JPH08303884A - Compression type heat pump - Google Patents

Abstract

PURPOSE: To carry out the maximum high grade coefficient operation regardless of changes in the condition of intake or radiation heat source used by controlling the switching operation of first and second passage switching means to make a refrigerant to be evaporated passing through an expansion means from a low effect intake heat exchanger to a high effect intake heat exchanger sequentially. CONSTITUTION: In the heat intake operation, a controller 10 makes a refrigerant to be evaporated passing through an expansion valve 4 pass from a heat source heat exchanger as a low effect intake heat exchanger to a high effect intake heat exchanger sequentially based on the results of judgment of a judging means. In the heat radiation operation, the refrigerant to be condensed discharged from a compressor 3 is made to pass from a heat source heat exchanger as a low effect radiation heat exchanger to a high effect heat source heat exchanger sequentially. In this case, each in the heat intake and heat radiation operation, the switching operation of two-way valves V1-V4 as first and second passage switching means K1 and K2 is controlled. This enables the maximum high grade coefficient operation at any time regardless of changes in the condition of the respective intake heat sources thereby achieving a saving of energy.

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 compressor in which first and second heat collecting heat exchangers for heating a circulating refrigerant by individual heat collecting sources as an evaporator are connected in series. A compression heat pump as a heat source, and first and second cooling the flowing refrigerant by individual heat radiation sources as a condenser
, A heat-dissipating heat pump with two heat radiation sources connected in series, and first and second heat source heat exchangers that heat or cool the flowing refrigerant by individual heat radiation sources are connected in series, Refrigerant is circulated in the order of compressor-output heat exchanger-expansion means-first and second heat source heat exchangers to make the output heat exchanger function as a condenser, and the first and second heat source heats. Heat collection operation that makes the exchanger function as an evaporator as a heat collection heat exchanger,
Refrigerant is circulated in the order of compressor-first set of first and second heat source heat exchangers-expansion means-output heat exchanger to make the output heat exchanger function as an evaporator, and the first and second heat source heats. TECHNICAL FIELD The present invention relates to a compression heat pump having two heat radiation sources, which switches the operating state between a heat radiation operation in which the exchanger functions as a heat radiation heat exchanger and a condenser function.

[0002]

2. Description of the Related Art Conventionally, in this type of serial connection type compression heat pump, as shown in FIG. 8, the refrigerant to be vaporized which has passed through the expansion means 4 is made to flow in series (flow indicated by solid line arrow). 1st and 2nd heat collecting heat exchangers Ne1, Ne2,
Also, with respect to both 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), a series combination of these heat exchangers (That is, the series combination of Ne1 and Ne2 or the series combination of Nc1 and Nc2) is simply inserted in the circulation path of the refrigerant, and the first and second heat collecting heat exchangers are used. Order of refrigerant serial flow for Ne1 and Ne2, and first and second heat radiation heat exchangers Nc1 and Nc
The order of the serial flow of the refrigerant with respect to No. 2 was fixed.

It should be noted that G1 and G2 are individual heat-collecting sources for the first and second heat-collecting heat exchangers Ne1 and Ne2, or individual heat-discharging sources for the first and second heat-dissipating heat exchangers Nc2 and Nc1. Indicates a heat source.

In addition, a heat collection operation in which the first and second heat source heat exchangers function as evaporators as the heat collection heat exchangers Ne1 and Ne2 by reversing the refrigerant circulation direction by a four-way valve or the like,
These first and second heat source heat exchangers are connected to the heat radiation heat exchanger Nc.
In the type in which the operation mode is switched to the heat radiation operation in which the condenser functions as 1, Nc2 (that is, in the type in which the flow shown by the solid line and the flow shown by the broken line in FIG. 8 are switched), the refrigerant circulation direction is reversed. Although the sequence of the refrigerant series flow to the first and second heat source heat exchangers is reversed between the heat collection operation and the heat radiation operation, the first and second heat collection heat exchangers Ne1 and Ne2 are collected in the heat collection operation. The order of the refrigerant serial flow is fixed, and the order of the serial refrigerant flow to the first and second radiating heat exchangers Nc1 and Nc2 is fixed in the heat radiation operation.

[0005]

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

When the situation of any of the heat collecting sources G1 and G2 changes due to various causes (for example, temperature change and flow rate change of the heat collecting source), the heat collecting heat of the upstream side is changed due to the situation change of these heat collecting sources. The level relationship between the refrigerant temperature raising effect by the heat collecting source G1 used in the exchanger Ne1 and the refrigerant temperature raising effect by 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 evaporation temperature te may change, which may cause a decrease in the coefficient of performance cop due to the decrease in the evaporation pressure pe and the evaporation temperature te.

Similarly, regarding the heat radiation source, the cooling effect of the refrigerant by the heat radiation sources G2 and G1 used in each of the first and second heat radiation heat exchangers Nc1 and Nc2 (that is, a saturated liquid is formed through the condensation process). In terms of the effect of further cooling the existing refrigerant by cooling, in short, the effect of obtaining the supercooling degree sc), the refrigerant by the heat radiation source G2 used in the heat radiation heat exchanger Nc1 located on the upstream side in the serial flow Due to the level relationship between the temperature lowering effect and the refrigerant temperature lowering effect by the heat radiation source G1 used in the radiation heat exchanger Nc2 located on the downstream side, the condensing pressure pc and the condensing temperature t of the refrigerant in the heat pump operation.
c will be different.

When any one of the heat radiation sources G2 and G1 changes its condition due to various causes (for example, temperature change and flow rate change of the heat radiation source), the heat radiation heat exchange on the upstream side due to the change of the condition of these heat radiation sources. The level relationship between the refrigerant temperature lowering effect by the used heat radiation source G2 in the vessel Nc1 and the refrigerant temperature lowering effect by the used heat source G1 in the downstream side heat radiation 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 there is a case where tc changes, which may cause a decrease in the coefficient of performance cop due to an increase in the condensation pressure pc and the condensation temperature tc.

In view of the above-mentioned circumstances, the object of the present invention is to enable and maximize the maximum coefficient of performance operation under the situation at each time regardless of the situation change of each heat collecting source or each heat radiating source. The point is to simplify the improved configuration to achieve. 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 heat collecting source or heat radiating source.

[0010]

[Means for Solving the Problems]

[First Characteristic Configuration] A first characteristic configuration of the present invention (a characteristic configuration of the invention according to claim 1) relates to a compression heat pump, in which a circulating refrigerant is heated by an individual heat collecting source as an evaporator.
And a configuration in which the second heat collecting heat exchanger is connected in series, the outlet flow path of the expansion means is selectively connected to one end and the other end of the series combination of the first and second heat collecting heat exchangers. And a second flow path switching means for selectively connecting the suction flow path of the compressor to one end and the other end of the series combination of the first and second heat collection heat exchangers. Means and the first and second
Regarding the heat collection heat exchanger, a highly effective heat collection heat exchanger in which the refrigerant temperature raising effect by the used heat collection source is higher than the other,
Determination means for determining a low effect heat collection heat exchanger in a situation where the refrigerant temperature raising effect by the used heat collection source is lower than the other, and the evaporation target refrigerant that has passed through the expansion means based on the determination result of this determination means So as to flow in order from the low-effect heat collection heat exchanger to the high-effect heat collection heat exchanger.
And the control means for controlling the switching of the second flow path switching means.

[Second Characteristic Configuration] A second characteristic structure of the present invention (a characteristic structure of the invention according to claim 2) is the same as the first characteristic structure described above, wherein the determination means is configured to detect the low effect and the high effect. Along with determining the heat heat exchanger, it is configured to determine whether or not the difference in the refrigerant temperature raising effect of these heat collection heat exchangers is equal to or more than a set difference, and the control means, based on this determination result, When the difference in the refrigerant temperature raising effect of the heat collecting heat exchanger is equal to or more than the set difference, the supply of the heat collecting source to the heat collecting heat exchanger having the low effect is stopped.

[Third Characteristic Configuration] A third characteristic configuration of the present invention (a characteristic configuration of the invention according to claim 3) relates to a compression heat pump, and cools the flowing refrigerant by a separate heat source as a condenser. In a configuration in which the first and second radiant heat exchangers are connected in series, the inlet passage of the expansion means is selectively connected to one end and the other end of the series set of the first and second radiant heat exchangers. First flow path switching means, and second flow path switching means for selectively connecting the discharge flow path of the compressor to one end and the other end of the series combination of the first and second radiant heat exchangers In the first and second radiant heat exchangers, a high-efficiency heat radiating heat exchanger in which the cooling effect of the heat source used is higher than that of the other, and a cooling effect of the heat source used is lower than that of the other. Determining means for determining a low-efficiency heat radiation heat exchanger in Based on the determination result of the stage, the refrigerant to be condensed discharged from the compressor is passed through the low-efficiency heat radiation heat exchanger in the order of the high-efficiency heat radiation heat exchanger. The control means for switching the flow path switching means is provided.

[Fourth Characteristic Configuration] According to a fourth characteristic structure of the present invention (a characteristic structure of the invention according to claim 4), in the above-mentioned third characteristic structure, the judging means is characterized in that the low-effect and high-effect heat dissipation is achieved. Along with determining the heat exchanger, it is configured to determine whether or not the difference in the refrigerant cooling effect of these radiant heat exchangers is equal to or greater than a set difference, and the control means, based on this determination result, both radiant heat exchangers. When the difference in the refrigerant cooling effect of the heat exchanger is equal to or more than the set difference, the supply of the heat radiation source to the low heat radiation heat exchanger is stopped.

