US20040140083A1

US20040140083A1 - Vibration-type heat exchanger

Info

Publication number: US20040140083A1
Application number: US10/468,019
Authority: US
Inventors: Gi-chun Kim; Doo-hwan Kim
Original assignee: PARK SANG-HAE
Current assignee: PARK SANG-HAE
Priority date: 2001-02-28
Filing date: 2002-02-27
Publication date: 2004-07-22
Also published as: JP2004522126A; WO2002068891A1

Abstract

The present invention relates to a heat exchanger capable of producing an ice slurry of a process fluid based on a heat exchange between a coolant and the process fluid. The heat exchanger according to the present invention includes a coolant chamber 10 through which a coolant flows, more than one heat transfer tube 20 though which the process fluid flows in a state surrounded by the coolant chamber 10 in order for the coolant to absorb a heat, a vibration member 30 which is vibrated in a state that the vibration member 30 is inserted along the heat transfer tube 20 for thereby separating a frozen coat of the process fluid formed in an inner wall of the heat transfer tube 20, and a vibration unit 40 for vibrating the vibration member 30. The vibration member 30 is selected from the group comprising a screw shaped vibration member 30A, a spring type vibration member 30B, a screw shaped wing type vibration member 30C, a circular plate wing type vibration member 30D, an upper and lower wing type vibration member 30E. The vibration unit 40 includes a vibration motor 41, a plurality of vibration transfer rods 42 connected with the vibration motor 41 for transferring a vibration, and a vibration plate 43 which the vibration member 30 is installed and transfer a vibration of the vibration transfer rods 42 to the vibration member 30.

Description

TECHNICAL FIELD

The present invention relates to a heat exchanger, and in particular to a vibration type heat exchanger which is well adapted to an ice storage system capable of performing an air cooling in such a manner that a ice slurry of the process fluid is formed using a surplus power of a midnight and performing a cooling operation using the ice slurry at a daytime in which the use of power is high.

BACKGROUND ART

Generally, a heater, cooler, evaporator, condenser, etc. each include a heat exchanger for cooling and heating a certain fluid by heat-exchanging between two separated fluids.

Such heat exchangers are constructed in various structures based on its inherent purpose of use. The heat exchanger generally includes a section in which a process fluid is circulated, and a section in which a coolant or heat medium, which heat-exchanges with the process fluid, is circulated. The process fluid and the coolant and heat medium are circulated with respect to the boundary of the materials (for example, a cooper heat transfer tube) having a high heat conduction rate.

As one of the systems that use the heat exchanger, an ice storage system is developed. In the ice storage system, a ice slurry of the process fluid is generated using a surplus power at a midnight in which the rate of the power is low and is stored in a heat accumulator, and the cooling operation is performed using the ice slurry at a daytime in which the rate and load of the power are high. The ice storage system has attracted a big attention as a measurement for saving the energy.

A prior ice storage system will be described with reference to the accompanying drawings. FIG. 9 is a schematic view illustrating a conventional ice storage system. As shown therein, the

ice storage system

100 includes a cooling tower 110, a cooler 120, a heat exchanger 130, a heat accumulator 140, a heat exchanger 150, and an indoor unit 160. A midnight power and daytime common power are alternately used for driving the ice storage system 100.

Namely, at the midnight in which the rate of the low, the

cooler

120 and the heat exchanger 130 are driven for thereby circulating a coolant to a coil 131 of the heat exchanger 130, so that it is possible to produce a ice slurry of a process fluid, and the produced ice slurry is stored in the heat accumulator 140. In addition, at the daytime in which the rate of the power is high, the heat exchanger 150 and the indoor unit 160 are driven for thereby thawing the ice slurry and cooling through the indoor unit 160. In the above conventional ice storage system 100, there are some problems. Among the above problem, as a frozen coat of the process fluid is formed on a surface of the coil 131, the heat transfer efficiency is decreased due to an insulation operation of the frozen coat for thereby decreasing a producing efficiency of the ice slurry.

