CN214199793U

CN214199793U - Heat exchanger and heat exchange device

Info

Publication number: CN214199793U
Application number: CN202022859737.2U
Authority: CN
Inventors: 高峰; 刘在祥; 陈艳凤; 蔡园丰; 王兵; 牛争艳
Original assignee: Shanghai Xingye Material Technology Co Ltd
Current assignee: Shanghai Xingye Material Technology Co Ltd
Priority date: 2020-12-02
Filing date: 2020-12-02
Publication date: 2021-09-14
Anticipated expiration: 2030-12-02

Abstract

The application relates to a heat exchanger and heat transfer device, the heat exchanger includes: the mandrel extends left and right along the axis and is spirally wound on the periphery of the mandrel for at least 2 circles of spiral winding tape; the spiral winding belt comprises a plurality of liquid-running winding belts which spirally surround the mandrel and are internally provided with spiral liquid channels, the liquid-running winding belts are parallel to each other and are arranged at intervals in the radial direction of the mandrel, and therefore a first air-running channel which is communicated left and right is formed among the liquid-running winding belts; the spiral winding belts of any two adjacent turns are separated by a certain distance, so that a spiral second air passing flow passage which is communicated from left to right is formed between the spiral winding belts of the adjacent turns. The heat exchanger has large heat exchange amount and high heat exchange efficiency.

Description

Heat exchanger and heat exchange device

Technical Field

The application relates to the field of heat exchange, in particular to a heat exchanger and a heat exchange device.

Background

The heat exchanger is equipment for transferring heat of hot fluid to cold fluid, the heat exchanger is mainly applied to life and industrial production, and the traditional heat exchanger generally occupies a large area due to pursuing a larger heat exchange area, so that the heat exchanger has the defects of higher requirement on installation space, inconvenience in maintenance and the like. Therefore, on the premise of ensuring that the heat exchange area is sufficient, how to reduce the size of the heat exchanger is a problem which needs to be solved urgently in the industry.

The utility model discloses a chinese utility model patent with publication number 204495135U discloses a novel spiral plate type reaction heat exchanger, including first sheet metal, the second sheet metal, intermediate bottom and outer barrel, wherein first sheet metal and second sheet metal interval winding constitution double helix shape barrel, intermediate bottom is connected with the first sheet metal and the second sheet metal tip that is close to spiral center department respectively, and separate double helix barrel into two spaces that do not mutually interfere, one of them space is the hot fluid passageway of operation hot fluid (hot-medium entering chamber), another space is the cold fluid passageway of operation cold fluid (cold-medium entering chamber), hot fluid passageway and cold fluid passageway interval distribution, hot fluid passageway and cold fluid passageway are provided with hot fluid import and cold fluid export respectively near spiral center department, hot fluid passageway and cold fluid passageway are provided with hot fluid export and cold fluid import respectively in the position of periphery, when heat exchange is carried out, the surface areas of the first thin plate and the second thin plate are the heat exchange areas of cold and hot fluids, so that the sufficiency of the heat exchange areas is ensured, and meanwhile, the size of the heat exchanger can be effectively reduced due to the arrangement of the double-spiral cylinder. However, the spiral plate type reaction heat exchanger in the patent document has the following disadvantages:

1. the flow resistance is large. The hot fluid and the cold fluid respectively move in the hot fluid flow channel and the cold fluid flow channel along the spiral curling direction for a long distance, the moving direction of the fluid is changed at any moment in the moving process, and a large interaction force can be generated between the thin plate and the heat exchange fluid, so that the flowing resistance of the fluid in the flow channels is large, and the heat exchange fluid is not suitable for the heat exchange of gaseous fluid.

2. The maintenance frequency is high. Although the flow channel of the hot fluid is in a spiral winding shape, the hot fluid is still substantially a space, namely the hot fluid is conveyed in a single flow channel, and the cold fluid flow channel and the cold fluid are conveyed in the same way. By way of example, the single flow channel has the problems that if a certain position of the hot fluid flow channel is blocked, the conveying of the hot fluid in the whole hot fluid flow channel is influenced, the hot fluid cannot be conveyed seriously, so that the heat exchanger cannot work normally, namely, as long as the hot fluid flow channel is blocked at one position, a worker needs to maintain the heat exchanger, and the maintenance frequency is high.