[Fifth Characteristic Configuration] A fifth characteristic configuration of the present invention (a characteristic configuration of the invention according to claim 5) relates to a compression heat pump, wherein a circulating refrigerant is heated or cooled by an individual heat collecting / radiating source. Connecting the first and second heat source heat exchangers in series,
Refrigerant is circulated in the order of a series of a compressor, an output heat exchanger, an expansion means, and the first and second heat source heat exchangers to make the output heat exchanger function as a condenser, and the first and second heat exchangers. (2) Heat collection operation in which the heat source heat exchanger functions as an evaporator as a heat collection heat exchanger, and refrigerant is used in series with the compressor, the first and second heat source heat exchangers, the expansion means, and the output heat exchanger. Circulation direction in which the operating state is switched to heat dissipation operation in which the output heat exchanger functions as an evaporator and the first and second heat source heat exchangers function as condensers as heat dissipation heat exchangers in the order of One end of the series combination of the first and second heat source heat exchangers is the switching means and the flow path which becomes the outlet flow path of the expansion means in the heat collection operation and becomes the entrance flow path of the expansion means in the heat radiation operation. And a first flow path switching means selectively connected to the other end, and heat collection The suction flow path of the compressor in rotation and the discharge flow path of the compressor in heat radiation operation are selected as one end and the other end of the series combination of the first and second heat source heat exchangers. In the heat collection operation, the second flow path switching unit that is integrally connected and the first and second heat source heat exchangers are highly effective in the situation where the refrigerant temperature raising effect by the used heat collection and radiation source is higher than the other. A heat source heat exchanger to be a heat collection heat exchanger,
It is determined that the heat source heat exchanger is a heat collecting heat exchanger having a low effect in a situation where the refrigerant temperature raising effect by the used heat collecting and radiating source is lower than the other, and in the heat radiating operation, the first and second heat source heat exchanges. Heat source heat exchanger that becomes a highly effective heat dissipation heat exchanger in the situation where the cooling and cooling effect of the heat source used is higher than that of the other, and low effect when the cooling effect of the refrigerant by the used heat source is lower than the other Based on the determination means for determining the heat source heat exchanger to be the heat radiation heat exchanger, the evaporation target refrigerant that has passed through the expansion means in the heat collection operation is set to the low effect heat collection heat. In order to flow from the heat source heat exchanger that is the exchanger to the heat source heat exchanger that is the high-efficiency heat collecting heat exchanger, and in the heat radiation operation, the refrigerant to be condensed discharged from the compressor is From the heat source heat exchanger that will be the effective heat dissipation heat exchanger A control means for switching and controlling the first and second flow path switching means in each of the heat collection operation and the heat radiation operation is provided so that the heat source heat exchanger which becomes the effective heat radiation heat exchanger flows in order. is there.

[Sixth Characteristic Configuration] A sixth characteristic structure of the present invention (a characteristic structure of the invention according to claim 6) is the above-mentioned fifth characteristic structure, wherein the determination means is configured to reduce the low effect in the heat collecting operation. While determining the heat source heat exchanger to be a highly effective heat collection heat exchanger, it is determined whether the difference in the refrigerant temperature raising effect of these heat source heat exchangers as the heat collection heat exchanger is equal to or greater than the set difference. And, in the heat radiation operation, while determining the heat source heat exchanger to be the low effect and high effect heat radiation heat exchanger, the difference in the refrigerant cooling effect of the heat source heat exchanger as these heat radiation heat exchanger is equal to or more than the set difference. With a configuration to determine whether there is, the control means, based on the determination result, when the difference in the refrigerant temperature raising effect of both heat source heat exchangers in the heat collection operation is equal to or more than the set difference, the low effect Stops supplying heat from the heat source to the heat source heat exchanger Further, in the heat radiation operation, when the difference in the refrigerant cooling effect of both heat source heat exchangers is equal to or more than the set difference, the supply of the heat collection and heat radiation source to the heat source heat exchanger to be the heat radiation heat exchanger of the low effect is stopped. It is as it is.

[0016]

[Action]

[Operation of First Characteristic Configuration] That is, the refrigerant heating effect by the used heat collecting source in the upstream heat collecting heat exchanger and the refrigerant heating effect by the used heat collecting source in the downstream heat collecting heat exchanger Due to the high / low relationship, the evaporation pressure p of the refrigerant in the heat pump operation
As a result of studying that e and evaporating temperature te are different, the refrigerant heating effect by the heat collecting source used in the downstream heat collecting heat exchanger is increased by the heat collecting source used in the upstream heat collecting heat exchanger. It has been found that when the temperature raising effect is higher than that in the opposite case, the heat pump operation with higher evaporation pressure pe and evaporation temperature te becomes possible.

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 set in the downstream heat collecting heat exchanger. , The refrigerant evaporates under the evaporation temperature te to reach the saturated vapor, and subsequently the refrigerant temperature is increased from the evaporation temperature te to obtain the superheat degree sh. On the other hand, in the heat collection heat exchanger on the upstream side,
Since the refrigerant is only evaporated to a certain degree of dryness x under the same evaporation pressure pe and evaporation temperature te as those of the heat collecting heat exchanger on the downstream side, such a serial flow type is used. Appropriate superheat degree sh in heat pump operation
The evaporating pressure pe and the evaporating temperature te in the case of obtaining the temperature difference depend on the refrigerant temperature increasing effect (acquisition effect of the superheat degree sh) by the heat collecting source used in the downstream heat collecting heat exchanger.

Regarding the heat collecting heat exchanger on the downstream side, in the operation of keeping the evaporation pressure pe and the evaporation temperature te constant, the refrigerant temperature raising effect by the heat collecting source used in the heat collecting heat exchanger on the downstream side As can be understood from the fact that the obtained superheat degree sh increases as the refrigerant temperature increasing effect increases, when the constant superheat degree sh is changed, when the constant superheat degree sh is obtained, The effect of increasing the temperature of the refrigerant by the heat collection source used is so high that the refrigerant temperature at the outlet of the heat collection heat exchanger can be increased (that is, the refrigerant temperature rise by the superheat degree sh from the evaporation temperature te (sensible heat (The exchange) can be performed more efficiently), the evaporation pressure pe and the evaporation temperature te may be high,
From this, when the refrigerant temperature increasing effect by the heat collecting source used 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 opposite of Compared with the case, the operation with higher evaporation pressure pe and evaporation temperature te becomes possible.

With this in mind, in the first characteristic configuration of the present invention, the first and second heat collecting heat exchangers connected in series have a higher refrigerant temperature raising effect by the heat collecting source used than the other. Judge the high-efficiency heat-collecting heat exchanger and the low-effect heat-collecting heat exchanger in which the refrigerant temperature raising effect by the used heat-collecting source is lower than the other, using an appropriate determination method such as by detecting the heat-collecting source situation. Based on the result of the determination, the control means causes the refrigerant to be evaporated that has passed through the expansion means to flow in the order from the low-effect heat collection heat exchanger to the high-effect heat collection heat exchanger. By controlling the first and second flow path switching means to change the flow order of the refrigerant to the first and second heat collecting heat exchangers, the heat collecting heat exchangers in the respective heat collecting heat exchangers change due to changes in the situation of each heat collecting source. Despite the change in the refrigerant temperature rise 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 first heat collecting heat exchanger 2A is used for changing the flow order by the first and second flow path switching means.
Is the high-efficiency heat-collecting heat exchanger (Fig. 2 (b))
), The first flow path switching means K1
Is the second heat collection heat exchanger 2B in the series combination of the first and second heat collection heat exchangers 2A and 2B, which is connected to the outlet passage re of the expansion means 4.
The second flow passage switching means K2 connects the suction flow passage rc of the compressor 3 to the series set 2
A switching state is established in which the first and second heat collecting heat exchangers 2A and 2B are connected to each other, whereby the refrigerant to be evaporated that has passed through the expansion means 4 is a second heat collecting heat exchanger having a low effect. Flow from the heat collection heat exchanger 2B to the first heat collection heat exchanger 2A, which is a highly effective heat collection heat exchanger, in that order.

On the contrary, when the second heat collecting heat exchanger 2B is the highly effective heat collecting heat exchanger (see the solid arrow in FIG. 2A), the first flow path switching means K1 Is in a switching state in which the outlet flow path re of the expansion means 4 is connected to the end of the series set 2A, 2B on the side of the first heat collection heat exchanger 2A, and the second flow path switching means K2 is compressed. The suction flow path rc of the machine 3 is connected to the end of the series set 2A, 2B on the side of the second heat collection heat exchanger 2B, so that the refrigerant to be evaporated that has passed through the expansion means 4 is reduced. The first heat collection heat exchanger 2A which is an effective heat collection heat exchanger and the second heat collection heat exchanger 2B which is a high effect heat collection heat exchanger are made to flow in this order.

[Operation of Second Characteristic Configuration] In the above-described first characteristic configuration, by placing a highly effective heat-collecting heat exchanger on the downstream side, it is possible to operate the evaporation pressure pe and the evaporation temperature te as high as possible. On the other hand, if the refrigerant temperature raising effect of the heat collecting source used in the low heat collection heat exchanger is too small compared to the refrigerant temperature raising effect of the heat collecting source used in the high heat collecting heat exchanger, In the low-effect heat-collection heat exchanger, the working temperature for the refrigerant is lower than the evaporation temperature te (that is, the used heat-collection source acts as a cooling source on the evaporation-target refrigerant in reverse), This causes a decrease in the coefficient of performance cop.

