CN116182435A

CN116182435A - Desuperheating assembly of condenser, condenser and refrigeration system

Info

Publication number: CN116182435A
Application number: CN202310130778.3A
Authority: CN
Inventors: 王小勇; 胡海利; 张营; 岳清学; 武永强
Original assignee: Gree Electric Appliances Inc of Zhuhai
Current assignee: Gree Electric Appliances Inc of Zhuhai
Priority date: 2023-02-17
Filing date: 2023-02-17
Publication date: 2023-05-30

Abstract

The present disclosure provides a desuperheating assembly for a condenser, and a refrigeration system. The desuperheating assembly includes: the overheat removing box is provided with an overheat removing box inner cavity, and is provided with an overheat removing box gas inlet which is communicated with the overheat removing box inner cavity and is used for receiving the gaseous working medium and an overheat removing box gas outlet which is used for outputting the gaseous working medium, and the overheat removing box inner cavity comprises a gas cooling cavity which is communicated with the overheat removing box gas inlet and the overheat removing box gas outlet; and the first heat exchange tube is arranged on the desuperheating box and comprises a desuperheating tube section positioned in the gas cooling cavity, and the desuperheating tube section is configured to cool gaseous working medium in the gas cooling cavity. The heat exchange coefficient of the superheating heat exchange of the condenser is improved, so that the overall heat exchange efficiency of the condenser is improved.

Description

Desuperheating assembly of condenser, condenser and refrigeration system

Technical Field

The disclosure relates to the technical field of heat exchange equipment, and in particular relates to a desuperheating component of a condenser, the condenser and a refrigerating system.

Background

At present, the most used condenser in the refrigeration system is a shell-and-tube condenser or a plate condenser manufactured by using materials such as copper, aluminum, titanium and the like and utilizing a solid heat conduction principle, and the main working principle is that refrigerant working medium and secondary refrigerant working medium are respectively positioned in different processes and exchange heat in a convection and heat conduction mode of a heat exchange tube.

In some refrigeration systems, for example, in a refrigeration system of a commercial water-cooling unit, a high-temperature and high-pressure gaseous refrigerant discharged through a compressor is in an overheated state, and thus, the refrigerant at the condenser inlet of the refrigeration system is also generally in an overheated state. The gaseous refrigerant in the overheat state firstly generates single-phase sensible heat exchange (desuperheating heat exchange) in the shell of the condenser, and the refrigerant steam only releases heat and does not generate phase change; the gaseous refrigerant is cooled from the overheat state to the saturation state, and then the gaseous refrigerant in the saturation state generates latent heat exchange and is converted into a liquid refrigerant in the saturation state. The heat exchange strength of the latent heat exchange is 10-20 times of that of the single-phase sensible heat exchange.

The heat exchange amount of the superheating heat exchange generally accounts for about 6% of the total heat exchange amount of the condenser, and the heat exchange amount of the superheating area heat exchange under partial working conditions can reach up to 10% of the total heat exchange amount of the condenser, but because the heat exchange intensity of single-phase sensible heat exchange is lower, the superheat degree of the refrigerant can be reduced by sacrificing a large amount of top heat exchange area of the condenser or using additional auxiliary cooling equipment in the condenser. This prevents further increases in energy efficiency and cost optimization of condensers, such as the horizontal condensers used in commercial chiller units.

Disclosure of Invention

The invention aims to provide a desuperheating component of a condenser, the condenser and a refrigerating system, and aims to solve the problem that the heat exchange strength of single-phase sensible heat exchange of the condenser is low.

A first aspect of the present disclosure provides a desuperheating assembly for a condenser, comprising:

the overheat removing box is provided with an overheat removing box inner cavity, and is provided with an overheat removing box gas inlet which is communicated with the overheat removing box inner cavity and is used for receiving gaseous working media and an overheat removing box gas outlet which is used for outputting the gaseous working media, and the overheat removing box inner cavity comprises a gas cooling cavity which is communicated with the overheat removing box gas inlet and the overheat removing box gas outlet; and

the first heat exchange tube is arranged on the desuperheating box and comprises a desuperheating tube section positioned in the gas cooling cavity, and the desuperheating tube section is configured to cool the gaseous working medium in the gas cooling cavity.

In the desuperheating assembly of some embodiments,

the desuperheating box gas inlet comprises a first gas inlet hole positioned at the middle part of the desuperheating box along the first direction, and the desuperheating box gas outlet comprises two first gas outlet holes positioned at two ends of the desuperheating box along the first direction respectively; or alternatively

The desuperheating box gas inlet comprises a second gas inlet hole positioned at the middle part of the desuperheating box along the first direction, and the desuperheating box gas outlet comprises a plurality of second gas outlet holes positioned at the desuperheating box and distributed along the first direction; or,

the desuperheating box gas inlet comprises two third gas inlet holes positioned at two ends of the desuperheating box along the first direction, and the desuperheating box gas outlet comprises a third gas outlet hole positioned at the middle of the desuperheating box along the first direction.

In the desuperheating assembly of some embodiments,

the desuperheating box gas inlet and the desuperheating box gas outlet are positioned on the same side of the desuperheating box; or (b)

The desuperheating box gas inlet and the desuperheating box gas outlet are positioned on two opposite sides of the desuperheating box; or (b)

The desuperheating box gas inlet and the desuperheating box gas outlet are positioned on two adjacent sides of the desuperheating box.

In some embodiments, the desuperheating box includes a mounting aperture plate portion including a mounting aperture through which the first heat exchange tube passes for mounting on the desuperheating box.

In some embodiments, the desuperheating box comprises two mounting hole plate parts which are oppositely arranged, and the first heat exchange pipe penetrates into the two mounting hole plate parts at the same time to be mounted on the desuperheating box.

In some embodiments, the desuperheating assembly further comprises a cooling tube section located outside of the desuperheating box.

In some embodiments, the desuperheating assembly includes a plurality of the first heat exchange tubes arranged in a side-by-side spaced relationship.

In some embodiments, the first heat exchange tube is a straight tube extending in a first direction, the desuperheating assembly is symmetrical about a surface perpendicular to the first direction and/or the desuperheating assembly is symmetrical about a surface parallel to the first direction.

In some embodiments, the desuperheating box gas inlet includes a first inlet aperture located in a middle of the desuperheating box in a first direction, and the desuperheating box gas outlet includes two first outlet apertures located at each of two ends of the desuperheating box in the first direction, the first inlet aperture having a diameter

Diameter +.>

Satisfy->

In the desuperheating assembly of some embodiments,

the desuperheating box inner cavity further comprises an air inlet and air equalizing cavity, and the air inlet and air equalizing cavity is positioned between the desuperheating box gas inlet and the gas cooling cavity and is communicated with the desuperheating box gas inlet and the gas cooling cavity;

the desuperheating component further comprises an air inlet air homogenizing plate positioned in the desuperheating box, and the air inlet air homogenizing plate is positioned between the air inlet air homogenizing cavity and the air cooling cavity so as to separate the air inlet air homogenizing cavity and the air cooling cavity, and a plurality of air inlet air homogenizing holes communicated with the air inlet air homogenizing cavity and the air cooling cavity are formed in the air inlet air homogenizing plate.

In some embodiments, the desuperheating assembly comprises an intake baffle region opposite the intake direction and an intake orifice region connected to the intake baffle region, the plurality of intake air holes being located on the intake orifice region.

In the desuperheating assembly of some embodiments, the plurality of air inlet air equalizing holes are divided into a plurality of air inlet air equalizing hole groups along a direction from the air inlet baffle area to the air inlet orifice area, wherein a diameter of a first air inlet air equalizing hole of the air inlet air equalizing hole group close to the air inlet baffle area is smaller than a diameter of a second air inlet air equalizing hole of the air inlet air equalizing hole group far away from the air inlet baffle area.

In some embodiments, the desuperheating assembly, the inlet orifice area includes two inlet air equalizing hole groups, a diameter of a first inlet air equalizing hole of the inlet air equalizing hole groups proximate to the inlet baffle area

Diameter of a second air inlet and air equalizing hole of the air inlet and air equalizing hole group far away from the air inlet baffle area +.>

Satisfy->

In some embodiments, the desuperheater module includes a desuperheater box gas inlet having a diameter

Is a first air inlet of (1)A hole; the pressure drop delta P of the gaseous working medium flowing through the desuperheating component is as follows:

ΔP＝Cρv ² ；

ρ is the density of the gaseous working medium of the desuperheating box gas inlet, and the unit is kg/m ³ ；

v is the flow velocity of the gaseous working medium at the gas inlet of the desuperheating box, and the unit is m/s;

n ₁ is of uniform pore diameter

The number of first air inlet air equalizing holes of the air equalizing hole group;

n ₂ is of uniform pore diameter

The number of second air inlet and air equalizing holes of the air equalizing hole group;

and->

Is in m.

In some embodiments, the desuperheating assembly includes a gas baffle positioned on a side of the intake air equalization plate facing the incoming flow of gaseous working fluid.

In the desuperheating assembly of some embodiments,

wherein alpha is the product of logarithmic average temperature difference and heat exchange area, the value range of alpha is 10-100, and the unit is m ² *K；

n is the number of the first heat exchange tubes;

d is the outer diameter of the first heat exchange tube, and the unit is m;

l is the length of the desuperheated pipe section, and the unit is m;

T _in the unit of the temperature of the gaseous working medium at the gas inlet of the desuperheating box is K;

T _out the unit is K for the gaseous working medium temperature of the gas outlet of the desuperheating box;

T _wall the average temperature of the outer surface of the desuperheated pipe section is given in K.

In some embodiments, the desuperheating assembly further comprises a baffle disposed within the gas cooling cavity and configured to form a baffle flow channel within the gas cooling cavity, an inlet end of the baffle flow channel in communication with the desuperheating box gas inlet, an outlet end of the baffle flow channel in communication with the desuperheating box gas outlet, and at least a portion of the desuperheating pipe section within the baffle flow channel.

In some embodiments of the desuperheating assembly, a plurality of baffles are spaced apart within the gas cooling cavity along the direction of extension of the first heat exchange tube.

In the desuperheating assembly of some embodiments,

the inlet end of the baffling flow channel is positioned at the middle part of the gas cooling cavity along the axial direction of the first heat exchange tube, and the outlet end of the baffling flow channel is positioned at the end part of the gas cooling cavity along the axial direction of the first heat exchange tube; or alternatively

The inlet end of the baffling flow channel is positioned at the end part of the gas cooling cavity along the axial direction of the first heat exchange tube, and the outlet end of the baffling flow channel is positioned at the middle part of the gas cooling cavity along the axial direction of the first heat exchange tube.