3. This kind of heat exchanger is multilayer spiral winding structure, in order to carry out abundant heat transfer, obtain higher heat exchange efficiency, this structure can twine the multilayer usually for radial size is too big, when the heat exchanger is installed, need provide great radial space and be used for installing the heat exchanger, this can't realize the concealed installation of heat exchanger in the limited occasion in some radial spaces.

4. As described above, in order to perform sufficient heat exchange and obtain high heat exchange efficiency, the structure is usually wound with multiple layers to increase the movement stroke of the internal fluid, and due to the spiral flow channel, the internal resistance is high, so that when blockage occurs, the blockage is difficult to clean.

5. The heat exchanger is of a single-channel structure, and when the heat exchanger is actually applied, a cold fluid and a hot fluid respectively only have one channel, so that the amount of fluid is small, the heat exchange amount is small, and the heat exchange capacity (temperature rising or temperature lowering capacity) is insufficient. If the sectional area of the spiral flow channel is increased to improve the flow rate of the fluid, the heat exchange area of the heat exchanger with the same size is greatly reduced, namely, the heat exchanger is known as 26911and the heat exchanger is also known as a bead.

The present application is hereby presented.

Disclosure of Invention

The technical problem that this application will solve is: in order to solve the problems, the heat exchanger with large heat exchange amount and high heat exchange efficiency and the heat exchange device formed by combining the heat exchangers are provided.

The technical scheme of the application is as follows:

a heat exchanger, comprising:

a mandrel having its axis extending to the left and right, an

The spiral winding tape is spirally wound on the periphery of the mandrel for at least 2 circles;

the spiral winding belt comprises a plurality of liquid-running winding belts which spirally surround the mandrel and are internally provided with spiral liquid channels, the liquid-running winding belts are parallel to each other and are arranged at intervals in the radial direction of the mandrel, and therefore a first air-running channel which is communicated left and right is formed among the liquid-running winding belts;

the spiral winding belts of any two adjacent turns are separated by a certain distance, so that a spiral second air passing flow passage which is communicated from left to right is formed between the spiral winding belts of the adjacent turns.

On the basis of the technical scheme, the application also comprises the following preferable scheme:

and a first liquid inlet and outlet port is arranged at the inner side end of each liquid walking winding tape in the spiral direction, and a second liquid inlet and outlet port is arranged at the outer side end of each liquid walking winding tape in the spiral direction.

The lengths of the liquid-walking winding belts in the spiral direction are equal.

The first liquid inlet and outlet interface is parallel to the axis of the mandrel and extends leftwards, and the second liquid inlet and outlet interface is parallel to the axis of the mandrel and extends rightwards.

The first air flow passage at each first liquid inlet and outlet interface is sealed by a seal.

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

The liquid-flowing winding belt comprises two parallel heat-conducting thin belts and a liquid sealing strip arranged between the two sides of the two heat-conducting thin belts in a sealing mode, and the spiral liquid channel is formed between the liquid sealing strip and the two heat-conducting thin belts.

And a plurality of stamping protrusions which are arranged in the spiral liquid channel and supported between the two heat-conducting thin strips and distributed at intervals are integrally arranged on at least one of the heat-conducting thin strips.

A plurality of stamping bulges which are distributed at intervals and are positioned in the first air flowing channel and supported between the two adjacent liquid flowing winding belts are integrally arranged on at least one of the heat conducting thin belts, and a plurality of stamping bulges which are distributed at intervals and are positioned in the second air flowing channel and supported between the spiral winding belts of the two adjacent circles are integrally arranged on at least one of the heat conducting thin belts.

The first air channel is provided with an air channel supporting piece clamped between two adjacent liquid-passing winding belts, and the second air channel is provided with an air channel supporting piece clamped between two adjacent spiral winding belts.

The air duct supporting piece is a plurality of ventilation pipes parallel to the core shaft, and the ventilation pipes are closely arranged along the spiral direction of the first air passing flow passage or the second air passing flow passage.

The wind channel support piece is corrugated sheet, corrugated sheet includes along first air flow way or the second air flow way's the spiral direction is walked many stupefied peaks and many stupefied valleys of arranging in proper order in turn, and the length of every stupefied peak and every stupefied valley all is on a parallel with the axis extension setting of dabber.

The spiral winding belt is wound on the periphery of the mandrel in a non-circular spiral shape.

The spiral winding belt is spirally wound on the periphery of the mandrel in an oval shape.

A heat exchange device comprises at least two heat exchangers with the structure, wherein mandrels of the heat exchangers are coaxially arranged, and a first liquid inlet and outlet interface or a second liquid inlet and outlet interface of any two adjacent heat exchangers are mutually butted.