FIG. 10 is a schematic view illustrating a conventional heat exchanger in which a heat transfer efficiency decrease problem due to a frozen coat is improved. FIG. 11 is a cross-sectional view of FIG. 10. As shown therein, the

heat exchanger

200 includes an outer tube 210 through which a coolant flows, an inner tube 220 through which a process fluid flows, and a wiper 230 for removing a frozen coat formed on an inner surface of the inner tube 220. In the heat exchanger 200, the coolant, which circulates along the outer tube 210, is evaporated, and the process fluid that circulates along the inner tube 220 becomes a ice slurry. At this time, the frozen coat formed in the inner surface of the inner tube 220 is removed by the rotation of the wiper 230. Therefore, it is possible to prevent a decrease of the heat transfer efficiency due to the frozen coat.

However, as shown in FIGS. 10 and 11, in the case of the

heat exchanger

200, it is possible to slightly decree the decrease of the heat transfer efficiency due to the frozen coat, but it is impossible to install a plurality of inner tubes 220 in the outer tube 210 due to its limited structural problem. Therefore, it is impossible to implement a large capacity of the system. It is impossible to increase the performance of the system.

In addition, as shown in FIG. 12, as another conventional heat exchanger, there is a

heat exchanger

300 which has whip rods orbitally driven. The above heat exchanger 300 includes an evaporation tube 310, a plurality of heat transfer tubes 320, a plurality of counter-cranks 330 and whip rods 340, a driving plate 350, an eccentric crank 360, and a driving motor 370.

In the

above heat exchanger

300, a coolant of a low temperature flows through the evaporation tube 310 and cools a process fluid which flows through the heat transfer tube 320 during the evaporation of the coolant. At this time, each whip rod 340 at an eccentric position of the counter crank 330 is orbitally driven along a certain orbital through the driving motor 370, the eccentric crank 360, the driving plate 350, and the counter crank 330. The whip rod 340 scratches the inner of the heat transfer tube 320, and the process fluid frozen on the inner wall of each heat transfer tube 310 is separated from the inner wall of the heat transfer tube 320 and downwardly flows along an inner wall of the same in a ice slurry state.

In the

heat exchanger

300 of FIG. 12, since a plurality of heat transfer tubes 320 are installed in one evaporation tube 310, the efficiency of the heat transfer is enhanced, and the amount of the ice slurry is increased compared to the prior art. However, since the heat exchanger 300 of FIG. 12 includes a accurate whip rod driving system implemented by the driving motor 370, the eccentric crank 360, the driving plate 350, a plurality of counter-cranks 330, and a plurality of whip rods 340 for concurrently orbitally moving a plurality of whip rods 340 positioned in the interior of a plurality of heat transfer tubes 320, the construction of the heat exchanger 300 is very complicated, and a failure frequently occurs in a related part of the system.

In particular, the

whip rod

340 orbitally moves based on the rotation of the counter-crank 330 in a state that the whip rod 340 is caught to the counter-crank 330, and the driving force of the driving plate 350 is transferred to the circular movement of the counter-crank 330 based on the connection between the hole 351 of the driving plate 350 and the protrusion 331 of the counter-crank 330. Therefore, much load is applied to the counter crank 330 that is usually made of plastic resin, and the operation work is frequently stopped due to the damages of the counter crank 330 and the driving plate 350. In addition, there may be a quality problem in the ice slurry of the process fluid.

DISCLOSURE OF INVENTION

Accordingly, it is an object of the present invention to provide a vibration type heat exchanger that overcomes the problems encountered in the conventional art.