With this in mind, in the second characteristic configuration of the present invention, the heat collection heat exchangers of low effect and high effect are determined, and the refrigerant temperature raising effect by the heat collection source used in these heat collection heat exchangers is determined. The determination means determines whether or not the difference between the two is greater than or equal to the set difference, and based on this determination result, when the difference between the refrigerant temperature raising effects of both heat collection heat exchangers is greater than or equal to the set difference, the control means Heat pump operation is performed with the heat collection source supply to the low-efficiency heat-collecting heat exchanger stopped and only the high-efficiency heat-collecting heat exchanger is allowed to function as an evaporator. Avoid the situation where the heat collection source used in the heat collection 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 Third Characteristic Configuration] That is, the refrigerant cooling effect by the heat radiation source used in the upstream radiation heat exchanger and the refrigerant temperature cooling effect by the heat radiation source used in the downstream radiation heat exchanger are high and low. As a result of researching 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 heat radiation source used in the heat radiation heat exchanger on the downstream side is the heat radiation heat exchanger on the upstream side. It has been found that when the effect of cooling the refrigerant by the used heat radiation source is higher than that in the opposite case, the condensing pressure pc and the condensing temperature tc are lower than those in the opposite case.

That is, in the type in which the refrigerant to be condensed discharged from the compressor is made to flow in series with the first and second radiant heat exchangers, the radiant heat exchanger on the downstream side has a constant condensing pressure pc and condensation. The refrigerant is condensed under the temperature tc to reach the saturated liquid, and then the condensation temperature t
The refrigerant temperature is lowered from e to obtain the supercooling degree sc, while the upstream side heat radiation heat exchanger
Under a condensing pressure pc and a condensing temperature tc that are equal to those of the radiant heat exchanger on the downstream side, a certain degree of wetness m (= 1-dryness x)
Since only the refrigerant is condensed up to the condensing pressure pc, when obtaining an appropriate supercooling degree sc in such a serial flow type heat pump operation,
The condensing temperature tc varies depending on the cooling effect of the refrigerant by the heat radiation source used in the radiation heat exchanger on the downstream side (the effect of obtaining the degree of supercooling sc).

As for the radiant heat exchanger on the downstream side, in the operation of maintaining the condensing pressure pc and the condensing temperature tc constant, the effect of cooling the refrigerant by the radiant heat source used in the radiant heat exchanger on the downstream side is changed. In this case, as can be understood from the fact that the higher the refrigerant cooling effect is, the larger the acquired supercooling degree sc is, in the case of obtaining a constant supercooling degree sc,
Used in the radiant heat exchanger on the downstream side The effect of cooling the refrigerant by the radiant heat source is high, and the refrigerant temperature at the outlet of the radiant heat exchanger can be lowered (that is, the subcooling degree sc from the condensing temperature tc). The refrigerant temperature can be lowered (sensible heat exchange more efficiently) and the condensing pressure pc and the condensing temperature tc can be low. From this fact, the cooling of the refrigerant by the radiation source used in the radiation heat exchanger on the downstream side can be performed. When the effect is higher than the effect of cooling the refrigerant by the radiating heat source used in the radiant heat exchanger on the upstream side, the operation with lower condensing pressure pc and condensing temperature tc becomes possible compared to the opposite case.

With this in mind, in the third characteristic configuration of the present invention, in the first and second radiating heat exchangers connected in series, the refrigerant cooling effect by the radiating heat source used is higher than the other effect. The radiant heat exchanger and the radiant heat exchanger with a low effect in which the cooling effect of the refrigerant by the used radiant heat source is lower than the other, let the deciding means decide by an appropriate deciding method such as detecting the radiant heat source situation, Then, based on this determination result, the control means causes the first and second streams to flow so that the refrigerant to be condensed discharged from the compressor flows in the 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 sequence for the first and second radiant heat exchangers, regardless of the change in the refrigerant cooling effect in each radiant heat exchanger due to the change in the status of each radiant heat source, Condensation pressure under the 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, regarding the above-mentioned change of the flow order by the first and second flow path switching means, the first radiating heat exchanger 2A is used.
Is the high-efficiency heat radiation heat exchanger (Fig. 2 (a))
), The first flow path switching means K1
Is the first radiant heat exchanger 2A in the series combination of the first and second radiant heat exchangers 2A and 2B, which are connected to the inlet passage re of the expansion means 4.
The second flow path switching means K2 connects the discharge flow path rc of the compressor 3 to the series set 2 described above.
A switching state is established in which A and 2B are connected to the ends on the side of the second radiant heat exchanger 2B, whereby the refrigerant to be condensed discharged from the compressor 3 is transferred to the second radiant heat exchanger, which is a low-effective radiant heat exchanger. The first radiant heat exchanger 2A, which is a highly effective radiant heat exchanger, is caused to flow in order from the exchanger 2B.

On the contrary, when the second radiant heat exchanger 2B is the highly effective radiant heat exchanger (see the broken line arrow in FIG. 2B), the first flow path switching means K1 is The inlet flow path re of the expansion means 4 is brought into a switching state in which it is connected to the end of the series set 2A, 2B on the side of the second radiant heat exchanger 2B, and the second flow path switching means K2 is the compressor 3. The discharge flow path is the first radiating heat exchanger 2 in the series set 2A, 2B.
The switching target is connected to the end on the A side, whereby the refrigerant to be condensed discharged from the compressor 3 is transferred from the first radiant heat exchanger 2A, which is a low radiative heat exchanger, to a high radiative heat exchange. The second radiant heat exchanger 2B, which is a container, is allowed to flow in that order.

[Operation of Fourth Characteristic Configuration] In the above-mentioned third characteristic configuration, when the highly effective radiant heat exchanger is located on the downstream side, it is possible to operate the condensation pressure pc and the condensation temperature tc as low as possible. Use in low-efficiency heat-radiation heat exchanger If the cooling effect of the refrigerant by the heat-dissipation source is too small compared to the effect of cooling the refrigerant by the heat-dissipation source in the high-efficiency heat-exchanger, the low-efficiency heat dissipation placed on the upstream In the heat exchanger, the working temperature for the refrigerant is higher than the above condensation temperature tc (that is, the heat radiation source used conversely acts as a heating source for the refrigerant to be condensed), which results in the coefficient of performance cop. Cause a decrease in.

With this in mind, in the fourth characteristic configuration of the present invention, the difference in the cooling effect of the refrigerant depending on the heat radiation source used in these heat radiating heat exchangers is determined along with the determination of the heat radiating heat exchangers of low effect and high effect. If the difference between the refrigerant cooling effects of the two heat radiating heat exchangers is equal to or greater than the set difference, the control means determines whether the heat radiating heat is less than the set difference. Heat pump operation is performed with the heat radiation source supply to the exchanger stopped and only the high-efficiency heat-radiation heat exchanger functions as a condenser. Avoid the situation where the heat radiation source acts as a heat 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 Fifth Characteristic Configuration] In the fifth characteristic configuration, while the first and second heat source heat exchangers function as evaporators as heat collecting heat exchangers, heat is collected from individual heat collecting and radiating sources. , 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 condensers to function as heat radiation heat exchangers, The heat radiation operation of causing the output heat exchanger to function as an evaporator and cooling the object to be cooled while causing the heat radiation source to perform heat radiation is selectively performed by switching the refrigerant circulation direction.

In the heat collecting operation using the first and second heat source heat exchangers as the heat collecting heat exchangers, the refrigerant temperature raising effect by the used heat collecting and radiating source is higher than that of the other one, as in the above-mentioned first characteristic configuration. A heat source heat exchanger that is a highly effective heat collection heat exchanger in high conditions,
The heat source heat exchanger, which is a heat collecting heat exchanger with a low effect when the temperature rise effect of the heat collecting / radiating source is lower than that of the other, is determined by the judging means using an appropriate judgment method such as detecting the condition of the heat collecting / radiating source. , Based on this determination result, the refrigerant to be evaporated that has passed through the expansion means is made to flow in the order of the heat source heat exchanger, which is a low-effect heat collection heat exchanger, and the heat source heat exchanger, which is a high-effect heat collection heat exchanger. As described above, the control means controls the first and second flow path switching means to change the refrigerant flow sequence for the first and second heat source heat exchangers. In spite of a change in the refrigerant temperature increasing effect in the heat source heat exchanger, it is possible to operate the evaporation pressure pe and the evaporation temperature te as high as possible, that is, the coefficient of performance cop as high as possible under the circumstances at each time.

Further, regarding the above-mentioned change of the flow order by the first and second flow path switching means in the heat collecting operation, the first heat source heat exchanger 2A is highly effective as in the first characteristic construction. In the case of a heat heat exchanger (see the solid arrow in FIG. 2B), the first flow path switching means K1 uses the flow path re serving as the outlet flow path of the expansion means 4 as the first and second heat source heat. Exchanger 2A,
2B, the second heat source heat exchanger 2B side end of the series combination, and the second flow path switching means K2 has a flow path rc which is the suction flow path of the compressor 3 in the series combination 2A, 2B. First
The heat source heat exchanger 2A is connected to the end portions on the side of the heat exchanger 2A so that 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 heat collecting heat exchanger having a low effect.
Heat source heat exchanger 2A which is a highly effective heat collecting heat exchanger
When the second heat source heat exchanger 2B is a highly effective heat collection heat exchanger (see the solid line arrow in FIG. 2 (A)), the first flow path switching means K1 is , The outlet flow passage re of the expansion means 4 is at the end of the series set 2A, 2B on the first heat source heat exchanger 2A side, and the second flow passage switching means K2 is the compressor 3 The flow passage rc, which is the suction flow passage, is connected to the ends on the second heat source heat exchanger 2B side in the series combination 2A, 2B, respectively, and is brought into a switching state, whereby the refrigerant to be evaporated that has passed through the expansion means 4 is The first heat source heat exchanger 2A, which is a low-effect heat collection heat exchanger, is made to flow from the second heat source heat exchanger 2B, which is a high-effect heat collection heat exchanger, in this order.

