CN209910451U - Shell and tube heat exchanger - Google Patents

Abstract

The utility model discloses a shell and tube heat exchanger, the heat exchange tube passes the jet flow board, extend in the casing, the casing both ends are sealed, the outside cold-carrying agent that flows of heat exchange tube, the inside refrigerant that flows, the cold-carrying agent passes through the jet flow through-hole that sets up on the jet flow board, spray to the heat exchange tube surface on, accomplish the heat transfer, the jet flow board cross-section shows bow-shaped form, the first terminal surface of jet flow board and third terminal surface are the plane parallel to each other, the second terminal surface is an inclined plane, first terminal surface is located the border position, the third terminal surface is located the middle part position, connect through second terminal surface and first terminal surface, it has the jet flow through-hole to open along perpendicular to terminal surface tangential direction on the second terminal surface, it. By applying the technical scheme, because the jet flow directions of the edge and the middle jet flow hole are not parallel, the secondary refrigerant is mixed at the heat exchange tube arranged on the boundary to form liquid disturbance, thereby improving the heat exchange efficiency of the heat exchange tube and achieving the effect of integrally improving the heat exchange efficiency.

Description

Shell and tube heat exchanger

Technical Field

The utility model belongs to a heat exchanger, concretely relates to shell and tube heat exchanger.

Background

The shell and tube heat exchanger used in the field of air conditioning generally adopts a mode that a heat exchange tube penetrates through a baffle plate, secondary refrigerant flows outside the heat exchange tube, bypasses the baffle plate through a gap formed by the baffle plate and a shell, and flows through the outer surface of the heat exchange tube by a curve, so that the heat exchange is completed with the heat exchange tube.

The shell and tube heat exchanger has the defects that the flow velocity of secondary refrigerant is low and the heat exchange efficiency is low, the baffle plate is replaced by the jet flow plate, the jet flow plate is provided with jet holes parallel to the axis of the heat exchange tube, the edge of the jet flow plate is sealed with the inner wall of the shell, the secondary refrigerant is forcibly sprayed to the heat exchange tube through the jet flow holes to exchange heat, and the heat exchange efficiency is greatly improved due to the high flow velocity.

However, in this way, since the jet flow plates adopt the same plane structure, and the whole plate surface is uniformly provided with the circular jet flow through holes with the same specification, the pressure of the secondary refrigerant at each position of the plate surface is inconsistent, so that the flow and the flow rate of the secondary refrigerant sprayed by the through holes on the whole plate surface are inconsistent, especially the flow of the edge part is less, the flow rate is lower, and the flow rate direction flows in parallel with the heat exchange tube, so that the heat exchange efficiency of the heat exchange tube is not high, and the heat exchange efficiency of the shell-and-tube heat exchanger is comprehensively influenced.

SUMMERY OF THE UTILITY MODEL

In order to overcome the defects, the utility model provides a shell and tube heat exchanger, including heat exchange tube, casing and efflux board, place in the efflux board in the casing inside, the edge with the shells inner wall closely laminates, the heat exchange tube passes the efflux board, extends in the casing, the casing both ends are sealed, the heat exchange tube outside flow secondary refrigerant, the inside refrigerant that flows, the secondary refrigerant passes through the efflux through-hole that sets up on the efflux board, sprays on the heat exchange tube surface, accomplishes the heat transfer between secondary refrigerant and the refrigerant, the efflux board cross-section shows bow-shaped form, the efflux board divide into first terminal surface, second terminal surface and third terminal surface, first terminal surface and third terminal surface are the plane that is parallel to each other, the second terminal surface is an inclined plane, first terminal surface is located the border position, the third terminal surface is located the middle part position, through second terminal surface and first terminal surface are connected, the second end face is provided with jet flow through holes along the direction perpendicular to the tangential direction of the end face, the third end face is provided with circular heat exchange tube fixing holes and jet flow through holes, and the protruding part of the jet flow plate faces the flow direction of the secondary refrigerant.

Further, the jet flow plate is of a disc-shaped structure with steps.

Furthermore, the first end face is uniformly provided with fixing screw through holes.

Furthermore, the heat exchange tube fixing holes, the jet flow through holes and the fixing screw rod through holes on the jet flow plate are uniformly arranged along the scattering line by taking the circle center of the jet flow plate as a base point.

Further, on the third terminal surface, in being less than 3/4 distance of third terminal surface total diameter, the jet through-hole diameter is 2 ~ 4 millimeters's benchmark round hole, and remaining the jet through-hole diameter is 1 ~ 1.25 times of benchmark round hole diameter.

