Heat exchangers and heat exchange devices

Abstract

The present application relates to a heat exchanger and a heat exchange device, the heat exchanger comprises: a core shaft with an axis extending left and right, a spiral coil wound at least 2 times in a spiral shape around the outer periphery of the core shaft; the spiral coil comprises a plurality of liquid-carrying coils spirally wound around the outside of the core shaft and having spiral liquid channels inside, the plurality of liquid-carrying coils are parallel to each other and arranged at intervals in the radial direction of the core shaft, so that a spiral first liquid-carrying channel that passes left and right is formed between the plurality of liquid-carrying coils; any two adjacent layers of spiral coils are separated by a certain distance, so that a spiral second liquid-carrying channel that passes left and right is formed between the adjacent layers of spiral coils. The heat exchanger has a large heat exchange capacity and high heat exchange efficiency.

Description

Technical Field

[0001] The present application relates to the field of heat exchange, and in particular to a heat exchanger and a heat exchange device. Background Art

[0002] Heat exchangers are devices that transfer heat from hot fluids to cold fluids. Heat exchangers are important in life and industrial production. Traditional heat exchangers generally occupy a large area due to the pursuit of a larger heat exchange area, so they have disadvantages such as high installation space requirements and inconvenient maintenance. Therefore, how to reduce the size of the heat exchanger while ensuring sufficient heat exchange area is an urgent problem to be solved in the industry.

[0003] The Chinese utility model patent with publication number 204495135U discloses a novel spiral plate reaction heat exchanger, comprising a first thin plate, a second thin plate, a middle partition and an outer cylinder, wherein the first thin plate and the second thin plate are interlaced and wound to form a double spiral cylinder, the middle partition is respectively connected to the ends of the first thin plate and the second thin plate near the center of the spiral, and the double spiral cylinder is divided into two spaces that do not interfere with each other, one of which is a hot fluid channel (hot medium entry chamber) for running hot fluid, and the other space is a cold fluid channel (cold medium entry chamber) for running cold fluid, the hot fluid channel and the cold fluid channel are distributed at intervals, and the hot fluid channel and the cold fluid channel are respectively provided with a hot fluid inlet and a cold fluid outlet at the positions near the center of the spiral, and the hot fluid channel and the cold fluid channel are respectively provided with a hot fluid outlet and a cold fluid inlet at the outermost positions, when heat exchange is performed, the surface areas of the first thin plate and the second thin plate are both the heat exchange areas of the hot and cold fluids, ensuring sufficient heat exchange area, and at the same time, the setting of the double spiral cylinder can effectively reduce the volume of the heat exchanger. However, the spiral plate reaction heat exchanger in the patent document has the following disadvantages:

[0004] 1. Large flow resistance. The hot fluid and the cold fluid move in the hot fluid flow channel and the cold fluid flow channel respectively over a long distance in the spiral curling direction. During the movement, the movement direction of the fluid is constantly changing, and a large interaction force will be generated between the thin plate and the heat exchange fluid, which makes the flow resistance of the fluid in the flow channel large, and is not suitable for heat exchange of gaseous fluids.

[0005] 2. High maintenance frequency. Although the hot fluid flow channel is in a spiral curled shape, it is actually still a space, that is, the hot fluid is transported in a single flow channel, and the cold fluid flow channel is the same. Taking the hot fluid flow channel as an example, the problem with a single flow channel is that if a certain position of the hot fluid flow channel is blocked, it will affect the transportation of the hot fluid in the entire hot fluid flow channel. In severe cases, it will directly cause the hot fluid to be unable to be transported, making the heat exchanger unable to work normally. That is, as long as there is a blockage in one position of the hot fluid flow channel, the staff will need to maintain the heat exchanger, and the maintenance frequency is high.

[0006] 3. This type of heat exchanger is a multi-layer spiral winding structure. In order to achieve sufficient heat exchange and obtain higher heat exchange efficiency, the structure is usually wound in multiple layers, which makes the radial dimension too large. When the heat exchanger is installed, a larger radial space is required for installing the heat exchanger. This makes it impossible to achieve concealed installation of the heat exchanger in some occasions where the radial space is limited.

[0007] 4. As mentioned above, in order to achieve sufficient heat exchange and obtain higher heat exchange efficiency, the structure is usually wound in multiple layers to increase the internal fluid movement stroke. Due to the spiral flow channel, the internal resistance is large, so when blockage occurs, it is extremely difficult to clean out the blockage.

