KR19980087189A - Absorption Refrigeration Unit - Google Patents

Abstract

(Problem) The efficiency of the absorption cycle does not decrease in the wide cooling capacity from the maximum cooling capacity to the partial cooling capacity.

(Solution means) In the refrigerant liquid spreading port 42, between the refrigerant liquid storage part 422 and the refrigerant liquid outlet part 423 of the refrigerant liquid storage container 420 for storing the supplied refrigerant liquid. An orifice 421A for restricting the flow rate of the refrigerant liquid passing through is formed below the partition plate 421. When the coolant capacity is large and the flow rate of the coolant liquid supplied from the condenser 5 is large, the coolant liquid is limited at the orifice 421A, so that the flow rate of the coolant liquid supplied to the evaporator 4 is decreased, so that the concentration of the absorbent liquid in the absorption cycle is increased. As a result, a large refrigerant capacity can be secured. If the cooling capacity is small and the refrigerant flow rate from the condenser 5 is small, the refrigerant liquid is not limited to the orifice 421A. Therefore, the concentration of the absorption liquid in the absorption cycle decreases, and the refrigerant vapor is easily generated even with a small heating amount. .

Description

Absorption Refrigeration Unit

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to an absorption refrigeration apparatus having an absorption cycle including an aqueous solution such as lithium bromide as an absorption liquid, and more particularly, to a refrigerant flow path structure in an absorption cycle for ensuring efficient cooling capacity regardless of the size of the cooling load. will be.

In an absorption type refrigerating device, a low concentration absorbent liquid is heated and boiled by a burner in a regenerator to separate a high concentration absorbent liquid and a refrigerant vapor. The refrigerant vapor separated from the regenerator is cooled in the condenser to form a refrigerant liquid. When the high concentration absorbent liquid separated from the regenerator is scattered on the surface of the absorption tube (absorption coil) in the absorber, and the refrigerant liquid is dispersed in the evaporator tube (evaporation coil) in the evaporator installed through the absorber, the refrigerant liquid evaporates on the surface of the evaporator tube. The evaporated heat is evaporated from the cold and hot water passing through the tube. On the other side of the absorber tube, the high concentration absorbent absorbs the refrigerant vapor and evaporates it.

The cold and hot water deprived of heat from the evaporator tube circulates through the heat exchanger formed as a cooling target by the operation of the pump, and becomes a cooling source in the cooling target. The hot and cold water, which has risen in reverse from the heat exchanger, is cooled again in the evaporator.

On the other side, the heat generated when the absorbent liquid absorbs the refrigerant vapor on the surface of the absorber tube is moved to the cooling tower installed outside and discharged from the cooling tower by the array cooling water passing through the absorber tube by the operation of the pump.

The absorption cycle is configured so that the absorption liquid absorbed with the refrigerant liquid in the absorber and reduced in concentration is returned to the regenerator by the absorption liquid pump.

In the absorption type refrigerating device having the above structure, the cooling capacity is changed by the heat amount of the burner heating the regenerator, and when the required cooling capacity is large, the heating amount in the regenerator is increased to increase the temperature difference and the pressure difference of each part. This increases the amount of refrigerant generated in the absorbent liquid and increases the amount of circulation of the absorbent liquid. Therefore, the amount of refrigerant evaporated in the evaporator and the amount of refrigerant absorbed by the absorbent liquid in the absorber are promoted, and a large cooling capacity is ensured by the amount of evaporated at that time.

On the contrary, when the required cooling capacity is small, the amount of heat generated in the regenerator is reduced to reduce the temperature difference and the pressure difference of each part, thereby reducing the amount of refrigerant generated and the amount of circulation of the absorbing liquid. Therefore, the cooling capacity is suppressed by reducing the amount of evaporation of the refrigerant liquid in the evaporator and the amount of refrigerant absorbed by the absorption liquid in the absorber.

As described above, in the conventional absorption cycle, the heating amount is changed according to the required cooling capacity, but the heat exchange capacity, the concentration of the absorbing liquid, and the like of each device in the absorption cycle are set according to the maximum cooling capacity. Therefore, when operating at the maximum cooling capacity, each part functions sufficiently to secure the necessary cooling capacity. However, when operating at the partial cooling capacity that does not reach the maximum cooling capacity, the necessary capacity of the heat exchange area of each part is inherently necessary. In contrast, since the efficiency of the absorption cycle was improved, the efficiency of the absorption cycle was lowered.

The cause of such a problem is as follows.

Conventionally, since the concentration of the absorbing liquid in the entire absorption cycle is set so that the refrigerant vapor can be appropriately generated by the heating amount given during the operation at the maximum cooling capacity, even when the operation is performed at the partial cooling capacity, the regenerator The internal temperature is the same as when operating at the maximum cooling capacity, and the temperature rises to the temperature at which the absorbing liquid boils. Therefore, the pressure in the regenerator is increased so that the pressure difference in the condenser and the evaporator is increased, so that the amount of circulation of the absorbent liquid is excessive with respect to the driving ability, even though it is a partial cooling capacity. For this reason, most of the heating amount given to the regenerator is required for raising the temperature of the absorbing liquid, and the amount of heat used for evaporating the refrigerant is small, so that the ratio of the amount of refrigerant vapor generation to the given heating amount is small.

Therefore, the amount of refrigerant liquid obtained in the condenser decreases, and accordingly, the amount of refrigerant liquid supplied to the evaporator decreases, so that the heat of evaporation taken away from the evaporator coil in the evaporator decreases, resulting in a decrease in cooling capacity, which results in a decrease in the efficiency of the absorption cycle. Was brought.

