阅读说明：本技术 一种新型壳管式换热器及船用制冷系统 (Novel shell and tube heat exchanger and marine refrigerating system ) 是由 杨牧青 杨滨滨 邓志阳 黄家丽 邓志红 向淼 于 2020-07-03 设计创作，主要内容包括：本发明公开一种新型壳管式换热器,包括换热管、壳体、流体挡板,流体挡板内置于壳体内部,换热管穿过流体挡板,在壳体内延伸,壳体沿换热管方向通过流体挡板分隔,两端密封；换热管外部流动载冷剂,内部流动制冷剂,载冷剂通过流体挡板分隔的空隙流动,流过换热管,完成载冷剂和制冷剂之间的换热,在载冷剂流入壳体一侧,离换热管端面及靠近此侧壳体密封面之间,设置一个静压腔体,里面固定设置有一个同轴线的活动叶轮,可通过流入壳体的载冷剂推动叶轮运转。应用该技术方案,在静压腔体内设置一个叶轮,可通过静压腔,减少动力损失,也通过推动叶轮,改变流向,达到降低动力损耗,还额外提供了一部分流向换热管方向动力,加强了换热。(The invention discloses a novel shell-and-tube heat exchanger, which comprises a heat exchange tube, a shell and a fluid baffle, wherein the fluid baffle is arranged in the shell, the heat exchange tube penetrates through the fluid baffle and extends in the shell, the shell is separated by the fluid baffle along the direction of the heat exchange tube, and two ends of the shell are sealed; the secondary refrigerant flows outside the heat exchange tube, the refrigerant flows inside the heat exchange tube, the secondary refrigerant flows through the gap separated by the fluid baffle and flows through the heat exchange tube to finish the heat exchange between the secondary refrigerant and the refrigerant, a static pressure cavity is arranged between the end surface of the heat exchange tube and the sealing surface of the shell close to the side when the secondary refrigerant flows into the shell, a coaxial movable impeller is fixedly arranged inside the static pressure cavity, and the impeller can be pushed to operate by the secondary refrigerant flowing into the shell. By applying the technical scheme, the impeller is arranged in the static pressure cavity, power loss is reduced through the static pressure cavity, the flow direction is changed by pushing the impeller, power loss is reduced, part of power flowing to the direction of the heat exchange tube is additionally provided, and heat exchange is enhanced.)

1. A novel shell-and-tube heat exchanger comprises a heat exchange tube, a shell and a fluid baffle, wherein the fluid baffle is arranged in the shell, the heat exchange tube penetrates through the fluid baffle and extends in the shell, the shell is separated by the fluid baffle along the direction of the heat exchange tube, and two ends of the shell are sealed; the heat exchange tube is characterized in that a static pressure cavity is further arranged on one side of the heat exchange tube where the secondary refrigerant flows, and an impeller coaxial with the shell is arranged in the static pressure cavity, and the impeller is movably fixed in the static pressure cavity and can push blades which are arranged on the impeller and inclined towards the direction of the secondary refrigerant flowing to the heat exchange tube to rotate so as to drive the impeller to operate.

2. The novel shell and tube heat exchanger as claimed in claim 1, wherein the fluid baffle is a baffle plate, the baffle plate partially shields the inner cross section of the shell and tube along the direction of the heat exchange tubes, the baffle plate is arranged in a staggered manner from top to bottom in sequence to form a curved flow passage, and the coolant flows in the flow passage in a curved manner to complete the heat exchange with the heat exchange tubes.

3. The novel shell and tube heat exchanger as set forth in claim 1 wherein the fluid baffle is a jet plate, the outer edge of the jet plate is sealed with the inner surface of the shell and has jet holes formed therein, and a coolant is injected through the jet holes onto the heat exchange tubes to perform heat exchange with the heat exchange tubes.

4. The novel shell and tube heat exchanger as set forth in claim 1 wherein the impeller extends a rotary rod centrally along the heat exchange tubes, the rotary rod passing through a bearing fixed to the fluid baffle plate, terminating at the sealing surface of the other end of the shell, and being fixed and rotatable by the bearing.

5. The novel shell and tube heat exchanger as set forth in claim 4 wherein flights are fixedly disposed in segments on rotating rods separated by said fluid baffle segments, said flights being freely rotatable without obstruction.

6. The novel shell and tube heat exchanger as set forth in claim 4 wherein the connection between the rotating rod and the impeller is a flexible connection.

7. The novel shell-and-tube heat exchanger as recited in claim 4, wherein the diameter of the rotating rod is 5-10 mm, and the surface is provided with spiral concave veins.

8. The shell and tube heat exchanger as set forth in claim 1 wherein coolant entering the shell flows through open channels located near the central axis of the shell and tangentially upward along the central portion of the impeller to propel the impeller blades.

9. The shell and tube heat exchanger as recited in claim 1 wherein coolant entering said shell flows in through a channel of circular arc shape disposed at an upper portion of said static pressure chamber, and is sealed along a section of four sides coaxial with said shell and enclosed by an inner wall of said shell, and exits through an outlet port in the same direction as a tangential line of said impeller, thereby driving said impeller blades to rotate.

