JPH05164425A - Absorption type cold water or hot water machine - Google Patents

Abstract

PURPOSE:To provide a small-sized low temperature regenerator and assure an efficient operating state even under a low temperature state by a method wherein a part of rich resolution got from the low temperature regenerator is sucked and the sucked rich solution is added to dilute solution supplied to the low temperature regenerator. CONSTITUTION:In an absorption type cold water or hot water machine in which dilute solution sent from an absorption device 5 is regenerated into rich solution through evaporation of refrigerant vapor at a high temperature regenerator 1 and a low temperature regenerator 2, a part of rich solution got from the low temperature regenerator 2 is sucked and the sucked rich solution is added to the dilute solution supplied to the low temperature regenerator 2. The part of the rich solution is added to the dilute solution and an amount of solution supplied to the low temperature regenerator 2 is adjusted to be increased, thereby the most suitable control over a heat exchanging performance in the low temperature regenerator 2 is enabled. In addition, the heat exchanging efficiency can be improved due to an increasing of an amount of supplied solution and a temperature difference between a pressure balanced temperature and a refrigerant vapor balanced temperature at an outlet of rich solution of the low temperature regenerator can be made low. That is, the temperature difference can be controlled through an adjustment of the amount of dispersed liquid and then a pressure of the high temperature regenerator 1 can be controlled.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an absorption chiller-heater using water as a refrigerant and a salt solution such as lithium bromide as an absorbent, and more particularly to improvement of a low-temperature regenerator.

[0002]

2. Description of the Related Art As shown in FIG. 7, a conventional absorption chiller-heater is a high temperature regenerator 1, a low temperature regenerator 2, which is heated by an external heat source such as combustion heat of kerosene or city gas fuel. The condenser 3, the evaporator 4, the absorber 5, the high temperature solution heat exchanger 6, the low temperature solution heat exchanger 7, the solution pump 8 and the refrigerant pump 9 are operatively connected by piping.

During cooling, the cooling water CW cooled by the cooling tower CT is passed by the cooling water pump 10 to the absorber 5 and the condenser 3, and the evaporator 4 is caused to pass the cold water 4a.
This cold water 4a is circulated through an indoor air handling unit via a hot / cold water pipe for cooling. Specifically,
The dilute solution heated in the high temperature regenerator 1 generates refrigerant vapor and is concentrated, and the dilute solution in the low temperature regenerator 2 is heated by the refrigerant vapor generated in the high temperature regenerator 1 to generate refrigerant vapor. Concentrated.

The refrigerant vapor generated in the high temperature regenerator 1 and used as the heat source of the low temperature regenerator 2 and the refrigerant vapor generated in the low temperature regenerator 2 are cooled by the cooling water CW in the condenser 3 to become liquid refrigerant. .. Then, this liquid refrigerant is sent to the evaporator 4 via the liquid refrigerant conduit 17.

The liquid refrigerant in the evaporator 4 is the refrigerant pump 9
After being sprayed on the heat exchanger by the heat exchanger, the heat is taken from the cold water 4a to be vaporized and naturalized, and then guided to the absorber 5. On the other hand, the concentrated solution produced in the high temperature regenerator 1 is mixed with the concentrated solution produced in the low temperature regenerator 2 via the high temperature solution heat exchanger 6 and then passed through the low temperature solution heat exchanger 7 to detect the pressure difference and the head difference. Is guided to the absorber 5 and is sprayed onto the heat exchanger by the solution spray pump 18. The concentrated solution sprinkled on the heat exchanger of the absorber 5 is
While being cooled by the cooling water CW, the refrigerant vapor from the evaporator 4 is absorbed to form a dilute solution, and the dilute solution is sent to the high temperature regenerator 1 and the low temperature regenerator 2 by the solution pump 8. The absorption cooling cycle is configured as described above.

During heating, the refrigerant pump 9 is stopped and the cooling / heating switching valve 12 is opened. The refrigerant vapor generated in the high temperature regenerator 1 is divided into two after passing through the heating vapor conduit 16 branched from the heat transfer pipe header portion of the low temperature regenerator 2 and the cooling / heating switching valve 12. Then, one is guided to the absorber 5 via the bubble pump 13. The other is guided to the evaporator 4 via the bypass pipe 14, flows in the heat transfer pipe of the evaporator 4 and exchanges heat with the hot water 4b to be condensed and liquefied. This liquid refrigerant is guided to the bubble pump 13 via the heating liquid refrigerant conduit 15, and is sent to the absorber 5 by the bubble pump action of the refrigerant vapor from the high temperature regenerator 1. The heating cycle was configured as described above.