[0008] 5. The heat exchanger has a single-channel structure. In actual application, the cold fluid and the hot fluid have only one channel respectively. The fluid volume is small, resulting in small heat exchange and insufficient heat exchange capacity (heating or cooling capacity). If the cross-sectional area of ​​the spiral channel is increased to increase the fluid flow rate, the heat exchange area of ​​the heat exchanger of the same size will be greatly reduced, which is a waste of money.

[0009] This application arises from this. Summary of the invention

[0010] The technical problem to be solved by the present application is: in view of the above problems, a heat exchanger with large heat exchange capacity and high heat exchange efficiency and a heat exchange device composed of such heat exchangers are proposed.

[0011] The technical solution of this application is:

[0012] A heat exchanger, comprising:

[0013] A mandrel with its axis extending left and right, and

[0014] A spiral coil spirally wound around the mandrel for at least 2 turns;

[0015] The spiral coil includes a plurality of liquid-carrying belts spirally wound around the core shaft and having spiral liquid channels inside, wherein the plurality of liquid-carrying belts are parallel to each other and arranged at intervals in the radial direction of the core shaft, so that a spiral first liquid-carrying flow channel that passes through the left and right sides is formed between the plurality of liquid-carrying belts;

[0016] The spiral tapes of any two adjacent layers are separated by a certain distance, so that a second spiral air flow passage penetrating from left to right is formed between the spiral tapes of the adjacent layers.

[0017] Based on the above technical solutions, this application also includes the following preferred solutions:

[0018] Each liquid conveying belt is provided with a first liquid inlet and outlet interface at the inner end in the spiral direction of the liquid conveying belt, and each liquid conveying belt is provided with a second liquid inlet and outlet interface at the outer end in the spiral direction of the liquid conveying belt.

[0019] The lengths of the plurality of liquid-carrying belts in the spiral direction are equal.

[0020] The first liquid inlet and outlet interface extends to the left in parallel with the axis of the core shaft, and the second liquid inlet and outlet interface extends to the right in parallel with the axis of the core shaft.

[0021] The first gas flow passages at each first liquid inlet and outlet interface are blocked by a sealing strip.

[0022] Each first liquid inlet and outlet interface is the same interface, and each second liquid inlet and outlet interface is the same interface.

[0023] The liquid conveying belt comprises two heat-conducting thin belts arranged in parallel and a liquid sealing strip sealed between the side edges of the two heat-conducting thin belts, and the spiral liquid channel is formed between the liquid sealing strip and the two heat-conducting thin belts.

[0024] At least one of the heat-conducting thin strips is integrally provided with a plurality of stamping protrusions located in the spiral fluid channel and supported between the two heat-conducting thin strips and distributed at intervals.

[0025] At least one of the heat-conducting thin strips is integrally provided with a plurality of stamped protrusions distributed at intervals, which are located in the first gas flow channel and supported between two adjacent liquid flow tapes; at least one of the heat-conducting thin strips is integrally provided with a plurality of stamped protrusions distributed at intervals, which are located in the second gas flow channel and supported between two adjacent spiral coils.

[0026] The first air flow channel is provided with an air duct support member sandwiched between two adjacent liquid-carrying coils, and the second air flow channel is provided with an air duct support member sandwiched between two adjacent spiral coils.

[0027] The air duct support is a plurality of ventilation pipes parallel to the core shaft, and each ventilation pipe is closely arranged along the spiral direction of the first air duct or the second air duct.

[0028] The air duct support is a corrugated board, which includes a plurality of corrugated peaks and a plurality of corrugated valleys arranged alternately in sequence along the spiral direction of the first air duct or the second air duct, and the length of each corrugated peak and each corrugated valley is extended parallel to the axis of the core shaft.

[0029] The spiral tape is wound around the outer periphery of the core shaft in a non-circular spiral shape.

[0030] The spiral tape is wound around the outer periphery of the core shaft in an elliptical spiral shape.

[0031] A heat exchange device comprises at least two heat exchangers of the above structure, wherein the core shafts of the heat exchangers are arranged coaxially, and the first liquid inlet and outlet interfaces or the second liquid inlet and outlet interfaces of any two adjacent heat exchangers are butted against each other.

[0032] The core shaft is a hollow tube with an axial through hole, and a pull rod with external threads at both ends is passed through the axial through hole. Both ends of the pull rod are respectively threadedly connected to locking nuts for axially clamping each spiral heat exchanger.

[0033] Each of the heat exchangers comprises a cylindrical shell coaxially arranged on the periphery of the spiral coil, and the cylindrical shells of any two adjacent heat exchangers are sealed and abutted.

