JP2000130886A - Absorber for absorption refrigerating machine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an absorber exhibiting a higher absorbing power as compared with a conventional absorber. SOLUTION: A plurality of cooling water pipes 2 extending in the horizontal direction are arranged, in an absorber chamber, in a plurality of stages at an interval in the vertical direction and each planar heat transfer means 1 comprises a plurality of heat transfer plates provided for one or a plurality of stages of the cooling water pipes 2. Each heat transfer plate extends in the horizontal direction and a specified gap is provided between the lower end face of an upper heat transfer plate and the upper end face of a lower heat transfer plate. One or a plurality of stages of cooling water pipes 2 penetrates each heat transfer plate and the upper end face of each heat transfer plate is substantially flush with the upper end of the outer circumferential surface of the cooling water pipes 2 on the uppermost stage penetrating each heat transfer plate for all heat transfer plates including or not including the uppermost one.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an absorber for absorbing refrigerant vapor generated from an evaporator into an absorbing liquid in an absorption refrigerator.

[0002]

2. Description of the Related Art In a double effect absorption refrigerator,
As shown in FIG. 8, an eliminator 30 is installed inside the closed drum 3, an evaporator chamber 31 and an absorber chamber 32 are formed on both sides thereof, and an evaporator (not shown) is installed in the evaporator chamber 31. An absorber 50 is installed in the absorber room 32. In addition, closed drum 3
A pipe 62 extending to the high-temperature regenerator through the low-temperature heat exchanger and the high-temperature heat exchanger is connected to the bottom of the pipe, and an absorption liquid pump 6 is mounted in the middle of the pipe 62.

[0003] The absorber 50 is a pipe extending from the low-temperature heat exchanger.
It comprises an absorbing liquid spraying mechanism 4 connected to the tip of 61 and a cooling water piping system having a plurality of cooling water pipings 2 extending in the horizontal direction.

In the absorber 50, an absorbing liquid (aqueous lithium bromide solution) is sprayed from the absorbing liquid spraying mechanism 4 toward the cooling water pipe 2 as shown by a broken line. The absorbing liquid absorbs the refrigerant vapor generated from the evaporator in the process of falling, and the absorbing liquid whose temperature has increased due to the condensation heat and the mixing heat (absorption heat) generated at this time flows through the cooling water pipe 2. Cooled by cooling water.

[0005]

In the conventional absorber 50, the absorbing liquid sprayed from the absorbing liquid spraying mechanism 4 first falls on the outer peripheral surface of the cooling water pipe 2 at the uppermost stage, and drops. After flowing downward along the outer peripheral surface as it is, it falls onto the outer peripheral surface of the lower cooling water pipe 2. In this way, the absorbing liquid
The droplets are transmitted to the lower cooling water pipe 2 in order as they are. Therefore, the absorbing liquid not only falls at a relatively high speed due to the action of gravity, but also does not spread sufficiently on the outer peripheral surface of the cooling water pipe 2, and the absorption area of the absorbing liquid to absorb the refrigerant vapor and the pipe surface The wet area is small.
As a result, sufficient absorption and heat exchange were not performed, and there was a problem that the absorption capacity of the absorber was low.

Accordingly, an object of the present invention is to provide an absorber capable of obtaining higher absorption capacity than before.

[0007]

An absorber of an absorption refrigerator according to the present invention is provided with an absorption liquid supply mechanism in a closed chamber to which the absorption liquid and the refrigerant vapor are to be supplied, and a lower part of the absorption liquid supply mechanism. At the position, a cooling water piping system formed by connecting a plurality of cooling water pipings extending in a lateral direction in series or in parallel to each other is installed, and a plurality of plate-shaped heat transfer means are vertically spaced apart from each other. In the absorber of an absorption refrigerator in which the plurality of cooling water pipes penetrate these heat transfer plates, the plurality of cooling water pipes are vertically spaced from each other. The plate-like heat transfer means is composed of a plurality of heat transfer plates provided in one or more stages of the cooling water pipe arrangement, and each heat transfer plate is arranged in a horizontal direction. It extends and the lower end surface of the upper heat transfer plate and the lower heat transfer plate Predetermined gap is provided between the upper end surface of the heat transfer plate, in the heat transfer plates, 1 of the cooling water pipe array of
Alternatively, in the case where a plurality of stages penetrate and all the heat transfer plates or other heat transfer plates except the top heat transfer plate, the upper end surface of each heat transfer plate and the top stage cooling which penetrates each heat transfer plate The upper end of the outer peripheral surface of the water pipe is arranged at the same or substantially the same height. Preferably, the gap is set to 2 mm to 5 mm.

