CN108302962B - Partition plate and construction method, straight pipe double-flow-path dry type shell and tube heat exchanger and construction method - Google Patents

Partition plate and construction method, straight pipe double-flow-path dry type shell and tube heat exchanger and construction method Download PDF

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CN108302962B
CN108302962B CN201510866174.0A CN201510866174A CN108302962B CN 108302962 B CN108302962 B CN 108302962B CN 201510866174 A CN201510866174 A CN 201510866174A CN 108302962 B CN108302962 B CN 108302962B
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heat exchange
exchange tube
tube
partition plate
distance
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CN108302962A (en
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谢吉培
张捷
靳文超
李林
赵雷
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Qingdao Haier Air Conditioning Electric Co Ltd
Haier Smart Home Co Ltd
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Qingdao Haier Air Conditioning Electric Co Ltd
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Abstract

The invention discloses a construction method of a partition board, which comprises the following steps: constructing a first separator; constructing a second separator; constructing a third partition plate; and a plurality of fourth partition plates are constructed, the first partition plate, the second partition plate, the third partition plate and the tube plate are connected into a whole by the fourth partition plates, so that a closed chamber is formed among the tube plate, the first partition plate, the second partition plate, the third partition plate and the fourth partition plates, and all the through holes are positioned in the chamber. The invention also discloses a partition plate, a construction method of the straight pipe double-flow-pass dry type shell-and-tube heat exchanger and the straight pipe double-flow-pass dry type shell-and-tube heat exchanger. The construction method, the partition plate and the straight pipe double-flow dry type shell-and-tube heat exchanger adopt the partition plate with a specific shape, the partition plate is used in the straight pipe double-flow dry type shell-and-tube heat exchanger, the flow velocity of a refrigerant can be improved, the phenomenon that the refrigerant falls into the bottom of the heat exchanger is reduced, the refrigerant is uniformly distributed into the heat exchange tubes of the second flow, and the heat exchange efficiency is improved.

Description

Partition plate and construction method, straight pipe double-flow-path dry type shell and tube heat exchanger and construction method
Technical Field
The invention relates to the field of temperature adjusting devices, in particular to a partition plate and a construction method thereof, a straight pipe double-flow-path dry shell and tube heat exchanger and a construction method thereof.
Background
At present, in large and medium-sized water chilling units in China, shell and tube heat exchangers are the most main using types. The shell and tube heat exchanger mainly has two types of dry type and flooded type, and for a heat pump unit, the dry type heat exchanger is absolutely preferred in consideration of the fact that the heat pump unit can operate under two working conditions of refrigeration and heating. The fatal weakness of a flooded heat exchanger unit is the oil return problem, particularly under low-temperature working conditions, the lower part of a heat exchanger cylinder body can accumulate oil, reliable oil return measures are required, and otherwise the safe operation of a system can be influenced. And special oil return equipment is added, so that the cost of the unit is increased, and the reliability of the unit is also reduced. The dry heat exchanger is relatively mature in application, oil return equipment does not need to be independently added, lubricating oil directly enters the compressor along with a refrigerant, and the problem of oil accumulation is generally avoided; meanwhile, the refrigerant filling amount is relatively small, and is generally 1/3 of the flooded heat exchanger. However, for the straight tube double-flow dry shell-and-tube heat exchanger, when the refrigerant enters the first loop, the refrigerant liquid can be gradually gasified, the refrigerant can be in a gas-liquid two-phase state, and when the refrigerant enters the turning part of the end cover tube box of the second loop, if the refrigerant is not well treated, the refrigerant can fall to the bottom of the heat exchanger under the action of gravity, so that the refrigerant entering each heat exchange tube of the next loop is unevenly distributed, and the heat transfer effect of the heat exchanger is seriously influenced. In order to distribute the refrigerant uniformly in the tube box and improve the effect of the heat exchanger, it is necessary to design the tube box structure of the straight tube double-flow dry heat exchanger reasonably.
Fig. 1 is a schematic diagram of the refrigerant flow of a straight tube double-flow dry shell-and-tube heat exchanger in the prior art. The arrows indicate the coolant flow squares. After entering the evaporator, the throttled liquid refrigerant exchanges heat with water flowing outside through the heat exchange tube and then turns into a gas state to flow out. The throttled liquid refrigerant enters the heat exchanger through the fluorine inlet pipe 102, flows through a first loop at the lower part of the heat exchanger cylinder 101, turns in the end cover pipe box 104 to enter a second loop at the upper part of the heat exchanger cylinder 101, and is changed into a gaseous refrigerant after heat exchange and flows out of the fluorine outlet pipe 103. As can be seen from the refrigerant cycle shown in fig. 1, the liquid refrigerant is partially gasified in the first loop, the liquid refrigerant and the gas mixture coming out from each heat exchange tube of the first loop are mixed in the end cover tube box 104 and enter each heat exchange tube of the second loop, if the refrigerant flow rate does not reach the minimum flow rate at which the liquid refrigerant does not fall, the liquid refrigerant will be stored in the tube box to the bottom heat exchange tube due to the action of gravity, and meanwhile, the refrigerant flow entering the second loop is unevenly distributed, which affects the heat exchange efficiency of the heat exchange tubes.
At present, in order to solve the problem of uneven distribution of refrigerant in a tube box of a double-flow-pass dry shell-and-tube heat exchanger, a countermeasure for making the refrigerant distributed uniformly and the best is to make a heat exchange tube in the heat exchanger into a U-shaped tube and remove the tube box and a tube plate at a turning part. Therefore, the refrigerant enters the heat exchange tube from the first loop and enters the turning part of the second loop, the refrigerant cannot be mixed, the refrigerant cannot be subjected to gas-liquid separation under the action of gravity, and liquid accumulation at the bottom of the heat exchanger cannot occur. The U-shaped pipe well solves the problem of uneven distribution of the refrigerant. However, the requirements of the U-shaped pipe on the production process are relatively high, meanwhile, the pipe plate is removed from the heat exchanger at the turning part, and in order to increase the heat exchange at the water side, a plurality of baffle plates (PP plastic plates) are additionally arranged on the outer side of the heat transfer pipe in the cylinder body, so that water flows transversely and repeatedly through the pipe bundle, and the copper pipe bundle in the cylinder body is fixed only by the baffle plates (PP plastic plates). The transverse flow force of water in the cylinder inevitably causes abrasion between the copper pipe and the baffle plate (PP plastic plate) and between the baffle plate (PP plastic plate) and the cylinder for a long time, and a gap is formed between the copper pipe and the baffle plate and the cylinder, so that the problem of water side leakage is caused. Practice proves that a clearance of about 3mm is formed between the outer edge of the baffle plate and the cylinder body, a clearance of about 2mm is formed between the baffle plate and the heat transfer pipe, the heat transfer coefficient of the water side is reduced by 20-30% due to water leakage, and the total heat transfer coefficient is reduced by 5-15%.