As shown in FIG. 1, an orbital rod evaporator, such as an orbital rod freezer, 10 includes a single drive plate 12 having a plurality of drive holes 14 which are matched to interfit with a plurality of drive pins 16 in a plurality of countercranks 18. Each countercrank 18 has a feed orifice 20 and one or more whip rod holes 22 through which a whip rod 24 is supported by an annular flange 26 at its upper end. Each whip rod 24 is thereby supported within a tube 28, tubes 28 being held in a fixed and spaced relationship by an upper and

lower tube sheet

30, 32. The process fluid 34 (represented by arrows in FIG. 1) flows through the holes 14 in drive plate 12 and onto the top of countercrank 18 which has an upper peripheral lip 36 for “pooling” the process fluid as it flows through the orifice hole 20 and unoccupied whip rod hole 22 into the interior of tube 28. As whip rod 24 is driven orbitally around the interior of tube 28, it spreads the process fluid around the interior wall in a thin film which provides the many advantages as explained in the prior art patents mentioned above for orbital whip rod heat exchangers. Refrigerant is circulated through the interior space 38 between

tube sheets

30, 32 which chills the process fluid 34 as it flows through the tubes 28 so that an ice slurry exits the bottom 40 of tubes 28. It is important to note that the tube bottoms 40 are unobstructed as the whip rods 24 are solely supported and driven at their upper ends by countercranks 18. It is also noted in FIG. 1 that whip rods 24 are shown installed in alternate ones of the whip rod holes 22, with respect to the location of drive pin 16. Thus, the mass of whip rods 24 as shown in FIG. 1 is balanced about the center of countercranks 18, or stated differently, the mass of whip rods 24 is distributed equally about the circumference of countercranks 18, or stated differently, the whip rods 24 are balanced within tubes 28, or stated still differently, the dynamic forces generated by the whip rods 24 as they are driven orbitally within tubes 28 are balanced.

It is another object of the present invention to provide a vibration type heat exchanger which is capable of producing an ice slurry of a process fluid using a surplus power of a low rate power at a midnight and storing the produced ice slurry in a heat accumulator and implementing a cooling operation using the ice slurry stored in the heat accumulator at a daytime in which a power rate is high and a power load is high for thereby being well adapted to an ice storage system.

It is still another object of the present invention to provide a vibration type heat exchanger which is capable of effectively preventing a formation of a frozen coat of a process fluid formed on an inner wall of a heat transfer tube and significantly preventing an operation stop problem due to a part damage.

In order to achieve the above objects, there is provided a vibration type heat exchanger which includes a coolant chamber through which a coolant flows, more than one heat transfer tube through which a process fluid flows in a state surrounded by the coolant chamber in order for a coolant to absorb a heat a vibration member which is vibrated in a state that the vibration member is inserted along the heat transfer tube for thereby separating a frozen coat of the process fluid formed in an inner wall of the heat transfer tube, and a vibration unit for vibrating the vibration member. An ice slurry is produced based on a heat exchange between the coolant and the process fluid.

The vibration member can be selected from the group comprising a screw shaped vibration member in which there is not any displacement in an upward and downward direction due to an externally applied force, a spring type vibration member having a certain elastic force in an upward and downward direction, a screw shaped wing type vibration member in which a screw shaped wing is formed in an outer circumferential portion of the rod, a circular plate wing type vibration member in which a circular plate type wing is formed in an outer circumferential surface of the rod, and an upper and lower wing type vibration member in which an upper and lower wing is attached in an upward and downward direction of the rod.

The vibration unit includes a vibration motor, a plurality of vibration transfer rods connected with the vibration motor, and a vibration plate which transfers a vibration of the vibration transfer rod to the vibration member.

The vibration member is connected to the vibration plate by interposing a connection sleeve engaged to an upper portion of the heat transfer tube.

A reinforcing bolt is installed in the interiors of the screw shaped vibration member and the spring type vibration member for thereby decreasing an expansion and contraction of the vibration member. The reinforcing bolt may include at least one water prevention plate.

A non-adhesive film is coated in an inner wall of the heat transfer tube for minimizing a freezing operation of the ice slurry of the process fluid.

