JPH11211149A - Heat transfer device - Google Patents

Abstract

(57) [Summary] [PROBLEMS] In a heat-driven heat transfer device, when starting,
Even if the liquid refrigerant in the main refrigerant circuit does not exist in the heating heat exchanger, the apparatus can be started smoothly. SOLUTION: A liquid pipe (37, 38) of a transfer circuit (C) having two tanks (T1, T2) and a main liquid pipe (2, 2) of a use side circuit (B) are provided.
5,26). In the tanks (T1, T2), a heating heat exchanger (35) that generates a high pressure by evaporating the liquid refrigerant and a cooling heat exchanger (36) that generates a low pressure by condensing the gas refrigerant are connected to the tanks (T1, T2). ). The cooling heat exchanger (36) is located above the heating heat exchanger (35). Cooling heat exchanger (36)
The liquid supply pipe (33) and the liquid recovery pipe (34) of the heating heat exchanger (35) are connected by a starting liquid pipe (50). When the cooling heat exchanger (36) and the heating heat exchanger (35) are at the same pressure, such as during startup, the refrigerant condensed in the cooling heat exchanger (36) is supplied to the heating heat exchanger (35). Is done.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a heat transfer device, and more particularly to an improvement in a heat transfer device for circulating a refrigerant without using a mechanical pump.

[0002]

2. Description of the Related Art Conventionally, heat transfer apparatuses have been disclosed in
As disclosed in Japanese Patent No. 178217, a tank is provided for storing a liquid refrigerant, and the inside of the tank is pressurized and the liquid refrigerant in the tank is pushed out to the main refrigerant circuit, while the inside of the tank is depressurized to reduce the pressure in the main refrigerant circuit. There is a type in which a liquid refrigerant is recovered in a tank, thereby enabling circulation of the refrigerant without using a pump.

Specifically, as shown in FIG. 4, this heat transfer device is provided with a pair of tanks (t1, t2) for storing a liquid refrigerant in a main refrigerant circuit (b) while a cooling heat exchanger ( A driving refrigerant circuit (c) for performing a vapor compression refrigeration cycle is provided, which includes d) and a heating heat exchanger (e). Further, an indoor heat exchanger (h) and a heat source (a) are connected to the main refrigerant circuit (b). In the driving refrigerant circuit (c), the refrigerant circulates,
In the cooling heat exchanger (d) and the heating heat exchanger (e), heat is exchanged between the refrigerant in the driving refrigerant circuit (c) and a part of the refrigerant in the main refrigerant circuit (b). Thereby, in the heating heat exchanger (e),
The liquid refrigerant in the main refrigerant circuit (b) is heated and evaporated by the refrigerant in the driving refrigerant circuit (c), and a high pressure is generated. On the other hand, in the cooling heat exchanger (d), the gas refrigerant in the main refrigerant circuit (b) is cooled and condensed by the refrigerant in the driving refrigerant circuit (c), and a low pressure is generated.

Then, the high pressure generated in the heating heat exchanger (e) is applied to the first tank (t1) to pressurize the first tank (t1).
Extrudes liquid refrigerant from At the same time, the low pressure generated in the cooling heat exchanger (d) is applied to the second tank (t2) to reduce the pressure, and the liquid refrigerant is collected in the tank (t2). Thereby, the circulation operation of the refrigerant in the main refrigerant circuit (b) is obtained. And, by the refrigerant flowing through the main refrigerant circuit (b), the heat source (a)
Is transferred to the indoor exchanger (h) and is used for indoor air conditioning by the indoor heat exchanger (h). Furthermore,
When the liquid refrigerant in the first tank (t1) runs out, the first tank (t1) is depressurized and simultaneously switched to pressurize the second tank (t2) to continuously obtain the refrigerant circulation operation. Like that. The main refrigerant circuit (b) includes a plurality of solenoid valves (f, f,...) And check valves (g, g.
Is provided.

In the heat transfer apparatus shown in FIG. 4, the tanks (t1, t2) are connected in parallel, and the pressure can be increased and reduced by the heating heat exchanger (e) and the cooling heat exchanger (d). A small auxiliary tank (i) is provided. The pressurizing operation and the depressurizing operation on the auxiliary tank (i) are repeated by the heating heat exchanger (e) and the cooling heat exchanger (d). That is, the operation of recovering a part of the liquid refrigerant extruded from one of the tanks into the auxiliary tank (i) and the operation of collecting the recovered liquid refrigerant into the heat exchanger (e).
Is repeated. As a result, a situation in which the liquid refrigerant does not exist in the heating heat exchanger (e) is avoided, and a continuous pressurizing operation for one of the tanks can be performed.

[0006]

However, in the above-mentioned conventional heat transfer device, when the liquid refrigerant of the main refrigerant circuit (b) does not exist in the heating heat exchanger (e) at the time of starting, the heating is performed. The high pressure cannot be generated in the heat exchanger (e). That is, since a sufficient pressure difference is not generated in the main refrigerant circuit (b), the refrigerant cannot be circulated and the starting operation becomes impossible.

Further, when the auxiliary tank (i) is provided as described above, even if the refrigerant is condensed in the cooling heat exchanger (d), the pressing force by the heating heat exchanger (e) cannot be obtained. For,
The liquid refrigerant is not pushed out of one tank and the auxiliary tank
The liquid refrigerant cannot be introduced into (i). For this reason,
The liquid refrigerant cannot be supplied from the auxiliary tank (i) to the heating heat exchanger (e), and the starting operation cannot be performed because the function of the auxiliary tank (i) cannot be obtained. That is, even when the auxiliary tank (i) for supplying the liquid refrigerant to the heating heat exchanger (e) is provided, the starting operation cannot be performed in a situation where the pressure is not obtained.

The present invention has been made in view of the above point, and an object of the present invention is to ensure that a liquid refrigerant for generating high pressure is present in a heating heat exchanger at the time of startup.
The purpose is to avoid inability to start.

[0009]

SUMMARY OF THE INVENTION According to the present invention, there is provided a heat transfer apparatus which obtains a circulation driving force of a refrigerant by applying a pressure generated by evaporating the liquid refrigerant to a tank capable of storing the liquid refrigerant. The apparatus is configured to be capable of supplying a liquid refrigerant for generating high pressure to a pressurizing means (heating heat exchanger).