[0034] An axially penetrating through hole is provided between the cylindrical shell and the spiral coil. The through holes on each heat exchanger are coaxially arranged and a liquid inlet pipe connected to the first inlet and outlet liquid interface or the second inlet and outlet liquid interface of one of the endmost heat exchangers is provided therein.

[0035] Beneficial effects of this application:

[0036] 1. The spiral coil wound around the core shaft in a spiral shape is composed of multiple parallel and spaced spiral liquid-carrying coils. In actual application, each liquid-carrying coil can flow liquid independently, so that multiple heat exchange liquids can be introduced into the heat exchanger, thereby improving the liquid flow and heat exchange capacity of the heat exchanger, overcoming the defects of large flow resistance and small flow rate of single liquid-path heat exchangers. Multiple liquid-carrying coils will only increase the radial size of the heat exchanger, making full use of the radial size of the heat exchanger to increase the heat exchange, which is very suitable for application environments with sufficient radial space.

[0037] 2. The spiral winding tape is composed of multiple liquid-carrying tapes with spiral liquid channels inside. Each liquid-carrying tape is parallel to each other and spaced apart in the radial direction of the core shaft, so that a spiral-shaped gas flow channel that runs left and right is formed between the two liquid-carrying tapes. The spiral winding tapes of any two adjacent layers are also separated by a certain distance, so that a spiral-shaped gas flow channel that runs left and right is also formed between the spiral winding tapes of adjacent layers. The gas flow channel in the heat exchanger is a spiral flow channel that runs left and right. The spiral flow channel is set to provide sufficient heat exchange area, but its movement path is from the left end face of the liquid-carrying tape to the right end face of the liquid-carrying tape. The movement direction is parallel to the plane of the spiral flow channel. The gas flow resistance is small, and the gas flow channel is easy to clean.

[0038] 3. The lengths of the liquid coils are set to be equal so that the outflow temperatures of the liquid flows are close to each other, and thus the outflow temperatures of the "two paths" of gas that exchange heat with the two liquid flows are also very close.

[0039] 4. The liquid inlet and outlet interfaces of a single heat exchanger are arranged on both sides of the heat exchanger in the axial direction and extend in the axial direction, so that the liquid inlet and outlet interfaces are always located within the radial range of the heat exchanger, which does not increase the installation space required for the heat exchanger in the radial direction, and is also conducive to the axial connection of multiple heat exchangers. When multiple heat exchangers of this structure are connected in series in the axial direction to form a larger heat exchange device, the heat exchanged gas flows in the axial direction of the heat exchange device, and the liquid in each single heat exchanger flows in reverse spirals in the axial arrangement direction, so that the device has uniform discharge temperature and exhaust temperature at the same time, which is particularly suitable for applications that have high requirements for the uniformity of discharge temperature or exhaust temperature.

[0040] 5. Multiple heat exchangers of this structure can be infinitely connected and expanded in series along the axial direction, so as to "extract" as much heat or cold as possible from the heat exchange liquid, thereby making the air temperature discharged from the heat exchange device infinitely close to the inlet temperature of the heat exchange liquid, and the expanded heat exchange device will not occupy radial space in the environment. Of course, this method can also "extract" as much heat or cold as possible from the heat exchange gas, thereby making the liquid flow temperature discharged from the heat exchange device infinitely close to the inlet temperature of the heat exchange gas.

[0041] 6. The heat exchange efficiency of a heat exchange device composed of multiple single heat exchangers is determined by the total number of single heat exchangers. Therefore, the heat exchange efficiency of each single heat exchanger itself is reduced. Therefore, the number of winding circles of the coiled tape of the single heat exchanger can be appropriately reduced during production. In this way, due to the small single radial dimension, multiple heat exchangers are connected in series along the axial direction to form a tubular heat exchange device, which can be concealedly installed in the corners of the wall without providing a special installation space for installation.

[0042] 7. The number of windings of the coil on a single heat exchanger is small, which means that the spiral fluid movement stroke in the coil is short. Compared with the background technology, when a blockage occurs, it is easier to clean the blockage along the spiral direction. Even if a single heat exchanger in the heat exchange device is blocked, the blocked single heat exchanger can be removed and replaced with a spare heat exchanger that can be used normally to continue working, so as not to affect the normal use of the heat exchange device.