Therefore, in order to increase the amount of refrigerant generated at the time of partial cooling capacity, the condition for promoting the generation of the refrigerant is given, that is, the concentration of the absorbent liquid as a whole in the absorption cycle may be reduced. However, this also lowers the concentration of the high concentration absorbent itself, and conversely, at the maximum cooling capacity, the concentration of the high concentration absorbent liquid to be supplied to the absorber is not sufficiently high, thereby lowering the absorption capacity and causing a decrease in the cooling capacity. There is a problem.

It is an object of the present invention to obtain an appropriate cooling capacity without reducing the efficiency of the absorption cycle in a wide range of cooling capacity from the maximum cooling capacity to the partial cooling capacity.

1 is a schematic configuration diagram of an air conditioning apparatus showing an embodiment of the present invention.

Figure 2 is a partial cross-sectional view of the freezer body showing the assembly portion with the condenser and the evaporator in an embodiment of the present invention.

Figure 3 is a perspective view of a freezer body showing the assembly portion of the refrigerant liquid dispersion port and the evaporation coil of the evaporator in the embodiment of the present invention

Figure 4 is a plan view showing a refrigerant liquid dispersion port in an embodiment of the present invention

Figure 5 is a side view showing a refrigerant liquid dispersion port in an embodiment of the present invention

6 is a cross-sectional view taken along the line A-A in FIG.

Figure 7 is a partial cross-sectional view of the freezer body of the assembly portion with the condenser and evaporator for showing another embodiment of the present invention.

Explanation of symbols for main parts of the drawings

101-Refrigerator body (absorption refrigeration unit) 1-High temperature regenerator

2-Low Temperature Regenerator 3-Absorber

4-Evaporator 420-Refrigerant liquid storage container (concentration adjusting means)

421A-Orifice (refrigerant flow rate adjusting means, refrigerant liquid flow rate limiting means)

22-Refrigerant liquid storage part (open refrigerant liquid storage container)

5-condenser P1-absorbent pump

The present invention relates to a regenerator for heating an absorption liquid containing a refrigerant to separate refrigerant vapor from the absorption liquid, a condenser for cooling and condensing the refrigerant vapor separated by the regenerator, and a refrigerant condensed in the condenser. An evaporator for evaporating the liquid at low pressure, an absorber for absorbing the refrigerant vapor evaporated in the evaporator into the absorbent liquid supplied from the regenerator, and a pump for returning the absorbent liquid from the absorber to the regenerator in an absorption type refrigeration apparatus. The technical means is that a concentration adjusting means for adjusting the concentration of the absorbing liquid in the regenerator is provided during the absorption cycle.

2. The technical means according to claim 1, wherein the concentration adjusting means is a refrigerant amount adjusting means for adjusting the amount of refrigerant circulating in the absorption cycle in the process of being supplied from the condenser to the evaporator.

3. The technical means according to claim 2, wherein the refrigerant amount adjusting means is a refrigerant liquid flow rate limiting means for restricting a flow rate of the refrigerant liquid supplied from the condenser to the evaporator.

The method according to claim 3, wherein the refrigerant liquid flow rate limiting means is composed of an open refrigerant liquid storage container for storing the refrigerant liquid supplied from the condenser and an orifice formed under the refrigerant liquid storage container as technical means. .

With the above configuration, in the present invention, when the absorbent liquid containing the refrigerant is heated in the regenerator, the refrigerant vapor is separated from the absorbent liquid, and the refrigerant vapor separated from the regenerator is cooled and condensed in the condenser to form a refrigerant liquid. On the other hand, the absorbent liquid concentrated in the regenerator by separation of the refrigerant is supplied to the absorber.

When the absorbent liquid absorbs the refrigerant vapor in the absorber, the evaporation of the refrigerant liquid supplied into the evaporator connected to the absorber is promoted, and the inside of the evaporator is cooled by the heat of evaporation to become a cooling source for cooling.

The absorbent liquid whose concentration is lowered by absorbing the refrigerant in the absorber is returned to the regenerator by the absorbent liquid pump, and repeatedly removes the refrigerant vapor so that the absorbent liquid and the refrigerant circulate in the absorption cycle.

In the circulation of the refrigerant in the absorption cycle as described above, as the concentration of the absorption liquid in the regenerator decreases, the pressure difference in each part in the absorption cycle decreases and the circulation amount of the absorption liquid decreases. For this reason, the amount of heat (sensible heat amount) required to raise the temperature of the absorbent liquid to the boiling point in the regenerator becomes small, and most of the heat amount can be used as the heat amount (latent heat amount) for evaporating the refrigerant.

In addition, as the boiling point decreases due to the decrease in concentration, the temperature of the container portion itself of the regenerator decreases, so that the amount of heat (heatrose) that is not used for heating the absorbing liquid and radiated to the outside from the regenerator is reduced. For this reason, the refrigerant can be separated even with a small heating force.

EMBODIMENT OF THE INVENTION Hereinafter, embodiment of this invention is described in detail based on drawing.

1 shows an embodiment of an air conditioning apparatus according to the present invention.

The air conditioner is an absorption type refrigeration apparatus, which is composed of an outdoor unit 100 and an indoor unit (RU), and the outdoor unit 100 is composed of a refrigerator main body 101 and a cooling tower (cooling tower; CT). In addition, the air conditioning apparatus is controlled by the controller 102.