More specifically, the first solution taken by the present invention is, as shown in FIG. 1, a utilization side circuit (B) and a transportation circuit (C).
And a heat transfer device comprising: The use side circuit (B) has a main liquid pipe between the heat source side heat exchanger (22) and the use side heat exchanger (21).
The refrigerant circulates through (25, 26) and the main gas pipe (27) to carry out heat transfer. Further, the transport circuit (C) is connected to the main liquid pipe (25, 26) of the use side circuit (B) and is capable of storing a liquid refrigerant (T1, T2), and the tank means (T1 , T2) to the gas pipe (3
1), the liquid refrigerant is heated and evaporated to generate a high pressure, and the high pressure is applied to the tank means (T1, T2) via the gas pipe (31) to cause the tank means (T1, T2) a pressurizing means (35) for extruding the refrigerant to the use side circuit (B), and a liquid pipe for recovering the liquid refrigerant to the pressurizing means (35) using the pressing force from the pressurizing means (35) (34), and the pressure acting on the tank means (T1, T2) generates a refrigerant circulation driving force in the utilization side circuit (B) and pressurizes the liquid pipe (34) from the pressure means (35). The liquid refrigerant collected in step (1) contributes to the generation of high pressure. When the heat transfer device is started, the liquid piping in the transfer circuit (C) is set so that the liquid refrigerant for generating high pressure is present in the pressurizing means (35).
A starting liquid pipe (50) capable of supplying the liquid refrigerant of one of the pipes other than (34) and the utilization side circuit (B) to the pressurizing means (35) is provided.

According to this specific matter, by the action on the high-pressure tank means (T1, T2) generated by the pressurizing means (35), the refrigerant is transferred from the tank means (T1, T2) to the use side circuit (B). Extrusion is performed, and the circulation driving force of the refrigerant in the use side circuit (B) is obtained. By this refrigerant circulation, the heat of the heat source side heat exchanger (22) is transferred to the use side heat exchanger (21).

On the other hand, when the apparatus is started, the transfer circuit (C)
Alternatively, since the liquid refrigerant of the use side circuit (B) is supplied to the pressurizing means (35) via the starting liquid pipe (50), the liquid refrigerant for generating high pressure is supplied to the pressurizing means (35) when the apparatus is started. The situation where is not present is avoided. That is, the liquid refrigerant for generating the high pressure can be reliably present in the pressurizing means (35).

The second solution is also a heat transfer device having a use side circuit (B) and a transfer circuit (C) as shown in FIG. The use side circuit (B) is the same as that of the above-mentioned first solving means. The transport circuit (C) includes a tank means (T1, T1) in addition to the pressurizing means (35) similar to the first solving means described above.
2) is connected to the gas pipe (32) through a gas pipe (32) to cool and condense the gas refrigerant, thereby generating a low pressure and applying the low pressure to the gas pipe (3).
2) through the tank means (T1, T2) through the use side circuit (B)
Pressure reducing means (3) for collecting the refrigerant from the tank means (T1, T2)
6). For this heat transfer device, at startup, the liquid refrigerant condensed in the pressure reducing means (36) can be supplied to the pressure means (35) so that the liquid refrigerant for generating high pressure is present in the pressure means (35). A configuration is provided in which a starting liquid pipe (50) is provided.

According to this specific matter, the high-pressure tank means generated by the pressurizing means (35) and the low-pressure tank means generated by the depressurizing means (36)
By the action on (T1, T2), the refrigerant is pushed out from the tank means (T1, T2) to the use side circuit (B) and the refrigerant is recovered from the use side circuit (B) to the tank means (T1, T2). Is performed and the user side circuit
The circulation driving force of the refrigerant in (B) is obtained. By this refrigerant circulation, the heat of the heat source side heat exchanger (22) is transferred to the use side heat exchanger (21). When the apparatus is started, the liquid refrigerant condensed in the pressure reducing means (36) is supplied to the pressurizing means (35) via the starting liquid pipe (50). The situation in which no liquid refrigerant for generation is present is avoided. In other words, the liquid refrigerant for generating high pressure is
Can reliably exist.

According to a third aspect of the present invention, in the second aspect, the pressurizing means (35) and the depressurizing means (36) are connected to a liquid pipe (34).
(33) to the tank means (T1, T2).
Further, the pressure reducing means (36) is located above the pressure applying means (35), and one end of the starting liquid pipe (50) is connected to the liquid pipe (3) of the pressure reducing means (36).
3), and the other end is connected to the liquid pipe (34) of the pressurizing means (35).

According to this specific matter, the supply of the liquid refrigerant from the pressure reducing means (36) to the pressurizing means (35) is carried out by utilizing a height difference (head difference) of the arrangement position of these means. .

A fourth means for solving the problem is, as shown in FIG. 3, a heat transfer device provided with a use side circuit (B) and a transfer circuit (C). The use side circuit (B) is the same as that of the above-mentioned first solving means. The transport circuit (C) includes a pressurizing means (35) similar to the first solving means described above. With respect to this heat transfer device, while the heat source side heat exchanger (22) is positioned above the pressurizing means (35), at the time of startup, the pressurizing means (35) is such that a liquid refrigerant for generating high pressure exists in the pressurizing means (35). To the heat source side heat exchanger by connecting the pressurizing means (35) and the main liquid pipe (26) of the utilization side circuit (B).
A starting liquid pipe (50) for supplying the liquid refrigerant of (22) to the pressurizing means (35) is provided.

According to this specific matter, the heat source side heat exchanger (22)
Is supplied to the pressurizing means (35) by the starting liquid pipe (50), so that the liquid refrigerant is supplied to the pressurizing means (35) when the apparatus is started, as in the case of the first solving means described above. The situation where no refrigerant is present is avoided.

A fifth solution is the reverse of the first, second or fourth solution, wherein only the flow of the liquid refrigerant toward the pressurizing means (35) is permitted through the starting liquid pipe (50). Stop valve (CV-
6) is provided.

