CN106288497A - Absorption refrigeration unit internal heat assembly, absorption refrigeration unit and matrix - Google Patents

Abstract

The invention relates to the field of absorption refrigerating machines, and discloses an internal heat exchange component of an absorption refrigerating unit, which is any one of a regenerator, an absorber, a condenser, an evaporator or a solution heat exchanger. When the internal heat exchange component of the absorption refrigeration unit is any one of regenerator, absorber, condenser or evaporator, the internal heat exchange component of the absorption refrigeration unit includes a shell-and-tube heat exchanger, and its heat exchange tube is made of plastic production. When the internal heat exchange component of the absorption refrigeration unit is a solution heat exchanger, the internal heat exchange component of the absorption refrigeration unit includes a plate heat exchanger, and its heat exchange wall plate is made of plastic. The weight of the whole machine of the absorption refrigerating machine manufactured by adopting the internal heat exchange component of the absorption refrigerating unit provided by the invention can be greatly reduced. At the same time, the corrosion resistance of the plastic is stronger, and it can avoid being corroded by the solution to produce non-condensable gas, which increases the working efficiency of the absorption refrigerator. Plastic is easy to seal, which can effectively reduce the difficulty of sealing.

Description

Internal heat exchange components of absorption refrigeration unit, absorption refrigeration unit and matrix

technical field

The invention relates to the field of absorption refrigerating machines, in particular to an internal component of the absorption refrigerating machine, in particular to a condenser, an evaporator, an absorber and a regenerator of the absorption refrigerating machine.

Background technique

Absorption refrigerator, which uses a binary solution as a working medium, in which the low-boiling point component is used as a refrigerant, that is, it is used for refrigeration by its evaporation; the high-boiling point component is used as an absorbent, that is, it is used to absorb the refrigerant vapor. Complete the work cycle. For example, the lithium bromide absorption refrigerator uses pure water as the refrigerant, that is, relies on the evaporation and heat absorption of pure water in a high vacuum environment to realize the refrigeration function. After absorbing heat and evaporating, the refrigerant vapor is absorbed by the lithium bromide solution, transported, heated and regenerated, condensed, and after returning to liquid state, it absorbs heat and evaporates again, and the refrigeration cycle is continuously carried out.

In the absorption refrigerator, the condenser, evaporator, absorber and regenerator are the main components to realize the refrigeration cycle, and the heat exchange tubes are made of brass or other metal materials with relatively high heat transfer coefficient, which leads to absorption The overall weight of the absorption refrigerator is large, and it is difficult to reduce the weight of the absorption refrigerator. At the same time, the metal is easily corroded by the solution, and produces non-condensable gases such as hydrogen, which reduces the working efficiency of the absorption refrigerator; the metal heat exchange tube has high requirements on the sealing process, and the sealing cost is high.

Contents of the invention

The purpose of the present invention is to overcome the deficiencies of the prior art, and provide an internal heat exchange component of an absorption refrigeration unit, in which the heat exchange tube and the heat exchange wall plate are made of plastic, so that the heat exchange performance can be satisfied under the premise of Absorption refrigerating machine achieves weight reduction. At the same time, the heat exchange tube made of plastic is easy to seal; the plastic has strong corrosion resistance, can avoid non-condensable gas, and increases the working efficiency of the absorption refrigerator.

Another object of the present invention is to provide an absorption refrigeration unit equipped with the above-mentioned internal heat exchange components of the absorption refrigeration unit.

The third object of the present invention is to provide an absorption refrigeration matrix equipped with the above absorption refrigeration unit.

Embodiments of the invention are achieved through the following technical solutions:

The internal heat exchange component of the absorption refrigeration unit is any one of regenerator, absorber, condenser, evaporator or solution heat exchanger. When the internal heat exchange component of the absorption refrigeration unit is any one of regenerator, absorber, condenser or evaporator, the internal heat exchange component of the absorption refrigeration unit includes a shell-and-tube heat exchanger. A shell and tube heat exchanger has a shell and tube heat exchanger shell and heat exchange tubes. The heat exchange tubes are arranged in the casing of the shell and tube heat exchanger. The heat exchange tubes are made of plastic. When the internal heat exchange component of the absorption refrigeration unit is a solution heat exchanger, the internal heat exchange component of the absorption refrigeration unit includes a plate heat exchanger; the plate heat exchanger has a plate heat exchanger shell and a heat exchange wall plate. The heat exchange wall plate is arranged in the shell of the plate heat exchanger; the heat exchange wall plate is made of plastic.

The inventors have found through research that in order to improve heat transfer performance, the heat exchange tubes in the condenser, evaporator, absorber and regenerator are made of metal materials with relatively high heat transfer coefficients. The heat exchange wall plates of the solution heat exchanger are also made of metal materials. However, the metal material has a high density, resulting in a large overall weight of the absorption refrigerator. In addition, metal heat exchange tubes and heat dissipation wall plates are corroded by the solution to produce non-condensable gas, which affects the working efficiency of the absorption refrigerator, and the sealing process requires high requirements and high sealing costs. Compared to metal materials, plastics have a lower density. The weight of plastic is much lower than that of metal materials (such as brass) under the same volume. For this reason, the inventor made the heat exchange tubes and the heat exchange wall plates from plastics. The weight of the absorption refrigeration machine manufactured by adopting the internal heat exchange components of the absorption refrigeration unit provided by the embodiment of the present invention can be greatly reduced. Heat exchange tubes and heat exchange wall plates made of plastic are easy to seal. The corrosion resistance of the plastic is stronger, and it can avoid being corroded by the solution to produce non-condensable gas, which increases the working efficiency of the absorption refrigerator.

In one embodiment of the present invention, the tube wall thickness of the heat exchange tube is 0.1-0.5 mm.

In one embodiment of the present invention, the wall thickness of the heat exchange tube is 0.15 mm.

In one embodiment of the present invention, several rows of heat exchange tubes are arranged in upper and lower layers; a plurality of support bars are arranged at intervals between two adjacent rows of heat exchange tubes; the support bars are used to support two adjacent rows of heat exchange tubes.

In one embodiment of the invention, the support bars are made of plastic.

In one embodiment of the present invention, the support bar and the heat exchange tube are made of the same plastic.

In one embodiment of the present invention, the outer diameter of the heat exchange tube is 3mm˜5mm. The center-to-center distance between adjacent heat exchange tubes in the same row is 4 mm to 6 mm. The center distance between the upper and lower adjacent heat exchange tubes is 5 mm to 8 mm.

In one embodiment of the present invention, the outer diameter of the heat exchange tube is 3mm. The center-to-center distance between adjacent heat exchange tubes in the same row is 4mm. The center-to-center distance between the upper and lower adjacent heat exchange tubes is 7mm.

In one embodiment of the present invention, when the internal heat exchange component of the absorption refrigeration unit is any one of regenerator, absorber, condenser or evaporator, the shell of the shell-and-tube heat exchanger is made of plastic .

In one embodiment of the present invention, the shell and the heat exchange tubes of the shell-and-tube heat exchanger are made of the same plastic.

In one embodiment of the present invention, the thickness of the heat exchange wall plate is 0.1mm-0.5mm.

In one embodiment of the present invention, the thickness of the heat exchange wall plate is 0.15 mm.

In one embodiment of the present invention, textured ribs are distributed on the heat exchanging wall plate for supporting the heat exchanging wall plate and making the fluid flowing through the ribs turbulent to improve the heat transfer coefficient.

In one embodiment of the invention, the ribs are made of plastic.

In one embodiment of the present invention, the ribs and the heat exchange wall are made of the same plastic.

In one embodiment of the present invention, the heat exchange wall plates are arranged in multiple layers. The distance between the heat exchange wall panels of two adjacent layers is 0.5 mm to 3 mm.

In one embodiment of the present invention, the distance between the heat exchange wall plates of two adjacent layers is 1mm.

In one embodiment of the present invention, when the internal heat exchange component of the absorption refrigeration unit is a solution heat exchanger, the shell of the plate heat exchanger is made of plastic.

In one embodiment of the present invention, the shell of the plate heat exchanger and the heat exchange wall are made of the same plastic.