Disclosure of Invention
The invention aims to overcome the defects in the prior art and provides a method for constructing a partition plate, which is used for a straight pipe double-flow-pass dry type shell-and-tube heat exchanger.
Another object of the embodiments of the present invention is to overcome the above disadvantages of the prior art, and to provide a partition plate for a straight tube double-flow-pass dry-type shell-and-tube heat exchanger, where the partition plate is installed behind the straight tube double-flow-pass dry-type shell-and-tube heat exchanger, so as to increase the flow rate of a refrigerant, and solve the problem of refrigerant accumulation at the bottom of the heat exchanger due to gas-liquid separation of the refrigerant caused by gravity.
Another object of the embodiments of the present invention is to provide a method for constructing a straight tube double-flow dry-type shell-and-tube heat exchanger, which overcomes the above-mentioned shortcomings of the prior art, and the straight tube double-flow dry-type shell-and-tube heat exchanger constructed by the method adopts a partition plate with a specific shape, so as to increase the flow rate of the refrigerant and solve the problem of refrigerant accumulation at the bottom of the heat exchanger due to gas-liquid separation of the refrigerant caused by gravity.
Another object of the embodiments of the present invention is to overcome the above-mentioned deficiencies of the prior art, and to provide a straight tube dual-flow dry shell-and-tube heat exchanger, which adopts a partition plate with a specific shape, so as to increase the flow rate of the refrigerant and solve the problem of refrigerant accumulation at the bottom of the heat exchanger due to gas-liquid separation of the refrigerant caused by gravity.
Still another object of the embodiments of the present invention is to overcome the above-mentioned deficiencies of the prior art, and to provide a straight tube double-flow dry-type shell-and-tube heat exchanger, which is constructed by the above-mentioned construction method of a straight tube double-flow dry-type shell-and-tube heat exchanger, and can improve the flow rate of the refrigerant, and solve the problem that the refrigerant accumulates at the bottom of the heat exchanger due to gas-liquid separation caused by the action of gravity.
In order to achieve the above purpose, the technical solution of the embodiment of the present invention is as follows:
a construction method of a partition plate is characterized in that the partition plate is used for a straight pipe double-flow-pass dry type shell and tube heat exchanger, a first heat exchange tube array formed by a plurality of rows of first heat exchange tubes and a second heat exchange tube array formed by a plurality of rows of second heat exchange tubes are arranged in a tube body of the heat exchanger, a refrigerant flows out of the first heat exchange tube array and then enters the second heat exchange tube array, a tube plate is arranged at one end of the tube body of the heat exchanger, a plurality of through holes corresponding to the first heat exchange tubes or the second heat exchange tubes are arranged on the tube plate, the first heat exchange tubes and the second heat exchange tubes penetrate into the corresponding through holes from a first surface of the tube plate and extend to a second surface of the tube plate opposite to the first surface, the second surface of the tube plate is taken as a reference plane, and the horizontal direction on the reference plane is set as the x direction, the vertical direction is set as the y direction; the construction method comprises the following steps: constructing a first partition plate, wherein the first partition plate is parallel to the second surface of the tube plate, the bottom edge of the first partition plate is positioned corresponding to the position of the first heat exchange tube at the uppermost row in the first heat exchange tube array, the length of the bottom edge of the first partition plate is equal to the total width of the first heat exchange tube at the uppermost row in the first heat exchange tube array along the x direction, the top edge of the first partition plate is positioned corresponding to the position of the second heat exchange tube at the lowermost row in the second heat exchange tube array, the length of the top edge of the first partition plate is equal to the total width of the second heat exchange tube at the lowermost row in the second heat exchange tube array along the x direction, and the lengths of the two side edges of the first partition plate are equal to the distance from the first heat exchange tube at the uppermost row in the first heat exchange tube array to the second heat exchange tube at the lowermost row in the second heat exchange tube array; constructing a second partition plate having an upper end connected to a lower end of the first partition plate, the length of the upper end of the second partition plate in the y-direction to the lower end of the second partition plate being equal to the distance from the first heat exchange tube in the uppermost row of the first array of heat exchange tubes to the first heat exchange tube in the lowermost row of the first array of heat exchange tubes, the distance from the surface of the second partition plate near the upper end to the second surface of the tube sheet being greater than the distance from the surface of the second partition plate near the lower end to the second surface of the tube sheet, the length of the second partition plate in the x-direction continuously varying with the total width of each row of the first heat exchange tubes in the corresponding first array of heat exchange tubes in the x-direction; constructing a third partition plate having a lower end connected to the upper end of the first partition plate, the length of the upper end of the third partition plate in the y-direction from the lower end of the third partition plate being equal to the distance from the uppermost row of the second array of heat exchange tubes to the lowermost row of the second array of heat exchange tubes, the distance from the surface of the third partition plate near the lower end to the second surface of the tube sheet being greater than the distance from the surface of the third partition plate near the upper end to the second surface of the tube sheet, the length of the third partition plate in the x-direction continuously varying with the total width of each row of the second heat exchange tubes in the corresponding second array of heat exchange tubes in the x-direction; and a plurality of fourth partition plates are constructed, the first partition plate, the second partition plate, the third partition plate and the tube plate are connected into a whole by the fourth partition plates, so that a closed chamber is formed among the tube plate, the first partition plate, the second partition plate, the third partition plate and the fourth partition plates, and all the through holes are positioned in the chamber.