The refrigerator main body 101 is formed mainly of stainless steel to form an absorption cycle of a lithium bromide aqueous solution as a refrigerant and an absorbing liquid. The high temperature regenerator 1 provided with a gas burner B as a heating means at the lower side, and this high temperature Dual-use type regenerators composed of low temperature regenerators 2 disposed to cover the outside of the regenerators 1, and also absorbers 3 and evaporators 4 arranged in order outwardly on the outer periphery of the low temperature regenerators 2; And the condenser 5 disposed above the absorber 3 and the evaporator 4 in the outer circumference of the low temperature regenerator 2 through several passages.

In addition, the absorbent contains an inhibitor for suppressing corrosion caused by the reaction between stainless steel and lithium bromide.

The high temperature regenerator 1 is installed by extending the medium absorbent liquid separation cylinder 12 above the heating tank 11 heated by the gas burner B, and the high temperature regenerator 1 is installed above the medium concentration absorbent liquid separation cylinder 12. A vertical cylindrical hermetic refrigerant recovery tank 10 is provided to cover the outer circumference.

Under the inner side of the medium concentration absorbent liquid separation container 12, the absorption liquid partition container 13 arrange | positioned at intervals between the inner wall of the medium concentration absorbent liquid separation cylinder 12, and several places of the upper peripheral part are carried out the medium concentration absorbent liquid. An absorbent liquid ascending flow passage 14 in which the absorbent liquid heated in the heating tank 11 rises between the medium absorbent liquid separation cylinder 12 and the absorbent liquid partition vessel 13, which is bonded to the inner side of the separating cylinder 12. Is formed.

In the medium concentration absorbent liquid separation vessel 12 above the absorbent liquid partition vessel 13, an absorbent liquid return plate 15 for returning the absorbent liquid rising up the absorbent liquid flow passage 14 is provided. The cylinder 12 consists of two upper and lower members of the upper member positioned above the absorbent liquid return plate 15 and the lower member positioned lower, and these are joined to the absorbent liquid return plate 15 by welding. will be.

On the side of the absorbent liquid partition vessel 13, an inflow path of the medium absorbent liquid flow path L1 for supplying the medium concentration absorbent liquid separated and highly concentrated to the low temperature regenerator 2 is opened, and the absorbent liquid partition vessel 13 The inflow path of the heating absorbent liquid flow path L4 for supplying the absorbent liquid heated at the time of a heating operation to the evaporator 4 is opened at the bottom part.

Inside the refrigerant recovery tank 10, a refrigerant compartment 17 for forming a thermal insulation gap 17a between the medium absorbent liquid separator 12 is joined to the medium absorbent liquid separator 12. It is. Therefore, the heat in the medium concentration absorbent liquid separation cylinder 12 is blocked, so that the refrigerant in the refrigerant recovery tank 10 is not heated by the high temperature absorbent liquid in the absorbent liquid rising passage 14.

The refrigerant recovery tank 10 outside the refrigerant compartment 17 is a refrigerant reservoir 10a in which the separated refrigerant is stored, and the refrigerant passage 10a communicates with the condenser 5 in the refrigerant reservoir (10a). The inlet of L5) is open.

With the above configuration, in the high temperature regenerator 1, the low concentration absorbent liquid contained in the heating tank 11 is heated by the gas burner B to evaporate water as the refrigerant in the low concentration absorbent liquid, and the medium concentration as the refrigerant vapor (water vapor). The medium absorbent liquid separated from the absorbent liquid separating vessel 12 and concentrated by the evaporation of the refrigerant vapor is returned to the inner absorbent liquid partition vessel 13 of the medium absorbent liquid separating vessel 12, and the medium absorbent liquid flow passage L1. Is supplied to the low temperature regenerator (2). In addition, the separated refrigerant vapor is recovered from the refrigerant recovery tank 10 and supplied to the condenser 5 through the refrigerant passage L5.

The low temperature regenerator 2 has a vertical cylindrical low temperature regenerator case 20 provided eccentrically on the outer circumference of the refrigerant recovery tank 10, and a refrigerant vapor outlet 21 is formed around the ceiling of the low temperature regenerator case 20. It is.

The ceiling head portion of the low temperature regenerator case 20 is connected to the inside of the absorbent liquid partition vessel 13 in the medium absorbent liquid separation tank 12 through the heat exchanger H by the medium absorbent liquid flow path L1.

In the medium absorbent liquid flow path L1, an orifice (not shown) for restricting the flow rate of the medium absorbent liquid flowing from the absorbent liquid partition vessel 13 to the low temperature regenerator 2 is formed, and the medium concentration is contained in the low temperature regenerator case 20. The medium absorbent liquid is supplied by the pressure difference from the absorbent liquid separator 12 (about 70 mmHg in the low temperature regenerator case 20 and about 700 mmHg in the medium absorbent liquid separator 12).

Therefore, the low temperature regenerator 2 reheats the medium concentration absorbent liquid supplied into the low temperature regenerator case 20 as the heat source as the heat source, and the medium concentration absorbent liquid is separated from the gas liquid at the upper portion of the low temperature regenerator case 20. In the section 22, the refrigerant vapor and the high concentration absorbent liquid are separated, and the high concentration absorbent liquid is stored in the high concentration absorbent liquid receiver 23.

At the bottom of the high concentration absorbent liquid receiving part 23, an inlet port of the high concentration absorbent liquid flow path L2 communicating with the absorber 3 is opened.

The outer periphery of the low temperature regenerator case 20 is a cylindrical type, and the airtight evaporation / absorption case 30 is concentrically arranged at the bottom and the condenser case 50 is arranged at the top, respectively, and the refrigerant recovery tank 10 and the low temperature regenerator are respectively arranged. The case 20 and the evaporation / absorption case 30 are integrally welded to the bottom plate portion 18, and the inner end of the bottom plate portion 18 is connected to the lower member 12b of the medium absorbent liquid separator 12. It is welded to the outer circumferential surface to form the refrigerator main body 101.