In one embodiment of the present invention, the heat exchange component inside the absorption refrigeration unit is an evaporator. The inside of the heat exchange tube is used for the flow of cold water, and the space between the heat exchange tube and the shell of the shell-and-tube heat exchanger is used for the flow of refrigerant water.

In one embodiment of the present invention, the side of each row of heat exchange tubes facing the absorber is provided with a sloping liquid baffle, and the sloping liquid baffle is used to trap refrigerant water and only allow refrigerant steam to pass through.

In one embodiment of the present invention, the internal heat exchange component of the absorption refrigeration unit is a condenser; the inside of the heat exchange tube is used for cooling water to flow, and the space between the heat exchange tube and the shell of the shell-and-tube heat exchanger is used for supplying Refrigerant vapor flows.

In one embodiment of the present invention, the side of each row of heat exchange tubes facing the regenerator is provided with a sloping liquid baffle, and the sloping liquid baffle is used to trap liquid droplets in the refrigerant vapor and only allow the refrigerant vapor to pass through .

In one embodiment of the present invention, the internal heat exchange component of the absorption refrigeration unit is an absorber or a regenerator, and the heat exchanger shell and heat exchange tubes together constitute a shell-and-tube heat exchanger. The space between the heat exchange tube and the casing of the shell-and-tube heat exchanger is used for the flow of the lithium bromide solution. When the internal heat exchange component of the absorption refrigeration unit is an absorber, the inside of the heat exchange tube is used for cooling water flow; when the internal heat exchange component of the absorption refrigeration unit is a regenerator, the inside of the heat exchange tube is used for the flow of hot water.

In one embodiment of the present invention, the internal heat exchange assembly of the absorption refrigeration unit also includes a solution distributor; the solution distributor is arranged on the upper part of the shell-and-tube heat exchanger; the solution distributor has a cavity inside, and the lower part of the solution distributor is Solution spray surface for spraying solution to the heat exchange tubes below.

In one embodiment of the invention, the solution dispenser is made of plastic.

In one embodiment of the invention, the solution distributor and the shell and tube heat exchanger housing are made of the same plastic.

In one embodiment of the present invention, the size of the solution spraying surface is the same as that of the upper end surface of the shell-and-tube heat exchanger. A number of discharge holes are arranged on the solution spraying surface of the solution distributor for uniformly dispersing the solution to the surface of the heat exchange tube below.

In one embodiment of the present invention, when the internal heat exchange component of the absorption refrigeration unit is an absorber, each row of heat exchange tubes is provided with a sloped liquid baffle on the side facing the evaporator, and the sloped liquid baffle is used for Refrigerant water is intercepted and only refrigerant steam is allowed to pass through. When the internal heat exchange component of the absorption refrigeration unit is a regenerator, each row of heat exchange tubes is provided with a slope-type liquid separator on the side facing the condenser. The slope-type liquid separator is used to trap liquid droplets in the refrigerant vapor. Refrigerant vapor passes through.

The absorption refrigeration unit includes any one of the above-mentioned internal heat exchange components of the absorption refrigeration unit.

The absorption refrigeration matrix includes several above-mentioned absorption refrigeration units.

The technical solution of the present invention has at least the following advantages and beneficial effects:

In the internal heat exchange assembly of the absorption refrigeration unit provided by the embodiment of the present invention, the heat exchange tube and the heat exchange wall plate are made of plastic. The weight of the absorption refrigeration machine manufactured by adopting the internal heat exchange components of the absorption refrigeration unit provided by the embodiment of the present invention can be greatly reduced. At the same time, the heat exchange tube made of plastic is easy to seal. The corrosion resistance of the plastic is stronger, and it can avoid being corroded by the solution to produce non-condensable gas, which increases the working efficiency of the absorption refrigerator.

The absorption refrigeration unit provided by the embodiment of the present invention has the beneficial effects of low weight, easy sealing, stronger corrosion resistance and high working efficiency because it has the above-mentioned internal heat exchange components of the absorption refrigeration unit.

The absorption refrigeration matrix provided by the embodiment of the present invention has the above-mentioned absorption refrigeration unit, so it also has the beneficial effects of low weight, easy sealing, stronger corrosion resistance, and high working efficiency.

Description of drawings

In order to illustrate the technical solutions of the embodiments of the present invention more clearly, the drawings that need to be used in the embodiments are briefly introduced below. It should be understood that the following drawings only illustrate some embodiments of the present invention, and should not be considered as limiting the scope of the present invention. Those skilled in the art can obtain other drawings based on these drawings without creative effort.

Fig. 1 is the front view of the structure of the condenser and one side regenerator in the embodiment of the present invention;

Fig. 2 is a structural cross-sectional view of a condenser and a side regenerator in an embodiment of the present invention;

Figure 3 is an exploded view of the structure of the condenser and the regenerator on one side in the embodiment of the present invention;

Fig. 4 is an assembly state diagram of the evaporator and the absorber on one side in the embodiment of the present invention;

Fig. 5 is a cross-sectional view of the structure of the evaporator and one side absorber in the embodiment of the present invention;

Fig. 6 is an exploded view of the structure of the evaporator and the absorber on one side in the embodiment of the present invention;

7 is a schematic diagram of a three-dimensional structure of a solution heat exchanger in an embodiment of the present invention;

Fig. 8 is a schematic structural view of the exposed heat exchange wall plate after some components are removed in the embodiment of the present invention.

In the figure: 100-condenser; 101-shell-and-tube heat exchanger shell; 102-heat exchange tube; 103-support bar; 104-throttle hole; 200-regenerator; 201-shell-and-tube heat exchanger shell body; 202-heat exchange tube; 203-solution distributor; 204-solution spray surface; 205-discharge hole; 206-support bar; 207-supply hole; Liquid plate; 300-evaporator; 301-shell-and-tube heat exchanger shell; 302-heat exchange tube; 303-support bar; 400-absorber; 401-shell-and-tube heat exchanger shell; 402-heat exchange Tube; 403-solution distributor; 404-solution spraying surface; 405-discharge hole; 406-support bar; 410-shell-and-tube heat exchanger; - dilute solution inlet; 602 - concentrated solution outlet; 604 - channel of concentrated solution to absorber shell side; 606 - concentrated solution inlet; 608 - outlet of dilute solution; 609 - channel of dilute solution to regenerator; 612 - channel of dilute solution ; 614-concentrated solution channel; 620-heat exchange wall plate; 622-raised strip; 624-plate heat exchanger shell; 631-solution pump.

detailed description

In order to make the purpose, technical solutions and advantages of the embodiments of the present invention clearer, the technical solutions in the embodiments of the present invention will be clearly and completely described below in conjunction with the accompanying drawings. Apparently, the described embodiments are some, not all, embodiments of the present invention.

Therefore, the following detailed description of the embodiments of the present invention is not intended to limit the scope of the claimed invention, but merely represents some embodiments of the present invention. Based on the embodiments of the present invention, all other embodiments obtained by persons of ordinary skill in the art without creative efforts fall within the protection scope of the present invention.

It should be noted that, in the case of no conflict, the embodiments of the present invention and the features and technical solutions in the embodiments can be combined with each other.

It should be noted that like numerals and letters denote similar items in the following figures, therefore, once an item is defined in one figure, it does not require further definition and explanation in subsequent figures.

In the description of the present invention, it should be noted that the orientation or positional relationship indicated by the terms "upper", "lower", etc. is based on the orientation or positional relationship shown in the drawings, or the conventionally placed position when the product of the invention is used. Orientation or positional relationship, or the orientation or positional relationship commonly understood by those skilled in the art, such terms are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the referred device or element must have a specific orientation, Constructed and operative in a particular orientation and therefore are not to be construed as limitations of the invention.

Example:

In an absorption refrigerator, the condenser, evaporator, absorber, regenerator and solution heat exchanger are the main components to realize the refrigeration cycle, and the heat exchange tubes and heat exchange wall plates use metal materials with relatively high heat transfer coefficients. (such as brass), which leads to a large overall weight of the absorption refrigerator, and it is difficult to reduce the weight of the absorption refrigerator. At the same time, the metal is easily corroded by the solution and produces non-condensable gases such as hydrogen, which reduces the working efficiency of the absorption refrigerator.