10. The marine refrigeration system using the novel shell-and-tube heat exchanger as claimed in any one of claims 1 to 9, wherein the refrigeration system comprises a compressor, a heat recovery liquid storage tank, an air-cooled condenser, a throttling device, an evaporator, a freezing liquid storage tank and a refrigeration end, a high-temperature high-pressure gas refrigerant discharged by the compressor firstly flows into the novel shell-and-tube heat exchanger through an exhaust pipe, exchanges heat with a secondary refrigerant in the novel shell-and-tube heat exchanger, the heated secondary refrigerant flows into the heat recovery liquid storage tank for storage, the refrigerant which completes primary heat recovery continuously flows into the air-cooled condenser, and finally completes condensation through forced heat exchange of a fan; the condensed liquid refrigerant continuously flows into the throttling device through a pipeline, flows into the evaporator after being throttled, is evaporated, absorbs the heat of the secondary refrigerant flowing into the evaporator, circularly flows into the freezing liquid storage tank to be stored after the temperature of the secondary refrigerant is reduced, the evaporated gas refrigerant is finished, and then flows back to the compressor for compression through an air return pipeline, and the refrigeration compression cycle is continuously finished;

the low-temperature secondary refrigerant stored in the freezing liquid storage tank directly flows into the heat exchange tube at the refrigerating tail end, and the fresh-keeping or freezing requirement of the articles is realized in a way that the refrigerating tail end absorbs the heat of the articles; the secondary refrigerant absorbing heat circularly flows back to the freezing liquid storage tank and flows to the evaporator through the freezing liquid storage tank, and circularly exchanges heat with the refrigerant evaporated in the evaporator to continuously absorb cold;

when the surface of the refrigeration tail end is frosted and the heat exchange efficiency is reduced, the refrigeration secondary refrigerant flowing to the refrigeration tail end is closed at the moment, the high-temperature secondary refrigerant stored in the heat recovery liquid storage tank flows into the refrigeration tail end to defrost by absorbing the cold energy of the refrigeration tail end, the temperature of the secondary refrigerant absorbing the cold energy is reduced, the secondary refrigerant circularly flows back to the heat recovery liquid storage tank and then flows into the novel shell and tube heat exchanger by the heat recovery liquid storage tank, the heat of the high-temperature high-pressure gas refrigerant is circularly absorbed, the temperature of the high-temperature secondary refrigerant is ensured during defrosting, the defrosting is finally completed, and after the defrosting is completed, the high-temperature secondary refrigerant stops supplying liquid to the refrigeration tail end, and the low-temperature secondary refrigerant stored in the refrigeration liquid storage tank supplies.

11. The marine refrigeration system of claim 10 wherein said high and low temperature coolant is calcium chloride, sodium chloride or ethylene glycol.

12. A marine refrigeration system according to claim 10, wherein said low temperature coolant temperature is in the range of-10 ℃ to-60 ℃.

13. A marine refrigeration system according to claim 10, wherein said evaporator is a new shell and tube heat exchanger.

14. A marine refrigeration system according to claim 10, wherein said evaporator is a flooded shell and tube heat exchanger.

15. The marine refrigeration system of claim 10 wherein said refrigeration terminal is a low temperature air cooler of aluminum fin construction, the cold air flowing through the fins and the low temperature coolant within the heat exchange tubes disposed within the fins effecting heat exchange.

16. The marine refrigeration system of claim 10 wherein said refrigeration terminal is a frame-type quick-freeze system, wherein items to be frozen are placed on the heat exchange tubes and heat exchange is accomplished by flowing cryogenic coolant.

17. A marine refrigeration system as claimed in claim 10 wherein said refrigeration terminal is a quick freeze screw bed type system.

18. The marine refrigeration system of claim 10 wherein said refrigeration terminal is a wall bank pipe freezing arrangement system.

19. The marine refrigeration system of claim 10 wherein the refrigeration terminal is an ice making system, and wherein the low temperature coolant flows through the heat exchange tubes to exchange heat with water outside the heat exchange tubes, such that the water becomes ice, thereby making ice.

Technical Field

The invention relates to the field of heat exchangers and refrigeration, in particular to a novel shell-and-tube heat exchanger and a marine refrigeration system using the novel shell-and-tube heat exchanger.