The jet flow through holes in the peripheral part of the third end face are larger than the jet flow through holes in the middle part, because the pressure distribution of the secondary refrigerant on the jet flow plate face is smaller in the edge part than in the middle part, the secondary refrigerant flow in the edge part is smaller than that in the middle part due to the same aperture, and the jet flow in the edge part can be improved by properly improving the jet flow aperture of the edge part, so that the jet flow of the whole end face is uniform.

Further, the shape of the second end surface inclined plane is a plane or a curved surface.

Furthermore, the included angle alpha between the cross sections of the second end surface and the third end surface is greater than 90 degrees and less than 180 degrees.

Furthermore, the through holes formed in the second end face are circular, oval or strip-shaped.

Further, the flow cross-sectional area of the second end face jet flow through hole is 1.5-2 times of the flow cross-sectional area of the reference jet flow through hole of the third end face.

The jet holes arranged on the second end surface are not parallel to the jet direction of the jet holes on the third end surface to form a certain included angle, so that secondary refrigerant flowing through the outside of the heat exchange tube arranged on the edge part can flow, and because the flowing included angles are inconsistent, fluid mixed at the heat exchange tube can form turbulent flow, thereby achieving the purpose of improving the heat exchange effect between the heat exchange tube and the secondary refrigerant.

Meanwhile, the flow cross section area of the jet flow through hole on the second end surface is larger than that of the jet flow hole on the third end surface, so that impurities with larger particles in the heat exchanger can smoothly pass through the blocking of the jet flow plate, the situation that the impurities are blocked due to too small through holes of the jet flow plate is avoided, and the effect of normally exerting the heat exchange efficiency of the heat exchange tube with accumulated impurities can be achieved.

In addition, because the flow cross-sectional area of the jet through hole on the second end surface is larger than that of the reference jet hole on the third end surface, the jet flow effect of improving the jet flow passing through the jet through hole can be achieved, and the effect of uniform flow of the jet plate jet hole is achieved.

Furthermore, a spring fixing hole is formed in the third end face and is arranged at the upper portion, close to the center of the jet flow through hole, of the spring fixing hole.

Further, the spring is wound into a spiral shape, one end of the spring is inserted into the spring fixing hole and fixed on the concave surface of the jet flow plate, and the other end of the spring is inserted into the jet flow through hole.

The spring is inserted into the jet hole, and the power of secondary refrigerant flowing through the jet hole can be utilized, so that the spring rocks in the jet hole, foreign matters in the jet hole are often cleared away through the rocking of the spring, the blockage of the foreign matters in the jet hole is avoided, and the effect of keeping unobstructed for a long time is achieved.

Meanwhile, due to the fact that the springs are inserted into the jet holes to shake, the secondary refrigerant flowing through the jet holes is disturbed to a certain degree, and when the secondary refrigerant flows through the heat exchange tubes, the effect of improving the heat efficiency to a certain degree can be achieved on the basis of original heat exchange.

In addition, the inserted spring can also play a role in adjusting the jet flow to a certain extent.

Further, the diameter of the spring is 0.2-0.5 mm.

Furthermore, an annular scattering cone is arranged on the back surface of the second end surface of the jet flow plate along the edge of the jet flow through hole.

In order to avoid the secondary refrigerant ejected by the jet holes on the second end surface from flowing to the heat exchange tube, because the through hole with a longer distance from the heat exchange tube and the through hole with a closer distance, if no flow channels are used, they interfere with each other to create ineffective vortices, resulting in ineffective loss of power to propel the coolant, such as dead circulation of coolant in a region, therefore, the scattering cone is arranged at the edge of the jet flow aperture to form a flared opening similar to a horn shape, so that the secondary refrigerant coming out of the jet flow hole is used as a diffusion flow channel by means of the horn opening, gradually and slowly diffused in the flaring, and finally flows onto the heat exchange tube, and is mixed with the secondary refrigerant flowing out from the jet hole horizontally arranged at the third end surface at the heat exchange tube, because the outflow angles are different, disturbance is formed at the heat exchange tube, so that the invalid loss of driving the secondary refrigerant to flow is avoided being reduced, and the heat exchange efficiency of the heat exchange tube is improved.

Furthermore, every heat exchange tube outside overlaps the heat exchange tube fin alone to closely laminate, the heat exchange tube fin is circular terminal surface, and it has the triangle-shaped breach to open above that, shows ratchet form, the height of heat exchange tube outer wall to the most advanced outward flange of triangle-shaped fin is for cup jointing heat exchange tube radial 0.5 ~ 1 times, and fin thickness is 0.25 ~ 0.5 millimeter.