According to a sixth aspect of the present invention, in the fourth aspect, an equalizing pipe (51) for equalizing the heat source side heat exchanger (22) and the pressurizing means (35) is provided. An opening / closing valve (SV) is provided in the pressure equalizing pipe (51), and by opening the opening / closing valve (SV), the heat source side heat exchanger (22) and the pressurizing means (35) are equalized, and the heat source side The liquid refrigerant of the heat exchanger (22) is supplied to the pressurizing means (35).

According to a seventh aspect of the present invention, in the first, second, or fourth aspect, the starting liquid pipe (50) is allowed to introduce a liquid refrigerant into the pressurizing means (35) by an opening operation. The opening and closing valve is provided.

By these specific items, the operation of supplying the liquid refrigerant to the pressurizing means (35) can be performed well. That is, the fifth solution means can prevent the liquid refrigerant from flowing backward through the starting liquid pipe (50). In the sixth and seventh solutions, the liquid refrigerant can be introduced into the pressurizing means (35) only when the on-off valve is opened.

According to an eighth aspect of the present invention, in the above sixth and seventh aspects, the on-off valve is opened only at the time of startup to allow the introduction of the liquid refrigerant to the pressurizing means (35).

According to this specific matter, the liquid refrigerant always exists in the pressurizing means (35) at the time of starting.

A ninth solving means is the detecting means (Th) according to the sixth and seventh solving means, which is capable of detecting whether or not the high-pressure generating liquid refrigerant is present in the pressurizing means (35). Is provided. At startup, the on-off valve is opened when the detecting means (Th) detects that the liquid refrigerant for generating high pressure does not exist in the pressurizing means (35).

Due to this particular matter, the operation of introducing the liquid refrigerant to the pressurizing means (35) is performed only in a state in which the start-up failure state occurs, that is, only when the liquid refrigerant is not present in the pressurizing means (35). Will be performed.

[0027]

Embodiment 1 Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. As shown in FIG. 1, the air conditioner conveys hot and cold heat generated in the heat source side circuit (A) as a heat source to an indoor heat exchanger (21) as a use side heat exchanger to perform air conditioning. The heat source side circuit (A), the use side circuit (B), the transfer circuit (C), and the drive circuit (D).
And

First, the transfer circuit (C) provides a refrigerant transfer force to the use side circuit (B). The transfer side circuit (C) is filled with the use side refrigerant and the cooling heat exchanger (36) serving as a pressure reducing means. ), A heating heat exchanger (35) which is a pressurizing means, and a sub tank (ST),
First and second main tanks (T1, T2) as tank means are provided.

A gas supply pipe (31), which is a gas pipe, is connected to the upper end of the heating heat exchanger (35). This gas supply pipe (31) is branched into three branch pipes (31a, 31b, 31c), and each branch pipe (31a-31c) is an upper end of each main tank (T1, T2) and sub tank (ST). Connected individually. These branch pipes (31a to 31c) have first to third tank pressurizing solenoid valves (S
V-P1 to SV-P3) are provided. A liquid recovery pipe (34) as a liquid pipe according to the present invention is connected to a lower end of the heating heat exchanger (35). The liquid recovery pipe (34) is connected to the lower end of the sub tank (ST) to form a liquid pipe. The liquid recovery pipe (34) is provided with a check valve (CV-1) that allows only the outflow of the refrigerant from the sub tank (ST). Each main tank (T1, T2) is installed at a position lower than the cooling heat exchanger (36). Further, the sub tank (ST) is installed at a position higher than the heating heat exchanger (35).

On the other hand, a gas recovery pipe (32), which is a gas pipe, is connected to the upper end of the cooling heat exchanger (36). The gas recovery pipe (32) is branched into three branch pipes (32a to 32c), and each of the branch pipes (32a to 32c) is a branch pipe (31a to 31c) of the gas supply pipe (31).
connected to c). Thereby, the gas recovery pipes (32) are individually connected to the upper ends of the main tanks (T1, T2) and the sub tank (ST). These branch pipes (32a to 32c) are provided with first to third tank pressure reducing solenoid valves (SV-V1 to SV-V3). A liquid supply pipe (33), which is a liquid pipe, is connected to a lower end of the cooling heat exchanger (36). This liquid supply pipe
(33) is branched into two branch pipes (33a, 33b), and each branch pipe (33
a, 33b) are connected to the lower ends of the main tanks (T1, T2), respectively. The branch pipes (33a, 33b) are provided with check valves (CV-2, CV-2) that allow only recovery of the usage-side refrigerant to the main tanks (T1, T2).

A liquid pipe for recovery (38) and a liquid pipe for extrusion (37) are connected to each main tank (T1, T2).
The recovery liquid pipe (38) is branched into two branch pipes (38a, 38b), and each branch pipe (38a, 38b) is connected to a lower end of each main tank (T1, T2). Each of these branch pipes (38a, 38
b) is provided with check valves (CV-5, CV-5) that allow only refrigerant to flow into the main tanks (T1, T2). on the other hand,
The extrusion liquid pipe (37) is branched into three branch pipes (37a, 37b, 37c), and each of the branch pipes (37a to 37c) is a branch pipe (38a, 38b) of the recovery liquid pipe (38) and By connecting to the liquid recovery pipe (34), it is connected to the lower end of each main tank (T1, T2) and sub tank (ST). Among these branch pipes (37a to 37c), branch pipes (37a, 37b) connected to each main tank (T1, T2) include:
While a check valve (CV-3) that allows only the outflow of the refrigerant from the lower end of the main tank (T1, T2) is provided, a branch pipe (37c) connected to the sub tank (ST) includes the sub tank (ST). A check valve (CV-4) is provided to allow only the use-side refrigerant to flow into the pump. Further, a driving circuit is provided in the above-mentioned extrusion liquid pipe (37).
A radiating heat exchanger (42) for exchanging heat with (D) is connected. Also, the drive circuit (D) is connected to the collection liquid piping (38).
And an endothermic heat exchanger (44) for exchanging heat with the heat exchanger.