Background

The shell and tube heat exchanger that uses in the air conditioning field at present, generally for the secondary refrigerant gets into shell and tube heat exchanger after, directly strikes and places the heat exchange tube of shell and tube heat exchanger in, after using for a period of time, can cause the damage of this part pipeline, leads to the refrigerant to reveal to influence shell and tube heat exchanger's normal use, and because the secondary refrigerant business turn over direction is perpendicular with shell and tube heat exchanger's heat exchange tube, cause the secondary refrigerant to flow into shell and tube heat exchanger after, the direction changes suddenly, make the kinetic energy loss of secondary refrigerant great, and can form the endless loop in the part, directly influence the heat transfer. Based on above shortcoming, a shell and tube heat exchanger appears afterwards, and this kind of heat exchanger adds one section cavity when secondary refrigerant gets into the casing, separates through a reposition of redundant personnel orifice plate, supplies the liquid for the heat exchange tube through the hole that sets up on the reposition of redundant personnel orifice plate, accomplishes the heat transfer, because the heat exchange tube is located reposition of redundant personnel orifice plate opposite side, just so can avoid the loss that the striking produced, this kind of technical record is in patent application number: CN201220473419.5, the patent name "shell and tube heat exchanger of central air conditioner set".

However, in practical use, the technical scheme has the defect that holes formed in the flow dividing pore plate are easy to block after being used for a period of time, and the secondary refrigerant is connected with an external pipeline in a complex and troublesome-to-replace mode through a pipeline liquid supply mode coaxial with the shell of the heat exchanger.

Disclosure of Invention

In order to overcome the defects, the invention provides a novel shell-and-tube heat exchanger which comprises a heat exchange tube, a shell and a fluid baffle, wherein the fluid baffle is arranged in the shell, the heat exchange tube penetrates through the fluid baffle and extends in the shell, the shell is separated by the fluid baffle along the direction of the heat exchange tube, and two ends of the shell are sealed; the heat exchange tube is characterized in that secondary refrigerant flows outside the heat exchange tube, refrigerant flows inside the heat exchange tube, the secondary refrigerant flows through a gap separated by the fluid baffle and flows through the heat exchange tube to complete heat exchange between the secondary refrigerant and the refrigerant, a static pressure cavity is further arranged between the end surface of the heat exchange tube and a sealing surface of the shell close to the side where the secondary refrigerant flows into the shell, an impeller coaxial with the shell is arranged in the static pressure cavity, and the impeller is movably fixed in the static pressure cavity and can push blades which are arranged on the impeller and inclined towards the direction of the secondary refrigerant flowing into the heat exchange tube to rotate so as to drive the impeller to operate.

Furthermore, the fluid baffle is a baffle plate, the baffle plate partially shields the inner section of the shell tube along the direction of the heat exchange tube, the baffle plate is sequentially arranged up and down to form a curved flow channel, and the secondary refrigerant flows in the flow channel in a curved manner to finish heat exchange with the heat exchange tube. The baffle plates are arranged, a curve flow channel is formed through the baffle plates, the flow state of the secondary refrigerant is changed by changing the flow direction of the secondary refrigerant, and the effect of improving the heat exchange efficiency is achieved.

Furthermore, the fluid baffle is a jet flow plate, the outer edge of the jet flow plate is sealed with the inner surface of the shell, a jet hole is formed in the upper surface of the jet flow plate, and secondary refrigerant is sprayed onto the heat exchange tube through the jet hole to complete heat exchange between the secondary refrigerant and the heat exchange tube.

The jet holes are formed in the baffle plate, secondary refrigerant is sprayed onto the heat exchange tubes through the jet holes, the flow velocity is greatly improved, and the effect of improving the heat exchange efficiency can be achieved.

Furthermore, a rotating rod extends from the central position of the impeller along the direction of the heat exchange tube, and the stirring rod penetrates through a bearing fixed on the fluid baffle plate, is stopped at the sealing surface at the other end of the shell, and is fixed and rotates through the bearing.

The rotary rod is arranged, and the secondary refrigerant is disturbed through the rotation of the rotary rod, so that the effect of further improving the heat exchange efficiency is achieved.

Further, on the rotating rods partitioned by the fluid baffle segments, spiral pieces are fixedly arranged in segments, and the spiral pieces can freely rotate without obstacles.

The spiral piece is arranged on the rotating rod, and the secondary refrigerant can be further disturbed through the rotation of the spiral piece, so that the effect of further improving the heat exchange efficiency is achieved.

Further, the rotating rod is movably connected with the impeller.

The movable connection can achieve the effect of being convenient for replacing the damaged rotary rod.

Further, the diameter of the rotating rod is 5-10 mm, and spiral concave grains are arranged on the surface of the rotating rod.

The rotary rod is provided with the spiral concave veins, so that the secondary refrigerant can be further disturbed through the spiral concave veins, and the effect of further improving the heat exchange efficiency is achieved.

Furthermore, the secondary refrigerant entering the shell flows out of a pipeline arranged at the middle position of the impeller and in the tangential upward direction through a pipeline arranged at the central axis of the shell close to the impeller, so as to push the blades of the impeller to operate.

The inflow direction of the secondary refrigerant is arranged along the tangential direction of the middle part of the impeller, so that the kinetic energy loss of the secondary refrigerant can be reduced, and the effect of influencing heat exchange due to possible formation of dead circulation is avoided.