In addition, the low temperature regenerator case 20 communicates with the inside of the condenser case 50 through the refrigerant vapor outlet 21 and the gap 5A.

The absorber 3 is an absorption coil wound in a coil shape as an absorption tube in which a copper tube is formed in a vertical cylindrical shape between an inner portion of the evaporation / absorption case 30 and the low temperature regenerator case 20 and a cooling water for array flows therein. (31) is arranged, and a high concentration absorbent liquid dispersion port (32) for dispersing a high concentration absorbent liquid on the absorbent coil (31) is disposed above the absorbent coil (31).

As shown in FIG. 2, the high concentration absorbent liquid dispersion port 32 is supplied to the high concentration absorbent liquid passage L2 connected to the high concentration absorbent liquid receiver 23 of the low temperature regenerator 2 through the heat exchanger H. Two formed in order to evenly distribute and drop the absorbent liquid cooling container 32a to collect and cool down by collecting the same, respectively, on each circumference of the absorbent coil 31 which is double-wound inside and outside the absorbent liquid collected in the absorbent liquid cooling container 32a. Two absorption liquid dispersion tubes 32b.

By the above structure, in the absorber 3, the high concentration absorbent liquid of the high concentration absorbent liquid receiving part 23 of the low temperature regenerator 2 flows in from the high concentration absorbent liquid flow path L2 by the pressure difference, and the high concentration absorbent liquid which flowed in is in the high concentration absorbent liquid dispersion opening. (32) is scattered on the upper end of the absorption coil (31), adheres to the surface of the absorption coil (31) to form a thin film, and flows downward by the action of gravity to absorb water vapor to form a low concentration absorption liquid. When absorbing this water vapor, heat is generated on the surface of the absorption coil 31, but is cooled by the array cooling water circulating in the absorption coil 31. In addition, water vapor absorbed by the absorbing liquid is generated as refrigerant vapor in the evaporator 4 described later.

The bottom part 33 of the absorber 3 is connected with the bottom part of the heating tank 11 in the low concentration absorbent liquid flow path L3 equipped with the heat exchanger H and the absorbent liquid pump P1, and the absorbent liquid pump P1. The low concentration absorbent liquid in the absorber 3 is supplied into the heating tank 11 by the operation of.

In addition, the absorption coil 31 circulates the cooling water for the array cooled by the cooling tower CT during the cooling operation.

The evaporator 4 is formed on the outer circumference of the partition plate 40 with a plurality of communication holes (not shown) in a vertical cylindrical form formed on the outer circumference of the absorption coil 31 in the evaporation and absorption case 30. , By installing a vertical cylindrical evaporation coil 41 consisting of a copper tube through which the cooling and hot water for cooling and heating flows, and attaching the coolant liquid dispersion port 42 thereon.

The coolant liquid spreading port 42 is for dispersing the coolant liquid supplied from the condenser 5 described later and dropping the coolant liquid on the evaporation coil 41. As shown in FIG. And a refrigerant liquid storage container 420 which collects and collects the refrigerant liquid supplied from 5) and two refrigerant liquid distribution pipes 420a and 420b having a substantially annular shape.

As shown in Figs. 3, 4 and 5, the refrigerant liquid storage container 420 is an arc-shaped open container having an open upper side, and a partition plate for dividing the refrigerant liquid storage container 420 into two parts therein. 421 is formed, and the larger one divided by the partition plate 421 occupies most of the refrigerant liquid storage container 420 to store the refrigerant liquid supplied from the refrigerant passage L6. The reservoir 422 is provided, and the smaller side is the refrigerant liquid outlet 423.

In the partition plate 421 formed to divide the refrigerant liquid reservoir 422 and the refrigerant liquid outlet 423, the refrigerant liquid reservoir 422 moves from the refrigerant liquid reservoir 422 to the refrigerant liquid outlet 423 as shown in FIG. 6. A small opening orifice 421A is formed to limit the flow rate of the refrigerant liquid. The orifice 421A restricts the flow rate of the coolant liquid supplied to the coolant liquid outlet 423 when most of the coolant liquid supplied to the height of the orifice 421A is supplied and stores the coolant liquid. The formed refrigerant flow rate limiting means and the refrigerant amount adjusting means.

The orifice 421A becomes a flow path resistance when the flow rate of the refrigerant liquid supplied from the refrigerant flow rate L6 is large, restricts the flow rate of the refrigerant liquid, and does not become a flow path resistance when the flow rate of the refrigerant liquid supplied is small. The diameter dimension (for example, diameter 3.4mm) is set so that most of it can be moved to the refrigerant | coolant liquid outflow part 423. FIG.

Further, the U-shaped cutout groove 421B on the upper part of the partition plate 421 is a refrigerant liquid storage part 422 in the condenser 5 when only a predetermined amount of refrigerant is stored in the refrigerant liquid storage part 422. In order to prevent the refrigerant liquid supplied to the overflow, the refrigerant liquid to the outlet portion 423.

At the bottom of the coolant liquid outlet 423, as shown in FIGS. 5 and 6, two distribution inlet pipes 424a and 424b are connected to the coolant liquid distribution pipes 420a and 420b disposed below, respectively. It is installed.