By using this configuration, the absorbing liquid comes into contact with the refrigerant vapor over a wide area to absorb the refrigerant vapor, and the heat generated thereby is effectively cooled by sufficient heat exchange.

[0009] Of the two heat transfer plates vertically adjacent to each other,
Since a predetermined gap is provided between the lower end surface of the upper heat transfer plate and the upper end surface of the lower heat transfer plate, a part of the absorbent flowing down the outer peripheral surface of the cooling water pipe is When flowing down the surface of the heat transfer plate after separating from the cooling water pipe, it merges with part of the absorbing liquid flowing down and flowing down from the horizontally adjacent cooling water pipe, and as it is, the two cooling units disposed in the lower stage Even if a flow that passes between the water pipes occurs, when the flow of the absorbing liquid reaches the lower end surface of the heat transfer plate, a part of the absorbing liquid is transferred to the lower end surface of the heat transfer plate and the lower heat transfer plate. It diffuses right and left along the top surface. Then, when the absorbing liquid reaches the upper end of the outer peripheral surface of the uppermost cooling water pipe penetrating the lower heat transfer plate, thereafter, the absorbing liquid flows down along the outer peripheral surface of the cooling water pipe.

Therefore, the absorbing liquid flowing down along the surface of the heat transfer plate and the outer peripheral surface of the cooling water pipe is subjected to the above-described diffusion action each time it passes through the gap between the heat transfer plates, and the surface of the heat transfer plate Not only that, it also spreads sufficiently on the outer peripheral surface of the cooling water pipe to flow down. As a result, a plurality of heat transfer plates, that is, the above-mentioned effect by the plate-shaped heat transfer means is exhibited, and the direct cooling effect by the cooling water pipe is sufficiently exhibited, so that a higher absorption capacity is obtained. Become.

More specifically, it is preferable that the plurality of plate-shaped heat transfer means are arranged at a pitch of 3 mm to 15 mm.

By using this configuration, the pitch is too small, and the absorbing liquids merge and flow down, the flow path of the refrigerant vapor is blocked by the absorbing liquid, and the refrigerant vapor contacts the absorbing liquid with a sufficient area. No absorption capacity is significantly reduced. Further, as the pitch of the plate-like heat transfer means increases, the number of plate-like heat transfer means arranged over the entire length of the cooling water pipe decreases, and the absorption area of the absorbing liquid to absorb the refrigerant vapor and the plate Area of the absorbing liquid on the plate-shaped heat transfer means (the contact area of the absorbing liquid adhering to the plate-shaped heat transfer means surface with the plate-shaped heat transfer means; m2) is reduced, but by setting the pitch to 15 mm or less, Absorption and heat exchange can be obtained over conventional absorbers without plate heat transfer means.

Further, the heat transfer plates vertically adjacent to each other may be arranged in a staggered manner in the vertical direction. And, specifically, the plurality of heat transfer plates are arranged in a horizontal direction in a vertical posture at a predetermined interval, and each vertically adjacent heat transfer plate is arranged at the predetermined interval in the vertical direction. 1/2
It is good also as a structure arrange | positioned at every shift.

By using this structure, the absorbing liquid flowing down the upper heat transfer plate surface is prevented from flowing directly to the lower heat transfer plate surface, and the cooling water pipe penetrating the lower heat transfer plate is provided. Spreads sufficiently on the outer peripheral surface of and flows down. As a result, it is possible to alleviate the absorption liquid flowing down the surface of the heat transfer plate, improve the wettability of the outer peripheral surface of the cooling water pipe, and obtain a greater absorption amount and heat exchange amount.