Here, in the low temperature regenerator 2, the refrigerant vapor generated in the high temperature regenerator 1 is introduced into the tubes of the heat transfer tube group arranged horizontally, and the low temperature heat exchanger 7 is provided outside the tubes by the solution spraying device S. It is a spray type low temperature regenerator in which the diluted solution that has passed through is sprayed. This type is disclosed in JP-A-52-38661. Further, as disclosed in JP-A No. 52-150852, a liquid-filled regenerator which fills a solution outside a horizontal tube with a dilute solution from one end and a concentrated solution from the other end, or a semi-regenerator in which both are combined. A heat exchange system such as a liquid-filled low temperature regenerator has also been proposed.

By the way, for controlling the heat exchange performance of the low temperature regenerator, for example, Japanese Patent Publication No. 46-1869.
As disclosed in No. 7, there is a method of adjusting the supply amount of the heating medium and a method of reducing the heat transfer area by lowering the liquid surface of the solution in the full type.

However, in the case of the spray type low temperature regenerator which requires the heating medium in the refrigerant vapor from the high temperature regenerator, the heating medium is subordinate to the high temperature regenerator, and therefore the method for adjusting the supply amount of the heating medium cannot be used. Since there is no liquid level in the heat transfer tube, the liquid level control method cannot be used. That is, in the spray medium low temperature regenerator dependent on the heating medium, there was no method for effectively controlling the heat exchange performance.

[0010]

However, although the difference in heat exchange temperature between the refrigerant vapor generated in the high-temperature regenerator, which is a heating source, and the solution in the low-temperature regenerator is small, the absorption chiller-heater has a high temperature in a wide operating range. In order to improve performance, it is necessary to optimally control the heat exchange temperature difference, that is, control of the heat exchange performance of the low temperature regenerator.

Therefore, an object of the present invention is to realize optimum control of heat exchange performance for a low temperature regenerator in an absorption chiller-heater.

Another object of the present invention is to further improve the performance of the low temperature regenerator.

[0013]

In order to achieve the above object, according to the present invention, a part of the concentrated solution from the low temperature regenerator is sucked and the sucked concentrated solution is supplied to the low temperature regenerator. The heat exchange performance in the low temperature regenerator is optimized by adding a portion of the concentrated solution to the dilute solution and increasing the amount of solution supplied to the low temperature regenerator. It is possible to control.
Such control is based on the following knowledge.

A heat mass transfer experiment was conducted on a spray type low temperature regenerator having a horizontal heat transfer tube group of 8 rows and 1 row and a unit length of 80 mm, and the spray liquid amount, that is, the liquid film outflow amount per unit width T (kg /
ms) and the heat transfer coefficient h ₀ (kW / m ² K) defined by the following equation.
I investigated the relationship. Here, Q is the heat exchange amount (kW), A ₀
Is the external heat transfer area (m ² ), TLG _o is the low temperature regenerator concentrated solution outlet refrigerant vapor equilibrium temperature (° C), TLG _i is the low temperature regenerator dilute solution inlet refrigerant vapor equilibrium temperature (° C), and THG _s is the high temperature. Regenerator refrigerant vapor pressure equilibrium temperature (° C). Therefore,
(Equation 1) is an equation that evaluates not only heat transfer but also mass transfer. As a result of the experiment, as shown in FIG. 8, it was found that the heat transfer performance of the low-temperature regenerator is proportional to about 1/2 power of the liquid film flow rate. Further, as a result of observation, it was found that heat exchange was promoted by replacing the concentrated solution with the diluted solution under the flow of the diluted solution.

Thus, the fact that the heat exchange performance is improved by increasing the liquid film flow rate, that is, the solution supply amount means that the pressure equilibrium temperature of the high temperature regenerator and the low temperature regenerator concentrated solution are increased by increasing the liquid film flow rate. The temperature difference from the outlet refrigerant vapor equilibrium temperature can be reduced. That is, the temperature difference can be controlled by adjusting the amount of spray liquid, and thus the pressure of the high temperature regenerator can be controlled.

