CN111141162A - Shell and tube heat exchanger - Google Patents
Shell and tube heat exchanger Download PDFInfo
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- CN111141162A CN111141162A CN201811311617.XA CN201811311617A CN111141162A CN 111141162 A CN111141162 A CN 111141162A CN 201811311617 A CN201811311617 A CN 201811311617A CN 111141162 A CN111141162 A CN 111141162A
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- Prior art keywords
- tube
- heat exchange
- shell
- heat exchanger
- vortex generator
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
- F28D7/1607—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation with particular pattern of flow of the heat exchange media, e.g. change of flow direction
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/24—Arrangements for promoting turbulent flow of heat-exchange media, e.g. by plates
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fluid Mechanics (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
The invention relates to a shell-and-tube heat exchanger, which comprises a shell, a heat exchange tube and a vortex generator, wherein the two ends of the heat exchange tube are fixedly distributed in the shell through a first tube plate and a second tube plate respectively, the vortex generator is arranged at the inlet end of the heat exchange tube, and the vortex generator comprises an intermediate body and spiral blades wound on the periphery of the intermediate body. The invention has simple structure, no movable parts inside, can effectively improve the performance of the heat exchanger, improve the uniformity of the internal flow of the heat exchange tube, shorten the length of the heat exchange tube and the size of the evaporator and reduce the production cost.
Description
Technical Field
The invention relates to the technical field of heat exchange equipment, in particular to a shell-and-tube heat exchanger.
Background
In the current industrial production, heat exchangers are widely applied to heat exchange systems, wherein a dry-type shell-and-tube evaporator belongs to one type of heat exchangers, a dry-type shell-and-tube evaporation heat exchanger utilizes liquid refrigerant to be evaporated and boiled in a heat exchange tube under low pressure to be converted into steam, and absorbs heat from a cooling medium between the periphery of the heat exchange tube and a shell in the process of converting liquid into gas so as to achieve the purpose of refrigeration, and the dry-type shell-and-tube evaporation heat exchanger is widely applied to modern air conditioners and refrigeration systems. Because the flow distribution of the liquid refrigerant inside the heat exchange tube is uneven and the fluid boundary layer of the inner wall of the heat exchange tube is thick, the flow velocity of the liquid refrigerant inside the heat exchange tube is low, and the heat exchange efficiency of the heat exchanger is seriously influenced. In order to improve the heat transfer rate, the length of the heat exchange tube can be increased, but the problems of increased volume of the heat exchanger, high production cost, inconvenience in transportation and installation and the like can be caused.
Disclosure of Invention
Based on this, it is necessary to provide a shell-and-tube heat exchanger aiming at the problem of low heat exchange efficiency in the shell-and-tube heat exchanger, which includes a shell, a heat exchange tube with two ends respectively fixed inside the shell through a first tube plate and a second tube plate, and a vortex generator installed at the inlet end of the heat exchange tube, where the vortex generator includes an intermediate body and a helical blade wound around the periphery of the intermediate body.
In one embodiment, the shell comprises a cylinder body, and a first end cover and a second end cover which are respectively arranged at two ends of the cylinder body, the first tube plate and the second tube plate are respectively fixed at two ends of the cylinder body to arrange the heat exchange tube inside the cylinder body, the first end cover is provided with a refrigerant inlet, and an inlet end of the heat exchange tube is communicated with the refrigerant inlet.
In one embodiment, the vortex generators are arranged coaxially with the corresponding heat exchange tubes.
In one embodiment, the inflow side of the vortex generators is mounted on the first tube sheet, and at least a portion of the vortex generators extend into the corresponding heat exchange tubes.
In one embodiment, the spiral blade is provided with a positioning boss at the inflow side of the vortex generator, and the first tube plate is provided with a positioning groove matched with the positioning boss.
In one embodiment, the shell-and-tube heat exchanger further comprises a baffle plate arranged between the first tube plate and the first end cover and used for tightly pressing the vortex generator on the first tube plate, and the baffle plate is provided with an avoiding hole corresponding to the inflow side of the vortex generator.
In one embodiment, a seal is provided between the baffle and the tubesheet to compress the vortex generator against the first tubesheet.
