heat-collecting heat exchanger in high situations,
The determination means determines the heat source heat exchanger to be a low-effect heat collection heat exchanger in a situation in which the refrigerant temperature increase effect by the used heat collection and release source is lower than the other, using an appropriate determination method by detecting the state of the collection and release heat source. Based on the result of this determination, the refrigerant to be evaporated that has passed through the expansion means is passed in order from the heat source heat exchanger serving as a low-efficiency heat collecting heat exchanger to the heat source heat exchanger serving as a high-effect heat collecting heat exchanger. As described above, the control means controls the first and second flow path switching means to change the refrigerant flow order to the first and second heat source heat exchangers. Irrespective of the change in the effect of increasing the temperature of the refrigerant in the heat source heat exchanger, an operation in which the evaporation pressure pe and the evaporation temperature te are as high as possible, that is, an operation in which the coefficient of performance cop is as high as possible, is possible.

In addition, the first heat source heat exchanger 2A has a high effect for the above-mentioned change of the flow order by the first and second flow path switching means in the heat collecting operation, similarly to the first characteristic configuration. In the case of a heat heat exchanger (see the solid arrow in FIG. 2B), the first flow path switching means K1 sets the flow path re, which is the outlet flow path of the expansion means 4, to the first and second heat source heat sources. Exchanger 2A,
At the end on the side of the second heat source heat exchanger 2B in the series set of 2B, and the second flow path switching means K2, a flow path rc serving as a suction flow path of the compressor 3 is provided in the series set 2A, 2B. First
A switching state is established in which each of the refrigerants is connected to the end on the side of the heat source heat exchanger 2A, whereby the refrigerant to be evaporated that has passed through the expansion means 4 is transferred to the second heat source heat exchanger 2B, which is a low-efficiency heat collecting heat exchanger.
Heat source heat exchanger 2A, which is a highly effective heat collecting heat exchanger
When the second heat source heat exchanger 2B is a high-efficiency heat collecting heat exchanger (see the solid line arrow in FIG. 2A), the first flow path switching means K1 The flow path re, which is the outlet flow path of the expansion means 4, is provided at the end of the series combination 2A, 2B on the side of the first heat source heat exchanger 2A, and the second flow path switching means K2 is In the switching state, the flow path rc serving as the suction flow path is connected to the end of the series combination 2A, 2B on the side of the second heat source heat exchanger 2B, whereby the refrigerant to be evaporated that has passed through the expansion means 4 is The heat is passed from the first heat source heat exchanger 2A, which is a low-effect heat-exchanger, to the second heat-source heat exchanger 2B, which is a high-effect heat-exchanger.

On the other hand, in the heat dissipation operation in which the first and second heat source heat exchangers are used as heat dissipation heat exchangers, as in the case of the above-described second characteristic configuration, the cooling and cooling effect of the used heat dissipation source is higher than the other. The heat source heat exchanger, which is a high-efficiency heat-dissipating heat exchanger, and the heat-source heat exchanger, which is a low-effect heat-dissipating heat exchanger in which the cooling effect of the used heat sink is lower than the other, The determination means is determined by an appropriate determination method based on detection or the like, and based on the determination result, the refrigerant to be condensed discharged from the compressor is changed from the heat source heat exchanger which becomes a low-efficiency heat radiation heat exchanger to a high-effect heat radiation heat exchanger. The first and second flow path switching means are controlled by the control means to change the refrigerant flow order to the first and second heat source heat exchangers so that the heat source heat exchangers flow in order. Depending on each heat source Regardless of changes in the refrigerant temperature lowering effect in the exchanger, the occasional situation in the condensation pressure pc, the lowest possible operation of the condensation temperature tc, i.e., to allow the highest possible operation of the coefficient of performance (cop).

In the heat dissipation operation, the first heat source heat exchanger 2A provides a high-efficiency heat dissipation as in the above-described second characteristic configuration for changing the flow order by the first and second flow path switching means. In the case of a heat exchanger (see the dashed arrow in FIG. 2A), the first flow path switching means K1 sets the flow path re, which is the inlet flow path of the expansion means 4, to the first and second heat source heat exchange. Vessel 2
A, at the end on the side of the first heat source heat exchanger 2A in the series set of A and 2B, and the second flow path switching means K2 connects the flow path rc serving as the discharge flow path of the compressor 3 to the series set 2A, 2B is connected to the end of the second heat source heat exchanger 2B on the side of the second heat source heat exchanger 2B, whereby the refrigerant to be condensed discharged from the compressor 3 is changed to the second heat source heat exchange which is a low-efficiency heat radiation heat exchanger. Vessel 2
B. First heat source heat exchanger 2 which is a high-efficiency heat radiation heat exchanger
When the second heat source heat exchanger 2B is a high-efficiency heat radiation heat exchanger (see the broken arrow in FIG. 2B), the first flow path switching means K1 , Expansion means 4
At the end of the series combination 2A, 2B on the side of the second heat source heat exchanger 2B, and the second flow path switching means K2 is connected to the discharge flow path of the compressor 3. Channel rc
To the first heat source heat exchanger 2A in the series set 2A, 2B.
In a switching state in which each is connected to the end on the side of
The refrigerant to be condensed discharged from the compressor 3 is allowed to flow from the first heat source heat exchanger 2A, which is a low-efficiency heat radiation heat exchanger, to the second heat source heat exchanger 2B, which is a high-effect heat radiation heat exchanger.

When performing the heat collecting operation, the first
As with the characteristic configuration, the heat source heat exchangers that are low-effect and high-effect heat-exchanger heat exchangers are determined, and the refrigerant heat-up effect by the heat-extraction and heat-dissipation sources used in the heat-source heat exchangers as these heat-exchanger heat exchangers The determination means determines whether or not the difference is equal to or greater than the set difference, and, based on the determination result, when the difference in the refrigerant temperature increasing effect of both heat source heat exchangers is equal to or greater than the set difference, the control means The supply of the heat radiation source to the heat source heat exchanger, which is a low-effect heat exchanger, is stopped, and the heat pump operation is performed with only the heat source heat exchanger, which is the high-effect heat exchanger, functioning as an evaporator. By doing so, it is possible to avoid a situation in which the heat collecting and radiating source used in the heat source heat exchanger which is a low-efficiency heat collecting heat exchanger acts as a cooling source for the refrigerant to be evaporated. Prevents the coefficient of performance cop from decreasing.

[0035] Also, in the case of performing the heat operation release the first of the aforementioned
As with the two- characteristic configuration, along with the determination of the heat source heat exchanger to be a low-effect and high-effect heat radiation heat exchanger, the difference in the refrigerant cooling effect by the sampling heat radiation source used in the heat source heat exchanger as the heat radiation heat exchanger is determined. The determination means determines whether or not the difference is equal to or greater than the set difference, and based on the determination result, when the difference in the refrigerant cooling effect between the two heat source heat exchangers is equal to or greater than the set difference, the control means causes the low-efficiency heat radiation. The supply of the heat radiation source to the heat source heat exchanger serving as the heat exchanger is stopped, and the heat pump is operated in a state where only the heat source heat exchanger serving as the high-efficiency heat radiation heat exchanger functions as a condenser. Use the heat source heat exchanger to be an effective heat radiation heat exchanger. Avoid the situation where the heat radiation source acts as a heating source for the refrigerant to be condensed, and reduce the coefficient of performance cop due to the occurrence of such a situation. To prevent.

