CN217604434U - Pressure-equalizing spiral shell type evaporator - Google Patents

Abstract

The utility model discloses a voltage-sharing spiral shell and tube evaporator, be the tubulose casing of closed form including both ends, the tubulose casing is cut apart into cold medium along the axial with it and keeps in the cavity, heat transfer cavity and exhaust cavity in proper order through first baffle (equalizer plate) and second baffle respectively, evenly laid many spiral heat exchange tubes in the heat transfer cavity, the one end of heat exchange tube is passed behind the second baffle and is communicate with the exhaust cavity, the other end passes through whirl shower nozzle and cold medium and keeps in the cavity intercommunication, be equipped with gaseous state hot medium entry and leakage fluid dram on the pipe wall of heat transfer cavity respectively, and the diameter that is equipped with gaseous state hot medium entry one side is greater than leakage fluid dram one side diameter. The utility model discloses a combined action of equalizer plate and whirl shower nozzle makes liquid coolant can evenly get into spiral heat exchange tube with fan form fog equivalent in, and the reasonable overall arrangement of spiral heat exchange tube in addition can realize coolant and the abundant heat transfer of gaseous state hot medium, is showing and has improved coefficient of heat transfer and heat exchange efficiency.

Description

Pressure-equalizing spiral shell type evaporator

Technical Field

The utility model belongs to the technical field of shell-and-tube heat exchanger, concretely relates to voltage-sharing spiral shell type evaporimeter.

Background

As is well known, an evaporator is a heat exchange device in a refrigeration system, and is a heat exchanger for absorbing heat at low temperature of a refrigerant, which is an important part in four major components of refrigeration. The evaporator mainly comprises a heating chamber and an evaporation chamber. The heating chamber provides heat required by evaporation to the liquid to promote boiling and vaporization of the liquid, and the evaporation chamber completely separates gas phase from liquid phase.

Among them, the shell-and-tube evaporator is widely used in various refrigeration equipments because of its advantages of good heat transfer effect, compact structure, small occupied area, simple manufacture, low maintenance cost, convenient installation, etc. The method can be divided into a falling film evaporator and a rising film evaporator according to the difference of the position of feed liquid (liquid cold medium) entering a heating pipe, wherein the biggest difference between the falling film evaporator and the rising film evaporator is that the feed liquid of the rising film evaporator forms a film on the pipe wall and moves upwards under the action of high-speed secondary steam flow and vacuum, the evaporated feed liquid and the secondary steam enter a separator from the top of the evaporator, and the separation of the evaporated feed liquid and the secondary steam is realized; the falling film evaporator distributes the incoming material to each film falling pipe under the action of the material-liquid distributor and flows from top to bottom along the pipe wall in a film state under the action of self gravity and secondary steam flow, and the evaporated material liquid and the secondary steam enter the separator at the bottom of the evaporator to realize the complete separation of the evaporated material liquid and the secondary steam. Because the rising film evaporator requires a large heating temperature difference, the operation is not easy to control, and phenomena such as deflection and the like are easily caused, the rising film evaporator is gradually eliminated by the market in recent years, and the existing falling film evaporator has the following disadvantages: firstly, because the volume of the feed liquid can expand many times when the feed liquid is evaporated, the volume of the feed liquid entering the evaporator is generally small in consideration of the flow velocity after gasification, and the flow distribution entering each heat exchange tube is uneven due to uneven pressure, so that the local heat exchange is uneven; secondly, the heat exchange tube structure (straight tubes) of the existing evaporator and the layout thereof are unreasonable, so that the retention time of the feed liquid in the evaporator is short, and the feed liquid cannot be in full contact with a heat medium; thirdly, the device is quite sensitive to the fluctuation of the feeding load, and when the design or the operation is not proper, the film is not easy to form, and at the moment, the convection heat transfer coefficient is obviously reduced; based on the reasons, the whole heat exchange efficiency of the existing falling film evaporator is not high, and the feed liquid cannot be fully utilized.

In view of the above, the present inventors have devised a pressure equalizing spiral shell-and-tube evaporator to solve the above technical problems.

