JPH05149559A - Heat transfer device - Google Patents

Abstract

PURPOSE:To eliminate the delay time of starting of pressure reduction in a liquid receiver and contrive the enlargement of the transfer amount of heat, in a heat transfer device utilizing a pressure increase upon a heating refrigerant for the heat of space heating. CONSTITUTION:The title device is provided with a heat transfer unit 18, provided with a refrigerant heater 2, a gas/liquid separator 1, a liquid receiver 5, an opening and closing valve 8 and a first non-return valve 6, and an annular circulating passage 19, consisting of the gas/liquid separator 1, a radiator 10, a second non-return valve 12 and the liquid receiver 5, which are connected sequentially. Further, the title device is constituted of a liquid refrigerant pumping device 20, provided at the inlet side of the liquid refrigerant of a liquid receiver 5, and a controller 22, operating the liquid refrigerant pumping device 20 upon closing the opening and closing valve 8, whereby the liquid refrigerant is poured forcibly into the liquid receiver 5 when the opening and closing valve 8 is closed.

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 for utilizing heat for heating or the like by utilizing a pressure increase when heating a refrigerant.

[0002]

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

That is, the gas-liquid separator 1 is arranged 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 connected by an annular pipe line. ing. Further, the liquid receiver 5 is arranged 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 provided with a pressure equalizing pipe 9 having an opening / closing valve 8 by an outlet pipe. It is connected to the gas-liquid separator 1 via 4. The gas-liquid separator 1 and the radiator 10 arranged on the indoor side as the use side are connected by a gas refrigerant forward pipe 11, and the radiator 10 and the liquid receiver 5 are liquid refrigerant return pipes having a second check valve 12. It is connected at 13. 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 sequentially connected by piping. Reference numeral 14 is a temperature detector provided in the outlet pipe 4 of the refrigerant heater 2, and 15 is a control device for controlling the opening / closing time of the opening / closing valve 8 according to the temperature detected by the temperature detector 14. Reference numeral 16 is a burner provided in the refrigerant heater 2, and the burner 16 heats the refrigerant. A blower 17 is provided in the radiator 10.

The operation of the above structure will be described below. In the refrigerant heater 2, the refrigerant heated by the combustion heat of the burner 16 flows into the gas-liquid separator 1 through the outlet pipe 4 in a two-phase state of gas and liquid, and the liquid refrigerant is heated again from the inlet pipe 3 by the refrigerant heating. Flows into the vessel 2. On the other hand, gas-liquid separator 1
The gas refrigerant of the two-phase state refrigerant that has flowed into the heat exchanger 10 enters the radiator 10 through the gas refrigerant forward pipe 11 and exchanges heat with the indoor air sent by the blower 17, condenses heat and condenses into supercooled liquid.

When the opening / closing valve 8 is closed, the supercooled liquid refrigerant condensed and liquefied in the radiator 10 is returned to the liquid refrigerant return pipe 13
Through the second check valve 12 to flow into the liquid receiver 5 by condensing the gas refrigerant. At this time, the pressure inside the liquid receiver 5 is lower than the pressure inside the gas-liquid separator 1, so the first check valve 6 is in a closed state. In this state,
When the open / close valve 8 is opened, the liquid receiver 5 and the gas-liquid separator 1 communicate with each other through the pressure equalizing pipe 9 to be in a pressure equalizing state, and the liquid refrigerant in the liquid receiver 5 passes through the first check valve 6 by gravity. It 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 subcooling liquid refrigerant of the radiator 10 flows into the liquid receiver 5 immediately. The cycle in which the liquid is sucked by the reduced pressure and the liquid receiver 5 is filled with the liquid refrigerant is repeated. As described above, the natural circulation cycle between the gas-liquid separator 1 and the refrigerant heater 2 is based on the evaporated refrigerant pressure, and the supply of the liquid refrigerant from the liquid receiver 5 to the gas-liquid separator 1 and the refrigerant heater 2 is performed by the open / close valve 8 It is an intermittent operation cycle according to the open / close cycle.