[0036]

[Effects of the first characteristic configuration] According to the first characteristic configuration of the present invention, the maximum high coefficient of performance operation can be performed at any time regardless of a change in the situation of each heat source, thereby saving energy. Can be effectively achieved, and a high heating capacity can be stably obtained on the condenser side.

In addition, as an improvement to the refrigerant path for obtaining this effect, the connection between the first heat-collecting heat exchanger and the second heat-collecting heat exchanger can be achieved by simply connecting them in series with a connecting pipe. Take the same simple connection form as before,
Further, a first connecting means for selectively connecting the outlet flow path of the expansion means to one end and the other end of the series combination of the first and second heat collecting heat exchangers.
Flow path switching means, and the first and second suction paths of the compressor.
As the second flow path switching means that is selectively connected to one end and the other end in the series set of the heat collecting heat exchangers, one three-way valve and two two-way valves that can be bidirectional are used, respectively. Only a simple passage switching configuration with a small number of valves, such as a single passage, can be used. For example, a passage switching configuration using a total of four three-way valves Va as shown in FIG. 9 or a total of six passages as shown in FIG. Two-way valve V
As compared with the case where the flow path switching configuration using the b is adopted and the flow order of the refrigerant to be evaporated to the first and second heat sampling heat exchangers 2A and 2B can be changed, the improvement of the refrigerant path is simple and the device is manufactured. Can be facilitated and the apparatus cost can be reduced.

[0038] And also, according to the first characterizing feature of the present invention, to being able to prevent a decrease in coefficient of performance caused by difference of the refrigerant Atsushi Nobori effect of the first and second adopts heat exchanger becomes excessively large good is, the improvement of growth績係number can be more effectively achieved.

Further, when the difference in the effect of raising the temperature of the refrigerant between the first and second heat-collecting heat exchangers is equal to or greater than the set difference, the low-effect heat-collecting heat exchanger is stopped. Since the heat source supply to the exchanger is stopped and the function of the low-efficiency heat-exchange heat exchanger is stopped, for example, by diverting the refrigerant to be evaporated to the low-effect heat-exchange heat exchanger, the low-efficiency heat-exchange heat exchanger is less effective. adopted compared with the form in which stall the heat exchanger, can the switching valve of the coolant channel and the bypass for bypassing unnecessary, to
However, the configuration of the refrigerant path can be simplified.

[Effects of Second Characteristic Configuration] According to the second characteristic configuration of the present invention, the maximum high coefficient of operation can be performed at any time regardless of a change in the situation of each heat radiation source, thereby saving energy. And a high cooling capacity can be stably obtained on the evaporator side.

Further, as an improvement to the refrigerant path for obtaining this effect, the connection between the first heat radiation heat exchanger and the second heat radiation heat exchanger is the same as the conventional method in which both are simply connected in series by a connecting pipe. Take the same simple connection form as
Also, a first connecting means for selectively connecting the inlet flow path of the expansion means to one end and the other end of the series combination of the first and second radiating heat exchangers.
Flow path switching means, and the first and second discharge paths of the compressor.
As for the second flow path switching means which is selectively connected to one end and the other end in the series set of the heat radiating heat exchangers, only one three-way valve or two two-way valves capable of bidirectional use are used, respectively. And the like, a simple flow path switching configuration with a small number of valves can be used. Therefore, a flow path switching configuration using four three-way valves Va as shown in FIG. 9 described above, or a six-way switching configuration as shown in FIG. As compared with the case where the flow path switching configuration using the valve Vb is adopted and the flow order of the refrigerant to be condensed to the first and second radiating heat exchangers 2A and 2B can be changed, the improvement of the refrigerant path is simple and the device is manufactured. Can be facilitated and the apparatus cost can be reduced.

[0042] And also, according to the second characterizing feature of the present invention, Ri by the ability to prevent a decrease in coefficient of performance caused by difference of the refrigerant temperature decreasing effect of the first and second heat radiating heat exchanger is excessively large , it is possible to achieve improved growth績係number more effectively.

Further, when the difference between the refrigerant temperature lowering effects of the first and second heat radiating heat exchangers is equal to or larger than the set difference, the function of the low effect heat radiating heat exchanger is stopped. Since the heat source supply is stopped and the low-efficiency heat-dissipation heat exchanger is stopped, the low-efficiency heat-dissipation heat exchanger functions, for example, by diverting the refrigerant to be condensed to the low-effect heat-dissipation heat exchanger. Compared with the stop mode, the refrigerant flow path for bypass and the switching valve for bypass can be dispensed with.
However, the configuration of the refrigerant path can be simplified.

[Effect of Third Characteristic Configuration] According to the third characteristic configuration of the present invention, the heat collecting operation using the first and second heat source heat exchangers as the heat collecting heat exchangers, In the one that switches between the heat-dissipation operation and the heat-dissipation operation using the heat-source heat exchanger as the heat-dissipation heat exchanger, the heat-dissipation operation and the heat-dissipation operation are performed regardless of the status change of each heat-dissipation and heat-dissipation source Occasionally, the maximum high coefficient of performance operation can be performed, whereby energy saving can be effectively achieved, and a high cooling capacity and a high heating capacity can be stably obtained on the output side.

As an improvement to the refrigerant path for obtaining this effect, the refrigerant circulation direction is switched only by adopting the same switching configuration as in the prior art such as using a four-way valve. The connection between the heat exchanger and the second heat source heat exchanger also employs a simple connection form similar to the conventional one in which both are simply connected in series by a connection pipe.
As in the above-described first and third characteristic configurations, the first and second flow path switching means are valves that only use one three-way valve or two two-way valves that can be bidirectional, respectively. It is possible to use only a small number of simple flow path switching configurations, thereby providing a flow path switching configuration using four three-way valves Va as shown in FIG. 9 described above or a six-way switching configuration as shown in FIG. Way valve V
b), the first in the heat recovery operation is adopted.
And a change in the flow sequence of the refrigerant to be evaporated to the second heat source heat exchanger and a change in the flow sequence of the refrigerant to be condensed to the first and second heat source heat exchangers in the heat dissipation operation. Can be easily improved, the manufacturing of the device can be facilitated, and the cost of the device can be reduced.

[0046] And also, according to the third characterizing feature of the present invention, in Tonetsu operation for the heat exchanger adopts the first and second heat source heat exchanger, the first and second heat source heat exchanger In the heat dissipation operation using the first and second heat source heat exchangers as heat dissipation heat exchangers, the first and second heat source heat exchanges are reduced in the coefficient of performance caused by an excessively large difference in the refrigerant temperature increasing effect. the difference of the refrigerant temperature lowering effect of vessel Ri by that it is possible to prevent the respective reduction in the coefficient of performance caused by excessively large, the improvement in growth <br/>績係number can be more effectively achieved.