BRIEF DESCRIPTION OF THE DRAWING

The present invention will become better understood with reference to the accompanying drawings which are given only by way of illustration and thus are not limitative of the present invention, wherein; [0023]
FIG. 1 is a disassembled perspective view illustrating a vibration type heat exchanger according to the present invention; [0024]
FIG. 2 is a cross-sectional view illustrating a vibration type heat exchanger according to the present invention; [0025]
FIG. 3 is a schematic view illustrating vibration members which may be adapted to a vibration type heat exchanger according to the present invention; [0026]
FIG. 4 is a plan view illustrating a vibration plate according to the present invention; [0027]
FIG. 5 is a perspective view illustrating a connection sleeve according to the present invention; [0028]
FIG. 6 is a perspective view illustrating a maintaining member according to the present invention; [0029]
FIG. 7 is a cross-sectional view illustrating a state of use of a connection sleeve according to the present invention; [0030]
FIG. 8 is a perspective view illustrating an engaged state of a reinforcing bolt according to the present invention; [0031]
FIG. 9 is a block diagram illustrating an example of a conventional heat exchanger; [0032]
FIG. 10 is a perspective view illustrating a conventional heat exchanger, [0033]
FIG. 11 is a cross-sectional view of FIG. 10; and [0034]
FIG. 12 is a disassembled perspective view illustrating another example of a conventional heat exchanger.[0035]