On the other hand, in the heat radiation operation using the first and second heat source heat exchangers as the heat radiation heat exchangers, the refrigerant cooling effect by the used heat radiation source is higher than that of the other in the same manner as the above-mentioned third characteristic configuration. The heat source heat exchanger, which is a high-efficiency heat radiation heat exchanger, and the heat source heat exchanger, which is a low-efficiency heat radiation heat exchanger when the cooling effect of the refrigerant by the used heat radiation source is lower than the other, The determination means is caused to make a determination by an appropriate determination method such as detection, and based on this determination result, the refrigerant to be condensed discharged from the compressor is a low-efficiency heat exchange heat exchanger. The first and second flow path switching means are controlled by the control means so that the heat source heat exchangers to be flowed in order are changed to change the refrigerant flow sequence for the first and second heat source heat exchangers. Each heat source due to changes in the situation of each heat radiation 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).

Further, regarding the above-mentioned change of the flow order by the first and second flow path switching means in the heat radiation operation, the first heat source heat exchanger 2A can radiate heat with a high effect, as in the third characteristic configuration. When the heat exchanger is a heat exchanger (see the dashed arrow in FIG. 2 (a)), the first flow path switching unit K1 uses the flow path re serving as the inlet flow path of the expansion unit 4 as the first and second heat source heat exchangers. Bowl 2
At the end of the series combination of A and 2B on the side of the first heat source heat exchanger 2A, and the second flow path switching means K2, the flow path rc which is the discharge flow path of the compressor 3 is connected to the series combination 2A, 2B is in a switching state in which it is connected to the ends on the side of the second heat source heat exchanger 2B, so that the refrigerant to be condensed discharged from the compressor 3 is transferred to the second heat source heat exchanger, which is a low-efficiency heat exchanger. Bowl 2
First heat source heat exchanger 2 which is a highly effective radiant heat exchanger from B
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 is , Expansion means 4
Of the series set 2A, 2B at the end on the second heat source heat exchanger 2B side, and the second flow path switching means K2 serves as the discharge flow path of the compressor 3. Flow path rc
The first heat source heat exchanger 2A in the series set 2A, 2B
In the switching state where they are connected to the ends on the side of
The refrigerant to be condensed discharged from the compressor 3 is caused to flow in order from the first heat source heat exchanger 2A which is a low effect heat radiation heat exchanger to the second heat source heat exchanger 2B which is a high effect heat radiation heat exchanger.

[Operation of Sixth Characteristic Configuration] In the sixth characteristic configuration, when heat collection operation is performed in the above fifth characteristic configuration,
Similar to the above-mentioned second characteristic configuration, the heat source heat exchanger to be a low-effect and high-effect heat collecting heat exchanger is determined, and the heat collecting heat exchanger is used as a heat collecting heat exchanger. The determination means determines whether or not the difference in the refrigerant temperature increasing effect is equal to or more than the setting difference, and based on this determination result, when the difference in the refrigerant temperature increasing effect between the two heat source heat exchangers is equal to or more than the setting difference, A state in which the control means stops the supply of heat collecting and radiating heat to the heat source heat exchanger that becomes a low effect heat collecting heat exchanger, and only the heat source heat exchanger that becomes a high effect heat collecting heat exchanger functions as an evaporator. In this way, the heat pump operation is performed with the heat source heat exchanger, which is a low-efficiency heat-collecting heat exchanger. To prevent the coefficient of performance cop from decreasing due to the occurrence of various situations.

Further, in the case of performing the heat radiation operation in the fifth characteristic configuration, as in the fourth characteristic configuration, the heat source heat exchanger which is a low effect and high effect heat radiation heat exchanger is determined, and Use as a heat source heat exchanger as a radiant heat exchanger Use the heat source heat exchanger to determine whether the difference in the cooling effect of the refrigerant due to the heat radiating source is greater than or equal to the set difference. When the difference in the refrigerant cooling effect of the heat exchanger is equal to or more than the set difference, the control means stops the supply of the heat radiation source to the heat source heat exchanger, which is the low heat radiation heat exchanger, and the high heat radiation heat exchanger. The heat pump is operated with only the heat source heat exchanger that functions as a condenser functioning, and as a result, it is used in the heat source heat exchanger that functions as a low-efficiency heat radiation heat exchanger. Avoid situations that act as , To prevent a reduction in the coefficient of performance cop due to the occurrence of such a situation.

[0039]

【The invention's effect】

[Effect of First Characteristic Configuration] According to the first characteristic configuration of the present invention, energy saving can be effectively achieved by performing maximum high coefficient of performance operation at each time regardless of changes in the status of each heat collecting source. In addition, a high heating capacity can be stably obtained on the condenser side.

Moreover, as an improvement to the refrigerant path for obtaining this effect, regarding the connection between the first heat collecting heat exchanger and the second heat collecting heat exchanger, they are simply connected in series by a connecting pipe. Taking the same simple connection form as the conventional one,
In addition, the first flow path of the expansion means is selectively connected to one end and the other end of the series combination of the first and second heat collection heat exchangers.
The flow path switching means and the suction flow path of the compressor are first and second.
As for the second flow path switching means that is selectively connected to one end and the other end of the series combination of the heat collection heat exchangers, a bidirectional one-way valve and two two-way valve are used, respectively. Since a simple flow path switching configuration with a small number of valves, such as, can be used, for example, a flow path switching configuration using a total of four three-way valves Va as shown in FIG. 9 or a total of six flow path switching elements as shown in FIG. Two-way valve V
Compared to the case where the flow passage switching configuration using b is adopted to change the flow order of the refrigerant to be evaporated to the first and second heat collecting heat exchangers 2A and 2B, the improvement of the refrigerant path is simple and the device is manufactured. And the cost of the device can be reduced.

[Effect of Second Characteristic Configuration] According to the second characteristic configuration of the present invention, the coefficient of performance caused by an excessively large difference between the refrigerant temperature increasing effects of the first and second heat collecting heat exchangers By preventing the decrease, it is possible to more effectively achieve the improvement of the coefficient of performance in combination with the effect of the first characteristic configuration described above.

Further, when the difference in the temperature raising effect of the refrigerant between the first and second heat collecting heat exchangers is equal to or larger than the set difference, the low effect heat collecting heat exchanger is caused to stop functioning. Since the heat-collecting source supply to the exchanger is stopped to stop the low-effect heat-collecting heat exchanger from functioning, for example, by evaporating the refrigerant to be evaporated to the low-effect heat-collecting heat exchanger, Compared with the mode in which the heat collection heat exchanger is stopped, the bypass refrigerant flow path and the bypass switching valve can be eliminated, and the refrigerant path configuration can be simplified in combination with the effect of the first characteristic configuration described above. .

[Effect of Third Characteristic Configuration] According to the third characteristic structure of the present invention, the maximum high coefficient of performance operation can be performed at any time regardless of the change in the status of each heat radiating source, thereby saving energy. In addition, a high cooling capacity can be stably obtained on the evaporator side.

Further, as an improvement to the refrigerant path for obtaining this effect, as for the connection between the first radiant heat exchanger and the second radiant heat exchanger, both of them are simply connected in series by connecting pipes. Adopting the same simple connection form as
Also, the first flow path selectively connects the inlet flow path of the expansion means to one end and the other end of the series combination of the first and second heat radiation heat exchangers.
The flow path switching means and the discharge flow path of the compressor are first and second.
For the second flow path switching means that is selectively connected to one end and the other end of the series set of radiant heat exchangers, only one bidirectional three-way valve or two bidirectional valves are used. Since a simple flow path switching configuration with a small number of valves such as 4 can be used, a flow path switching configuration using four three-way valves Va as shown in FIG. 9 or six two-way valves as shown in FIG. Compared with the case where the flow passage switching structure using the valve Vb is adopted to change the flow order of the refrigerant to be condensed to the first and second radiating heat exchangers 2A and 2B, the improvement of the refrigerant path is simple and the device is manufactured. And the cost of the device can be reduced.

[Effect of Fourth Characteristic Configuration] According to the fourth characteristic configuration of the present invention, a decrease in the coefficient of performance caused by an excessively large difference in the refrigerant cooling effect of the first and second radiating heat exchangers is caused. By being able to prevent it, the improvement of the coefficient of performance can be achieved more effectively in combination with the effect of the third characteristic configuration.

When the difference between the refrigerant cooling effects of the first and second radiant heat exchangers is equal to or more than the set difference, the low effect radiant heat exchanger is stopped when the low effect radiant heat exchanger is stopped. Since the heat source supply is stopped and the low-efficiency radiant heat exchanger stops functioning, for example, the low-effective radiant heat exchanger functions by diverting the refrigerant to be condensed to the low-effective radiant heat exchanger. Compared with the stop mode, the bypass refrigerant flow path and the bypass switching valve can be eliminated, and the refrigerant path configuration can be simplified in combination with the effect of the third characteristic configuration described above.

[Effect of Fifth Characteristic Configuration] According to the fifth characteristic configuration of the present invention, the heat collection operation using the first and second heat source heat exchangers as the heat collecting heat exchangers, and the first and the second heat collecting operations. In the case where the heat radiation operation using the heat source heat exchanger of 2 as a heat radiation heat exchanger is selectively switched, the heat collection operation and the heat radiation operation are performed independently of the situation change of each heat radiation source. The maximum high coefficient of performance operation can be performed from time to time, whereby energy saving can be effectively achieved, and high cooling capacity and high heating capacity can be stably obtained on the output side.