SUMMERY OF THE UTILITY MODEL

An object of the utility model is to overcome above-mentioned prior art's shortcoming, a voltage-sharing spiral shell and tube formula evaporimeter is provided, this evaporimeter is earlier through throttling arrangement to the liquid cold medium step-down that gets into the cold medium chamber of keeping in, then through the combined action of equalizer plate and whirl shower nozzle, make liquid cold medium evenly be full of the cold medium chamber of keeping in, secondly make its even spout into spiral heat exchange tube in the effect of whirl shower nozzle, liquid cold medium carries out abundant heat transfer with gaseous state hot medium in the heat transfer chamber, and spiral heat exchange tube is rationally distributed, thereby the purpose of high-efficient heat transfer has been realized.

The utility model aims at solving through the following technical scheme:

a pressure-equalizing spiral shell type evaporator comprises a tubular shell with two closed ends, wherein a cavity of the tubular shell is axially divided into a cold medium temporary storage cavity, a heat exchange cavity and an exhaust cavity through a first partition plate and a second partition plate respectively, and the heat exchange cavity is positioned between the cold medium temporary storage cavity and the exhaust cavity;

the cold medium temporary storage chamber is communicated with a refrigerant liquid inlet pipe and is used for temporarily storing liquid cold medium;

a plurality of spiral heat exchange tubes are uniformly distributed in the heat exchange cavity along the axial direction of the tubular shell, one end of each spiral heat exchange tube penetrates through the second partition plate and then is communicated with the exhaust cavity, the other end of each spiral heat exchange tube is provided with a spiral flow nozzle, the spiral flow nozzle is communicated with the cold medium temporary storage cavity through the first partition plate, the tube wall of the heat exchange cavity is respectively provided with a gaseous heat medium inlet and a liquid discharge port, the gaseous heat medium inlet is arranged close to one side of the cold medium temporary storage cavity and is connected with a carrier gas pipeline, and the liquid discharge port is arranged close to one side of the exhaust cavity and is used for discharging liquid obtained after the gaseous heat medium is liquefied through the heat exchange cavity;

the exhaust chamber is provided with an exhaust port for exhausting gas generated by vaporizing the liquid cold medium by the heat exchange chamber.

Further, the heat exchange chamber is composed of a first chamber and a second chamber which are coaxial, the diameter of the first chamber is larger than that of the second chamber, and the gaseous heat medium inlet is arranged on the pipe wall of the first chamber and is used for enabling the gaseous heat medium which just enters the heat exchange chamber to be in contact with the spiral heat exchange pipe fully and uniformly.

Furthermore, the spiral heat exchange tubes are arranged in the heat exchange cavity in a multilayer mode and are wound in a staggered mode according to the spiral line shape, the distance between any two adjacent layers of spiral heat exchange tubes is the same, and the spiral winding directions are opposite.

Furthermore, each layer of spiral heat exchange tubes are distributed in an annular array by taking the axial lead of the tubular shell as the center, the number of the spiral heat exchange tubes of each layer is increased from the inner layer to the outer layer in sequence, and the thread pitch, the spiral radius and the spiral direction of the spiral heat exchange tubes positioned on the same layer are the same.

Furthermore, the whirl shower nozzle includes that nozzle and cover establish the outside shell that spouts of nozzle, spout shell entry end department and can dismantle and be connected with the filter screen panel, exit port department has seted up the efflux hole, the nozzle is located one side annular equipartition in efflux hole and has three spiral guiding gutters.

Further, the first partition plate is composed of two pressure equalizing plates arranged at intervals, threaded holes matched with the number and the positions of the spiral heat exchange tubes one by one are formed in the two pressure equalizing plates, the spiral flow nozzle is arranged between the two pressure equalizing plates, the inlet end of the spiral flow nozzle is communicated with the cold medium temporary storage cavity through the threaded holes, and the outlet end of the spiral flow nozzle is connected with the inlet port of the spiral heat exchange tube.

Furthermore, the connection part of the rotational flow nozzle and the first partition plate, the connection part of the rotational flow nozzle and the spiral heat exchange tube and the connection part of the spiral heat exchange tube and the second partition plate are in sealing connection, so that gas or liquid leakage is prevented.

Furthermore, the evaporator is installed in a vertical or horizontal arrangement mode, and when the evaporator is vertically arranged, the cold medium temporary storage chamber is positioned at the top end of the tubular shell.

Furthermore, the refrigerant liquid inlet pipe is connected with a throttling device and used for reducing the pressure of the liquid cold medium flowing into the cold medium temporary storage chamber.