Further, when the difference between the refrigerant temperature raising effects of the first and second heat source heat exchangers in the heat collecting operation is equal to or larger than the set difference,
And a heat-source heat exchanger that is a low-effect heat-collecting heat exchanger or a low-effect heat-radiation heat exchanger when the difference between the refrigerant cooling effects of the first and second heat-source heat exchangers is greater than or equal to a set difference in the heat-dissipation operation. In stopping the function, the first characteristic configuration and the second
As in the two- character configuration, a mode is adopted in which the function of the heat source heat exchanger is stopped by stopping the supply of the heat radiation source to the heat source heat exchanger serving as a low-effect heat-exchange heat exchanger or a low-effect heat-dissipation heat exchanger. Therefore, by diverting the refrigerant to be evaporated and the refrigerant to be condensed to the heat source heat exchanger, which is a low-effect heat-collecting heat exchanger or a low-effect heat-radiating heat exchanger, compared to shutting down the heat-source heat exchanger In addition, the detour refrigerant flow path and the detour switching valve can be dispensed with, so that the configuration of the refrigerant path can be simplified.

[0048]

DESCRIPTION OF THE PREFERRED EMBODIMENTS In FIG. 1, reference numeral 1 denotes an output heat exchanger used for heating (heating) or cooling (cooling) of an area to be cooled or heated, or heating or cooling an article, and 2A and 2B are connected in series to a first heat exchanger.
And the second heat source heat exchanger, and these output heat exchangers 1
And the heat source heat exchangers 2A and 2B include a compressor 3 and an expansion valve 4.
(Or a capillary tube) to constitute a compression heat pump.

The first heat source heat exchanger 2A is an air / refrigerant heat exchanger using the air G1 supplied by the fan 5 as a heat source or a heat radiating source. The heat collecting and radiating source used in the first heat source heat exchanger 2A is used. For the air G1, the outside air, exhaust air from the area to be cooled or heated, or heated air that has passed through a heating means such as a solar heat collector or cooling air that has passed through a cooling means such as a water spray cooler is applied. it can.

On the other hand, the second heat source heat exchanger 2B
Using the water G2 supplied by the heat source or heat radiation source
Water G2, which is a refrigerant heat exchanger and is a heat radiation source used in the second heat source heat exchanger 2B, includes river water, well water, seawater, sewage, and the like.
Domestic effluent, industrial effluent, or heating water or heating brine that has passed through heating means such as a solar heat collector, cooling water or cooling brine that has passed through cooling means such as a cooling tower, or heat storage means Heat storage water or heat storage brine that stores cold heat can be applied.

Reference numeral 7 denotes a four-way valve as means for switching the direction of circulation of the refrigerant.
The refrigerant is supplied to the compressor 3-output heat exchanger 1-expansion valve 4-first and second heat source heat exchangers 2A and 2A as indicated by solid arrows in the drawing.
In the drawing, the heat collection operation of circulating in the order of the series set of B, and the refrigerant,
As shown by the broken-line arrow, the operation is switched to the heat radiation operation in which the compressor 3-the series combination of the first and second heat source heat exchangers 2A and 2B-the expansion valve 4-the output heat exchanger 1 are circulated in this order.

That is, in the heat collecting operation, the first and second heat source heat exchangers 2A and 2B are made to function as evaporators, and the respective heat collecting and radiating sources G1 and G2 are made to function as heat collecting heat exchangers. The output heat exchanger 1 is made to function as a condenser to heat the object to be heated. On the other hand, in the heat radiation operation, the first and second heat source heat exchangers 2A and 2B are made to function as condensers, and the respective heat collection and radiation sources G1, The output heat exchanger 1 is caused to function as an evaporator while allowing the G2 to perform a heat radiation function as a heat radiation heat exchanger, thereby causing the cooling target to be cooled.

V1 and V2 are two-way valves capable of bidirectional operation. These two-way valves V1 and V2 serve as outlet passages of the expansion valve 4 in the heat collecting operation, and also serve as the outlet flow path of the expansion valve 4 in the heat radiation operation. A first flow path switching means K1 for selectively connecting the flow path re serving as the inlet flow path to one end and the other end of the series combination of the first and second heat source heat exchangers 2A and 2B is provided.

V3 and V4 are also two-way valves capable of bidirectional operation. These two-way valves V3 and V4 serve as suction passages of the compressor 3 in the heat collecting operation, and also serve as the compressor in the heat radiation operation. The flow path rc serving as the discharge flow path of the third and the third flow path
A second flow path switching unit K2 is connected to one end and the other end of the series combination of the heat source heat exchangers 2A and 2B.

In other words, in the heat collecting operation, the refrigerant to be evaporated uses the first and second heat source heat exchangers 2A and 2B as heat collecting heat exchangers.
When the four-way valves V1 to V4 are switched in series, the refrigerant to be evaporated having passed through the expansion valve 4 is passed through the first heat source as shown by the solid arrow in FIG. The flow form in which heat flows from the heat exchanger 2A to the second heat source heat exchanger 2B in order, and the refrigerant to be evaporated that has passed through the expansion valve 4, as shown by the solid arrow in FIG. Switching is performed between the heat exchanger 2B and the first heat source heat exchanger 2A in order.

In the heat radiation operation, when the refrigerant to be condensed flows in series to the first and second heat source heat exchangers 2A and 2B as the heat radiation heat exchangers, these four two-way valves V
By the switching operation of 1 to V4, the refrigerant to be condensed discharged from the compressor 3 flows from the second heat source heat exchanger 2B to the first heat source heat exchanger 2A in the order shown by the broken line arrow in FIG. 2B, the refrigerant to be condensed discharged from the compressor 3 flows in reverse order from the first heat source heat exchanger 2A to the second heat source heat exchanger 2B, as indicated by the dashed arrow in FIG. The flow mode is switched to the flow mode.

On the other hand, 8P is a refrigerant pressure detector for detecting the evaporator outlet pressure pe equal to the evaporation pressure of the refrigerant (that is, the pressure of the low-pressure vapor refrigerant sucked by the compressor 3), and 8T is the refrigerant evaporation temperature te and the overheating. The refrigerant temperature detector 9A detects the evaporator outlet temperature te '(that is, the temperature of the low-pressure vapor refrigerant sucked by the compressor 3), which is equal to the sum of the temperature sh and 9A is a heat radiation source used by the first heat source heat exchanger 2A. The temperature t1 of the air G1
9B is the second heat source heat exchanger 2B
Is a water-side detector for detecting the temperature t2 of water G2 as a heat radiation source. Reference numeral 10 denotes each detector 8P, 8T, 9A, 9B.
Is a controller that controls the operation of the heat pump in accordance with the detection result of the above-mentioned and the heat load of the output heat exchanger 1 detected by an appropriate detecting means.

As a basic control, the controller 10 switches between the heat collecting operation and the heat radiation operation by switching the four-way valve 7 in accordance with the operation mode command, and outputs the heat output in each of the heat collecting operation and the heat radiation operation. The output of the compressor 3 is adjusted according to the heat load of the exchanger 1, and the pressure pe detected by the refrigerant pressure detector 8P and the temperature t detected by the refrigerant temperature detector 8T
The degree of throttle of the expansion valve 4 is adjusted so that the degree of superheat sh calculated from e ′ becomes the target degree of superheat.

The degree of superheat sh is determined by the refrigerant pressure detector 8P.
(Sh = t) between the temperature (evaporation temperature te) of the saturated vapor refrigerant under the detected pressure pe (evaporation pressure) and the temperature te ′ (evaporator outlet temperature) detected by the refrigerant temperature detector 8T.
e'-te).