Next, the use side circuit (B) is a heat source side heat exchanger (2) that exchanges heat with the heat source side circuit (A) as a heat source.
2), an indoor heat exchanger (21), and a use-side electric expansion valve (23) are a refrigerant circuit connected by a refrigerant pipe (8). Specifically, the liquid side of the indoor heat exchanger (21) is connected to the usage-side electric expansion valve (2
While 3) is connected, the gas side of the indoor heat exchanger (21) is connected to the heat source side heat exchanger (22). In addition, one end of the use-side electric expansion valve (23) and one end of the heat source-side heat exchanger (22) are connected via the use-side four-way switching valve (24) to the recovery liquid pipe of the transfer circuit (C). (38) and an extruding liquid pipe (37) are switchably connected. And a refrigerant pipe (8) connecting the use side electric expansion valve (23) and the use side four-way switching valve (24), a heat source side heat exchanger (22) and a use side four way switching valve (24) And a refrigerant pipe connecting the indoor heat exchanger (21) and the heat source side heat exchanger (22).
(8) is configured as a main gas pipe (27).

The driving circuit (D) is a transport circuit.
(C) A circuit for heating and cooling the use-side refrigerant, which is configured to perform a vapor compression refrigeration cycle. The driving circuit (D) includes a driving compressor (41), a heating heat exchanger (35), and a radiating heat exchanger (42), and a downstream side of the radiating heat exchanger (42) is branched. , One of which is a drive electric expansion valve
(43) and the cooling heat exchanger (36), the other end of which is an electric expansion valve for heat absorption.
(45) and the endothermic heat exchanger (44) are connected to each other.
The downstream sides of these heat exchangers (36, 44) are merged and connected to the suction side of the driving compressor (41).

The heating heat exchanger (35) and the cooling heat exchanger (3)
In 6), heat is exchanged between the drive refrigerant of the drive circuit (D) and the use-side refrigerant of the transfer circuit (C). And the heating heat exchanger (3
In 5), the drive refrigerant of the drive circuit (D) is condensed, and the use-side refrigerant of the transfer circuit (C) is heated and evaporated. On the other hand, in the cooling heat exchanger (36), the drive refrigerant of the drive circuit (D) evaporates, and the use-side refrigerant of the transfer circuit (C) is cooled and condensed. In the endothermic heat exchanger (44), heat is exchanged between the drive refrigerant of the drive circuit (D) and the use-side refrigerant recovered in each main tank (T1, T2) of the transfer circuit (C). Then, the use-side refrigerant collected in each of the main tanks (T1, T2) is cooled to avoid generation of flash gas, and the main tanks (T1, T2) are cooled.
Only the liquid-side use-side refrigerant is recovered to T2). On the other hand, in the heat radiation heat exchanger (42), the driving circuit
(D) drive refrigerant and main tanks (T1,
The use side liquid refrigerant extruded from T2) performs heat exchange.
Then, the excess heat generated in the driving circuit (D) is radiated.

The heat source side circuit (A) includes a heat source side compressor (11)
, A heat source side four-way switching valve (14), an outdoor heat exchanger (12), a heat source side electric expansion valve (13), and a heat source side heat exchanger (22).
It is connected in (8) and is configured as a closed circuit for performing a vapor compression refrigeration cycle. Further, the heat source side four-way switching valve (14)
Thus, the circulation direction of the heat source side refrigerant in the heat source side circuit (A) is reversible, and the heat source side heat exchanger (22) generates hot and cold heat.

As a feature of this embodiment, the liquid supply pipe (33) and the liquid recovery pipe (34) of the transfer circuit (C) are connected by a starting liquid pipe (50). The starting liquid pipe (50) is provided with a check valve (CV-6) that allows only the flow of the liquid refrigerant from the liquid supply pipe (33) to the liquid recovery pipe (34). That is, when the internal pressure of the liquid supply pipe (33) is equal to the internal pressure of the liquid recovery pipe (34), the cooling heat exchanger (36) and the heating heat exchanger (3
Using the height difference (head difference) with the cooling heat exchanger (3)
The liquid refrigerant in 6) is configured to be introduced into the heating heat exchanger (35) via the starting liquid pipe (50) and the liquid recovery pipe (34).

-Operating operation- Next, the operating operation of the present apparatus during the cooling operation will be described. During this operation, first, each of the electric expansion valves (13, 23, 4
3, 45) is adjusted to a predetermined opening. In addition, each solenoid valve (SV-P1,
SV-P2, ...) is described from the following state. First
Pressurized solenoid valve (SV-P1) of main tank (T1), sub tank (SV
The pressurizing solenoid valve (SV-P3) of T) and the depressurizing solenoid valve (SV-V2) of the second main tank (T2) are open. On the other hand, the pressurized solenoid valve (SV-P2) of the second main tank (T2) and the first main tank (T1)
Pressure reducing solenoid valve (SV-V1) and sub tank (ST) pressure reducing solenoid valve (SV
-V3) is closed. The use-side four-way switching valve (24) and the heat source-side four-way switching valve (14) are switched as shown by a solid line in FIG.

In this state, in the heat source side circuit (A), the high-temperature and high-pressure heat source side gas refrigerant discharged from the heat source side compressor (11) is supplied to the outdoor heat exchanger ( In 12), heat exchange is performed with the outside air to condense. Thereafter, the heat-source-side refrigerant is depressurized by the heat-source-side electric expansion valve (13), flows into the heat-source-side heat exchanger (22), and exchanges heat with the use-side refrigerant in the use-side circuit (B). Evaporates and returns to the heat source side compressor (11), and such a circulating operation is repeated.