In some embodiments, the desuperheating assembly includes two of the baffle flow channels arranged in an axial direction of the first heat exchange tube.

In some embodiments, the baffle is disposed at an angle to the axis of the desuperheating pipe section, and the baffle has a through-hole through which the desuperheating pipe section passes.

In some embodiments, the desuperheating box inner chamber includes an air-out air-homogenizing chamber located between and in communication with the gas cooling chamber and the desuperheating box gas outlet.

In some embodiments, at least part of the wall portion of the desuperheating box is a double-layer wall, the double-layer wall comprises an inner layer wall and an outer layer wall arranged outside the inner layer wall, the cavity wall of the air outlet and homogenizing cavity comprises at least part of the inner layer wall and at least part of the outer layer wall, and the desuperheating box gas outlet is arranged on the outer layer wall.

In some embodiments, the desuperheating box gas outlet comprises a plurality of second gas outlet holes distributed on the outer wall.

In some embodiments of the desuperheating assembly, the plurality of second gas outlet holes form a plurality of groups of gas outlet holes of successively decreasing diameter from a side proximate to the desuperheating box gas inlet to a side distal to the desuperheating box gas inlet.

In some embodiments, the desuperheating assembly satisfies:

ε＝0.1-0.5；

wherein T is _in The unit of the temperature of the gaseous working medium at the gas inlet of the desuperheating box is K;

T _wall the average temperature of the outer surface of the desuperheated pipe section is expressed as K;

ρ is the density of the gaseous working medium at the gas inlet of the removed overheat box, kg/m ³ ；

D is the diameter of a through-flow part at the air inlet hole of the desuperheating box air inlet, and the unit is m;

l is the length of the desuperheated pipe section, and the unit is m;

n is the number of the first heat exchange tubes;

d is the outer diameter of the first heat exchange tube, and the unit is m;

d _k the equivalent diameter of the tube distribution of the first heat exchange tube is m;

Lambda is the heat conductivity coefficient of the gaseous working medium in the inner cavity of the desuperheating box at the average temperature, and the unit is W/(m.times.K);

C _p the unit of the specific heat capacity of the gaseous working medium in the inner cavity of the desuperheating box at the average temperature is kJ/(kg x K);

mu is the viscosity of the gaseous working medium in the inner cavity of the desuperheating box at the average temperature, and the unit is P _a *s；

μ _w The unit is P for the viscosity of the gaseous working medium in the inner cavity of the desuperheating box at the average temperature of the pipe wall of the desuperheating pipe section _a *s；

P _t The unit is m for the pipe spacing of the first heat exchange pipe;

D _k the unit is m for the inner diameter of the shell of the condenser where the desuperheating box is positioned;

l _b the unit is m, which is the distance between the adjacent baffle plates;

u is the flow velocity calculated according to the flow section of the superheating area, m/s;

P _r is the Plantt number;

epsilon is a constant and takes a value of 0.1-0.5.

In some embodiments of the desuperheating assembly, the number of baffles satisfies:

wherein,,

ΔP is the pressure drop generated by the gaseous working fluid flowing through the desuperheating component;

n _b is the total number of baffles;

c is a constant and takes a value of 0.02-0.25.

In some embodiments, the baffle is provided with a vent hole through which the gaseous working medium flows.

In some embodiments, the de-superheating assembly, the vent hole has a diameter of 2mm to 8mm; and/or the total flow area of all the vent holes on the baffle plate accounts for 1/8-3/4 of the total area of the baffle plate.

In some embodiments, the desuperheating assembly comprises at least two baffles having an average hydraulic diameter D _d In the extending direction of the first heat exchange tube, the distance between two adjacent baffle plates is l _b ，D _d And l _b The following relationship is satisfied:

wherein Δp is the pressure drop generated by the flow of the gaseous working fluid through the desuperheating assembly;

c is a constant, and the value is 0.3-1.5;

v ₀ The unit is m/s for the average flow velocity of the gaseous working medium flowing through the at least two baffle plates;

n is the number of the first heat exchange tubes;

d is the outer diameter of the first heat exchange tube, and the unit is m.

In some embodiments of the desuperheating assembly, the first heat exchange tube has an outer diameter d that satisfies the following relationship:

ρ is the density of the gaseous working medium at the gas inlet of the desuperheating box, kg/m ³ The method comprises the steps of carrying out a first treatment on the surface of the D is the diameter of a through-flow part at the air inlet hole of the desuperheating box air inlet, and the unit is m;

l is the length of the desuperheated pipe section, and the unit is m;

n is the number of the first heat exchange tubes;

C _p for the desuperheating boxThe specific heat capacity of the gaseous working medium in the inner cavity at the average temperature is in kJ/(kg. Times.K);

mu is the viscosity of the gaseous working medium in the inner cavity of the desuperheating box at the average temperature, and the unit is P _a * s; epsilon is a constant and takes a value of 15 to 200;

d _e the equivalent diameter of the tube distribution of the first heat exchange tube is m;

P _t and the unit is m for the pipe spacing of the first heat exchange pipe.

In some embodiments, the desuperheating component comprises an air outlet air-homogenizing plate, wherein the air outlet air-homogenizing plate is arranged in the desuperheating box and is positioned between the air cooling cavity and the air outlet air-homogenizing cavity, and the air outlet air-homogenizing plate is provided with an air outlet air-homogenizing hole communicated with the air cooling cavity and the air outlet air-homogenizing cavity.

In some embodiments, the desuperheating component comprises an air outlet baffle plate region and an air outlet pore plate region, the air outlet baffle plate region corresponds to the region where the baffle plate in the air cooling cavity is located, and the air outlet pore plate region is located at one side of the air outlet baffle plate region away from the desuperheating box air inlet.

In some embodiments of the desuperheating assembly, the ratio of the length L1 of the gas outlet aperture plate zone to the length L2 of the gas outlet baffle zone is 1/10 to 1/2 in the first direction of the desuperheating box.

In the desuperheating component of some embodiments, the air outlet air-equalizing plate is provided with a plurality of air outlet air-equalizing holes, the plurality of air outlet air-equalizing holes comprise a first air outlet air-equalizing hole and a second air outlet air-equalizing hole, and the diameter of the first air outlet air-equalizing hole is larger than that of the second air outlet air-equalizing hole.

In some embodiments, the diameter of the first air outlet vent is 12 mm-20 mm; and/or the diameter of the second air outlet and air equalizing hole is 6 mm-12 mm.

In some embodiments, the desuperheating box gas inlet comprises two third gas inlet holes positioned at two ends of the desuperheating box along a first direction, the desuperheating box gas outlet comprises a third gas outlet hole positioned at the middle of the desuperheating box along the first direction, the second gas outlet gas equalizing hole is close to the edge of the gas outlet gas equalizing plate, perpendicular to the second direction, of the first gas outlet gas equalizing hole relative to the first gas outlet gas equalizing hole, and the ratio of the length of the area of the first gas outlet gas equalizing hole in the second direction to the length of the area of the second gas outlet gas equalizing hole in the second direction is 3-10.

In some embodiments, the desuperheating component is further provided with a gas homogenizing plate liquid passing port on the gas homogenizing plate.

In some embodiments, the desuperheating box gas inlet comprises two third gas inlet holes at both ends of the desuperheating box in the first direction, and the desuperheating box gas outlet comprises a third gas outlet hole at a middle of the desuperheating box in the first direction; the desuperheating component comprises a first partition board, the first partition board is arranged in the gas cooling cavity, the gas cooling cavity is divided into two sub-cooling cavities along the first direction, the two sub-cooling cavities are in one-to-one correspondence with the two third air inlet holes, and each sub-cooling cavity is internally provided with a baffle board.

In some embodiments, the desuperheating assembly further comprises a second partition plate, the second partition plate is located in the sub-cooling cavity and divides the sub-cooling cavity into a first gas cooling cavity and a second gas cooling cavity which are communicated with the desuperheating box gas inlet, a communication port which is communicated with the first gas cooling cavity and the second gas cooling cavity is formed in the second partition plate or between the second partition plate and the desuperheating box, and the baffle plate is arranged in the second gas cooling cavity.

In some embodiments, the desuperheating assembly further comprises a screen disposed on the desuperheating box at the desuperheating box gas outlet configured to separate liquid within the gaseous working fluid passing through the desuperheating box gas outlet.

In the desuperheating assembly of some embodiments,

the desuperheater cartridge further comprises a desuperheater cartridge liquid outlet;

the desuperheating box inner cavity further comprises a liquid collecting cavity, and the liquid collecting cavity is positioned between the gas cooling cavity and the desuperheating box liquid outlet;

the desuperheating component further comprises a liquid separation plate, and a liquid separation plate liquid passing port which is communicated with the gas cooling cavity and the desuperheating box liquid outlet is formed in the liquid separation plate.

In some embodiments, the desuperheating assembly further comprises a drain pipe connected to the desuperheating box and in communication with the desuperheating box liquid outlet.

In some embodiments, the desuperheating assembly further comprises an inlet conduit in communication with the desuperheating box gas inlet.

A second aspect of the present disclosure provides a condenser comprising:

the shell is provided with a gaseous working medium inlet and a liquid working medium outlet;

A desuperheating assembly of the first aspect of the present disclosure, the desuperheating assembly being located within the housing, the desuperheating cartridge and the housing forming a condensing chamber, the gaseous working medium inlet communicating with the desuperheating cartridge gas inlet, the desuperheating cartridge gas outlet communicating with the condensing chamber, the liquid working medium outlet communicating with the condensing chamber; and

and the second heat exchange tube is positioned in the condensation cavity and is configured to condense the gaseous working medium entering the condensation cavity from the gas outlet of the desuperheating box into liquid working medium.

In some embodiments, the condenser further comprises a support plate assembly, the support plate assembly comprises a support plate and a support rod, the desuperheating box is connected to the support plate, the support plate is connected with the inner wall of the shell, and the support rod is connected with the support plate and a tube plate for supporting the second heat exchange tube.

In some embodiments, the shell is cylindrical, the length direction of the desuperheating box extends along the axial direction of the shell, and the first heat exchange tube and the second heat exchange tube extend along the axial direction of the shell.

In some embodiments, the desuperheater cartridge is symmetrically disposed about a plane passing through the axis of the housing, wherein,

The ratio of the distance of the desuperheating box in the radial direction of the shell to the inner diameter of the shell in the section of the plane is 0.1-0.35; and/or

The ratio of the length of the desuperheating box to the length of the shell is 0.4-1 along the axial direction of the shell.

In some embodiments, the ratio of the number of first heat exchange tubes to the sum of the number of first heat exchange tubes and the number of second heat exchange tubes is 3 to 25%.