The heat exchange fins are sleeved on each heat exchange tube to increase the heat exchange area and improve the heat exchange efficiency of the heat exchange tubes, the fins are triangular pieces to achieve the effect that the gap is provided for the secondary refrigerant to smoothly flow through the fins, and meanwhile due to the fact that the plurality of ratchet-shaped fins are arranged, the secondary refrigerant can also generate disturbance when flowing through the fins, and therefore the effect of improving the heat exchange efficiency is finally achieved.

Furthermore, the interval between the heat exchange tube fins of each heat exchange tube set is 5-10 mm, and the heat exchange tube fins of different heat exchange tube sets are not interfered with each other.

Further, a flow divider is arranged inside the shell, and the heat exchange tube is communicated with an external refrigerant pipeline through the flow divider.

Furthermore, a plurality of heat exchange tube U-shaped elbows are adopted to connect the heat exchange tubes in series from front to back, and the heat exchange tubes are lengthened in the shell.

Furthermore, the shell is circular, the left end face of the shell is in sealing connection with a left sealing end cover which is in detachable flange connection, and the left sealing end cover is respectively connected with a refrigerant inlet pipe and a refrigerant outlet pipe in a penetrating manner; and the right end surface of the shell is in sealing connection with the right sealing end cover, and is in welded connection.

Furthermore, a plurality of groups of shunts connected with the refrigerant inlet pipe and the refrigerant outlet pipe, and shunt capillary tubes, heat exchange tubes and U-shaped elbows of the heat exchange tubes, which are connected with the shunts in a matching manner, are arranged in the shell.

Further, the heat exchange tube is an internal thread copper tube.

Furthermore, the secondary refrigerant inlet pipe and the secondary refrigerant outlet pipe are positioned at the upper parts of the two ends of the shell and are communicated with the inside of the shell.

By applying the technical scheme, the jet flow plate is in the shape of an arch, so that the jet flow direction of the jet hole at the edge is not parallel to the jet flow direction of the jet hole at the middle part to form an included angle, and the jetted secondary refrigerant can form disturbance between fluids at the boundary of the heat exchange tube at the edge part, thereby improving the heat exchange efficiency of the heat exchange tube and achieving the effect of integrally improving the heat exchange efficiency of the heat exchanger.

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 for those skilled in the art, other drawings can be obtained according to these drawings without inventive effort.

FIG. 1 is the working principle diagram of the shell-and-tube heat exchanger of the present invention

FIG. 2-1 is a front view of the bow-shaped jet plate of the present invention

FIG. 2-2 is a schematic cross-sectional view of the bow-shaped jet plate of the present invention

FIG. 2-3 is a back view of the bow-shaped jet plate of the present invention

Fig. 2-4 are schematic views of the third end face of the bow-shaped jet plate of the present invention

Fig. 3 is a schematic view of the spring structure of the present invention

FIG. 4 is the schematic diagram of the fin suit on the heat exchange tube of the present invention

FIG. 5 is a schematic view of the U-shaped elbow extended heat exchange tube of the present invention

FIG. 6 is a schematic view of the present invention with multiple inlet and outlet pipes

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 obvious that the described embodiments are only some embodiments of the present invention, not all embodiments. Based on the embodiments in the present invention, all other embodiments obtained by a person skilled in the art without creative efforts belong to the protection scope of the present invention.

The embodiment of the utility model provides a shell and tube heat exchanger, as shown in fig. 1, including refrigerant inlet pipe 100, refrigerant outlet pipe 103, heat exchange tube 111, U type elbow 113, casing 108, secondary refrigerant feed liquor pipe 102, first shunt 104, second shunt 105, secondary refrigerant drain pipe 112, left sealing end cover 101, right sealing end cover 114, reposition of redundant personnel capillary 106, efflux board 107, efflux board set screw 110 and heat exchange tube fin 109; the jet flow plate 107 and the shell 108 are circular, the outer diameter of the jet flow plate 107 is the same as the diameter of the inner wall of the shell 108, and jet flow through holes 107b and 107g, a heat exchange tube fixing hole 107c and a fixing screw rod through hole 107i are formed in the jet flow plate 107; a refrigerant inlet pipe 100 and a refrigerant outlet pipe 103 respectively penetrate through a left sealing end cover 101 and are respectively in sealing connection with a first flow divider 104 and a second flow divider 105 which are arranged in the left sealing end cover 101, one end of a flow dividing capillary 106 is communicated with the flow dividing holes of the first flow divider 104 and the second flow divider 105 and is fixedly connected with the flow dividing holes in a welding mode, the other end of the flow dividing capillary is communicated with the pipe orifice at one end of a heat exchange pipe 111 and is fixedly connected with the pipe orifice at the other end of the heat exchange pipe 111 in a welding mode, the heat exchange pipe 111 penetrates through a heat exchange pipe fixing hole 107c of a jet plate 107 and extends in a shell 108, the protruding part of the jet plate 107 faces the flow direction of secondary refrigerant, the pipe orifice at the other end face of the extended heat exchange pipe 111 is communicated with the pipe orifice of a U-shaped elbow 113 and is fixedly connected with the heat exchange pipe in a welding mode to form a, the two ends are connected and fixed through nuts, and the secondary refrigerant inlet pipe 101 and the secondary refrigerant outlet pipe 112 are respectively arranged at the edge positions of the left end and the right end of the upper part of the shell 108 and are communicated with the shell 108.

