JPS5847624B2 - Nijiyuukouyoukiyuushiyureitosouchi Oyobi Sono Seigiyohouhou - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a dual-effect absorption refrigeration system that operates with a plurality of generators in an absorption refrigeration system that performs an absorption refrigeration cycle using a refrigerant liquid and an absorption solution.

Generally, in a dual-effect absorption refrigeration system, a system is adopted in which high fn (f5 medium vapor) generated in the first generator among multiple generators is used to heat the second generator. Conventionally, the high-temperature refrigerant liquid and vapor at the outlet of the second generator pass through the liquid seal part and the thermal energy of the refrigerant vapor, which was lost, is directly discarded into the cooling water in the condenser, which improves the efficiency of the refrigeration cycle. There was a diseconomie that did not contribute to the rise.

The present invention aims to provide an absorption refrigeration system that can appropriately eliminate these conventional disadvantages and significantly improve the efficiency of a dual-effect absorption refrigeration cycle.

In addition, the present invention provides a dual-effect absorption refrigeration system that accurately recovers thermal energy released as waste heat, guarantees safe and smooth operation, and also makes it possible to ensure high operating efficiency over all loads. It also aims to provide.

The present invention focuses on the thermal energy of the high-temperature refrigerant liquid at the outlet of the second generator that is directly discarded into the cooling water in the condenser, and in order to recover this energy, the evaporator A1
It is composed of an absorber B1, a first generator C1, a second generator D1, a condenser E, a first heat exchanger F1, a second heat exchanger G, and leads the refrigerant vapor from the first generator C to the second generator D, In a double-effect absorption refrigerator in which the refrigerant liquid condensed in the second generator D is guided to the evaporator A via the condenser E, a line from the outlet of the solution pump to the second heat exchanger The low-temperature, low-concentration absorbing solution is introduced into the exhaust heat recovery heat exchanger to exchange heat with the high-temperature refrigerant liquid or refrigerant vapor from the second generator, and then the first generator or first heat exchanger F is A line is provided to bypass the required amount of the absorption solution that exits and reaches the first generator C, and a heat source heat amount control valve H for controlling the refrigeration capacity that controls the amount of heat source to the first generator C, and as the case may be. By modifying the structure of the first generator C, it is not necessary to provide this control valve H, but a solution for controlling the flow rate of bath liquid sent from the absorber B to the first generator C. Flow rate control valves ■, ■, or an integrated control valve having the functions of these two control valves 1 and II, such as a three-way control valve or only one of the control valves, with the other one as a fixed throttle mechanism, simultaneously or selectively. In order to operate the refrigerant vapor, the capacity is controlled by changing the distribution of the solution flow rate according to fluctuations in the pressure or saturation temperature of the refrigerant vapor generated in the first generator C or fluctuations in the cold water outlet temperature of the evaporator A. It is characterized by the fact that

The present invention will be described by way of example with reference to FIG.
Evaporator A1 Absorber B1 First generator C1 Second generator D1 Condenser E1 and first heat exchanger F1 Second heat exchanger G, refrigerant vapor is transferred from the first generator C to the second generator In a double-effect absorption refrigerator in which the refrigerant liquid condensed in the second generator D is guided to the evaporator A via the condenser E, the evaporator A has the same can body as the absorber B. 1, the absorber B is provided with a liquid circulation pipe 4 having a cold water tube 2 and a refrigerant pump 3, and a spray pipe 5, and the absorber B is provided with a cooling water tube 6, a pipe 8 having a solution pump 7, and a spray pipe 5. A return pipe 9 connects the first generator C and the second generator D via the second heat exchanger G and the first heat exchanger F.

This first generator C carries a generator tube 10 having a heat source heat amount control valve H and is connected to a second generator D via a first heat exchanger F by a return pipe 11. has a generator tube 12 through which the heating medium passes, and is installed in the same can body 14 as the condenser E with the condenser tube 13 in a communication down state, and connects the condenser E and the evaporator A with a pipe 15. At the same time, the second generator D is connected to the absorber B via the second heat exchanger G by a return pipe 9, and the generator tube 12 is connected to the first generator C by a refrigerant vapor pipe 16, and the return pipe is connected to the absorber B via the second heat exchanger G. 1
7 is connected to condenser E.