An ejector is preferably used as a mechanism for sucking the concentrated solution from the low temperature regenerator. Such an ejector includes a driving liquid supply pipe for supplying the dilute solution from the absorber in a jet state, a liquid suction pipe for sucking the concentrated solution from the low temperature regenerator, and a discharge for mixing the concentrated solution with the dilute solution and delivering it. And a section.

Regarding the use of such an ejector,
It is possible to connect the liquid supply pipe to the liquid outflow pipe that is connected to the lower part of the low temperature regenerator and sends the concentrated solution from the low temperature regenerator, or the liquid suction pipe in parallel with the liquid outflow pipe. It can also be connected directly to the bottom of the.

As a means for adjusting the suction amount of the concentrated solution, a flow rate control valve can be provided in the liquid supply pipe. Further, regarding the structure in which the liquid suction pipe is provided in parallel with the liquid outflow pipe, a partition plate capable of partitioning the lower part of the low temperature regenerator into a part to which the liquid outflow pipe is connected and a part to which the liquid outflow pipe is connected is provided. It can be used as a means for adjusting the suction amount.

These adjusting means can be controlled on the basis of various information in the operating state, or can be controlled by utilizing the characteristics of the shape memory material based on the temperature.

Further, in the present invention, the solution spraying device is improved in order to improve the performance of the low temperature regenerator, particularly to improve the quality of the liquid film formation in the solution spraying. That is, in the solution spraying device according to the present invention, a distribution duct connected to the liquid introducing pipe for supplying the dilute solution to the low temperature regenerator and a gap serving as a flow path for the solution flow are formed in the distribution duct in the length direction. It is formed by one or a combination of two or more spraying units consisting of the droplet dispersion plates connected in this way.

In the solution spraying device of this solution spraying device, the solution supplied to the distribution duct flows down along the upper surface of the droplet dispersion plate from the flow path extending in the lengthwise direction as a gap between the solution and the droplet dispersion plate. By means of the flow along the upper surface of the droplet dispersion plate, it is possible to form a falling liquid film which is extremely uniform and has no film breakage.

Dispersing the solution with a highly uniform and stable liquid film in this way is more reliable for ensuring the effectiveness of the heat exchange performance control in the low temperature regenerator by adjusting the liquid film flow rate. It is extremely convenient from the point of view.

In order to make the liquid film formed by the droplet dispersion plate flow more uniformly, a plurality of notches are formed at appropriate intervals in the skirt of the droplet dispersion plate, and the notches form the solution. Are prevented from flowing in the length direction of the droplet dispersion plate.

Further, in the present invention, the performance of the low temperature regenerator is improved by efficiently removing the solution mist generated from the dilute solution sprayed in the low temperature regenerator. That is, the present invention devises a partition structure provided between the low-temperature regenerator and the condenser, and such a partition structure has a low-temperature regenerator from the top to the tip of the low-temperature regenerator. An upper partition plate vertically extending from the middle part to the lower part and a lower partition plate erected from the lower part of the low temperature regenerator at a height where the tip part overlaps the tip part of this upper partition plate, A combination is formed so that a passage leading from the low temperature regenerator side to the condenser side is formed in the overlapping portion of the tip portions.

According to such a partition structure, it is possible to give the refrigerant vapor a flow that flows in parallel with the downward direction of the diluted solution sprayed from above. As a result, the mist of the dilute solution can be made to flow downward, and can be efficiently captured and removed. In addition, the extremely simple structure of combining only the upper and lower partition plates allows the flow pressure loss of the refrigerant vapor flowing to the condenser side to be greatly reduced compared to, for example, the conventional eliminator, and the regeneration efficiency of the dilute solution. Can be improved.

[0026]

EXAMPLES Examples of the present invention will be described below. One embodiment of the absorption chiller-heater according to the present invention is, as shown in FIG. 1, similar to the conventional absorption chiller-heater, a high temperature regenerator 1, a low temperature regenerator 2, a condenser 3, an evaporator 4 and an absorber. 5, high temperature solution heat exchanger 6, low temperature solution heat exchanger 7, solution pump 8, refrigerant pump 9, cooling tower CT, eliminator 11, cooling / heating switching valve 12, bubble pump 13, bypass pipe 14, heating refrigerant conduit 15, heating A vapor conduit 16, a liquid refrigerant conduit 17, a solution spray pump 18, a dilute solution introducing pipe 19 and the like are provided, a solution spraying device 20 as shown in FIGS. 2 and 3, and an ejector 25.