When the heat exchanger is in practical use, high-temperature gaseous refrigerant enters a refrigerant inlet pipe 100 with the pipe diameter of 22 mm and a first flow divider 104 which is welded and communicated with the refrigerant inlet pipe 100, respectively enters a heat exchange pipe 111 which is welded and communicated with the other end of the flow dividing capillary 106 through a flow dividing capillary 106 which is welded and communicated with a flow dividing hole and has the diameter of 6.35 mm, an internal thread copper pipe with the pipe diameter of 9.52 mm of the heat exchange pipe 111 flows in the heat exchange pipe 111 and flows to the tail end of the heat exchange pipe 111, then continuously enters the other heat exchange pipe 111 through a U-shaped elbow 113 which is welded and communicated with the heat exchange pipe 111, flows in the other heat exchange pipe 111 in the opposite direction, the two heat exchange pipes are welded through the U-shaped elbow 113 to form a U-shaped heat exchange pipe, the refrigerant flows in the U-shaped heat exchange pipe and exchanges heat with external secondary refrigerant, the liquid refrigerant flows into the second flow divider 105 through the flow dividing holes of the second flow divider 105, and the liquid refrigerant gathered in the second flow divider 105 flows out of the shell-and-tube heat exchanger through the refrigerant outlet pipe 103 with the diameter of 16 mm, so that the heat exchange is completed.

The U-shaped heat exchange tube may also be bent as a whole, in which case the U-shaped bend 113 exists as a part of the U-shaped heat exchange tube as a whole.

The heat exchange pipe 111 may be made of other materials such as an aluminum pipe, a seamless steel pipe, etc. in addition to the above copper pipe.

The shell 108 of the shell-and-tube heat exchanger has an outer diameter of 180 mm, a wall thickness of 2 mm and an inner diameter of 176 mm, a coolant inlet pipe 102 is arranged in the middle of the upper part of the left end cover 101, a coolant outlet pipe 112 is arranged at the upper part of the left end of the shell 108, the coolant inlet and outlet pipes are communicated with the inner wall, and the diameters of the inlet and outlet pipes are 38 mm. The coolant is water, and after flowing into the casing 108 through the coolant inlet tube 102, the coolant is forcibly injected onto the heat exchange tube 111 through the jet holes 107b and 107g formed in the jet plate 107 for fixing the heat exchange tube 111, and performs forced heat exchange with the coolant flowing inside the heat exchange tube 111.

The coolant may be selected from ethylene glycol, brine, etc. in addition to the above water.

Since the axes of the jet holes 107b, 107g are not parallel, the fluids injected through the holes 107b, 107g of the coolant are mixed and disturbed at the heat exchange tubes 111 disposed near the inner wall edge of the casing 108.

The schematic view of the jet flow plate 107 is shown in fig. 2-1, 2-2 and 2-3, the jet flow plate 107 is of a step-shaped disc-shaped structure, the cross section of the jet flow plate 107 is arc-shaped, the diameter of the outer edge of the jet flow plate 107 is 176 mm, the jet flow plate is arranged perpendicular to the axis of the heat exchange tube 111, and the edge of the jet flow plate 107 is tightly attached and sealed with the inner wall of the shell 108.

The jet flow plate 107 is divided into a first end face 107h, a second end face 107f and a third end face 107a, the first end face 107h and the third end face 107a are planes parallel to each other, the second end face 107f is an inclined plane, an included angle alpha between the third end face 107a and the second end face 107f is 120 degrees, the first end face 107h is positioned at the edge of a disc, the third end face 107a is positioned at the middle position of the disc and connected with the first end face 107h through the second end face 107f, a jet flow through hole 107g is formed in the second end face 107f along the tangential direction perpendicular to the second end face 107f, and a circular heat exchange tube fixing hole 107c and a jet flow through hole 107b are formed in the third end face 107 a; the first end face 107h is provided with 4 circular fixing screw through holes 107i, the diameter of each fixing screw through hole 107i is 4 mm, the fixing screw through holes are symmetrically arranged in a cross shape, and the protruding parts of the jet flow plates 107 face the flow direction of the secondary refrigerant.

