JPH0634286A - Heat conveying apparatus - Google Patents

Abstract

PURPOSE:To eliminate a pressure reduction start delay time in a liquid receiver and to enhance the heat conveying capacity of the title apparatus which uses heat for room heating by utilizing a pressure rise at the time of heating refrigerant. CONSTITUTION:The heat conveying apparatus comprises a refrigerant heater 2, a heat conveyor 18 in which a vapor liquid separator 1 is annularly connected by an inlet tube 3 and an outlet tube 4 and a liquid receiver 5 provided above the separator 1 is connected to the separator 1 through a switching valve 8 and a first check valve 6, an annular circulation passage 19 in which the separator 1, a heat radiator 10, a second check valve 12 and the receiver 5 are sequentially connected, a liquid refrigerant pressure feeder 20 and liquid refrigerant diffusing nozzle 23 provided in parallel with the valve 12 at a liquid refrigerant inlet side of the receiver 5, and a controller 22 for operating the feeder 20 at the time of closing the valve 8. When the valve 8 is closed, liquid refrigerant is forcedly poured in the receiver.

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, for example, in Japanese Patent Laid-Open No. 3-5.
As shown in the 1631 publication, it has a configuration 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 further has an outlet pipe by a pressure equalizing pipe 9 having an opening / closing valve 8. 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. 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 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. Reference numeral 17 is a blower 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
Of the two-phase refrigerant that has flowed into the gas refrigerant, the gas refrigerant enters the radiator 10 through the gas refrigerant outflow pipe 11 and exchanges heat with the indoor air sent by the blower 17, dissipates heat and condenses into supercooled liquid.

When the on-off valve 8 is closed, the radiator 1
The supercooled liquid refrigerant condensed and liquefied at 0 flows into the liquid receiver 5 from the liquid refrigerant return pipe 13 through the second check valve 12 by condensing the gas refrigerant. At this time, the pressure in the liquid receiver 5 is lower than the pressure in the gas-liquid separator 1,
The first check valve 6 is closed. When the on-off valve 8 is opened in this state, 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 is subjected to the first check by gravity. Gas-liquid separator 1 through valve 6
Flows in.

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 is rapidly decompressed into the liquid receiver 5. And the liquid receiver 5 is filled with the liquid refrigerant and the cycle 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 of

[0008]

In the above-mentioned conventional structure, the decompression start delay in the liquid receiver 5 is set as shown in FIG. It was necessary to consider the time T _l . That is,
From the time t ₁ when the open / close valve 8 is switched from the open state to the closed state, T _l
After that, the pressure in the receiver 5 is reduced, and the receiver 5 is filled with the liquid refrigerant in the pressure reduction time _Tr to complete the pressure reduction. The depressurization start delay time T _l is mainly due to the heat capacity of the container of the liquid receiver 5 and insufficient diffusion of the liquid refrigerant entering the liquid receiver 5. The decompression time T _r is the time until the liquid refrigerant finishes flowing 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 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 drop pipe 7 are set. It is determined by the flow path resistance of.

[0009] closing period T _s of the thus-off valve 8 is the sum of the open time T _ON and the closing time _{T OFF (T s = T O} N + T OFF), further closing time T _OFF is vacuum start delay time T _It is the sum of _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 there is no choice but to set the opening / closing cycle T _{S to} be long, and the heat transfer amount (when used for heating is used. There was a constraint on increasing the heating capacity).

The present invention is intended to solve the above problems, and aims at shortening the opening / closing cycle by eliminating the depressurization start delay time and increasing the heat transfer capacity.

[0011]

In order to achieve the above object, the present invention provides a refrigerant heater, a liquid-liquid separator connected by an annular pipe line, and a liquid receiver provided above the gas-liquid separator. , A heat transfer part connected to the gas-liquid separator via an on-off valve and a first check valve, and an annular circulation path sequentially connecting the gas-liquid separator, a radiator, a second check valve and the liquid receiver And a liquid refrigerant pressure feeder and a liquid refrigerant diffusion nozzle provided in parallel with the second check valve on the liquid refrigerant inlet side of the liquid receiver, and actuating the liquid refrigerant pressure feeder when the on-off valve is closed. And a control device for controlling.