Therefore, this embodiment provides an internal heat exchange component of an absorption refrigeration unit, and the internal component may be any one of a condenser, an evaporator, an absorber, a regenerator or a solution heat exchanger. The heat exchange tubes of the condenser, evaporator, absorber or regenerator are thin-walled heat exchange tubes made of plastic, and the heat exchange wall plates of the solution heat exchanger are thin-walled plates made of plastic, so as to meet the Under the premise of improving the heat transfer performance, the weight of the absorption refrigerator is reduced. At the same time, the plastic has strong anti-corrosion performance, can avoid non-condensable gas, and increases the working efficiency of the absorption refrigerator.

In this embodiment, the so-called plastic refers to engineering plastics (engineering-plastics), such as polycarbonate (Polycarbonate, PC), polyamide (nylon, Polyamide, PA), polyoxymethylene (Polyacetal, PolyoxyMethylene, POM), polyphenylene Ether (Polyphenylene Oxide, PPO), polyester (PET, PBT), polyphenylene sulfide (Polyphenylene Sulfide, PPS), polyaryl ester, etc.

In this embodiment, the condenser, evaporator, absorber, regenerator and solution heat exchanger inside the lithium bromide absorption refrigerator are taken as examples for illustration.

condenser 100 and regenerator 200

Referring to FIG. 1 , FIG. 1 is a structural front view of a condenser 100 and a side regenerator 200 in an embodiment of the present invention. In FIG. 1 , the right side is the condenser 100 , the left side is the regenerator 200 , and between the condenser 100 and the regenerator 200 is a sloped liquid separator 501 . The slope type liquid separator 501 can be regarded as a part of the condenser 100 , and can also be regarded as a part of the regenerator 200 . The function of the regenerator 200 on the left is to heat the dilute lithium bromide solution, so that the refrigerant water absorbed in the dilute solution is continuously vaporized into refrigerant steam, and the refrigerant steam enters the condenser 100 on the right and then condenses when it is cooled down to become a high-pressure and low-temperature refrigerant. Liquid refrigerant water. When the refrigerant water in the condenser 100 enters the evaporator of the refrigerator through the orifice, it absorbs a large amount of heat from the cold water flowing in the tube side of the evaporator and vaporizes, thereby achieving the purpose of cooling the cold water. The function of the condenser 100 of the present invention is to cool and condense the refrigerant steam generated by the regenerator 200 to become refrigerant water. The slope-type liquid separator 501 is used to intercept liquid droplets entrained in the refrigerant vapor produced by heating and evaporation of the regenerator 200 on the left, and only allows the refrigerant vapor to pass through the slope-type liquid separator 501 and enter the condenser 100 .

Next, the condenser 100 will be described.

Referring to FIG. 2 , FIG. 2 is a structural cross-sectional view of the condenser 100 and the side regenerator 200 in the embodiment of the present invention.

The condenser 100 is a shell-and-tube heat exchanger, including a shell-and-tube heat exchanger shell 101 and heat exchange tubes 102 . In this embodiment, several rows of heat exchange tubes 102 are arranged in upper and lower layers (only part of the heat exchange tubes 102 are shown in the figure. It can be understood that in other specific implementation manners, the heat exchange tubes 102 can be arranged in other ways. ) The heat exchange tube 102 is fixed in the shell 101 of the shell and tube heat exchanger. During operation, cooling water circulates in the heat exchange tube 102 , and refrigerant steam from the regenerator 200 flows between the heat exchange tube 102 and the shell 101 of the shell-and-tube heat exchanger. The cooling water in the heat exchange tube 102 is used to cool down and condense the refrigerant steam to obtain refrigerant water.

In the condenser 100, the heat exchange tube 102 is made of plastic, and the thickness of the tube wall of the heat exchange tube 102 is 0.1mm˜0.5mm. In this embodiment, the tube wall thickness of the heat exchange tube 102 is 0.15 mm. Compared with metal heat exchange tubes, such an extremely thin thickness increases the heat exchange area by more than ten times under the same volume, making up for the insufficient heat transfer performance of plastics, so that the heat transfer performance of the heat exchange tube 102 can reach the absorption type. Chiller requirements. Since the heat exchange tubes 102 are made of plastic, compared with metal heat dissipation tubes, the weight of the condenser 100 can be greatly reduced, thereby achieving light weight. Due to the excellent anti-corrosion performance of the plastic, it is also possible to avoid the generation of non-condensable gas due to the corrosion of the heat exchange tube 102, which increases the working efficiency of the absorption refrigerating machine. At the same time, the heat exchange tube 102 made of plastic is easier to seal than the metal heat exchange tube.

The inventors have found through research that the traditional condenser using metal heat exchange tubes is difficult to seal the metal. In order to ensure the sealing performance of the condenser, the shell can only be made of thick steel plates or castings, thereby further increasing The weight of the condenser is increased, and the corrosion resistance is poor.

For this reason, in this embodiment, the shell-and-tube heat exchanger casing 101 of the condenser 100 is also made of plastic, so that the sealing between the shell-and-tube heat exchanger casing 101 and the heat exchange tubes 102 can be easily In this way, the thickness of the shell 101 of the shell-and-tube heat exchanger can be reduced. In this way, the weight of the condenser 100 is further reduced, and the corrosion resistance of the condenser 100 is also enhanced. As an example, the shell 101 and the heat exchange tubes 102 of the shell-and-tube heat exchanger can be made of the same type of plastic, and integrally formed by injection molding, so as to provide excellent sealing performance.

In addition to reducing the weight of the condenser 100 , the inventor also hopes to reduce the size of the condenser 100 . The miniaturized condenser 100 can make the overall volume of the absorption refrigerating machine smaller, so that it can be applied to households or other commercial occasions that do not require high cooling power. However, the inventors found in the miniaturization process of the condenser 100 that the heat exchange efficiency of the condenser 100 is not high, and it is difficult to meet the use requirements after miniaturization. After research, the inventor found that the reason why the heat exchange efficiency of the condenser 100 is not high is that: when the refrigerant vapor enters the condenser 100 and undergoes heat exchange with the heat exchange tube 102 to liquefy, water droplets are formed on the surface of the heat exchange tube 102, and the Under the action of gravity, it collects and drips freely. During the dripping process, the condensed water continuously drips to each row of heat exchange tubes 102 below, forming a falling water film on the surface of the heat exchange tubes 102, especially at the lower arc of the heat exchange tubes 102. The thickness of the water film is often very thick, which increases the heat transfer resistance between the refrigerant steam and the heat exchange tube 102, which is not conducive to the contact between the refrigerant steam and the heat exchange tube 102, thus resulting in low heat exchange efficiency.

Therefore, the inventors optimized the outer diameter of the heat exchange tubes 102 and the center-to-center distance between adjacent heat exchange tubes 102 . Set the outer diameter of the heat exchange tubes 102 to 3 mm to 5 mm, set the center distance of adjacent heat exchange tubes 102 in the same row to 4 mm to 6 mm, and set the center distance of the upper and lower adjacent heat exchange tubes 102 to 5 mm ~8mm. In this embodiment, the outer diameter of the heat exchange tubes 102 is 3 mm; the center-to-center distance of adjacent heat exchange tubes 102 in the same row is 4 mm; the center-to-center distance of the upper and lower adjacent heat exchange tubes 102 is 7 mm. By adopting the heat exchange tubes 102 with small diameter and large density, a large heat exchange area is obtained per unit volume, thereby achieving a smaller volume under the premise of satisfying high heat exchange efficiency. The gap between adjacent heat exchange tubes 102 in the same row is only 1mm, such a small gap can play a beneficial role in the surface tension of the refrigerant water, so that the refrigerant water condensed on the surface of the heat exchange tubes 102 gathers and drips in the gap. The condensed refrigerant water will not drop to the surface of the lower heat exchange tube 102 to form a water film, so that the thickness of the water film hanging on the lower arc surface of the heat exchange tube 102 can be reduced, thereby improving the overall working efficiency of the condenser 100 . In this way, the condenser 100 can be miniaturized.

Referring to FIG. 3 , FIG. 3 is an exploded view of the structure of the condenser 100 and the side regenerator 200 in the embodiment of the present invention. Between two adjacent rows of heat exchange tubes 102 , a plurality of support bars 103 are arranged at equal intervals, and the support bars 103 are arranged to intersect with the heat exchange tubes 102 and are perpendicular to the heat exchange tubes 102 . The support bar 103 is used to support the two adjacent rows of heat exchange tubes 102 up and down, and bear the structural stress brought by the high vacuum inside the shell and tube heat exchanger shell 101 . In this embodiment, the support bar 103 is made of plastic to ensure light weight. As an example, the support bars 103 and the heat exchange tubes 102 are made of the same type of plastic to facilitate manufacture.