[0007]

In the above-mentioned conventional structure, the decompression start delay in the liquid receiver 5 is set as shown in FIG. 4 for setting the opening / closing operation cycle of the opening / closing valve 8 for heat transfer by heating the refrigerant. It was necessary to consider the time T _l . That is, after the time t ₁ when the open / close valve 8 is switched from the open state to the closed state, the pressure reduction in the liquid receiver 5 occurs after a delay of the time T _l , and the pressure reduction time T
_{At r} , the liquid receiver 5 is filled with the liquid refrigerant, and the pressure reduction is completed. This depressurization start delay time T _l is mainly due to the heat capacity of the container of the liquid receiver 5. Further, the depressurization time T _r is the time until the liquid refrigerant completely flows into the empty receiver 5 and depends on the internal volume of the receiver 5 and the flow path resistance from the radiator 10 to the receiver 5. Determined. Further, the opening time T _ON is the time required for the liquid refrigerant to drop from the liquid receiver 5 that 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 drop pipe 7 are set. It is determined by the flow path resistance of.

As described above, the opening / closing cycle T _S of the opening / closing valve 8 is the sum of the opening time T _ON and the closing time T _OFF (T _S = T _ON + T _OFF ), and the closing time T _OFF is the depressurization start delay time T _l. And the depressurization time T _r (T _OFF = T _l + T _r ). Since this depressurization start delay time T _l is relatively large, there is a restriction on the reduction of the closing time T _OFF , and the opening / closing cycle T _S has to be set longer. There was a restriction on increasing the heating capacity).

The present invention is intended to solve the above problems, and an object thereof is to shorten the opening / closing cycle by eliminating the depressurization start delay time and to increase the heat transfer amount.

[0010]

In order to achieve the above object, the present invention provides a refrigerant heater, a gas-liquid separator communicating with the refrigerant heater, an opening / closing valve for the gas-liquid separator, and a first
A heat transfer part having a liquid receiver communicating through a check valve, an annular circulation path sequentially connecting the gas-liquid separator, the radiator, the second check valve and the liquid receiver, and the liquid receiver. The liquid refrigerant pumping device provided on the liquid refrigerant inlet side and the control device for operating the liquid refrigerant pumping device when the on-off valve is closed are provided.

[0011]

According to the present invention, with the above-described structure, the liquid refrigerant pumping device is actuated when the on-off valve is closed to forcibly inject the liquid refrigerant into the liquid receiver, and the gas refrigerant inside the liquid receiver starts to be condensed. make. Condensation of the gas refrigerant by the forcibly injected supercooled liquid refrigerant causes a pressure reduction in the liquid receiver to occur without a delay in starting the pressure reduction, and the liquid refrigerant is sucked into the liquid receiver at once.

By eliminating the decompression start delay time in this way, the closing time of the on-off valve is greatly shortened, the opening / closing cycle is shortened, and the number of times the liquid receiver is sucked / dropped per unit time is increased. By increasing the circulation amount and increasing the refrigerant heating amount, the heat transfer amount (heating capacity in the case of use for heating) can be increased.

[0013]

Embodiment An embodiment of the present invention will be described below with reference to FIG.

In FIG. 1, the same reference numerals as those in FIG. 3 denote the same members and have the same functions, and therefore detailed description thereof will be omitted.
The different points will be mainly described.

Reference numeral 18 connects the refrigerant heater 2 having the burner 16 and the gas-liquid separator 1 to the annular pipe line, the liquid receiver 5 provided above the gas-liquid separator 1 and the first check valve 6. It is a heat transfer section which is connected to the annular pipe line by a drop pipe 7 and a pressure equalizing pipe 9 having an on-off valve 8. Reference numeral 19 is an annular circulation path in which the gas-liquid separator 1, the radiator 10, the second check valve 12, and the liquid receiver 5 are sequentially connected by piping. Reference numeral 20 denotes a liquid refrigerant pumping device provided on the liquid refrigerant inlet side of the liquid receiver 5, which is connected to a liquid refrigerant return pipe 13 which connects the liquid receiver 5 and the radiator 10, and in the present embodiment, a second check valve. 12 is provided in parallel with 12 to bypass the second check valve 12.

Reference numeral 21 denotes a combustion amount varying device for varying the combustion amount of the burner 16, and 22 denotes an on / off valve 8 electrically connected to the on-off valve 8, the temperature detector 14, the liquid refrigerant pump 20, and the combustion amount varying device 21. It is a control device that operates the liquid refrigerant pump 20 at the time of closing.