The ejector 25 sucks a part of the concentrated solution sent from the low temperature regenerator 2 to the low temperature solution heat exchanger 7 via the concentrated solution outflow pipe 29, and supplies this to the dilute solution supplied to the low temperature regenerator 2. In addition to that. Specifically, the dilute solution whose pressure is increased by the solution pump 8 of the absorber 5 is ejected toward the discharge portion 28 by the nozzle-shaped drive liquid supply pipe 26, and thus the liquid suction pipe connected to the concentrated solution outflow pipe 29. The concentrated solution is sucked through 27, mixed with the diluted solution, and sent out from the discharge part 28 toward the diluted solution introducing pipe.

The solution spraying device 20 is composed of two spraying units 20u, and each spraying unit 20u is
It is composed of a distribution duct pipe 21 connected to a branch header 19a connected to the liquid introduction pipe 19, and a droplet dispersion plate 23 fitted into the distribution duct pipe 21 by a fitting mechanism portion 22. Here, the fitting mechanism portion 22 is a recess at a constant interval formed in the central portion of the distribution duct pipe 21, and the liquid dispersion plate 23 is also formed with a similar recess. A section without the fitting mechanism section 22 forms a gap 22a extending in the lengthwise direction, which serves as a flow path for the solution to flow from the distribution duct tube 21 onto the droplet dispersion plate 23, and in the axial direction of the heat transfer tube. Acts as an orifice for uniform distribution of the solution. Then, the liquid flowing out from the gap 22a flows gently on the upper surface of the droplet dispersion plate 23 by rapidly expanding the flow path on the upper surface of the droplet dispersion plate 24 bent in an L shape, and the droplets are splashed. Occurrence is prevented. Further, the skirt portion 24 of the droplet dispersion plate 23
A cutout portion 24c is provided in this to prevent the solution flowing on the droplet dispersion plate 23 from flowing in the axial direction of the heat transfer tube and flowing down in large quantities from one location. Further, even if the temperature of the spray solution is high and the vapor pressure is higher than the pressure inside the machine, self-evaporation occurs while flowing over the droplet dispersion plate 23, so that droplets of droplets are generated. The boiling that causes it is prevented. As a result, a uniform liquid film is formed on the heat transfer tube over a wide liquid flow rate range.

The operation of such an absorption chiller-heater is as follows. The dilute solution sprayed from the solution spraying device 20 on the heat transfer tube group 2a of the low temperature regenerator 2 forms a liquid film outside the heat transfer tube and flows down, during which the high temperature regenerator 1 is introduced into the heat transfer tube.
The refrigerant is heated by the latent heat of condensation of the refrigerant vapor generated in the above to generate the refrigerant vapor and is condensed. The concentrated solution generated in the low temperature regenerator 2 is sent to the low temperature solution heat exchanger 7 through the outflow pipe 29, and a part of the concentrated solution is branched and sucked by the ejector 25 as described above to the low temperature regenerator 2. Is mixed with a dilute solution of.

As a result, the low temperature regenerator 2 is sprayed with a larger amount of solution than the circulating dilute solution in the usual case, and a high heat transfer coefficient is obtained for the reasons described above. Therefore, the heat transfer area of the low-temperature regenerator can be reduced according to the increase in the heat transfer coefficient, and resource saving can be achieved.

In the condenser 3, the refrigerant vapor of the low-temperature regenerator 2 and the refrigerant vapor from the high-temperature regenerator 1 passing through the low-temperature regenerator 2 are condensed while being cooled by the cooling water CW to be a liquid refrigerant, and the liquid refrigerant conduit 17 Is sent to the evaporator 4 via. Evaporator 4
The liquid refrigerant is sprayed on the heat exchanger by the refrigerant pump 9 and removes heat from the cold water 4a to be evaporated and vaporized and guided to the absorber 5. On the other hand, the concentrated solution produced in the high temperature regenerator 1 is mixed with the concentrated solution produced in the low temperature regenerator 2 via the high temperature solution heat exchanger 6 and passes through the low temperature solution heat exchanger 7 to generate a pressure difference and a head difference. It is guided to the absorber 5 and sprayed onto the heat exchanger by the solution spray pump 18. The concentrated solution sprayed on the heat exchanger of the absorber 5 absorbs the refrigerant vapor from the evaporator 4 while being cooled by the cooling water CW to generate a dilute solution, and the solution pump 8 cools the high temperature regenerator 1 and the low temperature solution. It is sent to each of the regenerators 2. The absorption cooling cycle is configured as described above.