On the other hand, a bypass pipe 18 is provided to bypass the low-temperature, low-concentration absorption solution from the pipe 8 of the solution pump 7, that is, the line from the discharge port of the bath liquid pump to the second heat exchanger G. The bypass pipe 18 is connected to the generator C, and the bypass pipe 18 is equipped with a solution flow rate control valve (1), a throttle valve, or an orifice, and a heat exchanger 19 for exhaust heat recovery. In order to heat-exchange the high-temperature refrigerant liquid or refrigerant vapor, a line from the discharge port of the solution pump 7 to the inlet of the second heat exchanger is connected to the return pipe 17 for heat exchange with the low-temperature, low-concentration absorption solution for exhaust heat recovery. 19 to exchange heat with the high-temperature refrigerant liquid or refrigerant vapor from the second generator, and then leave the first generator C or the first heat exchanger F to the absorption solution that reaches the first generator C. Only the required amount is bypassed.

Furthermore, the absorption solution piping 8 is provided with a solution flow rate control valve I,
Together with the solution flow rate control valve (■) in the bypass pipe 18, it is connected to the cold water outlet temperature detector 20 of the evaporator A or the steam valve of the first generator C that is controlled by this, and controls the operation of the valve. .

Then, the refrigerant evaporated in the evaporator A is absorbed into the solution in the absorber B, and the solution is transferred to the second heat exchanger G1 by the solution pump 7.
The solution is sent to the first generator C via the first heat exchanger F, where it is heated to release refrigerant vapor, and the solution is concentrated and enters the first heat exchanger F through the pipe 11, where the solution from the absorber B is The refrigerant vapor is heated by the heating tube of the generator tube 12 to generate refrigerant vapor again, and the refrigerant vapor generated in the second generator D enters the condenser E and is heated by the heating tube of the generator tube 12. It is cooled and condensed by the cooling water of No. 13.

On the other hand, the solution in the second generator is transferred to the second heat exchanger G through the return pipe 9.
The refrigerant cools down through heat exchange with the solution from absorber B and returns to absorber B, and the refrigerant accumulated in condenser E returns to evaporator A via return piping 15 for double-effect refrigeration. The cycle is repeated, and the low-temperature, low-concentration absorption solution from the line from the discharge port of the solution pump 7 to the inlet of the second heat exchanger G is guided to the heat exchanger 19 for waste heat recovery, and is then transferred from the second generator. After exchanging heat with the high temperature refrigerant liquid or refrigerant vapor, it exits the first generator C or the first heat exchanger F and is transferred to the first generator C.
By bypassing the absorption solution by the required amount, energy savings equivalent to the amount of heat exchanged in the exhaust heat recovery heat exchanger 19 can be obtained from the heat source in the first generator C.

That is, less heating energy is required to obtain the required refrigerating capacity, improving thermal efficiency.

When bypassing, a flow control valve I, which adjusts the amount sent from the absorber B to the first generator C,
(2) using the pressure of the first generator C or the pressure difference between both generators C and D as a signal, or instead of using these pressures, the pressure of the first generator C or the second generator D can be used as a signal. Control may be performed using the saturated temperature of the refrigerant vapor or an approximate saturated temperature, or by detecting the humidity at the cold water outlet of the evaporator A.

That is, the heat source heat quantity control valve H is operated using the chilled water outlet temperature as a signal, and the solution flow rate control valve (■) and the flow rate are operated using the refrigerant liquid temperature in the tube 12 of the second generator D as a signal, and the flow rate distribution is adjusted. That means you are doing it.

In addition, instead of the line directly connected to the first generator C, the solvent bypass piping 18 may be provided with a line 22 indirectly extending from the outlet of the first heat exchanger F to the first generator C.

In these cases, if the bypass pipe 18 is connected between the 11th and 2nd heat exchangers and the dilute solution is returned, the resistance of the solution flow path will also increase, causing the resistance value of the refrigerant cooling device and the resistance value of the low temperature solution heat exchanger to increase. If these are not balanced, it will not be possible to distribute the dilute solution between the two, and as a result, the head of the solution circulation pump will have to be raised to balance the flow path resistance of both heat exchangers. Therefore, the dilute solution leaving the heat exchanger 19 is returned directly to the first generator C side or the outlet side of the first heat exchanger F without passing through the solution heat exchanger F to reduce the loss resistance and reduce the dilute solution. This means that the heat exchange amount of the first heat exchanger F (flow rate x
It is also possible to prevent a decrease in temperature difference x specific heat).