The mandrel is a hollow pipe with an axial through hole, a pull rod with outer threads at two ends penetrates through the axial through hole, and two ends of the pull rod are respectively in threaded connection with a locking nut which clamps each heat exchanger axially.

Each heat exchanger comprises a cylindrical shell coaxially arranged on the periphery of the spiral winding belt, and the cylindrical shells of any two adjacent heat exchangers are in sealing butt joint.

And a through hole which is axially communicated is arranged between the cylindrical shell and the spiral winding belt, and the through hole on each heat exchanger is coaxially arranged and internally provided with a liquid guide pipe which is connected with the first liquid inlet and outlet interface or the second liquid inlet and outlet interface of one heat exchanger at the most end side.

The beneficial effect of this application:

1. the spiral winding belt wound outside the mandrel in the spiral mode is formed by a plurality of parallel spaced spiral liquid-running winding belts, and when the spiral winding belt is applied practically, each liquid-running winding belt can independently run liquid, so that multi-path heat exchange liquid can be introduced into the heat exchanger, the liquid-running amount and the heat exchange capacity of the heat exchanger are improved, and the defects of large flow resistance, small flow and the like of a single-liquid-path heat exchanger are overcome. The radial size of the heat exchanger can be increased only by the aid of the multi-liquid-running winding tape, heat exchange quantity is improved by fully utilizing the radial size of the heat exchanger, and the heat exchanger is very suitable for application environments with sufficient radial space.

2. The spiral winding belt is composed of a plurality of liquid-running winding belts with spiral liquid channels inside, and each liquid-running winding belt is parallel to each other and arranged at intervals in the radial direction of the mandrel, so that a spiral air-running channel which is communicated from left to right is formed between the two liquid-running winding belts. The spiral winding tapes of any two adjacent circles are also separated by a certain distance, so that a spiral air passage which is communicated from left to right is also formed between the spiral winding tapes of the adjacent circles. The gas flow channel in the heat exchanger is a spiral flow channel which is communicated from left to right, wherein the spiral flow channel is arranged to provide sufficient heat exchange area, but the moving path of the gas flow channel is from the left end surface of the liquid-walking winding tape to the right end surface of the liquid-walking winding tape, the moving direction of the gas flow channel is parallel to the plane of the spiral flow channel, the gas flow resistance is small, and the cleaning difficulty of the gas flow channel is low.

3. The lengths of the liquid-carrying winding belts are set to be equal, so that the outflow temperature of each path of liquid flow is close to that of the other path of liquid flow, and the outflow temperature of the two paths of gas which exchange heat with the two paths of liquid flow is also very close to that of the other path of gas.

4. The liquid inlet interface and the liquid outlet interface of a single heat exchanger are arranged on two axial sides of the heat exchanger and extend out along the axial direction, so that the liquid inlet interface and the liquid outlet interface are always positioned in the radial range of the heat exchanger, the mounting space of the heat exchanger required in the radial direction can not be increased, and meanwhile, the heat exchangers are beneficial to being connected in series along the axial direction. After a plurality of heat exchangers with the structure are axially connected in series to form a larger heat exchange device, heat exchange gas flows axially along the heat exchange device, and liquid in each single heat exchanger flows in a reverse spiral mode along the axial arrangement direction in sequence, so that the device has uniform liquid discharge temperature and uniform exhaust temperature, and is particularly suitable for application occasions with high requirements on the uniformity of the liquid discharge temperature or the exhaust temperature.

5. The heat exchangers with the structure can be infinitely extended in series along the axial direction, so that heat or cold of the heat exchange liquid can be extracted as much as possible, the temperature of air discharged from the heat exchange device is infinitely close to the inflow temperature of the heat exchange liquid, and the heat exchange device obtained by extension does not occupy radial space in the environment. Of course, this approach also allows as much heat or cold as possible to be "squeezed" from the heat exchange air, thereby allowing the temperature of the liquid stream exiting the heat exchange device to approach the temperature of the incoming heat exchange air indefinitely.

6. The heat exchange efficiency of the heat exchange device formed by combining the plurality of single heat exchangers is determined by the total number of the single heat exchangers, so that the heat exchange efficiency of each single heat exchanger is reduced, the winding number of turns of the single heat exchanger during production can be properly reduced, and the heat exchange device can be arranged at the corner of a wall in a concealed mode in a manner that the plurality of heat exchangers are connected in series along the axial direction and form a tubular shape due to the fact that the single radial size is small, and special installation space is not required to be provided for installation.