In the cycle having the above construction, when the pressure of the high temperature regenerator 1 becomes high, the differential pressure of the high temperature regenerator circulation amount adjusting orifice 40 becomes large, so that the amount of solution circulating liquid in the high temperature regenerator 1 increases. As a result, the amount of liquid passing through the low temperature heat exchanger 7 also increases, and the pressure loss of the low temperature heat exchanger 7 increases. However, the solution spray pump 18 is arranged at the outflow end of the concentrated solution of the low temperature heat exchanger, which requires a substantially constant suction head. Therefore, the increase in the pressure loss of the low temperature heat exchanger 7 causes the rise of the liquid level formed in the concentrated solution outflow pipe 29 which connects the low temperature regenerator 2 and the low temperature heat exchanger 7. As a result, the amount of solution flowing into the liquid suction pipe 27 is larger when the liquid level formed in the concentrated solution conduit 29 is higher. Therefore, the higher the pressure of the high temperature regenerator 1, the amount of sprayed liquid of the low temperature regenerator 2. Will be achieved to provide a high heat transfer coefficient, which is a very convenient self-control function for safe operation of the cycle. When the pressure of the low temperature regenerator 2 is low, the liquid level formed in the concentrated solution conduit 29 also rises, so that the liquid film flow rate of the low temperature regenerator 2 increases and a high heat transfer coefficient is obtained, thus saving energy. Can be achieved.

During heating, the refrigerant pump 9 is stopped and the cooling / heating switching valve 12 is opened. After the refrigerant vapor generated in the high temperature regenerator 1 is sufficiently lowered below the refrigerant liquid level in the evaporator 4 via the branch pipe 16 branched from the heat transfer pipe header portion of the low temperature regenerator 2 and the cooling / heating switching valve 12, 2 Be divided. Then, one of them passes through the bubble pump 13 and the absorber 5
Be led to. The other one is guided to the evaporator 4 via the bypass pipe 14 and exchanges heat with the hot water 4b flowing in the heat transfer pipe of the evaporator 4 to be condensed and liquefied. This liquid refrigerant is guided to the bubble pump 13 via the heating liquid refrigerant conduit 15, and is sent to the absorber 5 by the bubble pump action of the refrigerant vapor from the high temperature regenerator 1. The solution in the absorber 5 is sent by the solution pump 8 and passed through the low temperature heat exchanger 7 and then halved. One is sent to the low temperature regenerator 2 via the ejector 25, and the other is further heated to the high temperature heat exchanger 6. Is sent to the high temperature regenerator 1 via the flow control valve. In the low temperature regenerator 2, the solution is sprinkled on the heat transfer tubes, but no refrigerant vapor is generated, so that the condenser 3 does not perform condensation. Further, the solution spray pump 18 is stopped, and the hot concentrated solution is returned to the absorber 5 via the bypass pipe 41 without being sprayed to the heat transfer pipe of the absorber 5.

As explained above, in the so-called parallel flow absorption cooling cycle in which the dilute solution is fed back to the high temperature regenerator 1 and the low temperature regenerator 2 in this embodiment, the pressure inside the high temperature regenerator 1 fluctuates. The heat transfer amount control for automatically controlling the liquid film flow rate of the low temperature regenerator 2 in a self-controllable direction is performed, and the high performance and downsizing of the low temperature regenerator 2 can be achieved.

FIG. 4 shows another embodiment of the present invention. The difference between this embodiment and the above-mentioned embodiment is that the liquid suction pipe 27 is directly connected to the lower portion of the low temperature regenerator 2 and Lower part A of the low temperature regenerator connected with the suction pipe 27 and the concentrated solution outflow pipe 29
That is, the partition plate 31 is provided so as to partition the lower part B of the connected low temperature regenerator.

That is, the lower plate A and the lower plate B are separated by the partition plate 31.
When the and are partitioned, the concentrated solution accumulates on the lower side A, and the amount of the concentrated solution flowing into the liquid suction pipe 27 increases. On the other hand, when this partition is stopped, the amount of concentrated solution flowing into the liquid suction pipe 27 is reduced as compared with the case where the partition is provided. Therefore, by selecting these, the liquid film flow rate in the low temperature regenerator 2 can be changed and the heat transfer coefficient can be controlled.