Further, in the driving circuit (D), as shown by the two-dot chain line arrow in FIG. 2, the high-temperature and high-pressure driving gas refrigerant discharged from the driving compressor (41) is heated by a heating heat exchanger ( 35). The driving refrigerant flowing into the heating heat exchanger (35)
The heat exchange with the use side refrigerant of the transfer circuit (C) is performed, and a part thereof is condensed to heat the use side refrigerant of the transfer circuit (C). After that, the driving refrigerant partially condensed in the heating heat exchanger (35) flows to the heat radiation heat exchanger (42), and from the first main tank (T1) to the use side circuit (B), the use side liquid refrigerant. Heat exchange with
Everything condenses. This condensed driving refrigerant is branched,
One of the pressures is reduced by the drive electric expansion valve (43), and then flows into the cooling heat exchanger (36). The drive refrigerant flowing into the cooling heat exchanger (36) exchanges heat with the use-side refrigerant of the transfer circuit (C), evaporates, and cools the use-side refrigerant. The other drive refrigerant flows into the endothermic heat exchanger (44) after being decompressed by the heat absorbing electric expansion valve (45). The driving refrigerant that has flowed into the heat absorption heat exchanger (44) exchanges heat with the utilization-side refrigerant of the transfer circuit (C), evaporates, and merges with the driving refrigerant that has passed through the cooling heat exchanger (36). Then, it is sucked into the driving compressor (41). Such a circulating operation is performed in the driving circuit (D).

In the transfer circuit (C), in the heating heat exchanger (35), the refrigerant on the use side of the transfer circuit (C) evaporates to generate high pressure. This high pressure is applied to the branch pipe (31a) of the gas supply pipe (31).
Is supplied to the first main tank (T1), and the first main tank (T1) is pressurized. Therefore, the first main tank (T
The use-side liquid refrigerant stored in 1) is pushed out of the first main tank (T1) as shown by the solid arrow in FIG. Then, the flow of the use-side refrigerant pushed out of the first main tank (T1) is controlled by the check valves (CV-3, CV-5), and flows into the extruding liquid pipe (37). Further, the use-side refrigerant flowing through the extruding liquid pipe (37) exchanges heat with the driving refrigerant of the driving circuit (D) in the heat radiation heat exchanger (42) to condense the driving refrigerant.

Further, in the cooling heat exchanger (36), the refrigerant on the use side of the transfer circuit (C) is condensed to generate a low pressure. This low pressure acts on the second main tank (T2) via the branch pipe (32b) of the gas recovery pipe (32), and the pressure of the second main tank (T2) is reduced. Further, the flow direction of the refrigerant in the recovery liquid pipe (38) is controlled by each check valve (CV-3, CV-5). For this reason, the use-side liquid refrigerant that has passed through the endothermic heat exchanger (44) is collected in the second main tank (T2) as indicated by the solid arrow in FIG.

On the other hand, in the use side circuit (B), the use side refrigerant pushed out of the first main tank (T1) and flowing through the extruding liquid pipe (37) passes through the use side four-way switching valve (24). Main liquid piping (2
Flow to 5). The use-side refrigerant flowing through the main liquid pipe (25)
After passing through the use-side electric expansion valve (23), the indoor heat exchanger (21) exchanges heat with room air and evaporates to cool the room air. The use-side refrigerant evaporated in the indoor heat exchanger (21) is
It flows through the main gas pipe (27) and condenses in the heat source side heat exchanger (22),
Thereafter, it flows through the main liquid pipe (26), and flows into the endothermic heat exchanger (44) via the use-side four-way switching valve (24). Then, the use-side refrigerant that has flowed into the endothermic heat exchanger (44) flows through the collection liquid pipe (38) and is collected in the second main tank (T2).

In the transport circuit (C), the sub tank (S
T) is equalized with the heating heat exchanger (35). Therefore, as shown by a solid line arrow in FIG. 2, the use side liquid refrigerant in the sub tank (ST) is supplied to the heating heat exchanger (35) through the liquid recovery pipe (34). The supplied usage-side liquid refrigerant is supplied to the heating heat exchanger.
It evaporates in (35) and contributes to pressurization in the first main tank (T1). Thereafter, when most of the use side liquid refrigerant in the sub tank (ST) is supplied to the heating heat exchanger (35), the sub tank (S
The pressurizing solenoid valve (SV-P3) of T) is closed, and the depressurizing solenoid valve (SV-V3) of the sub tank (ST) is opened. As a result, the pressure in the sub tank (ST) becomes low, and a part of the use-side refrigerant flowing through the extruding liquid pipe (37) is recovered as indicated by a broken arrow in FIG.

After performing such an operation for a predetermined time, the solenoid valves (SV-P1, SV-P2,...) Of the transfer circuit (C) are switched. That is, the pressurized solenoid valve (SV-P1) of the first main tank (T1), the second
Pressure reducing solenoid valve (SV-V2) of main tank (T2), sub tank (SV
Close the pressure reducing solenoid valve (SV-V3) of T). 2nd main tank
(T2) pressurized solenoid valve (SV-P2), first main tank (T1) depressurized solenoid valve (SV-V1), sub tank (ST) pressurized solenoid valve (SV-P3)
To release.

As a result, the internal pressure of the first main tank (T1) becomes low, and conversely, the internal pressure of the second main tank (T2) and the sub tank (ST) becomes high. For this reason, the use side liquid refrigerant pushed out from the second main tank (T2) circulates in the same manner as described above, and enters a refrigerant circulation state in which it is collected in the first main tank (T1). The use side liquid refrigerant is supplied to the heating heat exchanger (35). Also in this case, when most of the liquid refrigerant in the sub tank (ST) is supplied to the heating heat exchanger (35), the pressurizing solenoid valve (SV-P3) of the sub tank (ST) is closed, The decompression solenoid valve (SV-V3) of the sub tank (ST) is opened, and the refrigerant is collected in the sub tank (ST).

As described above, each of the solenoid valves (SV-P1, SV-P2,...) Performs a switching operation, and the refrigerant is pushed out of the first main tank (T1) and collected in the second main tank (T2). Behavior and
The operation in which the refrigerant is pushed out of the second main tank (T2) and collected in the second main tank (T2) is performed alternately. Then, the refrigerant circulates in the use side circuit (B), and the room is continuously cooled.

Next, the operation during the heating operation will be described. During this operation, first, the use-side four-way switching valve
(24) and the heat source side four-way switching valve (14) are switched as shown by the broken line in FIG.
3, 43, 45) and the solenoid valves (SV-P1, SV-P2, ...) are operated in the same manner as in the cooling operation.

In this state, the transport circuit (C) and the drive circuit
(D) operates in the same manner as in the cooling operation.