The inlet port of one side distribution inlet pipe 424a which is in communication with the outside coolant liquid distribution pipe 420a is formed directly downward from the bottom of the coolant liquid storage container 420, but the inside of the coolant liquid distribution pipe ( One side distribution inlet pipe 424b communicating with 420b is formed to protrude inwardly from the bottom of the refrigerant liquid storage container 420 and to be inclined in the middle of the inside of the refrigerant liquid storage container 420. Have. When the amount of the coolant liquid supplied into the coolant liquid outlet 423 is small due to the step of the height in which the openings of the distribution inlet pipes 424a and 424b are formed, only the inner coolant liquid distribution pipe 420a is used as the evaporation coil. When the coolant liquid is scattered and the amount of the coolant liquid supplied into the coolant liquid outlet 423 is large, the coolant liquid is dispersed in both of the coolant liquid distribution pipes 420a and 420b.

The two refrigerant liquid distribution pipes 420a and 420b are arranged in double and inside each other, forming one coiled coil having a height difference at both ends, and the distribution inlet pipes 424a and 424b are each pipes 420a and 420b. It is connected from the side slightly lower than the middle part of

The refrigerant liquid distribution pipes 420a and 420b are distributed in respective annular portions, and the refrigerant liquid discharge holes 425 are formed upward, and the refrigerant liquid discharge holes 425 are discharged upward. Liquid induction grooves 426 having grooves for guiding the refrigerant liquid downward and falling off are fitted respectively.

In addition, each of the refrigerant liquid distribution pipes 420a and 420b has a high level difference at both ends, so that the refrigerant liquid pressure increases as the lower portion thereof, so that the amount of refrigerant liquid discharged from each refrigerant discharge hole 425 is equalized. For this purpose, the diameters of the upper portions are set larger as the diameters of the lower portions correspond to the upper and lower positions of the portions where the refrigerant discharge holes 425 are formed, respectively. Therefore, the discharge amount can be made uniform without being affected by the refrigerant liquid pressure at the formation portions of the refrigerant discharge holes 425.

By the above configuration, in the evaporator 4, when the coolant liquid (water) flows over the evaporation coil 41 in the coolant liquid dispersion port 42 during the cooling operation, the flow of the coolant liquid is evaporated by the surface tension. The vaporization heat is removed from the evaporation coil 41 in the evaporation / absorption case 30 at low pressure (e.g., 6.5 mmHg) while being wetted to form a membrane and falling downward by the action of gravity. Cools the cold / hot water for air conditioning flowing through the evaporation coil (41).

In addition, the bottom portion 43 of the evaporator 4 is connected to the bottom portion of the absorbent liquid partition vessel 13 in the medium concentration absorbent liquid separation tank 12 by the heating absorbent liquid flow path L4 having the electronic cold / hot water switching valve 6. It leads one after another

Next, the condenser 5 is demonstrated.

The condenser 5 is provided by installing a cooling coil 51 inside the condenser case 50 to circulate the interior cooling water cooled by the cooling tower CT.

As shown in FIG. 2, the condenser case 50 blocks the upper opening of the evaporation / absorption case 30 and forms a boundary plate 52 and a boundary plate 52 which form a bottom portion of the condenser case 950. It consists of a condenser cover plate 53 which coats and forms a condenser chamber.

A refrigerant liquid receiving part 50a is installed between the cooling coil 51 and the boundary plate 52 to receive the refrigerant liquid liquefied by the refrigerant vapor cooled by the cooling coil 51 in the condenser case 50. The coolant liquid receiving part 50a cools the coolant to be scattered on the high concentration absorbent liquid dispersion port 32 of the absorber 3 and the evaporator coil 41 of the evaporator 4 under the boundary plate 52. The boundary plate assembly is formed in advance such as the refrigerant cooler 54 installed for the purpose.

The condenser cover plate 53 has a preliminary attachment of an eliminator 55 formed of several members in which the cooling coil 51 is contained in the coil support port 51a and also contains a part of the medium absorbent liquid flow path L1. The condenser assembly is then formed.

In addition, between the condenser 5 and the refrigerant cooler 54 in the evaporator 4, the inside of the condenser case 50 and the inside of the refrigerant cooler 54 are directly passed in succession without interposing the refrigerant liquid receiving part 50a. The coolant liquid flow path L7 is provided, and the coolant liquid flow path L7 is provided with an electronic coolant valve 7 which closes the valve during normal operation and opens the valve at the end of operation or at the start of operation.

In addition, both ends of the cooling coil 51 are disposed adjacent to the outer circumferential portion of the condenser cover plate 53 as inlet and outlet portions to the condenser 5, respectively.

The condenser 5 having the above structure communicates with the refrigerant storage portion 10a of the refrigerant recovery tank 10 by a refrigerant passage L5 in which an orifice (not shown) for limiting the refrigerant flow rate is formed. The low temperature regenerator 2 is also connected through the steam outlet 21 and the gap 5A, and both of them are supplied with the refrigerant due to the pressure difference (about 70 mmHg in the case of the accumulator).

In the condenser 5, the refrigerant vapor supplied into the condenser case 50 is cooled by the cooling coil 51 to liquefy. The refrigerant liquid receiving portion 50a provided below the condenser 5 and the refrigerant liquid spreading port 42 disposed above the evaporation coil 41 of the evaporator 4 are successively connected in the refrigerant liquid supply path L6. Doing. The liquefied refrigerant liquid is supplied to the refrigerant liquid spreading port 42 via the refrigerant liquid supply path L6 and the refrigerant cooler 54.

According to the above configuration, the absorbent liquid has a high temperature regenerator (1) → medium concentration absorbent liquid passage (L1) → low temperature regenerator (2) → high concentration absorbent liquid passage (L2) → high concentration absorbent liquid dispersion port (32) → absorber (3) → absorbent pump (P1) → low concentration absorption liquid flow path (L3) → high temperature regenerator (1).