Further, still include: setting a distance from a surface of the second separator plate to a second surface of the tubesheet: setting the direction vertical to the reference plane as the z direction; measuring the total width d of the first heat exchange tube at the uppermost row in the first heat exchange tube array along the x direction1And the total width of the first heat exchange tube at the lowermost row in the first heat exchange tube array along the x direction is d2(ii) a Setting a first distance m in the z-direction from the upper end of the second partition plate to the second surface of the tube plate1The upper end of the second partition board corresponds to the first heat exchange tube which is arranged at the uppermost row in the first heat exchange tube array, and the area of a first cross section corresponding to the first heat exchange tube which is arranged at the uppermost row in the first heat exchange tube array is m1×d1Said first cross section being parallel to the z direction; setting a second distance m in the z-direction from the lower end of the second partition plate to the second surface of the tube plate2The lower end of the second partition board corresponds to the first heat exchange tube at the lowermost row in the first heat exchange tube array, and the area of a second cross section corresponding to the first heat exchange tube at the lowermost row in the first heat exchange tube array is m2×d2The second cross section is parallel to the z direction; collecting the flow of the refrigerant passing through the first section as Q1And the flow rate of the refrigerant passing through the second section is Q2The rising flow velocity V of the refrigerant passing through the first section1=Q1/(m1×d1) The rising flow velocity V of the refrigerant passing through the second cross section2=Q2/(m2×d2) (ii) a Measuring the minimum rising speed V for preventing the refrigerant from falling; selecting a value of said first distance, according to V1=Q1/(m1×d1) To obtain V1(ii) a Suppose V1=V2If V is1Greater than V, then m2=(m1×Q2×d1)/(Q1×d2) If V is1If not, adjusting the first distance to V1And if the distance is larger than V, obtaining the value of the second distance according to the value of the first distance.
Further, still include: setting a distance from a surface of the third separator plate to the second surface of the tubesheet: determining the total width d of the second heat exchange tube at the lowermost row in the second heat exchange tube array along the x direction3And the total width of the second heat exchange tube at the uppermost row in the second heat exchange tube array along the x direction is d4(ii) a Setting a third distance m in the z-direction from the lower end of the third partition plate to the second surface of the tube plate3The lower end of the third partition board corresponds to the second heat exchange tube at the lowermost row in the second heat exchange tube array, and the area of a third section corresponding to the second heat exchange tube at the lowermost row in the second heat exchange tube array is m3×d3Said third cross-section being parallel to the z-direction; setting a fourth distance m in the z-direction from the upper end of the third partition plate to the second surface of the tube plate4The upper end of the third partition board corresponds to the second heat exchange tube at the uppermost row in the second heat exchange tube array, and the area of a fourth cross section corresponding to the second heat exchange tube at the uppermost row in the second heat exchange tube array is m4×d4Said fourth cross-section being parallel to the z-direction; collecting the refrigerant passing through the third section with a flow rate Q3And the flow rate of the refrigerant passing through the fourth section is Q4The rising flow velocity V of the refrigerant passing through the third cross section3=Q3/(m3×d3) A rising flow velocity V of the refrigerant passing through the fourth cross section4=Q4/(m4×d4) (ii) a Selecting a value of said third distance, according to V3=Q3/(m3×d3) To obtain V3(ii) a Suppose V3=V4If V is3Greater than V, then m4=(m3×Q4×d3)/(Q3×d4) If V is3If the distance is not more than V, adjusting the third distance until V3And if the distance is larger than V, obtaining the value of the fourth distance according to the value of the third distance.
Further: when the first heat exchange tube in the first heat exchange tube array and the second heat exchange tube in the second heat exchange tube array are arranged symmetrically, the first heat exchange tube array and the second heat exchange tube array are arranged symmetricallyA third distance m in the z-direction from the lower end of the third partition plate to the second surface of the tube plate1A fourth distance m in the z-direction from the upper end of the third partition plate to the second surface of the tube plate2
Further: a fifth distance in the z-direction from a bottom edge of the first baffle plate to the second surface of the tubesheet is equal to the first distance.
Further: a sixth distance in the z-direction from the top edge of the first baffle plate to the second surface of the tubesheet is equal to the third distance.
Further: the flow of the refrigerant in each first heat exchange tube is q, and the total number of the first heat exchange tubes in the first heat exchange tube array is K1Then Q is1=K1X q, the number of the first heat exchange tubes at the lowermost row in the first heat exchange tube array is k2Then Q is2=k2×q。
Further: the diameter of the first heat exchange tube isWhen the first heat exchange tubes in each row of the first heat exchange tube array are closely arranged, the number of the first heat exchange tubes in the uppermost row of the first heat exchange tube array is k1The total width of the first heat exchange tube at the uppermost row in the first heat exchange tube array along the x directionThe total width of the first heat exchange tubes at the lowermost row in the first heat exchange tube array along the x direction is
Further: the flow rate of the refrigerant in each second heat exchange tube is Q, and then Q is3=Q1The number of the second heat exchange tubes at the uppermost row in the second heat exchange tube array is k4Then Q is4=k4×q。
Further: the diameter of the second heat exchange tube isWhen the second heat exchange tubes of each row in the second heat exchange tube array are closely arranged, the number of the second heat exchange tubes at the lowest row in the second heat exchange tube array is k3The total width of the second heat exchange tube at the lowermost row in the second heat exchange tube array along the x directionThe total width of the second heat exchange tube at the uppermost row in the second heat exchange tube array along the x direction is
Further, it is characterized by further comprising: and partition plate through holes are formed in the first partition plate, the second partition plate, the third partition plate and/or the fourth partition plate.
A separator constructed by the above-described method of constructing a separator.
A method for constructing a straight pipe double-flow-pass dry shell-and-tube heat exchanger adopts the method for constructing the partition plate to construct the partition plate in the heat exchanger.
A straight tube, double flow pass, dry shell and tube heat exchanger comprising: the separator constructed by the above-described method of constructing a separator.
And the straight pipe double-flow dry type shell-and-tube heat exchanger is constructed by adopting the construction method of the straight pipe double-flow dry type shell-and-tube heat exchanger.
The embodiment of the invention has the following beneficial effects:
1. the method for constructing the partition plate can design the partition plate with a specific shape, when the partition plate is used in the straight pipe double-flow-pass dry type shell-and-tube heat exchanger, the flow velocity of the refrigerant can be improved, the phenomenon that the refrigerant falls into the bottom of the heat exchanger is reduced, the refrigerant is uniformly distributed into the heat exchange tubes of the second flow pass, and the heat exchange efficiency is improved.
2. According to the construction method of the partition board provided by the embodiment of the invention, the through holes are formed in the partition board, so that the pressure on two sides of the partition board is balanced.
3. The partition plate provided by the embodiment of the invention has a specific shape, when the partition plate is used in a straight pipe double-flow-pass dry shell-and-tube heat exchanger, the flow velocity of a refrigerant can be improved, the phenomenon that the refrigerant falls into the bottom of the heat exchanger is reduced, the refrigerant is uniformly distributed into the heat exchange tubes of the second flow pass, and the heat exchange efficiency is improved.
4. According to the construction method of the straight pipe double-flow dry type shell and tube heat exchanger, the partition plate with the specific shape is constructed, so that the flow velocity of the refrigerant can be improved, the phenomenon that the refrigerant falls into the bottom of the heat exchanger is reduced, the refrigerant is uniformly distributed into the heat exchange pipes of the second flow, and the heat exchange efficiency is improved.