7. The winding number of turns of the winding belt on a single heat exchanger is small, which means that the movement stroke of the spiral fluid in the winding belt is short, and compared with the background technology, the difficulty of cleaning the blockage along the spiral direction is low when the blockage occurs. Even if certain monomer heat exchanger takes place the jam among the heat transfer device, can dismantle the monomer heat exchanger that blocks up, but the heat exchanger that changes the reserve normal use continues work to do not influence heat transfer device's normal use.

8. The dabber can enough support outlying spiral rolling band, can set up the pull rod of axial through-hole in order to wear to establish both ends spiro union nut again in it to utilize the pull rod with a plurality of monomer heat exchangers axial tensioning fixed, promoted heat transfer device's assembly convenience and structural integrity.

Drawings

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, and it is apparent that the drawings in the following description only relate to some embodiments of the present application and are not limiting on the present application.

Fig. 1 is a schematic left end view of a heat exchanger according to an embodiment of the present application with an outer shell removed.

Fig. 2 is a schematic right end view of a heat exchanger according to an embodiment of the present application with a housing removed.

Fig. 3 is a schematic perspective view of a heat exchanger according to a first embodiment of the present application, which is used for showing a left end face.

Fig. 4 is a schematic perspective view of a heat exchanger according to a first embodiment of the present application, which is used for showing a right end face.

Fig. 5 is a schematic perspective view of a heat exchange device according to a first embodiment of the present application.

Fig. 6 is a schematic cross-sectional structure view of a heat exchange device in an embodiment of the present application.

Fig. 7 is an exploded view of fig. 5.

Fig. 8 is a schematic left end view of a heat exchanger according to a second embodiment of the present application with an outer shell removed.

Fig. 9 is a right end view of the heat exchanger of the second embodiment of the present application with the outer shell removed.

For convenience of patterning, the stamping protrusions on the thin heat-conductive strip are hidden in fig. 5 and 6, and the mandrel is hidden in fig. 4 to 8.

Wherein:

1-mandrel, 2-spiral winding belt, 3-second gas flow channel, 4-first liquid inlet and outlet interface, 5-second liquid inlet and outlet interface, 6-pull rod, 7-locking nut, 8-shell, 9-liquid guiding pipe and 10-perforation;

101-axial through hole, 201-liquid running winding, 202-first gas flow channel, 2011-spiral liquid channel, 2012-heat conducting thin strip, 2013-liquid sealing strip, 2012 a-stamping protrusion.

Detailed Description

In order to make the objects, technical solutions and advantages of the embodiments of the present application clearer, the technical solutions of the embodiments of the present application will be clearly and completely described below with reference to the drawings of the embodiments of the present application. It should be apparent that the described embodiments are only some of the embodiments of the present application, and not all embodiments. All other embodiments, which can be derived by a person skilled in the art from the described embodiments of the application without any inventive step, are within the scope of protection of the application.

Unless defined otherwise, technical or scientific terms used herein shall have the ordinary meaning as understood by one of ordinary skill in the art to which this application belongs. The use of the terms "a" or "an" and the like in the description and in the claims of the present application do not denote a limitation of quantity, but rather denote the presence of at least one.

In the description of the present specification and claims, the terms "upper", "lower", "horizontal", and the like indicate orientations or positional relationships based on those shown in the drawings, and are only for convenience of describing the present application and simplifying the description, but do not indicate or imply that the referred device or unit must have a specific direction, be constructed in a specific orientation, and be operated, and thus, should not be construed as limiting the present application.

The term "plurality" as used herein and in the appended claims means two or more.

Specific embodiments of the present application will now be described with reference to the accompanying drawings.

The first embodiment is as follows:

referring to fig. 1 to 4, the heat exchanger of the present embodiment is mainly composed of a mandrel 1 and a spiral winding tape 2, wherein the spiral winding tape 2 is spirally wound around the mandrel 1 for two turns. In order to be able to describe the specific structure of the heat exchanger more conveniently, the longitudinal direction of the mandrel 1 is defined as the left-right direction, that is, the axis of the mandrel 1 extends left and right (extends from left to right).

The spiral winding tape 2 mainly comprises two liquid-running winding tapes 201 which spirally surround the mandrel 1 and are internally provided with spiral liquid channels 2011, and the two liquid-running winding tapes 201 are parallel to each other and are arranged at intervals in the radial direction of the mandrel 1, so that a first left-right through spiral air-running channel 202 is formed between the two liquid-running winding tapes 201. The spiral winding belts 2 of any two adjacent turns are separated by a certain distance, so that a spiral second air flow passage 3 which is communicated from left to right is formed between the spiral winding belts 2 of the adjacent turns.