The heat exchange tube fixing holes 107c and the jet flow through holes 107b are uniformly arranged along the scattering line by taking the center of the jet flow plate 107 as a base point.

The second end surface 107f may also be a curved surface, such as an arc-shaped curved surface, and the jet hole is provided with a through hole in a direction perpendicular to a tangential direction on the curved surface, i.e., in a normal direction.

On the concave surface of the second end surface 107f, i.e. the surface facing away from the flow direction of the coolant, in order to avoid that the coolant ejected through the jet holes 107g of the second end surface 107f will interfere with the fluid ejected from the jet holes 107g near the heat exchange tube 111 before reaching the heat exchange tube 111, and thus cause ineffective vortex and make ineffective waste of jet power, two diverging cones 107j are arranged near the outlet edge of the jet holes 107g, and the diverging cones 107j are annular structures.

The scattering cone takes the jet flow through hole 107g as the position center to form a flared opening similar to a horn shape, and the secondary refrigerant jetted out through the jet flow hole 107g of the second end surface 107f is gradually and slowly diffused in the flared opening by taking the horn opening as a diffusion flow channel and finally flows onto the heat exchange tube 111.

The diameter of the jet hole 107b of the heat exchange tube opened on the third end face 107a is different according to the position of arrangement, as shown in fig. 2-4, the diameter of the circle of the outer edge 1a of the third end face 107a is 132 mm, at the distance of 3/4 mm of the diameter, that is, at the diameter of 99 mm, the broken line 1c divides the third end face 107a into two parts, the inner part of the jet hole 1d has a reference hole with a diameter of 2 mm, and the outer periphery of the broken line 1d, the inner part of the outer edge 1a of the third end face 107a, the diameter of the jet hole 1b is 1.25 times the diameter of the jet hole 1d as the reference hole, that is, the diameter is 2.5 mm.

The second end face 107f is provided with a circular flow passage 107g having a flow area 2 times that of the reference flow passage 1d, i.e., a diameter of 2.8 mm.

The diameter of the jet hole on the dotted line 1c is the same as that of the jet through hole 1 b.

The jet through holes 1b and 1d with different apertures are arranged at different positions of the third end surface 107a, so that the problem that the injected flow rate is inconsistent due to different pressures of the coolant fluid at different positions on the jet plate surface is avoided.

The second end face 107f is provided with the jet flow through holes with the flow area larger than that of the jet flow through holes of the third end face, so that the uniform flow rate of the jet flow through the jet flow holes on the third end face 107a is ensured, and the jet flow holes are axially provided with a certain included angle, so that secondary refrigerants sprayed to heat exchange tubes arranged at the edge can be ensured to be mixed, thereby generating fluid disturbance and improving the heat exchange efficiency; thirdly, the larger jet hole can ensure that the larger particles of impurities in the shell 108 can smoothly flow through the jet plate 107, and the reduction of heat exchange efficiency caused by the accumulation of the impurities is avoided.

Besides 120 degrees, the included angle α between the third end face 107a and the second end face 107f can be set to other angles according to actual use requirements, such as 90 degrees, or 175 degrees, etc., the jet flow plates 107 are sleeved on the heat exchange tube 111, the number of the jet flow plates 107 can be selected according to actual use requirements, such as 3, 4, etc., besides 2 jet flow plates arranged close to two ends of the heat exchange tube 111 in fig. 1, the redundant parts are arranged between the jet flow plates 107 at two ends, can be uniformly arranged at equal intervals, can also meet the requirements of actual heat exchange efficiency, and are arranged in a non-equidistant mode, for example, the front-back distance of the jet flow plates can be increased progressively by alkali in an equal ratio mode.

Taking 5 fluidic plates as an example, the distance between the first block and the second block can be 200 mm, the distance between the second block and the third block can be 400 mm, the distance between the third block and the fourth block can be 800 mm, the distance between the fourth block and the fifth block can be 1600 mm, the selected distances increase in an equal ratio manner or decrease in opposite directions, and the total length between the first block and the fifth fluidic plate at two ends is 3000 mm.

Other diameters of the fluidic through-holes may be chosen, for example, the diameter of the reference fluidic through-hole 1d may be chosen to be 2.5 mm, or 4 mm, etc., while the corresponding fluidic through- holes 1b and 107g may be chosen according to the corresponding multiples described above.