In addition to the above-described basic control, the controller 10 performs the following in the heat collection operation: “basic start / stop according to the state of the heat source”, “comparison and judgment of the effect of increasing the temperature of the refrigerant”, and “ Control (see the flowchart in FIG. 3) of the “switching of the heat source supply”, and in the heat dissipation operation, “basic start / stop according to the condition of the heat sink”, “comparison and determination of the refrigerant cooling effect”,
Then, each control (see the flowchart of FIG. 4) of “switching between refrigerant flow and heat radiation source supply” is executed.

(Basic Heating Operation) "Basic Start / Stop by Heating Source Status" The first heat source heat exchanger 2 when the set lower limit evaporation pressure and lower limit evaporation temperature are set to the execution evaporation pressure pe and the evaporation temperature te.
Using the arithmetic logic R1 set for the correlation between the refrigerant heating capacity HQ1 of the air heat source G1 at A and the temperature t1 of the air heat source G1, the lower limit evaporation pressure is calculated from the detected temperature t1 of the air-side detector 9A. , The refrigerant heating capacity HQ1 of the air heat source G1 in the first heat source heat exchanger 2A in the current state when the lower limit evaporation temperature is the execution evaporation pressure pe and the evaporation temperature te is calculated.

Similarly, the second case in which the lower limit evaporation pressure and the lower limit evaporation temperature are set to the actual evaporation pressure pe and the evaporation temperature te, respectively.
From the detected temperature t2 of the water-side detector 9B using the arithmetic logic R2 set for the correlation between the refrigerant heating capacity HQ2 of the water heat source G2 in the heat source heat exchanger 2B and the temperature t2 of the water heat source G2. Calculate the refrigerant heating capacity HQ2 of the water heat source G2 in the second heat source heat exchanger 2B in the current case where the lower limit evaporation pressure and the lower limit evaporation temperature are the executed evaporation pressure pe and the evaporation temperature te.

Then, the sum of the calculated refrigerant heating capacities HQ1 and HQ2 by the heat sources G1 and G2, the lower limit evaporation pressure,
The refrigerant heating capacity HQ1, which is calculated by comparing the set required heating capacity HQQ of the first and second heat source heat exchangers 2A and 2B as a whole when the lower limit evaporation temperature is the execution evaporation pressure pe and the evaporation temperature te. When the sum of HQ2 is less than the above set required heating capacity HQQ (HQ1 + HQ2 <HQQ),
The compressor 3 is stopped to stop the heat pump operation. In addition, the sum of the calculated refrigerant heating capacities HQ1 and HQ2 is equal to or greater than the above-described required heating capacity HQQ (HQ1 + HQ2 ≧ HQ).
In the case of Q), the heat pump operation is continuously performed.

[Comparison of Refrigerant Temperature Elevation Effect] Refrigerant temperature increase effects HT1 and HT2 of the heat collection sources G1 and G2 used in each of the heat source heat exchangers 2A and 2B (that is, the refrigerant which has become saturated vapor through the evaporation process). Using the determination logic R3 set for the correlation between the effect of raising the temperature by heating, in other words, the effect of acquiring the superheat degree sh) and the temperatures t1 and t2 of the heat sources G1 and G2. Detector 9
From the detected temperature t1 of A and the detected temperature t2 of the water-side detector 9B, the heat collecting sources G1, G used in each heat source heat exchanger 2A, 2B.
2 is determined.

In the determination of the height relationship, the heat source heat exchanger that is a high-effect heat-exchanger in which the refrigerant temperature-raising effect HT by the used heat-collecting source is higher than the other, A heat source heat exchanger that is a low-effect heat-exchange heat exchanger in which the temperature effect HT is lower than the other is determined, and a refrigerant temperature rise in the heat-source heat exchanger that is the high-effect heat-exchange heat exchanger is determined. The effect (that is, HT1 if HT1> HT2, HT2 if HT1 ≦ HT2) is compared with the set lower limit refrigerant heating effect HTT, and the heat source heat exchanger which is a high-efficiency heat collecting heat exchanger is compared. When the refrigerant heating effect HT1 or HT2 is less than the lower limit refrigerant heating effect HTT (<HTT), the compressor 3 is stopped and the heat pump operation is stopped.

Further, when the refrigerant heating effect HT1 or HT2 in the heat source heat exchanger, which is a high-efficiency heat-exchanging heat exchanger, is greater than or equal to the lower-limit refrigerant heating effect HTT (≧ HTT), the high-efficiency heat-exchanging heat exchange Difference between the refrigerant heating effect HT of the heat source heat exchanger serving as a heat exchanger and the heat source heat exchanger serving as a low-efficiency heat collecting heat exchanger (that is, HT1-HT2, HT1 when HT1> HT2)
If ≦ HT2, it is determined whether or not HT2−HT1) is equal to or greater than the set difference ΔHT.

"Switching of refrigerant flow and supply of heat source" The following switching control a to d is executed in accordance with the result of the above judgment on the refrigerant heating effect HT. a. The first heat source heat exchanger 2A is a high-effect heat collecting heat exchanger, the second heat source heat exchanger 2B is a low-effect heat collecting heat exchanger, and the first and second heat source heat exchangers 2A, 2A, When the difference between the refrigerant heating effects HT of 2B is smaller than the set difference ΔHT (that is, HT1> HT2 and HT1−HT2 <ΔH)
In T), the two-way valves V1 to V4 are switched so that the refrigerant to be evaporated flows in series in the order from the second heat source heat exchanger 2B to the first heat source heat exchanger 2A (that is, FIG.
(B), the air heat source G1 is supplied to the first heat source heat exchanger 2A by the fan 5 and the second heat source heat exchange is performed by the pump 6. In both cases, the supply of the water heat source G2 to the heat exchanger 2B is continuously performed, whereby the first heat source heat exchanger 2A, which is a high-efficiency heat collection heat exchanger, is located in the downstream side in a serial flow state. These first and second heat source heat exchangers 2A, 2B
The heat pump operation which makes both of them effectively function as an evaporator is performed.

FIG. 5A is a pressure p / specific enthalpy h diagram (Mollier diagram) showing the heat pump cycle at this time, and Δx is each heat source heat exchanger 2A, 2B.
Shows the amount of change in the dryness x at the time.

B. The first heat source heat exchanger 2A is a high-effect heat collecting heat exchanger, the second heat source heat exchanger 2B is a low-effect heat collecting heat exchanger, and the first and second heat source heat exchangers 2A are used.
When the difference between the refrigerant heating effects HT of A and 2B is equal to or larger than the set difference ΔHT (that is, HT1> HT2, and HT1-
HT2 ≧ ΔHT), by switching the two-way valves V1 to V4, the flow of the refrigerant to be evaporated flowing in series from the second heat source heat exchanger 2B to the first heat source heat exchanger 2A in the same manner as in the above a. Although a flow mode (that is, a flow mode indicated by a solid line arrow in FIG. 2B) is adopted, the supply of the water heat source G2 to the second heat source heat exchanger 2B by the pump 6 is stopped, and the fan 5 Only the supply of the air heat source G1 to the first heat source heat exchanger 2A is continuously performed, whereby the first heat source heat exchanger 2A, which is a high-efficiency heat collection heat exchanger, is connected in series with the downstream side. In the flowing state, the evaporator function of the upstream second heat source heat exchanger 2B, which is a low-effect heat-exchange heat exchanger, is stopped, and the downstream first heat-source heat exchange, which is a high-effect heat-exchange heat exchanger, A heat pump operation is performed in which only the vessel 2A functions effectively as an evaporator.