A first liquid inlet and outlet port 4 extending leftwards and parallel to the axis of the mandrel 1 is arranged at the inner side end of each liquid walking winding tape 201 in the spiral direction (namely the length direction), and a second liquid inlet and outlet port 5 extending rightwards and parallel to the axis of the mandrel 1 is arranged at the outer side end of each liquid walking winding tape 201 in the spiral direction. The first liquid inlet and outlet port 4 and the second liquid inlet and outlet port 5 are communicated with each other through a spiral liquid channel 2011 in the winding belt. In practical applications, the liquid (usually water or refrigerant liquid) fed into one of the liquid inlet and outlet ports flows to the other liquid inlet and outlet port along the spiral direction of the liquid carrying tape 201 (also the spiral direction of the spiral liquid channel). Meanwhile, the gas to be heated or cooled flows into the first air flow passage 202 and the second air flow passage 3 from left to right or from right to left from one axial side of the heat exchanger, and then flows out from the other axial side of the heat exchanger. And the gas flowing in the two gas channels and the liquid flowing in the liquid-carrying coiling tape 201 exchange heat due to the temperature difference, so as to obtain the gas or the liquid with the required temperature.

However, this type of heat exchanger has a significant disadvantage: if the first liquid inlet and outlet port 4 at the inner side end of the liquid-moving winding tape 201 is a liquid inlet and the second liquid inlet and outlet port 5 is a liquid outlet, the liquid fed into the liquid-moving winding tape is low-temperature liquid with the temperature lower than the temperature of the air in the air-moving flow passage. Because the liquid flows from inside to outside in the liquid-moving winding tape 201 and continuously absorbs the heat of the gas in the ventilation pipe in the flowing process, the liquid flow temperature in the liquid-moving winding tape 201 increases gradually from inside to outside. After gas enters the two gas-passing flow passages from one axial side of the heat exchanger, the liquid-passing winding belts contacted by the gas at different positions have different temperatures, namely the temperature of the liquid-passing winding belt contacted by the peripheral gas is higher than that of the liquid-passing winding belt contacted by the gas at the inner side. This results in uneven temperature of the gas discharged from the other side of the heat exchanger axis, failing to meet those applications where high requirements are placed on the temperature uniformity of the target gas.

For the reasons, a plurality of heat exchangers with the structures can be combined and used according to the mode shown in fig. 5 and fig. 6, so that the heat exchange device capable of uniformly discharging air is formed. In fig. 5 and 6, the mandrels 1 of the heat exchangers with the above structures are coaxially arranged, and the corresponding liquid inlet and outlet ports of any two adjacent heat exchangers are mutually butted. For convenience of description, the four heat exchangers in fig. 5 and 6 are referred to as a first heat exchanger, a second heat exchanger, a third heat exchanger and a fourth heat exchanger from left to right in sequence, a second liquid inlet and outlet interface 5 at the right end of the first heat exchanger is in butt joint with a second liquid inlet and outlet interface 5 at the left end of the second heat exchanger, a first liquid inlet and outlet interface 4 at the right end of the second heat exchanger is in butt joint with a first liquid inlet and outlet interface 4 at the left end of the third heat exchanger, and a second liquid inlet and outlet interface 5 at the right end of the third heat exchanger is in butt joint with a second liquid inlet and outlet interface 5 at the left end of the fourth heat exchanger.

From the above analysis we have known that if the cryogenic liquid used for temperature reduction flows in the heat exchanger from inside to outside in a spiral direction, the outside end liquid temperature is higher than the inside end liquid temperature. Obviously, if cryogenic liquid flows in the heat exchanger from outside to inside in a spiral direction, the inside end liquid temperature is higher than the outside end liquid temperature. In fig. 5 and 6, the heat exchange liquid in the first heat exchanger flows from inside to outside, the outside liquid temperature of the first heat exchanger is higher than the inside liquid temperature, and the heat release strength of the inside air in the first heat exchanger is higher than that of the outside air. The liquid for heat exchange in the second heat exchanger flows from outside to inside, the liquid temperature at the outer side of the second heat exchanger is lower than the liquid temperature at the inner side, and the heat release intensity of the air at the inner side in the second heat exchanger is lower than that of the air at the periphery. The liquid for heat exchange in the third heat exchanger flows from inside to outside, the liquid temperature at the outer side of the third heat exchanger is higher than the liquid temperature at the inner side, and the heat release intensity of the air at the inner side in the third heat exchanger is higher than that of the air at the periphery. The heat exchange liquid in the fourth heat exchanger flows from outside to inside, the liquid temperature at the outer side of the fourth heat exchanger is lower than the liquid temperature at the inner side, and the heat release intensity of the air at the inner side in the fourth heat exchanger is lower than that of the air at the periphery. When the air flows through the first, second, third and fourth heat exchangers in order from left to right in fig. 5 and 6, the target air having a relatively uniform temperature can be obtained, which is very suitable for an air conditioning system.