The injection holes 107g formed in the second end face 107f may be formed in an elliptical shape, a strip shape, or the like, in addition to the circular shape.

In order to avoid the blockage of the jet hole 107b on the third end surface 107a, a spring fixing hole 107d is formed in the third end surface 107a at a position close to the upper part of the jet hole 107b, the spring fixing hole 107d is a circular hole with an aperture of 0.2 mm, the spring fixing hole 107d is used in cooperation with a spring 107e, the spring fixing hole 107d can be a through hole, and the fixing hole 107d arranged at the position close to the upper part of the jet hole 107b can be arranged along a scattering line of the jet hole 107b, can also be vertically arranged, or can be arranged at other positions convenient to install.

The spring fixing hole 107d may be a through hole or not.

The structure schematic diagram of the spring 107e is shown in fig. 3, one end of the spring 107e is wound into a spiral shape 2c, two ends of the spring are straight line segments 2a and 2b, the diameter of the spring is 0.2 mm, when in actual use, the straight line segment 2a is inserted into a through hole 107d formed in one surface of the third end surface 107a of the jet flow plate, which is back to the flow direction of the coolant, and the straight line segment 2a and the plane of the third end surface 107a, which faces the flow direction of the coolant, are flush and firmly fixed in the same direction as the spiral shape 2c, the other straight line segment 2b of the spring 107e is inserted into the jet flow through holes 1b and 1d, the end surface of the straight line segment 2b is longer than the jet flow holes 1b and 1d, enters the plane.

When the secondary refrigerant flows through the jet holes 1b and 1d, the flowing power can enable the spring inserted into the jet hole to freely bounce in the jet hole, the jet through hole can be cleaned at any time along with the flowing of the fluid, meanwhile, the freely bouncing spring can also disturb the flowing secondary refrigerant, so that the flowing fluid can flow onto the heat exchange tube with partial disturbance, and the heat exchange is enhanced.

The spring cleaning structure can also be used in the jet through hole 107g on the second end face 107f, as required above.

The spring 107e can also select springs with other specifications and diameters, such as 0.5 mm diameter, meanwhile, springs with different specifications and diameters can be selected on the jet flow through holes 1b, 1d and 107g of different end faces, such as the jet flow through hole 1b selects a spring with a diameter of 0.5 mm, the jet flow through hole 1b selects a spring with a diameter of 0.25 mm, and the jet flow through hole 107g selects a spring with a diameter of 0.2 mm.

In order to improve the heat exchange efficiency between the heat exchange tube and the secondary refrigerant, a heat exchange tube fin 109 is sleeved on the heat exchange tube 111, the fin is sleeved on the heat exchange tube, as shown in a schematic diagram of fig. 4, the bottom 109b of the heat exchange tube fin 109 is tightly attached to the outer wall of the heat exchange tube 111, the fin is in a triangular sheet shape 109a and is in a ratchet shape, the diameter of the heat exchange tube 111 is 9.52 mm, the height from the outer wall to the outer edge of the tip of the triangular fin is 9.52 mm, and the thickness of the.

Alternatively, the height of the outer wall to the outer edge of the triangular fin tip is 4.8 millimeters and the fin thickness is 0.25 millimeters.

The distance of each heat exchange tube fin 109 sleeved on the same heat exchange tube 111 is 5 mm or 10 mm, and the heat exchange tube fin 109 can be sleeved on the outer wall of the heat exchange tube 111 in a spiral structure except for the single-piece manner.

The sleeving method comprises the steps of firstly determining the sleeving position of the heat exchange tube 111, secondly respectively sleeving the jet flow plate 107 and the heat exchange tube fins 109 on the determined position, and then expanding the heat exchange tube 111 in a mechanical tube expansion mode to complete the fixation among the heat exchange tube 111, the jet flow plate 107 and the heat exchange tube fins 109.

The heat exchange tube fins 109 sleeved between each heat exchange tube 111 do not interfere with each other, so that the secondary refrigerant sprayed through the jet holes of the jet plate 107 can be ensured to flow smoothly along the axial direction of the heat exchange tubes 111 through the triangular gaps of the heat exchange tube fins 109 and the fin gaps sleeved between different heat exchange tubes.

The fins of the heat exchange tube fins 109 may be in the shape of a bar or other notches, except for the triangular notches.

The fixing mode, except the mechanical expansion tube, can also adopt other modes, for example, water expansion, or adopt high-frequency welding mode between the heat exchange tube fin 109 and the heat exchange tube 111 to carry out.