In the heat source side circuit (A), the heat source side compressor
The high-temperature and high-pressure heat source side gas refrigerant discharged from (11) exchanges heat with the use side refrigerant of the use side circuit (B) in the heat source side heat exchanger (22) and condenses. Thereafter, the heat-source-side refrigerant is reduced in pressure by the heat-source-side electric expansion valve (13), flows into the outdoor heat exchanger (12),
Here, heat exchange is performed with the outside air to evaporate, and the heat source side compressor (1
Returning to 1), such a circulating operation is repeated.

On the other hand, in the use side circuit (B), the use side refrigerant pushed out of the first main tank (T1) and flowing through the extruding liquid pipe (37) passes through the use side four-way switching valve (24). Main liquid piping (2
Flow to 6). The use-side refrigerant flowing through the main liquid pipe (26)
It is heated and evaporated in the heat source side heat exchanger (22). The evaporated use-side refrigerant flows into the indoor heat exchanger (21), condenses, and heats the indoor air. The condensed use-side refrigerant flows through the main liquid pipe (25), and the use-side four-way switching valve (24) and the collection liquid pipe
It flows through (38) and is collected in the second main tank (T2).

-Operation at Startup- Next, the operation at the start-up, which is an operation characteristic of the present embodiment, will be described. At the time of this startup, the heating heat exchanger (35)
In the state where the evaporating operation of the refrigerant and the condensing operation of the refrigerant in the cooling heat exchanger (36) have not been performed yet, the liquid supply pipe
The internal pressure of (33) is equal to the internal pressure of the liquid recovery pipe (34). For this reason, the use side liquid refrigerant in the cooling heat exchanger (36)
Heating heat exchanger via the starting liquid pipe (50) and the liquid recovery pipe (34)
(35). In other words, this heating heat exchanger (35)
A use-side liquid refrigerant for generating a high pressure is introduced therein.

From this state, the compressors (11, 41) of the heat source side circuit (A) and the driving circuit (D) are started, and the above-described air conditioning operation is started. At this time, in the heating heat exchanger (35), the use-side liquid refrigerant introduced from the starting liquid pipe (50) is heated and evaporated, and the evaporated use-side refrigerant contributes to pressurization of one tank. Will do. After this operation is started, a high pressure is generated in the heating heat exchanger (35) and a low pressure is generated in the cooling heat exchanger (36). For this reason, the internal pressure of the liquid recovery pipe (34) becomes higher than the internal pressure of the liquid supply pipe (33), and the starting liquid pipe (50) is provided with a check valve (CV-6). The supply of the use-side liquid refrigerant from the liquid supply pipe (33) to the liquid recovery pipe (34) is not performed.

According to the first embodiment, the starting liquid pipe (50) for introducing the use side refrigerant condensed in the cooling heat exchanger (36) to the heating heat exchanger (35). ) Is provided. For this reason, it is possible to avoid a situation in which the heating-side heat exchanger (35) does not have the liquid-phase use-side refrigerant at the time of startup and thus cannot be started. Therefore, starting failure can be avoided with a simple configuration, and the reliability of the device can be improved.

[0054]

Embodiment 2 of the present invention is different from Embodiment 1 in that the use side liquid refrigerant condensed in the cooling heat exchanger (36) is supplied to the heating heat exchanger (35). As shown in FIG. 3, the use side liquid refrigerant of the heat source side heat exchanger (22) is supplied to the heating heat exchanger (35). In this embodiment,
Only differences from the first embodiment will be described.
3, the same members as those in FIG. 1 are denoted by the same reference numerals, and description thereof will be omitted.

As shown in FIG. 3, the heating heat exchanger (35) is arranged below the heat source side heat exchanger (22). Also,
The main liquid pipe (26) of the use side circuit (B) and the liquid recovery pipe (34) of the transfer circuit (C) are connected by a starting liquid pipe (50). The starting liquid pipe (50) is connected to the liquid recovery pipe (3) from the main liquid pipe (26).
Check valve (C
V-6) is provided.

Further, the gas supply pipe (31) of the heating heat exchanger (35)
The main gas pipe (27) of the use side circuit (B) is connected by a pressure equalizing pipe (51). The pressure equalizing pipe (51) is provided with an electromagnetic valve (SV) as an on-off valve. In other words, this solenoid valve
(SV) is opened and the heating heat exchanger (35) and the heat source side heat exchanger (2
2), the use side liquid refrigerant in the heat source side heat exchanger (22) passes through the main liquid pipe (26), the starting liquid pipe (50), and the liquid recovery pipe (34). It is configured to be introduced into the heating heat exchanger (35).

-Operating operation- The operating operation of the air conditioner of this embodiment is performed in the same manner as in the first embodiment (see each arrow in FIG. 3).

In the starting operation of the present embodiment, the solenoid valve (SV) of the pressure equalizing pipe (51) is opened at the time of starting. With this, the heating heat exchanger (35) and the heat source side heat exchanger
(22) is equalized. This equalization allows the heat source side heat exchanger
(22) The use side liquid refrigerant in the main liquid pipe (26) and the starting liquid pipe (5
0) and a liquid recovery pipe (34) to be introduced into the heating heat exchanger (35). That is, a liquid-phase use-side refrigerant for generating a high pressure is introduced into the heating heat exchanger (35).

From this state, the compressors (11, 41) of the heat source side circuit (A) and the driving circuit (D) are started, and the air-conditioning operation similar to that of the first embodiment is started. Become. At this time, in the heating heat exchanger (35), the use-side liquid refrigerant introduced from the starting liquid pipe (50) is heated and evaporated, and the evaporated use-side refrigerant contributes to pressurization of one tank. Will do. After this operation is started, the pressure equalizing pipe (5
1) The solenoid valve (SV) is closed. Because of this, the heating heat exchanger
The high voltage generated in (35) will not be introduced into the use side circuit (B).

-Effects of the Second Embodiment- According to the second embodiment as well, it is possible to avoid a situation in which the heating-use heat exchanger (35) does not have the liquid-phase use-side refrigerant at the time of startup and thus cannot be started. it can. This allows
The reliability of the device can be improved.