C. The second heat source heat exchanger 2B is a high-effect heat collecting heat exchanger, the first heat source heat exchanger 2A is a low-effect heat collecting heat exchanger, and the first and second heat source heat exchangers 2B are used.
When the difference between the refrigerant heating effects HT of A and 2B is smaller than the set difference ΔHT (that is, HT2 ≧ HT1 and HT2-
HT1 <ΔHT), by switching the two-way valves V1 to V4, the first heat source heat exchanger 2A to the second heat source heat exchanger 2B
2 (i.e., the flow indicated by the solid arrows in FIG. 2A), and the air from the fan 5 to the first heat source heat exchanger 2A. Both the supply of the heat source G1 and the supply of the water heat source G2 to the second heat source heat exchanger 2B by the pump 6 are continuously performed, whereby the second heat source heat, which is a high-efficiency heat source heat exchanger, is provided. In a serial flow state in which the exchanger 2B is located on the downstream side, a heat pump operation is performed in which both the first and second heat source heat exchangers 2A and 2B function effectively as evaporators.

FIG. 5B is a pressure p / specific enthalpy h diagram (Mollier diagram) showing the heat pump cycle at this time.

D. The second heat source heat exchanger 2B is a high-effect heat collecting heat exchanger, the first heat source heat exchanger 2A is a low-effect heat collecting heat exchanger, and the first and second heat source heat exchangers 2B are used.
When the difference between the refrigerant heating effects HT of A and 2B is equal to or larger than the set difference ΔHT (that is, HT2 ≧ HT1, and HT2-
HT1 ≧ ΔHT), by switching the two-way valves V1 to V4, the refrigerant to be evaporated is passed in series from the first heat source heat exchanger 2A to the second heat source heat exchanger 2B in the same manner as in c above. Although a flow mode (that is, a flow mode indicated by a solid arrow in FIG. 2A) is adopted, the supply of the air heat source G1 to the first heat source heat exchanger 2A by the fan 5 is stopped, and the pump 6
, The supply of the water heat source G2 to the second heat source heat exchanger 2B is continuously performed, whereby the second heat source heat exchanger 2B, which is a high-efficiency heat collection heat exchanger, is positioned downstream. In the flowing state, the evaporator function of the upstream first heat source heat exchanger 2A, which is a low-effect heat sampling heat exchanger, is stopped, and the downstream second heat source heat, which is a high-effect heat sampling heat exchanger, is stopped. A heat pump operation is performed in which only the exchanger 2B functions effectively as an evaporator.

(Heat-dissipation operation) "Basic start and stop by heat-dissipation source status" The first heat-source heat exchanger 2 when the set upper-limit condensation pressure and upper-limit condensation temperature are the condensing pressure pc and the condensation temperature tc, respectively.
Using the arithmetic logic R4 set for the correlation between the refrigerant cooling capacity LQ1 of the air radiating source G1 at A and the temperature t1 of the air radiating source G1, the upper limit condensation pressure is calculated from the detected temperature t1 of the air-side detector 9A. , The refrigerant cooling capacity LQ1 by the air heat radiation source G1 in the first heat source heat exchanger 2A at the present time when the upper limit condensation temperature is the execution condensation pressure pc and the condensation temperature tc.

Similarly, when the upper limit condensing pressure and the upper limit condensing temperature are the actual condensing pressure pc and the condensing temperature tc, respectively,
From the detected temperature t2 of the water-side detector 9B using the arithmetic logic R5 set for the correlation between the refrigerant cooling capacity LQ2 of the water heat radiator G2 in the heat source heat exchanger 2B and the temperature t2 of the water radiator G2. The refrigerant cooling capacity LQ2 of the water heat radiation source G2 in the second heat source heat exchanger 2B at the present time when the upper limit condensing pressure and the upper limit condensing temperature are the actual condensing pressure pc and the condensing temperature tc is calculated.

Then, the sum of the calculated refrigerant cooling capacities LQ1 and LQ2 by the heat radiation sources G1 and G2, the upper limit condensing pressure,
When the upper limit condensing temperature is the condensing pressure pc and the condensing temperature tc, the required cooling capacity LQQ of the first and second heat source heat exchangers 2A and 2B as a whole is compared, and the calculated refrigerant cooling capacity LQ1, When the sum of LQ2 is less than the required cooling capacity LQQ (LQ1 + LQ2 <LQQ),
The compressor 3 is stopped to stop the heat pump operation. In addition, the sum of the calculated refrigerant cooling capacities LQ1 and LQ2 is equal to or greater than the above-described required cooling capacity LQQ (LQ1 + LQ2 ≧ LQ
In the case of Q), the heat pump operation is continuously performed.

[Comparison of Refrigerant Cooling Effect] Refrigerant cooling effects LT1 and LT2 due to the radiating sources G1 and G2 used in each of the heat source heat exchangers 2A and 2B (that is, cooling the refrigerant which has become a saturated liquid through the condensation process). Using the determination logic R6 set for the correlation between the level of the effect of lowering the temperature, in other words, the effect of obtaining the degree of supercooling sc) and the temperatures t1, t2 of the heat radiation sources G1, G2. 9
From the detected temperature t1 of A and the detected temperature t2 of the water side detector 9B, the heat radiation sources G1, G used in each heat source heat exchanger 2A, 2B.
2 is determined.

In the determination of the height relationship, the heat-source heat exchanger which is a high-efficiency heat-radiating heat exchanger in a situation where the refrigerant heat-radiating effect LT is higher than the other heat-radiating source; Is determined to be a heat-source heat exchanger that is a low-efficiency heat-radiating heat exchanger in a situation lower than that of the other, and the refrigerant cooling effect in the heat-source heat exchanger that is the high-effect heat-radiating heat exchanger (that is, LT1> LT2 for LT2, LT2 for LT1 ≦ LT2) and the set lower-limit refrigerant cooling effect LTT, and the refrigerant cooling effect LT1 or LT2 in the heat source heat exchanger which is a high-efficiency radiating heat exchanger is obtained. If the lower limit refrigerant cooling effect is less than the LTT (<LTT), the compressor 3 is stopped and the heat pump operation is stopped.

Further, when the refrigerant cooling effect LT1 or LT2 in the heat source heat exchanger serving as a high-efficiency heat radiation heat exchanger is equal to or greater than the lower limit refrigerant cooling effect LTT (≧ LTT), the heat source serving as a high-efficiency heat radiation heat exchanger The difference in the refrigerant cooling effect LT between the heat exchanger and the heat source heat exchanger serving as the low-efficiency heat radiation heat exchanger (that is, LT1−LT2, LT1 when LT1> LT2)
If ≤ LT2, it is determined whether or not LT2-LT1) is equal to or larger than the set difference ΔLT.