Compared with the prior art, the utility model discloses following beneficial effect has:

1. the utility model relates to a voltage-sharing spiral shell type evaporator, this evaporator gets into its inside liquid cold medium after reducing the pressure through throttling arrangement throttle earlier, then get into cold medium temporary storage cavity via refrigerant feed liquor pipe, because the combined action of first baffle (equalizer plate) and whirl shower nozzle, liquid cold medium is even to be full of cold medium temporary storage cavity, form the pressure differential around the whirl shower nozzle promptly, through the effect of this pressure differential, make liquid cold medium after the spiral guiding gutter through the whirl shower nozzle, can be even get into the spiral heat exchange tube that is located heat transfer cavity front end (diameter is slightly bigger) with the form of fan-shaped fog, and contact spiral heat exchange tube pipe wall earlier, immediately carry out the heat transfer with gaseous state hot state medium; in addition, the spiral flow spray heads are uniformly distributed on the pressure equalizing plate in a layered annular array mode according to the layout of the spiral heat exchange tubes, the spiral winding directions of any two adjacent spiral heat exchange tubes are opposite, and the turbulence degree in the heat exchange cavity and the spiral heat exchange tubes is increased. In conclusion, compared with the traditional evaporator, the evaporator structure has the following advantages: firstly, liquid cold medium can uniformly enter the heat exchange tube in a fan-shaped fog state to contact the tube wall under the action of the swirl nozzle, so that the film is more easily formed, and the heat exchange is facilitated; the heat exchange tube adopts a spiral type and is reasonable in structural layout, compared with the traditional laminar flow/straight-line tube, the heat exchange time of the liquid cold medium and the gaseous heat medium is prolonged, and the turbulence degree is increased by matching with the structure of the heat exchange cavity; thirdly, the structure utilizes the disturbance generated by the spiral heat exchange tube and the higher density and viscosity of the liquid compared with the gas to uniformly evaporate in the limited descending process, thereby greatly enhancing the film forming effect of the liquid, enhancing the heat exchange strength in unit area and improving the convection heat transfer coefficient; based on the advantages, compared with the traditional technology, the evaporator obviously improves the heat exchange efficiency, and the heat exchange strength is improved by 2-3 times through actual tests.

2. The utility model relates to a voltage-sharing spiral shell type evaporator, this falling film evaporator is because liquid cold medium is the isothermal process almost at the pipe side uniform evaporation (liquid cold medium becomes gaseous state cold medium, the temperature does not change, only the phase state has changed), even the evaporator adopts the following current mode also can realize very little end difference (because it changes to be the phase state, the heat of obtaining has mainly aroused the phase transition of medium, be the change of latent heat promptly mainly, the change of sensible heat is minimum), consequently this falling film evaporator's overall arrangement can perpendicular or horizontal dual mode, the convenience is carried out the on-the-spot demand and is laid as required.

Drawings

The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate embodiments of the invention and together with the description, serve to explain the principles of the invention.

In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, and it is obvious for those skilled in the art that other drawings can be obtained according to the drawings without inventive labor.

FIG. 1 is a schematic view of the tubular casing structure of the present invention;

FIG. 2 is a schematic view of the overall structure of the evaporator according to the present invention;

FIG. 3 is a schematic view of a first partition plate according to the present invention;

FIG. 4 is a schematic view of the structure of the swirl sprinkler head of the present invention;

FIG. 5 is a schematic view of a nozzle structure of the swirl nozzle of the present invention; wherein, a is a front view of the nozzle, and b is a side view of the nozzle.

Wherein: 1 is a tubular shell; 2 is a first partition plate; 3 is a second clapboard; 4 is a refrigerant liquid inlet pipe; 5 is a spiral heat exchange tube; 6 is a rotational flow nozzle; 11 is a cold medium temporary storage chamber; 12 is a heat exchange chamber; 12-1 is a first chamber; 12-2 is a second chamber; 13 is an exhaust chamber; 21 is a threaded hole; 61 is a nozzle; spray shell 62; 63 is a filter screen cover; 121 is a gaseous heat medium inlet; 122 is a liquid outlet; 131 is an exhaust port; 611 is a spiral diversion trench; 621 is an orifice.

Detailed Description

Reference will now be made in detail to the exemplary embodiments, examples of which are illustrated in the accompanying drawings. When the following description refers to the accompanying drawings, like numbers in different drawings represent the same or similar elements unless otherwise indicated. The embodiments described in the following exemplary embodiments do not represent all embodiments consistent with the present invention. Rather, they are merely examples of apparatus consistent with certain aspects of the invention, as detailed in the following claims.