5. According to the straight pipe double-flow dry type shell and tube heat exchanger disclosed by the embodiment of the invention, the partition plates with specific shapes are arranged, so that the flow velocity of the refrigerant can be improved, the phenomenon that the refrigerant falls into the bottom of the heat exchanger is reduced, the refrigerant uniformly enters the heat exchange tubes of the second flow, and the heat exchange efficiency is improved.
Drawings
Fig. 1 is a refrigerant flow schematic diagram of a straight tube dual-flow dry shell-and-tube heat exchanger in the prior art;
FIG. 2 is a schematic structural view of a straight tube dual pass dry shell and tube heat exchanger in accordance with a preferred embodiment of the present invention;
FIG. 3 is a right side perspective view of the straight tube dual pass dry shell and tube heat exchanger in accordance with a preferred embodiment of the present invention;
fig. 4 is a schematic plan view of a separator according to a preferred embodiment of the invention.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more apparent, the present invention will be described in further detail below with reference to the accompanying drawings and examples. It should be understood that the specific embodiments described herein are merely illustrative of the invention and are not intended to limit the invention.
The embodiment of the invention provides a construction method of a partition board. The baffle plate is used in a straight pipe double-flow-path dry shell-and-tube heat exchanger. Fig. 2 to 4 are respectively a schematic structural view, a right perspective view and a schematic plan view of a partition plate of a straight tube double-flow dry shell-and-tube heat exchanger according to a preferred embodiment of the present invention.
As shown in fig. 2, the structure of the straight tube double-flow dry shell-and-tube heat exchanger to which the separators are to be attached (corresponding to the structure of the straight tube double-flow dry shell-and-tube heat exchanger in the related art) is as follows:
a first heat exchange tube array 208 formed by a plurality of rows of first heat exchange tubes and a second heat exchange tube array 209 formed by a plurality of rows of second heat exchange tubes are arranged in the tube body 201 of the heat exchanger. The first heat exchange tube array 208 is located below the second heat exchange tube array 209. The refrigerant flows out of the first heat exchange tube array 208 and then enters the second heat exchange tube array 209. One end of the tube body 201 of the heat exchanger is provided with a tube sheet 205. The tube plate 205 is provided with a plurality of through holes corresponding to the first heat exchange tube or the second heat exchange tube. The first and second heat exchange tubes penetrate the corresponding through-holes from a first surface of the tube sheet 205 and extend to a second surface of the tube sheet 205 opposite to the first surface. An end cap channel box 204 is provided at one end of the tube body 201. The end cover header 204 houses a tube sheet 205. A refrigerant inlet 202 and a refrigerant outlet 203 are provided at the other end of the pipe body 201. The refrigerant inlet 202 is communicated with a first heat exchange tube in the first heat exchange tube array 208 to form a first loop; the refrigerant outlet 203 is communicated with a second heat exchange tube in the second heat exchange tube array 209 to form a second loop. It should be understood that the positions of the refrigerant inlet 202 and the refrigerant outlet 203 are not limited to be arranged at the other end of the tube 201, and may be arranged according to the positions of the first heat exchange tube array 208 and the second heat exchange tube array 209, so as to meet the requirement that the refrigerant flows into the first heat exchange tube array 208 from the refrigerant inlet 202 and flows out from the second heat exchange tube array 209 through the refrigerant outlet 203. The heat exchange tube is also provided with a medium inlet and a medium outlet for allowing a medium to be heat exchanged to flow into or out of the heat exchanger.
For convenience of description, the second surface of the tube plate 205 is taken as a reference plane, the horizontal direction on the reference plane is taken as the x direction, the vertical direction is taken as the y direction, and the direction perpendicular to the reference plane is taken as the z direction. The specific process of the construction method of the separator is as follows:
step S10: a first partition 216 is constructed.
The first spacer 216 is parallel to the second surface of the tube sheet 205.
The position of the bottom edge of the first partition plate 216 corresponds to the position of the uppermost row of first heat exchange tubes in the first heat exchange tube array 208, and the length of the bottom edge of the first partition plate 216 is equal to the total width of the uppermost row of first heat exchange tubes in the first heat exchange tube array 208 along the x direction.
The position of the top edge of the first partition 216 corresponds to the position of the second heat exchange tube at the lowermost row in the second heat exchange tube array 209, and the length of the top edge of the first partition 216 is equal to the total width of the second heat exchange tube at the lowermost row in the second heat exchange tube array 209 along the x direction.
The length of both side edges of the first partition plate 216 is equal to the distance from the first heat exchange tube at the uppermost row in the first heat exchange tube array 208 to the second heat exchange tube at the lowermost row in the second heat exchange tube array 209.
Step S20: the second partition 226 is constructed.
The upper end of the second barrier 226 is connected to the lower end of the first barrier 216.
The length in the y-direction from the upper end of the second partition 226 to the lower end of the second partition 216 is equal to the distance from the uppermost row of the first heat exchange tubes of the first heat exchange tube array 208 to the lowermost row of the first heat exchange tubes of the first heat exchange tube array 209.
The surface of the second partition 226 near the upper end is located at a greater distance from the second surface of the tube plate 205 than the surface of the second partition 226 near the lower end is located at the second surface of the tube plate 205.
The length of the second partition 226 in the x-direction continuously varies with the total width of each row of the first heat exchange tubes in the corresponding first heat exchange tube array 208 in the x-direction.
Step S30: a third partition 236 is constructed.
The lower end of the third partition 236 is connected to the upper end of the first partition 216.
The length in the y-direction from the upper end of the third partition 236 to the lower end of the third partition 236 is equal to the distance from the second heat exchange tube at the uppermost row in the second heat exchange tube array 209 to the second heat exchange tube at the lowermost row in the second heat exchange tube array 209.
The surface of the third partition 236 near the lower end is located at a greater distance from the second surface of the tube plate 205 than the surface of the third partition 236 near the upper end is located at the second surface of the tube plate 205. The length of the third partition 236 in the x-direction continuously varies with the total width of each row of second heat exchange tubes in the corresponding second heat exchange tube array 209 in the x-direction.
Step S40: a plurality of fourth separators are constructed.
The plurality of fourth baffles integrally connect the first baffle plate 216, the second baffle plate 226, the third baffle plate 236 and the tube plate 205 such that the tube plate 205 and the first baffle plate 216, the second baffle plate 226, the third baffle plate 236, the plurality of fourth baffles form a sealed chamber 207 therebetween. The through holes are all located within the chamber 207.