Furthermore, the secondary refrigerant entering the shell flows in through the upper position of the static pressure cavity, is sealed along a section of four sides which is coaxial with the shell and is surrounded by the inner wall of the shell, and flows out from an arc-shaped flow channel with an outlet in the same direction with the tangent line of the impeller, so that the impeller blades are pushed to operate.

The outflow direction of the circular arc-shaped flow channel is arranged along the tangential direction of the impeller, so that the kinetic energy loss of the secondary refrigerant can be reduced, and the effect of influencing heat exchange due to possible formation of dead circulation is avoided.

The invention also provides a marine refrigeration system applying the novel shell-and-tube heat exchanger, the refrigeration system comprises a compressor, a heat recovery liquid storage tank, an air-cooled condenser, a throttling device, an evaporator, a freezing liquid storage tank and a refrigeration tail end, high-temperature and high-pressure gas refrigerant discharged by the compressor firstly flows into the novel shell-and-tube heat exchanger through an exhaust pipe and exchanges heat with secondary refrigerant in the novel shell-and-tube heat exchanger, the heated secondary refrigerant flows into the heat recovery liquid storage tank for storage, the primary heat recovery refrigerant is finished, the secondary refrigerant continuously flows into the air-cooled condenser, and the condensation is finished finally through forced heat exchange of a fan; the condensed liquid refrigerant continuously flows into the throttling device through a pipeline, flows into the evaporator after being throttled, is evaporated, absorbs the heat of the secondary refrigerant flowing into the evaporator, circularly flows into the freezing liquid storage tank for storage after the temperature of the secondary refrigerant is reduced, and the evaporated gas refrigerant flows back to the compressor through the pipeline to continuously complete the compression cycle;

the low-temperature secondary refrigerant stored in the freezing liquid storage tank directly flows into the heat exchange tube at the refrigerating tail end, and the fresh-keeping or freezing requirement of the articles is realized in a way that the refrigerating tail end absorbs the heat of the articles; the secondary refrigerant absorbing heat circularly flows back to the freezing liquid storage tank and flows to the evaporator through the freezing liquid storage tank, and circularly exchanges heat with the refrigerant evaporated in the evaporator to continuously absorb cold;

when the surface of the refrigeration tail end is frosted and the heat exchange efficiency is reduced, the refrigeration secondary refrigerant flowing to the refrigeration tail end is closed at the moment, the high-temperature secondary refrigerant stored in the heat recovery liquid storage tank flows into the refrigeration tail end to defrost by absorbing the cold energy of the refrigeration tail end, the temperature of the secondary refrigerant absorbing the cold energy is reduced, the secondary refrigerant circularly flows back to the heat recovery liquid storage tank and then flows into the novel shell and tube heat exchanger by the heat recovery liquid storage tank, the heat of the high-temperature high-pressure refrigerant is circularly absorbed, the temperature of the high-temperature secondary refrigerant is ensured during defrosting, defrosting is finally completed, and after defrosting is completed, the high-temperature secondary refrigerant stops supplying liquid to the refrigeration tail end, and continues to be supplied with liquid to the refrigeration tail end by the low-temperature.

The heat exchange effect between the refrigerant and the secondary refrigerant can be effectively improved, and the marine refrigeration system has the advantages of more compact volume and convenience in installation and maintenance.

Further, the high-temperature secondary refrigerant and the low-temperature secondary refrigerant are calcium chloride, sodium chloride or ethylene glycol.

Calcium chloride, sodium chloride or ethylene glycol is used as the high-temperature and low-temperature secondary refrigerant, and the high-temperature and low-temperature secondary refrigerant is a common material, so that the high-temperature and low-temperature secondary refrigerant has the effects of convenience in purchase and lower use cost.

Further, the temperature of the low-temperature secondary refrigerant is-10 to-60 ℃.

The temperature of the low-temperature secondary refrigerant is-10 to-60 ℃, and the effect of adjusting the temperature of the low-temperature secondary refrigerant according to the requirement to realize the fresh-keeping or refrigeration requirement can be achieved.

Further, the evaporator is a novel shell and tube heat exchanger.

The evaporator uses a novel shell and tube heat exchanger, and can achieve the effect of improving the evaporation heat exchange efficiency.

Further, the evaporator is a flooded shell and tube heat exchanger.

The evaporator adopts a flooded shell and tube heat exchanger, and the effect of improving the energy efficiency can be achieved.

Furthermore, the refrigeration tail end is a low-temperature air cooler with an aluminum fin structure, and cold air flows through the fins and low-temperature secondary refrigerant in the heat exchange tubes arranged in the fins to complete heat exchange.

The refrigeration end adopts the air-cooler, can take hoist and mount and sit ground formula mounting means, can many parallelly connected uses, can reach the installation flexibility, is convenient for change, and can realize in a flexible way keeping fresh to article, perhaps freezing treatment's effect.

Furthermore, the refrigeration tail end is a frame type quick-freezing structural system, articles to be frozen are placed on the heat exchange tube, and heat exchange is completed through flowing low-temperature secondary refrigerant.