[0043] 8. The core shaft can not only support the outer spiral winding belt, but also be provided with an axial through hole therein to pass through a tie rod with nuts screwed at both ends, so that multiple single heat exchangers can be axially tightened and fixed by the tie rod, thereby improving the assembly convenience and structural integrity of the heat exchange device. BRIEF DESCRIPTION OF THE DRAWINGS

[0044] In order to more clearly illustrate the technical solutions of the embodiments of the present application, the drawings of the embodiments will be briefly introduced below. Obviously, the drawings in the following description only relate to some embodiments of the present application, rather than limiting the present application.

[0045] Figure 1It is a schematic diagram of the left end surface of the heat exchanger in Example 1 of the present application after the outer shell is removed.

[0046] Figure 2 It is a schematic diagram of the right end surface of the heat exchanger in Example 1 of the present application after the outer shell is removed.

[0047] Figure 3 It is a schematic diagram of the three-dimensional structure of the heat exchanger in Example 1 of the present application, used to show the left end surface.

[0048] Figure 4 It is a schematic diagram of the three-dimensional structure of the heat exchanger in Example 1 of the present application, used to show the right end surface.

[0049] Figure 5 It is a schematic diagram of the three-dimensional structure of the heat exchange device in Example 1 of the present application.

[0050] Figure 6 It is a schematic diagram of the cross-sectional structure of the heat exchange device in Example 1 of the present application.

[0051] Figure 7 yes Figure 5 Exploded diagram of .

[0052] Figure 8 It is a schematic diagram of the left end surface of the heat exchanger in Example 2 of the present application after the outer shell is removed.

[0053] Fig. 9 It is a schematic diagram of the right end surface of the heat exchanger in Example 2 of the present application after the outer shell is removed.

[0054] To facilitate composition, Figure 5 and Figure 6 The stamping protrusions on the thermal conductive tape are hidden. Figures 4 to 8 The mandrel is hidden in the middle.

[0055] in:

[0056] 1- mandrel, 2- spiral winding tape, 3- second gas flow channel, 4- first inlet and outlet liquid interface, 5- second inlet and outlet liquid interface, 6- tie rod, 7- locking nut, 8- shell, 9- liquid introduction tube, 10- perforation;

[0057] 101 - axial through hole, 201 - liquid conveying belt, 202 - first gas flow channel, 2011 - spiral liquid channel, 2012 - heat conductive thin belt, 2013 - liquid sealing strip, 2012a - stamping protrusion. DETAILED DESCRIPTION

[0058] In order to make the purpose, technical scheme and advantages of the embodiment of the present application clearer, the technical scheme of the embodiment of the present application will be clearly and completely described in conjunction with the drawings of the embodiment of the present application. Obviously, the described embodiment is a part of the embodiment of the present application, not all of the embodiments. Based on the described embodiment of the present application, all other embodiments obtained by ordinary technicians in this field without creative work belong to the scope of protection of this application.

[0059] Unless otherwise defined, the technical terms or scientific terms used herein shall have the common meanings understood by persons with ordinary skills in the field to which this application belongs. The words "one" or "an" and the like used in the patent application specification and claims of this application do not indicate a quantity limitation, but indicate the existence of at least one.

[0060] In the description of the specification and claims of this application, the terms "upper", "lower", "horizontal", etc. indicate directions or positional relationships based on the directions or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present application and simplifying the description, rather than indicating or implying that the device or unit referred to must have a specific direction, be constructed and operated in a specific orientation, and therefore, should not be understood as a limitation on the present application.

[0061] The term "plurality" as used in the present specification and claims refers to two or more.

[0062] Now, specific embodiments of the present application are described with reference to the accompanying drawings.

[0063] Embodiment 1:

[0064] Reference Figures 1 to 4 As shown, the heat exchanger of this embodiment is mainly composed of a core shaft 1 and a spiral coil 2, wherein the spiral coil 2 is spirally wound around the core shaft 1 for two turns. In order to more conveniently describe the specific structure of the heat exchanger, the length direction of the core shaft 1 is now defined as the left-right direction, that is, the axis of the core shaft 1 extends left and right (extending from left to right).

[0065] The spiral coil 2 is mainly composed of two liquid-carrying belts 201 spirally wound around the core shaft 1 and having spiral liquid channels 2011 inside. The two liquid-carrying belts 201 are parallel to each other and arranged at intervals in the radial direction of the core shaft 1, so that a spiral first liquid-carrying channel 202 that runs left and right is formed between the two liquid-carrying belts 201. Any two adjacent layers of spiral coils 2 are separated by a certain distance, so that a spiral second liquid-carrying channel 3 that runs left and right is formed between the adjacent layers of spiral coils 2.