The installation method of the shell-and-tube heat exchanger comprises the following specific steps:

firstly, fixing a spring 107e on the arched jet plate 107 and installing the spring in an inserted jet hole;

secondly, fixing the heat exchange tube 111 with the arched jet flow plate 107 and the heat exchange tube fins 109 by adopting the fixing mode, penetrating the jet flow plate fixing screw 110 through a fixing screw through hole 107i on the jet flow plate 107, and connecting and fixing two ends of the jet flow plate fixing screw through nuts;

thirdly, the refrigerant inlet pipe 100 and the refrigerant outlet pipe 103 respectively penetrate through the left sealing end cover 101, and are respectively welded and fixedly communicated with a corresponding first flow divider 104 and a corresponding second flow divider 105 which are arranged in the left sealing end cover 101, and are simultaneously communicated and welded and fixedly connected with a corresponding flow dividing capillary 106 and a U-shaped heat exchange pipe 111 to form an integral component.

Fourth, the above-described integrated components are inserted into the housing 108 in place and the left and right end caps 101, 114 and the housing 108 are finally sealed at both ends.

The schematic diagram of the lengthened heat exchange tube 111 is shown in fig. 5, in the shell 108, one end of the first flow divider 104 is communicated with the refrigerant inlet tube 100, the other end is communicated with the tube opening of the first heat exchange tube 111, one opening of the U-shaped elbow 113 is inserted, the other opening of the U-shaped elbow 113 is inserted into the tube opening of the second heat exchange tube 111 and is welded and fixed to form a U-shaped heat exchange tube extension, meanwhile, the tube opening of the other end of the second heat exchange tube 111 is communicated with one opening of the other U-shaped elbow 113, the other tube opening of the U-shaped elbow 113 is welded and continuously extended at the tube opening connected with the third heat exchange tube 111, the heat exchange tubes are gradually extended in sequence, finally, the tube opening of the last communicated heat exchange tube 111 is connected with one end of the second flow divider 105 to complete the extension of the required tube, and then, the other.

The heat exchange tube can also be prolonged by welding the U-shaped elbow 113 in the above way by making the integral U-shaped heat exchange tube.

In order to reduce the volume of the shell and tube heat exchanger, a plurality of sets of flow dividers connected with the refrigerant inlet and outlet pipes and matched flow dividing capillary tubes 106, heat exchange tubes 111 and heat exchange tube U-bends 113 can be arranged in one shell 108, as shown in fig. 6.

The left sealing end cover 101 is provided with 3 through holes from top to bottom, three refrigerant inlet pipes 100a, 100b and 100c are respectively inserted, the pipe diameter is 22 mm, meanwhile, the left sealing end cover 101 is provided with 3 through holes from top to bottom at symmetrical positions on the right side, three refrigerant outlet pipes 103a, 103b and 103c are respectively inserted, the pipe diameter is 16 mm, wherein 100a, 103a, 100b, 103b, 100c and 103c are in one-to-one correspondence, and are respectively communicated with matched flow divider, flow dividing capillary tubes, heat exchange tubes and U-shaped elbows through being arranged in the shell 108 to respectively form independent refrigerant loops.

The pipe diameters between the matched refrigerant inlet pipe and the matched refrigerant outlet pipe can be the same or different, and the pipe diameter of the refrigerant inlet pipe of the general flowing gas is larger than that of the liquid pipeline, so that the loss of the flow resistance of the refrigerant can be reduced.

The refrigerant inlet pipe and the refrigerant outlet pipe are symmetrically arranged in 3 groups, and in actual use, pipelines can also be symmetrically arranged in 2 groups or more than 3 groups; the positions may be arranged in other suitable manners, such as vertically symmetrical arrangement, in addition to the above-described laterally symmetrical arrangement.

The shell and the shape of the shell-and-tube heat exchanger can adopt other structures such as square structures, oval structures and the like besides the circular structures, and the shape of the jet plate is correspondingly adjusted to ensure that the outer edge can be tightly attached to the inner wall of the shell.

The above is only a 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 embodiments of the present invention are also 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.

Claims (21)

1. A shell and tube heat exchanger comprises a heat exchange tube, a shell and a jet flow plate, wherein the jet flow plate is arranged in the shell, the edge of the jet flow plate is tightly attached to the inner wall of the shell, the heat exchange tube penetrates through the jet flow plate and extends in the shell, two ends of the shell are sealed, secondary refrigerant flows outside the heat exchange tube, refrigerant flows inside the heat exchange tube, and the secondary refrigerant is sprayed onto the outer surface of the heat exchange tube through jet flow through holes arranged on the jet flow plate to finish heat exchange between the secondary refrigerant and the refrigerant, the shell and tube heat exchanger is characterized in that the cross section of the jet flow plate is in an arched shape, the jet flow plate is divided into a first end surface, a second end surface and a third end surface, the first end surface and the third end surface are planes parallel to each other, the second end surface is an inclined plane, the first end surface is positioned at the edge position, the second end face is provided with jet flow through holes along the direction perpendicular to the tangential direction of the end face, the third end face is provided with circular heat exchange tube fixing holes and jet flow through holes, and the protruding parts of the jet flow plates face the flow direction of the secondary refrigerant.