As an improvement to the refrigerant path for obtaining this effect, the switching structure similar to the conventional one such as using a four-way valve for switching the refrigerant circulation direction is adopted, and the first heat source heat exchange is performed. Regarding the connection between the container and the second heat source heat exchanger, while adopting the same simple connection form as the conventional one in which they are simply connected in series by a connecting pipe,
Similar to the above-mentioned first and third characteristic configurations, the first and second flow path switching means are each a valve that uses only one bidirectional three-way valve or two two-way valves. A small number of simple flow passage switching configurations can be used, and as a result, the flow passage switching configuration using the four three-way valves Va as shown in FIG. 9 described above and the six flow switching configurations as shown in FIG. Way valve V
1) in heat collection operation by adopting the flow path switching configuration using b
Compared with enabling to change the flow order of the evaporation object refrigerant to the second and second heat source heat exchangers and to change the flow order of the condensation object refrigerant to the first and second heat source heat exchangers in the heat radiation operation, the refrigerant path Can be easily improved, the device can be manufactured easily, and the device cost can be reduced.

[Effect of Sixth Characteristic Configuration] According to the sixth characteristic configuration of the present invention, in the heat collecting operation using the first and second heat source heat exchangers as the heat collecting heat exchangers, these first and second The decrease in the coefficient of performance caused by an excessively large difference in the refrigerant temperature raising effect of the heat source heat exchanger, and the heat radiation operation using the first and second heat source heat exchangers as the heat radiation heat exchangers Second
It is possible to prevent a decrease in the coefficient of performance caused by an excessively large difference in the cooling effect of the refrigerant of the heat source heat exchanger, so that the improvement of the coefficient of performance is achieved more effectively in combination with the effect of the fifth characteristic configuration described above. can do.

Further, in the heat collection operation, when the difference between the refrigerant temperature raising effects of the first and second heat source heat exchangers is equal to or more than the set difference,
Also, in the heat radiation operation, when the difference between the refrigerant cooling effects of the first and second heat source heat exchangers is equal to or more than the set difference, the heat source heat exchanger becomes a low effect heat collecting heat exchanger or a low effect heat radiating heat exchanger. In stopping the function of the heat source, like the above-mentioned second characteristic configuration and fourth characteristic configuration, the stop of supply of the heat collecting and radiating source to the heat source heat exchanger which becomes the heat collecting heat exchanger of low effect or the heat radiating heat exchanger of low effect. Therefore, the heat source heat exchanger is deactivated, so that the evaporation target refrigerant and the condensation target refrigerant are diverted to the heat source heat exchanger which becomes the low effect heat collection heat exchanger or the low effect heat radiation heat exchanger. This makes it possible to eliminate the need for a bypass refrigerant flow path and a bypass switching valve, as compared to the case where the heat source heat exchanger stops functioning. This simplifies the refrigerant path configuration in combination with the effect of the fifth characteristic configuration described above. Can be transformed.

[0051]

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

The first heat source heat exchanger 2A is an air / refrigerant heat exchanger which uses the air G1 supplied by the fan 5 as a heat collecting source or a heat radiating source, and the heat collecting and radiating source used in the first heat source heat exchanger 2A. As the air G1, the outside air, the exhaust from the cooling / heating target area, the heating air that has passed through the heating means such as the solar heat collector, the cooling air that has passed through the cooling means such as the sprinkler cooler, etc. are applied. it can.

On the other hand, the second heat source heat exchanger 2B includes a pump 6
Using the water G2 supplied as a heat source or heat source
Water G2, which is a refrigerant heat exchanger and is used as a heat collecting and radiating source in the second heat source heat exchanger 2B, includes river water, well water, sea water, sewage,
Domestic wastewater, factory wastewater, heated 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 by heat storage means. Heat storage water that stores cold heat or heat storage brine can be applied.

Reference numeral 7 is a four-way valve as a circulation direction switching means for the refrigerant. By switching the four-way valve 7,
As for the refrigerant, as shown by solid arrows in the figure, compressor 3-output heat exchanger 1-expansion valve 4-first and second heat source heat exchangers 2A, 2
In the figure, the heat collection operation of circulating the series of B in order and the refrigerant are
As shown by the dashed arrow, switching is performed between the compressor 3 and the series combination of the first and second heat source heat exchangers 2A and 2B-expansion valve 4-output heat exchanger 1 in order of circulation.

That is, in the heat collection operation, the first and second heat source heat exchangers 2A and 2B are caused to function as evaporators, and the respective heat radiation sources G1 and G2 are acted as heat collection heat exchangers, In the heat radiation operation, the output heat exchanger 1 functions 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 function as the condensers to collect heat from the respective heat radiation sources G1 and G1. While radiating heat to G2 as a heat radiating heat exchanger, the output heat exchanger 1 is caused to function as an evaporator to cool the object to be cooled.

V1 and V2 are two-way valves capable of bidirectional operation, and these two-way valves V1 and V2 serve as the outlet passages of the expansion valve 4 during the heat collection operation, and of the expansion valve 4 during the heat radiation operation. The first flow path switching means K1 is configured to selectively connect 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.

Further, V3 and V4 are also bidirectional two-way valves, and these two-way valves V3 and V4 serve as the suction flow path of the compressor 3 in the heat collecting operation and the compressor in the heat radiating operation. The flow path rc, which serves as the discharge flow path of the third
A second flow path switching means K2 is selectively connected to one end and the other end of the series combination of the heat source heat exchangers 2A and 2B.

That is, in the heat collecting operation, the refrigerant to be evaporated is the first and second heat source heat exchangers 2A and 2B as the heat collecting heat exchangers.
On the other hand, when the four flow valves V1 to V4 are switched in series, the refrigerant to be vaporized that has passed through the expansion valve 4 is passed through the expansion valve 4 by the switching operation of the four two-way valves V1 to V4, as shown in FIG. The flow form in which the heat exchanger 2A and the second heat source heat exchanger 2B flow in this order, and 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 the order in which the current flows.

Further, in the heat radiation operation, when the refrigerant to be condensed is caused to flow 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 are used.
By the switching operation from 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 this order, as indicated by a dashed arrow in FIG. 2B, the refrigerant to be condensed discharged from the compressor 3 flows in reverse from the first heat source heat exchanger 2A to the second heat source heat exchanger 2B. Switch to the flow mode.

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

As a basic control, the controller 10 switches between the heat collection operation and the heat radiation operation by switching the four-way valve 7 in accordance with the operation mode command, and the output heat in each of the heat collection 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 are adjusted.
The throttling degree of the expansion valve 4 is adjusted so that the superheat degree sh calculated from e ′ becomes the target superheat degree.

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

In addition to the above-mentioned basic control, the controller 10 also performs the following "basic start / stop depending on the condition of the heat collecting source", "comparison judgment of refrigerant temperature increasing effect", and "refrigerant flow and Each control (refer to the flowchart in FIG. 3) of "switching of heat source supply" is executed, and in the heat radiation operation, "basic start / stop depending on heat source status", "comparison judgment of refrigerant cooling effect" as described below,
Also, each control of "switching of refrigerant flow and supply of heat radiation source" (see the flowchart of FIG. 4) is executed.

(Heat collection operation) "Basic start / stop depending on heat collection source status" Evaporation pressure pe and evaporation temperature te for executing the set lower limit evaporation pressure and lower limit evaporation temperature
Air heat source G1 in the first heat source heat exchanger 2A
The lower limit evaporation pressure and the lower limit evaporation temperature are executed from the detection temperature t1 of the air side detector 9A by using the arithmetic logic R1 set for the correlation between the refrigerant heating capacity HQ1 according to the above and the temperature t1 of the air heat collection source G1. Evaporation pressure pe, evaporation temperature te
In such a case, the refrigerant heating capacity HQ1 by the air heat source G1 in the first heat source heat exchanger 2A in the present situation is calculated.

Similarly, in the case where the lower limit evaporation pressure and the lower limit evaporation temperature are the execution evaporation pressure pe and the evaporation temperature te, respectively, the second
From the detection 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 collection source G2 in the heat source heat exchanger 2B and the temperature t2 of this water heat collection source G2. , The lower limit evaporation pressure and the lower limit evaporation temperature are used as the execution evaporation pressure pe and the evaporation temperature te, respectively, and the refrigerant heating capacity HQ2 by the water heat source G2 in the second heat source heat exchanger 2B is calculated.

Then, the sum of the calculated refrigerant heating capacities HQ1 and HQ2 by the respective heat collection sources G1 and G2, the lower limit evaporation pressure,
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 when the lower limit evaporation temperature is set to 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 and the heat pump operation is stopped. Further, the sum of the calculated refrigerant heating capacities HQ1 and HQ2 is equal to or more than the above-mentioned required heating capacity HQQ (HQ1 + HQ2 ≧ HQ
In the case of Q), the heat pump operation is continued.

"Comparison judgment of refrigerant heating effect" Refrigerant heating effect HT1 and HT2 by the heat collecting sources G1 and G2 used in the heat source heat exchangers 2A and 2B (that is, refrigerant that has become saturated vapor through the evaporation process) The effect of raising the temperature by heating, in other words, the level relationship of the effect of obtaining the degree of superheat sh)
Using the decision logic R3 set for the correlation between the temperatures t1 and t2 of 1 and G2, the temperature t detected by the air side detector 9A is used.
From 1 and the temperature t2 detected by the water side detector 9B, the level relationship between the refrigerant temperature raising effects HT1 and HT2 by the heat collection sources G1 and G2 used in the heat source heat exchangers 2A and 2B is determined.