The plurality of fourth baffles may form a continuous surface with the first baffle 216, the second baffle 226, and the third baffle 236, or may be a plurality of panels assembled together.
According to the partition plate constructed by the method, the partition plate has the shape of high middle and low top and bottom, when the refrigerant flows out of the first heat exchange tube array, the refrigerant is blocked by the partition plate with a specific shape, the flow velocity of the refrigerant is improved, the condition that the refrigerant falls into the bottom of the heat exchanger due to the action of gravity is reduced, the phenomenon of gas-liquid separation of the refrigerant is reduced, the refrigerant is conveniently distributed into the heat exchange tubes of the second flow, and the heat exchange efficiency is improved.
Preferably, the method for constructing the partition plate of the present invention may further set the distances from the first partition plate 216, the second partition plate 226, and the third partition plate 236 to the tube plate 205, so as to prevent the refrigerant from falling to the bottom of the heat exchanger due to gravity, which is as follows:
1. the distance from the surface of the second partition 226 to the second surface of the tube sheet 205 is set.
(1) The total width d of the first heat exchange tube at the uppermost row in the first heat exchange tube array 208 along the x direction is measured1And the first heat exchange tube in the lowermost row of the first heat exchange tube array 208 has a total width d in the x direction2
When the first heat exchange tubes of each row in the first heat exchange tube array 208 are closely arranged (close arrangement means that the heat exchange tubes in one row are next to each other in sequence), d can be obtained by the following method1And d2. The diameter of the first heat exchange tube isThe number of the first heat exchange tubes at the uppermost row in the first heat exchange tube array 208 is k1The number of the first heat exchange tubes in the lowermost row in the first heat exchange tube array 208 is k2The total width of the first heat exchange tube in the uppermost row of the first heat exchange tube array 208 along the x directionThe total width of the first heat exchange tube at the lowermost row in the first heat exchange tube array 208 along the x direction is
(2) Let a first distance m in the z-direction from the upper end of the second partition 226 to the second surface of the tube sheet 2051. The upper end of the second partition 226 corresponds to the uppermost row of the first heat exchange tubes in the first heat exchange tube array 208, and the area of the first cross section corresponding to the uppermost row of the first heat exchange tubes in the first heat exchange tube array 208 is m1×d1The first cross section is parallel to the z direction.
(3) Let a second distance m in the z-direction from the lower end of the second partition 226 to the second surface of the tube plate 2052. The lower end of the second partition 226 corresponds to the first heat exchange tube at the lowermost row in the first heat exchange tube array 208, and the area of the second cross section corresponding to the first heat exchange tube at the lowermost row in the first heat exchange tube array 208 is m2×d2The second cross-section is parallel to the z-direction.
(4) Collecting the refrigerant passing through the first section as Q1And the flow rate of the refrigerant passing through the second section is Q2The rising flow velocity V of the refrigerant passing through the first cross section1=Q1/(m1×d1) The rising flow velocity V of the refrigerant passing through the second cross section2=Q2/(m2×d2)。
Specifically, Q can be obtained by the following method1And Q2: the flow rate of the refrigerant collected in each first heat exchange tube is q, and the total number of the first heat exchange tubes in the first heat exchange tube array 208 is K1Then Q is1=K1X q, the number of the first heat exchange tubes at the lowermost row in the first heat exchange tube array 208 is k2Then Q is2=k2×q。
(5) The minimum rising speed at which the refrigerant does not fall is measured as V.
(6) Selecting a value of the first distance, according to V1=Q1/(m1×d1) To obtain V1
(7) Suppose V1=V2If V is1Greater than V, then m2=(m1×Q2×d1)/(Q1×d2) If V is1If not, adjusting the first distance to V1If the distance is larger than V, the value of the second distance is obtained according to the value of the first distance.
Second baffle 226 is a continuous plane, and by virtue of the first distance and the second distance, the distance from the surface located between the upper and lower ends of second baffle 226 to tube sheet 205 (i.e., continuously varying between the first distance and the second distance) can be determined, thereby determining the distance from the surface of second baffle 226 to the second surface of tube sheet 205.
2. The distance from the surface of the third partition 236 to the second surface of the tube sheet 205 is set.
(1) The total width d of the second heat exchange tube in the lowermost row of the second heat exchange tube array 209 in the x direction is measured3And the second heat exchange tube in the uppermost row in the second heat exchange tube array 209 has a total width d in the x direction4
The diameter of the second heat exchange tube is equal to that of the first heat exchange tube, and when the second heat exchange tubes of each row in the second heat exchange tube array 209 are closely arranged, d can be obtained by the following method3And d4. The number of the second heat exchange tubes at the lowermost row in the second heat exchange tube array 209 is k3The total width of the second heat exchange tube in the lowermost row in the second heat exchange tube array 209 along the x directionThe second heat exchange tube at the uppermost row in the second heat exchange tube array 209 has a total width in the x direction of
(2) Let a third distance m in the z-direction from the lower end of the third partition 236 to the second surface of the tube plate 2053The lower end of the third partition 236 corresponds to the second heat exchange tube at the lowermost row in the second heat exchange tube array 209, and the area of the third cross section corresponding to the second heat exchange tube at the lowermost row in the second heat exchange tube array 209 is m3×d3And the third section is parallel to the z-direction.
(3) Let a fourth distance m in the z-direction from the upper end of the third partition 236 to the second surface of the tube plate 2054The upper end of the third partition 236 corresponds to the second heat exchange tube at the uppermost row in the second heat exchange tube array 209, and the area of the fourth cross section corresponding to the second heat exchange tube at the uppermost row in the second heat exchange tube array 209 is m4×d4The fourth section is parallel to the z-direction.
(4) Collecting the refrigerant passing through the third section at a flow rate of Q3And the flow rate of the refrigerant passing through the fourth section is Q4The rising flow velocity V of the refrigerant passing through the third cross section3=Q3/(m3×d3) The rising flow velocity V of the refrigerant passing through the fourth cross section4=Q4/(m4×d4)。
Specifically, Q can be obtained by the following method1And Q2: when the diameters of the second heat exchange tubes are equal to the diameter of the first heat exchange tube, the flow rate of the refrigerant in each second heat exchange tube is Q, all the refrigerants pass through the third section, and then Q is obtained3=Q1. Then every time the refrigerant passes through one row of second heat exchange tubes, the amount of the residual refrigerant is Q3The amount of the refrigerant entering the lower row of second heat exchange tubes is subtracted. The number of the second heat exchange tubes at the uppermost row in the second heat exchange tube array is k4Then Q is4=k4×q。
(5) Selecting a value of the third distance, according to V3=Q3/(m3×d3) To obtain V3
(6) Suppose V3=V4If V is3Greater than V, then m4=(m3×Q4×d3)/(Q3×d4) If V is3If not, adjusting the third distance to V3If the distance is larger than V, the value of the fourth distance is obtained according to the value of the third distance.