A third aspect of the present disclosure provides a refrigeration system, including a compressor and a condenser, where the condenser is a condenser according to the second aspect of the present disclosure, and an exhaust port of the compressor is connected to a gaseous working medium inlet of the condenser.

The overheat removing component of the condenser can be installed in the shell of the condenser, the overheat removing box gas inlet of the overheat removing component is connected with the gaseous working medium inlet of the condenser, so that the gaseous working medium enters the overheat removing box inner cavity of the overheat removing box before entering the condensing cavity of the condenser, and is cooled by the overheat removing pipe section in the gas cooling cavity of the overheat removing box, so that the gaseous working medium can fully exchange heat with the overheat removing pipe section in the gas cooling cavity, and the airflow in the overheat removing box can be better organized, thereby being beneficial to improving the heat exchange coefficient of overheat removing heat of the condenser and the overall heat exchange efficiency of the condenser.

Other features of the present disclosure and its advantages will become apparent from the following detailed description of exemplary embodiments of the disclosure, which proceeds with reference to the accompanying drawings.

Drawings

The accompanying drawings, which are included to provide a further understanding of the disclosure, illustrate and explain the present disclosure, and together with the description serve to explain the present disclosure. In the drawings:

fig. 1 is a schematic structural view of a condenser according to a first embodiment of the present disclosure.

Fig. 2 is a schematic structural view of the desuperheating assembly of the condenser shown in fig. 1, without the top plate of the desuperheater box shown.

FIG. 3 is a schematic front view, partially in section, of the band of the desuperheating assembly of FIG. 2.

FIG. 4 is a schematic cross-sectional view of the desuperheating assembly shown in FIG. 3.

Fig. 5 is a schematic cross-sectional structural view of one direction of the desuperheater cartridge of the desuperheater assembly of fig. 2.

Fig. 6 is a schematic cross-sectional view of the desuperheater cartridge of fig. 5 in another direction.

Fig. 7 is a schematic view of a structure of an intake air equalizing plate of the desuperheating assembly shown in fig. 2 in one direction.

Fig. 8 is a schematic view of the intake air equalizing plate shown in fig. 7 in another direction.

Fig. 9 is a schematic view illustrating a connection structure of the desuperheating assembly and the support plate assembly of the condenser shown in fig. 1.

Fig. 10 is a schematic structural view of a heat exchange assembly of a condenser according to a second embodiment of the present disclosure.

Fig. 11 is a schematic cross-sectional structural view of the heat exchange assembly of the condenser of the embodiment shown in fig. 10.

Fig. 12 is a schematic structural view of a combined structure of a desuperheating assembly and an intake pipe of the condenser of the embodiment shown in fig. 10 excluding the first heat exchange tube.

Fig. 13 is an exploded view of the combination structure shown in fig. 12.

Fig. 14 is a schematic view of the composite structure of fig. 13 with the outer wall removed.

Fig. 15 is a schematic cross-sectional view of fig. 14.

Fig. 16 is a schematic side view of fig. 14.

Fig. 17 is a schematic view of the structure of baffles of the desuperheating assembly of the condenser shown in fig. 10.

Fig. 18 is a schematic view of the outer wall of the double wall of the desuperheater box of the desuperheater assembly of the condenser of fig. 10.

Fig. 19 is a schematic view showing a partial structure of the outer wall shown in fig. 18.

Fig. 20 is a schematic structural view of a condenser according to a third embodiment of the present disclosure.

Fig. 21 is a side view of the combination of the desuperheater assembly and the housing of the condenser of fig. 20.

Fig. 22 is a perspective view of the desuperheater assembly of the condenser of fig. 20.

Fig. 23 is an internal structure of the desuperheater assembly in the condenser of fig. 20.

Fig. 24 is a view showing the structure of a first baffle in the condenser shown in fig. 20.

Fig. 25 is a view showing the structure of a second baffle in the condenser shown in fig. 20.

Fig. 26 is a side view of a gas equalization plate in the condenser shown in fig. 20.

Fig. 27 is a top view of a gas equalization plate in the condenser shown in fig. 20.

Fig. 28 is a schematic distribution diagram of air holes on a single plate body of the air-homogenizing plate in the condenser shown in fig. 20.

In fig. 1 to 28, each reference numeral represents:

1. a left water chamber;

2. a left side tube sheet;

3. a shell, a 3A and a gaseous working medium inlet, 3B, a liquid working medium outlet, 3C and a condensation cavity;

4. a second heat exchange tube;

5. a desuperheating component 501, a desuperheating box 5011, a first wall, 5012, a second wall, 5013, a third wall, 5014, a mounting hole plate part, 501A, a desuperheating box gas inlet, 501B, a desuperheating box gas outlet, 501C, a desuperheating box, C1, an air inlet uniform air cavity, C2, a gas cooling cavity, C21, a first gas cooling cavity, C22, a second gas cooling cavity, C3, an air outlet uniform air cavity, C4, a liquid collecting cavity, 501D and a desuperheating box liquid outlet; 502. the air inlet and air homogenizing plate comprises an air inlet and air homogenizing plate, 5021, an air inlet baffle area, 5022, an air inlet pore plate area, 5023, a coaming area, 502A, a first air inlet and air homogenizing hole, 502B, a second air inlet and air homogenizing hole, 503, a first heat exchange tube, 504, an air baffle, 505, an air inlet tube, 506, a baffle, 506A, a through tube, 506B, a vent, 507, an air outlet and air homogenizing plate, 507A, a first air outlet and air homogenizing hole, 507B, a second air outlet and air homogenizing hole, 507C, an air homogenizing plate liquid passing opening, 508, a first partition plate, 509, a second partition plate, 510, a filter screen, 511, a liquid separating plate, 511A, a liquid separating plate liquid passing opening, 512 and a liquid outlet pipe;

6. A support plate assembly 601, a support plate, 602, and a support rod;

7. a right side tube sheet;

8. a right flange;

9. a right water chamber;

10. a right water chamber gasket;

11. a liquid collecting part;

12. left water chamber gasket;

13. a left flange;

14. the water discharging chamber is connected with a pipe;

15. the water feeding chamber is connected with the pipe.

Detailed Description

The following description of the technical solutions in the embodiments of the present disclosure will be made clearly and completely with reference to the accompanying drawings in the embodiments of the present disclosure, and it is apparent that the described embodiments are only some embodiments of the present disclosure, not all embodiments. The following description of at least one exemplary embodiment is merely illustrative in nature and is in no way intended to limit the disclosure, its application, or uses. All other embodiments, which can be made by one of ordinary skill in the art without inventive effort, based on the embodiments in this disclosure are intended to be within the scope of this disclosure.

The relative arrangement of the components and steps, numerical expressions and numerical values set forth in these embodiments do not limit the scope of the present disclosure unless it is specifically stated otherwise. Meanwhile, it should be understood that the sizes of the respective parts shown in the drawings are not drawn in actual scale for convenience of description. Techniques, methods, and apparatus known to one of ordinary skill in the relevant art may not be discussed in detail, but should be considered part of the specification where appropriate. In all examples shown and discussed herein, any specific values should be construed as merely illustrative, and not a limitation. Thus, other examples of the exemplary embodiments may have different values. It should be noted that: like reference numerals and letters denote like items in the following figures, and thus once an item is defined in one figure, no further discussion thereof is necessary in subsequent figures.

In the description of the present disclosure, it should be understood that the use of terms such as "first," "second," etc. for defining components is merely for convenience in distinguishing corresponding components, and the terms are not meant to be construed as limiting the scope of the present disclosure unless otherwise indicated.

In the description of the present disclosure, it should be understood that the azimuth or positional relationships indicated by the azimuth terms such as "front, rear, upper, lower, left, right", "lateral, vertical, horizontal", and "top, bottom", etc., are generally based on the azimuth or positional relationships shown in the drawings, merely to facilitate description of the present disclosure and to simplify the description, and these azimuth terms do not indicate and imply that the apparatus or elements referred to must have a specific azimuth or be configured and operated in a specific azimuth, and thus should not be construed as limiting the scope of protection of the present disclosure; the orientation word "inner and outer" refers to inner and outer relative to the contour of the respective component itself.

As shown in fig. 1-28, embodiments of the present disclosure provide a desuperheating assembly 5 for a condenser. The desuperheating assembly 5 includes a desuperheating box 501 and a first heat exchange tube 503.

The desuperheater cartridge 501 has a desuperheater cartridge cavity 501C and has a desuperheater cartridge gas inlet 501A for receiving gaseous working fluid and a desuperheater cartridge gas outlet 501B for outputting gaseous working fluid in communication with the desuperheater cartridge cavity 501C. The desuperheater chamber 501C includes a gas cooling chamber C2 in communication with a desuperheater gas inlet 501A and a desuperheater gas outlet 501B.

The first heat exchange tube 503 is mounted on the desuperheating box 501, and the first heat exchange tube 503 includes a desuperheating tube section 5031 located in the gas cooling chamber C2, the desuperheating tube section 5031 being configured to cool the gaseous working fluid in the gas cooling chamber C2.

According to the overheat removing component of the condenser, the overheat removing component can be arranged in the shell of the condenser, the overheat removing box gas inlet of the overheat removing component is connected with the gaseous working medium inlet of the condenser, so that the gaseous working medium enters the overheat removing box inner cavity of the overheat removing box before entering the condensing cavity of the condenser, is cooled by the overheat removing pipe section in the gas cooling cavity, is favorable for fully exchanging heat between the gaseous working medium in the gas cooling cavity and the overheat removing pipe section, is favorable for better organizing the airflow flow in the overheat removing box, and is favorable for improving the heat exchange coefficient of overheat removing heat exchange of the condenser and the whole heat exchange efficiency of the condenser.

In the desuperheating assembly 5 of some embodiments, as shown in fig. 1-9, the desuperheating box gas inlet 501A comprises one first inlet aperture located in the middle of the desuperheating box 501 in the first direction and the desuperheating box gas outlet 501B comprises two first outlet apertures located at both ends of the desuperheating box 501 in the first direction, respectively.

In some embodiments of the desuperheating assembly 5, as shown in fig. 10-19, the desuperheating box gas inlet 501A comprises one second inlet aperture located in the middle of the desuperheating box 501 in the first direction and the desuperheating box gas outlet 501B comprises a plurality of second outlet apertures located in the desuperheating box 501 distributed in the first direction.

In the desuperheating assembly 5 of some embodiments, as shown in fig. 20-28, the desuperheating box gas inlet 501A comprises two third inlet holes at both ends of the desuperheating box 501 in the first direction, and the desuperheating box gas outlet 501B comprises a third outlet hole in the middle of the desuperheating box 501 in the first direction.