[0066] Each liquid-flowing coil 201 is provided with a first liquid inlet and outlet interface 4 extending to the left parallel to the axis of the mandrel 1 at the inner end in the spiral direction (i.e., the length direction), and each liquid-flowing coil 201 is provided with a second liquid inlet and outlet interface 5 extending to the right parallel to the axis of the mandrel 1 at the outer end in the spiral direction. The first liquid inlet and outlet interface 4 and the second liquid inlet and outlet interface 5 are interconnected through the spiral liquid channel 2011 in the coil. In actual application, the liquid (usually water or refrigerant liquid) sent to one of the liquid inlet and outlet interfaces will flow to the other liquid inlet and outlet interface along the spiral direction of the liquid-flowing coil 201 (also the spiral direction of the spiral liquid channel). At the same time, the gas that needs to be heated or cooled enters the first gas flow channel 202 and the second gas flow channel 3 from one axial side of the heat exchanger and flows from left to right or from right to left, and then flows out from the other axial side of the heat exchanger. And the gas flowing in the two gas flow channels and the liquid flowing in the liquid-flowing coil 201 undergo heat exchange due to the temperature difference, and the gas or liquid at the required temperature is obtained.

[0067] However, this heat exchanger has a relatively obvious disadvantage: if the first inlet and outlet interface 4 of the inner end of the liquid flow coil 201 is the liquid inlet, and the second inlet and outlet interface 5 is the liquid outlet, the liquid fed into the liquid flow coil is a low-temperature liquid lower than the air temperature in the flow channel. Because the liquid flows from the inside to the outside in the liquid flow coil 201, and continuously absorbs the heat of the gas in the ventilation pipe during the flow process, the liquid flow temperature in the liquid flow coil 201 increases from the inside to the outside. After the gas enters the two flow channels from one side of the heat exchanger axis, the liquid flow coil temperature contacted by the gas at different positions is different - the liquid flow coil temperature contacted by the outer gas is higher than the liquid flow coil temperature contacted by the inner gas. This results in that the temperature of the gas discharged from the other side of the heat exchanger axis is uneven, which cannot meet those applications that have high requirements for the temperature uniformity of the target gas.

[0068] Based on the above reasons, we can combine multiple heat exchangers of the above structure into Figure 5 and Figure 6 The methods shown are used in combination to form a heat exchange device capable of evenly discharging air. Figure 5 and Figure 6 In the embodiment, the core shafts 1 of the heat exchangers of the above structure are arranged coaxially, and the corresponding inlet and outlet interfaces of any two adjacent heat exchangers are connected to each other. Figure 5 and Figure 6 The four heat exchangers in the embodiment are called the first heat exchanger, the second heat exchanger, the third heat exchanger and the fourth heat exchanger from left to right. The second inlet and outlet liquid interface 5 at the right end of the first heat exchanger is connected to the second inlet and outlet liquid interface 5 at the left end of the second spiral heat exchanger, the first inlet and outlet liquid interface 4 at the right end of the second heat exchanger is connected to the first inlet and outlet liquid interface 4 at the left end of the third spiral heat exchanger, and the second inlet and outlet liquid interface 5 at the right end of the third heat exchanger is connected to the second inlet and outlet liquid interface 5 at the left end of the fourth spiral heat exchanger.

[0069] Through the above analysis, we already know that if the cryogenic liquid used for cooling flows from the inside to the outside in the heat exchanger along the spiral direction, the liquid temperature at the outer end is higher than the liquid temperature at the inner end. Obviously, if the cryogenic liquid flows from the outside to the inside in the heat exchanger along the spiral direction, the liquid temperature at the inner end is higher than the liquid temperature at the outer end. Figure 5 and Figure 6 In the first heat exchanger, the heat exchange liquid flows from the inside to the outside, the liquid temperature on the outside of the first heat exchanger is higher than the liquid temperature on the inside, and the heat release intensity of the air inside the first heat exchanger is greater than that of the surrounding air. In the second heat exchanger, the heat exchange liquid flows from the outside to the inside, the liquid temperature on the outside of the second heat exchanger is lower than the liquid temperature on the inside, and the heat release intensity of the air inside the second heat exchanger is lower than that of the surrounding air. In the third heat exchanger, the heat exchange liquid flows from the inside to the outside, the liquid temperature on the outside of the third heat exchanger is higher than the liquid temperature on the inside, and the heat release intensity of the air inside the third heat exchanger is greater than that of the surrounding air. In the fourth heat exchanger, the heat exchange liquid flows from the outside to the inside, the liquid temperature on the outside of the fourth heat exchanger is lower than the liquid temperature on the inside, and the heat release intensity of the air inside the fourth heat exchanger is lower than that of the surrounding air. So when the air is in Figure 5 and Figure 6 The air flows through the first, second, third and fourth heat exchangers from left to right in sequence, and the target air with relatively uniform temperature can be obtained, which is very suitable for air conditioning systems.