The third baffle 236 is a continuous plane, and the distance from the surface located between the upper and lower ends of the third baffle 236 to the tube sheet 205 can be determined (i.e., continuously varied between the third and fourth distances) by the third and fourth distances, thereby determining the distance from the surface of the third baffle 236 to the second surface of the tube sheet 205.
In particular, when the first heat exchange tube in the first heat exchange tube array 208 and the second heat exchange tube in the second heat exchange tube array 209 are arranged symmetrically, a third distance m along the z direction from the lower end of the third partition 236 to the second surface of the tube sheet 205 is1And a fourth distance m in the z-direction from the upper end of the third partition plate 236 to the second surface of the tube plate 2052
3. The distance from the surface of the first spacer 216 to the second surface of the tube sheet 205 is set.
(1) A fifth distance in the z-direction from the bottom edge of first spacer 216 to the second surface of tubesheet 205 is equal to the first distance.
(2) A sixth distance in the z-direction from the top edge of the first baffle 216 to the second surface of the tube sheet 205 is equal to the third distance.
First baffle 216 is a continuous plane, and by a fifth distance and a sixth distance, the distance from the face between the bottom edge and the top edge of first baffle 216 to tubesheet 205 can be determined (i.e., continuously varied between the fifth distance and the sixth distance) to determine the distance from the face of first baffle 216 to the second face of tubesheet 205.
Specifically, when the first heat exchange tube in the first heat exchange tube array 208 and the second heat exchange tube in the second heat exchange tube array 209 are arranged symmetrically, the distance from the surface of the first partition 216 to the second surface of the tube sheet 205 is equal to the first distance.
Through the specific size design of the first partition plate 216, the second partition plate 226 and the third partition plate 236, the rising speed of the liquid is not less than the minimum flow speed at which the liquid does not fall, so that the phenomenon of gas-liquid separation of the refrigerant is further avoided, and no liquid refrigerant is accumulated in the heat exchanger.
To equalize the pressure inside and outside chamber 207, the diaphragm construction method further includes the step of providing diaphragm throughbores 210 in first diaphragm 216, second diaphragm 226, third diaphragm 236, and/or fourth diaphragm.
The baffle through-holes 210 are designed such that a small portion of the gas can flow out of the chamber 207 through the baffle through-holes 210, thereby equalizing the pressure inside and outside the chamber 207. Therefore, the size of the partition plate through hole 210 should not be too large, and only a small amount of gas needs to flow out, so that the refrigerant is prevented from leaking from the partition plate through hole 210. Preferably, the diameter of the partition wall through hole 210 is about 5 mm.
The number of the partition through holes 210 is not limited, and may be selected according to specific situations, and preferably, the partition through holes 210 are uniformly distributed on the partition.
The embodiment of the invention also provides the clapboard constructed by adopting the construction method of the clapboard.
The embodiment of the invention also provides a construction method of the straight pipe double-flow-pass dry shell-and-tube heat exchanger. Unlike the conventional method of constructing a heat exchanger, the method of the embodiment of the present invention constructs a separator in a heat exchanger using the above-described method of constructing a separator.
The construction method of the straight pipe double-flow-path dry-type shell-and-tube heat exchanger can specifically comprise the following steps:
1. a tube 201 is provided.
2. A first array of heat exchange tubes 208 and a second array of heat exchange tubes 209 are mounted within the tube body 201.
3. A tube sheet 205 is provided at one end of the tube body 201.
4. A plurality of through holes corresponding to the first heat exchange tube or the second heat exchange tube are provided on the tube plate 205.
5. The first and second heat exchange tubes are penetrated from a first surface of the tube sheet 205 into the corresponding through holes and extended to a second surface of the tube sheet 205 opposite to the first surface.
6. The end-cap tube box 204 is disposed at one end of the tube body 201 such that the end-cap tube box 204 covers the tube sheet 205.
7. The refrigerant inlet 202 and the refrigerant outlet 203 are arranged at the other end of the tube body 201, the refrigerant inlet 202 is communicated with a first heat exchange tube in the first heat exchange tube array 208 to form a first loop, and the refrigerant outlet 203 is communicated with a second heat exchange tube in the second heat exchange tube array 209 to form a second loop.
8. A medium inlet and a medium outlet are provided on the pipe body 201.
9. The separator is set by the method described above.
It should be understood that the order of the above-described processes is not limited, and an appropriate order may be selected according to actual operations.
According to the construction method of the straight pipe double-flow dry type shell and tube heat exchanger, the partition plate with the specific shape is constructed, so that the flow velocity of the refrigerant can be improved, the phenomenon that the refrigerant falls into the bottom of the heat exchanger is reduced, the refrigerant is uniformly distributed into the heat exchange pipes of the second flow, and the heat exchange efficiency is improved.
The embodiment of the invention also provides a straight pipe double-flow dry shell and tube heat exchanger. The heat exchanger includes a separator constructed by the above-described method of constructing a separator.
The embodiment of the invention also provides a straight pipe double-flow dry shell and tube heat exchanger. The heat exchanger is constructed by adopting the construction method of the straight pipe double-flow-path dry-type shell-and-tube heat exchanger.
The structure of the heat exchanger is as follows: a first heat exchange tube array 208 formed by a plurality of rows of first heat exchange tubes and a second heat exchange tube array 209 formed by a plurality of rows of second heat exchange tubes are arranged in the tube body 201 of the heat exchanger. The first heat exchange tube array 208 is located below the second heat exchange tube array 209. The refrigerant flows out of the first heat exchange tube array 208 and then enters the second heat exchange tube array 209. One end of the tube body 201 of the heat exchanger is provided with a tube sheet 205. The tube plate 205 is provided with a plurality of through holes corresponding to the first heat exchange tube or the second heat exchange tube. The first and second heat exchange tubes penetrate the corresponding through-holes from a first surface of the tube sheet 205 and extend to a second surface of the tube sheet 205 opposite to the first surface. An end cap channel box 204 is provided at one end of the tube body 201. The end cover header 204 houses a tube sheet 205. A refrigerant inlet 202 and a refrigerant outlet 203 are provided at the other end of the pipe body 201. The refrigerant inlet 202 is communicated with a first heat exchange tube in the first heat exchange tube array 208 to form a first loop; the refrigerant outlet 203 is communicated with a second heat exchange tube in the second heat exchange tube array 209 to form a second loop. The partition plate obtained by the above method is provided on the tube plate 205 so that a closed chamber 207 is formed between the partition plate and the tube plate 205. The through holes are all located within the chamber 207.