At the fulcrum 32 of the partition plate 31, for example, about 8
Shape memory alloys that regain their shape at 0 ° C can be used. In this case, when the temperature is low, the partition plate 31 rotates to stop the partition at the lower part of the low temperature regenerator, so that the liquid film flow rate of the low temperature regenerator 2 is small and therefore the heat transfer coefficient is low, so that the high temperature regenerator 1 is
The pressure becomes relatively high. Such an operating condition is when the cooling water temperature is low, and in the normal case, the high temperature regenerator 1 is used.
The internal pressure of the reactor decreases and the amount of solution circulation decreases, resulting in an increase in the concentration difference between the dilute solution and the concentrated solution, the limit of which is the crystallization of the concentrated solution produced in the high temperature regenerator 1. However, in the case of the present invention, it is possible to control the liquid film flow rate in the low temperature regenerator 2 as described above, and by this control, the heat transfer coefficient is reduced to increase the pressure in the high temperature regenerator 1 and the solution circulation amount. Can be prevented. That is, the operation can be performed even at a lower cooling water temperature without causing crystallization of the concentrated solution.

FIG. 5 shows still another embodiment of the present invention. The feature of this embodiment is that a flow control valve 35 is provided in a liquid suction pipe 27 in which a concentrated solution conduit 29 branches to communicate with an ejector 25.
In addition, the eliminator 11 in FIG. 1 is abolished, and the upper partition plate 33 that partitions the low temperature regenerator 2 from the upper part to the middle and the lower partition plate 34 that partitions the condenser 3 side from the lower part to the middle are disposed. is there. Flow control valve 35
Can detect and control the state quantity of time or cycle, for example, the solution temperature of the low temperature regenerator 2, the pressure and temperature of the high temperature regenerator 1, the cooling water temperature and the like. Further, when the machine is started by a timer, the flow rate control valve 35 is closed to reduce the heat transfer coefficient in the low temperature regenerator and increase the pressure in the high temperature regenerator 1 to improve the solution circulation in the high temperature regenerator 1 and It is also possible to spray the accumulated concentrated solution on the absorber 5 early so that the cooling capacity can be exerted quickly. Of course, when it is desired to maximize the cooling capacity, the control valve 35
It is also possible to increase the liquid film flow rate of the low temperature regenerator 2 by opening the air conditioner to achieve high efficiency operation due to the high heat transfer coefficient.

By providing a pair of upper and lower partition plates 33 and 34 instead of the eliminator, the refrigerant vapor generated in the low temperature regenerator 2 can be directed downward from the top together with the spray solution. That is, it is possible to form a flow of the refrigerant vapor that flows in parallel with the flow direction of the solution. As a result, the solution mist slightly generated on the heat transfer tube is given a downward flow and easily drops. Then, only the refrigerant vapor is inverted and goes upward in the lower part, and is sent to the condenser 3 side through a passage formed in a portion where the upper partition plate 33 and the lower partition plate 34 overlap each other at their tip ends. The solution mist is captured by collision of the concentrated solution accumulated in the lower part or the side lower partition plate 34 and remains in the low temperature regenerator 2, so that the solution mist is efficiently removed.

Further, the partition structure of the upper partition plate 33 and the lower partition plate 34 has a low temperature regenerator 2 to a condenser 3
Since the flow pressure loss of the refrigerant vapor flowing to is reduced, it contributes to the high performance of the low temperature regenerator 2 and the condenser 3.

Further, another embodiment of the present invention is shown in FIG.
This example differs from the example shown in FIG. 1 in the solution flow and heating cycle.

First, regarding the flow of the solution, the entire amount of the dilute solution in the absorber 5 is sent to the low temperature regenerator 2 via the low temperature heat exchanger 7 and the ejector 25. A part of the concentrated solution in the low temperature regenerator 2 is sent to the high temperature regenerator 1 via the high temperature heat exchanger 6 and the control valve by the auxiliary circulation pump 36 via the concentrated solution outflow conduit 29a. The concentrated solution in the high temperature regenerator 1 is mixed with the remaining concentrated solution in the low temperature regenerator 2 through the high temperature heat exchanger 6 and the orifice 40 in the concentrated solution outflow conduit 29b, and is passed through the low temperature heat exchanger 7 to the solution spray pump. It is sprayed on the absorber 5 by 18. In this embodiment, a large amount of solution is sprayed on the low temperature regenerator 2 and a high heat transfer coefficient can be obtained. Further, in this embodiment, the liquid suction pipe 27 of the ejector 25 is connected to the concentrated solution outflow conduit 29b via the flow rate control valve 35, and the same effect as in the embodiment of FIG. 5 can be obtained. Note that the piping configuration in the embodiment of FIG. 4 or 2 can also be applied to the flow of this embodiment.