[0070] It is not difficult to understand that if the sizes and structures of the above four heat exchangers are exactly the same, the four can be easily connected according to Figure 5 and Figure 6 The heat exchangers are assembled together in the manner shown, and after the assembly is completed, the heat exchangers are arranged neatly and flush.

[0071] Refer to Figure 5 and Figure 6 As shown, in order to more conveniently connect the four heat exchangers tightly together, the core shaft 1 of each heat exchanger in this embodiment adopts a hollow tube structure with an axial through hole 101, and a tie rod 6 with external threads at both ends is passed through the axial through hole 101, and a locking nut 7 is threadedly connected to the two ends of the tie rod 6, so that each heat exchanger is axially clamped and fixed by means of the tie rod 6 and the two locking nuts 7.

[0072] Figure 5 and Figure 6 In the embodiment, each heat exchanger comprises a cylindrical shell 8 coaxially arranged on the periphery of the spiral coil 2 and fixed to the spiral coil. In order to minimize the axial gap between two adjacent heat exchangers to reduce gas leakage, the cylindrical shells 8 of any two adjacent heat exchangers are sealed and abutted in this embodiment.

[0073] In addition, an axially penetrating through hole 10 is provided between the cylindrical shell 8 and the spiral coil 2. The through holes 10 on each heat exchanger are coaxially arranged, and a liquid inlet pipe 9 connected to the first liquid inlet and outlet interface 4 of the rightmost heat exchanger is passed through these through holes, so that the liquid used for heat exchange can be introduced and discharged from the same axial side of the heat exchange device.

[0074] Considering that in actual application, the gas axially introduced into each inlet position of the heat exchanger flow channel usually has a consistent inflow temperature, and the liquid sent into the above two spiral liquid channels 2011 usually has a consistent inflow temperature and speed, and the outflow temperature of the two liquid flows mainly depends on the length of the liquid channel. Therefore, in this embodiment, the lengths of the two liquid flow coils 201 in the spiral direction are set to be equal, so that the outflow temperatures of the two liquid flows are close.

[0075] Obviously, the smaller the radial thickness of the liquid flow tape 201 - the flatter it is, the greater the heat exchange area and efficiency of the heat exchanger. However, it is very difficult to provide an axially extending inlet and outlet liquid interface on the flat liquid flow tape 201. Based on this, in this embodiment, seals 203 are provided at both ends of the length of the first flow channel 202 to block the first flow channel 202 at the position of the first inlet and outlet liquid interface 4 of the two liquid flow tapes 201, and to block the first flow channel 202 at the position of the second inlet and outlet liquid interface 5 of the two liquid flow tapes 201. In actual application, the heat exchange liquid can be passed as a whole to the positions of the two first inlet and outlet liquid interfaces 4 (or the two second inlet and outlet liquid interfaces). Since the first flow channel 202 at this location is blocked by the seal, there will be no problem of the supplied heat exchange liquid entering the first flow channel 202. This is equivalent to integrating the first inlet and outlet interfaces 4 of the two liquid conveying belts 201 into one main interface, and integrating the second inlet and outlet interfaces 5 of the two liquid conveying belts 201 into another main interface. In addition, this structural design also facilitates the centralized extraction of the heat exchange liquid in each liquid conveying belt 201.

[0076] The liquid conveying belt 201 in this embodiment includes two parallel thermal conductive thin belts 2012 and a sealing liquid strip 2013 sealed between the sides of the two thermal conductive thin belts. The spiral liquid channel 2011 is formed between the sealing liquid strip and the two thermal conductive thin belts.

[0077] It is not difficult to understand that the above-mentioned sealing strip 2013 can not only seal the liquid channel to prevent the liquid flow from leaking out, but also support the two heat-conducting thin strips 2012 of the liquid-flowing tape 201 to ensure that the two heat-conducting thin strips 2012 are separated by a certain distance to form a liquid flow channel. However, the supporting strength and supporting area of ​​the sealing strip 2013 for the two heat-conducting thin strips 2012 are limited. If the axial width of the liquid-flowing tape 201 is large, it is easy to cause the two heat-conducting thin strips 2012 to be close to each other and the flow channel to be blocked. Based on this, in this embodiment, a plurality of spaced stamping protrusions 2012a located in the spiral liquid channel 2011 and supported between the two heat-conducting thin strips 2012 are integrally provided on one of the heat-conducting thin strips 2012. The two heat-conducting thin strips 2012 are further supported by the densely distributed stamping protrusions 2012a, thereby ensuring that the spiral liquid channel structure is stable and not easy to collapse and block.