[Switching of refrigerant flow and supply of heat radiating source] Switching control of the following e to h is executed in accordance with the result of the above judgment on the refrigerant cooling effect LT. e. The first heat source heat exchanger 2A is a high-effect heat radiation heat exchanger, the second heat source heat exchanger 2B is a low-effect heat radiation heat exchanger, and the first and second heat source heat exchangers 2A, 2B When the difference between the refrigerant cooling effects LT is smaller than the set difference ΔLT (that is, LT1> LT2 and LT1−LT2 <ΔL)
In T), the two-way valves V1 to V4 are switched so that the refrigerant to be condensed flows in series in the order from the second heat source heat exchanger 2B to the first heat source heat exchanger 2A (that is, FIG.
(A), the air radiating source G1 is supplied to the first heat source heat exchanger 2A by the fan 5 and the pump 6 is supplied to the second heat source heat exchanger 2B. Both of the supply of the water heat radiation source G2 are continuously performed, whereby the first heat source heat exchanger 2A, which is a high-efficiency heat radiation heat exchanger, is located in the downstream side, and the first and second water heat radiation sources G2 are connected in series. A heat pump operation is performed in which both the two heat source heat exchangers 2A and 2B function effectively as condensers.

FIG. 6A is a pressure p / specific enthalpy h diagram (Mollier diagram) showing the heat pump cycle at this time, and Δm represents each heat source heat exchanger 2A, 2B.
Shows the amount of change in the wetness m (= 1−dryness x) in FIG.

F. The first heat source heat exchanger 2A is a high-effect heat radiation heat exchanger, the second heat source heat exchanger 2B is a low-effect heat radiation heat exchanger, and the first and second heat source heat exchangers 2 are used.
When the difference between the refrigerant cooling effects LT of A and 2B is equal to or greater than the set difference ΔLT (that is, LT1> LT2 and LT1-
In LT2 ≧ ΔLT), by switching the two-way valves V1 to V4, as in the case of e, the refrigerant to be condensed flows in series in the order of the second heat source heat exchanger 2B to the first heat source heat exchanger 2A. Although the flow form (that is, the flow form shown by the broken arrow in FIG. 2A) is adopted, the supply of the water heat radiation source G2 to the second heat source heat exchanger 2B by the pump 6 is stopped, and the fan 5 Only the supply of the air heat radiation source G1 to the first heat source heat exchanger 2A is continuously performed, whereby the first heat source heat exchanger 2A, which is a high-efficiency heat radiation heat exchanger, is positioned on the downstream side. In the state, the condenser function of the upstream second heat source heat exchanger 2B, which is a low-effect heat radiation heat exchanger, is stopped, and only the downstream first heat source heat exchanger 2A, which is a high-effect heat radiation heat exchanger, is stopped. A heat pump operation is performed to effectively function as a condenser.

G. The second heat source heat exchanger 2B is a high-efficiency heat radiation heat exchanger, the first heat source heat exchanger 2A is a low-effect heat radiation heat exchanger, and the first and second heat source heat exchangers 2B are used.
When the difference between the refrigerant cooling effects LT of A and 2B is less than the set difference ΔLT (that is, LT2 ≧ LT1 and LT2-
LT1 <ΔHT), by switching the two-way valves V1 to V4, the first heat source heat exchanger 2A to the second heat source heat exchanger 2B
2 (ie, a flow mode indicated by a broken-line arrow in FIG. 2B), and air is supplied from the fan 5 to the first heat source heat exchanger 2A. Both the supply of the heat radiation source G1 and the supply of the water heat radiation source G2 to the second heat source heat exchanger 2B by the pump 6 are continuously performed, whereby the second heat source heat exchange which is a highly effective heat radiation heat exchanger is performed. In a serial flow state in which the heat exchanger 2B is positioned on the downstream side, a heat pump operation is performed in which both the first and second heat source heat exchangers 2A and 2B function effectively as condensers.

FIG. 6B is a pressure p / specific enthalpy h diagram (Mollier diagram) showing the heat pump cycle at this time.

H. The second heat source heat exchanger 2B is a high-efficiency heat radiation heat exchanger, the first heat source heat exchanger 2A is a low-effect heat radiation heat exchanger, and the first and second heat source heat exchangers 2B are used.
When the difference between the refrigerant cooling effects LT of A and 2B is equal to or larger than the set difference ΔLT (that is, LT2 ≧ LT1 and LT2-
In the case of LT1 ≧ ΔLT), the two-way valves V1 to V4 are switched so that the refrigerant to be condensed flows in series in the order from the first heat source heat exchanger 2A to the second heat source heat exchanger 2B in the same manner as in the above g. Although a flow mode (that is, a flow mode indicated by a dashed arrow in FIG. 2B) is adopted, the supply of the air heat radiation source G1 to the first heat source heat exchanger 2A by the fan 5 is stopped, and the pump 6
Only the supply of the water heat radiating source G2 to the second heat source heat exchanger 2B by the above-described method, whereby the second heat source heat exchanger 2B, which is a high-efficiency heat radiating heat exchanger, is connected in series to the downstream side. In the flowing state, the condenser function of the upstream first heat source heat exchanger 2A, which is a low-efficiency heat radiation heat exchanger, is stopped, and the downstream second heat source heat exchanger 2B, which is a high-effect heat radiation heat exchanger, A heat pump operation is performed to make only the effective function as a condenser.

In summary, in this embodiment, the controller 1
0 is the first and second heat source heat exchangers 2 connected in series for heating or cooling the flowing refrigerant by the individual heat radiation sources G1 and G2.
Regarding A and 2B, in the “heat-collection operation”, the heat-source heat exchanger that becomes a high-effect heat-collection heat exchanger in a situation where the refrigerant temperature-raising effect HT by the used heat-collecting / radiating source is higher than the other is used. In the situation where the refrigerant temperature raising effect HT is lower than the other, the heat source heat exchanger which is a low-effect heat collecting heat exchanger is determined,
It is determined whether or not the difference between the refrigerant heating effects HT1 and HT2 of the heat source heat exchangers 2A and 2B as the heat collecting heat exchangers is equal to or larger than a set difference ΔHT. A heat source heat exchanger that becomes a high-efficiency heat radiation heat exchanger when the refrigerant temperature drop effect LT by the heat source is higher than the other, and a low effect heat radiation heat exchange when the refrigerant temperature drop effect LT that is used by the used heat radiation source is lower than the other. The heat source heat exchanger as the heat source heat exchanger is determined.
The difference between the refrigerant cooling effects LT1 and LT2 of A and 2B is the set difference Δ
The determination means X for determining whether or not the value is LT or more is configured.

