JP2827863B2 - Heat transfer device - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a heat transfer apparatus for utilizing heat for heating or the like by utilizing a pressure increase when a refrigerant is heated.

[0002]

2. Description of the Related Art A conventional heat transfer device is disclosed in, for example,
As shown in Japanese Patent No. 51631, the configuration is as shown in FIG.

That is, the gas-liquid separator 1 is disposed above the refrigerant heater 2 and is connected by an inlet pipe 3 of the refrigerant heater 2 and an outlet pipe 4 of the refrigerant heater 2 and is connected by an annular pipe. Have been. The liquid receiver 5 is disposed above the gas-liquid separator 1, is connected to the gas-liquid separator 1 by a drop pipe 7 having a first check valve 6, and is further connected to an outlet pipe by a pressure equalizing pipe 9 having an on-off valve 8. 4 is connected to the gas-liquid separator 1. The gas-liquid separator 1 and a radiator 10 arranged on the indoor side as a utilization side are connected by a gas refrigerant outflow pipe 11, and the radiator 10 and the liquid receiver 5 are connected to a liquid refrigerant return pipe having a second check valve 12. 13 are connected. As described above, the gas-liquid separator 1, the radiator 10, the second check valve 12, the liquid receiver 5, and the first check valve 6 form an annular circulation path that is sequentially connected to the pipe. Reference numeral 14 denotes a temperature detector provided in the outlet pipe 4 of the refrigerant heater 2, and reference numeral 15 denotes a control device that controls the opening / closing time of the on-off valve 8 based on the temperature detected by the temperature detector 14. Reference numeral 16 denotes a burner provided in the refrigerant heater 2, and the refrigerant is heated by the burner 16. 17 is a blower provided in the radiator 10.

The operation of the above configuration will be described below. In the refrigerant heater 2, the refrigerant heated by the burner 16 passes through the outlet pipe 4 in a two-phase state of gas and liquid, flows into the gas-liquid separator 1, and the liquid refrigerant flows from the inlet pipe 3 to the refrigerant heater 2 again. Inflow. On the other hand, the gas refrigerant among the two-phase refrigerant flowing into the gas-liquid separator 1 is a gas refrigerant outgoing pipe 11.
The heat exchanger 10 enters the radiator 10 and exchanges heat with the room air sent by the blower 17 to radiate and condense to be supercooled and liquefied.

When the on-off valve 8 is closed, the supercooled liquid refrigerant condensed and liquefied by the radiator 10 is supplied to the liquid refrigerant return pipe 13.
Then, the gas refrigerant flows into the liquid receiver 5 through the second check valve 12 by condensing the gas refrigerant. At this time, since the pressure in the liquid receiver 5 is lower than the pressure in the gas-liquid separator 1, the first check valve 6 is in a closed state. In this state,
When the on-off valve 8 is opened, the liquid receiver 5 and the gas-liquid separator 1 communicate with each other by the pressure equalizing pipe 9 to be in a pressure equalized state, and the liquid refrigerant in the liquid receiver 5 passes through the first check valve 6 due to gravity. The gas flows into the gas-liquid separator 1.

Next, when the on-off valve 8 is closed again, the first check valve 6 is closed, and the condensed and supercooled liquid refrigerant of the radiator 10 flows into the receiver 5. The cycle in which the liquid is sucked by the rapid pressure reduction and the liquid receiver 5 is filled with the liquid refrigerant is repeated. As described above, a natural circulation cycle is performed between the gas-liquid separator 1 and the refrigerant heater 2 by the evaporated refrigerant pressure, and the supply of the liquid refrigerant from the receiver 5 to the gas-liquid separator 1 and the refrigerant heater 2 is performed by the on-off valve 8. Is an intermittent operation cycle based on the opening / closing cycle.