It should be noted that, in other specific embodiments, the wall thickness of the heat exchange tube 102 can be adjusted between 0.1 mm and 0.5 mm; the outer diameter of the heat exchange tube 102 can be adjusted between 3 mm and 5 mm; The center distance of the adjacent heat exchange tubes 102 in the same row can be adjusted between 4 mm and 6 mm; the center distance between the upper and lower adjacent heat exchange tubes 102 can be adjusted between 5 mm and 8 mm.

Next, the regenerator 200 will be described.

Referring again to FIG. 2 , the regenerator 200 includes a shell-and-tube heat exchanger shell 201 , heat exchange tubes 202 and a solution distributor 203 . In this embodiment, several rows of heat exchange tubes 202 are arranged in upper and lower layers (only part of the heat exchange tubes 202 are shown in the figure. It can be understood that in other specific implementation manners, the heat exchange tubes 202 can be arranged in other ways. ), the heat exchange tube 202 is fixed in the casing 201 of the shell-and-tube heat exchanger, thereby forming the shell-and-tube heat exchanger 210 . During operation, hot water circulates in the heat exchange tube 202, and the space between the heat exchange tube 202 and the shell 201 of the shell-and-tube heat exchanger is used for the flow of dilute lithium bromide solution. The hot water in the heat exchange tube 202 is used to heat the dilute lithium bromide solution, so that the refrigerant water absorbed in the dilute solution is continuously vaporized to become refrigerant steam. The solution distributor 203 is a cuboid with a cavity inside, and the cavity is used for flowing the dilute lithium bromide solution. The lower part of the solution distributor 203 is a solution spraying surface 204 . The solution distributor 203 is arranged on the upper part of the shell-and-tube heat exchanger 210 , and the size of the solution spraying surface 204 is the same as that of the upper end surface of the shell-and-tube heat exchanger 210 . Referring to FIG. 3 again, a plurality of discharge holes 205 are uniformly arranged on the solution spraying surface 204 . As an embodiment, the discharge holes 205 are long holes extending in the width direction of the solution spraying surface 204 and three holes are equally spaced to form a row. In the length direction of the solution spraying surface 204, multiple drainage orifices 205 are arranged at equal intervals. The drain hole 205 is used to uniformly spray the dilute lithium bromide solution in the cavity to the heat exchange tube 202 below.

Referring to FIG. 2 again, the shell-and-tube heat exchanger shell 201 of the regenerator 200 and the shell-and-tube heat exchanger shell 101 of the condenser 100 are of an integrated structure, and the heat exchange tube 202 of the regenerator 200 and the condenser 100 The heat exchange tubes 102 are separated by sloped liquid separators 501 .

In the regenerator 200, the heat exchange tube 202 is made of plastic, and the thickness of the tube wall of the heat exchange tube 202 is 0.1mm˜0.5mm. In this embodiment, the tube wall thickness of the heat exchange tube 202 is 0.15mm. Compared with the metal heat exchange tube, such an extremely thin thickness increases the heat exchange area by more than ten times under the same volume, which makes up for the insufficient heat transfer performance of plastic, so that the heat transfer performance of the heat exchange tube 202 can reach the absorption type. Chiller requirements. Since the heat exchange tube 202 is made of plastic, the weight of the regenerator 200 can be greatly reduced compared with the use of metal heat dissipation tubes, thereby achieving light weight. Due to the excellent anti-corrosion performance of the plastic, it is also possible to avoid the generation of non-condensable gas due to the corrosion of the regenerator 200, thereby increasing the working efficiency of the absorption refrigerating machine. The heat exchange tube 202 made of plastic is easier to seal than the metal heat exchange tube.

The inventors have found through research that the traditional condenser using metal heat exchange tubes is difficult to seal the metal. In order to ensure the sealing performance of the condenser, the shell can only be made of thick steel plates or castings, thereby further increasing The weight of the condenser is increased, and the corrosion resistance is poor.

For this reason, in this embodiment, the shell-and-tube heat exchanger casing 201 of the regenerator 200 is also made of plastic, so that the sealing between the shell-and-tube heat exchanger casing 201 and the heat exchange tubes 202 can be easily In this way, the thickness of the shell 201 of the shell-and-tube heat exchanger can be reduced. In this way, the weight of the regenerator 200 is further reduced, and the anti-corrosion performance of the regenerator 200 is also enhanced. As an example, the shell 201 and the heat exchange tube 202 of the shell-and-tube heat exchanger can be made of the same type of plastic, and integrally formed by injection molding, so as to provide excellent sealing performance.

In this embodiment, the solution dispenser 203 can also be made of plastic to achieve further weight reduction. As an example, the solution distributor 203 and the shell and tube heat exchanger housing 201 can be made of the same type of plastic to facilitate manufacture, assembly and sealing.

In addition to reducing the weight of the regenerator 200 , the inventors also wish to reduce the size of the regenerator 200 . The miniaturized regenerator 200 can make the overall volume of the absorption refrigerating machine smaller, so that it can be applied to households or other commercial occasions that do not require high cooling power. However, the inventor found in the process of miniaturization of the regenerator 200 that as the cooling power decreases, the required circulation of the working medium also decreases, and correspondingly, the outer surface of the heat exchange tube 202 cannot be fully wetted by the lithium bromide solution. And the unfavorable phenomenon of "dry spot". In order to avoid dry spots, the inventor tried to increase the flow rate of the circulation pump, and continuously sprayed the working liquid far more than the actual required circulation volume from the liquid accumulation pool at the bottom of the regenerator 200 to the heat exchange at the top. Tube 202 on. However, this increases the flow rate of the circulating pump, increasing parasitic energy consumption and operating costs. Contrary to the trend of miniaturization and family-oriented development of absorption refrigerators.

Therefore, the inventors optimized the outer diameter of the heat exchange tubes 202 and the center-to-center distance between adjacent heat exchange tubes 202 . Set the outer diameter of the heat exchange tubes 202 to 3 mm to 5 mm, set the center distance of adjacent heat exchange tubes 202 in the same row to 4 mm to 6 mm, and set the center distance of the upper and lower adjacent heat exchange tubes 202 to 5 mm ~8mm. In this embodiment, the outer diameter of the heat exchange tubes 202 is 3 mm; the center-to-center distance between adjacent heat exchange tubes 102 in the same row is 4 mm; the center-to-center distance between the upper and lower adjacent heat exchange tubes 202 is 7 mm. By adopting the above-mentioned heat exchange tubes 202 with small diameter and large density arrangement, a large heat exchange area is obtained per unit volume, thereby realizing a smaller volume under the premise of satisfying high heat exchange efficiency. The gap between adjacent heat exchange tubes 202 in the same row is only 1mm. In this gap, the surface tension and gravity of the lithium bromide solution combine to make the lithium bromide solution not only drip, but also diffuse and accumulate in the gap. , so as to ensure that the refrigerant water is always submerged in the heat exchange tube 202 . The lithium bromide solution and the heat exchange tube 202 perform combined heat exchange of immersion type and falling film type. At the same time, under the effect of the surface tension of the lithium bromide solution, the lithium bromide solution does not need to fill the entire shell 201 of the shell-and-tube heat exchanger, only the lithium bromide solution needs to be able to immerse the heat exchange tube 202 all the time. Therefore, the deposition height of the lithium bromide solution in the gap can be adjusted according to the flow rate of the lithium bromide solution, so that the lithium bromide solution can evenly immerse the heat exchange tube 202 when the cooling load is small and the flow rate of the lithium bromide solution is small. In this way, the contact between the lithium bromide solution and the heat exchange tube 202 can be ensured without multiple pumping, which effectively prevents dry spots, reduces parasitic energy consumption and operating costs, and makes the regenerator 200 miniaturized.