The controller 10 constitutes the judgment means X and, based on the judgment result of this judgment means X, operates for the purpose of operating at a high coefficient of performance cop.
Then, the refrigerant to be evaporated that has passed through the expansion valve 4 as the expansion means flows from the heat source heat exchanger serving as a low-efficiency heat-collecting heat exchanger to the heat-source heat exchanger serving as a high-effect heat-collecting heat exchanger. In the “radiation operation”, the refrigerant to be condensed discharged from the compressor 3 is changed from the heat source heat exchanger serving as a low-efficiency heat exchanger to the heat source heat exchanger serving as a high-efficiency heat radiation heat exchanger. The two-way valves V1 to V4 as the first and second flow path switching means K1 and K2 are controlled to be switched in each of the “heating operation” and the “radiation operation” so that the flow is performed in the order of Heat source heat exchanger 2 as heat extraction heat exchanger in "Sampling operation"
When the difference between the refrigerant temperature raising effects HT of A and 2B is equal to or larger than the set difference ΔHT, the supply of the heat radiation source to the heat source heat exchanger serving as the low effect heat collecting heat exchanger (that is, acts as a cooling source). Supply of the heat source which may be stopped), and the two heat source heat exchangers 2 as heat radiation heat exchangers in the “radiation operation”
When the difference between the refrigerant cooling effects LT of A and 2B is equal to or larger than the set difference ΔLT, the supply of the heat radiation source to the heat source heat exchanger which is a low-effect heat radiation heat exchanger (that is, there is a possibility of acting as a heating source). Control means Y for stopping the supply of a certain heat radiation source) is configured.

In the switching control of b in the heat collecting operation, when the supply of the water heat source G2 to the second heat source heat exchanger 2B, which is a low-effect heat collecting heat exchanger, is stopped, the stagnant water sampling is performed. Since the heat source G2 may freeze around the second heat source heat exchanger 2B, the water heat source G2 stagnant from around the second heat source heat exchanger 2B due to the switching control of b.
It is preferable to perform an operation of discharging water (so-called water drainage) or take an antifreezing measure such as adopting brine (antifreeze aqueous solution) for the water heat source G1.

[Another Embodiment] Next, another embodiment will be described. Of the heat collecting operation and the heat radiation operation in the above-described embodiment, the heat radiation operation may not be performed, and only the heat collecting operation with the control shown in the flowchart of FIG. 3 may be performed. In addition, the heating operation was not performed, and FIG.
May be configured to execute only the heat dissipation operation accompanied by the control shown in the flowchart of FIG.

The individual heat collecting sources G1 and G2 used in the first and second heat collecting heat exchangers 2A and 2B may be any of a liquid, a gas and a solid. Or different types. Similarly, the first and second radiating heat exchangers 2
The individual heat radiation sources G1 and G2 used in A and 2B are liquid,
Any of a gas and a solid may be used, and these heat radiating sources may be of the same type or different types.

First and second flow path switching means K1, K2
Is constituted by two two-way valves each capable of two-way operation as shown in the above-described embodiment, but one three-way valve capable of two-way operation as shown in FIGS. Valve V5, V
6 may be used.

The heat collecting source G1 used in the first heat collecting heat exchanger 2A
Temperature relationship between the refrigerant temperature raising effect HT1 and the refrigerant temperature raising effect HT2 by the heat collecting source G2 used in the second heat collecting heat exchanger 2B, as in the above-described embodiment, the detected temperature of each of the heat collecting sources G1 and G2. Instead of making the determination based on t1 and t2, the determination may be made based on a plurality of types of detection state values (for example, temperature t and humidity r or specific enthalpy h) of each of the heat collection sources G1 and G2, or It is also possible to adopt a determination mode in which a determination is made based on one or more types of detection state values of G1 and G2 and the detected flow rates of the heat collecting sources G1 and G2. Similarly, the relationship between the temperature drop of the refrigerant LT1 caused by the used heat radiation source G1 in the first heat radiation heat exchanger 2A and the temperature drop effect of the refrigerant LT2 caused by the heat radiation source G2 used in the second heat radiation heat exchanger 2B is described above. As in the embodiment, the detected temperature t of each heat radiation source G1, G2
1, the heat radiation sources G1,
Judgment is made based on a plurality of detection state values of G2 (for example, temperature t, humidity r, or specific enthalpy h), or one or a plurality of detection state values of each heat radiation source G1, G2 and each heat radiation source A determination form such as a determination based on the detected flow rates of G1 and G2 may be adopted.

In the heat collecting operation, [HT1 ≧ HTT? ], [HT2 ≧ HTT? ]
May be adopted in a control form in which the part is omitted. Similarly,
In the heat dissipation operation, [L in the flowchart of FIG.
T1 ≧ LTT? ], [LT2 ≧ LTT? ] May be adopted.

In the above embodiment, each of the heat radiation sources G1,
The sum of the refrigerant cooling capacities LQ1 and LQ2 of G2 is the first and second.
By setting the operating condition to be equal to or higher than the required cooling capacity LQQ as a whole of the heat source heat exchangers 2A and 2B,
Although an appropriate supercooling degree sc is ensured, the supercooling degree sc is adjusted by adjusting the fan 5 and the pump 6 for the heat radiation source.
In the control that adjusts the supercooling degree to the target supercooling degree, or in the system in which the supercooling degree is increased by heat exchange between the evaporator outlet refrigerant and the refrigerant at the final stage of the condenser passage, the supercooling degree sc is adjusted by adjusting the heat exchange amount. May be controlled to adjust the temperature to the target degree of supercooling.

In the claims, reference numerals are provided for convenience of comparison with the drawings, but the present invention is not limited to the configuration shown in the attached drawings.

[Brief description of the drawings]

FIG. 1 is a diagram showing a device configuration.

FIG. 2 is a diagram showing a mode of switching refrigerant flow.

FIG. 3 is a control flowchart of a heat collection operation.

FIG. 4 is a control flowchart of a heat dissipation operation.

FIG. 5 is a Mollier diagram showing an operation cycle.

FIG. 6 is a Mollier diagram showing an operation cycle.

FIG. 7 is a diagram showing a device configuration and a switching mode of refrigerant flow according to another embodiment.

FIG. 8 is a diagram showing a conventional apparatus configuration.

FIG. 9 is a diagram showing a comparative example of a flow path switching configuration.

FIG. 10 is a diagram showing another comparative example of the flow path switching configuration.

[Explanation of symbols]

G1, G2 heat collecting source, heat radiating source, heat collecting and radiating source 2A, 2B heat collecting heat exchanger, heat radiating heat exchanger, heat source heat exchanger 1 output heat exchanger 3 compressor 4 expansion means 7 circulation direction switching means K1, K2 flow Route switching means re Outlet flow path or inlet flow path of expansion means rc Suction flow path or discharge flow path of compressor HT (HT1, HT2) Refrigerant heating effect ΔHT Setting difference in refrigerant heating effect LT (LT1, LT2) Refrigerant Temperature drop effect ΔLT Setting difference of refrigerant temperature drop effect X determination means Y control means

──────────────────────────────────────────────────続 き Continued on the front page (58) Field surveyed (Int. Cl. ⁷ , DB name) F25B 1/00 F25B 5/00-6/04

Claims (3)