The refrigerant may be a high temperature regenerator (1; refrigerant vapor) → a refrigerant passage (L5; refrigerant vapor) or a low temperature regenerator (2; refrigerant steam) → a condenser (5; refrigerant liquid) → a refrigerant supply passage (L6; refrigerant liquid) → The refrigerant liquid spray port 42 (refrigerant liquid) → evaporator (4; refrigerant vapor) → absorber (3; absorption liquid) → absorption liquid pump (P1) → low concentration absorption liquid flow path (L3) → high temperature regenerator (1).

The absorption coil 31 of the absorber 3 and the cooling coil 51 of the condenser 5, which exchange heat with the absorbent liquid, are connected to each other to form a continuous coil. The continuous coil is connected to the cooling tower CT by the cooling water flow path 34. It is connected with and forms the cooling water circulation path.

In the cooling water circulation path, the cooling water flow path 34 between the inlet of the absorption coil 31 and the cooling tower CT is equipped with a cooling water pump P2 for sending the cooling water into the continuous coil, and the cooling water pump P2. Cooling water passing through the continuous coil by the operation of the absorption coil 31 absorbs the heat of absorption in the cooling coil 51, respectively, becomes a relatively high temperature is supplied to the cooling tower CT.

According to the above configuration, in the cooling operation, the cooling water in the cooling tower CT is operated by the operation of the cooling water pump P2, the cooling tower CT) → the cooling water pump P2 → the absorption coil 31 → the cooling coil 51 → It circulates in order of cooling tower CT.

In the cooling tower CT, self-cooling is performed to partially evaporate the falling cooling water in the air to cool the remaining cooling water, and the cooling water is radiated to the air to form an array cycle at low temperature. In addition, the evaporation of water is promoted by blowing from the blower (S).

The air conditioning heat exchanger 44 installed in the indoor unit RU is connected to the evaporator coil 41 of the evaporator 4 in the cold / hot water flow passage 47, and the cold / hot water flow passage 47 is provided with a cold / hot water pump P3.

By the above structure, it cycles in order.

The air conditioner heat exchanger 44 is provided in the indoor unit RU, and the blower 46 which passes the indoor air through the heat exchanger 44 and blows it back to the room is provided.

In addition, the heating absorbing liquid flow path L4 and the cooling / heating switching valve 6 are provided for the heating operation, and the heating / heating switching valve 6 is opened during the heating operation to operate the absorbing liquid pump P1.

Accordingly, the hot medium absorbent liquid in the absorbent liquid partition vessel 13 in the medium absorbent liquid separator 12 is introduced into the evaporator 4, and the cold and hot water in the evaporator coil 41 is heated to heat the evaporated coil 41. The cold and hot water therein is supplied to the air conditioning heat exchanger 44 from the hot and cold water flow passage 47 by the operation of the cold and hot water pump P3, and becomes a heat source of heating.

The medium concentration absorbent liquid in the evaporator 4 enters the absorber 3 side through the communication port of the partition plate 40, and is returned to the heating tank 11 by the absorbent liquid pump P1 via the low concentration absorbent liquid flow path L3. .

In the absorption type refrigerating device having the above structure, the absorbent liquid pump P1 and the cold / hot water pump P3 constitute a tandem pump driven simultaneously by the same motor, and the absorbent liquid pump P1 and the cold / hot water pump P3 are always the same. Rotate by the speed.

The control device 102 for controlling the absorption refrigeration apparatus is 1500 kPa / h to a detection temperature of a cold / hot water temperature sensor (not shown) for detecting the temperature of the cold / hot water supplied to the indoor unit RU in the cooling operation. Adjust the input of the gas burner (B) between 4800 mW / h. Further, in accordance with the detection temperature of the absorbent liquid temperature sensor (not shown) formed to detect the absorbent liquid temperature in the heating tank 11 as the control of the absorbent liquid pump P1, when the absorbent liquid temperature is low, the rotation speed is lowered and the absorbent liquid temperature is lowered. The higher the speed, the more the rotational speed is proportionally controlled.

By controlling as described above, when the cooling load is large, the absorbent liquid pump P1 and the cold / hot water pump P3 are driven at a high rotational speed, and a large amount of refrigerant is separated in each regenerator 1 and 2 in the absorption cycle. Then, a large amount of refrigerant liquid is supplied from the condenser 5 to the refrigerant liquid dispersion port 42. Therefore, a high concentration of absorbent liquid is supplied to the absorber 3.

Therefore, a large amount of the coolant liquid supplied to the coolant liquid storage container 420 of the coolant liquid dispersion port 42 is limited in flow rate by the orifice 421A of the partition plate 421, so that the coolant liquid storage part 422 Only the flow rate that is stored and can pass through the orifice 421A flows out to the coolant liquid outlet 423 and flows down to the evaporator coil 41 of the evaporator 4 by the coolant liquid distribution pipes 420a and 420b.

In addition, the flow rate through the orifice 421A increases due to the increase in head pressure due to the rise of the liquid level in the refrigerant liquid storage part 422.

As a result, a large amount of refrigerant liquid in the absorption liquid containing the refrigerant is stored in the refrigerant liquid storage portion 422 of the refrigerant liquid storage container 420 in the absorption cycle, so that the amount of refrigerant except the refrigerant liquid stored in the absorption cycle is reduced. The concentration of the entire absorbent liquid in the absorption cycle is increased.