[0015]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment in which the present invention is applied to an absorber of a double-effect absorption refrigerator will be specifically described below with reference to the drawings.

The absorber 5 of this embodiment is installed in an absorber chamber 32 formed in the closed drum 3 as in the conventional case shown in FIG.

As shown in FIGS. 1 and 2, in the absorber 5 of the present embodiment, a plurality of cooling water pipes 2 extending in the horizontal direction are arranged in the absorber chamber 32, for example, up to 22 mm in length and width.
Are arranged at a pitch of Further, a plurality of plate-like heat transfer means 1 are arranged in a horizontal direction in a vertical posture with an interval therebetween, and the plurality of cooling water pipes 2 penetrate these heat transfer means 1 vertically. As the heat transfer means 1, for example, a plate-like copper plate having a thickness Td of 0.5 mm is employed. In addition, heat transfer means 1
It is also possible to adopt other well-known materials, for example, those made of aluminum or the like. Heat transfer means 1
Is set to 3 to 15 mm.

In the absorber 5, cooling water is supplied into the cooling water pipe 2, and the surfaces of the plate-like heat transfer means 1 and the cooling water pipe 2 are sufficiently cooled by the cooling water.

Absorbing liquid spraying mechanism 4 as absorbing liquid supply means
The absorbing liquid is supplied to the surface of the plate-shaped heat transfer means 1 from above, and then the absorbing liquid spreads on the surface of the plate-shaped heat transfer means 1 and travels along the outer peripheral surfaces of the plate-shaped heat transfer means 1 and the cooling water pipe 2. Flow down. In this process, the absorbing liquid comes into contact with the refrigerant vapor passing between the plate-shaped heat transfer means 1 with a sufficient area to absorb the refrigerant vapor. Moreover, in the process of flowing down the surface of the plate-shaped heat transfer means 1, the absorption liquid wets the surface of the plate-shaped heat transfer means 1 over a wide area, and the absorption liquid is decelerated by the flow resistance. As a result, it flows over the surface of the plate-shaped heat transfer means 1 over a sufficient time. Therefore, sufficient heat exchange is performed between the surface of the plate-shaped heat transfer means 1 and the absorbing liquid is effectively cooled.

As described above, the absorbing liquid comes into contact with the refrigerant vapor over a large area to absorb the refrigerant vapor, and the heat generated thereby is effectively cooled by sufficient heat exchange, and as a result, a high absorption capacity is obtained. can get.

More specifically, each plate-like heat transfer means 1
The cooling water pipe 2 is composed of a plurality of heat transfer plates 11 provided at every two upper and lower stages of the array, and each heat transfer plate 11 extends in the horizontal direction to form two heat transfer plates 11 vertically adjacent to each other. Of which, the upper heat transfer plate
A gap G of 2 to 5 mm is provided vertically between the lower end surface of the heat transfer plate 11 and the upper end surface of the lower heat transfer plate 11. The upper and lower two stages of the array are penetrated. In the other heat transfer plates 11 except the top heat transfer plate 11, the upper end surface of each heat transfer plate 11 and the upper end of the outer peripheral surface of the upper cooling water pipe 2 penetrating each heat transfer plate 11 But are aligned at the same height. As described above, in the absorber equipped with the conventional spraying mechanism 4 as the absorbing liquid supply means, all the heat transfer plates 11 including the uppermost heat transfer plate 11 are used.
Cooling water pipe 2 at the top of the upper surface of each heat transfer plate 11
It is also possible to adopt a configuration in which the upper end surface of the second or lower heat transfer plate 11 excluding the uppermost heat transfer plate 11 is the same as the upper end of the outer peripheral surface of the heat transfer plate 11 as described above. It is also possible to adopt a configuration in which the uppermost cooling water pipe 2 penetrating through the hot plate 11 is flush with the upper end of the outer peripheral surface.