BEST MODE FOR CARRYING OUT THE INVENTION

The vibration type heat exchanger according to the present invention will be described with reference to the accompanying drawings. In the following embodiments of the present invention, a vibration type heat exchanger according to the present invention is illustrative only, not limits the scope of claims of the present invention. [0036]
As shown in FIGS. 1 and 2, the [0037] heat exchanger 1 according to the present invention includes a coolant chamber 10, a plurality of heat transfer tubes 20 installed in the coolant chamber 10, a plurality of vibration members 30 which each correspond to each heat transfer tube 20, and a vibration unit 40 which integrally vibrates the vibration members 30.
The [0038] coolant chamber 10 is a chamber through which a coolant flows and is changed to a phase (for example, evaporation). As shown in FIGS. 1 and 2, the coolant chamber 10 is preferably formed in a cylindrical shape. A coolant inlet 11 is formed in a lower portion of the coolant chamber 10. A coolant outlet 12 is formed in an upper portion of the same.
A low temperature coolant is flown into the [0039] coolant inlet 11 and is vaporized (phase-change) and absorbs a heat from the surrounding portions and discharges through the coolant outlet 12. The coolant inlet 11 is formed in the lower portion of the coolant outlet 12 for the reasons that the time required in order for the coolant to stay in the coolant chamber 10 is extended for thereby extending the heat exchange time.
[0040] Heat transfer tubes 20 are installed in the interior of the coolant chamber 10. An upper chamber 2 is installed in the upper portion of the coolant chamber 10 for flowing a process fluid into the heat transfer tube 20. A lower chamber 3 is installed in the lower portion of the coolant chamber 10 for gathering the ice slurry of the process fluid therein. The ice slurry of the process fluid gathered in the lower chamber 3 is flown into the heat accumulator (not shown).
The [0041] heat transfer tubes 20 are installed over the upper plate 13 and the lower plate 14 transversely to the coolant chamber 10 and are surrounded by the coolant chamber 10. The heat transfer tube 20 is formed of a material (for example, cooper tube) having a high heat transfer ratio. As shown in FIG. 7, the curved portions formed in the outer wall of the heat transfer tube 20 are directed to increasing the contact surface with the coolant for thereby enhancing heat transfer efficiency.
The process fluid is flown through the upper portion of the [0042] heat transfer tube 20 and is flown along the heat transfer tube 20 and is flown through the lower portion of the heat transfer tube 20. In the above flowing operation, the process fluid is heat-exchanged with the coolant of the coolant chamber 10 which surrounds the heat transfer tubes 20. The cooled process fluid is flown to the heat transfer tubes 20 in an ice slurry shape. The above ice slurry is flown to the heat accumulator for thereby being used for implementing a cooling operation.
The [0043] upper chamber 2 may be installed on the upper plate 13 of the coolant chamber 10. The upper chamber 2 may be formed of a transparent acryl cylindrical shell 4 and top plate 5 in order for the interior of the same to be seen from the outside. The upper chamber 2 is installed on the upper plate 13 over the top plate 5 and the upper plate 13 using a plurality of engaging bolts 6. A packing 2 a is inserted into the portions between the shell 4 and the upper plate 13, and the shell 4 and the top plate 5. A process fluid supply port 7 is formed in the top plate 5 for supplying the process fluid to the upper chamber 2 and is engaged with a process fluid supply tube 8.
The [0044] lower chamber 3 may be flange-connected with the lower plate 14 of the coolant chamber 10. A discharging port 9 is formed in a lower portion of the lower chamber 3. The ice slurry of the process fluid is discharged through the discharging port 9. The lower surface of the lower chamber 3 is inclined in the direction of the discharging port 9 in order for the ice slurry to be easily discharged.
As shown in FIG. 2, only one [0045] heat transfer tube 20 is installed in the coolant chamber 10. In a preferred embodiment of the present invention, as shown in FIG. 1, in the coolant chambers 10, more than a few tens or more than one hundred of the heat transfer tubes 20 may be installed.
The [0046] vibration member 30 is inserted into each heat transfer tube 20. As the vibration member 30 adapted to the present invention, any type of the vibration member 30 which is capable of repeatedly impacting an inner wall of the heat transfer tube 20 when vibrated by the vibration unit 40 for thereby separating and breaking the process fluid frozen on the inner wall of the heat transfer tube 20 and downwardly flowing the same may be adapted in the present invention.
Preferably, the [0047] vibration member 30 includes a certain length for thereby crossing the entire length of the heat transfer tube 20. In addition, the outer surface of the vibration member 30 is not closely contacted with the inner wall of the heat transfer tube 20 and has a certain diameter capable of impacting the inner wall of the heat transfer tube 20 when vibrated by the vibration unit 40.
As shown in FIGS. 1, 2 [0048] 7 and 8, as the vibration member 30, a screw shaped vibration member 30A may be adapted. Here, the screw shaped vibration member 30A is formed in a helical or spiral structure formed by winding a certain lineal material in a screw shape like a common coil spring and has a hollow inner portion, so that the process fluid freely moves between the inner side and the outer side through the spaces formed between the spirally shaped lines. Namely, the screw type vibration member 30A is formed in the shape of the coil spring but is not basically directed to providing an elastic force. Therefore, the screw type vibration member 30A is preferably directed to having a helical structure from which an elastic function (upper and lower displacements of spiral lines) that is an inherent characteristic of the common spring is removed.
Preferably, the outer surface of the screw shaped [0049] vibration member 30A has a certain contour corresponding to the contour of the inner wall of the heat transfer tube 20, so that it is possible to enhance the efficiency for separating the frozen coats of the process fluid when impacting the inner wall of the heat transfer tube 20. In addition, the outer surfaces of the screw shaped vibration member 30A may be formed in a protruded shape for implementing an effective impact operation with respect to the inner wall of the heat transfer tube 20.