[0007]

In the above-mentioned conventional configuration, the opening / closing operation cycle of the on-off valve 8 for performing heat transfer by heating the refrigerant includes a delay in the start of pressure reduction in the receiver 5 as shown in FIG. The time Tl had to be taken into account. That is, the pressure in the receiver 5 is reduced by a time Tl from the time t1 when the on-off valve 8 switches from the open state to the closed state, and the pressure reduction time Tr
Then, the inside of the liquid receiver 5 is filled with the liquid refrigerant, and the pressure reduction is completed. This depressurization start delay time Tl is mainly due to the heat capacity of the container of the liquid receiver 5. The decompression time Tr is a time until the liquid refrigerant has completely flowed into the empty receiver 5 and is determined by the internal volume of the receiver 5 and the flow path resistance from the radiator 10 to the receiver 5. . Further, the open time TON is a time required for the liquid refrigerant to drop from the liquid receiver 5 which is full to the gas-liquid separator 1, and the internal volume of the liquid receiver 5 and the pressure equalizing pipe 9
And the flow path resistance of the drop tube 7.

As described above, the open / close cycle TS of the on-off valve 8 is the sum of the open time TON and the close time TOFF (TS = TON + TOFF), and the close time TOFF is the sum of the depressurization start delay time Tl and the depressurize time Tr (TOFF = Tl + Tr). Since the depressurization start delay time Tl is relatively large, there is a restriction in shortening the closing time TOFF, and the opening and closing cycle Ts must be set to a longer time. ) Was limited.

The present invention solves the above-mentioned drawbacks.
After connecting the connection pipe that connects the check valve and the liquid receiver to the valve driver, this valve driver is mounted on the upper surface of the receiver to reduce the amount of heat generated by the valve driver to conduct to the receiver. By doing so, the opening / closing cycle is shortened and the heat transfer amount is increased.

[0010]

According to the present invention, in order to achieve the above object, a partition plate is provided for partitioning an upper liquid receiving portion and a lower gas-liquid separator liquid reservoir portion disposed above a refrigerant heater. A container, an inlet pipe and an outlet pipe that communicate the refrigerant heater and the gas-liquid separator liquid reservoir, an electric coil that drives an on-off valve to the partition plate and the on-off valve on the upper surface of the liquid receiving part by a valve shaft. A heat transfer unit having a driving unit, an annular circulation path in which the gas-liquid separator reservoir, the radiator and the liquid receiver are sequentially connected, and a connection pipe connecting the second check valve and the liquid receiver. After being joined to the electric coil driving section, the electric coil driving section is attached to the liquid receiving section.

[0011]

According to the present invention, the electric coil drive section is energized to open and close the on-off valve by the valve shaft, thereby replacing the liquid refrigerant in the liquid receiving section with the high-temperature refrigerant gas. During this time, the temperature of the electric coil driving unit becomes high due to heat generated by energization. After the connecting pipe is joined to the electric coil driving section, the electric coil driving section is provided on the upper surface of the liquid receiving section, so that the heat generated in the electric coil driving section is cooled by the low-temperature supercooled refrigerant of the connecting pipe and the liquid receiving section is cooled. Is not heated. Therefore, when the on-off valve is closed, the supercooled liquid refrigerant flows from the radiator through the second check valve to the inside of the low-temperature liquid receiving portion from the connection pipe, so that there is no time delay.

Further, the supercooled liquid refrigerant flowing from the connection pipe to the liquid receiving part is atomized by the valve shaft, uniformly jetted into the liquid receiving part, and rapidly mixed with the high-temperature gas refrigerant in the liquid receiving part. Therefore, the gas inside is condensed by the fine particles of the supercooled refrigerant, and the refrigerant pressure inside the liquid receiving portion drops rapidly, so that the low-temperature liquid refrigerant is sucked from the radiator, and is received by the condensation of the gas refrigerant by the supercooled liquid refrigerant. The decompression in the liquid part occurs without the decompression start delay time, and at the same time the on-off valve is closed, the liquid refrigerant is sucked into the liquid receiving part at a stretch.

As described above, by eliminating the decompression start delay time, the closing time of the on-off valve is greatly shortened, the opening / closing cycle is reduced, and the number of suction / drop of the liquid receiving portion per unit time is increased to increase the refrigerant flow. By increasing the amount of circulation and increasing the amount of heating of the refrigerant, it is possible to obtain a large heat transfer amount (heating capacity in the case of use for heating).