In some embodiments of the desuperheating assembly 5, as shown in fig. 20-28, the desuperheating box gas inlet 501A is on the same side of the desuperheating box 501 as the desuperheating box gas outlet 501B.

In some embodiments of the desuperheating assembly 5, as shown in fig. 1-9, the desuperheating box gas inlet 501A and the desuperheating box gas outlet 501B are located on opposite sides of the desuperheating box 501; or (b)

In some embodiments of the desuperheating assembly 5, as shown in fig. 10-19, the desuperheating box gas inlet 501A and the desuperheating box gas outlet 501B are located on adjacent sides of the desuperheating box 501.

In the desuperheating assembly 5 of some embodiments, as shown in fig. 1-28, the desuperheating box 501 includes a mounting

orifice portion

5014, 5014', or 5014″ that includes a mounting orifice 5014A through which the first heat exchanging tube 503 penetrates to be mounted on the desuperheating box 501.

In some embodiments of the desuperheating assembly 5, as shown in fig. 1-28, the desuperheating box 501 includes two oppositely disposed mounting

orifice portions

5014, 5014' or 5014″ into which the first heat exchange tube 503 simultaneously penetrates for mounting on the desuperheating box 501.

In some embodiments of the desuperheating assembly 5, as shown in fig. 1-28, the first heat exchange tube 503 further includes a cooling tube segment 5032 located outside of the desuperheating box 501.

In some embodiments of the desuperheating assembly 5, as shown in fig. 1-28, the desuperheating assembly 5 includes a plurality of first heat exchange tubes 503 arranged in a side-by-side, spaced relationship.

In some embodiments of the desuperheating assembly 5, as shown in fig. 1-28, the first heat exchange tube 503 is a straight tube extending along a first direction, the desuperheating assembly 5 is symmetrical about a surface perpendicular to the first direction and/or the desuperheating assembly 5 is symmetrical about a surface parallel to the first direction.

In the desuperheating assembly 5 of some embodiments, as shown in fig. 1-9, the desuperheating box gas inlet 501A comprises a first gas inlet hole located in the middle of the desuperheating box 501 in the first direction, and the desuperheating box gas outlet 501B comprises two first gas outlet holes located at both ends of the desuperheating box 501 in the first direction, respectively, the diameter of the first gas inlet hole

Diameter +.>

Satisfy->

In the desuperheating assembly 5 of some embodiments, as shown in fig. 1-9, the desuperheating box interior cavity 501C further includes an inlet gas plenum cavity C1, the inlet gas plenum cavity C1 being located between the desuperheating box gas inlet 501A and the gas cooling cavity C2 and in communication with the desuperheating box gas inlet 501A and the gas cooling cavity C2; the desuperheating assembly 5 further comprises an air inlet air homogenizing plate 502 positioned in the desuperheating box 501, wherein the air inlet air homogenizing plate 502 is positioned between the air inlet air homogenizing cavity C1 and the air cooling cavity C2 to separate the air inlet air homogenizing cavity C1 and the air cooling cavity C2, and a plurality of air inlet air homogenizing holes communicated with the air inlet air homogenizing cavity C1 and the air cooling cavity C2 are formed in the air inlet air homogenizing plate 502.

In the desuperheating assembly 5 of some embodiments, as shown in fig. 1-9, the intake air equalizing plate 502 includes an intake baffle region 5021 opposite the intake air direction and an intake orifice region 5022 connected to the intake baffle region 5021, with a plurality of intake air equalizing holes located on the intake orifice region 5022.

In the desuperheating assembly 5 of some embodiments, as shown in fig. 1 to 9, the plurality of intake air equalizing holes are divided into a plurality of intake air equalizing hole groups along a direction from the intake baffle region 5021 to the intake orifice region 5022, wherein a diameter of a first intake air equalizing hole 502A of the intake air equalizing hole group near the intake baffle region 5021 is smaller than a diameter of a second intake air equalizing hole 502B of the intake air equalizing hole group far from the intake baffle region 5021.

In the desuperheating assembly 5 of some embodiments, as shown in fig. 1-9, the inlet orifice area 5022 includes two inlet air equalizing hole groups, the diameter of the first inlet air equalizing hole 502A of the inlet air equalizing hole groups proximate the inlet baffle area 5021

Diameter +.>

Satisfy->

In some embodiments of the desuperheating assembly 5, as shown in FIGS. 1-9, the diameter of the first inlet aperture of the desuperheating box gas inlet 501A is

The pressure drop deltap of the gaseous working fluid flowing through the desuperheating component 5 is:

ΔP＝Cρv ² ；

ρ is the density of the gaseous working medium of the desuperheating box gas inlet 501A, and the unit is kg/m ³ ；

v is the flow rate of the gaseous working medium from the superheating box gas inlet 501A, and the unit is m/s;

n ₁ is of uniform pore diameter

The number of first intake air equalizing holes 502A of the equalizing hole group;

n ₂ Is of uniform pore diameter

The number of second intake air equalizing holes 502B of the equalizing hole group;

and->

Is in m. />

In some embodiments of the desuperheating assembly 5, as shown in fig. 1-9, the desuperheating assembly 5 includes a gas baffle 504, the gas baffle 504 being located on the incoming side of the inlet gas baffle 502 facing the gaseous working fluid.

In some embodiments, desuperheating assembly 5, as in FIG. 1As shown in the view of figure 9,

n is the number of first heat exchange tubes 503;

d is the outer diameter of the first heat exchange tube 503 in m;

l is the length of the desuperheater pipe section 5031, and the unit is m;

T _in the unit is K for the temperature of the gaseous working medium at the gas inlet 501A of the desuperheating box;

T _out the unit is K for the temperature of the gaseous working medium at the gas outlet 501B of the desuperheating box;

T _wall for the removal of the outer surface average temperature of the superheater tube section 5031, the unit is K.

In various embodiments of the present disclosure, the average temperature of the gaseous working fluid in the desuperheater 501C is referred to generally as T _in And T is _out Average value of (2).

In some embodiments of desuperheating assembly 5, as shown in fig. 10-28, desuperheating assembly 5 further includes a baffle 506 disposed within gas-cooling chamber C2 and configured to form a baffle flow path P within gas-cooling chamber C2, an inlet end PA of baffle flow path P in communication with desuperheating box gas inlet 501A and an outlet end PB of baffle flow path P in communication with desuperheating box gas outlet 501B, at least a portion of desuperheating tube section 5031 being located within baffle flow path P.

In the desuperheating assembly 5 of some embodiments, as shown in fig. 10-28, a plurality of baffles 506 are spaced apart within the gas-cooling chamber C2 along the direction of extension of the first heat exchange tubes 503.

In the desuperheating assembly 5 of some embodiments, as shown in fig. 10 to 19, the inlet end PA of the baffle flow passage P is located at the middle of the gas cooling chamber C2 in the axial direction of the first heat exchange tube 503, and the outlet end PB of the baffle flow passage P is located at the end of the gas cooling chamber C2 in the axial direction of the first heat exchange tube 503.

In the desuperheating assembly 5 of some embodiments, as shown in fig. 20 to 28, the inlet end PA of the baffle flow passage P is located at an end of the gas cooling chamber C2 in the axial direction of the first heat exchange tube 503, and the outlet end PB of the baffle flow passage P is located at a middle of the gas cooling chamber C2 in the axial direction of the first heat exchange tube 503.

In the desuperheating assembly 5 of some embodiments, as shown in fig. 10 to 28, the desuperheating assembly 5 includes two baffle flow passages P arranged in the axial direction of the first heat exchange tube 503.

In some embodiments of desuperheating assembly 5, as shown in fig. 10-28, baffle 506 is disposed at an angle to the axis of desuperheating tube section 5031, with aperture 506A through which desuperheating tube section 5031 passes.

In the desuperheating assembly 5 of some embodiments, as shown in fig. 10-28, the desuperheating box interior cavity 501C includes an outlet gas plenum cavity C3, the outlet gas plenum cavity C3 being located between the gas cooling cavity C2 and the desuperheating box gas outlet 501B and in communication with the gas cooling cavity C2 and the desuperheating box gas outlet 501B.

In the desuperheating assembly 5 of some embodiments, as shown in fig. 10-19, at least part of the wall portion of the desuperheating box 501 is a double wall comprising an inner wall 5012 'and an outer wall 5016' disposed outside the inner wall 5012', and the chamber walls of the gas-homogenizing chamber C3 comprise at least part of the inner wall 5012' and at least part of the outer wall 5016', and the desuperheating box gas outlet 501B is disposed on the outer wall 5016'.

In some embodiments of the desuperheating assembly 5, as shown in fig. 10-19, the desuperheating box gas outlet 501B includes a plurality of second gas outlet holes distributed over the outer wall 5016'.

In the desuperheating assembly 5 of some embodiments, as shown in fig. 10-19, the plurality of second gas outlet holes form a plurality of gas outlet hole groups of successively decreasing diameter from a side closer to the desuperheating box gas inlet 501A to a side farther from the desuperheating box gas inlet 501A.

In some embodiments of the desuperheating assembly 5, as shown in fig. 10-19, the desuperheating assembly 5 satisfies:

ε＝0.1-0.5；

Wherein T is _in The temperature of the gaseous working medium at the gas inlet 501A of the desuperheating box is shown as K;

T _wall the average temperature of the outer surface of the de-superheating pipe section 5301 is given by K;

ρ is the density of the gaseous working medium at the desuperheating box gas inlet 501A, kg/m ³ ；

D is the diameter of the through-flow portion at the inlet hole of the desuperheating box gas inlet 501A, for example, the inner diameter of the inlet pipe 505 connected to the desuperheating box gas inlet 501A in m;

l is the length of the desuperheater pipe section 5031, and the unit is m;

n is the number of first heat exchange tubes 503;

d is the outer diameter of the first heat exchange tube 503 in m;

d _k the equivalent diameter of the first heat exchange tube 503 is given by m;

λ is the coefficient of thermal conductivity of the gaseous working medium in the desuperheating box cavity 501C at the average temperature, and the unit is W/(m×k);

C _p for removing the specific heat capacity of the gaseous working medium in the inner cavity 501C of the superheating box at the average temperature, the unit is kJ/(kg×k);

mu is the viscosity of the gaseous working medium in the inner cavity 501C of the desuperheating box at the average temperature, and the unit is P _a *s；

μ _w For removing viscosity of gaseous working medium in the inner cavity 501C of the superheating box at the average temperature of the pipe wall of the superheating pipe section 5031, the unit is P _a *s；

P _t The unit is m for the tube pitch of the first heat exchange tube 503;

D _k the unit is m for removing the inner diameter of the shell 3 of the condenser where the thermal box 5 is located;

l _b is the spacing of adjacent baffles 506 in m;

P _r is the Plantt number;

epsilon is a constant and takes a value of 0.1-0.5.