As the screw shaped [0050] vibration member 30A is vibrated by the vibration unit 40, the frozen coat of the process fluid formed on the inner wall of the heat transfer tube 20 is separated and broken by the repeating impacts of the screw shaped vibration member and is downwardly flown. At this time, the screw shaped structure of the screw shaped vibration member 30A helps a smooth flowing down operation of the ice slurry of the process fluid.
As shown in FIG. 3, as the [0051] vibration member 30, a spring type vibration member 30B, a screw shaped wing type vibration member 30C, a circular plate wing type vibration member 3D, or an upper and lower wing type vibration member 30E may be adapted.
In the spring [0052] type vibration member 30B of FIG. 3A, a common coil spring is adapted to the vibration member 30. There is not any difference with respect to the screw shaped vibration member 30A in their outer appearance. As a difference between the screw shaped vibration member 30A and the spring type vibration member 30B, the former is directed to removing the elastic characteristic in its upper and lower portions in maximum, and the later is directed not to removing the upper and lower elastic characteristics using a common spring. Therefore, when the spring type vibration member 30B is vibrated by the vibration unit 40, the vibration may occur in the upward and downward directions based on its elastic characteristic.
The screw shaped wing [0053] type vibration member 30C of FIG. 3B is a vibration member 30 which is formed by protruding a screw shaped wing 32 from a surrounding portion of the rod 31. The screw shaped vibration member 30C is formed of a rod 31 in the center of the same, not being hollow compared to the screw shaped vibration member 30A.
The circular plate wing shaped [0054] vibration member 30D of FIG. 3C is a vibration member 30 which is formed by protruding a circular plate shaped wing 34 at a certain distance from an outer surrounding portion of the rod 33 and does not have a screw shaped wing compared to the screw shaped wing type vibration member 30C, namely, it is formed in a horizontal circular plate. The circular plate wing 34 is formed in a trapezoid in which the upper portion of the same is wider and the lower portion is narrow for effectively guiding the flow of the process fluid in the direction of the heat transfer tube 20.
The upper and lower wing shaped [0055] vibration member 30E of FIG. 3D is a vibration member 30 which is formed by protruding upper and lower direction wings 36 from an outer surrounding portion of the rod 35. The wings 36 are formed transversely with respect to the length of the rod 35 in the upper and lower directions.
As described above, the [0056] vibration member 30 is vibrated by the vibration unit 40. As the vibration unit 40 adapted to the present invention, the vibration unit 40 is not limited to its type if the vibration member 30 is vibrated in order for the vibration member 30 to impact the inner wall of the heat transfer tube 20 repeatedly.
Preferably, the [0057] vibration unit 40 may include a vibration motor 41 installed in the upper portion of the upper chamber 2, vibration transfer rods 42 connected with the vibration motor 41 and transferring a vibration therethrough, and a vibration plate 43 connected between the vibration transfer rods 42 and the vibration members 30 for transferring the vibration of the vibration transfer rods 42 to the vibration members 30. Preferably, an anti-vibration unit 44 (for example, an anti-vibration spring) may be included for preventing the vibration of the vibration motor 41 from being transferred to other elements except for the vibration member 30.
The [0058] vibration motor 41 is installed on a motor base 41 a, and an upper portion of each vibration transfer rod 42 (for example, four rods) is engaged to the motor base 41 a. The vibration transfer rod 42 passes through the top plate 5 and has a lower end engaged to the vibration plate 43 for preventing a vibration from being transferred to the top plate 5. In the drawings, reference numeral 45 represents a flexible cover for covering the vibration transfer rod which is exposed to the outside.
The [0059] vibration plate 43 is constructed in such a manner that the process fluid is smoothly flown into the upper chamber 2 at the minimum resistance, so that the process fluid is uniformly distributed with respect to the multiple heat transfer tubes 20.
As shown in FIGS. 1, 2 and [0060] 4, the vibration plate 43 is formed in a circular plate having a certain size which is received in the upper chamber 2. In the vibration plate 43, heat transfer tube engaging holes 43 a are made by the number corresponding to the number of the heat transfer tubes 20. The vibration member 30 is engaged to the heat transfer tube engaging hole 43 a.
The [0061] vibration member 30 may be directly engaged to the heat transfer tube engaging hole 43 a, but is engaged thereto using the connection sleeve 50. As shown in FIGS. 5, 7 and 8, the connection sleeve 50 may be implemented by forming a vibration member engaging protrusion 52 in a lower portion of the body 51 and forming the vibration plate engaging shoulder portion 53 in the upper portion. The connection sleeve 50 is engaged between the vibration plate 43 and the heat transfer tube 20. At this time, the vibration member 30 is engaged to the vibration member engaging protrusion 52. The vibration plate engaging shoulder portion 53 is laid over the heat transfer tube engaging hole 43 a formed in the vibration plate 43.
The [0062] body 51 of the connection sleeve 50 is formed in a cylindrical shape having a certain outer contour corresponding to an inner contour of the heat transfer tube 20. The diameter of the body 51 is determined based on the condition that a certain gap is formed in order for the process fluid to flow between the inner walls of the surrounding heat transfer tube 20. The process fluid flown into the body 51 is discharged through the discharging holes 54 (preferable, four holes) formed in the lower surrounding portion.