[0012]

With the above-described structure, the present invention serves as a trigger for starting the condensation of the gas refrigerant in the liquid receiver by forcibly injecting the liquid refrigerant into the liquid receiver by operating the liquid refrigerant pump with the closing of the on-off valve. make. Due to this forced injection action and atomization and diffusion of the supercooled liquid refrigerant by the diffusion nozzle, the supercooled liquid refrigerant efficiently contacts and condenses with the gas refrigerant. As a result, the decompression in the liquid receiver occurs without the decompression start delay time, and the liquid refrigerant is sucked into the liquid receiver all at once.

By eliminating the depressurization 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 of sucking and dropping of the liquid receiver per unit time is increased to increase the refrigerant. 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.

[0014]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS 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 thus 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. The heat transfer section is connected to the annular pipe line by a drop pipe 7 and a pressure equalizing pipe 9 having an opening / closing 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 pump that is provided on the liquid refrigerant inlet side of the liquid receiver 5, and is connected to a liquid refrigerant return pipe 13 that connects the liquid receiver 5 and the radiator 10, and in the present embodiment, a second check valve. It is provided in parallel with 12 and bypasses the second check valve 12.

Reference numeral 21 is a combustion amount varying device for varying the combustion amount of the burner 16, 22 is electrically connected to the on-off valve 8, the temperature detector 14, the liquid refrigerant pump 20, and the combustion amount varying device 21.
The control device operates the liquid refrigerant pump 20 when the on-off valve 8 is closed. Reference numeral 23 is a diffusion nozzle that atomizes and discharges the liquid refrigerant sent from the liquid refrigerant pressure feeder into the liquid receiver 5.

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
By the operation of the liquid refrigerant pumping device 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.

In FIG. 2, at the time t ₀ when the open / close valve 8 is switched from the open state to the closed state, at the same time, the liquid refrigerant pumping device 20 is operated and the first supercooled liquid for condensing the gas refrigerant in the liquid receiver. Is atomized from the diffusion nozzle 23 and forcedly injected into the liquid receiver. Since the pressure reduction in the receiver starts due to the forced injection and atomization of the supercooled liquid, the pressure reduction start delay time T '
_L can be practically eliminated (T ′ _l = 0).

[0021] Accordingly, the closing time T _'OFF need only decompression time T _r of the net (T' _OFF = T _r) of the on-off valve 8, the opening and closing period T _'s is greatly reduced _{(T' s = T r +} T _ON ) Yes. Therefore, the refrigerant circulation capacity increases due to the increase in the number of times the liquid refrigerant is sucked and dropped in the liquid receiver, increasing the combustion amount in the refrigerant heater and increasing the heat transfer amount (heating capacity when used for heating). Greater ability can be achieved.

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 for 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 pressure feeder 20 does not have to be performed at the same time as the closing of the on-off valve 8 and can be arbitrarily set at the time of closing, and the pressure drop due to the natural heat dissipation of the conventional receiver and the heat transfer system. As compared with the case where the decompression start is generated due to the eventual condition such as the pressure fluctuation, the controllability of the suction / fall operation of the liquid receiver 5 is improved, and the fine refrigerant circulation amount control can be performed.

Further, the liquid refrigerant pump 20 is connected to the second check valve 12.
If it is provided in parallel with and has a bypass configuration, it is not necessary to consider the flow path resistance of the liquid refrigerant pumping device 20 against the rapid flow of the liquid refrigerant during rapid depressurization in the liquid receiver, which facilitates the structural design. Become.

[0025]

As described above, the heat transfer device of the present invention includes the heat transfer portion, the circulation path, the diffusion nozzle and the liquid refrigerant pumping device provided on the liquid refrigerant inlet side of the liquid receiver, and the closing of the on-off valve. Since it is configured to have a control device that operates the liquid refrigerant pump at the time of forming, it is possible to almost eliminate the depressurization start delay time,
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 decompression 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 1st check valve 8 Open / close valve 10 Radiator 12 2nd check valve 18 Heat transfer part 19 Circulation path 20 Liquid refrigerant pressure transmitter 22 Control device 23 Diffusion nozzle

Claims (1)

[Claims] 1. A refrigerant heater and a gas-liquid separator are connected by an annular pipe line, and a liquid receiver provided above the gas-liquid separator is connected to the gas-liquid separator via an opening / closing valve and a first check valve. A heat transfer unit connected to the gas-liquid separator, the radiator, the second check valve, and the liquid receiver in this order, and the second reverse side at the liquid refrigerant inlet side of the liquid receiver. A heat transfer device provided with a liquid refrigerant pressure feeder provided in parallel with a stop valve, a liquid refrigerant diffusion nozzle, and a control device for operating the liquid refrigerant pressure feeder when the on-off valve is closed.