[0078] The thermal conductive thin strip 2012 is made of aluminum foil with a thickness of less than one millimeter. The thickness (or depth) of each spiral fluid channel 2011 in the fluid flow belt 201 and the distance between adjacent layers of the fluid flow belt 201 are only a few millimeters. The thin thermal conductive thin strip and thin fluid flow channel increase the heat exchange area and heat exchange efficiency of the cold and hot fluids.

[0079] In this embodiment, the spiral band 2 is wound around the mandrel 1 in a circular spiral shape, that is, the spiral band 2 is in a circular spiral shape, and a heat exchanger of this shape is easier to process and manufacture. In some other embodiments of the present application, the spiral band 2 is in a non-circular spiral shape, that is, the spiral band 2 can also be wound around the mandrel 1 in a non-circular spiral shape. Generally speaking, the aforementioned non-circular spiral is preferably an elliptical spiral. A heat exchanger of this shape has a flat appearance and is more beautiful, and can be arranged in a flat space, making full use of the flat space to maximize the heat exchange performance of the heat exchanger.

[0080] Embodiment 2:

[0081] Figure 8 and Fig. 9 The second specific embodiment of the heat exchanger of the present application is shown, which has a structure substantially the same as that of the first embodiment, except that:

[0082] In order to prevent the adjacent spiral coils 2 from sticking to each other and thus blocking the second airflow channel 3, this embodiment provides an airflow channel support member sandwiched between two adjacent spiral coils 2 in the second airflow channel 3. The airflow channel support member is another stamping protrusion 2012a integrally formed on the heat conductive thin strip 2012, which is arranged in a spaced relationship in the second airflow channel 3 and supported between two adjacent spiral coils 2.

[0083] In other embodiments of the present application, the above-mentioned air duct support member can also adopt other structural members such as ventilation pipes, corrugated boards, etc. When it is a ventilation pipe, each ventilation pipe needs to be closely arranged along the spiral direction of the second air flow channel 3 and parallel to the core shaft 1. When the air duct support member is a corrugated board sandwiched between two adjacent layers of spiral coils 2, it is best to arrange multiple flute peaks and multiple flute valleys of the corrugated board alternately in sequence along the spiral direction of the second air flow channel 3, and the length of each flute peak and each flute valley is extended parallel to the axis of the core shaft 1. It is beneficial to arrange the corrugated board used as the air duct support member in this way: the corrugated board is easy to bend in the arrangement direction of the flute peaks and flute valleys, and has strong bending resistance in the length extension direction of the flute peaks or flute valleys. By utilizing the aforementioned structural characteristics of the corrugated board, its corrugated peaks and corrugated valleys are arranged alternately in sequence along the spiral direction of the second airflow channel, which not only enables the corrugated board to be bent and arranged along the spiral direction, facilitating the processing and manufacturing of the heat exchanger, but also improves the bending strength of the main part of the heat exchanger.

[0084] Furthermore, in order to prevent the two liquid conveying belts from sticking to each other and causing the first liquid conveying channel 202 to be blocked, the present embodiment further provides a plurality of spaced-apart stamped protrusions 2012a on the thermal conductive tape 2012, which are located in the first liquid conveying channel 202 and supported between two adjacent liquid conveying belts 201. Obviously, the aforementioned stamped protrusions 2012a can also be replaced by ventilation pipes or corrugated boards.

Claims

1. A heat exchanger, characterized in that: include: A core shaft (1) with its axis extending left and right, and A spiral coil (2) spirally wound around the core shaft (1) for at least 2 turns; The spiral coil (2) comprises a plurality of liquid-carrying belts (201) spirally wound around the outside of the core shaft and having spiral liquid channels (2011) inside, the plurality of liquid-carrying belts (201) being parallel to each other and arranged at intervals in the radial direction of the core shaft (1), so that a first spiral air flow channel (202) penetrating from left to right is formed between the plurality of liquid-carrying belts (201), and the first air flow channel (202) is provided with an air channel support member; The spiral winding tapes (2) of any two adjacent layers are separated by a certain distance, so that a spiral second air flow channel (3) that passes through the adjacent layers is formed between the spiral winding tapes (2); The liquid conveying coil (201) comprises two heat-conducting thin strips (2012) arranged in parallel and a liquid sealing strip (2013) sealed between the side edges of the two heat-conducting thin strips, and the spiral liquid channel (2011) is formed between the liquid sealing strip and the two heat-conducting thin strips.