Each of the heat transfer plates 11 is provided with a plurality of steam flow holes 12 apart from the outer peripheral surface of each cooling water pipe 2. The steam flow hole 12 has an inner diameter of 2 mm to 3 mm, and is opened so as to be located between the arrangements of the cooling water pipes 2 which are horizontally adjacent to each other. This focuses on the fact that each heat transfer plate 11 has a non-wetting surface area, and a plurality of steam flow holes 12 are opened in the surface area of the heat transfer plate 11 where the absorbing liquid spreads and is hard to wet, so that the heat transfer plate 11 To generate a flow of refrigerant vapor passing therethrough. As a result, the ratio of the wetted area to the surface of the heat transfer plate 11 increases, the absorption capacity increases, and the heat transfer plate 11 does not hinder the flow of the refrigerant vapor, flows evenly in the absorption chamber 32, and absorbs. It will be sufficiently absorbed by the liquid. Since the gap G between the heat transfer plates 11 is provided as described above, the steam flow holes 12 having a small inner diameter are provided.
The above-described flow of the refrigerant vapor can be generated only by providing a plurality of the heat transfer plates, and there is no possibility that the wet area of the surface of the heat transfer plate 11 of the absorbing liquid is reduced by opening the vapor circulation holes.

Next, the effect of the heat transfer plate 11 having the gap G will be described.

In the process in which the absorbing liquid transferred from the absorbing liquid spraying mechanism 4 to the surface of the heat transfer plate 11 flows down the heat transfer plate 11 and the surface of the cooling water pipe 2, as shown by a dotted arrow in FIG. Even if a flow that passes between two adjacent cooling water pipes 2 and 2 or a flow that merges after flowing on the surfaces of these cooling water pipes 2 and 2 occurs, such a flow of the absorbing liquid is When the liquid reaches the lower end surface of the heat transfer plate 11, a part of the absorbing liquid diffuses right and left along the lower end surface of the heat transfer plate 11 and the upper end surface of the heat transfer plate 11 thereunder. When the absorbent reaches the upper end of the outer peripheral surface of the cooling water pipe 2, the absorbent then flows down the outer peripheral surface of the cooling water pipe 2.

As described above, in the process of flowing down the surface of the heat transfer plate 11, the absorbing liquid comes into contact with the refrigerant vapor passing between the heat transfer plates 11 with a sufficient area to absorb the refrigerant vapor and to transfer the refrigerant vapor. Hot plate 11
The flow is decelerated by the flow resistance of the surface and flows through the surface of the heat transfer plate 11 from the upper end to the lower end in a sufficient time, and a large heat exchange amount is obtained. The absorbing liquid flowing down the surface of the heat transfer plate 11 and the cooling water pipe 2 is
Each time it passes through the gap between 1 and 11, it undergoes the above-described diffusion action and spreads sufficiently not only on the heat transfer plate 11 but also on the surface of the cooling water pipe 2 to flow down. As a result, in addition to the above-described effects of the heat transfer plate 11, a sufficient cooling effect by the cooling water pipe 2 is exhibited, and a high absorption capacity is obtained.

Next, for each of the absorber A of the present invention having the above-described structure and the conventional absorber B having no heat transfer plate, a small experimental machine having the same volume was manufactured, and the absorption liquid flow rate was measured using this. As shown in FIG. 4, the relationship between the dashed line and the solid line was obtained for the absorber A of the present invention and the conventional absorber B as shown in FIG. The results in FIG. 4 are obtained by calculating the refrigerating capacity and the flow rate of the absorbing solution of the absorbers A and B having the above-mentioned specifications based on the refrigerating capacity and the flow rate of the absorbing solution obtained by the experimental machine.

As is apparent from FIG. 4, a plurality of heat transfer plates 11
According to the absorber A of the present invention provided with the above, it is possible to obtain a larger refrigeration capacity than the conventional absorber B regardless of the absorption liquid flow rate.