Additionally, if the flow rate of dilute solution to the refrigerant cooling device is not restricted, the refrigeration capacity will decrease, and even when the refrigerant vapor drain decreases, a large amount of dilute solution will have to be circulated through this device, which will significantly reduce the efficiency of the absorption refrigeration cycle. Therefore, in order to control the flow rate control valves I to reduce the amount of dilute solution supplied as the load becomes low, the decrease in load is detected by the chilled water outlet temperature, etc. , the flow distribution is controlled to prevent a drop in efficiency during partial loads.

On the other hand, the high-temperature refrigerant liquid from the outlet of the second generator D is cooled by exchanging heat with the low-temperature, low-concentration absorbing solution in the exhaust heat recovery heat exchanger 19, and is then led to the condenser E where it evaporates. A line 23 leading to the vessel A or, if necessary, a line 24 joining the liquid refrigerant line 15 from the condenser E to the evaporator A can also be provided.

Furthermore, although the first illustrated example shows an example in which the system is applied to a dual-effect absorption refrigeration system that uses steam or high-temperature water as a heating source, it can be applied to any absorption refrigeration system that uses a dual-effect absorption refrigeration cycle. .

For example, an absorption refrigeration system using a dual-effect absorption refrigeration cycle using steam, high-temperature water, city gas, kerosene, etc. as a heating source, etc. An example was shown.

When the heat source heat amount control valve H to the first generator C is activated by the signal of the cold water outlet temperature, the amount of heating to the first generator C changes, and the bath liquid humidity in the first generator C changes. , the generated refrigerant vapor pressure and its saturation temperature decrease.

In other words, when the heat source calorific value foot valve H operates, the refrigerant liquid moisture in the tube 12 of the second generator D changes, which causes the solution flow rate control valve I to operate, and on the other hand, the bypass piping 1
In 8, an appropriate throttling mechanism such as an orifice is inserted so that a constant amount of the low-temperature, low-concentration solution flows into the exhaust heat recovery heat exchanger 19, thereby easily controlling the capacity. .

The present invention provides a dual effect system in which refrigerant vapor is guided from the first generator C to the second generator D, and the refrigerant liquid condensed in the second generator D is guided to the evaporator A via the condenser E. In an absorption refrigerator, by recovering the thermal energy of the high-temperature refrigerant liquid from the second generator D directly in the condenser E without discarding it into the cooling water, energy savings equivalent to this amount of heat can be achieved by heating the first generator C. You can get it at source.

That is, since the dilute absorption solution is sent to the heat recovery heat exchanger and sent to the first generator line, the heating of this line saves double-effect thermal energy, and the heat recovery heat exchanger is completely Loss due to entrainment of not only refrigerant liquid but also refrigerant vapor can be recovered at the same time, and there is also the advantage that the amount of absorption solution to the heat recovery heat exchanger can be determined arbitrarily. Due to the reduction of the absorption solution in the first heat exchanger (
On the other hand, the temperature of the solution at the outlet of this heat exchanger becomes higher due to the bypass portion), and the efficiency increases due to the effect of rising due to the flow rate reduction and heat transfer load reduction. Since it is a circulation system that returns the solution, the amount of heat exchanged in the first heat exchanger increases, and the flow rate of the diluted solution in the first heat exchanger does not increase, resulting in less pressure loss and no effect on pump characteristics. Less heating energy is required to obtain the refrigerating capacity, improving thermal efficiency.

For example, if the present invention is implemented under normal air conditioning conditions, approximately 5% of heating energy can be saved, so the effect is significant.Also, since the thermal energy released as waste heat is recovered, the amount of heat equivalent to this amount is reduced on the cooling water side. Cost savings can be achieved.

For example, the amount of cooling water can be reduced by an amount equivalent to the amount of heat dissipated, and the recirculation method has the advantage of reducing the capacity of the cooling tower by this amount.In addition, the power of the cooling water pump can also be saved, and the first generation occurs when controlling the capacity. Since there is always a liquid seal between the generator and the second generator, gas bypass can be accurately prevented and safe operation can be performed. The flow rate of the solution entering the generator can be changed arbitrarily by changing the characteristics of the flow control valve and the characteristics of the humidity signal, resulting in an extremely efficient refrigeration cycle depending on the state of the heat source, and the capacity of the It has the advantage of good responsiveness, helping to reduce operating costs, and improving safety.