In some embodiments of desuperheating assembly 5, as shown in fig. 10-19, the number of baffles 506 satisfies:

wherein,,

Δp is the pressure drop generated by the flow of gaseous working fluid through desuperheating assembly 5;

n _b is the total number of baffles 506;

c is a constant and takes a value of 0.02-0.25.

In some embodiments of desuperheating assembly 5, as shown in fig. 20-28, baffle 506 is provided with a vent 506B through which gaseous working fluid flows.

In some embodiments of the desuperheating assembly 5, as shown in fig. 20-28, the diameter of the vent 506B is 2 mm-8 mm; and/or the total flow area of all of the vents 506B on the baffle 506 is 1/8 to 3/4 of the total area of the baffle 506.

In some embodiments of the desuperheating assembly 5, as shown in fig. 20-28, the desuperheating assembly 5 includes at least two baffles 506, the at least two baffles 506 having an average hydraulic diameter D _d And the distance between two adjacent baffles 506 in the extending direction of the first heat exchange tube 503 is l _b ，D _d And l _b The following relationship is satisfied:

wherein deltaP is the pressure drop generated by the gaseous working fluid flowing through the desuperheating component 5;

c is a constant, and the value is 0.3-1.5;

v ₀ The average flow rate of the gaseous working medium flowing through at least two baffle plates 506 is expressed as m/s;

d is the diameter of a through-flow part at the air inlet hole of the desuperheating box air inlet 501A, and the unit is m;

n is the number of first heat exchange tubes 503;

d is the outer diameter of the first heat exchange tube 503 in m.

The first heat exchange tube 503 has an outer diameter d, which satisfies the following relationship:

wherein T is _in The unit is K for the temperature of the gaseous working medium at the gas inlet 501A of the desuperheating box;

T _out the unit is K, which is the average temperature of the gaseous working medium at the gas outlet 501B of the desuperheating box;

T _wall to remove the exterior of the superheater tube section 5301The surface average temperature is expressed as K;

L is the length of the desuperheater pipe section 5031, and the unit is m;

n is the number of first heat exchange tubes 503;

cp is the specific heat capacity of the gaseous working medium in the inner cavity 501C of the desuperheating box at the average temperature, and the unit is kJ/(kg. Times.K);

Epsilon is a constant and takes a value of 15 to 200;

d _e the equivalent diameter of the first heat exchange tube 503 is given by m;

P _t the unit is m for the tube pitch of the first heat exchange tube 503.

In the desuperheating component 5 of some embodiments, as shown in fig. 20 to 28, the desuperheating component 5 includes an air outlet air-homogenizing plate 507, the air outlet air-homogenizing plate 507 is disposed in the desuperheating box 501 and is located between the air cooling cavity C2 and the air outlet air-homogenizing cavity C3, and air outlet air-homogenizing holes communicating the air cooling cavity C2 and the air outlet air-homogenizing cavity C3 are disposed on the air outlet air-homogenizing plate 507.

In some embodiments of the desuperheating assembly 5, as shown in fig. 20-28, the gas outlet baffle 507 has a gas outlet baffle region 5071 and a gas outlet orifice region 5072, the gas outlet baffle region 5071 corresponding to the region of the baffle 506 within the gas cooling chamber C2, the gas outlet orifice region 5072 being located on the side of the gas outlet baffle region 5071 remote from the desuperheating box gas inlet 501A.

In some embodiments of the desuperheating assembly 5, as shown in fig. 20-28, the ratio of the length L1 of the perforated plate region 5072 to the length L2 of the baffle region 5071 is 1/10-1/2 in the first direction of the desuperheating box 501.

In the desuperheating component 5 of some embodiments, as shown in fig. 20 to 28, a plurality of air outlet holes are formed on the air outlet plate 507, and the plurality of air outlet holes include a first air outlet hole 507A and a second air outlet hole 507B, where the diameter of the first air outlet hole 507A is greater than the diameter of the second air outlet hole 507B.

In the desuperheating module 5 of some embodiments, as shown in fig. 20 to 28, the diameter of the first air outlet holes 507A is 12mm to 20mm; and/or the diameter of the second air outlet and equalizing hole 507B is 6 mm-12 mm.

In the desuperheating assembly 5 of some embodiments, as shown in fig. 20 to 28, the desuperheating box gas inlet 501A includes two third gas inlet holes at both ends of the desuperheating box 501 in the first direction, the desuperheating box gas outlet 501B includes a third gas outlet hole at the middle of the desuperheating box 501 in the first direction, the second gas outlet holes 507B are close to the edge of the gas outlet plate 507A in the second direction perpendicular to the first direction with respect to the first gas outlet holes 507A, and the ratio of the length of the region of the first gas outlet holes 507A in the second direction to the length of the region of the second gas outlet holes 507B in the second direction is 3 to 10.

In some embodiments of the desuperheating assembly 5, as shown in fig. 20-28, the gas outlet equalization plate 507 is further provided with equalization plate liquid passing openings 507C.

In the desuperheating assembly 5 of some embodiments, as shown in fig. 20-28, the desuperheating box gas inlet 501A comprises two third gas inlet holes at both ends of the desuperheating box 501 in the first direction, and the desuperheating box gas outlet 501B comprises a third gas outlet hole at the middle of the desuperheating box 501 in the first direction; the desuperheating component 5 comprises a first partition plate 508, the first partition plate 508 is arranged in the gas cooling cavity C2 and divides the gas cooling cavity C2 into two sub-cooling cavities along the first direction, the two sub-cooling cavities are in one-to-one correspondence with the two third air inlet holes, and a baffle plate 506 is arranged in each sub-cooling cavity.

In the desuperheating assembly 5 of some embodiments, as shown in fig. 20-28, a second partition 509 is further included, the second partition 509 is located in the sub-cooling chamber and divides the sub-cooling chamber into a first gas cooling chamber C21 and a second gas cooling chamber C22 that are in communication with the desuperheating box gas inlet 501A, a communication port is provided on the second partition 509 or between the second partition 509 and the desuperheating box 501 to communicate the first gas cooling chamber C21 and the second gas cooling chamber C22, and a baffle 506 is disposed in the second gas cooling chamber C22.

In the desuperheating assembly 5 of some embodiments, as shown in fig. 20-28, a screen 510 is further included, the screen 510 being disposed on the desuperheating box 501 and located at the desuperheating box gas outlet 501B and configured to separate liquid within the gaseous working fluid passing through the desuperheating box gas outlet 501B.

In some embodiments of the desuperheating assembly 5, as shown in fig. 20-28, the desuperheating box 501 further includes a desuperheating box liquid outlet 501D; the desuperheater cartridge cavity 501C also includes a liquid collection cavity C4, the liquid collection cavity C4 being located between the gas cooling cavity C2 and the desuperheater cartridge liquid outlet 501D; the desuperheating assembly 5 further comprises a liquid baffle 511, and a liquid baffle passing port 511A is formed in the liquid baffle 511 for communicating the gas cooling chamber C2 with the desuperheating box liquid outlet 501D.

In some embodiments of the desuperheating assembly 5, as shown in fig. 20-28, a drain pipe 512 is also included, the drain pipe 512 being connected to the desuperheating box 501 and in communication with the desuperheating box liquid outlet 501D.

In some embodiments of the desuperheating assembly 5, as shown in fig. 1-28, the desuperheating assembly 5 further includes an inlet pipe 505, the inlet pipe 505 being in communication with the desuperheating box gas inlet 501A.

The present disclosure also provides a common condenser, as shown in fig. 1 to 28, including a housing 3, a desuperheating assembly 5 of an embodiment of the present disclosure, and a second heat exchange tube 4.

The housing 3 has a gaseous working medium inlet 3A and a liquid working medium outlet 3B.

The desuperheating component 5 is located in the shell 3, the desuperheating box 501 and the shell 3 form a condensation cavity 3C, the gaseous working medium inlet 3A is communicated with the desuperheating box gas inlet 501A, the desuperheating box gas outlet 501B is communicated with the condensation cavity 3C, and the liquid working medium outlet 3B is communicated with the condensation cavity 3C.

The second heat exchange tube 4 is located in the condensation chamber 3C and is configured to condense the gaseous working fluid entering the condensation chamber 3C from the desuperheating box gas outlet 501B into a liquid working fluid.

The condenser of the presently disclosed embodiments has the same advantages as the desuperheating assembly 5 of the presently disclosed embodiments.

In the condenser of some embodiments, as shown in fig. 1 to 28, the condenser further comprises a support plate assembly 6 including a support plate 601 and a support rod 602, the desuperheater cartridge 501 is connected to the support plate 601, the support plate 601 is connected to the inner wall of the shell 3, and the support rod 602 is connected to the support plate 601 and the tube sheet for supporting the second heat exchange tube 4 (e.g., the left-side tube sheet 2 and/or the right-side tube sheet 7 in fig. 1 and 20).

In the condenser of some embodiments, as shown in fig. 1 to 28, the housing 3 is cylindrical, the length direction of the desuperheater cartridge 501 extends in the axial direction of the housing 3, and the first heat exchange tube 503 and the second heat exchange tube 4 extend in the axial direction of the housing 3.

In some embodiments of the condenser, as shown in fig. 1-28, the desuperheater cartridge 501 is symmetrically disposed about a plane passing through the axis of the housing 3, wherein,

the ratio of the distance in the radial direction of the housing 3 to the inner diameter of the housing 3 of the desuperheating box 501 in the plane cross section is 0.1 to 0.35; and/or the ratio of the length of the desuperheater cartridge 501 to the length of the housing 3 is 0.4-1 in the axial direction of the housing.

In the condenser of some embodiments, as shown in fig. 1 to 28, the ratio of the number of the first heat exchange tubes 503 to the sum of the numbers of the first heat exchange tubes 503 and the second heat exchange tubes 4 is 3 to 25%.

The embodiment of the disclosure also provides a refrigeration system, which comprises a compressor and the condenser of the embodiment of the disclosure, wherein an exhaust port of the compressor is connected with a gaseous working medium inlet 3A of the condenser.

The refrigeration system of the present disclosure has the same advantages as the desuperheating assembly 5 and condenser of the present disclosure.

The desuperheating assembly 5, condenser, and refrigeration system of an embodiment of the present disclosure are further described below in conjunction with fig. 1-28. In addition, the technical features referred to in the different embodiments of the present disclosure described below may be combined with each other as long as they do not make a conflict with each other.