Further, as described above, in the present invention, the pitch Pd of the heat transfer means 1 is set to 3 to 15 mm. This is because as the pitch Pd of the heat transfer means 1 increases, the number of heat transfer means 1 arranged over the entire length of the cooling water pipe 2 decreases, and the absorption area of the absorbing liquid and the absorption of the heat transfer plate 11 Since the wet area of the liquid is small, the pitch Pd is 15
If it exceeds mm, the wetted area is almost the same as that of the conventional absorber without the heat transfer plate 11, and a heat exchange amount that is much larger than the conventional heat exchange amount cannot be obtained. When the pitch Pd of the heat transfer means 1 is smaller than 3 mm, the absorption liquids flowing on the two surfaces facing each other come into contact with each other due to the approach of the heat transfer means 1, and these absorption liquids merge. The reason for this is that the flow path of the refrigerant vapor is blocked by the absorbing liquid because the refrigerant vapor flows down, so that the refrigerant vapor does not contact the absorbing liquid with a sufficient area, and the absorption capacity is greatly reduced. Therefore, the pitch Pd of the heat transfer means 1 is desirably set in the range of 3 to 15 mm, whereby a higher absorption capacity can be obtained as compared with the conventional absorber, and it is necessary to exhibit the intended absorption capacity. Since the volume is small, the size of the absorber can be reduced. (Embodiment 2) FIG. 5 is a side view showing the arrangement of cooling water pipes and heat transfer plates in an absorber according to Embodiment 2. The same components as those in the first embodiment are denoted by the same reference numerals, the description thereof will be omitted, and the description will focus on the differences.

In the plate-shaped heat transfer means 1 of the first embodiment, each of the heat transfer plates 11 vertically adjacent to each other with a predetermined gap therebetween is
In the absorber 5, the heat transfer plates 21 vertically adjacent to each other are arranged in a staggered manner in the vertical direction as shown in FIG. . More specifically, the plurality of heat transfer plates 21 are arranged in a horizontal direction in a vertical position at a predetermined interval, and each heat transfer plate
21 are displaced from each other in the vertical direction by の of a predetermined interval.

By arranging the heat transfer plates 21 as described above, the absorbing liquid flowing down the upper heat transfer plate 21 surface directly flows to the lower heat transfer plate 21 surface as shown in FIG. After flowing on the surface of the cooling water pipe 2 penetrating the lower heat transfer plate 21 without flowing, it spreads sufficiently on the surface of the lower heat transfer plate 21 and the outer peripheral surface of the cooling water pipe 2 to flow down.

Accordingly, it is possible to improve the wettability of the outer peripheral surface of the cooling water pipe 2 by alleviating the absorption liquid flowing down along the surface of the heat transfer plate 21, thereby obtaining a further absorption amount and heat exchange amount. it can.

The configuration of each part of the present invention is not limited to the above embodiment, and various modifications can be made within the technical scope described in the claims.

For example, in the above embodiment, a plurality of cooling water pipes 2 can be arranged in a staggered manner.

Further, in place of the heat transfer plates 11 and 21 having a vertical flat plate shape,
It is also possible to adopt a corrugated heat transfer plate that undulates in the vertical direction. Furthermore, it is also possible to employ a heat transfer plate that has been subjected to surface processing in which irregularities appear along the vertical direction. When these heat transfer plates are employed, the flow resistance when the absorbing solution flows down increases, the flow speed decreases as compared with the heat transfer plates 11 and 21, and the absorbing area of the absorbing solution and the absorbing solution Since the wetted area increases, higher absorption capacity can be obtained.

In addition, as shown in FIG.
It is also possible to adopt a configuration in which a plurality of steam circulation holes 12 are opened in 1, 21. This focuses on the fact that the above-described heat transfer plates 11 and 21 have a surface area that is not wet, and a plurality of steam circulation holes 12 are opened in the heat transfer plates 11 and 21 to penetrate the heat transfer plates 11 and 21. It produces a flow of refrigerant vapor. As a result, the refrigerant vapor flows evenly in the absorber chamber 32 without being obstructed by the heat transfer plates 11 and 21, and is sufficiently absorbed by the absorbing liquid.

[0036]

According to the absorber of the absorption refrigerator according to the present invention, as compared with the conventional absorber, the absorbing liquid comes into contact with the refrigerant vapor over a wider area to absorb the refrigerant vapor and generate the same. The generated heat is effectively cooled by sufficient heat exchange, so that the absorption capacity is dramatically improved.