Then, in the determination of the level relationship, the heat source heat exchanger serving as a highly effective heat collecting heat exchanger in a situation where the refrigerant temperature raising effect HT by the used heat collecting source is higher than the other, and the refrigerant raising by the used heat collecting source. A heat source heat exchanger that is a low-effect heat-collection heat exchanger in a situation where the temperature effect HT is lower than the other is determined, and the temperature of the refrigerant is raised in the heat-source heat exchanger that is a high-effect heat-collection heat exchanger. The effect (that is, HT1 when HT1> HT2, HT2 when HT1 ≦ HT2) is compared with the set lower limit refrigerant temperature increasing effect HTT, and a heat source heat exchanger that becomes a highly effective heat-collecting heat exchanger is used. When the refrigerant temperature increasing effect HT1 or HT2 is less than the lower limit refrigerant temperature increasing effect HTT (<HTT), the compressor 3 is stopped and the heat pump operation is stopped.

Further, when the refrigerant temperature increasing effect HT1 or HT2 in the heat source heat exchanger, which is a highly effective heat collecting heat exchanger, is equal to or higher than the lower limit refrigerant temperature increasing effect HTT (≧ HTT), the highly effective heat collecting heat exchange. Of the refrigerant temperature increasing effect HT between the heat source heat exchanger that serves as a heat exchanger and the heat source heat exchanger that serves as a low-effect heat collecting heat exchanger (that is, HT1-HT2, HT1 if HT1> HT2)
If ≤HT2, it is determined whether or not (HT2-HT1) is greater than or equal to the setting difference ΔHT.

[Switching of refrigerant flow and supply of heat collecting source] Depending on the result of the above judgment regarding the refrigerant temperature increasing effect HT, the following a to
The switching control of d is executed. a. The first heat source heat exchanger 2A is a high-effect heat collection heat exchanger, the second heat source heat exchanger 2B is a low-effect heat collection heat exchanger, and these first and second heat source heat exchangers 2A, When the difference in the refrigerant temperature increasing effect HT of 2B is less than the set difference ΔHT (that is, HT1> HT2 and HT1-HT2 <ΔH
In T), by switching the two-way valves V1 to V4, a flow mode in which the evaporation target refrigerant flows in series from the second heat source heat exchanger 2B to the first heat source heat exchanger 2A (that is, FIG. 2).
(B) the flow form indicated by the solid line arrow), and the supply of the air heat source G1 to the first heat source heat exchanger 2A by the fan 5 and the second heat source heat exchange by the pump 6. Both of the supply of the water heat collection source G2 to the vessel 2B are continuously performed, whereby the first heat source heat exchanger 2A, which is a highly effective heat collection heat exchanger, is located in the downstream side in the serial flow state, These first and second heat source heat exchangers 2A, 2B
The heat pump operation is implemented so that both of them function effectively as evaporators.

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.
The amount of change in dryness x is shown.

B. The first heat source heat exchanger 2A is a high-effect heat collection heat exchanger, the second heat source heat exchanger 2B is a low-effect heat collection heat exchanger, and these first and second heat source heat exchangers 2
When the difference between the refrigerant temperature increasing 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, as in the case of the above-mentioned a, the refrigerant to be evaporated 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 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 is used. Only the air heat collecting source G1 is continuously supplied to the first heat source heat exchanger 2A, whereby the first heat source heat exchanger 2A, which is a highly effective heat collecting heat exchanger, is placed on the downstream side in series connection. In the flowing state, the evaporator function of the upstream second heat source heat exchanger 2B, which is a low-effect heat-collection heat exchanger, is stopped, and the downstream first heat-source heat exchanger, which is a high-effect heat-collection heat exchanger, is stopped. The heat pump operation is performed so that only the vessel 2A effectively functions as an evaporator.

C. The second heat source heat exchanger 2B is a high-effect heat collection heat exchanger, the first heat source heat exchanger 2A is a low-effect heat collection heat exchanger, and the first and second heat source heat exchangers 2 are
When the difference between the refrigerant temperature increasing effects HT of A and 2B is less than the setting difference ΔHT (that is, HT2 ≧ HT1 and HT2-
For HT1 <ΔHT), by switching the two-way valves V1 to V4 from the first heat source heat exchanger 2A to the second heat source heat exchanger 2B.
And the air to the first heat source heat exchanger 2A by the fan 5 while adopting the flow form in which the refrigerant to be evaporated flows in series in the order of (i.e., the flow form shown by the solid arrow in FIG. 2 (a)). Both the supply of the heat collection source G1 and the supply of the water heat collection 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 highly effective heat collection heat exchanger. In a serial flow state in which the exchanger 2B is located on the downstream side, heat pump operation is performed in which both the first and second heat source heat exchangers 2A and 2B effectively function as evaporators.

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 collection heat exchanger, the first heat source heat exchanger 2A is a low-effect heat collection heat exchanger, and the first and second heat source heat exchangers 2 are
When the difference between the refrigerant temperature increasing effects HT of A and 2B is equal to or greater than the set difference ΔHT (that is, HT2 ≧ HT1 and HT2-
HT1 ≧ ΔHT), by switching the two-way valves V1 to V4, as in the case of the above-described c, the refrigerant to be evaporated is allowed to flow in series in the order of the first heat source heat exchanger 2A to the second heat source heat exchanger 2B. Although the flow form (that is, the flow form shown by the 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 second heat source heat exchanger 2B is continuously supplied only to the second heat source heat exchanger 2B by this, whereby the second heat source heat exchanger 2B, which is a highly effective heat collecting heat exchanger, is located on the downstream side in series. In the flow state, the evaporator function of the upstream first heat source heat exchanger 2A, which is a low-effect heat-collection heat exchanger, is stopped, and the downstream second heat-source heat, which is a high-effect heat-collection heat exchanger, is stopped. A heat pump operation is performed in which only the exchanger 2B functions effectively as an evaporator.

(Heat radiation operation) Condensation pressure pc and condensation temperature tc for executing the upper limit condensing pressure and the upper limit condensing temperature set to "basic start / stop depending on the condition of the heat radiating source"
Air heat radiating source G1 in the first heat source heat exchanger 2A
The upper limit condensing pressure and the upper limit condensing temperature are executed from the detection temperature t1 of the air side detector 9A using the arithmetic logic R4 set for the correlation between the refrigerant cooling capacity LQ1 according to the above and the temperature t1 of the air heat radiation source G1. Condensation pressure pc, condensation temperature tc
Then, the refrigerant cooling capacity LQ1 by the air heat radiation source G1 in the first heat source heat exchanger 2A in the present situation is calculated.

Similarly, in the second case where the upper limit condensing pressure and the upper limit condensing temperature are the condensing pressure pc and the condensing temperature tc, respectively.
From the detection 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 radiation source G2 in the heat source heat exchanger 2B and the temperature t2 of the water heat radiation source G2. , The refrigerant cooling capacity LQ2 by the water heat radiating 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 condensing pressure pc and the condensing temperature tc for execution.

Then, the sum of the calculated refrigerant cooling capacities LQ1 and LQ2 by the respective heat radiation sources G1 and G2 and the upper limit condensing pressure,
Refrigerant cooling capacity LQ1, calculated by comparing the required cooling capacity LQQ of the first and second heat source heat exchangers 2A, 2B as a whole when the upper limit condensation temperature is set to the actual condensation pressure pc and condensation temperature tc When the sum of LQ2 is less than the above set required cooling capacity LQQ (LQ1 + LQ2 <LQQ),
The compressor 3 is stopped and the heat pump operation is stopped. Further, the sum of the calculated refrigerant cooling capacities LQ1 and LQ2 is equal to or more than the above-mentioned required cooling capacity LQQ (LQ1 + LQ2 ≧ LQ).
In the case of Q), the heat pump operation is continued.

"Comparison judgment of refrigerant cooling effect" Refrigerant cooling effect LT1, LT2 by heat radiation sources G1, G2 used in each heat source heat exchanger 2A, 2B (that is, cooling the refrigerant which becomes a saturated liquid through the condensation process) The effect of lowering the temperature by, that is, the level relationship of the effect of obtaining the supercooling degree sc), and the heat radiation source G
Using the decision logic R6 set for the correlation with the temperatures t1 and t2 of 1 and G2, the detected temperature t of the air side detector 9A
From 1 and the temperature t2 detected by the water side detector 9B, the level relationship of the refrigerant temperature lowering effects LT1, LT2 by the heat radiation sources G1, G2 used in the heat source heat exchangers 2A, 2B is determined.

In the determination of the relationship between the high and low, the heat source heat exchanger which is a highly effective heat radiating heat exchanger in a situation where the refrigerant temperature lowering effect LT due to the heat radiating source used is higher than the other, and the refrigerant temperature lowering effect LT due to the heat radiating source used Is determined to be a heat-source heat exchanger that is a low-efficiency heat-radiation heat exchanger in a situation where is lower than the other, and the refrigerant cooling effect (that is, LT1> (LT1 in the case of LT2, LT2 in the case of LT1 ≦ LT2) is compared with the set lower limit refrigerant temperature lowering effect LTT, and the refrigerant temperature lowering effect LT1 or LT2 in the heat source heat exchanger which is a high-efficiency heat radiating heat exchanger is compared. When the lower limit refrigerant cooling effect LTT is less than (<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 which is a highly effective heat radiation heat exchanger is equal to or higher than the lower limit refrigerant temperature cooling effect LTT (≧ LTT), the heat source which becomes a highly effective heat radiation heat exchanger. The difference in the refrigerant cooling effect LT between the heat exchanger and the heat source heat exchanger, which is a heat-dissipating heat exchanger having a low effect (that is, LT1-LT2, LT1 when LT1> LT2).
If ≤LT2, it is determined whether or not (LT2-LT1) is equal to or greater than the setting difference ΔLT.