It will be appreciated that if the four heat exchangers are identical in size and configuration, they can be assembled together in a very convenient manner as shown in figures 5 and 6, and that after assembly the heat exchangers are arranged exactly flush.

Referring to fig. 5 and 6 again, in order to more conveniently and tightly connect the four heat exchangers together, the mandrel 1 of each heat exchanger in this embodiment adopts a hollow tube structure with an axial through hole 101, and a pull rod 6 with two ends provided with external threads penetrates through the axial through hole 101, and two ends of the pull rod 6 are respectively in threaded connection with a locking nut 7, so that each heat exchanger is axially clamped and fixed by means of the pull rod 6 and the two locking nuts 7.

In fig. 5 and 6, each heat exchanger comprises a cylindrical shell 8 coaxially arranged on the periphery of the helical coil 2 and fixed thereto. In order to minimize the axial gap between two adjacent heat exchangers and to reduce gas leakage, the present embodiment seals the cylindrical shells 8 of any two adjacent heat exchangers against each other.

And, the above-mentioned cylindrical shell 8 and spiral winding strip 2 have axial through-going perforation 10, the perforation 10 on each heat exchanger is arranged coaxially, and penetrate and have the liquid-guiding tube 9 linking with first business turn over liquid interface 4 of the heat exchanger of the rightmost end side in these perforations, so make the liquid used for heat exchange can be drawn in and drawn out from the same axial side of the heat exchanger rig.

Considering that in practical application, the gas axially introduced into each inlet of the gas flow passage of the heat exchanger generally has a uniform inflow temperature, the liquid introduced into the two spiral liquid passages 2011 generally has a uniform inflow temperature and velocity, and the outflow temperatures of the two liquid passages mainly depend on the lengths of the liquid passages. Therefore, in the present embodiment, the lengths of the two liquid-carrying winding tapes 201 in the spiral direction are set to be equal, so that the outflow temperatures of the two liquid flows are close to each other.

Obviously, the smaller the radial thickness of the wicking tape 201-the flatter, the greater the heat exchange area and efficiency of the heat exchanger. However, it is difficult to provide the axially extending liquid inlet/outlet port on the flat liquid running tape 201. Therefore, in the present embodiment, the sealing strips 203 are disposed at both ends of the length of the first air flow passage 202, so as to block the first air flow passage 202 at the position of the first liquid inlet/outlet port 4 of the two liquid-transporting tapes 201, and block the first air flow passage 202 at the position of the second liquid inlet/outlet port 5 of the two liquid-transporting tapes 201. In practical application, the heat exchange liquid can be entirely led to the two first liquid inlet/outlet ports 4 (or two second liquid inlet/outlet ports), and the first gas flow passage 20 at the position is blocked by the sealing strip, so that the problem that the supplied heat exchange liquid flows into the first gas flow passage 202 in a series manner is avoided. This is equivalent to integrating the first liquid inlet/outlet interfaces 4 of the two liquid-moving tapes 201 together into one common interface, and integrating the second liquid inlet/outlet interfaces 5 of the two liquid-moving tapes 201 together into another common interface. And the structural design also facilitates the concentrated extraction of the heat exchange liquid in each liquid-running winding tape 201.

The liquid-running tape 201 in this embodiment includes two heat-conducting thin tapes 2012 arranged in parallel and a liquid-sealing strip 2013 disposed between the two heat-conducting thin tapes, and the spiral liquid channel 2011 is formed between the liquid-sealing strip and the two heat-conducting thin tapes.