Referring again to FIG. 3 , between two adjacent rows of heat exchange tubes 202 , a plurality of support bars 206 are arranged at equal intervals. The support bar 206 is used to support the two adjacent rows of heat exchange tubes 202 up and down, and bear the structural stress brought by the high vacuum inside the shell and tube heat exchanger shell 201 . In this embodiment, the support bar 206 is made of plastic to ensure light weight. As an example, the support bars 206 and the heat exchange tubes 202 are made of the same type of plastic to facilitate manufacture.

It should be noted that, in other specific embodiments, the wall thickness of the heat exchange tube 202 can be adjusted between 0.1 mm and 0.5 mm; the outer diameter of the heat exchange tube 202 can be adjusted between 3 mm and 5 mm; The center-to-center distance of adjacent heat exchange tubes 202 in the same row can be adjusted between 4 mm and 6 mm; the center-to-center distance between upper and lower adjacent heat exchange tubes 202 can be adjusted between 5 mm and 8 mm.

Evaporator 300 and Absorber 400

Referring to FIG. 4 , FIG. 4 is an assembly state diagram of the evaporator 300 and the one-side absorber 400 in the embodiment of the present invention. In FIG. 4 , the right side is the evaporator 300 , the left side is the absorber 400 , and between the evaporator 300 and the absorber 400 is a sloped liquid barrier 502 . The slope type liquid separator 502 can be regarded as a part of the evaporator 300 and also can be regarded as a part of the absorber 400 . The refrigerant water required by the evaporator 300 on the right is supplied from the orifice 104 provided at the bottom of the condenser above it. The function of the evaporator 300 on the right is to make the refrigerant water from the condenser absorb a large amount of heat from the cold water flowing in the tube side of the evaporator 300 to vaporize, thereby achieving the purpose of cooling the cold water. The generated refrigerant vapor enters the left absorber 400 . The concentrated solution required by the absorber 400 is supplied from the supply hole 207 at the bottom of the regenerator disposed above it. The absorber 400 cools the lithium bromide concentrated solution, so that the lithium bromide concentrated solution continuously absorbs refrigerant vapor to become a lithium bromide dilute solution. The resulting dilute lithium bromide solution is used for recycling back to the regenerator, thus completing the refrigeration cycle. The slope-type liquid separator 502 is used to trap liquid droplets entrained in the refrigerant vapor, and only allows the refrigerant vapor to pass through the slope-type liquid separator 502 and enter the absorber 400 .

Next, the evaporator 300 will be described.

Referring to FIG. 5 , FIG. 5 is a structural cross-sectional view of the evaporator 300 and the one-side absorber 400 in the embodiment of the present invention.

The evaporator 300 is a shell-and-tube heat exchanger, including a shell-and-tube heat exchanger shell 301 and heat exchange tubes 302 . In this embodiment, several rows of heat exchange tubes 302 are arranged in upper and lower layers (only part of the heat exchange tubes 302 are shown in the figure. It can be understood that in other specific implementation manners, the heat exchange tubes 302 can be arranged in other ways. ), the heat exchange tube 302 is fixed in the casing 301 of the shell-and-tube heat exchanger. During operation, cold water circulates in the heat exchange tube 302 , and the refrigerant water from the condenser flows between the heat exchange tube 102 and the shell 101 of the shell-and-tube heat exchanger. The refrigerant water absorbs a large amount of heat from the cold water in the heat exchange tube 302 and vaporizes to obtain refrigerant steam, thereby achieving the purpose of cooling the cold water.

In the evaporator 300, the heat exchange tube 302 is made of plastic, and the thickness of the tube wall of the heat exchange tube 302 is 0.1mm˜0.5mm. In this embodiment, the tube wall thickness of the heat exchange tube 302 is 0.15 mm. Compared with the metal heat exchange tube, such an extremely thin thickness increases the heat exchange area by more than ten times under the same volume, which makes up for the insufficient heat transfer performance of plastic, so that the heat transfer performance of the heat exchange tube 302 can reach the absorption type. Chiller requirements. Since the heat exchange tube 302 is made of plastic, the weight of the evaporator 300 can be greatly reduced compared with the use of metal heat dissipation tubes, thereby achieving light weight. Due to the excellent anti-corrosion performance of the plastic, it is also possible to avoid the generation of non-condensable gas due to the corrosion of the heat exchange tube 302, which increases the working efficiency of the absorption refrigerating machine. The heat exchange tube 302 made of plastic is easier to seal than the metal heat exchange tube.

Limited by the physical and chemical properties of pure water, for various refrigeration applications that meet the needs of human comfort, the evaporation temperature of the evaporator 300 is usually set at about 5°C, which requires the shell-and-tube heat exchanger shell of the evaporator 300 The saturation pressure of the body 301 must be kept at about 872Pa. This kind of pressure has high requirements on airtightness. The inventor found through research that the traditional evaporator using metal heat exchange tubes is difficult to seal the metal. In order to ensure the sealing performance of the evaporator, the shell can only It is made of thick steel plate or casting, which further increases the weight of the evaporator and has poor corrosion resistance.

For this reason, in this embodiment, the shell-and-tube heat exchanger casing 301 of the evaporator 300 is also made of plastic, so that the sealing between the shell-and-tube heat exchanger casing 301 and the heat exchange tubes 302 can be easily In this way, the thickness of the casing 301 of the shell-and-tube heat exchanger can be reduced. In this way, the weight of the evaporator 300 is further reduced, and the corrosion resistance of the evaporator 300 is also enhanced. As an example, the shell 301 and the heat exchange tube 302 of the shell-and-tube heat exchanger can be made of the same type of plastic, and integrally formed by injection molding, so as to provide excellent sealing performance.

In addition to reducing the weight of the evaporator 300 , the inventor also wishes to achieve a miniaturization of the evaporator 300 . The miniaturized evaporator 300 can make the overall volume of the absorption refrigerating machine smaller, so that it can be applied to households or other commercial occasions that do not require high cooling power. However, the inventor found in the miniaturization process of the condenser 100 that due to the high specific heat capacity of the refrigerant water, the flow rate of the refrigerant water that needs to be evaporated to complete the rated cooling capacity is relatively small, and it is necessary to set up a complicated refrigerant distributor to distribute the refrigerant water Precisely distributed to each heat exchange tube 302, so that the refrigerant water fully infiltrates the heat exchange tube 302 and forms a water film (falling film for short) whose thickness uniformly decreases along the surface of the heat exchange tube 302. With the evaporation of the refrigerant water, the refrigerant water decreases continuously, so that the heat exchange tube 302 cannot be fully wetted, resulting in "dry spots" on the surface of the heat exchange tube 302 . The appearance of dry spots greatly reduces the heat transfer coefficient of the evaporator 300 . Therefore, in order to ensure sufficient humidification, it is necessary to configure a dedicated refrigerant pump to use refrigerant water that is far more than the actual evaporation capacity. Under the pumping of the refrigerant pump, the non-evaporated refrigerant water is continuously sprayed from the bottom of the evaporator 300 to the The top of the evaporator 300. The existence of the refrigerant pump, on the one hand, increases the volume and weight of the refrigerator, making it difficult to miniaturize the evaporator 300, and on the other hand increases the operating cost.