According to the straight pipe double-flow dry type shell and tube heat exchanger disclosed by the embodiment of the invention, the partition plates with specific shapes are arranged, so that the flow velocity of the refrigerant can be improved, the phenomenon that the refrigerant falls into the bottom of the heat exchanger is reduced, the refrigerant uniformly enters the heat exchange tubes of the second flow, and the heat exchange efficiency is improved.
The present invention is provided in the above description only for the preferred embodiments of the present invention, and not intended to limit the present invention, and any modifications, equivalents and improvements made within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims (15)

1. A construction method of a partition plate is characterized in that the partition plate is used for a straight pipe double-flow-pass dry type shell and tube heat exchanger, a first heat exchange tube array formed by a plurality of rows of first heat exchange tubes and a second heat exchange tube array formed by a plurality of rows of second heat exchange tubes are arranged in a pipe body of the heat exchanger, a refrigerant flows out of the first heat exchange tube array and then enters the second heat exchange tube array, a tube plate is arranged at one end of the pipe body of the heat exchanger, a plurality of through holes corresponding to the first heat exchange tubes or the second heat exchange tubes are arranged on the tube plate, the first heat exchange tubes and the second heat exchange tubes penetrate into the corresponding through holes from a first surface of the tube plate and extend to a second surface of the tube plate opposite to the first surface, and the partition plate is characterized in that:
setting the second surface of the tube plate as a reference plane, wherein the horizontal direction on the reference plane is set as the x direction, and the vertical direction is set as the y direction;
the construction method comprises the following steps: constructing a first partition plate, wherein the first partition plate is parallel to the second surface of the tube plate, the bottom edge of the first partition plate is positioned corresponding to the position of the first heat exchange tube at the uppermost row in the first heat exchange tube array, the length of the bottom edge of the first partition plate is equal to the total width of the first heat exchange tube at the uppermost row in the first heat exchange tube array along the x direction, the top edge of the first partition plate is positioned corresponding to the position of the second heat exchange tube at the lowermost row in the second heat exchange tube array, the length of the top edge of the first partition plate is equal to the total width of the second heat exchange tube at the lowermost row in the second heat exchange tube array along the x direction, and the lengths of the two side edges of the first partition plate are equal to the distance from the first heat exchange tube at the uppermost row in the first heat exchange tube array to the second heat exchange tube at the lowermost row in the second heat exchange tube array;
constructing a second partition plate having an upper end connected to a lower end of the first partition plate, the length of the upper end of the second partition plate in the y-direction to the lower end of the second partition plate being equal to the distance from the first heat exchange tube in the uppermost row of the first array of heat exchange tubes to the first heat exchange tube in the lowermost row of the first array of heat exchange tubes, the distance from the surface of the second partition plate near the upper end to the second surface of the tube sheet being greater than the distance from the surface of the second partition plate near the lower end to the second surface of the tube sheet, the length of the second partition plate in the x-direction continuously varying with the total width of each row of the first heat exchange tubes in the corresponding first array of heat exchange tubes in the x-direction;
constructing a third partition plate having a lower end connected to the upper end of the first partition plate, the length of the upper end of the third partition plate in the y-direction from the lower end of the third partition plate being equal to the distance from the uppermost row of the second array of heat exchange tubes to the lowermost row of the second array of heat exchange tubes, the distance from the surface of the third partition plate near the lower end to the second surface of the tube sheet being greater than the distance from the surface of the third partition plate near the upper end to the second surface of the tube sheet, the length of the third partition plate in the x-direction continuously varying with the total width of each row of the second heat exchange tubes in the corresponding second array of heat exchange tubes in the x-direction;
and a plurality of fourth partition plates are constructed, the first partition plate, the second partition plate, the third partition plate and the tube plate are connected into a whole by the fourth partition plates, so that a closed chamber is formed among the tube plate, the first partition plate, the second partition plate, the third partition plate and the fourth partition plates, and all the through holes are positioned in the chamber.
2. The method of constructing a separator plate according to claim 1, further comprising: setting a distance from a surface of the second separator plate to a second surface of the tubesheet:
setting the direction vertical to the reference plane as the z direction;
measuring the total width d of the first heat exchange tube at the uppermost row in the first heat exchange tube array along the x direction1And the total width of the first heat exchange tube at the lowermost row in the first heat exchange tube array along the x direction is d2
Setting a first distance m in the z-direction from the upper end of the second partition plate to the second surface of the tube plate1The upper end of the second partition board corresponds to the first heat exchange tube which is arranged at the uppermost row in the first heat exchange tube array, and the area of a first cross section corresponding to the first heat exchange tube which is arranged at the uppermost row in the first heat exchange tube array is m1×d1Said first cross section being parallel to the z direction;
setting a second distance m in the z-direction from the lower end of the second partition plate to the second surface of the tube plate2The lower end of the second partition board corresponds to the first heat exchange tube at the lowermost row in the first heat exchange tube array, and the area of a second cross section corresponding to the first heat exchange tube at the lowermost row in the first heat exchange tube array is m2×d2The second cross section is parallel to the z direction;
collecting the flow of the refrigerant passing through the first section as Q1And the flow rate of the refrigerant passing through the second section is Q2The rising flow velocity V of the refrigerant passing through the first section1=Q1/(m1×d1) The rising flow velocity V of the refrigerant passing through the second cross section2=Q2/(m2×d2);
Measuring the minimum rising speed V for preventing the refrigerant from falling;
selecting a value of said first distance, according to V1=Q1/(m1×d1) To obtain V1
Suppose V1=V2If V is1Greater than V, then m2=(m1×Q2×d1)/(Q1×d2) If V is1If not, adjusting the first distance to V1And if the distance is larger than V, obtaining the value of the second distance according to the value of the first distance.