"Switching between refrigerant flow and heat radiation source supply" In accordance with the result of the above judgment regarding the refrigerant temperature lowering effect LT, the following e to
The switching control of h is executed. 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 these first and second heat source heat exchangers 2A, 2B are When the difference in the refrigerant cooling effect LT is less than the set difference ΔLT (that is, LT1> LT2 and LT1-LT2 <ΔL
In (T), by switching the two-way valves V1 to V4, a flow mode in which the refrigerant to be condensed flows in series from the second heat source heat exchanger 2B to the first heat source heat exchanger 2A (that is, FIG. 2).
(A) The flow form shown by the dashed arrow in (a) is adopted, and the supply of the air heat radiation source G1 to the first heat source heat exchanger 2A by the fan 5 and the second heat source heat exchanger 2B by the pump 6 are performed. Both of the supply of the water heat radiation source G2 are continuously performed, whereby the first and the second heat source heat exchangers 2A, which are highly effective heat radiation heat exchangers, are positioned in the downstream side in a serial flow state. The heat pump operation is performed so that both the two heat source heat exchangers 2A and 2B effectively function as condensers.

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

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 these first and second heat source heat exchangers 2
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-
LT2 ≧ ΔLT), by switching the two-way valves V1 to V4, as in the case of the above e, the refrigerant to be condensed is allowed to flow 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 dashed 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 is used. 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 highly effective heat radiation heat exchanger, is placed in the downstream side in series flow. In this state, the condenser function of the upstream second heat source heat exchanger 2B, which is a low-efficiency 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. The heat pump is operated to effectively function as a condenser.

G. The second heat source heat exchanger 2B is a high effect heat radiation heat exchanger, the first heat source heat exchanger 2A is a low effect heat radiation heat exchanger, and these first and second heat source heat exchangers 2
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-
For LT1 <ΔHT), by switching the two-way valves V1 to V4 from the first heat source heat exchanger 2A to the second heat source heat exchanger 2B.
And the air to the first heat source heat exchanger 2A by the fan 5 while adopting a flow form (that is, a flow form indicated by a dashed arrow in FIG. 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. A heat pump operation is performed in which both the first and second heat source heat exchangers 2A and 2B effectively function as condensers in a serial flow state in which the vessel 2B is located on the downstream side.

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 effect heat radiation heat exchanger, the first heat source heat exchanger 2A is a low effect heat radiation heat exchanger, and these first and second heat source heat exchangers 2
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, LT2 ≧ LT1 and LT2-
For LT1 ≧ ΔLT), by switching the two-way valves V1 to V4, the refrigerant to be condensed is allowed to flow in series in the order of the first heat source heat exchanger 2A to the second heat source heat exchanger 2B as in the case of the above g. Although the flow form (that is, the flow form shown by the broken line 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
The continuous supply of the water heat radiation source G2 to the second heat source heat exchanger 2B is carried out, whereby the second heat source heat exchanger 2B, which is a highly effective heat radiation heat exchanger, is placed in the downstream side. In the flowing state, the condenser function of the upstream first heat source heat exchanger 2A, which is a low-effect heat radiation heat exchanger, is stopped, and the downstream second heat source heat exchanger 2B, which is a high-effect heat radiation heat exchanger, is stopped. Perform heat pump operation that effectively functions only as a condenser.

In summary, in the present embodiment, the controller 1
0 is the first and second heat source heat exchangers 2 connected in series for heating or cooling the circulating refrigerant by the individual heat collecting and radiating sources G1 and G2.
Regarding A and 2B, in the "heat collection operation", depending on the heat source heat exchanger to be a highly effective heat collection heat exchanger in a situation where the refrigerant temperature raising effect HT by the used heat collection and radiation source is higher than the other, In the situation where the refrigerant temperature increasing effect HT is lower than the other, it is determined that the heat source heat exchanger is a low effect heat collecting heat exchanger,
It is determined whether or not the difference between the refrigerant temperature increasing effects HT1 and HT2 of the heat source heat exchangers 2A and 2B as the heat collecting heat exchangers is equal to or more than the set difference ΔHT, while in the “heat radiation operation”, the use and discharge A heat source heat exchanger that becomes a highly effective radiant heat exchanger when the refrigerant temperature lowering effect LT due to the heat source is higher than the other, and a low heat radiative heat exchange when the refrigerant temperature lowering effect LT due to the used heat radiating source is lower than the other Source heat exchanger 2 as a heat radiation heat exchanger
The difference between the refrigerant cooling effects LT1 and LT2 of A and 2B is the setting difference Δ.
A determination means X for determining whether or not it is equal to or higher than LT is configured.

Further, the controller 10 constitutes the above-mentioned judging means X and, for the purpose of operation with a high coefficient of performance cop, based on the judgment result of this judging means X, "heat collecting operation".
Then, the evaporation target refrigerant that has passed through the expansion valve 4 as the expansion means flows in the order of the heat source heat exchanger which becomes the low effect heat collecting heat exchanger and the heat source heat exchanger which becomes the high effect heat collecting heat exchanger. As described above, and in the "heat radiation operation", the refrigerant to be condensed discharged from the compressor 3 is changed from the heat source heat exchanger which is a low heat radiation heat exchanger to the high heat radiation heat exchanger which is a high heat radiation heat exchanger. The two-way valves V1 to V4 as the first and second flow path switching means K1 and K2 are switched and controlled by the "heat collection operation" and the "heat radiation operation", respectively, so as to flow in the order of ". Heat source heat exchanger 2 as heat collecting heat exchanger in heat collecting operation "
When the difference between the refrigerant temperature increasing effects HT of A and 2B is equal to or larger than the set difference ΔHT, the heat source heat exchanger serving as a heat collecting heat exchanger having a low effect is supplied with the heat collecting and radiating source (that is, acts as a cooling source). The supply of the heat source that may cause heat) is stopped, and both heat source heat exchangers 2 as the heat radiation heat exchangers in the “heat radiation operation”
When the difference between the refrigerant cooling effects LT of A and 2B is equal to or greater than the set difference ΔLT, the heat source heat exchanger serving as a heat-effect heat exchanger having a low effect is supplied with a heat-radiation source (that is, may act as a heating source). A control means Y for stopping the supply of a certain heat radiation source is configured.

In the switching control of b in the heat collection operation, when the supply of the water collection source G2 to the second heat source heat exchanger 2B, which is a heat collection heat exchanger having a low effect, is stopped, the stagnant water collection is stopped. Since the heat source G2 may freeze around the second heat source heat exchanger 2B, the water collection heat source G2 stagnant from around the second heat source heat exchanger 2B due to the switching control of b.
It is advisable to carry out an operation of discharging water (so-called water removal), or to take anti-freezing measures such as employing brine (antifreeze solution) as the water heat source G1.

[Other Examples] Next, other examples will be listed. Of the heat collecting operation and the heat radiating operation in the above-described embodiment, the heat radiating operation may not be performed, and only the heat collecting operation with the control shown in the flowchart of FIG. 3 may be performed. Also,
The heat collecting operation may not be performed, and only the heat radiation operation with the control shown in the flowchart of FIG. 4 may be performed.

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 liquid, gas, and solid, and these heat-collecting sources are of the same kind. It may be a different one or a different one. Similarly, the first and second radiation heat exchangers 2
The individual heat radiation sources G1 and G2 used in A and 2B are liquid,
It may be either a gas or a solid, and these heat radiation sources may be the same kind or different kinds.

First and second flow path switching means K1, K2
Instead of being constituted by two bidirectional valves each capable of bidirectional operation as shown in the above-mentioned embodiment, one bidirectional valve capable of bidirectional operation as shown in (a) and (b) of FIG. Valves V5, V
It may be configured with 6.

Heat collecting source G1 used in the first heat collecting heat exchanger 2A
The refrigerant temperature increasing effect HT1 by the second heat collecting heat exchanger 2B and the refrigerant temperature increasing effect HT2 by the heat collecting source G2 used in the second heat collecting heat exchanger 2B are compared with each other by the detected temperature of each heat collecting source G1, G2 as in the above-described embodiment. Instead of determining based on t1 and t2, determination based on a plurality of detection state values of each heat collecting source G1 and G2 (for example, temperature t, humidity r, or specific enthalpy h), or each heat collecting source A determination form such as determination based on one or a plurality of detection state values of G1 and G2 and the detected flow rate of each heat collection source G1 and G2 may be adopted. Similarly, the level relationship between the refrigerant temperature lowering effect LT1 by the heat radiation source G1 used in the first heat radiation heat exchanger 2A and the refrigerant temperature lowering effect LT2 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, heat radiation sources G1, instead of the form based on t2
It is judged 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 and G2 and each heat radiation source. A determination form such as determination based on the detected flow rates of G1 and G2 may be adopted.

In the heat collecting operation, [HT1 ≧ HTT? ], [HT2 ≧ HTT? ]
A control form in which the part of is omitted may be adopted, and similarly,
In the heat radiation operation, [L
T1 ≧ LTT? ], [LT2 ≧ LTT? A control mode in which the part [] is omitted may be adopted.