In one embodiment, the shell and tube heat exchanger further comprises a baffle plate arranged on the periphery of the heat exchange tube, a pull rod assembly for fixing the baffle plate is arranged between the baffle plate and the second tube plate, and the pull rod assembly comprises:
the supporting rods sequentially penetrate through the baffle plate, the first tube plate, the baffle plate and the second tube plate;
and the adjusting nuts are arranged at the two opposite ends of the supporting rod and respectively attached to the corresponding sides of the baffle and the second tube plate.
In one embodiment, the number of the helical blades is at least two, and each helical blade and the inner wall of the heat exchange tube form a plurality of refrigerant channels.
In one embodiment, the helical blade radius tapers from the inflow side to the outflow side of the spinning vortex generator.
In one embodiment, the intermediate comprises:
the spiral blades are distributed on the periphery of the body;
a ball head at one end of the body and facing the inflow side;
and the tail cone is positioned at the other end of the body and faces to the outflow side.
In one embodiment, the ball head is hemispherical.
The shell and tube heat exchanger provided by the invention has the advantages that the structure is simple, no movable part is arranged in the shell and tube heat exchanger, the performance of the heat exchanger can be effectively improved, the uniformity of the flow in the heat exchange tube is improved, the length of the heat exchange tube and the size of an evaporator are shortened, and the production cost is reduced.
Drawings
Fig. 1 is a schematic structural view of a shell-and-tube heat exchanger according to an embodiment of the present invention.
Fig. 2 is a partially enlarged schematic view of a portion a in fig. 1.
Fig. 3 is a partially enlarged schematic view of a portion B in fig. 1.
Fig. 4 is a schematic view of a partial installation of the vortex generator and shell and tube heat exchanger of fig. 1.
Fig. 5 is a schematic perspective view of the vortex generator of fig. 1.
Fig. 6 is a left side view of fig. 5.
Fig. 7 is a front view of fig. 5.
Fig. 8 is a schematic cross-sectional view of fig. 5.
Description of the main elements
The following detailed description will further illustrate the invention in conjunction with the accompanying drawings.
Detailed Description
The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and 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.
It will be understood that when an element is referred to as being "mounted on" another element, it can be directly on the other element or intervening elements may also be present. When a component is referred to as being "disposed on" another component, it can be directly on the other component or intervening components may also be present. When an element is referred to as being "secured to" another element, it can be directly secured to the other element or intervening elements may also be present.
Unless defined otherwise, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this invention belongs. The terminology used in the description of the invention herein is for the purpose of describing particular embodiments only and is not intended to be limiting of the invention. As used herein, the term "or/and" includes any and all combinations of one or more of the associated listed items.
Referring to fig. 1 to 8 together, an embodiment of the present invention provides a shell-and-tube heat exchanger, including a shell 1, a heat exchange tube 10 having two ends respectively fixed inside the shell 1 through a first tube plate 2 and a second tube plate 3, and a vortex generator 4 installed at an inlet end 101 of the heat exchange tube 10, where the vortex generator 4 includes a middle body 41 and a helical blade 42 wound around the periphery of the middle body 41.
The fluids for heat exchange in the shell-and-tube heat exchanger include two fluids, one fluid flowing in the heat exchange tube 10 (taking a refrigerant as an example) is called tube-side fluid; the other flows outside the heat exchange tubes 10 (taking water as an example) and is called shell-side fluid. Accordingly, the area through which water passes outside the heat exchange tube 10 is referred to as a shell side, and the area through which refrigerant passes inside the heat exchange tube 10 is referred to as a tube side. The area outside the heat exchange tube 10 is a sealed space formed by the tube plate, the shell 1 and the heat exchange tube 10, and the tube plate comprises a first tube plate 2 and a second tube plate 3.
The both sides of the shell 1 are respectively provided with a water inlet and a water outlet, and in the heat exchange process, the flow direction of water is as follows: water inlet-shell pass-water outlet, and water exchanges heat with refrigerant in the tube pass through the heat exchange tube 10 when passing through the shell pass. The refrigerant in the heat exchange tube 10 exchanges heat with the water outside the heat exchange tube 10 in the process of flowing into the heat exchange tube 10 from the inlet end 101.
Specifically, the water inlet and the water outlet may be connected to a pipeline communicated with the housing 1 to facilitate inflow and outflow of water, and correspond to the water inlet pipe 17 and the water outlet pipe 18, respectively, and are correspondingly welded to the barrel 11.