3. The method of constructing a separator plate according to claim 2, further comprising: setting a distance from a surface of the third separator plate to the second surface of the tubesheet:
determining the total width d of the second heat exchange tube at the lowermost row in the second heat exchange tube array along the x direction3And the total width of the second heat exchange tube at the uppermost row in the second heat exchange tube array along the x direction is d4
Setting a third distance m in the z-direction from the lower end of the third partition plate to the second surface of the tube plate3The lower end of the third partition board corresponds to the second heat exchange tube at the lowermost row in the second heat exchange tube array, and the area of a third section corresponding to the second heat exchange tube at the lowermost row in the second heat exchange tube array is m3×d3Said third cross-section being parallel to the z-direction;
setting a fourth distance m in the z-direction from the upper end of the third partition plate to the second surface of the tube plate4The upper end of the third partition board corresponds to the second heat exchange tube at the uppermost row in the second heat exchange tube array, and the area of a fourth cross section corresponding to the second heat exchange tube at the uppermost row in the second heat exchange tube array is m4×d4Said fourth cross-section being parallel to the z-direction;
collecting the refrigerant passing through the third section with a flow rate Q3Hetong (Chinese character of 'He')The flow rate of the refrigerant passing through the fourth section is Q4The rising flow velocity V of the refrigerant passing through the third cross section3=Q3/(m3×d3) A rising flow velocity V of the refrigerant passing through the fourth cross section4=Q4/(m4×d4);
Selecting a value of said third distance, according to V3=Q3/(m3×d3) To obtain V3
Suppose V3=V4If V is3Greater than V, then m4=(m3×Q4×d3)/(Q3×d4) If V is3If the distance is not more than V, adjusting the third distance until V3And if the distance is larger than V, obtaining the value of the fourth distance according to the value of the third distance.
4. A method of constructing a separator plate according to claim 3, wherein: when the first heat exchange tubes in the first heat exchange tube array and the second heat exchange tubes in the second heat exchange tube array are arranged symmetrically, a third distance from the lower ends of the third partition plates to the second surface of the tube plate along the z direction is m1A fourth distance m in the z-direction from the upper end of the third partition plate to the second surface of the tube plate2
5. The method of constructing a separator plate according to claim 2, wherein: a fifth distance in the z-direction from a bottom edge of the first baffle plate to the second surface of the tubesheet is equal to the first distance.
6. A method of constructing a separator plate according to claim 3, wherein: a sixth distance in the z-direction from the top edge of the first baffle plate to the second surface of the tubesheet is equal to the third distance.
7. The method of constructing a separator plate according to claim 2, wherein: the flow rate of the refrigerant in each first heat exchange tube is q, and the first heat exchange tubesThe total number of the first heat exchange tubes in the heat exchange tube array is K1Then Q is1=K1X q, the number of the first heat exchange tubes at the lowermost row in the first heat exchange tube array is k2Then Q is2=k2×q。
8. The method of constructing a separator according to claim 5, wherein: the diameter of the first heat exchange tube isWhen the first heat exchange tubes in each row of the first heat exchange tube array are closely arranged, the number of the first heat exchange tubes in the uppermost row of the first heat exchange tube array is k1The total width of the first heat exchange tube at the uppermost row in the first heat exchange tube array along the x directionThe total width of the first heat exchange tubes at the lowermost row in the first heat exchange tube array along the x direction is
9. The method of constructing a separator according to claim 5, wherein: the flow rate of the refrigerant in each second heat exchange tube is Q, and then Q is3=Q1The number of the second heat exchange tubes at the uppermost row in the second heat exchange tube array is k4Then Q is4=k4×q。
10. The method of constructing a separator plate according to claim 7, wherein: the diameter of the second heat exchange tube isWhen the second heat exchange tubes of each row in the second heat exchange tube array are closely arranged, the second heat exchange tubes of the lowermost row in the second heat exchange tube arrayHas a number of k3The total width of the second heat exchange tube at the lowermost row in the second heat exchange tube array along the x directionThe total width of the second heat exchange tube at the uppermost row in the second heat exchange tube array along the x direction is
11. A method of constructing a separator according to any one of claims 1 to 10, further comprising: and partition plate through holes are formed in the first partition plate, the second partition plate, the third partition plate and/or the fourth partition plate.
12. A separator constructed by the method of construction of a separator according to any one of claims 1 to 11.
13. A construction method of a straight pipe double-flow-path dry shell-and-tube heat exchanger is characterized by comprising the following steps: constructing the separator in the heat exchanger using the method of constructing a separator according to any one of claims 1 to 11.
14. A straight tube double-flow-path dry-type shell-and-tube heat exchanger is characterized by comprising: a separator constructed according to the method of construction of a separator as claimed in any one of claims 1 to 11.
15. A straight tube dual pass dry shell and tube heat exchanger constructed using the method of construction of a straight tube dual pass dry shell and tube heat exchanger as claimed in claim 13.
CN201510866174.0A 2015-12-01 2015-12-01 Partition plate and construction method, straight pipe double-flow-path dry type shell and tube heat exchanger and construction method Active CN108302962B (en)

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Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB748264A (en) * 1951-10-23 1956-04-25 Foster Wheeler Ltd Improvements in and relating to heat exchangers
CN2294448Y (en) * 1996-09-05 1998-10-14 郎逵 Heat exchanger
CN2395241Y (en) * 1999-11-18 2000-09-06 张文泼 Floating heat exchanger
CN2433585Y (en) * 2000-07-14 2001-06-06 西安市三桥机电设备有限公司 Shell-and-tube helical flow heat exchanger
CN1310327A (en) * 2001-03-14 2001-08-29 束润涛 Shell-and-tube heat exchanger of stress corrosion resisting rare earth alloy steel
CN2578766Y (en) * 2002-11-19 2003-10-08 江苏中圣石化工程有限公司 High-performance heat exchanger with external spiral pipes
CN202928410U (en) * 2012-12-10 2013-05-08 王国栋 Double-tube pass graphite tube type seawater heat exchanger

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB748264A (en) * 1951-10-23 1956-04-25 Foster Wheeler Ltd Improvements in and relating to heat exchangers
CN2294448Y (en) * 1996-09-05 1998-10-14 郎逵 Heat exchanger
CN2395241Y (en) * 1999-11-18 2000-09-06 张文泼 Floating heat exchanger
CN2433585Y (en) * 2000-07-14 2001-06-06 西安市三桥机电设备有限公司 Shell-and-tube helical flow heat exchanger
CN1310327A (en) * 2001-03-14 2001-08-29 束润涛 Shell-and-tube heat exchanger of stress corrosion resisting rare earth alloy steel
CN2578766Y (en) * 2002-11-19 2003-10-08 江苏中圣石化工程有限公司 High-performance heat exchanger with external spiral pipes
CN202928410U (en) * 2012-12-10 2013-05-08 王国栋 Double-tube pass graphite tube type seawater heat exchanger

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