The objects to be frozen are directly placed on the frame-type quick-freezing structure heat exchange tubes, and the frame-type quick-freezing structure is arranged in a tube row mode, so that the effect of quick freezing can be achieved.

Further, the refrigeration tail end is a quick-freezing spiral bed type system.

By adopting the quick-freezing spiral bed type system, the effect of freezing food in a short time can be achieved by rotating the articles on the spiral bed.

Further, the refrigeration end is a wall drain pipe freezing structure system.

The freezing structure of the wall calandria is adopted, the air temperature of the closed space is reduced firstly, then low-temperature air is contacted with objects, the freezing of the objects is realized, and the effects of simple structure and lower installation and maintenance cost can be achieved.

Furthermore, the refrigeration tail end is provided with an ice making system, and low-temperature secondary refrigerant flows through the heat exchange tube and exchanges heat with water outside the heat exchange tube, so that the water is changed into ice, and ice making is completed.

The ice is made by using the low-temperature secondary refrigerant, so that the effects of simple refrigeration system and convenient maintenance can be achieved.

By applying the technical scheme, the static pressure cavity is arranged at the end, close to the water inlet pipe, of the shell-and-tube heat exchanger, the rotatable impeller is arranged in the static pressure cavity, so that the secondary refrigerant flowing into the shell-and-tube heat exchanger firstly flows into the static pressure cavity along the tangential direction of the impeller and then expands in the static pressure cavity, the flow velocity is reduced, the loss of dynamic pressure can be greatly reduced, and meanwhile, the secondary refrigerant is changed along the flow direction of the heat exchange pipe of the shell-and-tube heat exchanger by pushing the impeller to rotate, so that the secondary refrigerant is more gentle; in the process of pushing the impeller to rotate, the pushing force can also be decomposed, and the power for pushing a part of moving secondary refrigerant to flow along the direction of the heat exchange tube of the shell-and-tube heat exchanger is provided, so that the heat exchange efficiency is improved, and therefore:

firstly, the problems of kinetic energy loss caused by direct impact of the secondary refrigerant on the heat exchange tube, possible damage of the heat exchange tube and possible reduction of heat exchange efficiency caused by dead circulation are effectively solved, the service life is effectively prolonged, the kinetic energy loss is reduced, and the heat exchange effect is improved;

secondly, because the secondary refrigerant has power flowing towards the direction of the heat exchange tube, the secondary refrigerant can avoid the aggregation of obstructions in the shell-and-tube heat exchanger by the power, and can achieve the effect of ensuring the normal heat exchange efficiency for a long time;

finally, a conventional tube distribution mode of the shell-and-tube heat exchanger for the secondary refrigerant to enter and exit can be adopted, so that the effect of simplifying the connection with an external pipeline and facilitating the connection and replacement in a narrow use space is achieved when the shell-and-tube heat exchanger is installed with the outside.

Drawings

In order to more clearly illustrate the technical solutions in the embodiments of the present invention, the drawings needed to be used in the description of the embodiments will be briefly introduced below, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and it is obvious for those skilled in the art to obtain other drawings based on these drawings without inventive exercise.

Fig. 1 is a front view showing the structure of a first embodiment 1 of the shell and tube heat exchanger of the present invention.

Fig. 2 is a side view of the structure of the first embodiment of the shell and tube heat exchanger 1 of the present invention.

Fig. 3 is a front view showing the structure of the second embodiment of the shell and tube heat exchanger 2 of the present invention.

Fig. 4 is a side view of a second embodiment of the shell and tube heat exchanger 2 of the present invention.

Figure 5 is a schematic diagram of a refrigeration system incorporating the present invention.

Detailed Description

In order to make the objects, technical solutions and advantages of the present invention clearer, the present invention will be described in further detail with reference to the accompanying drawings, and it is apparent that the described embodiments are only a part of the embodiments of the present invention, not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.

Embodiment 1 of the present invention provides a novel shell-and-tube heat exchanger, as shown in fig. 1, including a heat exchange tube, a U-shaped elbow, a left sealing end cover 100, a coolant inlet tube 101, an arc-shaped flow channel 102, an impeller 103, a static pressure cavity 106, a shell 107, a baffle plate 111, a coolant outlet tube 112, a 1 st flow divider 113, a 2 nd flow divider 114, and a right sealing end cover 115, where the baffle plate 111 is semicircular, the coolant inlet tube passes through the right sealing end cover 115, and is communicated with the built-in 1 st flow divider 113, the refrigerant enters the 1 st flow divider 113 through a refrigerant inlet pipe, then flows into the heat exchange tube communicating with the other end of the 1 st flow divider 113, and at the other end of the heat exchange tube, passes through a U-shaped bend communicating with the heat exchange tube, returns to the 2 nd flow divider 114, and flows out of the novel shell-and-tube heat exchanger through a refrigerant outlet pipe communicated with the 2 nd flow divider 114, passing through the right sealing end cover 115.