In one embodiment, the housing 1 includes a cylinder 11, and a first end cover 12 and a second end cover 13 respectively disposed at two ends of the cylinder 11, the first tube plate 2 and the second tube plate 3 are respectively fixed at two ends of the cylinder 11 to dispose the heat exchange tube 10 inside the cylinder 11, the first end cover 12 is provided with a refrigerant inlet, and the inlet end 101 of the heat exchange tube 10 is communicated with the refrigerant inlet. Specifically, the first tube plate 2 and the second tube plate 3 are respectively provided with a positioning hole 22 for fixing the heat exchange tube 10, the positioning hole 22 penetrates through the tube plate in the thickness direction, the heat exchange tube 10 is inserted and fixed on the positioning hole 22, and the diameter of the positioning hole 22 is consistent with that of the outer wall of the heat exchange tube 10. The first tube plate 2 and the second tube plate 3 are fixedly connected with the cylinder 11, so that the heat exchange tube 10 is fixed inside the cylinder 11.
In order to facilitate the formation of the pressure difference, end caps are respectively disposed at both ends of the cylinder 11, a refrigerant space is formed at the inlet end 101 of the heat exchange tube 10 near the first end cap 12 for the convenience of storing the refrigerant, and correspondingly, the second end cap 13 is provided with a refrigerant outlet. The flowing process of the refrigerant in the shell 1 is as follows: the refrigerant inlet of the first end cap 12, the refrigerant space, the inlet end 101 of the heat exchange tube 10, the outlet end of the heat exchange tube 10, and the refrigerant outlet of the second end cap 13.
Specifically, each tube plate is arranged at the corresponding end of the cylinder 11, the end face of the tube plate is flush with the end face of the cylinder 11, a first refrigerant space is formed between the first end cover 12 and the first tube plate 2, a refrigerant is conveyed to the first refrigerant space through a refrigerant inlet arranged on the first end cover 12, a second refrigerant space is formed between the second end cover 13 and the second tube plate 3, and the second end cover 13 is provided with a refrigerant outlet. Wherein, in order to raise the efficiency, coolant entry and coolant export can set up a plurality ofly.
To facilitate the inflow and outflow of the refrigerant, the refrigerant inlet and outlet are connected to the refrigerant inlet pipe 121 and the refrigerant outlet pipe 131, and may be connected to the end cap in a welded manner.
It can be understood that each end cover and the cylinder 11 are fixedly connected, and can be integrated or separated. When the split type air-conditioner is split, the barrel body 11 is fixedly connected with the tube plate, and then is fixedly connected with the end cover through the tube plate, so that the end cover is fixedly connected with the barrel body 11. Wherein, the tube plate and the end cover can be fixedly connected by bolts 14. Alternatively, the end cap may be fixedly attached directly to the barrel 11.
Specifically, in order to facilitate the fixing of the bolt 14, the end cover is provided with a flanging arranged along the circumferential direction towards the end of the barrel 11, correspondingly, the tube plate is also provided with a flanging arranged along the circumferential direction towards the end cover, and the bolt 14 is used for attaching and fixing the end cover and the tube plate through the flanging. Furthermore, in order to enhance the sealing effect, a sealing ring is arranged at the joint of the end cover and the tube plate.
As shown in fig. 4, in one embodiment, in order to increase the heat exchange speed, a vortex generator 4 is installed at the inlet end 101 of the heat exchange tube 10, that is, the vortex generator 4 is installed at the inlet end 101 of the heat exchange tube 10 near the refrigerant inlet. The refrigerant enters the heat exchange tube 10 through the vortex generator 4, the flow rate of the refrigerant is accelerated, and the refrigerant is uniformly distributed to flow into the heat exchange tube 10, so that the heat exchange rate is improved. It should be noted that the refrigerant is prevented from evaporating because the refrigerant is subjected to the flow-resisting action of the vortex generators 4 before entering the inlet end 101 of the heat exchange tube 10, so that the refrigerant left in the front of the inlet end 101 of the heat exchange tube 10 exists in a liquid state. When the refrigerant as a liquid fluid flows into the heat exchange tube 10 through the vortex generator 4, the flow cross-sectional area is reduced, the pressure difference variation range between the inflow side and the outflow side of the vortex generator 4 is relatively large, and the evaporation speed of the liquid refrigerant in the heat exchange tube 10 is increased.