(57) [Claims] 1. An individual heat source (G1) as an evaporator,
(G2) is a compression heat pump in which first and second heat collecting heat exchangers (2A) and (2B) for heating a flowing refrigerant are connected in series, and an outlet flow path of an expansion means (4) re) with the first and second
A first flow path switching unit (K) which is alternatively connected to one end and the other end of the series combination of the heat collecting heat exchangers (2A) and (2B).
1) and the suction passage (rc) of the compressor (3) is alternatively connected to one end and the other end of the series combination of the first and second heat sampling heat exchangers (2A) and (2B). Second flow path switching means (K2)
And a high-efficiency heat-exchange heat exchanger in which the first and second heat-exchange heat exchangers (2A) and (2B) are in a state where the refrigerant temperature-raising effect (HT) by the heat-collecting source used is higher than the other. Determining means (X) for determining a low-effect heat-exchanging heat exchanger in which the refrigerant temperature-raising effect (HT) by the used heat-collecting source is lower than that of the other.
Based on the determination result of the determination means (X), the refrigerant to be evaporated that has passed through the expansion means (4) is transferred in the order from the low-effect heat-exchange heat exchanger to the high-effect heat-exchange heat exchanger. The first and second flow path switching means (K1), (K
Setting control means (Y) for controlling switching of 2) only, said judging means (X) is adoption of the low efficiency and high effect heat heat
The heat exchanger (2)
A), (2B) Refrigerant heating effect (HT1), (HT2)
To determine whether the difference is equal to or greater than the set difference (ΔHT).
And the control means (Y) performs both sampling based on the determination result.
Refrigerant heating effect (HT) of the heat heat exchangers (2A) and (2B)
1) If the difference between (HT2) is greater than or equal to the set difference (ΔHT)
Supply of a heat collection source to the low-effect heat collection heat exchanger.
A compression heat pump that is configured to stop . 2. An individual heat radiation source (G1) as a condenser,
First and second heat radiation for cooling the flowing refrigerant by (G2)
Compression type heat exchanger with heat exchangers (2A) and (2B) connected in series
A port pump (re) for the expansion means (4),
One end of a series combination of heat-radiating heat exchangers (2A) and (2B)
A first flow path switching means (K
1) and the first and second discharge passages (rc) of the compressor (3).
One end of the series set of the heat exchangers (2A) and (2B)
Second flow path switching means (K2) alternatively connected to the other end
And the first and second radiating heat exchangers (2A) and (2B).
And the cooling effect of the heat radiation source (LT) is lower than the other.
High-efficiency heat-exchanger with high heat dissipation and heat dissipation
Source cooling effect (LT) is lower than the other
Judging means (X) for judging a low-efficiency heat radiation heat exchanger
And the compressor based on the determination result of the determination means (X).
The refrigerant to be condensed discharged from (3) is dissipated by the low effect heat radiation.
Flow from the heat exchanger in the order of the high-efficiency heat radiation heat exchanger
As described above, the first and second flow path switching means (K1), (K1)
2) a control means (Y) for controlling the switching is provided, and the determination means (X) is provided with the low-effect and high-effect heat radiation
Heat exchanger (2)
A), (2B) Refrigerant cooling effect (LT1), (LT2)
To determine whether the difference is equal to or greater than the set difference (ΔLT).
The control means (Y) performs a double release based on the determination result.
Refrigerant cooling effect (LT) of heat heat exchangers (2A) and (2B)
1) If the difference between (LT2) is greater than or equal to the set difference (ΔLT)
Supply of a heat radiation source to the low-effect heat radiation heat exchanger.
A compression heat pump that is configured to stop . 3. The method according to claim 1 , wherein the heat radiation sources (G1) and (G2) are provided separately.
First and second heat source heat exchange for heating or cooling the flowing refrigerant
Exchangers (2A) and (2B) are connected in series, and the refrigerant is compressed (3), output heat exchanger (1), expansion means
(4) The first and second heat source heat exchangers (2A), (2)
B) the output heat exchanger by circulating
(1) to function as a condenser, and the first and second heat sources
Evaporates heat exchangers (2A) and (2B) as heat exchangers
Heating operation to make the compressor function, and the refrigerant (3)
The first and second heat source heat exchangers (2A) and (2B) are connected in series.
Set, the inflatable hand stage (4), the order of the output heat exchanger (1)
And the output heat exchanger (1) functions as an evaporator.
And the first and second heat source heat exchangers (2A),
(2B) as a heat-radiating heat exchanger
Circulating direction switching means (7) for switching the operating state
In the heat recovery operation, it becomes the outlet flow path of the expansion means (4).
In the heat-dissipation operation, it becomes the inlet flow path of the expansion means (4).
The flow path (re) is connected to the first and second heat source heat exchangers (2).
A) Alternative to one end and the other end in the series set of (2B)
And a first flow path switching means (K1) connected to the compressor, and a suction flow path of the compressor (3) in the heat collecting operation.
In the heat dissipation operation, the flow serving as the discharge passage of the compressor (3)
Channel (rc) through the first and second heat source heat exchangers (2
A) Alternative to one end and the other end in the series set of (2B)
A second flow path switching means (K2) connected to the first and second heat source heat exchangers (2
For A) and (2B), the temperature rise of the refrigerant by the used heat radiation source
High-efficiency heat exchange in situations where the effect (HT) is higher than the other
Heat exchanger as a heat exchanger
Low-efficiency heat harvesting in situations where the thermal effect (HT) is lower than the other
Determines the heat source heat exchanger to be the exchanger and performs the heat dissipation operation
Then, the first and second heat source heat exchangers (2A), (2
Regarding B), the cooling / cooling effect (L
T) is a high-efficiency heat-radiating heat exchanger in situations where it is higher than the other.
Cooling effect of the heat source heat exchanger and the heat radiation source used
Low heat radiation heat exchanger where (LT) is lower than the other
The determination unit (X) for determining the heat source heat exchanger to be used, and the determination result of the determination unit (X),
The refrigerant to be evaporated, which has passed through the expansion means (4),
From the heat source heat exchanger, which is the
Flow through the heat source heat exchanger in order
And in the heat dissipation operation, discharged from the compressor (3).
A heat source that turns the refrigerant to be condensed into the low-efficiency heat-radiating heat exchanger
Heat source heat exchange from heat exchanger to said high-efficiency radiating heat exchanger
Of the heat collection operation and the heat radiation operation so that the heat flows in the order of the heat exchanger.
The first and second flow path switching means (K1) and (K2)
Control means (Y) for switching control between the low effect and the high effect in the heat collecting operation.
When determining the heat source heat exchanger to be the effective heat collecting heat exchanger
Heat source heat exchangers (2)
A), (2B) Refrigerant heating effect (HT1), (HT2)
Is determined to be greater than or equal to a set difference (ΔHT).
In the heat dissipation operation, the low-effect and high-effect heat exchanger
The heat source heat exchanger that determines
Refrigerant of heat source heat exchangers (2A) and (2B) as heat exchangers
The difference between the temperature drop effects (LT1) and (LT2) is the set difference (ΔL
And determining configuration whether a T) or more, the control unit (Y), based on the determination result, Tonetsu
In operation, the temperature rise of the refrigerant in both heat source heat exchangers (2A) and (2B)
The difference between the effects (HT1) and (HT2) is smaller than the set difference (ΔHT).
When above, the heat source heat becomes the low-efficiency heat-collecting heat exchanger
Stop supplying the heat radiation source to the exchanger, and
Is the cooling effect of both heat source heat exchangers (2A) and (2B)
If the difference between (LT1) and (LT2) is greater than or equal to the set difference (ΔLT)
Sometimes, the heat source heat exchange becomes the low-efficiency heat radiation heat exchanger
A compression heat pump that is configured to stop the supply of the heat radiation source to the vessel .