The heat exchange tube built in the shell 107 passes through the baffle plate 111 and is fixed by the baffle plate 111; the baffle plates 111 are arranged inside the shell 107 in a staggered manner from top to bottom in sequence along the direction of the heat exchange tubes to form a curved flow passage, secondary refrigerant flows in through the secondary refrigerant inlet tube 101 and flows into the shell 107 through the circular-arc flow passage 102, the circular-arc flow passage 102 is coaxial with the shell 107 and is a section of four-surface seal surrounded by the inner wall of the shell 107, the outlet direction of the channel is arranged along the tangential direction of the impeller 107, and the secondary refrigerant flowing out of the circular-arc flow passage 102 drives the impeller 103 to rotate by pushing blades arranged on the impeller 103.

The structural schematic diagram of the circular arc-shaped flow channel 102 is shown in fig. 2, and it can be seen that the liquid inlet pipe 101 is arranged at the upper position of the end surface of the casing 107, one end of the inner inlet is connected with the secondary refrigerant liquid inlet pipe 101, the periphery of the inner inlet is sealed, the inner wall of the casing 107 is coaxially arranged, the direction can be left and right, the outer wall of the circular arc-shaped flow channel 102 does not collide with the outer ring of the impeller 103, and the outlet direction of the circular arc-shaped flow channel 102.

The method adopts the tangential direction with the impeller 103 and sets the secondary refrigerant liquid outlet mode, so that the problems of kinetic energy loss caused by sudden change of the flow direction of the secondary refrigerant in the flow process and possible influence of the dead circulation of the secondary refrigerant on heat exchange can be effectively solved.

During actual use, the secondary refrigerant pushing the impeller 103 to rotate converges in the static pressure cavity 106, the flow rate is reduced in the static pressure cavity 106, the static pressure is increased, then the secondary refrigerant flows in a curve through a curve flow channel formed by the baffle plates 111, the secondary refrigerant finally completes heat exchange with the refrigerant flowing in the heat exchange tube, and the secondary refrigerant completing heat exchange flows out through the secondary refrigerant outlet pipe 112.

The coolant inlet pipe 101 is disposed at the upper portion of the housing 107, and the coolant outlet pipe 112 is disposed at the upper portion of the housing 107, but may be disposed at other suitable positions, for example, the coolant inlet pipe 101 is disposed on the left end cap 100, the coolant outlet pipe 112 is disposed on the right end cap 115, and so on; the directions of the secondary refrigerant liquid inlet pipe 101 and the secondary refrigerant liquid outlet pipe 112 are perpendicular to the heat exchange tubes of the shell-and-tube heat exchanger, and the shell-and-tube heat exchanger is arranged to be the same as a conventional shell-and-tube heat exchanger, so that subsequent pipeline connection with the outside can be greatly simplified. The blades of the impeller 103 incline in the flow direction of the secondary refrigerant flowing along the heat exchange tube direction, the secondary refrigerant flows out through the arc-shaped flow channel 102, and when the blades of the impeller 103 are pushed to rotate, the blades are divided into two parts of force along the blade direction, one part of force pushes the blades to rotate, and the other part of force pushes the secondary refrigerant to flow along the heat exchange tube direction.

The problem of reducing the kinetic energy loss of the secondary refrigerant and improving the heat exchange efficiency can be solved by utilizing the inclination of the blades of the impeller 103 to decompose the power of the secondary refrigerant into the force for pushing the impeller 103 to rotate and the force for pushing the secondary refrigerant to flow towards the heat exchange tube.

The impeller 103 is fixed by a 1 st bearing 104, and the 1 st bearing 104 is fixed on a base at the central position inside the left sealing end cover 100. In order to improve the heat exchange efficiency and the disturbance of the coolant, a rotating rod 108 extends out of the right center of the impeller and faces the direction of the right sealing end cover 115.

The rotating rod 108 may be a metal rod, such as a stainless steel metal rod, or a non-metal rod, such as a plastic rod, etc.

One end of the rotating rod 108 can be movably and fixedly connected with the impeller 103 through a movable slot 105 arranged at the right side of the impeller 103 in an inserting manner, and of course, other movable connection manners, such as a threaded connection, can also be adopted.

The diameter of the rotating rod 108 is 5 mm, or 10 mm, the actual size can be selected according to the heat exchange capacity of the shell-and-tube heat exchanger, for example, when the heat exchange capacity of the shell-and-tube heat exchanger is less than 25 kilowatts, the rotating rod 108 of 5 mm can be selected, when the heat exchange capacity of the shell-and-tube heat exchanger is greater than 25 kilowatts, the rotating rod 108 of 10 mm can be selected, or the rotating rod 108 of other sizes of 5-10 mm, in addition, in the actual use, the rotating rod 108 of specifications beyond 5-10 mm can be adopted, as long as it can be ensured that the rotating.

The rotating rod 108 passes through the inner cavity of the 2 nd bearing 109 fixed in the hole of the baffle plate 111 and is fixed through the 2 nd bearing 109, and the rotating rod 108 is movably and fixedly connected with the rotating rod 108, so that the rotating rod 108 is convenient to replace when damaged.