Further, the vortex generator 4 is coaxially arranged with the heat exchange tube 10, and the axis of the heat exchange tube 10 coincides with the axis of the vortex generator 4.
The vortex generator 4 includes a central body 41 and a helical blade 42 wound around the periphery of the central body 41, and the helical blade 42 is wound around the outer wall of the central body 41. The refrigerant flows in from the inflow side of the vortex generator 4, the pressure difference of the refrigerant between the periphery of the vortex generator 4 and the inner wall of the heat exchange tube 10 in the radial direction of the heat exchange tube 10 is basically kept consistent, the uniformity of the fluid flowing into the heat exchange tube 10 is improved, the refrigerant is forced to rotate around the intermediate body 41 violently along the spiral direction of the spiral blade 42 to form spiral precession flow, so that the fluid boundary layer on the inner wall surface of the heat exchange tube 10 is disturbed, and the wall surface heat exchange coefficient is enhanced.
As shown in fig. 5 to 8, in one embodiment, the spiral blades 42 are at least two, and each spiral blade 42 and the inner wall of the heat exchange tube 10 form a plurality of refrigerant channels 9. In the process that the refrigerant flows into the heat exchange tube 10 from the first refrigerant space, the refrigerant is divided into a plurality of strands of fluid under the action of the helical blades 42 of the vortex generator 4, and the fluid flows into the heat exchange tube 10 along each refrigerant channel 9, so that the disturbance of a fluid boundary layer on the inner wall surface of the heat pipe is enhanced, and the heat exchange rate is improved. Specifically, the number of the helical blades 42 and the rotation angle of each helical blade 42 can be adjusted according to requirements, for example, the number of the helical blades 42 can be 3-9.
In one embodiment, to accelerate the flow of the refrigerant into the heat exchange tube 10 through the vortex generator 4, the radius of the spiral blade 42 is gradually reduced from the inflow side to the outflow side of the vortex generator 4.
In one embodiment, the intermediate body 41 includes: a cylindrical body 411, wherein the helical blades 42 are distributed on the periphery of the body 411; a ball 412 at one end of the body 411 and facing the inflow side; a tail cone 413 at the other end of the body 411 facing the outflow side. The refrigerant at the inlet end 101 flows into the heat exchange tube 10 through the bulb 412, the helical blades 42 and the tail cone 413.
The cylindrical body 411 serves as a bearing body of the helical blade 42, so that the helical blade 42 is convenient to mount and support the helical blade 42, and the stability of the vortex generator 4 under the force of the refrigerant flow is improved. Specifically, the diameter d of the cylindrical body 411 is 1/4-1/2 of the diameter of the positioning hole 22 of the tube plate, and the cylindrical body 411 and the heat exchange tube 10 are arranged coaxially, so that the cold vortex generator 4 can be conveniently installed.
The bulb 412 disposed at one end of the main body 411 and facing the inflow side is used to improve the uniformity of flow distribution among the helical blades 42, and the spherical surface can better disperse the refrigerant flowing from the first refrigerant space into the inlet end 101 of the heat exchange tube 10. Further, when the plurality of spiral blades 42 form the refrigerant multiple channels, the bulb 412 helps to uniformly distribute the refrigerant flowing into the refrigerant channels 9. The contact surface between the ball 412 and the cylindrical body 411 is the largest area of each section. Further, the ball head 412 is hemispherical.
A tail cone 413 at the other end of the body 411, facing the outflow side, contributes to increasing the flow velocity of the precession flow formed by the helical blade 42, the tail cone 413 being arranged coaxially with the cylindrical body 411.
In order to increase the heat exchange rate, a plurality of refrigerant outlets and refrigerant inlets may be provided, and a plurality of heat exchange tubes 10 may be provided in the cylinder 11, and the vortex generators 4 are respectively installed at the inlet ends 101 of some of the heat exchange tubes 10, or the vortex generators 4 are installed at the inlet ends 101 of all the heat exchange tubes 10.