Therefore, the inventors optimized the outer diameter of the heat exchange tubes 302 and the center-to-center distance between adjacent heat exchange tubes 302 . Set the outer diameter of the heat exchange tubes 302 to 3 mm to 5 mm, set the center distance of adjacent heat exchange tubes 302 in the same row to 4 mm to 6 mm, and set the center distance of the upper and lower adjacent heat exchange tubes 302 to 5 mm ~8mm. In this embodiment, the outer diameter of the heat exchange tubes 302 is 3 mm; the center distance between adjacent heat exchange tubes 302 in the same row is 4 mm; the center distance between the upper and lower adjacent heat exchange tubes 302 is 7 mm. By adopting the heat exchange tubes 302 with small diameter and high density, a large heat exchange area is obtained per unit volume, thereby realizing a smaller volume under the premise of satisfying high heat exchange efficiency. The outer diameter of the heat exchange tubes 302 is only 3 mm, and the gap between adjacent heat exchange tubes 302 in the same row is only 1 mm, such a small gap can exert the beneficial effect of the surface tension of the refrigerant water. Under the combined effect of surface tension and gravity of the refrigerant water, part of the refrigerant water accumulates in the gap, diffuses and wets the row of heat exchange tubes 302 , and the other part drops to the lower heat exchange tubes 302 through the gap. Then, at each gap of the heat exchange tubes 302 , part of the refrigerant water drops to the lower layer through the gaps, and the other part accumulates and diffuses to wet the heat exchange tubes 302 . By analogy, the refrigerant water flows through the heat exchange tubes 302 of each layer in sequence. The refrigerant water flows through the layered heat exchange tubes 302 from the orifice 104 , all by gravity. When working in a steady state under rated refrigeration conditions, the refrigerant water supplied from the orifice 104 passes through the uppermost row of heat exchange tubes 302 , and when it reaches the lowermost row of heat exchange tubes 302 , it is completely evaporated without using a refrigerant pump. When the refrigerant water flows through the gap, under the dual effects of surface tension and gravity, there is both flow and accumulation in the gap; the gap can automatically adjust the accumulation height of the refrigerant water in the gap according to the flow rate of the refrigerant water. When the flow rate of refrigerant water is large, the height of liquid accumulated in the gap will submerge the heat exchange tube 302, and the flow rate flowing through the gap is also large. When the refrigerant water flow rate is small, the height of liquid accumulated in the gap is low, but due to the wettability of the surface of the heat exchange tube 302, the refrigerant liquid will infiltrate the heat exchange tube 302, reducing the chance of "dry spots" on the surface of the heat exchange tube 302, Improve heat transfer coefficient. In this way, there is no need to install a dedicated refrigerant pump and refrigerant distributor, which reduces operating costs and is also conducive to the miniaturization of the evaporator 300 .

Referring to FIG. 6 , FIG. 6 is an exploded view of the structure of the evaporator 300 and the one-side absorber 400 in the embodiment of the present invention. Between two adjacent rows of heat exchange tubes 302 , a plurality of support bars 303 are arranged at equal intervals, and the support bars 303 are arranged to intersect with the heat exchange tubes 302 and are perpendicular to the heat exchange tubes 302 . The support bar 303 is used to support the two adjacent rows of heat exchange tubes 302 up and down, and bear the structural stress brought by the high vacuum inside the shell and tube heat exchanger shell 301 . In this embodiment, the support bar 303 is made of plastic to ensure light weight. As an example, the support bars 303 and the heat exchange tubes 302 are made of the same type of plastic to facilitate manufacture.

It should be noted that, in other specific embodiments, the wall thickness of the heat exchange tube 302 can be adjusted between 0.1 mm and 0.5 mm; the outer diameter of the heat exchange tube 302 can be adjusted between 3 mm and 5 mm; The center-to-center distance of adjacent heat exchange tubes 302 in the same row can be adjusted between 4 mm and 6 mm; the center-to-center distance between upper and lower adjacent heat exchange tubes 302 can be adjusted between 5 mm and 8 mm.

Next, the absorber 400 will be described.

Referring again to FIG. 5 , the absorber 400 includes a shell-and-tube heat exchanger shell 401 , heat exchange tubes 402 and a solution distributor 403 . In this embodiment, several rows of heat exchange tubes 402 are arranged in upper and lower layers (only part of the heat exchange tubes 402 are shown in the figure. It can be understood that in other specific implementation manners, the heat exchange tubes 402 can be arranged in other ways. ), the heat exchange tube 402 is fixed in the casing 401 of the shell-and-tube heat exchanger, thereby forming the shell-and-tube heat exchanger 410 . During operation, cold circulates in the heat exchange tube 402 , and the space between the heat exchange tube 402 and the shell 401 of the shell-and-tube heat exchanger is used for the flow of concentrated lithium bromide solution. The cold water in the heat exchange tube 402 is used to cool the lithium bromide concentrated solution, so that the lithium bromide concentrated solution continuously absorbs refrigerant vapor. The solution distributor 403 is a cuboid with a cavity inside, and the cavity is used for flowing the lithium bromide concentrated solution. The lower part of the solution distributor 403 is a solution spraying surface 404 . The solution distributor 403 is arranged on the upper part of the shell-and-tube heat exchanger 410 , and the size of the solution spraying surface 404 is the same as that of the upper end surface of the shell-and-tube heat exchanger 410 . Referring to FIG. 6 again, a plurality of discharge holes 405 are uniformly arranged on the solution spraying surface 404 . As an embodiment, the discharge holes 405 are long holes extending in the width direction of the solution spraying surface 404 and three holes are equally spaced to form a row. In the length direction of the solution spraying surface 404, multiple drainage orifices 405 are arranged at equal intervals. The drain hole 405 is used to evenly spray the dilute lithium bromide solution in the cavity to the heat exchange tube 402 below.

Referring to FIG. 5 again, the shell-and-tube heat exchanger shell 401 of the absorber 400 and the shell-and-tube heat exchanger shell 301 of the evaporator 300 are of an integrated structure, and the heat exchange tube 402 of the absorber 400 and the shell-and-tube heat exchanger shell 402 of the evaporator 300 The heat exchange tubes 302 are separated by sloped liquid baffles 502 .

In the absorber 400, the heat exchange tube 402 is made of plastic, and the thickness of the tube wall of the heat exchange tube 402 is 0.1mm-0.5mm. In this embodiment, the tube wall thickness of the heat exchange tube 402 is 0.15 mm. Compared with the metal heat exchange tube, such an extremely thin thickness increases the heat exchange area by more than ten times under the same volume, which makes up for the insufficient heat transfer performance of plastic, so that the heat transfer performance of the heat exchange tube 402 can reach the absorption type Chiller requirements. Since the heat exchange tube 402 is made of plastic, the weight of the absorber 400 can be greatly reduced compared with the use of a metal heat dissipation tube, thereby achieving light weight. Due to the excellent anti-corrosion performance of the plastic, it is also possible to avoid the generation of non-condensable gas due to the corrosion of the absorber 400, thereby increasing the working efficiency of the absorption refrigerating machine. The heat exchange tube 302 made of plastic is easier to seal than the metal heat exchange tube.

The inventor found through research that the traditional absorber using metal heat exchange tubes is difficult to seal the metal. In order to ensure the sealing performance of the absorber, the shell can only be made of thick steel plate or casting, which further increases the The weight of the absorber is increased, and the corrosion resistance is poor.

For this reason, in this embodiment, the shell-and-tube heat exchanger shell 401 of the absorber 400 is also made of plastic, so that the seal between the shell-and-tube heat exchanger shell 401 and the heat exchange tube 402 can be easily In this way, the thickness of the shell 401 of the shell-and-tube heat exchanger can be reduced. In this way, the weight of the absorber 400 is further reduced, and the corrosion resistance of the absorber 400 is also enhanced. As an example, the shell 401 and the heat exchange tube 402 of the shell-and-tube heat exchanger can be made of the same type of plastic, and integrally formed by injection molding, so as to provide excellent sealing performance.

In this embodiment, the solution dispenser 403 can also be made of plastic to achieve further weight reduction. As an example, the solution distributor 403 and the shell and tube heat exchanger shell 401 can be made of the same type of plastic to facilitate manufacture, assembly and sealing.

In addition to reducing the weight of the absorber 400 , the inventors also wish to achieve miniaturization of the absorber 400 . The miniaturized absorber 400 can make the overall volume of the absorption refrigerating machine smaller, so that it can be applied to households or other occasions that do not require high cooling power. However, the inventor found in the process of miniaturization of the absorber 400 that as the cooling power decreases, the circulation volume of the required working fluid also decreases, and correspondingly, the outer surface of the heat exchange tube 402 cannot be fully wetted by the lithium bromide solution. And the unfavorable phenomenon of "dry spot". In order to avoid dry spots, the inventor tried to increase the flow rate of the circulating pump, and continuously sprayed the working medium liquid far more than the actual required circulating volume from the liquid pool at the bottom of the absorber 400 to the heat exchange at the top. on tube 402. However, this increases the flow rate of the circulating pump, increasing parasitic energy consumption and operating costs. Contrary to the trend of miniaturization and family-oriented development of absorption refrigerators.