[0014]

FIG. 1 shows an embodiment of the present invention. 1, the same reference numerals as those in FIG. 3 denote the same members, and have the same functions. Therefore, detailed description will be omitted, and different points will be mainly described.

Reference numeral 18 denotes a container arranged above the refrigerant heater 2, and the container 18 is divided into an upper liquid receiving portion 19 and a lower gas-liquid separate liquid reservoir 20 by a partition plate 21. The refrigerant heater 2 and the gas-liquid separate liquid reservoir 20 communicate with each other through an inlet pipe 3 and an outlet pipe 4. 22 is the burner 16
The liquid heater 20 and the gas-liquid separate liquid reservoir 20 are connected to an annular pipe, and the liquid receiver 19 and the gas-liquid separate liquid reservoir 2
0 and a heat transfer section connected to the annular pipe provided with the on-off valve 23 and the annular pipe. 24 is a gas-liquid separator liquid reservoir 2
0, a radiator 10, a second check valve 12, a connecting pipe 25, an electric coil driving section 26, and a liquid receiving section 19 are sequentially connected in a pipe to form an annular circulation path. The on-off valve 23 of the present embodiment includes a spring 27
As means for constantly applying the closing pressure and forcibly opening the on-off valve 23, there is provided an electric coil driving unit 26 via a valve shaft 28 and a control device 29 for controlling this operation. As another embodiment, the same operation is performed even when the electric coil driving unit is directly connected to the on-off valve. Then, the connection pipe 25 is connected to the electric coil driving unit 2.
6, the electric coil driving section 26 is attached to the upper surface of the liquid receiving section 19. Numeral 30 denotes a combustion amount varying device for varying the combustion amount of the burner 16, and a control device 29.
Are electrically connected to the on-off valve 8, the temperature detector 14, and the combustion amount varying device 30.

In the above configuration, the heating operation of the refrigerant is performed by heating the refrigerant by the opening / closing operation of the on-off valve 23, the combustion in the burner 16, and the operation of the blower 17.

Here, when the on-off valve 23 is closed, the supercooled liquid refrigerant condensed and liquefied by the radiator 10 flows from the liquid refrigerant return pipe 13 to the second check valve 12, the connection pipe 24, and the electric coil driving section 25. The gas refrigerant in the liquid receiving portion 19 is condensed through the liquid flowing through the liquid receiving portion 19. And the liquid receiver 19
The supercooled liquid refrigerant flows from the circulation path 24 into the controller, and in a state in which the liquid receiver 25 is filled with the liquid refrigerant, the controller 29 operates the electric coil drive unit 26 to move the valve shaft 28 to open and close the valve. When 23 is opened, the liquid receiving part 25 and the gas-liquid separator liquid storing part 20 communicate with each other to be in a pressure equalized state, and the liquid refrigerant in the liquid receiving part 19 passes through the on-off valve 23 due to gravity to be in the gas-liquid separate liquid storing part. 20. At this time, the gas refrigerant in the gas-liquid separator liquid reservoir 20 that simultaneously replaces the liquid refrigerant in the liquid receiver 19 is
It flows to the liquid receiving part 19 through the on-off valve 23. Next, when all the liquid refrigerant in the liquid receiving section 19 flows, when the on-off valve 23 is closed again, the liquid receiving section 19 is instantaneously reduced in pressure to a low pressure. The cycle in which the cooled liquid refrigerant is sucked and the liquid receiving portion 19 is filled with the liquid refrigerant is repeated.