In the above structure, the opening / closing operation of the opening / closing valve 8, the combustion in the burner 16, the operation of the blower 17 and the opening / closing valve 8 are performed.
By the operation of the liquid refrigerant pumping unit 20 at the time of closing, the heating of the heat transfer by heating the refrigerant is performed.

In the above heat transfer operation, the case where the liquid refrigerant pump 20 is operated at the same time when the on-off valve 8 is closed from the open state will be described with reference to FIG.

[0019] In FIG. 2, on-off valve 8 so that activates the time Tsu switched to the closed state t _O simultaneously the liquid refrigerant pumped 20 from the open state, the first subcooling to condense the gas refrigerant in the receiver Forcibly inject the liquid into the receiver. Since the pressure reduction in the liquid receiver is started by the forced injection of the supercooled liquid, the pressure reduction start delay time T _l ^' can be practically eliminated (T _l ^' = 0).

Therefore, the closing time T of the on-off valve 8_OFF ^'Is the net
Decompression time T_rJust good (T_OFF ^'= T_r), Opening and closing
Period T_S ^'Is significantly shortened (T_S ^'= T_r+ T_ON)it can.
Therefore, the number of times the liquid refrigerant is sucked and dropped in the receiver increases.
This increases the refrigerant circulation capacity and increases the combustion amount in the refrigerant heater.
Large amount of heat transfer (heating capacity when used for heating)
It can be empowered.

It should be noted that the liquid refrigerant pump 20 may have a small discharge amount, and a plunger type pump or the like can be applied. Therefore, the driving input is also small, and the input of heat transfer is small even when combined with the input of the on-off valve, and the economical efficiency is not lost.

Further, the operation of the liquid refrigerant pump does not have to be performed at the same time as the closing of the on-off valve, and can be arbitrarily set at the time of closing, the pressure drop due to the natural heat dissipation of the conventional receiver and the pressure of the heat transfer system. Compared to the start of depressurization due to fluctuation conditions such as fluctuations, the controllability of the suction / fall operation of the receiver is improved, and fine refrigerant circulation amount control is possible.

Further, if the liquid refrigerant pump is provided in parallel with the second check valve to form a bypass structure, the flow path of the liquid refrigerant pump is opposed to the rapid flow of the liquid refrigerant during the rapid pressure reduction in the receiver. The structure can be designed easily without considering the resistance.

[0024]

As described above, the heat transfer device of the present invention includes a heat transfer section, a circulation path, a liquid refrigerant pumping device provided on the liquid refrigerant inlet side of a liquid receiver, and a liquid when the on-off valve is closed. Since the control device for activating the refrigerant pumping device is provided, the depressurization start delay time can be eliminated, and there is an effect that the heat transfer amount can be increased by increasing the refrigerant circulation capacity by greatly shortening the opening / closing cycle. Further, since the liquid refrigerant pump can be arbitrarily controlled with a small input, there is an advantage that the refrigerant circulation amount can be finely controlled without losing the economical efficiency and the controllability is improved.

[Brief description of 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 pressure reduction characteristic diagram of a liquid receiver according to an embodiment of the present invention.

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.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Gas-liquid separator 2 Refrigerant heater 5 Liquid receiver 6 First check valve 8 Open / close valve 10 Radiator 12 Second check valve 18 Heat transfer part 19 Circulation path 20 Liquid refrigerant pressure transmitter 22 Control device

Claims (2)

[Claims] 1. A refrigerant heater, a gas-liquid separator which is arranged above the refrigerant heater and which communicates with the refrigerant heater through an inlet pipe and an outlet pipe, and which is arranged above the gas-liquid separator and which has an opening / closing valve and a first valve. 1. A heat transfer unit having a liquid receiver communicating with the gas-liquid separator via a check valve, the gas-liquid separator,
An annular circulation path in which a radiator, a second check valve, and the liquid receiver are sequentially connected, a liquid refrigerant pumping device provided on the liquid refrigerant inlet side of the liquid receiver, and the liquid when the on-off valve is closed. A heat transfer device provided with a control device for operating the refrigerant pump. 2. The heat transfer device according to claim 1, wherein the liquid refrigerant pump is provided in parallel with the second check valve.