In order to make those skilled in the art better understand the technical solution of the present invention, the present invention will be further described in detail with reference to the accompanying drawings and the embodiments.

Please refer to fig. 1-5 and show, the utility model provides a voltage-sharing spiral shell type evaporator, be the tubulose casing 1 of closed form including both ends, its whole appearance is cylindricly, the cavity of tubulose casing 1 is cut apart into cold medium through first baffle 2 and second baffle 3 with it along axial (length direction) and keeps in cavity 11, heat transfer cavity 12 and exhaust cavity 13, and heat transfer cavity 12 is located between cold medium keeps in cavity 11 and the exhaust cavity 13, cold medium keeps in cavity 11 promptly and exhaust cavity 13 and is located the head and the tail both ends of tubulose casing 1, the volume of each cavity is set for according to actual demand. Through above setting, liquid cold medium (like freon) etc. that the cold medium stored in the chamber 11 of keeping in get into heat transfer chamber 12 through the pipeline and carry out the heat exchange rather than inside gaseous state hot medium, can realize turning into the gaseous state with liquid cold medium to discharge through exhaust chamber 13, liquefy gaseous state hot medium into liquid simultaneously, and discharge through the leakage fluid dram.

Specifically, the embodiment of the utility model provides an in the cold medium keep in and seted up the entry on the cavity 11, the cold medium keeps in cavity 11 and is used for keeping in liquid cold medium through entry and refrigerant feed liquor pipe 4 intercommunication, cold medium keep in cavity 11, in order to avoid getting into the cold medium and keep in the liquid cold medium pressure in the cavity 11 uneven or too high, the flow that leads to follow-up entering heat exchange tube is uneven, influences heat exchange efficiency. Preferably, the utility model discloses be connected with throttling arrangement (prior art, not shown in the figure) on the refrigerant feed liquor pipe 4, through throttling arrangement to flowing into liquid cold medium depressurization in the cold medium chamber of keeping in 11.

In the embodiment of the utility model, a plurality of spiral heat exchange tubes 5 are uniformly distributed in the heat exchange cavity 12 along the axial direction of the tubular shell 1, one end of each spiral heat exchange tube 5 is communicated with the exhaust cavity 13 after passing through the second partition plate 3, the other end of each spiral heat exchange tube 5 is provided with the cyclone spray head 6, the cyclone spray head 6 is communicated with the cold medium temporary storage cavity 11 through the first partition plate 2, the tube wall of the heat exchange cavity 12 is respectively provided with a gaseous heat medium inlet 121 and a liquid discharge port 122, the gaseous heat medium inlet 121 is arranged close to one side of the cold medium temporary storage cavity 11 and is connected with a carrier gas pipeline, and the liquid discharge port 122 is arranged close to one side of the exhaust cavity 13 and is used for discharging liquid after the gaseous heat medium is liquefied through the heat exchange cavity 12; the exhaust chamber 13 is provided with an exhaust port 131 for exhausting gas generated by vaporizing the liquid refrigerant in the heat exchange chamber 12.

Preferably, the embodiment of the utility model provides an entry at gaseous state hot medium entry 121 and cold medium chamber 11 of keeping in all is provided with the filter screen, and the filter screen filters the edulcoration to the medium that gets into the evaporimeter inside and purifies, has reduced the emergence of heat transfer chamber 12 inner wall and 5 inside and outside walls scale deposit phenomena of spiral heat exchange tube, guarantees the long-term steady operation of evaporimeter.

Wherein, the embodiment of the utility model provides a heat transfer cavity 12 comprises coaxial first cavity 12-1 and second cavity 12-2, and the diameter of first cavity 12-1 is greater than second cavity 12-2, gaseous state hot medium entry 121 sets up on the pipe wall of first cavity 12-1, drain outlet 122 sets up in the terminal bottom of second cavity 12-2, the space of the gaseous state hot medium that just got into heat transfer cavity 12 promptly is bigger relatively, make gaseous state hot medium fully evenly contact with spiral heat exchange tube 5 (have cold medium in the pipe) when reducing the resistance, improve heat exchange efficiency.