As described above, when the cooling capacity of the absorption cycle is increased, a large amount of refrigerant liquid is stored and the concentration of the absorption liquid in the absorption cycle is increased, and when the cooling load is large by lowering the concentration of the absorption liquid in the entire absorption cycle in advance. Even during cooling operation, the concentration of the absorbing liquid can be maintained at an appropriate high concentration.

Conversely, when the cooling load is small, the absorbent liquid pump P1 and the cold / hot water pump P3 are driven at low rotational speeds, and the amount of refrigerant liquid separated in each regenerator 1 and 2 in the absorption cycle is reduced. .

Therefore, since the amount of the refrigerant liquid supplied to the refrigerant liquid storage container 420 of the refrigerant liquid dispersion port 42 is reduced, the flow rate is not limited by the orifice 421A of the partition plate 421, and is supplied from the condenser 5. It flows out into the refrigerant | coolant liquid outflow part 423 as it is, and flows into the evaporation coil 41 of the evaporator 4 by each refrigerant liquid distribution pipe 420a, 420b.

As a result, in the absorption cycle, the refrigerant liquid clogged in the refrigerant liquid storage portion 422 by the orifice 421A does not occur, so that the amount of refrigerant in the absorption cycle is larger than the large capacity and the concentration of the absorption liquid in the absorption cycle is lowered.

In this way, when the cooling capacity of the absorption cycle is reduced and the concentration of the absorbent liquid in the absorption cycle is lowered, the pressure difference in each part in the absorption cycle is reduced and the circulation amount of the absorbent liquid is lowered as the concentration of the absorbent liquid is lowered. For this reason, in the high temperature regenerator 1, the amount of heat (sensible heat amount) required to raise the absorbent liquid to the boiling point becomes small, and most of the heat amount can be used as the heat amount (latent heat amount) for evaporating the refrigerant. In addition, since the temperature of the container portion itself of the high temperature regenerator 1 decreases as the boiling point decreases due to the decrease in the concentration, the amount of heat (heatless) radiated from the regenerators 1 and 2 to the outside without being used for heating the absorbing liquid. This reduces.

For this reason, the efficiency of the absorption cycle does not decrease.

As described above, in the present invention, the refrigerant liquid supplied in the refrigerant liquid storage container 420 of the refrigerant liquid dispersion port 42 for supplying the refrigerant liquid from the condenser 5 to the evaporator 4 is received. In the coolant liquid storage part 422 at the lower part of the partition plate 421 which divides between the coolant liquid storage part 422 and the coolant liquid outlet part 423 which flows out coolant liquid to the coolant liquid injection pipes 420a and 420b. An orifice 421A is formed to limit the flow rate of the refrigerant liquid moving to the refrigerant liquid outlet 423, and when the refrigerant liquid supplied from the condenser 5 is large, the refrigerant liquid is stored in the refrigerant liquid storage part 422. Since the concentration of the absorbent liquid in the absorption cycle is adjusted according to the size of the cooling load, the concentration of the absorbent liquid is increased when the heating amount is large and the circulating amount of the absorbent liquid is high, and the concentration of the absorbent liquid when the heating amount is small and the circulation amount of the absorbent liquid is small. Can be lowered .

Therefore, regardless of the size of the cooling load, the amount of refrigerant corresponding to the cooling load can be separated from the absorbing liquid in the regenerator.

As a result, when the cooling load is large, a sufficient cooling capacity is ensured as in the conventional case, and even when the cooling load is small, the absorbent liquid having a low concentration can be boiled even with a small heating amount, so that the refrigerant can be separated. It does not occur and does not reduce the efficiency of the absorption cycle.

In the above embodiment, the orifice 421A is formed in the partition plate 421 between the refrigerant liquid storage part 422 and the refrigerant liquid outlet part 423 in the refrigerant storage container 420. If the flow rate of the coolant liquid flowing out of 422 can be limited, an orifice 421A may be formed at the bottom of the coolant liquid storage part 422. In that case, the coolant liquid outlet part 423 is located below the coolant liquid storage part 422.

Alternatively, instead of determining the refrigerant storage head by limiting the flow rate by the orifice, a structure may be formed in which the outflow flow rate is adjusted by a constant flow rate.

In addition, the height of the partition plate 421 between the refrigerant liquid storage part 422 and the refrigerant liquid outlet part 423 can be changed, and the height of the partition plate 421 is changed in proportion to the rotational speed of the absorbent liquid pump to thereby cool the refrigerant liquid storage part. The amount of refrigerant liquid stored in 422 may be adjusted.

Alternatively, the height of the partition plate 421 between the refrigerant liquid storage part 422 and the refrigerant liquid outlet part 423 is lower than the surrounding height of the refrigerant storage container 420, and the entire refrigerant storage container 420 is provided. Is formed so as to be inclined to drive from the coolant liquid storage part 422 toward the coolant liquid outlet part 423, and the inclination is changed in proportion to the rotational speed of the absorbent liquid pump to change the substantial capacity of the coolant liquid storage part 422. By adjusting, the amount of the coolant liquid stored in the coolant liquid storage part 422 may be adjusted.

7 shows another embodiment.

In the embodiment of FIG. 7, the sealed refrigerant liquid storage container 420 passes through the condenser 5 inward from the bottom of the condenser case 50, and the refrigerant liquid above the refrigerant liquid storage container 420. A suction pipe 430 is formed to continuously pass the storage container 420 to the inside of the evaporation / absorption case 30, and a pressure difference between the pressure in the condenser case 50 and the pressure in the evaporation / absorption case 30 is established. By storing the refrigerant liquid in the condenser case 50 into the refrigerant liquid storage container 420, the amount of storage is adjusted.