[0061]

Modification of Embodiment 2 As a modification of Embodiment 2 described above, the operation of introducing the liquid refrigerant into the heating heat exchanger (35) only when the liquid refrigerant does not exist in the heating heat exchanger (35). Will be described.

As shown in FIG. 3, a discharge gas temperature sensor (Th) as detection means is provided on the discharge side of the driving compressor (41). If no liquid refrigerant is present in the heating heat exchanger (35), the amount of heat exchange between the driving refrigerant and the usage-side refrigerant in the heating heat exchanger (35) is insufficient, and the sensor (Th The temperature of the discharge gas detected by ()) reaches or exceeds a predetermined temperature.
Therefore, by opening the solenoid valve (SV) only when the discharge gas temperature reaches a predetermined temperature or higher, the heat source side heat exchanger (2
2) It is possible to prevent a start-up failure while avoiding a situation where the liquid refrigerant in the heating heat exchanger (35) is unnecessarily introduced into the heating heat exchanger (35).

In each of the embodiments described above, the case where the heat transfer device according to the present invention is applied to an air conditioner has been described. However, the present invention is not limited to this, and can be applied to other refrigeration devices. is there.

Further, a pair of main tanks (T1, T2) and 1
The case where the present invention is applied to a heat transfer device having three sub-tanks (ST) has been described.
The present invention is also applicable to a device having at least two main tanks, a device having no sub-tank, and a device having two or more sub-tanks.

Further, in the circuit configuration of each embodiment, a solenoid valve may be used as an on-off valve instead of the check valve (CV-6) as a valve provided in the starting liquid pipe (50). In this case, the solenoid valve is opened only at the time of startup, or at this startup, the solenoid valve is opened only when the liquid refrigerant is not present in the heating heat exchanger (35). When opening the solenoid valve according to the presence of this liquid refrigerant, unnecessarily heating the heat exchanger
The situation of introducing a liquid refrigerant into (35) can be avoided.

[0066]

As described above, according to the present invention, the following effects are exhibited. According to the first, second and fourth aspects of the present invention, the vaporizing of the liquid refrigerant by the pressurizing means (35) and the gas refrigerant by the depressurizing means (36) are performed on the tank (T1, T2) capable of storing the liquid refrigerant. For the heat transfer device that obtains the circulation driving force of the refrigerant by applying the pressure generated by the condensation of the heat transfer device, when the device is started, the liquid refrigerant for high pressure generation exists in the pressurizing means (35), A starting liquid pipe (50) capable of supplying a liquid refrigerant to the pressurizing means (35) was provided. For this reason, when starting the apparatus, it is possible to avoid a situation in which no liquid refrigerant for generating high pressure exists in the pressurizing means (35). As a result, the apparatus can be started satisfactorily and reliability can be improved.

According to the third aspect of the present invention, the pressurizing means (35) and the pressure reducing means (36) are connected to the tank means via the liquid pipes (34) and (33).
(T1, T2), and the pressure reducing means (36) is connected to the pressure applying means (3
5), one end of the starting liquid pipe (50) is connected to the liquid pipe (33) of the pressure reducing means (36), and the other end is connected to the pressure means (3).
5) Connected to the liquid pipe (34). For this reason, the supply of the liquid refrigerant from the pressure reducing means (36) to the pressurizing means (35) is performed using the height difference of the arrangement position of these means, and requires a special supply drive source. It is possible to supply the liquid refrigerant to the pressurizing means (35) without performing. Therefore, the effect according to the first aspect of the present invention can be obtained with a simple configuration.

In the invention according to claims 5 to 7, the pressurizing means (3
A valve was adopted so that the operation of supplying the liquid refrigerant to 5) could be performed well. That is, in the invention of claim 5, the check valve (CV-6) is provided in the starting liquid pipe (50), and in the invention of claim 7, the opening and closing valve is provided in the starting liquid pipe (50). Further, in the invention according to claim 6, in order to supply the liquid refrigerant to the pressurizing means (35), a pressure equalizing pipe capable of equalizing the pressure means (35) and the heat source side heat exchanger (22). (51), and an on-off valve (SV) is provided in the pressure equalizing pipe (51). For this reason, it is possible to avoid a situation in which the liquid refrigerant flows backward in the starting liquid pipe (50) or the liquid refrigerant is inadvertently supplied to the pressurizing means (35), and the pressurizing means (35)
The reliability of the liquid refrigerant supply operation with respect to the above can be improved.

According to the eighth and ninth aspects of the invention, the control operation of the on-off valve is specified. That is, in the invention according to claim 8, the on-off valve is opened only when the apparatus is started. According to the ninth aspect of the present invention, when the apparatus is started, the pressurizing means
When it is detected in (35) that no liquid refrigerant for generating high pressure is present, the on-off valve is opened. For this reason, it is possible to avoid supplying the liquid refrigerant to the pressurizing means (35) more than necessary.

[Brief description of the drawings]

FIG. 1 is a refrigerant circuit diagram of an air-conditioning apparatus according to Embodiment 1.

FIG. 2 is a refrigerant circuit diagram illustrating a refrigerant circulation operation of the air-conditioning apparatus of Embodiment 1.

FIG. 3 is a refrigerant circuit diagram of the air-conditioning apparatus according to Embodiment 2.

FIG. 4 is a refrigerant circuit diagram of an air conditioner using a conventional heat transfer device.