In the above embodiment, each heat radiation source G1,
The sum of the refrigerant cooling capacities LQ1 and LQ2 of G2 is the first and second
By setting the operating condition that the total required cooling capacity LQQ of the heat source heat exchangers 2A, 2B is greater than or equal to
Although an appropriate subcooling degree sc is ensured, the subcooling degree sc is adjusted by adjusting the fan 5 and the pump 6 for the heat radiation source.
Control to adjust the supercooling degree to the target supercooling degree or to increase the subcooling degree by heat exchange between the evaporator outlet refrigerant and the refrigerant at the final stage of passage through the condenser. You may make it implement the control which adjusts to a target supercooling degree.

It should be noted that reference numerals are given in the claims for convenience of comparison with the drawings, but the present invention is not limited to the configurations of the accompanying drawings by the entry.

[Brief description of drawings]

FIG. 1 is a diagram showing a device configuration.

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

[Fig. 3] Control flowchart of heat collection operation

[Fig. 4] Control flowchart of heat radiation operation

FIG. 5: Mollier diagram showing the driving cycle

FIG. 6 is a Mollier diagram showing a driving cycle.

FIG. 7 is a diagram showing an apparatus configuration and a refrigerant flow switching mode of another embodiment.

FIG. 8 is a diagram showing a configuration of a conventional device.

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 collection source, heat radiation source, heat radiation source 2A, 2B heat collection heat exchanger, heat radiation heat exchanger, heat source heat exchanger 1 output heat exchanger 3 compressor 4 expansion means 7 circulation direction switching means K1, K2 flow Channel switching means re Outlet passage or inlet passage of expansion means rc Suction passage or discharge passage of compressor HT (HT1, HT2) Refrigerant temperature raising effect ΔHT Refrigerant temperature raising effect setting difference LT (LT1, LT2) Refrigerant Cooling effect ΔLT Refrigerant cooling effect setting difference X Judging means Y Control means

Claims (6)

[Claims] 1. An individual heat source (G1) as an evaporator,
A compression type heat pump in which first and second heat collecting heat exchangers (2A) and (2B) for heating the flowing refrigerant by (G2) are connected in series, and the outlet flow path (of the expansion means (4) ( re) to the first and second
First flow path switching means (K) selectively connected to one end and the other end of the series combination of the heat collection heat exchangers (2A) and (2B).
1) and the suction flow path (rc) of the compressor (3) are selectively connected to one end and the other end of the series combination of the first and second heat collecting heat exchangers (2A) and (2B). Second flow path switching means (K2)
And a high-efficiency heat-collection heat exchanger in which the first and second heat-collection heat exchangers (2A) and (2B) have a higher refrigerant temperature increasing effect (HT) due to the heat-collection source used than the other. Determination means (X) for determining a heat collecting heat exchanger having a low effect in which the refrigerant temperature increasing effect (HT) by the used heat collecting source is lower than 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 order from the low-effect heat collection heat exchanger to the high-effect heat collection heat exchanger. The first and second flow path switching means (K1), (K
A compression heat pump provided with a control means (Y) for switching and controlling 2). 2. The determining means (X) determines the low-effect and high-effect heat-collecting heat exchangers, and the refrigerant temperature-raising effect (HT) of these heat-collecting heat exchangers (2A), (2B).
1) and (HT2) are configured to determine whether or not the difference is equal to or greater than a set difference (ΔHT), and the control means (Y), based on the determination result, both heat collection heat exchangers (2A). , (2B) refrigerant heating effect (HT
The compression heat pump according to claim 1, wherein when the difference between (1) and (HT2) is equal to or larger than a set difference (ΔHT), the supply of the heat collection source to the low-effect heat collection heat exchanger is stopped. 3. An individual heat source (G1) as a condenser,
A compression type heat pump in which first and second radiant heat exchangers (2A) and (2B) for cooling the flowing refrigerant by (G2) are connected in series, and the inlet flow path (re) of the expansion means (4) is ) Is the first and second
First flow path switching means (K) selectively connected to one end and the other end of the series set of the radiant heat exchangers (2A) and (2B).
1) and the discharge flow path (rc) of the compressor (3) are selectively connected to one end and the other end of the series combination of the first and second radiant heat exchangers (2A) and (2B). Second flow path switching means (K2)
A high-efficiency heat radiation heat exchanger in which the refrigerant cooling effect (LT) by the heat radiation source used is higher than the other in the first and second heat radiation heat exchangers (2A), (2B). Judgment means (X) for judging a heat-refrigerant cooling effect (LT) by the heat source which is lower than that of the other one
Based on the determination result of the determination means (X), the refrigerant to be condensed discharged from the compressor (3) flows in the order of the low-effect heat radiation heat exchanger to the high-effect heat radiation heat exchanger. So that the first and second flow path switching means (K1), (K
A compression heat pump provided with a control means (Y) for switching and controlling 2). 4. The judging means (X) judges the low-effect and high-effect radiant heat exchangers, and the refrigerant cooling effect (LT) of these radiant heat exchangers (2A), (2B).
1), (LT2) is configured to determine whether or not the difference is equal to or greater than the set difference (ΔLT), the control means (Y), based on the result of this determination, both the heat radiation heat exchanger (2A), Refrigerant cooling effect of (2B) (LT
4. The compression heat pump according to claim 3, wherein when the difference between 1) and (LT2) is equal to or greater than a set difference ([Delta] LT), the supply of the heat radiation source to the low heat radiation heat exchanger is stopped. 5. A first and a second heat source heat exchangers (2A), (2B) for heating or cooling the flowing refrigerant by individual heat-radiation sources (G1), (G2) are connected in series, A compressor (3), an output heat exchanger (1), an expansion means (4), the first and second heat source heat exchangers (2A), (2)
The output heat exchanger (1) is made to function as a condenser, and the first and second heat source heat exchangers (2A) and (2B) are circulated in the order of the series combination of B) and the heat collection heat exchanger. Heat collection operation to function as an evaporator as a refrigerant, a refrigerant (3), a series combination of the first and second heat source heat exchangers (2A) and (2B), the expansion means (4), and the output heat. The output heat exchanger (1) is caused to function as an evaporator by circulating the heat in the order of the exchanger (1), and the first and second heat source heat exchangers (2A),
Circulation direction switching means (7) for switching the operating state between the heat radiation operation in which (2B) functions as a heat radiation heat exchanger and the condenser function.
And a flow path (re) which becomes the outlet flow path of the expansion means (4) in the heat collection operation and becomes the inlet flow path of the expansion means (4) in the heat radiation operation. Exchanger (2
A) and (2B), a first flow path switching means (K1) that is selectively connected to one end and the other end of the series set, and a suction flow path of the compressor (3) in heat collection operation, In addition, in the heat radiation operation, the flow path (rc) that is the discharge flow path of the compressor (3) is connected to the first and second heat source heat exchangers (2).
A), a second flow path switching means (K2) that is selectively connected to one end and the other end of the series combination of (2B), and in the heat collecting operation, the first and second heat source heat exchangers ( Two
Regarding A) and (2B), a heat source heat exchanger that becomes a highly effective heat collection heat exchanger in a situation where the refrigerant temperature raising effect (HT) by the used heat radiation source is higher than the other, and the refrigerant rise by the used heat radiation source. In a situation where the temperature effect (HT) is lower than the other, it is determined that the heat source heat exchanger is a heat collecting heat exchanger having a low effect, and in the heat radiation operation, the first and second heat source heat exchangers (2A). , (2
Regarding B), the cooling effect of the refrigerant by the used heat radiation source (L
A heat source heat exchanger that becomes a highly effective radiant heat exchanger when T) is higher than the other, and a less effective radiant heat exchanger when the refrigerant cooling effect (LT) by the used heat radiating source is lower than the other. Determination means (X) for determining the heat source heat exchanger, and based on the determination result of the determination means (X), the evaporation target refrigerant that has passed through the expansion means (4) in the heat collection operation is Condensation discharged from the compressor (3) in such a manner that the heat source heat exchanger serving as the heat collecting heat exchanger flows in the order of the heat source heat exchanger serving as the highly effective heat collecting heat exchanger, and in the heat radiation operation. In order for the target refrigerant to flow in the order of the heat source heat exchanger to be the high effect heat radiation heat exchanger from the heat source heat exchanger to be the low effect heat radiation heat exchanger, in each of the heat collection operation and the heat radiation operation. The first and second flow path switching means (K1), (K2)
A compression heat pump provided with a control means (Y) for switching control. 6. The determining means (X) determines the heat source heat exchangers that will be the low-effect and high-effect heat collecting heat exchangers in the heat collecting operation, and the heat source heats as these heat collecting heat exchangers. Refrigerant temperature raising effect (HT) of the exchangers (2A) and (2B)
1), it is determined whether or not the difference between (HT2) is a set difference (ΔHT) or more, and in heat dissipation operation, the heat source heat exchanger to be the low and high effects heat dissipation heat exchanger is determined. , A heat source heat exchanger (2
A), (2B) refrigerant cooling effect (LT1), (LT2)
Of the heat source heat exchangers (2A) and (2B) in the heat collection operation based on the result of this determination. When the difference between the refrigerant temperature increasing effects (HT1) and (HT2) in (1) is equal to or greater than the set difference (ΔHT), the supply of the heat collection and radiation source to the heat source heat exchanger, which is the heat collection heat exchanger with low effect, is stopped. In the heat radiation operation, when the difference between the refrigerant cooling effects (LT1) and (LT2) of the two heat source heat exchangers (2A) and (2B) is equal to or more than the set difference (ΔLT), the heat radiation heat exchange with the low effect is performed. The compression type heat pump according to claim 5, wherein the supply of the heat radiation source to the heat source heat exchanger that serves as a container is stopped.