The surface of the rotating rod 108 is provided with spiral concave veins, and one or more spiral concave veins can be opened along the length direction of the rotating rod 108, and are integrally and uninterruptedly arranged, or are arranged in sections according to the space separated by the baffle plates 111.

Besides spiral concave lines are formed on the rotating rod 108, spiral sheets 110 can be arranged on the outer surface of each section of the rotating rod 108 separated by the baffle plate 111, the spiral sheets 100 can freely rotate without obstacles, in practical use, other protrusions which are beneficial to enhancing the secondary refrigerant disturbance can be arranged, such as spiral convex lines or triangular protrusions, in addition, the spiral concave lines and the spiral sheets 100 can be arranged in a mixed mode on the rotating rod 108, namely spiral concave lines are arranged at the intervals of the spiral sheets 100 in a segmented mode, and the depth of the spiral concave lines can reach 1/4-1/3 of the radius size of the rotating rod 108.

When the secondary refrigerant pushes the impeller 103 to rotate, the rotating rod 108 connected with the impeller 103 also rotates along with the impeller, and the strength of the disturbed secondary refrigerant is improved by the spiral concave veins or the spiral sheets 100, so that the heat exchange efficiency is further improved.

Embodiment 2 of the present invention provides another novel shell-and-tube heat exchanger, specifically referring to fig. 3, which is different from the first one in that:

firstly, the baffle plate 111 is changed into a jet flow plate, the outer edge of the jet flow plate is sealed with the inner surface of the shell 107, the jet flow hole is formed in the jet flow plate, the secondary refrigerant is sprayed onto the heat exchange tube through the jet flow hole to complete heat exchange with the heat exchange tube, and the secondary refrigerant does not bypass the baffle plate any more and performs heat exchange in a curve flow mode like the embodiment 1.

By adopting the jet flow plate, when the secondary refrigerant passes through the jet holes, the secondary refrigerant is sprayed to the heat exchange tube at a higher jet speed, so that the heat exchange efficiency between the secondary refrigerant and the heat exchange tube is improved, and meanwhile, when the secondary refrigerant pushes the impeller 103 to rotate, the motive power flowing towards the heat exchange tube can push the blocking objects to flow, so that the blocking objects are prevented from being gathered in the jet holes on the jet flow plate, and the influence on heat exchange caused by the blockage of the jet holes on the jet flow plate is avoided.

Secondly, the coolant inlet pipe 101 is no longer disposed at the upper portion of the housing 107, but disposed upward along the tangential direction of the middle portion of the left end cap 100, and the specific structure is shown in fig. 4. as can be seen from fig. 4, after the coolant flows in through the coolant inlet pipe 101, the coolant flows out through the outlet of the coolant inlet pipe 101, and the impeller 103 is pushed to operate along the tangential flow path of the impeller 103 formed on the left end cap 100.

The coolant inlet 101 can be located in other suitable locations than the left end cap 100, such as on the housing 107 adjacent the impeller 103, and the coolant outlet 112 can be located on the right end cap 115 or on the housing 107, as desired.

In example 2, since

Compared with embodiment 1, embodiment 2 eliminates the arc-shaped flow passage 102 of embodiment 1, and is simpler and more compact in structure, except for the above differences, the other parts are the same as those of embodiment 1, and will not be described again here.

Fig. 5 shows a marine refrigeration system using the novel shell-and-tube heat exchanger of the present invention, which includes a compressor 205, a heat recovery liquid storage tank 207, an air-cooled condenser 201, a throttling device 216, an evaporator 213, a freezing liquid storage tank 215, and a refrigeration end 217, wherein a high-temperature and high-pressure gas refrigerant discharged from the compressor 205 flows into a heat exchange tube of the novel shell-and-tube heat exchanger 206 through an exhaust pipe 203, a coolant flows into the novel shell-and-tube heat exchanger 206 through a pipe 209, exchanging heat with the refrigerant flowing in the heat exchange tube of the novel shell-and-tube heat exchanger 206, condensing the refrigerant to release heat to the secondary refrigerant, flowing the heated secondary refrigerant into the heat recovery liquid storage tank 207 through the pipeline 208 for storage, finishing the primary heat recovery of the refrigerant, continuously flowing into the heat exchange tube of the air-cooled condenser 201, the fan 200 rotates to force air to flow across the surface of the air-cooled condenser 201, and forced heat exchange is carried out to finally finish condensation; the condensed liquid refrigerant continues to flow into the throttling device 216 through the pipeline 202, flows into the heat exchange tube of the evaporator 213 after throttling the refrigerant, evaporates to absorb the heat of the secondary refrigerant flowing into the evaporator 213 through the pipeline 212, flows out of the evaporator 213 through the pipeline 211 after reducing the temperature of the secondary refrigerant, circularly flows into the freezing liquid storage tank 215 for storage, and circulates back to the compressor 205 for compression through the gas return pipeline to finish the refrigeration compression cycle.