In one embodiment, in order to realize the shunting function of the vortex generators 4 on the refrigerant flowing into the heat exchange tubes 10 and to form a pressure difference to accelerate the evaporation of the refrigerant, at least one part of each vortex generator 4 extends into the corresponding heat exchange tube 10, and in order to realize the positioning installation of the vortex generator 4, the inflow side of each vortex generator 4 is installed on the first tube plate 2. It is understood that, as an alternative, the vortex generator 4 may also extend entirely into the heat exchange tube 10, the vortex generator 4 being positioned in fixed connection with the heat exchange tube 10.
In one embodiment, in order to position the vortex generator 4 in the heat exchange tube 10, the spiral blade 42 extends radially outward on the inflow side of the vortex generator 4 to form a positioning boss 421, and the first tube plate 2 is provided with a positioning groove 21 matching with the positioning boss 421. The vortex generator 4 is positioned and fixed on the first tube plate 2 by the matching of the positioning boss 421 and the positioning groove 21. When the spiral blades 42 are multiple, each spiral blade 42 is provided with a positioning boss 421, and all the positioning bosses 421 are uniformly distributed around the axis of the intermediate body 41.
In one embodiment, in order to stably install the vortex generator 4 in the heat exchange tube 10, the shell-and-tube heat exchanger further includes a baffle 5 disposed between the first tube plate 2 and the first end cap 12 to press the vortex generator 4 against the first tube plate 2, wherein the baffle 5 is provided with an avoiding hole 51 corresponding to the inflow side of the vortex generator 4.
The edge of the avoidance hole 51 is tightly pressed on the positioning boss 421 of the helical blade 42, the baffle 5 and the first tube plate 2 are clamped with each other to fasten the positioning boss 421 on the positioning groove 21, and the vortex generator 4 is fixed on the tube plate through the vortex generator 4, so that the vortex generator 4 is fixed on the first tube plate 2, and the part of the vortex generator 4 extends into the heat exchange tube 10.
Specifically, the diameter of the avoiding hole 51 of the baffle 5 is consistent with the outer diameter of the heat exchange tube 10, so that the refrigerant in the first refrigerant space can conveniently enter the heat exchange tube 10 through the avoiding hole 51. The heat exchange tube 10 is inserted and fixed in a positioning hole 22 in the tube plate, and the end part of the heat exchange tube 10 is positioned in the middle of the positioning hole 22 in the depth direction. The refrigerant enters the heat exchange tube 10 from the first refrigerant space and sequentially passes through: relief hole 51-positioning hole 22-heat exchange tube 10.
For enhancing the sealing performance, the baffle 5 and the tube plate are provided with a sealing member 6, and the sealing member 6 abuts against the positioning boss 421 adjacent to the vortex generator 4. The force exerted on the sealing element 6 by the clamping force between the baffle 5 and the first tube sheet 2, and the sealing element 6 and the first tube sheet 2 are clamped to each other to fix the vortex generator 4. The sealing member 6 may be a sealing ring. The baffle 5 compresses the vortex generator 4 through the sealing ring to prevent the vortex generator 4 from moving.
In one embodiment, as shown in fig. 1, to enhance the heat exchange effect, the shell and tube heat exchanger further includes a baffle plate 7 disposed at the periphery of the heat exchange tube 10, and a tie rod assembly for fixing the baffle plate 7 is disposed between the baffle plate 5 and the second tube plate 3, and the tie rod assembly includes:
the supporting rod 81 sequentially penetrates through the baffle 5, the first tube plate 2, the baffle plate 7 and the second tube plate 3;
and the adjusting nuts 82 are arranged at two opposite ends of the supporting rod 81 and are respectively abutted against the corresponding sides of the baffle plate 5 and the second tube plate 3.
It can be understood that the baffles 7 arranged on the periphery of the heat exchange tube 10 can increase turbulence and strengthen the flow path in the shell pass; the heat exchange effect is improved, and meanwhile, the baffle plate 7 plays a role in supporting and positioning the heat exchange pipe 10.
In order to strengthen and fix the position of the baffle plate 7, two ends of a support rod 81 penetrating through the baffle plate 7 are respectively fixed on the baffle plate 5 and the second tube plate 3 so as to fix the position of the baffle plate 7. The two ends of the supporting rod 81 are oppositely provided with a fixed connection mode of an adjusting nut 82. Specifically, the support rod 81 is located at the central axis of the barrel 11, which contributes to the installation stability of the shell-and-tube heat exchanger. Wherein, the baffle plate 7 can be provided in plurality.