In the heating cycle of this embodiment, the refrigerant pump 9 is operated even during heating, and the liquid refrigerant in the evaporator 4 is sent to the absorber 5 by opening the blow valve 42. Further, the refrigerant vapor generated from the high temperature regenerator 1 is guided to the steam generator 4 through the heating vapor conduit 16 by opening the cooling / heating switching valve 12. The dilute solution in the absorber 5 is sent to the low temperature regenerator 2 by the solution pump 8 and further to the high temperature regenerator 1 by the solution auxiliary pump 36. The circulation of the concentrated solution in the high temperature regenerator 1 is the same during cooling.

Such a heating cycle can be applied to the embodiment of FIG. 1 if necessary. Further, it is easy for those skilled in the art to apply the present invention shown in each of the above-mentioned embodiments to other cycle flows and multiple-effect cycles.

[0045]

Since the present invention is as described above, it has the following effects. (1) It is possible to improve the heat exchange performance and control it by adjusting the amount of solution sprayed by spraying the solution added by sucking a part of the concentrated solution of the low temperature regenerator into the low temperature regenerator. Therefore, it is possible to reduce the size of the low-temperature regenerator and adjust the pressure inside the high-temperature regenerator according to the temperature environment during operation, resulting in an efficient operating condition even at lower temperatures. Can be secured.

(2) A solution spraying device is formed by using a spraying unit consisting of a distribution duct for receiving the distribution of the solution and a droplet spraying plate for allowing the solution to flow down from the distribution duct with a uniform liquid film. Since it is possible to perform spraying with a highly uniform and stable liquid film, it is possible to perform more efficient regeneration treatment, and it is possible to improve the effectiveness of heat exchange control by adjusting the liquid amount.

(3) The partition structure between the low temperature regenerator and the condenser is formed by combining the upper and lower partition plates, and the refrigerant vapor is allowed to flow in the direction in which the solution flows downward and in parallel. As a result, it is possible to effectively prevent the mixture of the solution mist in the refrigerant vapor sent to the condenser, so that the passage of the refrigerant vapor can be reduced in pressure and the regeneration efficiency of the dilute solution can be improved. it can.

[Brief description of drawings]

FIG. 1 is a system flow diagram of an absorption chiller-heater showing an embodiment of the present invention.

FIG. 2 is a piping system diagram around a low temperature regenerator.

FIG. 3 is a cross-sectional perspective view of a solution spraying device.

FIG. 4 is a system flow diagram of a low temperature regenerator of an absorption chiller-heater showing another embodiment of the present invention.

FIG. 5 is a system flow diagram of a low-temperature regenerator of an absorption chiller-heater showing still another embodiment of the present invention.

FIG. 6 is a system flow diagram of an absorption chiller-heater according to still another embodiment of the present invention.

FIG. 7 is a system flow diagram of a conventional absorption chiller-heater.

FIG. 8 is a graph showing an example of experimental data of liquid film flow rate and horizontal extra-tube evaporation heat transfer coefficient of the low temperature regenerator.

[Explanation of symbols]

 1 High-temperature regenerator 2 Low-temperature regenerator 3 Condenser 4 Evaporator 5 Absorber 6 High-temperature solution heat exchanger 7 Low-temperature solution heat exchanger 8 Solution pump 9 Refrigerant pump CT Cooling tower CW Cooling water 11 Eliminator 4a Cold water 4b Hot water 12 Cold / warm switching Valve 13 Bubble pump 14 Bypass pipe 15 Heating liquid refrigerant conduit 16 Heating vapor conduit 17 Liquid refrigerant conduit 18 Solution spray pump 19 Dilute solution introducing pipe 19a Liquid header 20 Spraying device 21 Liquid distribution duct pipe 22 Fitting structure part 22a Gap channel 23 Droplet dispersion plate 24 Notch portion 25 Ejector 26 Ejector driving liquid introduction pipe 27 Ejector liquid suction pipe 28 Ejector liquid discharge pipe 29 Low temperature regenerator concentrated solution pipe 30 Flow control mechanism 31 Partition plate 32 Partition plate fulcrum 33 Low temperature regenerator side plate 34 Condenser side plate 35 Flow control valve 36 Auxiliary circulation Amplifier 40 the high-temperature regenerator concentrated solution flow rate adjusting orifice 41 solution bypass pipe 42 refrigerant blow valve