The low-temperature secondary refrigerant stored in the freezing liquid storage tank 215 is directly pumped into the heat exchange tube of the refrigeration tail end 217 through the 2 nd circulating pump 218 and the opened 4 th electromagnetic valve 220, and the fresh-keeping or the freezing requirement of the articles is realized in a way that the refrigeration tail end 217 absorbs the heat of the articles; the coolant absorbing heat circulates back to the freezing liquid storage tank 215 through the opened 2 nd solenoid valve 214 and flows to the evaporator 213 through the freezing liquid storage tank 215, and the coolant circulating and evaporating in the evaporator 213 exchanges heat to continuously absorb cold, and at this time, the 1 st solenoid valve 210 and the 3 rd solenoid valve 219 are closed.

When the surface of the refrigeration tail end 217 is frosted and the heat exchange efficiency is reduced, the 2 nd electromagnetic valve 214 and the 4 th electromagnetic valve 220 are closed at the moment, the high-temperature secondary refrigerant stored in the heat recovery liquid storage tank 207 is pumped into the heat exchange tube of the refrigeration tail end 217 through opening the 3 rd electromagnetic valve 219 and passing through the 1 st circulating pump 204 to absorb the cold energy of the refrigeration tail end 217, dissolve the frost and reduce the temperature of the secondary refrigerant absorbing the cold energy, the high-temperature high-pressure gas refrigerant is circularly absorbed by ensuring the temperature of the high-temperature secondary refrigerant during defrosting and finally finish defrosting after the temperature of the secondary refrigerant flows back to the heat recovery liquid storage tank 207 through the opened 1 st battery valve 210 and the heat recovery liquid storage tank 207, the 2 nd electromagnetic valve 214 and the grade 4 electromagnetic valve 220 are opened after the defrosting is finished, the high-temperature secondary refrigerant stops supplying liquid to the refrigeration tail end 217, and the low-temperature secondary refrigerant stored in the refrigeration liquid storage tank 215 continues to supply liquid to the, and (5) continuously cooling.

In order to adjust the temperature value of the low-temperature secondary refrigerant according to the requirement and realize the requirements of fresh keeping or refrigeration, the refrigeration system for the ship preferably selects the secondary refrigerant as calcium chloride, sodium chloride or ethylene glycol, and the temperature of the low-temperature secondary refrigerant is-10 to-60 ℃.

In order to improve the efficiency of the evaporation heat exchange, the evaporator 213 may be preferably a new shell-and-tube heat exchanger.

To improve energy efficiency, the evaporator 213 may preferably be a flooded shell and tube heat exchanger.

In order to solve the problems that the installation mode can be flexibly selected and used according to the needs, a plurality of cold air inlets can be connected in parallel for use, and replacement is convenient, preferably, the refrigeration tail end 217 can be selected and used as a low-temperature type air cooler with an aluminum fin structure, and cold air flows through fins and low-temperature secondary refrigerant arranged in heat exchange tubes inside the fins to complete heat exchange.

In order to solve the problem that the articles can be rapidly frozen, preferably, the refrigeration tail end 217 can be selected from a frame type quick-freezing structure system, the articles to be frozen are placed on the heat exchange tubes, heat exchange is completed through flowing low-temperature secondary refrigerant, the frame type quick-freezing structure is arranged in a tube row mode commonly used in a refrigeration house, namely, the heat exchange tubes are made into a frame shape capable of stacking the articles, and the articles are directly placed on the heat exchange tubes, so that the refrigeration requirement is met.

To solve the problem of time freezing food, the refrigeration end 217 may be preferably a quick-freezing spiral bed type system, i.e. a spiral bed, in which the conveyor belt is made into a spiral shape, the articles spirally move on the spiral conveyor belt, and the cold air cooled by the refrigeration end 217 forcibly flows to finish the quick freezing of the articles.

In order to solve the problem of reducing the installation and maintenance cost, the refrigeration tail end 217 is preferably a wall calandria freezing structure system, namely a wall calandria system, namely a heat exchange pipe is arranged close to a wall, articles to be frozen are placed in a closed space, and the freezing of the articles is completed through natural air convection or forced convection.

In order to solve the problem of convenience in maintenance during ice making, preferably, the refrigeration end 217 is an ice making system, and the low-temperature secondary refrigerant flows through the heat exchange tube and exchanges heat with water outside the heat exchange tube, so that the water is changed into ice to complete ice making.

In order to solve the stability problem of the refrigeration system for the ship, the whole refrigeration system can be integrally arranged on a shock absorption base for use, and certainly, part of components of the whole refrigeration system, such as a compressor 205 and the like, can be independently arranged on the shock absorption base or can be directly arranged on the ship for use.

The above description is only for the preferred embodiment of the present invention, but the scope of the present invention is not limited thereto, and any changes or substitutions that can be easily conceived by those skilled in the art within the technical scope of the embodiment of the present invention are included in the scope of the present invention. Therefore, the protection scope of the present invention shall be subject to the protection scope of the claims.