2. The heat exchanger according to claim 1, characterized in that: Each liquid conveying coil (201) is provided with a first liquid inlet and outlet interface (4) at its inner end in the spiral direction, and each liquid conveying coil (201) is provided with a second liquid inlet and outlet interface (5) at its outer end in the spiral direction.

3. The heat exchanger according to claim 2, characterized in that: The lengths of the plurality of liquid conveying belts (201) in the spiral direction are equal.

4. The heat exchanger according to claim 2, characterized in that: The first liquid inlet and outlet interface (4) extends to the left in parallel with the axis of the core shaft (1), and the second liquid inlet and outlet interface (5) extends to the right in parallel with the axis of the core shaft (1).

5. The heat exchanger according to claim 2, characterized in that: The first gas flow passage (202) at each first liquid inlet and outlet interface (4) is blocked by a sealing strip (203).

6. The heat exchanger according to claim 5, characterized in that The first liquid inlet and outlet interfaces (4) are the same interface, and the second liquid inlet and outlet interfaces (5) are the same interface.

7. The heat exchanger according to claim 1, characterized in that At least one of the heat-conducting thin strips (2012) is integrally provided with a plurality of stamping protrusions (2012a) located in the spiral liquid channel (2011) and supported between the two heat-conducting thin strips (2012) and distributed at intervals.

8. The heat exchanger according to claim 1, characterized in that At least one of the heat-conducting thin strips (2012) is integrally provided with a plurality of stamped protrusions (2012a) distributed at intervals and located in the first liquid flow channel (202) and supported between two adjacent liquid flow coils (201); at least one of the heat-conducting thin strips (2012) is integrally provided with a plurality of stamped protrusions (2012a) distributed at intervals and located in the second liquid flow channel (3) and supported between two adjacent spiral coils (2).

9. The heat exchanger according to claim 1, characterized in that: The first air flow channel (202) is provided with an air channel support member sandwiched between two adjacent liquid flow coils (201), and the second air flow channel (3) is provided with an air channel support member sandwiched between two adjacent spiral coils (2).

10. The heat exchanger according to claim 9, characterized in that The air duct support is a plurality of ventilation pipes parallel to the core shaft (1), and each ventilation pipe is closely arranged along the spiral direction of the first air duct (202) or the second air duct (3).

11. The heat exchanger according to claim 9, characterized in that The air duct support member is a corrugated board, which includes a plurality of corrugated peaks and a plurality of corrugated valleys arranged alternately in sequence along the spiral direction of the first air duct or the second air duct, and the length of each corrugated peak and each corrugated valley is extended and arranged parallel to the axis of the core shaft (1).

12. The heat exchanger according to claim 9, characterized in that The spiral winding tape (2) is wound around the periphery of the core shaft (1) in a non-circular spiral shape.

13. The heat exchanger according to claim 12, characterized in that The spiral winding tape (2) is wound in an elliptical spiral shape around the periphery of the core shaft (1).

14. A heat exchange device, characterized in that: It comprises at least two heat exchangers as claimed in claim 4, wherein the core shafts (1) of the heat exchangers are coaxially arranged, and the first inlet and outlet liquid interfaces (4) or the second inlet and outlet liquid interfaces (5) of any two adjacent heat exchangers are butted against each other.

15. The heat exchange device according to claim 14, characterized in that: The core shaft (1) is a hollow tube with an axial through hole (101), and a pull rod (6) with external threads at both ends is passed through the axial through hole (101). The two ends of the pull rod (6) are respectively threadedly connected to locking nuts (7) for axially clamping each of the heat exchangers.

16. The heat exchange device according to claim 14, characterized in that: Each of the heat exchangers comprises a cylindrical outer shell (8) coaxially arranged on the periphery of the spiral coil (2), and the cylindrical outer shells (8) of any two adjacent heat exchangers are sealed and abutted.

17. The heat exchange device according to claim 16, characterized in that: An axially penetrating through hole (10) is provided between the cylindrical shell (8) and the spiral coil (2); the through holes (10) on each heat exchanger are coaxially arranged and have a liquid inlet pipe (9) connected to a first liquid inlet and outlet interface (4) or a second liquid inlet and outlet interface (5) of one of the endmost heat exchangers.

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