According to the embodiment provided by the invention, the heat exchange tube 10 penetrates through the baffle plate 7, is arranged in the cylinder body 11, and is connected with the first tube plate 2 and the second tube plate 3 by using a tube expansion technology, wherein the cylinder body 11 is respectively welded with the second tube plate 3 and the first tube plate 2. The vortex generator 4 is arranged in the positioning hole 22 of the first tube plate 2, the positioning boss 421 of the vortex generator 4 is clamped in the positioning groove 21 of the first tube plate 2, and the inflow side of the vortex generator 4 faces the refrigerant inlet end. The pull rod assembly sequentially penetrates through the baffle 5, the sealing piece 6, the first tube plate 2, the baffle plate 7 and the second tube plate 3 from left to right, and plays a role in supporting the shell-and-tube heat exchanger.
As shown in fig. 2, the joint of the first end cap 12 and the first tube plate 2 sequentially includes the first tube plate 2, the sealing member 6, the baffle plate 5, the sealing ring 15, and the first end cap 12 from right to left, and the first tube plate 2 and the first end cap 12 are fastened by the bolt 14, wherein the size of the opening of the sealing member 6 is consistent with the avoiding hole 51 on the baffle plate 5 and the positioning hole 22 on the first tube plate 2, and the baffle plate 5 is pressed on the positioning boss 421 of the vortex generator 4 through the sealing member 6 to prevent the vortex generator from moving.
As shown in fig. 3, the joint of the second end cap 13 and the second tube plate 3 includes the second tube plate 3, the seal ring 16, and the second end cap 13 in this order from left to right, and the second tube plate 3 and the second end cap 13 are fastened by the bolts 14.
The working principle of the invention is as follows: the refrigerant flows into the first refrigerant space from the refrigerant inlet pipe 121, the flow cross-sectional area of the fluid is reduced when the refrigerant flows through the vortex generator 4, and the refrigerant is prevented from evaporating under the flow blocking effect of the vortex generator 4, so that the refrigerant in the first refrigerant space exists in a liquid state. The ball head 412 enables the flow rate flowing into each helical blade 42 to be uniformly distributed, and the pressure difference of the refrigerant between the periphery of the vortex generator 4 and the inner wall of the heat exchange tube 10 in the radial direction of the heat exchange tube 10 is basically kept consistent, so that the flow rate uniformity of the refrigerant flowing into the heat exchange tube 10 is improved; on the other hand, the range of variation of the pressure difference between the inflow side and the outflow side of the vortex generator 4 is large, and the evaporation rate of the refrigerant is increased. After the refrigerant as a fluid passes through the vortex generator 4 composed of a plurality of helical blades 42, the fluid is forced to rotate violently around the vortex generator 4 to form a helical precession flow, so that a fluid boundary layer on the inner wall surface of the heat exchange tube 10 is damaged, and the wall surface heat exchange coefficient is enhanced. The liquid refrigerant flows in from the inlet end 101, absorbs heat through evaporation, is converted into a gaseous refrigerant, and flows out from the refrigerant outlet pipe 131.
The invention has simple structure, no movable parts inside, can effectively improve the performance of the heat exchanger, improve the uniformity of the internal flow of the heat exchange tube 10, shorten the length of the heat exchange tube 10 and the size of the evaporator and reduce the production cost.
The technical features of the embodiments described above may be arbitrarily combined, and for the sake of brevity, all possible combinations of the technical features in the embodiments described above are not described, but should be considered as being within the scope of the present specification as long as there is no contradiction between the combinations of the technical features.
The above-mentioned embodiments only express several embodiments of the present invention, and the description thereof is more specific and detailed, but not construed as limiting the scope of the invention. It should be noted that, for a person skilled in the art, several variations and modifications can be made without departing from the inventive concept, which falls within the scope of the present invention. Therefore, the protection scope of the present patent shall be subject to the appended claims.
Claims (10)
1. The utility model provides a shell and tube heat exchanger, includes that casing and both ends are respectively through the fixed heat exchange tube that distributes in casing inside of first tube sheet and second tube sheet, its characterized in that: the vortex generator is arranged at the inlet end of the heat exchange tube and comprises an intermediate body and a helical blade wound on the periphery of the intermediate body.