[Explanation of symbols]

 (B) User side circuit (C) Transport circuit (T1) First main tank (tank means) (T2) Second main tank (tank means) (21) Indoor heat exchanger (use side heat exchanger) (22) ) Heat source side heat exchanger (25,26) Main liquid pipe (27) Main gas pipe (31) Gas supply pipe (gas pipe) (32) Gas recovery pipe (gas pipe) (33) Liquid supply pipe (liquid pipe) (34) Liquid recovery pipe (liquid pipe) (35) Heating heat exchanger (pressurizing means) (36) Cooling heat exchanger (pressure reducing means) (50) Starting liquid pipe (51) Equalizing pipe (CV-6 ) Check valve (SV) Solenoid valve (open / close valve)

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Masahiro Oka 1304 Kanaoka-cho, Sakai-shi, Osaka Daikin Industries Inside Kanaoka Plant of Sakai Seisakusho Co., Ltd. (72) Inventor Yasushi Hori 1304 Kanaoka-cho, Sakai-shi, Osaka Daikin Industries, Ltd. Sakai Plant Kanaoka Factory

Claims (9)

[Claims] 1. A heat source side heat exchanger (22) and a use side heat exchanger (2).
1), the refrigerant circulates through the main liquid pipes (25, 26) and the main gas pipe (27) to transfer heat, and the main circuit (B) of the main circuit (B). Tank means (T1, T2) connected to the liquid pipes (25, 26) and capable of storing a liquid refrigerant;
(T1, T2) is connected via a gas pipe (31), a high pressure is generated by heating and evaporating the liquid refrigerant, and the high pressure is applied to the tank means (T1, T2) via the gas pipe (31). Pressurizing means (35) for operating the tank means (T1, T2) to push the refrigerant to the use side circuit (B), and pressurizing the liquid refrigerant by using the pressing force from the pressurizing means (35). Means (35) for recovering the liquid pipe (34), and the above-mentioned pressures acting on the tank means (T1, T2) to generate the refrigerant circulation driving force in the utilization side circuit (B) and to perform the liquid pipe
A heat transfer device provided with a transfer circuit (C) adapted to cause the liquid refrigerant recovered from (34) to the pressurizing means (35) to generate high pressure; The pressure means (35) pressurizes one of the pipes other than the liquid pipe (34) in the transfer circuit (C) and the utilization side circuit (B) so that the liquid refrigerant for generating high pressure exists in the transfer circuit (C).
A heat transfer device, characterized in that a start-up liquid pipe (50) that can be supplied to the apparatus is provided. 2. A heat source side heat exchanger (22) and a use side heat exchanger (2).
1), the refrigerant circulates through the main liquid pipes (25, 26) and the main gas pipe (27) to transfer heat, and the main circuit (B) of the main circuit (B). Tank means (T1, T2) connected to the liquid pipes (25, 26) and capable of storing a liquid refrigerant;
(T1, T2) is connected via a gas pipe (31), a high pressure is generated by heating and evaporating the liquid refrigerant, and the high pressure is applied to the tank means (T1, T2) via the gas pipe (31). A pressurizing means (35) for operating the tank means (T1, T2) to push out the refrigerant from the tank means (B) to the use side circuit (B), and connected to the tank means (T1, T2) via a gas pipe (32), The low pressure is generated by cooling and condensing the gas refrigerant, and the low pressure is applied to the tank means (T1, T2) via the gas pipe (32) to cause the tank means (B) to
(T1, T2) and a pressure reducing means (36) for recovering the refrigerant, and these pressures acting on the tank means (T1, T2) are used by the utilization side circuit.
(B) in the heat transfer device provided with a transfer circuit (C) for generating a circulating drive force of the refrigerant, at startup, such that the high-pressure generation liquid refrigerant is present in the pressurizing means (35), A heat transfer device comprising a start-up liquid pipe (50) capable of supplying the liquid refrigerant condensed in the pressure reducing means (36) to the pressurizing means (35). 3. The heat transfer device according to claim 2, wherein the pressurizing means (35) and the depressurizing means (36) are connected to the tank means (T1, T2) via the liquid pipes (34), (33), respectively. The pressure reducing means (36) is located above the pressurizing means (35), and one end of the starting liquid pipe (50) is connected to the liquid pipe (33) of the pressure reducing means (36). And a second end connected to the liquid pipe (34) of the pressurizing means (35). 4. A heat source side heat exchanger (22) and a use side heat exchanger (2).
1), the refrigerant circulates through the main liquid pipes (25, 26) and the main gas pipe (27) to transfer heat, and the main circuit (B) of the main circuit (B). Tank means (T1, T2) connected to the liquid pipes (25, 26) and capable of storing a liquid refrigerant;
(T1, T2) is connected via a gas pipe (31), a high pressure is generated by heating and evaporating the liquid refrigerant, and the high pressure is applied to the tank means (T1, T2) via the gas pipe (31). Pressurizing means (35) for operating the tank means (T1, T2) to push the refrigerant from the tank means (T1, T2) to the use side circuit (B), and the use side circuit (B ), A heat transfer device having a transfer circuit (C) for generating a circulating drive force of the refrigerant, wherein the heat source side heat exchanger (22) is located above the pressurizing means (35). On the other hand, at the time of startup, the pressurizing means (35) is connected to the main liquid pipe (26) of the use side circuit (B) so that the liquid refrigerant for generating high pressure exists in the pressurizing means (35). Heat source side heat exchanger (22)
Start-up liquid piping that can supply the liquid refrigerant to the pressurizing means (35)
(50) The heat transfer device characterized by being provided. 5. The heat transfer device according to claim 1, wherein the starting liquid pipe (50) is provided with a check valve (CV) that allows only the flow of the liquid refrigerant toward the pressurizing means (35). -6) is provided. 6. The heat transfer device according to claim 4, further comprising a pressure equalizing pipe (51) capable of equalizing the heat source side heat exchanger (22) and the pressurizing means (35). The pipe (51) is provided with an on-off valve (SV), and by opening the on-off valve (SV), the heat source side heat exchanger (22) and the pressurizing means (35) are equalized, A heat transfer device wherein the liquid refrigerant of the heat source side heat exchanger (22) is supplied to the pressurizing means (35). 7. The heat transfer device according to claim 1, wherein the start-up liquid pipe (50) is provided with an on-off valve that allows introduction of the liquid refrigerant to the pressurizing means (35) by an opening operation. A heat transfer device provided. 8. The heat transfer device according to claim 6, wherein the on-off valve is opened only at the time of start-up to allow the introduction of the liquid refrigerant to the pressurizing means (35). . 9. The heat transfer device according to claim 6, further comprising a detecting means (Th) capable of detecting whether or not a liquid refrigerant for generating a high pressure is present in the pressurizing means (35). A heat transfer device characterized in that when the detecting means (Th) detects that there is no liquid refrigerant for generating high pressure in the pressurizing means (35), the on-off valve is opened.