As the [0063] vibration member 30, in the case that the screw shaped vibration member 30A and the spring type vibration member 30B are adapted, the vibration members 30A and 30B may be screw-engaged to the vibration member engaging protrusion 52. In addition, in the case that the screw shaped wing vibration member 30C, the circular plate wing shaped vibration member 30D or the upper and lower wing type vibration member 30E is adapted as the vibration member, the above vibration member may be screw-engaged by engaging the male screws 31 a, 33 a and 35 a to the female screws (not shown) of the connection sleeve 50.
Even when the screw shaped [0064] vibration member 30A is designed not to have any elastic characteristic, the screw shaped vibration member 30A may be elastically contracted due to its inherent characteristic of the spring. The elasticity of the screw shaped vibration member 30A may interfere with an effective discharge of the ice slurry by narrowing the distances between the spiral lines by increasing the winding number at the lower portion of the vibration member 30. Therefore, a certain amount of lump of the ice slurry of the process fluid may be accumulated in the lower portion of the heat transfer tube 20 for thereby preventing an efficient discharge of the ice slurry.
Therefore, it is preferably prevent the elasticity of the screw shaped [0065] vibration member 30A by fixedly inserting the reinforcing bolt 37 into the screw shaped vibration member 30A. In the case of the spring type vibration member 30B, the reinforcing bolt 36 may be adapted in the same manner.
As shown in FIGS. 2 and 7 and [0066] 8, the reinforcing bolt 37 is inserted into the bolt hole 55 formed in the connection sleeve 50, and the lower portion of the reinforcing bolt 37 is fixed to the lower end of the screw shaped vibration member 30A by the maintaining member 60.
Therefore, the elastic movement of the screw shaped [0067] vibration member 30A is prevented by the reinforcing bolt 30 in such a manner that the reinforcing bolt 37 is inserted into the bolt hole 55, the lower end of the reinforcing bolt 37 is inserted into the bolt hole 61 of the maintaining member 60, and the lower end of the screw shaped vibration member 30A is engaged to the threaded portion of the maintaining member 60 and is engaged using the nut 38.
As shown in FIG. 2, a [0068] water prevention plate 39 formed in a conical shaped in which an upper portion is narrower and a lower portion is wider, may be engaged to the reinforcing bolt 37. When the water prevention plate 39 is provided, it is possible to delay the flowing speed of the process fluid by providing a certain resistance thereto. In addition, the flow of the process fluid may be guided in the direction of the heat transfer tube 20 by the water prevention plate 39 for thereby enhancing a heat transfer efficiency.
A certain film formed of a non-adhesive material may be coated on an inner wall of the [0069] heat transfer tube 20 adapted in the heat exchanger 1 according to the present invention for thereby minimizing the attachment of the frozen process fluid. As a preferred non-adhesive material used for forming the above film, a fluorine resin (PTFE: polytetrafluoroethylene, FEP: fluoridated ethylene propylene copolymer) is commercially available by the trademark name of Teflon™ by the Dupon company. The above fluorine resin may be coated by coating and molding on an inner wall of the heat transfer tube 20 for thereby having a certain durability. Therefore, the freezing phenomenon of the process fluid on the heat transfer tube 20 may be minimized based on the coat formation of the non-adhesive material. The frozen process fluid is continuously removed in the above-described manner.
The operation of the [0070] heat exchanger 1 according to the present invention will be described with reference to the accompanying drawings.
The coolant is flown into the [0071] coolant inlet 11 and is discharged to the coolant outlet 12 through the coolant chamber 10. In the above operation, the coolant is vaporized and the heat is absorbed from the heat transfer tube 20.
The process fluid is flown into the [0072] upper chamber 2 through the process fluid supply tube 8 and is flown into the connection sleeves 50 through the heat transfer tube engaging holes 43 a and is downwardly flown through the gap 43 b formed in the surrounding portions of the vibration plate 43. Continuously, the coolant is flown into the heat transfer tubes 20 through the discharge holes 54 and the gap formed between the connection sleeve 50 and the heat transfer tube 20.
The process fluid flown into the [0073] heat transfer tubes 20 is downwardly flown and is gradually cooled for thereby forming the ice slurry of the process fluid, and a part of the process fluid is frozen on the inner wall of the heat transfer tubes 20 for thereby forming a coat.
The frozen coat of the process fluid formed in the inner wall of the [0074] heat transfer tubes 20 is continuously impacted by the vibration members 30 which are vibrated by the vibration unit 40, so that the frozen coat is separated from the heat transfer tubes 20 and is broken for thereby being downwardly flown.
Therefore, since the frozen coats of the process fluid attached on the [0075] heat transfer tube 20 are continuously removed for thereby preventing a heat transfer efficiency decrease due to the frozen coat.
The ice slurry of the process fluid which is discharged from the [0076] heat transfer tubes 20 and is gathered in the lower chamber 3 is moved to the heat accumulator through the discharging port 9 and is used for implementing a cooling operation.
As described above, in the vibration [0077] type heat exchanger 1 according to the present invention, the frozen coat of the process fluid formed on the inner wall of the heat transfer tube 20 is effectively separated and broken into small particles by the vibration impact of the vibration member 30, so that it is possible to minimize the decrease of the heat transfer efficiency of the heat transfer tube 20 due to the frozen coat of the process fluid. In addition, the lump type ice slurry is removed from the ice slurry of the finally produced process fluid for thereby enhancing the quality of the ice slurry.
As the present invention may be embodied in several forms without departing from the spirit or essential characteristics thereof, it should also be understood that the above-described examples are not limited by any of the details of the foregoing description, unless otherwise specified, but rather should be construed broadly within its spirit and scope as defined in the appended claims, and therefore all changes and modifications that fall within the meets and bounds of the claims, or equivalences of such meets and bounds are therefore intended to be embraced by the appended claims. [0078]