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Tatsuro Fujii 502 Jinritsu-cho, Tsuchiura-shi, Ibaraki Hiritsu Manufacturing Co., Ltd.Mechanical Research Laboratory (72) Inventor Go Nakao 603 Jinritsu-cho, Tsuchiura-shi, Ibaraki Hiritsu Manufacturing Co., Ltd. Tsuchiura factory

Claims (13)

[Claims] 1. An absorption chiller-heater in which a dilute solution sent from an absorber is regenerated into a concentrated solution by evaporation of a refrigerant vapor in a high temperature regenerator and a low temperature regenerator, respectively. An absorption chiller-heater characterized in that a portion is sucked and the sucked concentrated solution is added to a dilute solution supplied to a low temperature regenerator. 2. A driving liquid supply pipe for supplying the diluted solution from the absorber in a jetted state, a liquid suction pipe for sucking the concentrated solution from the low temperature regenerator, and a discharge part for mixing the concentrated solution with the diluted solution and sending it out. 2. The absorption chiller-heater according to claim 1, wherein the ejector provided with is used for sucking a concentrated solution. 3. The absorption chiller-heater according to claim 2, wherein a liquid suction pipe is connected to a lower portion of the low-temperature regenerator and a liquid outflow pipe for feeding a concentrated solution from the low-temperature regenerator. 4. The liquid suction pipe, which is connected to a lower portion of the low temperature regenerator and is arranged in parallel with a liquid outflow pipe for feeding a concentrated solution from the low temperature regenerator, is directly connected to a lower portion of the low temperature regenerator. Absorption cold water heater. 5. The absorption chiller-heater according to claim 3, wherein the liquid suction pipe is provided with a flow control valve for adjusting the suction amount of the concentrated solution. 6. The absorption chiller-heater according to claim 5, wherein the suction amount is adjusted according to the characteristics of the shape memory material based on the temperature of the flow control valve image. 7. The absorption chiller-heater according to claim 4, wherein a partition plate capable of partitioning a lower portion of the low temperature regenerator is provided in a portion to which the liquid outflow pipe is connected and a portion to which the liquid suction pipe is connected. .. 8. The absorption chiller-heater according to claim 7, wherein the partition state of the partition plate is adjusted by the characteristics of the shape-memory material based on temperature. 9. In an absorption chiller-heater equipped with a low-temperature regenerator that regenerates a concentrated solution while spraying a dilute solution from an absorber with a solution-dispersing device disposed above, the solution-dispersing device is a low-temperature regenerator. It is composed of a distribution duct connected to a liquid introduction pipe for supplying a dilute solution, and a droplet dispersion plate connected to the distribution duct so as to form a gap serving as a flow path for solution flow in the length direction. An absorption chiller-heater characterized by being formed by one or a combination of two or more spraying units. 10. The absorption chiller-heater according to claim 9, wherein notches are formed at appropriate intervals on the skirt of the droplet dispersion plate. 11. An absorption chiller-heater in which a low-temperature regenerator and a condenser are juxtaposed through a partition structure configured to send only refrigerant vapor in the low-temperature regenerator to the condenser. Is an upper partition plate that extends from the top of the low-temperature regenerator so that its tip goes below the middle part of the low-temperature regenerator, and low-temperature regeneration at a height where the tip overlaps the tip of this upper partition. It is characterized in that it is formed by combining a lower partition plate erected from the lower part of the vessel so that a passage communicating from the low temperature regenerator side to the condenser side is formed at the overlapping portion of the tips of both. Absorption chiller / heater. 12. The dilute solution from the absorber is supplied in parallel to each of the high temperature regenerator and the low temperature regenerator.
11. The absorption chiller-heater according to any one of 11. 13. The method according to claim 1, wherein all of the dilute solution from the absorber is first supplied to the low temperature regenerator, and the solution via the low temperature regenerator is sent to the high temperature regenerator. Absorption cold water heater.