In addition, in the embodiment of the present invention, the plurality of spiral heat exchange tubes 5 are arranged in the heat exchange chamber 12 in a multilayer manner and are wound and arranged in a staggered manner according to the spiral line shape, and the distance between any two adjacent layers of spiral heat exchange tubes 5 is the same, and the spiral winding directions are opposite; each layer of spiral heat exchange tubes 5 is distributed in an annular array by taking the axial lead of the tubular shell 5 as the center, the number of each layer of spiral heat exchange tubes 5 increases progressively from the inner layer to the outer layer, the screw pitches, the spiral radiuses and the spiral directions of the spiral heat exchange tubes 5 positioned on the same layer are the same, and the distribution diagram of the end parts of the spiral heat exchange tubes 5 is shown in figure 2. When the arrangement is used, the cold medium in the heat exchange tube flows along the spiral direction of the heat exchange tube, the gaseous heat medium in the heat exchange chamber 12 flows along the spiral channel formed by the same-interval spiral tube, and the heat exchange advantages are embodied in the following aspects: firstly, as the cold medium generates secondary circulation in the process of spiral flow, and the spiral angles of the two adjacent layers of spiral pipes are opposite numbers, the turbulence degree of the heat exchange chamber 12, the spiral heat exchange pipe 5 and the adjacent layers of the spiral heat exchange pipe 5 is increased, and the heat exchange capacity is enhanced; secondly, the heat exchange tube adopts the spiral tube winding mode, and its length is greater than heat exchange cavity 12 length far away, has both increased heat transfer area and great extension heat transfer time, has further improved heat exchange efficiency.

The embodiment of the utility model provides an in first baffle 2 comprises the equalizer plate (the level and smooth metal sheet in surface) that two intervals set up, and all set up on two equalizer plates with spiral heat exchange tube 5 quantity and the screw hole 21 of position one-to-one matching, screw hole 21 position department between two equalizer plates is located to whirl shower nozzle 6, and the entry end and the cold medium of whirl shower nozzle 6 keep in cavity 11 intercommunication, the exit end is connected with spiral heat exchange tube 5's entry port.

As shown in fig. 4, 5, the utility model discloses a whirl nozzle 6 include that nozzle 61 and cover establish the spout shell 62 outside nozzle 61, spout shell 62 entry department can dismantle and be connected with filter screen panel 63, it is little that this filter screen panel 63 is compared in the filter screen hole of cold medium temporary storage chamber 11 entrance, prevent to block whirl nozzle 6 with filtering fine impurity in the cold medium, discharge port department has seted up jet orifice 621, one side annular that nozzle 61 is located jet orifice 621 is provided with three spiral guiding gutter 611, like this through three spiral guiding gutter 611 tangential effect when liquid cooling medium passes through whirl nozzle 6 inner channel, liquid cold medium after whirl nozzle 6 can evenly spray in spiral heat exchange tube 5's pipe wall with the form of fan form fog, each whirl nozzle 6 corresponds a spiral heat exchange tube 5, guarantee that every spiral heat exchange tube 5's heat transfer effect is the same or is close.

The embodiment of the utility model provides a all adopt the sealing connection mode, for example the welding, in the junction of whirl shower nozzle 6 and first baffle 2, the junction of whirl shower nozzle 6 and spiral heat exchange tube 5 and the junction of spiral heat exchange tube 5 and second baffle 3 to prevent that gas or liquid from revealing.

The utility model discloses the evaporimeter is because liquid is almost isothermal process at pipe side uniform evaporation, even the evaporimeter adopts the following current mode also can realize very little end difference, consequently can select perpendicular or horizontally to lay the mode according to site environment or equipment demand, when laying perpendicularly, and cold medium keeps in chamber 11 and is located the top of tubulose casing 1.

The above description is only exemplary of the invention, and is intended to enable those skilled in the art to understand and implement the invention. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the generic principles defined herein may be applied to other embodiments without departing from the spirit or scope of the invention.

It is to be understood that the present invention is not limited to what has been described above, and that various modifications and changes may be made without departing from the scope thereof. The scope of the present invention is limited only by the appended claims.