2. The shell and tube heat exchanger as set forth in claim 1 wherein: the inflow side of the vortex generators is mounted on the first tube sheet, and at least a portion of the vortex generators extends into the corresponding heat exchange tubes.
3. The shell and tube heat exchanger as set forth in claim 2 wherein: the vortex generators and the corresponding heat exchange tubes are coaxially arranged.
4. The shell and tube heat exchanger as set forth in claim 1 wherein: the spiral blade is provided with a positioning boss at the inflow side of the vortex generator, and the first tube plate is provided with a positioning groove matched with the positioning boss.
5. The shell and tube heat exchanger as set forth in claim 1 wherein: the shell and tube heat exchanger further comprises a baffle plate which is arranged between the first tube plate and the first end cover and tightly presses the vortex generator on the first tube plate, and the baffle plate is provided with an avoiding hole corresponding to the inflow side of the vortex generator.
6. The shell and tube heat exchanger as set forth in claim 5 wherein: and a sealing element for pressing the vortex generator on the first tube plate is arranged between the baffle plate and the tube plate.
7. The shell and tube heat exchanger as set forth in claim 1 wherein: the spiral blades are at least two, and each spiral blade and the inner wall of the heat exchange tube form a plurality of refrigerant channels.
8. The shell and tube heat exchanger as set forth in claim 1 wherein: the radius of the helical blade is gradually reduced from the inflow side to the outflow side of the spin vortex generator.
9. The shell and tube heat exchanger as set forth in claim 1 wherein: the intermediate comprises:
the spiral blades are distributed on the periphery of the body;
a ball head at one end of the body and facing the inflow side;
and the tail cone is positioned at the other end of the body and faces to the outflow side.
10. The shell and tube heat exchanger as set forth in claim 9 wherein: the ball head is hemispherical.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811311617.XA CN111141162A (en) | 2018-11-06 | 2018-11-06 | Shell and tube heat exchanger |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811311617.XA CN111141162A (en) | 2018-11-06 | 2018-11-06 | Shell and tube heat exchanger |
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| CN111141162A true CN111141162A (en) | 2020-05-12 |
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| CN201811311617.XA Pending CN111141162A (en) | 2018-11-06 | 2018-11-06 | Shell and tube heat exchanger |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN115127371A (en) * | 2021-12-14 | 2022-09-30 | 中国石油天然气集团有限公司 | In-pipe swirl type adhesion-resistant medium evaporator |
| CN116164443A (en) * | 2021-11-25 | 2023-05-26 | 青岛海尔电冰箱有限公司 | Evaporator and refrigerator |
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| US3648754A (en) * | 1969-07-28 | 1972-03-14 | Hugo H Sephton | Vortex flow process and apparatus for enhancing interfacial surface and heat and mass transfer |
| SU1268929A1 (en) * | 1985-05-14 | 1986-11-07 | Уфимский Нефтяной Институт | Vortex shell-and-tube heat exchanger |
| SU1312361A1 (en) * | 1986-01-27 | 1987-05-23 | Уфимский Нефтяной Институт | Eddy-flow vertical shell-and-tube heat exchanger |
| CN202853666U (en) * | 2012-09-14 | 2013-04-03 | 浙江苍南仪表厂 | Screw-in vortex flow gauge |
| CN206001947U (en) * | 2016-06-17 | 2017-03-08 | 北京仟亿达科技股份有限公司 | A kind of tubular heat exchanger and its enhanced heat exchange structure |
| CN107606975A (en) * | 2017-10-18 | 2018-01-19 | 张少杰 | A kind of pipe heat exchanger |
| CN208671425U (en) * | 2018-08-17 | 2019-03-29 | 江西浩金欧博空调制造有限公司 | A kind of highly effective dry-type shell and tube evaporator with spiral nozzle distributor |
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|---|---|---|---|---|
| CN116164443A (en) * | 2021-11-25 | 2023-05-26 | 青岛海尔电冰箱有限公司 | Evaporator and refrigerator |
| CN115127371A (en) * | 2021-12-14 | 2022-09-30 | 中国石油天然气集团有限公司 | In-pipe swirl type adhesion-resistant medium evaporator |
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