[Brief explanation of the drawing]

FIG. 1 is a system explanatory diagram showing an embodiment of the present invention, and FIG. 2 is a system explanatory diagram of another embodiment. A...Evaporator, B...Absorber, C...
...First generator, D...Second generator, E.
... Condenser, F ... First heat exchanger, G.
...Second heat exchanger, H...Heat source heat amount control valve, ■...Solution flow rate control valve, ■...Solution flow rate control valve Figure 1 ) In Fig. 2, the aperture mechanism, 1,
14... Can body, 2... Cold water tube,
3...Refrigerant pump, 4...Liquid circulation pipe, 5...Spray pipe, 6...Cooling water tube, 7... Bath liquid pump, 8, 9, 11, 1
5... Piping, 10, 12... Generator tube, 13... Condenser tube, 1 6. −
... Refrigerant vapor piping, 17 ... Return piping, 18
......Bypass piping, 19...Heat exchanger, 20...Cold water outlet temperature detector, 22, 23,
24... line.

Claims (1)

[Claims] 1 Evaporator A1 Absorber B1 First generator C1 Second generator D
The refrigerant vapor is guided from the first generator C to the second generator D, and the refrigerant liquid condensed in the second generator D is In a double-effect absorption refrigerating machine that is guided to the evaporator A via the condenser E, the low-temperature, low-concentration absorption solution from the line from the outlet of the solution pump to the second heat exchanger is used for exhaust heat recovery. After being led to a heat exchanger to exchange heat with the high temperature refrigerant liquid or refrigerant vapor from the second generator D, the absorption leaves the first generator C or the first heat exchanger F and reaches the first generator C. A dual-effect absorption refrigeration device characterized by being equipped with a line that allows a required amount of solution to bypass. 2 Evaporator A1 Absorber B1 First generator C1 Second generator D
The refrigerant vapor is guided from the first generator C to the second generator D, and the refrigerant liquid condensed in the second generator D is In a double-effect absorption refrigerator, in which liquid is introduced to evaporator A via condenser E, waste heat is recovered from the low-temperature, low-concentration absorption solution from the line from the outlet of the solution pump to the second heat exchanger. After being led to a heat exchanger for heat exchange with the high temperature refrigerant liquid or refrigerant vapor from the second generator D, it exits the first generator C or the first heat exchanger F and reaches the first generator C. A solution flow control valve I, It or these two control valves I, An integrated control valve having a function, for example, a three-way control valve or only one of the control valves, and the other one as a fixed throttle mechanism, and the first generator C is operated simultaneously or selectively. The system is connected to a detector that detects fluctuations in the pressure or saturation temperature of the refrigerant vapor generated in the evaporator A, or fluctuations in the cold water outlet temperature of the evaporator A, and the capacity is controlled by changing the distribution of the solution flow rate. A dual-effect absorption refrigeration device. 3 Evaporator A1 Absorber B1 First generator C1 Second generator D
The refrigerant vapor is guided from the first generator C to the second generator D, and the refrigerant liquid condensed in the second generator D is In a double-effect absorption refrigerator that is guided to evaporator A via condenser E, the low-temperature, low-concentration absorption solution from the line from the outlet of the solution pump to the inlet of the second heat exchanger is used for exhaust heat recovery. After being led to a heat exchanger and exchanging heat with the high temperature refrigerant liquid or refrigerant vapor from the second generator D, it exits the first generator C or the first heat exchanger F and reaches the first generator C. A line for bypassing the absorbing solution by a required amount is provided, and a heat source calorific value system for controlling the refrigeration capacity that controls the amount of heat source to the first generator C (
(Installation) Valve H and solution flow rate control valves I and II for controlling the flow rate of the solution sent from the absorber B to the first generator C, and for selectively operating the solution flow rate control valves I and I. The heat source calorific value control valve H and the solution flow rate control valve I are included in the detector for detecting fluctuations in the pressure or saturation temperature of the refrigerant vapor generated in the first generator C or fluctuations in the cold water outlet temperature of the evaporator A. 1. A dual-effect absorption refrigeration system characterized in that the capacity of the bath liquid is controlled by changing the distribution of the flow rate of the bath liquid by communicating and deploying the II.