Claims

What is claimed is:

1. In a heat exchanger in which a ice slurry is produced based on a heat exchange between a coolant and a process fluid, a vibration type heat exchanger, comprising:

a coolant chamber through which said coolant flows;

more than one heat transfer tube through which said process fluid flows in a state surrounded by said coolant chamber in order for said coolant to absorb a heat;

a vibration member being inserted along each said heat transfer tube and being vibrated for thereby separating a frozen coat of said process fluid formed in an inner wall of said heat transfer tube; and

a vibration means for vibrating said vibration member.

2. A vibration type heat exchanger according to claim 1, wherein said vibration member is selected from the group comprising:

a screw shaped vibration member in which there is the minimum displacement in an upward and downward direction due to an externally applied force, a spring type vibration member having elasticity in an upward and downward direction, a screw shaped wing type vibration member in which a screw shaped wing is formed in an outer circumferential portion of a rod, a circular plate wing type vibration member in which a circular plate type wing is formed in an outer circumferential surface of a rod, and an upper and lower wing type vibration member in which an upper and lower wing is attached in an upward and downward direction of a rod.

3. A vibration type heat exchanger according to claim 1 or claim 2, wherein said vibration means includes:

a vibration motor;

a plurality of vibration transfer rods connected with said vibration motor for transferring a vibration; and

a vibration plate transferring a vibration of said vibration transfer rods to said vibration member.

4. A vibration type heat exchanger according to claim 1 or claim 2, said vibration member is connected to said vibration member by interposing a connection sleeve engaged to an upper portion of said heat transfer tube.

5. A vibration type heat exchanger according to claim 2, wherein a reinforcing bolt is installed in the interiors of said screw shaped vibration member and said spring type vibration member for thereby decreasing extension and contraction of said vibration member.

6. A vibration type heat exchanger according to claim 5, wherein said reinforcing bolt includes at least one water prevention plate.

7. A vibration type heat exchanger according to claim 1 or claim 2, wherein a non-adhesive film is coated in an inner wall of said heat transfer tube for minimizing a freezing operation of said ice slurry of the process fluid.