Here, the pressure equalizing tube 9 in the conventional example is eliminated,
By increasing the diameter of the on-off valve 23 so that the gas refrigerant is replaced at the same time as the liquid refrigerant falls from the on-off valve 23, the length becomes the shortest.
3 is the shortest. Therefore, the flow path resistance of the gas refrigerant and the liquid refrigerant flowing through the on-off valve 23 is reduced, and the liquid receiving unit 1 is filled with liquid when the on-off valve 23 is opened.
The liquid refrigerant 9 is replaced with a gas refrigerant and the gas-liquid separate liquid reservoir 2
It is dropped to 0 in large quantities. And the electric coil driving unit 2
6 to energize the valve shaft 28 to open the on-off valve 23 to replace and fill the liquid refrigerant in the liquid receiving portion 19 with the high-temperature refrigerant gas.
During this time, the temperature of the electric coil driving unit 26 becomes high due to heat generation due to energization. In the present invention, the connecting pipe 25 is connected to the electric coil driving unit 2.
After joining with the liquid crystal drive unit 6, the electric coil driving unit 26 is provided on the upper surface of the liquid receiving unit 19. For this reason, the heat generated in the electric coil drive unit 26 is cooled by the low-temperature supercooled refrigerant in the connection pipe 25 and the liquid receiving unit 19 is not heated. Therefore, when the on-off valve 23 is closed, the entire liquid receiving part 23 is at a low temperature, so that the supercooled liquid refrigerant flows from the radiator through the second check valve into the low-temperature liquid receiving part 19 from the connection pipe without delay. Therefore, there is no time delay in the pressure reducing operation.

The supercooled liquid refrigerant flowing from the connection pipe 25 to the liquid receiving part 19 is atomized by the valve shaft 28 and
And is rapidly mixed with the high-temperature gas refrigerant in the liquid receiving portion 19. Therefore, the gas inside is condensed by the fine particles of the supercooled refrigerant, and the refrigerant pressure inside the liquid receiving portion 19 is rapidly reduced, the low-temperature liquid refrigerant is immediately sucked from the radiator 10, and the gas refrigerant by the supercooled liquid refrigerant is removed. Liquid receiving part 1 by condensation
The decompression in 9 occurs without the decompression start delay time, and the on-off valve 2
Simultaneously with the closing of 3, the liquid refrigerant is sucked into the liquid receiving portion 19 at a stretch, and the cycle in which the liquid receiving portion 19 is filled with the liquid refrigerant is repeated.

A case where the on-off valve 23 is operated so as to be opened from a closed state in the above-described heat transfer operation will be described with reference to FIG. In FIG. 2, even when the on-off valve 23 is in the open state, the temperature of the liquid receiving portion 19 is low. Therefore, at the same time as the time tO when the valve is switched to the closed state, the pressure in the liquid receiving portion 19 is reduced and the supercooled refrigerant flows in. . Then, the high-temperature gas refrigerant inside is cooled and condensed by the fine-grained jet of the supercooled refrigerant, whereby the pressure reduction in the liquid receiving portion 19 can be started instantaneously, and the pressure reduction start delay time Tl 'is practically eliminated ( Tl '= 0). Therefore, the closing time TOFF 'of the on-off valve 23 is equal to the net decompression time Tr.
Only (TOFF '= Tr), and the opening / closing cycle TS' can be greatly reduced (TS '= Tr + TON). Therefore, the liquid receiving section 25
The refrigerant circulation capacity increases due to an increase in the number of times the liquid refrigerant is suctioned and dropped in the air, and the amount of combustion in the refrigerant heater 2 is increased, so that the heat transfer amount (or the heating capacity when used for heating) can be increased. . There is no need for a drive input, and the only input for heat transfer is the input of the electric coil drive unit 26, and the economy is not lost.

FIG. 5 shows another embodiment of the present invention.
When the ring-shaped plate is fixed to the valve shaft 28 and the projection 31 is provided, and the on-off valve 23 is closed, the supercooled liquid refrigerant flowing from the connection pipe 25 to the liquid receiving portion 19 is atomized by the valve shaft 28. Further, the liquid material collides with the projection 31 and becomes extremely fine, and is uniformly and widely ejected throughout the liquid receiving portion 19, and more rapidly mixes with the high-temperature gas refrigerant in the liquid receiving portion 19. Therefore, the internal high-temperature gas is condensed more quickly, and the refrigerant pressure inside the liquid receiving section 19 is rapidly reduced, so that the low-temperature liquid refrigerant is immediately sucked from the radiator 10, and the liquid receiving section 23 is sucked and discharged per unit time. By increasing the number of drops, it is possible to increase the refrigerant circulation amount, and by increasing the refrigerant heating amount, it is possible to obtain a large heat transfer amount. And
The faster condensation of the high-temperature gas allows the gas refrigerant to be condensed and decompressed even if the degree of subcooling of the supercooled liquid refrigerant is small, thereby increasing the stability of operation and the possible operating range.