It is understood that the liquid sealing strip 2013 can not only seal the liquid channel to prevent the liquid from flowing out, but also support the two heat-conducting thin strips 2012 of the liquid-running winding 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 the supporting area of the liquid sealing strip 2013 for the two heat conductive thin strips 2012 are limited, and if the axial width of the liquid running tape 201 is large, the two heat conductive thin strips 2012 are close to each other, and the flow channel is easily blocked. Therefore, in the present embodiment, a plurality of stamping protrusions 2012a, which are located in the spiral liquid channel 2011 and are supported between two heat conductive thin strips 2012, are integrally disposed on one of the heat conductive thin strips 2012. The densely distributed stamping protrusions 2012a are used for further supporting the two heat-conducting thin strips 2012, so that the stable structure of the spiral liquid channel is ensured, and the spiral liquid channel is not easy to collapse and block.

The heat conductive thin strip 2012 is made of aluminum foil with a thickness less than one millimeter. The thickness (or called depth) of each spiral liquid channel 2011 in the liquid-transporting coiling belt 201 and the distance between adjacent layers of liquid-transporting coiling belts 201 are only several millimeters, and the thin heat-conducting thin belt and the thin fluid flow channel improve the heat exchange area and the heat exchange efficiency of cold and hot fluid.

In the present embodiment, the spiral winding tape 2 is spirally wound around the mandrel 1 in a circular shape, that is, the spiral winding tape 2 is in a circular spiral shape, and the heat exchanger in such a shape is easier to process and manufacture. In some other embodiments of the present application, the spiral tape 2 has a non-circular spiral shape, i.e. the spiral tape 2 may also be wound around the mandrel 1 in a non-circular spiral shape. Generally, the non-circular spiral is preferably an elliptical spiral, and the heat exchanger with the shape is flat in appearance, more attractive in appearance and capable of being arranged in a flat space, and the flat space is fully utilized to exert the heat exchange performance of the heat exchanger to the maximum extent.

Example two:

fig. 8 and 9 show a second particular embodiment of a heat exchanger of the type of the present application, which has substantially the same structure as the first embodiment, with the difference that:

in order to prevent the spiral winding tapes 2 of the adjacent turns from abutting against each other and further causing the second air flow passage 3 to be blocked, the embodiment provides an air duct supporting member sandwiched between the two adjacent turns of the spiral winding tapes 2 in the second air flow passage 3. The duct supporting member is another stamped projection 2012a integrally formed on the thin heat conducting strip 2012, and these stamped projections 2012a are arranged in the second air passing channel 3 in a spaced manner and supported between the spiral wound strips 2 of two adjacent turns.

In other embodiments of the present application, other structural members such as ventilation tubes, corrugated board, etc. may be used as the duct support. When the air ducts are used, the air ducts are required to be closely arranged along the spiral direction of the second air passing flow passage 3 and are parallel to the mandrel 1. When the air duct supporting member is a corrugated plate clamped between two adjacent circles of spiral winding belts 2, a plurality of corrugated peaks and a plurality of corrugated valleys of the corrugated plate are preferably arranged in sequence and alternately along the spiral direction of the second air flow passage 3, and the length of each corrugated peak and each corrugated valley is parallel to the axis of the mandrel 1 and is arranged in an extending mode. It is beneficial to arrange the corrugated sheet as a duct support in such a way that: the corrugated board is easy to bend in the arrangement direction of the ridges and the valleys, and has strong bending resistance in the length extension direction of the ridges or the valleys. Utilize the aforementioned structural characteristic of corrugated sheet, with its stupefied peak and stupefied millet along the second walk the spiral direction of gas flow channel and arrange in proper order in turn, not only make corrugated sheet buckle along the spiral direction and arrange, made things convenient for the processing preparation of this heat exchanger, promoted the bending strength of this heat exchanger main part again.

In addition, in order to prevent the two liquid-transporting tapes from abutting against each other to block the first air-transporting channel 202, in this embodiment, a plurality of stamping protrusions 2012a which are located in the first air-transporting channel 202 and supported between two adjacent liquid-transporting tapes 201 and are distributed at intervals are further disposed on the heat-conducting thin tape 2012, and obviously, the stamping protrusions 2012a may be replaced by ventilation pipes or corrugated plates.

Claims

1. A heat exchanger, comprising:

a mandrel (1) whose axis extends to the left and right, and

a spiral winding strip (2) spirally wound on the periphery of the mandrel (1) for at least 2 circles;

the spiral winding belt (2) comprises a plurality of liquid-running winding belts (201) which spirally surround the mandrel and are internally provided with spiral liquid channels (2011), the liquid-running winding belts (201) are mutually parallel and are arranged at intervals in the radial direction of the mandrel (1), and therefore a first gas-running channel (202) which is communicated left and right is formed among the liquid-running winding belts (201);

the spiral winding belts (2) of any two adjacent circle layers are separated by a certain distance, so that a spiral second air passing flow passage (3) which is communicated with the left and the right is formed between the spiral winding belts (2) of the adjacent circle layers.