Claims (9)

1. A pressure-equalizing spiral shell type evaporator is characterized by comprising a tubular shell (1) with two closed ends, wherein a cavity of the tubular shell (1) is axially divided into a cold medium temporary storage cavity (11), a heat exchange cavity (12) and an exhaust cavity (13) through a first partition plate (2) and a second partition plate (3), and the heat exchange cavity (12) is positioned between the cold medium temporary storage cavity (11) and the exhaust cavity (13);

the cold medium temporary storage chamber (11) is communicated with the refrigerant liquid inlet pipe (4) and is used for temporarily storing liquid cold medium;

a plurality of spiral heat exchange tubes (5) are uniformly distributed in the heat exchange cavity (12) along the axial direction of the tubular shell (1), one end of each spiral heat exchange tube (5) penetrates through the second partition plate (3) and then is communicated with the exhaust cavity (13), the other end of each spiral heat exchange tube (5) is provided with a cyclone spray head (6), the cyclone spray head (6) is communicated with the cold medium temporary storage cavity (11) through the first partition plate (2), the tube wall of the heat exchange cavity (12) is respectively provided with a gaseous heat medium inlet (121) and a liquid discharge port (122), one side of the gaseous heat medium inlet (121) close to the cold medium temporary storage cavity (11) is provided with a temporary storage and is connected with a carrier gas pipeline, one side of the liquid discharge port (122) close to the exhaust cavity (13) is provided with a temporary storage and is used for discharging liquid obtained by liquefying the gaseous heat medium through the heat exchange cavity (12);

and the exhaust chamber (13) is provided with an exhaust port (131) for exhausting gas obtained by vaporizing the liquid cooling medium through the heat exchange chamber (12).

2. A pressure equalizing spiral shell evaporator as recited in claim 1, characterized in that said heat exchange chamber (12) is composed of a first chamber (12-1) and a second chamber (12-2) which are coaxial, and said first chamber (12-1) has a larger diameter than said second chamber (12-2), and said gaseous heat medium inlet (121) is provided on the tube wall of said first chamber (12-1) for bringing the gaseous heat medium just entering the heat exchange chamber (12) into substantially uniform contact with the spiral heat exchange tubes (5).

3. A pressure equalizing spiral shell type evaporator as recited in claim 1 or 2, characterized in that a plurality of said spiral heat exchange tubes (5) are arranged in a plurality of layers in the heat exchange chamber (12) and are alternately wound in a spiral shape, and the distance between any two adjacent layers of spiral heat exchange tubes (5) is the same and the spiral winding directions are opposite.

4. A pressure equalizing spiral shell type evaporator as claimed in claim 3, wherein each layer of spiral heat exchange tubes (5) is arranged in an annular array with the axis of the tubular shell (1) as the center, the number of each layer of spiral heat exchange tubes (5) increases from the inner layer to the outer layer in sequence, and the spiral pitches, spiral radii and spiral directions of the spiral heat exchange tubes (5) in the same layer are the same.

5. The pressure equalizing spiral shell type evaporator of claim 1, wherein the spiral flow nozzle (6) comprises a nozzle (61) and a spray shell (62) sleeved outside the nozzle (61), a filter screen cover (63) is detachably connected to an inlet end of the spray shell (62), a spray hole (621) is formed in an outlet port, and three spiral diversion trenches (611) are annularly and uniformly distributed on one side of the nozzle (61) located at the spray hole (621).

6. A pressure-equalizing spiral shell type evaporator as claimed in claim 1, wherein the first partition plate (2) is composed of two pressure equalizing plates arranged at intervals, each of the two pressure equalizing plates is provided with a threaded hole (21) matched with the number and position of the spiral heat exchange tubes (5), the spiral flow nozzle (6) is arranged between the two pressure equalizing plates, the inlet end of the spiral flow nozzle (6) is communicated with the cold medium temporary storage chamber (11) through the threaded hole (21), and the outlet end of the spiral flow nozzle is connected with the inlet end of the spiral heat exchange tube (5).

7. A pressure equalizing spiral shell type evaporator as claimed in claim 6, wherein the connection of the spiral flow nozzle (6) and the first clapboard (2), the connection of the spiral flow nozzle (6) and the spiral heat exchange tube (5) and the connection of the spiral heat exchange tube (5) and the second clapboard (3) are all in a sealing connection mode to prevent gas or liquid from leaking.

8. A pressure equalizing spiral shell evaporator as claimed in any one of claims 1 to 7, characterized in that the evaporator is installed in a vertical or horizontal arrangement, and the cold medium temporary storage chamber (11) is located at the top end of the tubular shell (1) when arranged vertically.

9. A pressure equalizing spiral shell evaporator as claimed in claim 8, characterized in that the refrigerant inlet pipe (4) is connected to a throttle device for depressurizing the liquid refrigerant flowing into the refrigerant buffer chamber (11).

Images