[0022]

As described above, the heat transfer apparatus according to the present invention comprises a container provided with a partition plate for partitioning an upper liquid receiving part and a lower gas-liquid separator liquid reservoir disposed above a refrigerant heater; An inlet pipe and an outlet pipe that communicate the refrigerant heater and the gas-liquid separator liquid reservoir, an on-off valve on the partition plate, and an electric coil driving unit that drives the on-off valve on the upper surface of the liquid receiving unit by a valve shaft. A heat transfer unit having an annular circulation path in which the gas-liquid separator liquid reservoir, the radiator and the liquid receiver are sequentially connected,
After the connecting pipe connecting the second check valve and the liquid receiving section is joined to the electric coil driving section, the electric coil driving section is attached to the liquid receiving section.

(1) After the connecting pipe is joined to the electric coil driving section, the heat generated in the electric coil driving section is cooled by the low-temperature supercooled refrigerant and the liquid receiving section is not heated, so that the supercooled liquid is produced without a time delay. The refrigerant is atomized and jetted out uniformly, cools and condenses the internal high-temperature gas refrigerant, and the heat transfer amount can be increased by increasing the refrigerant circulation amount by greatly shortening the opening and closing cycle.

(2) Further, the input of only the heat transfer is only the input of the electric coil driving unit, and the economy is not lost.

(3) Since the protruding portion is provided on the valve shaft, the supercooled liquid refrigerant is further finely ejected at the protruding portion, so that the high-temperature gas refrigerant is more rapidly mixed. As a result, the heat transfer amount can be increased, and the supercooled liquid refrigerant is directly mixed with the high-temperature gas refrigerant, so that the gas refrigerant can be condensed and decompressed even if the supercooled liquid refrigerant has a small degree of supercooling. Increases stability and possible operating range.

[Brief description of the drawings]

FIG. 1 is a system configuration diagram of a heat transfer device according to an embodiment of the present invention.

FIG. 2 is a decompression characteristic diagram of the liquid receiver.

FIG. 3 is a system configuration diagram of a conventional heat transfer device.

FIG. 4 is a decompression characteristic diagram of a liquid receiver in a conventional heat transfer device.

FIG. 5 is a system configuration diagram of a heat transfer device according to another embodiment of the present invention.

[Explanation of symbols]

 2 Refrigerant heater 3 Inlet pipe 4 Outlet pipe 10 Radiator 12 Second check valve 18 Container 19 Liquid receiving part 20 Gas-liquid separator liquid storage part 21 Partition plate 22 Heat transfer part 23 Open / close valve 24 Circulation path 25 Connection pipe 26 Electric Coil drive unit 28 Valve shaft 31 Projection

Continuation of front page (72) Inventor Ryuta Kondo 1006 Kazuma Kadoma, Kadoma, Osaka Prefecture Inside Matsushita Electric Industrial Co., Ltd. (56) References JP-A-60-30991 (JP, A) JP-A-3-156218 (JP) , A) JP-A-5-288427 (JP, A) (58) Fields investigated (Int. Cl. ⁶ , DB name) F24D 7/00

Claims (2)

(57) [Claims] 1. A container provided with a partition plate for partitioning an upper liquid receiving part and a lower gas-liquid separator liquid storage part disposed above a refrigerant heater, the refrigerant heater and the gas-liquid separator liquid storage part. An inlet pipe and an outlet pipe that communicate with each other; a heat transfer unit having an on-off valve on the partition plate and an electric coil drive unit that drives the on-off valve on the upper surface of the liquid receiving unit by a valve shaft; After joining an electric circuit, a radiator, and an annular circulation path that sequentially connects the liquid receiving part, and a connection pipe that connects the second check valve and the liquid receiving part to the electric coil driving part, the electric coil driving part is connected. A heat transfer device having a structure in which a part is attached to the liquid receiving part. 2. A structure in which a projection is provided on a valve shaft.
The heat transfer device as described in the above.