Fig. 1 to 9 show a condenser and its desuperheating assembly 5 according to a first embodiment of the present disclosure.

As shown in fig. 1, the condenser of the embodiment of the present disclosure is a horizontal condenser, which is used as a condenser of a refrigeration system. In this embodiment, the gaseous working medium is a gaseous refrigerant, and the liquid working medium is a liquid refrigerant.

As shown in fig. 1, the horizontal condenser comprises a left water chamber 1, a left side tube plate 2, a shell 3, a heat exchange tube 4, a desuperheating component 5, a support plate component 6, a right side tube plate 7, a right side flange 8, a right water chamber 9, a right water chamber gasket 10, a liquid collecting part 11, a left water chamber gasket 12, a left side flange 13, a lower water chamber connecting pipe 14 and an upper water chamber connecting pipe 15. The air inlet pipe 505 of the desuperheating component 5 is connected with the gaseous working medium inlet 3A, and the liquid collecting part 11 is connected with the liquid working medium outlet 3B.

The left water chamber component consisting of the left water chamber 1, the left water chamber gasket 12, the left flange 13, the lower water chamber connecting pipe 14 and the upper water chamber connecting pipe 15 is positioned at the left side of the shell 3, and sequentially passes through the left side tube plate 2, the left water chamber gasket 12 and the left flange 13 to be connected with the left end of the shell 3, while the right water chamber 9 sequentially passes through the right side tube plate 7, the right water chamber gasket 10 and the right flange 8 to be connected with the right end of the shell 3. The desuperheating assembly 5 is positioned on the housing 3 by a centrally positioned support plate assembly 6. The two ends of the first heat exchange tube 503 and the second heat exchange tube 4 are respectively arranged on the left side tube plate 2 and/or the right side tube plate 7 and are communicated with the left water chamber 1 and the right water chamber 9.

As shown in fig. 1 to 6 and 9, the desuperheating box 501 has a desuperheating box inner cavity 501C and has a desuperheating box gas inlet 501A and a desuperheating box gas outlet 501B, an air inlet pipe 505 and the desuperheating box 501 are connected to the desuperheating box gas inlet 501A, the air inlet pipe 505 passes through the gaseous working medium inlet 3A of the condenser to communicate the desuperheating box gas inlet 501A with the gaseous working medium inlet 3A, and the orifice of the air inlet pipe 505 forms a through-flow part of an air inlet hole of the desuperheating box gas inlet 501A.

As shown in fig. 1 to 6 and 9, the desuperheating box 501 includes a first wall 5011, a second wall 5012 spaced from the first wall 5011, two third walls 5013 respectively located on both sides of the first wall 5011 and the second wall 5012 and connecting the first wall 5011 and the second wall 5012, and two mounting hole plate portions 5014 in the form of two sealing plates respectively connected to both ends of the first wall 5011, the second wall 5012 and the third wall 5013, wherein a portion of the middle portion of the first heat exchange tube 503 located in the desuperheating box cavity 501C is a desuperheating tube section 5031, a portion of both ends of the first heat exchange tube 503 located in the condensing cavity 3C is a cooling tube section 5032, and through-holes 5014A for the first heat exchange tube 503 to pass through are provided in the mounting hole plate portions 5014. The desuperheater gas inlet 501A is provided on the first wall 5011 and the desuperheater gas outlet 501B is provided on the second wall 5012.

As shown in fig. 1 to 3 and 9, the housing 3 of the condenser has a cylindrical shape, the desuperheater 501 has a desuperheater cavity 501C, and extends in the axial direction of the housing 3, and the first heat exchange tube 503 and the second heat exchange tube 4 extend in the axial direction of the housing. The longitudinal direction of the desuperheater cartridge 501 is a first direction extending in the axial direction of the housing 3. The plurality of first heat exchange tubes 503 are arranged side by side at intervals and extend in the first direction. The plurality of second heat exchange tubes 4 are arranged side by side at intervals and extend in the first direction.

As shown in fig. 1 to 6 and 9, the desuperheating box gas inlet 501A is located in the middle of the desuperheating box 501 on the opposite side of the gaseous working medium inlet 3A in the first direction, and the desuperheating box gas outlet 501B is located at the end of the desuperheating box 501 on the side of the desuperheating box 501 in the first direction away from the gaseous working medium inlet 3A.

As shown in fig. 1-9, the desuperheating box gas outlet 501B comprises two first gas outlet holes that are symmetrical with respect to the desuperheating box gas inlet 501A.

As shown in FIG. 5, the desuperheater gas inlet 501A comprises a first inlet orifice having a diameter

Diameter +.f. of two first gas outlets to the desuperheating box gas outlet 501B>

Satisfy->

As shown in fig. 9, the condenser further includes a support plate assembly 6, the support plate assembly 6 includes a support plate 601, the desuperheater cartridge 501 is connected to the support plate 601, and the support plate 601 is connected to the inner wall of the housing 3. The support plate assembly 6 further includes a support rod 602, and the support rod 602 connects the support plate 601 and the tube sheet (left-side tube sheet 2 and/or right-side tube sheet 7) for supporting the second heat exchange tube 4. In this embodiment, both ends of the first heat exchange tube 503 and both ends of the second heat exchange tube 4 are respectively supported on the left side tube sheet 2 and/or the right side tube sheet 7.

The desuperheating assembly 5 and the support plate assembly 6 may be connected as one piece prior to assembly with the housing 3 for integral installation positioning.

The desuperheating box 501 is arranged symmetrically with respect to a plane passing through the center line of the gaseous medium inlet 3A and the axis of the housing 3, wherein the ratio of the distance in the radial direction of the housing 3 of the section of the desuperheating box 501 in this plane to the inner diameter of the housing 3 is 0.1 to 0.35, for example 0.2. The ratio of the length of the desuperheater cartridge 501 to the length of the casing 3 is 0.4 to 1, for example, 0.6, 0.8, etc.

The relative sizes of the desuperheating box 501 and the shell 3 are reasonably set, so that the reasonable division of the heat exchange space between desuperheating heat exchange and condensation heat exchange is facilitated, the desuperheating of the gaseous working medium is fully realized by utilizing the first heat exchange tube 503, and the formation of liquid working medium due to the excessive cooling of the gaseous working medium in the inner cavity 501C of the desuperheating box is prevented.

The ratio of the number of the first heat exchange tubes 503 to the sum of the numbers of the first heat exchange tubes 503 and the second heat exchange tubes 4 is 3 to 20%. The reasonable setting of the proportion is beneficial to fully realizing the desuperheating of the gaseous working medium by using the first heat exchange tube 503 and preventing the gaseous working medium from being excessively cooled in the inner cavity 501C of the desuperheating box to form a liquid working medium.

After the condenser is positioned and installed, the axis of the shell 3 is horizontal.

As shown in fig. 1 to 4 and fig. 6 to 9, the desuperheating assembly 5 includes an intake air equalizing plate 502 having a plurality of air equalizing holes, the intake air equalizing plate 502 is located in the desuperheating box inner cavity 501C and is disposed between the desuperheating box gas outlet 501A and the desuperheating box gas outlet 501B, and the desuperheating pipe section 5031 is located in the gas cooling cavity C2 between the intake air equalizing plate 502 and the desuperheating box gas outlet 501B. The desuperheating box cavity 501C between the desuperheating box gas outlet 501A and the inlet gas plenum plate 502 forms an inlet gas plenum C1. The intake air equalizing plate 502 is substantially parallel to the first heat exchange pipe 503. The inlet gas equalization plate 502 allows gaseous fluid to flow generally perpendicular to the axial direction of the first heat exchange tube 503 and uniformly through the desuperheater tube segment 5301 within the superheater box inner chamber 501C. Therefore, the heat exchange efficiency of the gaseous working medium and the superheating pipe section 5031 in the superheating box inner cavity 501C is improved, and the overall heat exchange efficiency of the condenser is improved.

As shown in fig. 1 to 4 and fig. 6 to 9, the intake air equalizing plate 502 includes an intake baffle region 5021 opposite to the intake air direction and an intake orifice region 5022 connected to the intake baffle region 5021, and the equalizing holes are located on the intake orifice region 5022. Providing the inlet baffle region 5021 facilitates preventing the gaseous working fluid flow from directly rushing over the first heat exchange tube 503.

As shown in fig. 1 to 4 and 6 to 9, the plurality of air holes are divided into a plurality of air hole groups along the direction from the air inlet baffle region 5021 to the air inlet orifice region 5022, wherein the diameter of the first air inlet air holes 502A of the air hole group close to the air inlet baffle region 5021 is smaller than the diameter of the second air inlet air holes 502B of the air hole group far from the air inlet baffle region 5021.

As shown in fig. 1 to 4 and fig. 6 to 9, the air intake orifice region 5022 includes two air equalizing hole groups, and the diameter of the first air intake air equalizing hole 502A of the air equalizing hole group near the air intake baffle region 5021

Diameter +.>

Satisfy->

The diameter of the air equalizing hole is reasonably set, so that gaseous working medium uniformly flows through the superheating pipe section 5031 in the inner cavity 501C of the superheating box, and the gaseous working medium and all parts of the superheating pipe section 5031 in the inner cavity 501C of the superheating box can uniformly exchange heat, and the overall heat efficiency of the condenser can be improved.

In the embodiment shown in fig. 1 to 9, the diameter of the first air inlet hole as the desuperheating box air inlet 501A is

ΔP＝Cρv ²

wherein ρ is the density of the gaseous working medium of the desuperheating box gas inlet 501A, and the unit is kg/m ³ ；

n ₁ is of uniform pore diameter

n ₂ is of uniform pore diameter

and->

Is in m.

The value of C is changed by reasonably controlling the opening parameters on the air homogenizing plate, thereby achieving the purpose of controlling the pressure drop of the heat exchanger and leading the heat exchanger to be specialLi Huanre the pressure drop is controlled within a reasonable interval. The pressure drop DeltaP is proportional to C and follows

Is decreased with an increase of +.>

And->

Is increased by an increase in (a). Thus, the pressure drop deltap of the gaseous working medium flowing through the desuperheating component 5 can be controlled in a reasonable range by reasonably designing the diameter of the desuperheating box gas inlet 501A and the diameters of all groups of air holes.

As shown in fig. 1 to 4 and fig. 6 to 9, the air inlet and homogenizing plate 502 further includes a coaming region 5023, the coaming region 5023 is located at the edges of the air inlet baffle region 5021 and the air inlet orifice region 5022 and forms an included angle with the air inlet baffle region 5021 and the air inlet orifice region 5022, and the coaming region 5023 is connected with the desuperheating box 501.