Therefore, the inventors optimized the outer diameter of the heat exchange tubes 402 and the center-to-center distance between adjacent heat exchange tubes 402 . Set the outer diameter of the heat exchange tubes 402 to 3 mm to 5 mm, set the center distance of adjacent heat exchange tubes 402 in the same row to 4 mm to 6 mm, and set the center distance of the upper and lower adjacent heat exchange tubes 402 to 5 mm ~8mm. In this embodiment, the outer diameter of the heat exchange tubes 402 is 3 mm; the center distance between adjacent heat exchange tubes 402 in the same row is 4 mm; the center distance between the upper and lower adjacent heat exchange tubes 402 is 7 mm. By adopting the heat exchange tubes 402 with small diameter and large density, a large heat exchange area is obtained per unit volume, thereby realizing a smaller volume under the premise of satisfying high heat exchange efficiency. The gap between adjacent heat exchange tubes 402 in the same row is only 1mm. In this gap, the surface tension and gravity of the lithium bromide solution combine to make the lithium bromide solution not only drip flow, but also diffuse and accumulate in the gap. , so as to ensure that the refrigerant water is always submerged in the heat exchange tube 402 . The lithium bromide solution and the heat exchange tube 402 perform combined heat exchange of immersion type and falling film type. At the same time, under the action of the surface tension of the lithium bromide solution, the lithium bromide solution does not need to fill the entire shell 401 of the shell-and-tube heat exchanger, only the lithium bromide solution needs to be able to immerse the heat exchange tube 402 all the time. Therefore, the deposition height of the lithium bromide solution in the gap can be adjusted according to the flow rate of the lithium bromide solution, so that the lithium bromide solution can evenly immerse the heat exchange tube 402 when the cooling load is small and the flow rate of the lithium bromide solution is small. In this way, the contact between the lithium bromide solution and the heat exchange tube 402 can be ensured without multiple pumping, which effectively prevents dry spots, reduces parasitic energy consumption and operating costs, and enables the absorber 400 to be miniaturized.

Referring again to FIG. 3 , between two adjacent rows of heat exchange tubes 402 , a plurality of support bars 406 are arranged at equal intervals. The support bar 406 is used to support the two adjacent rows of heat exchange tubes 402 up and down, and bear the structural stress brought by the high vacuum inside the shell and tube heat exchanger shell 401 . In this embodiment, the support bar 406 is made of plastic to ensure light weight. As an example, the support bar 406 and the heat exchange tube 402 are made of the same plastic to facilitate manufacture.

It should be noted that, in other specific embodiments, the wall thickness of the heat exchange tube 402 can be adjusted between 0.1 mm and 0.5 mm; the outer diameter of the heat exchange tube 402 can be adjusted between 3 mm and 5 mm; The center-to-center distance of adjacent heat exchange tubes 402 in the same row can be adjusted between 4 mm and 6 mm; the center-to-center distance between upper and lower adjacent heat exchange tubes 402 can be adjusted between 5 mm and 8 mm.

Solution Heat Exchanger 600

FIG. 7 is a schematic perspective view of a solution heat exchanger 600 in an embodiment of the present invention.

The solution heat exchanger 600 is a plate heat exchanger, which is used for heat exchange between the lithium bromide concentrated solution and the lithium bromide dilute solution.

FIG. 8 is a schematic structural view of the exposed heat exchange wall plate 620 after removing some components of the solution heat exchanger 600 in the embodiment of the present invention.

In the solution heat exchanger 600, multiple heat-exchanging wall plates 620 are arranged in multiple layers, and the interior of the plate heat exchanger shell 624 is evenly separated by multiple heat-exchanging wall plates 620 to form channels for the circulation of cold and hot solutions: that is, mutually Dilute solution channel 612 and concentrated solution channel 614 are separated. The low-temperature dilute lithium bromide solution and the high-temperature concentrated lithium bromide solution contact the heat exchange wall plate 620 at the same time, and the heat exchange wall plate 620 becomes the medium for heat exchange between the low-temperature lithium bromide dilute solution and the high-temperature lithium bromide concentrated solution. The four corners of the solution heat exchanger 600 are also respectively provided with inlets and outlets of the solution channels, which are respectively: the concentrated solution inlet 406 in the upper left corner, the concentrated solution outlet 402 in the lower left corner, the dilute solution inlet 401 in the lower right corner, and the dilute solution inlet 401 in the upper left corner. Solution outlet 408 .

Also visible in FIG. 8 is the solution pump 631 , the channel 604 for the concentrated solution to the shell side of the absorber 400 and the channel 609 for the weak solution to the regenerator 200 . The solution pump 631 is used to provide power to the dilute solution flowing in the solution heat exchanger 600, pump it from the dilute solution inlet 601 in the lower right corner to the dilute solution outlet 608 in the upper left corner, and deliver it to the regenerator 200 through the connecting pipe. solution dispenser (not shown on the figure).

As shown in FIG. 8 , the surface of the heat exchange wall plate 620 is stamped with densely distributed, vertically and horizontally alternate textured convex strips 622 , which are used to support the heat exchange wall plate 620 under The pressure generated by the vacuum simultaneously causes the fluid flowing through the protruding strips 622 to generate turbulent flow, so as to improve the heat transfer coefficient.

In the solution heat exchanger 600, the heat exchange wall plate 620 is made of plastic, and the thickness of the heat exchange wall plate 620 is 0.1mm˜0.5mm. In this embodiment, the thickness of the heat exchange wall plate 620 is 0.15 mm. Compared with the metal heat exchange wall plate, such an extremely thin thickness makes up for the insufficient heat transfer performance of the plastic, so that the heat transfer performance of the heat exchange wall plate 620 can meet the requirements of the absorption refrigerator. Since the heat exchanging wall plate 620 is made of plastic, the weight of the solution heat exchanger 600 can be greatly reduced compared with the metal heat exchanging wall plate, thereby achieving light weight. Due to the excellent anti-corrosion performance of the plastic, it is also possible to avoid the generation of non-condensable gas due to the corrosion of the heat exchange wall plate 620, thereby increasing the working efficiency of the absorption refrigerating machine. At the same time, the heat exchange wall plate 620 made of plastic is easier to seal than the metal heat exchange wall plate.

After research, the inventor found that the traditional solution heat exchanger using metal heat exchange wall plates is difficult to seal the metal. In order to ensure the sealing performance of the solution heat exchanger, the shell can only be made of thick steel plates or castings. As a result, the weight of the solution heat exchanger is further increased, and the corrosion resistance is poor.

For this reason, in this embodiment, the plate heat exchanger shell 624 of the solution heat exchanger 600 is also made of plastic, so that the sealing between the tube plate heat exchanger shell 624 and the heat exchange wall plate 620 can be easily In this way, the thickness of the plate heat exchanger shell 624 can be reduced. In this way, the weight of the solution heat exchanger 600 is further reduced, and the corrosion resistance of the solution heat exchanger 600 is also enhanced. As an example, the shell 624 of the plate heat exchanger and the heat exchange wall plate 620 can be made of the same type of plastic, and integrally formed by injection molding, so as to provide excellent sealing performance.

In this embodiment, the protruding strip 622 is made of plastic to ensure light weight. As an example, the protruding strip 622 and the heat exchange wall plate 620 are made of the same type of plastic to facilitate manufacture.

The distance between the heat exchange wall plates 620 of two adjacent layers is 0.5 mm to 3 mm, and the distance between the heat exchange wall plates 620 of two adjacent layers is 1 mm in this embodiment. At the same time, because the thickness of the heat exchange wall plate 620 is 0.15 mm, the structure of the solution heat exchanger 600 is more compact, and a larger heat exchange area is provided per unit volume, which is beneficial to the miniaturization of the solution heat exchanger 600 .

The condenser 100, regenerator 200, evaporator 300, absorber 400 and solution heat exchanger 600 described in this embodiment are used as a part of the absorption refrigeration unit to form the absorption refrigeration unit. Several absorption refrigeration units can also form an absorption refrigeration matrix.

The above descriptions are only some embodiments of the present invention, and are not intended to limit the present invention. For those skilled in the art, the present invention may have various modifications and changes. Any modifications, equivalent replacements, improvements, etc. made within the spirit and principles of the present invention shall be included within the protection scope of the present invention.