2. A heat exchanger according to claim 1, wherein each liquid-moving winding (201) is provided with a first liquid inlet and outlet port (4) at the inner end of the spiral direction, and each liquid-moving winding (201) is provided with a second liquid inlet and outlet port (5) at the outer end of the spiral direction.

3. A heat exchanger according to claim 2, characterized in that the lengths of the plurality of liquid-carrying coils (201) in the spiral direction are equal.

4. The heat exchanger according to claim 2, characterized in that the first port (4) extends to the left parallel to the axis of the mandrel (1) and the second port (5) extends to the right parallel to the axis of the mandrel (1).

5. The heat exchanger according to claim 2, characterized in that the first gas flow path (202) at each first liquid inlet/outlet connection (4) is closed off by a seal (203).

6. A heat exchanger according to claim 5, characterised in that each first inlet and outlet connection (4) is a common connection and each second inlet and outlet connection (5) is a common connection.

7. The heat exchanger according to claim 1, wherein the liquid-carrying tape (201) comprises two parallel heat-conducting thin tapes (2012) and a liquid-sealing strip (2013) disposed between the two heat-conducting thin tapes, and the spiral liquid channel (2011) is formed between the liquid-sealing strip and the two heat-conducting thin tapes.

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

9. The heat exchanger according to claim 7, characterized in that a plurality of punching protrusions (2012a) spaced apart from each other and located in the first air passing flow channel (202) and supported between two adjacent liquid passing coils (201) are integrally formed on at least one of the thin heat conducting strips (2012), and a plurality of punching protrusions (2012a) spaced apart from each other and located in the second air passing flow channel (3) and supported between two adjacent coils of the spiral coils (2) are integrally formed on at least one of the thin heat conducting strips (2012).

10. The heat exchanger according to claim 1, characterized in that an air duct support sandwiched between two adjacent liquid-carrying winding tapes (201) is arranged in the first air-carrying flow passage (202), and an air duct support sandwiched between two adjacent spiral winding tapes (2) is arranged in the second air-carrying flow passage (3).

11. The heat exchanger according to claim 10, characterized in that the air duct support is a plurality of ventilation ducts parallel to the mandrel (1), each ventilation duct being closely arranged along the spiral direction of the first air passage (202) or the second air passage (3).

12. The heat exchanger according to claim 10, wherein the air duct supporting member is a corrugated plate, the corrugated plate comprises a plurality of ridges and a plurality of valleys alternately arranged in sequence along the spiral direction of the first air passing flow passage or the second air passing flow passage, and the length of each ridge and each valley is arranged in parallel with the axis of the mandrel (1).

13. The heat exchanger according to claim 10, characterized in that the helical coil (2) is wound in a non-circular spiral around the mandrel (1).

14. The heat exchanger according to claim 13, characterized in that the helical coil (2) is helically wound in an elliptical shape around the mandrel (1).

15. A heat exchange device, characterized in that it comprises at least two heat exchangers according to claim 4, the mandrels (1) of each heat exchanger being arranged coaxially, and the first inlet and outlet connections (4) or the second inlet and outlet connections (5) of any two adjacent heat exchangers being in butt joint with each other.

16. The heat exchange device according to claim 15, wherein the mandrel (1) is a hollow tube with an axial through hole (101), a pull rod (6) with two external threads is arranged in the axial through hole (101) in a penetrating manner, and two ends of the pull rod (6) are respectively in threaded connection with a locking nut (7) for axially clamping each heat exchanger.

17. A heat exchange device according to claim 15, characterised in that each heat exchanger comprises a cylindrical shell (8) coaxially arranged on the periphery of the spiral coil (2), the cylindrical shells (8) of any two adjacent heat exchangers being in sealing abutment.

18. The heat exchange device according to claim 17, characterized in that axially through holes (10) are provided between the cylindrical shell (8) and the spiral winding (2), the through holes (10) of each heat exchanger are coaxially arranged, and a liquid guiding pipe (9) connected with the first liquid inlet and outlet port (4) or the second liquid inlet and outlet port (5) of one of the heat exchangers at the extreme side is arranged in the through holes.