As shown in fig. 1 to 4 and 6 to 9, the desuperheating assembly 5 includes a gas baffle 504, and the gas baffle 504 is located on the side of the gas inlet baffle region 5021 facing the incoming flow of gaseous working fluid.

The air baffle 504 can be blocked on one side of the air inlet air-equalizing plate 502 where gaseous working medium flows, so that air flow is prevented from directly rushing into the air inlet air-equalizing plate 502.

In the embodiment shown in figures 1 to 9,

n is the number of first heat exchange tubes 503;

d is the outer diameter of the first heat exchange tube 503 in m;

l is the length of the desuperheater pipe section 5031, and the unit is m;

T _in to remove the overheat boxThe temperature of the gaseous working medium at the gas inlet 501A is expressed as K;

With the increase of alpha, the smaller the desuperheating heat exchange coefficient of the heat exchanger is on the premise of unchanged total heat exchange quantity. The quantity and the size parameters (including the outer diameter and the length) of the heat exchange tubes are kept within the range of the reasonable interval of the existing heat exchange design by controlling the parameter alpha, so that the heat exchanger can adapt to different working conditions.

In the horizontal condenser of the embodiment of the present disclosure, the desuperheating assembly 5 is located at the upper portion of the inner space of the housing 3 of the condenser. The cross section of the desuperheating box 501 perpendicular to the housing 3 presents a trapezoid with a small upper part and a large lower part. The superheated gaseous refrigerant enters the desuperheating box inner cavity 501C of the desuperheating box 501 of the desuperheating assembly 5 through the air inlet pipe 505, exchanges heat with the desuperheating pipe section 5301 in the gas cooling cavity C2 thereof, cools to a saturated state, and flows out of the two first air outlet holes serving as the desuperheating box gas outlets 501B on the second wall 5012 at the bottom of the desuperheating box 501 along the axial two ends of the shell 3 and enters the condensation cavity 3C of the condenser for phase change.

The disclosed embodiment adds a built-in desuperheating assembly 5 for enhancing single-phase sensible heat exchange as compared to the horizontal condenser of the related art. The superheated gaseous refrigerant enters the desuperheater 501 of the superheating assembly 5 through the intake pipe 505. The gaseous refrigerant collides with the gas baffle 504 on the lower side thereof and is branched toward the gas inlet orifice areas 5022 of the gas inlet and equalizing plate 502 on both sides in the axial direction of the housing 3 of the condenser. The split gaseous refrigerant enters the gas cooling cavity C2 after passing through the plurality of first air inlet and air equalizing holes 502A and the second air inlet and air equalizing holes 502B on the air inlet orifice area 5022, exchanges heat with the desuperheating pipe section 5301 in the gas cooling cavity C2, is taken away by cooling medium such as cooling water in the desuperheating pipe section 5301 to cool, is in a saturated state or a nearly saturated state, and flows into the condensation cavity 3C from the two first air outlet holes serving as the desuperheating box gas outlet 501B on the second wall 5012 of the desuperheating box 501 to exchange heat with the second heat exchange pipe 4 and the cooling pipe section 5032 of the first heat exchange pipe 503, which is positioned in the condensation cavity 3C.

The desuperheating box 501 separates the desuperheating heat exchange process and the condensing heat exchange process of the condenser, and provides a controllable space for enhancing the desuperheating heat exchange independently. Secondly, the air baffle 504 of the desuperheating component 5 located below the air inlet pipe 505 reduces the vibration impact of the higher-speed air flow on the first heat exchange pipe 503, and improves the structural safety of the desuperheating component 5 and the condenser. Meanwhile, the air inlet air-equalizing plate 502 and the air-equalizing holes arranged on the air inlet air-equalizing plate turn the air flow from the direction parallel to the first heat exchange tube 503 to the direction perpendicular to the first heat exchange tube 503, which is beneficial to increasing the flow speed of the transverse tube bundle, reducing the included angle between the refrigerant air flow and the heat transfer direction of the first heat exchange tube 503, namely strengthening the field synergistic effect of single-phase sensible heat exchange and improving the heat exchange strength of the heat removal.

Therefore, the energy efficiency of the corresponding horizontal condenser can be further improved through the structural improvement. Meanwhile, the heat exchange area for the overheating heat exchange process can be correspondingly reduced because the overheating heat exchange process can be greatly enhanced, and the number of heat exchange pipes can be reduced, thereby being beneficial to reducing the cost and miniaturizing the condenser.

The first heat exchange tube 503 is arranged in the desuperheating component 5 to improve the single-phase heat exchange strength, and the oil-gas separation function can be realized in the desuperheating component 5. Since the first heat exchange tube 503 is provided, the area of the desuperheating component 5 for collision separation with the refrigerant can be increased, and thus the desuperheating component 5 has a better oil-gas separation effect.

Embodiments of the present disclosure also provide a condenser and a refrigeration system. The condenser includes a desuperheating assembly of embodiments of the present disclosure. The refrigeration system includes a condenser of an embodiment of the present disclosure. The condenser and refrigeration system of the disclosed embodiments have the same advantages as the desuperheating assembly of the disclosed embodiments.

Fig. 10-19 illustrate a condenser and its desuperheating assembly 5 according to a second embodiment of the present disclosure. In the following description, non-illustrated parts of the condenser of the second embodiment may be referred to the related description of the first embodiment.

As shown in fig. 10 to 19, the condenser includes a housing 3, a desuperheating assembly 5, and a second heat exchange tube 4.

The housing 3 has a gaseous working medium inlet 3A and a liquid working medium outlet 3B. The desuperheating assembly 5 is located within the housing 3 and includes a desuperheating box 501, baffles 506, and a first heat exchange tube 503. The desuperheater cartridge 501 has a desuperheater cartridge cavity 501C. The desuperheater cartridge 501 forms a condensing chamber 3C with the housing 3. The condensing chamber 3C communicates with the desuperheater chamber 501C through a desuperheater gas outlet 501B on the desuperheater chamber 501. The gaseous working medium inlet 3A is communicated with the desuperheating box inner cavity 501C through the desuperheating box gas inlet 501A. The liquid working medium outlet 3B is communicated with the condensation cavity 3C.

Baffle 506 is disposed within desuperheater chamber 501C and is configured to form a baffle flow path P within gas-cooling chamber C2. The inlet end PA of the baffling runner P is communicated with the gaseous working medium inlet 3A. The condensing chamber 3C communicates with the outlet end PB of the baffle flow passage P. The first heat exchange tube 503 includes a desuperheating tube section 5031 positioned within the gas cooling chamber C2 of the desuperheating box chamber 501C to cool the gaseous working fluid within the desuperheating box chamber 501C, at least a portion of the desuperheating tube section 5031 being positioned within the baffle flow path P.

The second heat exchange tube 4 is located in the condensation chamber 3C and is configured to condense the gaseous working fluid entering the condensation chamber 3C from the desuperheating box inner chamber 501C into a liquid working fluid.

By arranging the overheating box inner cavity 501C and arranging the baffle plate 506 in the gas cooling cavity C2 of the overheating box inner cavity 501C to form a baffle flow channel P, gaseous working media in an overheating state, such as gaseous refrigerant, can be continuously baffled and disturbed, the heat exchange area of the overheating pipe section 5031 in the overheating box inner cavity 501C is fully utilized, the heat exchange efficiency of the gaseous working media and the overheating pipe section 5031 is enhanced, and therefore the effect of reducing the temperature of the gaseous working media in the overheating state by using fewer overheating pipe sections 5031 is achieved.

The provision of the first heat exchange tubes 503 and baffles 506 in the desuperheating assembly 5 may also provide for oil-gas separation within the desuperheating assembly 5. Since the first heat exchange tube 503 is provided, the area of the desuperheating component 5 for collision separation with the refrigerant can be increased, and thus the desuperheating component 5 has a better oil-gas separation effect.

In this embodiment, the gaseous working medium is a gaseous refrigerant (refrigerant), the liquid working medium is a liquid refrigerant, and the heat exchange medium is water, for example.

In the embodiment of the disclosure, the condenser is a horizontal condenser, the shell 3 is cylindrical, after the horizontal condenser is installed in place, the heat exchange assembly is shown in fig. 10, the desuperheating assembly 5 is located above the interior of the shell 3, and the second heat exchange tube 4 is located below the desuperheating assembly 5. The first heat exchange tube 503 and the second heat exchange tube 4 each extend in the axial direction of the casing 3, so that the axial directions of the first heat exchange tube 503 and the second heat exchange tube 4 are in the same direction as the axial direction of the casing 3. Both ends of the first heat exchange tube 503 and the second heat exchange tube 4 extend into the left side tube sheet 2 and the right side tube sheet 7 located at both axial ends of the housing 3, respectively, so as to be positioned in the housing 3.

In some embodiments of the condenser, as shown in fig. 10-13, 16, the desuperheater cartridge 501 has a desuperheater cartridge cavity 501C and has a desuperheater cartridge gas inlet 501A and a desuperheater cartridge gas outlet 501B. The desuperheating assembly 5 comprises an air inlet pipe 505, wherein the air inlet pipe 505 is connected with the desuperheating box air inlet 501A and penetrates through the gaseous working medium inlet 3A so as to communicate the gaseous working medium inlet 3A with the desuperheating box air inlet 501A.

As shown in fig. 10, 13 to 15, the desuperheating box inner chamber 501C extends along the axial direction (corresponding to the first direction) of the first heat exchange tube 503, and a plurality of baffles 506 are arranged in the desuperheating box inner chamber 501C at intervals along the axial direction of the first heat exchange tube 503. The arrangement is beneficial to the longer flow path of the gaseous working medium, so that the heat exchange with the superheating pipe section 5031 is sufficient, and the heat exchange efficiency of single-phase sensible heat exchange is improved.

As shown in fig. 10 and 12 to 15, the inlet end PA of the baffle flow path P is located at the middle of the desuperheating box inner chamber 501C in the axial direction of the first heat exchange tube 503, and the outlet end PB of the baffle flow path P is located at the end of the desuperheating box inner chamber 501C in the axial direction of the first heat exchange tube 503.

As shown in fig. 10, 12 to 15, the condenser includes two baffle flow passages arranged in the axial direction of the first heat exchange tube 503.

In some embodiments of the condenser, as shown in FIG. 1, baffles 506 are disposed at an angle to the axis of the desuperheater tube section 5031, with perforations 506A through which the desuperheater tube section 5031 passes. The arrangement is beneficial to the gas working medium to transversely flow through the superheat-removing pipe section 5031, and improves the heat exchange strength between the gas working medium and the superheat-removing pipe section 5031, thereby being beneficial to improving the overall heat exchange efficiency of the condenser. In the embodiment shown in fig. 10-19, the baffles 506 are perpendicular to the axis of the desuperheater tube section 5031.