Claims (31)

1. absorption refrigeration unit internal heat assembly, it is characterised in that:

Described absorption refrigeration unit internal heat assembly is regenerator, absorber, condenser, vaporizer or solution heat exchanger In any one；

When described absorption refrigeration unit internal heat assembly is any one in regenerator, absorber, condenser or vaporizer When planting, described absorption refrigeration unit internal heat assembly includes shell-and-tube heat exchanger；Described shell-and-tube heat exchanger possesses shell Formula heat exchanger shell and heat exchanger tube；Described heat exchanger tube is arranged in described shell-and-tube heat exchanger housing；Described heat exchanger tube is by plastics Make；

When described absorption refrigeration unit internal heat assembly is solution heat exchanger, change inside described absorption refrigeration unit Hot assembly includes plate type heat exchanger；Described plate type heat exchanger possesses plate type heat exchanger housing and heat exchange wallboard；Described heat exchange wallboard It is arranged in described plate type heat exchanger housing；Described heat exchange wallboard is made of plastics.

Absorption refrigeration unit internal heat assembly the most according to claim 1, it is characterised in that:

The pipe thickness of described heat exchanger tube is 0.1～0.5mm.

Absorption refrigeration unit internal heat assembly the most according to claim 2, it is characterised in that:

The pipe thickness of described heat exchanger tube is 0.15mm.

Absorption refrigeration unit internal heat assembly the most according to claim 1, it is characterised in that:

Heat exchanger tube described in some rows is levels arrangement；It is arranged at intervals with multiple support bar between heat exchanger tube described in adjacent two rows； Described support bar is used for supporting heat exchanger tube described in adjacent two rows.

Absorption refrigeration unit internal heat assembly the most according to claim 4, it is characterised in that:

Described support bar is made of plastics.

Absorption refrigeration unit internal heat assembly the most according to claim 5, it is characterised in that:

Described support bar and described heat exchanger tube are made up of otherwise identical plastic.

Absorption refrigeration unit internal heat assembly the most according to claim 1, it is characterised in that:

The external diameter of described heat exchanger tube is 3mm～5mm；

The centre-to-centre spacing of the adjacent described heat exchanger tube being positioned at same row is 4mm～6mm；

The centre-to-centre spacing of neighbouring described heat exchanger tube is 5mm～8mm.

Absorption refrigeration unit internal heat assembly the most according to claim 7, it is characterised in that:

The external diameter of described heat exchanger tube is 3mm；

The centre-to-centre spacing of the adjacent described heat exchanger tube being positioned at same row is 4mm；

The centre-to-centre spacing of neighbouring described heat exchanger tube is 7mm.

Absorption refrigeration unit internal heat assembly the most according to claim 1, it is characterised in that:

When described absorption refrigeration unit internal heat assembly is any one in regenerator, absorber, condenser or vaporizer When planting, described shell-and-tube heat exchanger housing is made of plastics.

Absorption refrigeration unit internal heat assembly the most according to claim 9, it is characterised in that:

Described shell-and-tube heat exchanger housing and described heat exchanger tube are made up of otherwise identical plastic.

11. according to the absorption refrigeration unit internal heat assembly described in any one in claim 1～10, and its feature exists In:

The thickness of described heat exchange wallboard is 0.1mm～0.5mm.

12. absorption refrigeration unit internal heat assemblies according to claim 11, it is characterised in that:

The thickness of described heat exchange wallboard is 0.15mm.

13. according to the absorption refrigeration unit internal heat assembly described in any one in claim 1～10, and its feature exists In:

Weavy grain shape raised line is distributed on described heat exchange wallboard, is used for supporting described heat exchange wallboard, and makes to flow through the stream of described raised line Body produces turbulent flow to improve heat transfer coefficient.

14. absorption refrigeration unit internal heat assemblies according to claim 13, it is characterised in that:

Described raised line is made of plastics.

15. absorption refrigeration unit internal heat assemblies according to claim 14, it is characterised in that:

Described raised line and described heat exchange wallboard are made up of otherwise identical plastic.

16. according to the absorption refrigeration unit internal heat assembly described in any one in claim 1～10, and its feature exists In:

Described heat exchange wallboard is multilamellar arrangement；

The wooden partition spacing of the described heat exchange wallboard of adjacent two layers is 0.5mm～3mm.

17. absorption refrigeration unit internal heat assemblies according to claim 16, it is characterised in that:

The wooden partition spacing of the described heat exchange wallboard of adjacent two layers is 1mm.

18. according to the absorption refrigeration unit internal heat assembly described in any one in claim 1～10, and its feature exists In:

When described absorption refrigeration unit internal heat assembly is solution heat exchanger, described plate type heat exchanger housing is by plastics Make.

19. absorption refrigeration unit internal heat assemblies according to claim 18, it is characterised in that:

Described plate type heat exchanger housing and described heat exchange wallboard are made up of otherwise identical plastic.

20. according to the absorption refrigeration unit internal heat assembly described in any one in claim 1～10, and its feature exists In:

Described absorption refrigeration unit internal heat assembly is vaporizer；Described heat exchanger tube is internal for for cold water flow, described For flowing for coolant water between heat exchanger tube and described shell-and-tube heat exchanger housing.

21. absorption refrigeration unit internal heat assemblies according to claim 20, it is characterised in that:

Heat exchanger tube described in each row is provided with ramp type liquid islocation plate towards the side of absorber, and described ramp type liquid islocation plate is for cutting Stay chilled water, only allow coolant steam to pass through.

22. according to the absorption refrigeration unit internal heat assembly described in any one in claim 1～10, and its feature exists In:

Described absorption refrigeration unit internal heat assembly is condenser；Described heat exchanger tube is internal to flow for Cooling Water, institute State between heat exchanger tube and shell-and-tube heat exchanger housing for flowing for coolant steam.

23. absorption refrigeration unit internal heat assemblies according to claim 22, it is characterised in that:

Heat exchanger tube described in each row is provided with ramp type liquid islocation plate towards the side of regenerator, and described ramp type liquid islocation plate is for cutting Stay the drop in coolant steam, only allow coolant steam to pass through.

24. according to the absorption refrigeration unit internal heat assembly described in any one in claim 1～10, and its feature exists In:

Described absorption refrigeration unit internal heat assembly is absorber or regenerator, described heat exchanger shell and described heat exchanger tube Collectively form shell-and-tube heat exchanger；

For flowing for lithium-bromide solution between described heat exchanger tube and shell-and-tube heat exchanger housing；

When described absorption refrigeration unit internal heat assembly is absorber, described heat exchanger tube is internal for Cooling Water stream Dynamic；When described absorption refrigeration unit internal heat assembly is regenerator, described heat exchanger tube is internal to flow for supplying hot water.

25. absorption refrigeration unit internal heat assemblies according to claim 24, it is characterised in that:

Described absorption refrigeration unit internal heat assembly also includes solution dispenser；Described solution dispenser is arranged on described pipe Shell heat exchanger top；Having cavity inside described solution dispenser, described solution dispenser bottom is for changing downwards The spray solution face of heat pipe spray solution.

26. absorption refrigeration unit internal heat assemblies according to claim 25, it is characterised in that:

Described solution dispenser is made of plastics.

27. absorption refrigeration unit internal heat assemblies according to claim 26, it is characterised in that:

Described solution dispenser and shell-and-tube heat exchanger housing are made up of otherwise identical plastic.

28. absorption refrigeration unit internal heat assemblies according to claim 24, it is characterised in that:

Described spray solution face size is identical with described shell-and-tube heat exchanger upper surface；

The spray solution face of described solution dispenser is provided with some discharge orifices, for solution being distributed to uniformly lower section Heat exchanger tube surface.

29. absorption refrigeration unit internal heat assemblies according to claim 24, it is characterised in that:

When described absorption refrigeration unit internal heat assembly is absorber, described in each row, heat exchanger tube is towards the side of vaporizer Being provided with ramp type liquid islocation plate, described ramp type liquid islocation plate is used for retaining chilled water, only allows coolant steam to pass through；

When described absorption refrigeration unit internal heat assembly is regenerator, described in each row, heat exchanger tube is towards the side of condenser Being provided with ramp type liquid islocation plate, described ramp type liquid islocation plate, for retaining the drop in coolant steam, only allows coolant steam to lead to Cross.

30. absorption refrigeration unit, it is characterised in that:

Including the absorption refrigeration unit internal heat assembly described in any one in claim 1～29.

31. absorption refrigeration matrixes, it is characterised in that:

Including the absorption refrigeration unit described in several claim 30.