In this embodiment, for example, the pressure in the condenser case 50 when operated at a large capacity is 50 mmHg, and the pressure in the condenser case 50 when operated at a small capacity is 30 mm Hg and varies according to the capacity. In contrast, since the pressure in the evaporation / absorption case 30 is always 6.5 mmHg, a pressure difference depending on the capacity can be obtained. In the suction pipe 430, an orifice 431 for restricting communication between the inside of the evaporation / absorption case 30 and the inside of the condenser case 50 is formed to adjust the suction capacity.

In the above embodiment, the air-conditioning switching valve 6 was opened in the heating operation and closed in the cooling operation. However, in the dilution operation after the completion of the cooling operation, the valve is opened in the dilution operation. do.

In each of the above embodiments, the cooling tower CT of the cooling water flow path 34 is an open type in which cooling water is self-cooled by evaporating a part of the cooling water, but a closed circuit in which the cooling water circulating in the cooling water flow path 34 is not open to the atmosphere. The water cooling apparatus which provided this may be sufficient.

In the above embodiment, only the air conditioner heat exchanger 44 is formed in the indoor unit RU, but a heat exchanger for heating the air once cooled by the air conditioner heat exchanger 44 for dehumidification operation without lowering the room temperature. The group may be provided together with the air conditioning heat exchanger 44.

In the above embodiment, the air conditioner using the absorption type refrigerator is shown, but may be used in other refrigerators such as a refrigerator or a freezer.

In the said embodiment, although demonstrated by double-effect formula, single-effect formula may be sufficient. As a heating source, an oil burner or an electric heater may be used.

In Claim 1 of this invention, since the density | concentration adjusting means which adjusts the density | concentration of a regenerator is provided, when the density | concentration of the absorbent liquid as a whole in an absorption cycle is made low compared with the past, a small heating amount at the time of making the density | concentration of the absorbent liquid in a regenerator low In this case, the refrigerant can be easily evaporated, so that the refrigerant vapor can be reliably generated.

Therefore, if the concentration of the absorbent liquid is increased when the required cooling capacity is large, and the concentration of the absorbent liquid is lowered when the required cooling capacity is small, for example, a large heating is required when the required cooling capacity is large. The amount of cooling is given to the regenerator, and the smaller the required cooling capacity is, the smaller the heating amount to the regenerator can be. Even if the heating power is small, the amount of cooling can be ensured. Therefore, the efficiency decrease of the absorption cycle when the cooling capacity is small is eliminated. Can be.

In claim 2, as the concentration adjusting means, a refrigerant amount adjusting means for adjusting the amount of refrigerant circulating in the absorption cycle in the process of being supplied from the condenser to the evaporator is formed. The condenser is a portion where the refrigerant vapor separated from the absorbing liquid in the regenerator is cooled and becomes a refrigerant liquid. For example, the amount of refrigerant circulating in the absorption cycle when the refrigerant liquid generated here is not supplied to the evaporator as it is but is partially stored. Because of this adjustment, the concentration of the absorbent liquid in the absorber can be adjusted and the concentration of the absorbent liquid supplied from the absorber to the regenerator can be adjusted.

In Claims 3 and 4, as the refrigerant amount adjusting means, a refrigerant liquid flow rate limiting means for restricting the flow rate of the refrigerant liquid supplied from the condenser to the evaporator is formed.

Therefore, when the amount of refrigerant liquid generated in the condenser is small, the generated refrigerant liquid is not so limited by the refrigerant liquid flow rate limiting means, and the refrigerant liquid is supplied to the evaporator as it is. Therefore, the absorber absorbs the amount of refrigerant vapor supplied to the evaporator, and the concentration becomes the concentration set in the absorption cycle.

On the contrary, when the amount of the refrigerant liquid generated in the condenser is large, a large amount of refrigerant liquid is blocked by the refrigerant liquid flow rate limiting means, so that the amount of refrigerant supplied into the absorption cycle is reduced. As a result, the concentration of the absorbing liquid is relatively increased in the absorption cycle.

In this way, by limiting the refrigerant liquid generated in the condenser and supplying it to the evaporator, the refrigerant liquid in an amount corresponding to the amount of the refrigerant liquid generated is blocked in the absorption cycle, so that the concentration of the absorption liquid in the absorption cycle can be changed.

Claims (4)

A regenerator for heating the absorption liquid containing the refrigerant to separate the refrigerant vapor from the absorption liquid, a condenser for cooling and condensing the refrigerant vapor separated by the regenerator, an evaporator for evaporating the refrigerant liquid condensed in the condenser at low pressure, And an absorber for absorbing refrigerant vapor evaporated in the evaporator into an absorbent liquid supplied from the regenerator, and an absorption cycle formed by a pump for returning the absorbent liquid from the absorber to the regenerator, wherein the regenerator is used during the absorption cycle. And a concentration adjusting means for adjusting the concentration of the absorbent liquid. The absorption type refrigeration apparatus according to claim 1, wherein the concentration adjusting means is a refrigerant amount adjusting means for adjusting the amount of refrigerant circulating in the absorption cycle in the process of being supplied from the condenser to the evaporator. The absorption type refrigeration apparatus according to claim 2, wherein the refrigerant amount adjusting means is a refrigerant liquid flow rate limiting means for limiting a flow rate of the refrigerant liquid supplied from the condenser to the evaporator. 4. The absorption refrigerant according to claim 3, wherein the refrigerant liquid flow rate limiting means comprises an open refrigerant liquid storage container for storing the refrigerant liquid supplied from the condenser, and an orifice formed under the refrigerant liquid storage container. Device.