Further, the absorption liquid spreads not only on the surface of the heat transfer plate but also on the outer peripheral surface of the cooling water pipe due to the gap between the heat transfer plates and flows down. Sufficiently exhibited, higher absorption capacity can be obtained.

[Brief description of the drawings]

FIG. 1 is a partially broken perspective view showing a main part of an absorber according to an embodiment of the present invention.

FIG. 2 is a front view showing an arrangement of cooling water pipes in the absorber of FIG.

FIG. 3 is a partially cutaway front view illustrating a main part of the absorber of FIG. 1;

FIG. 4 is a graph showing a relationship between an absorption liquid flow rate and a refrigeration capacity.

FIG. 5 is a side view illustrating an arrangement state of cooling water pipes and heat transfer plates in an absorber 5 according to Embodiment 2 of the present invention.

6 is an explanatory diagram showing a flow of an absorbing liquid in a main part of the absorber 5 of FIG.

FIG. 7 is a diagram illustrating a configuration example in which a plurality of steam circulation holes are opened in a heat transfer plate, and dimensions and pitches of the steam circulation holes and cooling water pipe through holes at that time.

FIG. 8 is a schematic diagram showing an absorber installed in a closed drum in a double-effect absorption refrigerator.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Plate-shaped heat transfer means 2 Cooling water piping 3 Sealed drum 4 Absorbing liquid spraying mechanism (absorbing liquid supply means) 5, 50 Absorber 11, 21 Heat transfer plate 12 Steam flow hole

 ──────────────────────────────────────────────────続 き Continuation of the front page (72) Inventor Yoshio Ozawa 2-5-5 Keihanhondori, Moriguchi-shi, Osaka Sanyo Electric Co., Ltd. (72) Kenji Nasako 2-chome Keihanhondori, Moriguchi-shi, Osaka No.5-5 in Sanyo Electric Co., Ltd.

Claims (5)

[Claims] An absorption liquid supply mechanism is provided in a closed chamber to which the absorption liquid and the refrigerant vapor are to be supplied, and a plurality of laterally extending cooling water pipes are arranged in series below the absorption liquid supply mechanism. Alternatively, a cooling water piping system connected in parallel is installed, and a plurality of plate-like heat transfer means are arranged in a horizontal direction in a vertical posture at intervals from each other, and the plurality of cooling water pipings are An absorber of an absorption refrigerator penetrating a plate-shaped heat transfer means, wherein the plurality of cooling water pipes are arranged in a plurality of stages at intervals in a vertical direction, and each plate-shaped heat transfer means A plurality of heat transfer plates provided in one or more stages of the cooling water pipe arrangement, and each heat transfer plate extends in a horizontal direction, and out of two vertically adjacent heat transfer plates, A predetermined gap is provided between the lower end surface of the upper heat transfer plate and the upper end surface of the lower heat transfer plate. , Each heat transfer plate, wherein the one or more stages of arrangement of the cooling water piping penetrates, all of the heat transfer plate,
Alternatively, in the other heat transfer plates except the uppermost heat transfer plate, the upper end surface of each heat transfer plate and the upper end of the outer peripheral surface of the uppermost cooling water pipe penetrating each heat transfer plate are the same or substantially the same. Absorber for absorption refrigerator, characterized in that they are arranged at the same height. 2. The absorber according to claim 1, wherein the gap is set to 2 mm to 5 mm. 3. The absorber of an absorption refrigerator according to claim 1, wherein the plurality of plate-shaped heat transfer means are arranged at a pitch of 3 mm to 15 mm. 4. The heat transfer plate according to claim 1, wherein the heat transfer plates vertically adjacent to each other are arranged in a staggered manner in the vertical direction.
4. The absorber for an absorption refrigerator according to any one of claims 3 to 3. 5. The plurality of heat transfer plates are arranged in a horizontal direction in a vertical position with a predetermined space therebetween, and each vertically adjacent heat transfer plate is arranged at one of the predetermined distances in the vertical direction. 5. The absorber of an absorption refrigerator according to claim 4, wherein the absorber is arranged to be shifted by / 2.