2. The shell and tube heat exchanger of claim 1 wherein the flow plates are stepped, disc shaped structures.

3. The shell and tube heat exchanger of claim 2 wherein the first end face is uniformly perforated with fixing screw through holes.

4. The shell-and-tube heat exchanger of claim 2, wherein the heat exchange tube fixing holes, the jet flow through holes and the fixing screw through holes in the jet flow plate are all uniformly arranged along the scattering line with the center of the circle of the jet flow plate as a base point.

5. The shell and tube heat exchanger as set forth in claim 2, wherein the diameter of the jet through-hole is 2 to 4 mm of the reference circular hole within a distance of 3/4 which is less than the total diameter of the third end surface, and the diameters of the remaining jet through-holes are 1 to 1.25 times the diameter of the reference circular hole.

6. The shell and tube heat exchanger of claim 2 wherein the second end face chamfer is planar or curved in shape.

7. The shell and tube heat exchanger of claim 2 wherein the second end face is at an angle α of greater than 90 degrees and less than 180 degrees from the cross-sectional plane of the third end face.

8. The shell and tube heat exchanger of claim 2 wherein the second end face is provided with through holes having a circular, oval or strip shape.

9. The shell and tube heat exchanger of claim 8, wherein the second end face jet through hole flow cross-sectional area is 1.5 to 2 times the reference jet through hole flow cross-sectional area of the third end face.

10. The shell and tube heat exchanger of claim 2 wherein the third end face is further provided with a spring retention hole disposed proximate an upper portion of the central location of the jet opening.

11. The shell and tube heat exchanger as set forth in claim 10, wherein a spring is wound in a spiral shape, one end of which is inserted into the spring fixing hole and fixed, and the other end of which is inserted into the jet through hole, at the concave surface of the jet plate.

12. The shell and tube heat exchanger as set forth in claim 11, wherein the spring diameter is 0.2 to 0.5 mm.

13. The shell and tube heat exchanger of claim 2 wherein an annular diverging cone is provided along the edge of the flow aperture on the back of the second end face of the flow plate.

14. The shell and tube heat exchanger as recited in claim 2 wherein each of the heat exchange tubes is individually sleeved with and closely attached to a heat exchange tube fin, the heat exchange tube fin is a circular end surface with a triangular notch and is ratchet-shaped, the height from the outer wall of the heat exchange tube to the outer edge of the tip of the triangular fin is 0.5 to 1 time of the radius of the sleeved heat exchange tube, and the fin thickness is 0.25 to 0.5 mm.

15. The shell and tube heat exchanger as recited in claim 14 wherein the fin pitch of the heat exchange tube of each heat exchange tube set is 5 to 10 mm, and the fins of the heat exchange tubes of different heat exchange tube sets do not interfere with each other.

16. The shell and tube heat exchanger as recited in any one of claims 1 to 15 wherein a flow diverter is further provided inside the shell, the heat exchange tubes being in communication with an external refrigerant line through the flow diverter.

17. The shell and tube heat exchanger of claim 15 wherein the heat exchange tubes are connected in series from front to back by a plurality of U-bends, the tubes being elongated within the shell.

18. The shell and tube heat exchanger as recited in claim 15 wherein the shell is circular and the sealed connection between the left end face of the shell and the left end cap is a removable flange connection, the left end cap being connected across the refrigerant inlet and outlet tubes, respectively; and the right end surface of the shell is in sealing connection with the right sealing end cover, and is in welded connection.

19. The shell and tube heat exchanger of claim 15 wherein a plurality of sets of flow splitters connected to the refrigerant inlet and outlet tubes are provided within the shell, and wherein the flow splitters are provided in mating relationship with the flow splitting capillary tubes, the heat exchange tubes and the heat exchange tube U-bends.

20. The shell and tube heat exchanger of claim 15 wherein the heat exchange tubes are internally threaded copper tubes.

21. The shell and tube heat exchanger of claim 15 wherein coolant inlet and outlet tubes are located at upper positions on opposite ends of the shell and communicate with the interior of the shell.

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