As shown in fig. 10 to 16, the desuperheater cartridge 501 includes a mounting hole plate portion 5014 'having a mounting hole 5014A, and both axial ends of the first heat exchange tube 503 pass through the mounting hole 5014A on the mounting hole plate portion 5014'. The mounting orifice portion 5014' is provided as a seal plate.

As shown in fig. 10, 11, and 13, the desuperheater cartridge 501 is configured to divide the desuperheater cartridge cavity 501C into a gas cooling cavity C2 and a gas outlet equalization cavity C3 in communication with the gas cooling cavity C2. The gaseous working medium inlet 3A is communicated with the gas cooling cavity C2. Baffles 506 and de-superheating pipe sections 5031 are disposed within gas cooling chamber C2. The inlet end PA of the baffling runner P is communicated with the gaseous working medium inlet 3A. The air outlet and homogenizing cavity C3 is communicated with the outlet end PB of the baffling flow channel P. The desuperheating box gas outlet 501B on the desuperheating box 501 communicates with the gas outlet equalization chamber C3 and the condensation chamber 3C.

As shown in fig. 10 to 16, the gas cooling chamber C2 is surrounded by the desuperheating box 501, and the gas outlet uniform chamber C3 is surrounded by the desuperheating box 501.

As shown in fig. 11 and 13, at least part of the wall portion of the desuperheater box 501 is a double wall. The double wall includes an inner wall 5012' and an outer wall 5016' disposed outside the inner wall 5012 '. The inner wall 5012' forms at least part of the chamber wall of the desuperheater chamber 501C. The gas outlet and homogenizing chamber C3 is surrounded by an inner wall 5012' and an outer wall 5016', and the desuperheating box gas outlet 501B is provided in the outer wall 5016'.

As shown in fig. 12-13 and 18-19, the desuperheater gas outlet 501B comprises a plurality of second gas outlet holes evenly distributed on the outer wall 5016' of the desuperheater 501.

In the condenser of some embodiments, as shown in fig. 19, the plurality of second gas outlet holes includes a plurality of gas outlet hole groups having diameters sequentially decreasing from a side away from the second heat exchange tube 4 to a side closer to the second heat exchange tube 4.

As shown in fig. 10-19, the desuperheater cartridge 501 of the presently disclosed embodiments includes a first wall 5011', a double wall, an end connecting wall 5015', and a mounting orifice portion 5014'. As previously described, the double wall includes an inner wall 5012' and an outer wall 5016' located outside of the inner wall 5012 '.

The inner wall 5012' includes a second wall 50121' spaced apart from the first wall 5011' and third walls 50122' spaced apart from the second wall 50121 '. The first wall 5011 'is connected to two third walls 50122', respectively, and the first wall 5011 'is connected to the second wall 5012' as a cylindrical body. The cross section of the first wall 5011' perpendicular to the axis of the housing 3 is an arc curve arched toward a side away from the second wall 5012', and the cross section of the second wall 50121' perpendicular to the axis of the housing 3 is a trapezoid with a large upper side and a small lower side. Each baffle 506 is connected with the cylindrical body, and a circulation hole is formed between the baffle 506 and the cylindrical body for the gaseous working medium to pass through.

The outer wall 5016' includes a bottom plate portion 50161' attached to a side of the second wall 50121' away from the first wall 5011' and two porous plate portions 50162' provided separately on both sides of the bottom plate portion 50161', and an edge plate portion 50163' is further provided on a side of each porous plate portion 50162' away from the bottom plate portion 50161', the edge plate portion 50163' being connected to the first wall 5011 '.

The end connecting walls 5015 'are flat cylinders, and the two end connecting walls 5015' are respectively connected to both ends of the cylindrical main body in the axial direction of the housing 3 and to the first wall 5011 'and the outer wall 5016', and the cross-sectional shape of the wall surface of the flat cylinder connected to the first wall 5011 'perpendicular to the axis of the housing 3 is the same as the cross-sectional shape of the first wall 5011' perpendicular to the axis of the housing 3, and the cross-sectional shape of the wall surface of the flat cylinder connected to the outer wall 5016 'perpendicular to the axis of the housing 3 is the same as the cross-sectional shape of the outer wall 5016' perpendicular to the axis of the housing 3. Two mounting orifice portions 5014' are respectively connected to one side of the flat cylinder far away from the cylindrical main body.

Thus, the gas cooling chamber C2 is formed in the cylindrical body, the third wall 50122 'of the inner wall 5012', the perforated plate portion 50162 'of the outer wall 5016', and the edge plate portion 50163 'of each side of the cylindrical body form a gas outlet gas equalizing chamber C3, and the gas cooling chamber C2 and the gas outlet gas equalizing chamber C3 communicate through the space inside the end connecting wall 5015'.

As shown in fig. 19, a plurality of second air outlet holes are uniformly distributed on each perforated plate portion 50162'. In this embodiment, from low to high, each two rows of second air outlet holes form an air outlet hole group, and the diameters of the second air outlet holes of the plurality of air outlet hole groups increase sequentially from bottom to top. The size of the gas outlet 501B of the desuperheating box is set so as to distribute the gas-liquid mixed state refrigerant after desuperheating, the refrigerant can flow into the condensation cavity 3C through the second gas outlet holes with different apertures, the refrigerant in liquid form flows out through the second gas outlet holes with smaller apertures at the bottom, and the gaseous working medium gradually flows out through the second gas outlet holes which are sequentially enlarged. The diameter of the second gas outlet hole with the smallest aperture is, for example, phi 2mm. The incremental change in diameter of the adjacent two sets of second gas outlet holes may be, for example, 2mm to 3mm.

As shown in fig. 10, the condenser further includes a support plate assembly 6, and a desuperheater cartridge 501 of the desuperheater assembly 5 is connected to the inner wall of the housing 3 through the support plate assembly 6.

The diameter of the first heat exchange tube 503 is smaller than or equal to the diameter of the second heat exchange tube 4. For example, the first heat exchange tube 503 may be a heat exchange tube smaller than the second heat exchange tube 4 by one size, and the inner diameter of the first heat exchange tube 503 is, for example, 19.05mm to 22.23mm.

The first heat exchange tube 503 is a fin tube or a light pipe.

As shown in fig. 10 to 11, the housing 3 has a cylindrical shape, and the desuperheater cartridge 501 has a desuperheater cartridge cavity 501C, and the longitudinal direction of the desuperheater cartridge 501, i.e., the first direction, extends in the axial direction of the housing 3. The first heat exchange tube 503 and the second heat exchange tube 4 extend in the axial direction of the casing 3. Wherein the ratio of the length of the desuperheating box 501 to the length of the housing 3 is 0.4-1. The relative sizes of the desuperheating box 501 and the shell 3 are reasonably set, so that the reasonable division of the heat exchange space between desuperheating heat exchange and condensation heat exchange is facilitated, the desuperheating of the gaseous working medium is fully realized by utilizing the first heat exchange tube 503, and the formation of liquid working medium due to the excessive cooling of the gaseous working medium in the inner cavity 501C of the desuperheating box is prevented.

The ratio of the number of the first heat exchange tubes 503 to the sum of the numbers of the first heat exchange tubes 503 and the second heat exchange tubes 4 is 10 to 25%. The reasonable setting of the proportion is beneficial to fully realizing the desuperheating of the gaseous working medium by using the first heat exchange tube 503 and preventing the gaseous working medium from being excessively cooled in the inner cavity 501C of the desuperheating box to form a liquid working medium.

The desuperheating assembly 5 satisfies:

ε＝0.1-0.5；

l is the length of the de-superheating pipe section 5031 of the first heat exchange pipe 503, and the unit is m;

n is the number of first heat exchange tubes 503;

d is the outer diameter of the first heat exchange tube 503 in m;

d _k the equivalent diameter of the first heat exchange tube 503 is given by m;

λ is the thermal conductivity coefficient of the gaseous working medium in the desuperheating box cavity 501C at the average temperature, W/(m×k);

mu is the viscosity of the gaseous working medium in the inner cavity 501C of the desuperheating box at the average temperature, P _a *s；

μ _w To remove the viscosity of the gaseous working medium in the inner cavity 501C of the overheat box at the average temperature of the pipe wall of the first heat exchange pipe 503, the unit is P _a *s；

P _t The unit is m for the tube pitch of the first heat exchange tubes 503 (the pitch between the central axes of the adjacent two first heat exchange tubes 503);

D _k is the inner diameter of the shell 3, and the unit is m;

l _b is the spacing of adjacent baffles 506 in m;

u is the flow velocity calculated according to the flow section of the superheated zone (see the hatched portion S in fig. 5 for the flow section of the superheated zone), m/S;

P _r is the Plantt number;

epsilon is a constant and takes a value of 0.1-0.5.

The parameters epsilon are adjusted to comprehensively control factors such as the outer diameter of a heat exchange tube, the tube spacing and the like which influence the heat exchange capacity of the heat exchanger, so that the flow velocity of the inlet of the gaseous refrigerant is kept within a reasonable range, and the pressure drop generated by the gaseous refrigerant under the condition that the heat exchange capacity is as high as possible is obtained by the heat exchanger is minimum. Wherein, as the parameter epsilon increases, the total heat exchange coefficient of the superheating area is smaller.

The total number of baffles 506 can be reasonably set according to the pressure drop Δp required to be controlled by the gaseous working fluid flowing through the desuperheating assembly 5, and the total number of baffles 506 satisfies the following formula:

wherein,,

n _b is the total number of baffles 506;

c is a constant and takes a value of 0.02-0.25.

As the value of c increases, the pressure drop Δp increases.

Fig. 20-28 illustrate a condenser and its desuperheating assembly 5 according to a third embodiment of the present disclosure. In the following description, non-illustrated parts of the condenser of the third embodiment may be referred to the related description of the first and second embodiments.

In the third embodiment, the description will be given taking the example that the condenser is used in a refrigeration system, the gaseous working medium is a gaseous refrigerant, the liquid working medium is a liquid refrigerant, and the cooling medium is water.

As shown in fig. 20 to 28, the desuperheating assembly 5 is disposed inside the condenser housing 3. Which includes a desuperheater cartridge 501 and a first heat exchange tube 503. The desuperheater cartridge 501 has a desuperheater cartridge cavity 501C. The desuperheater chamber 501C includes a gas-cooled chamber C2. And the desuperheater box 501 is provided with a desuperheater box gas inlet 501A and a desuperheater box gas outlet 501B. The desuperheater gas inlet 501A communicates the gas cooling chamber C2 with a compressor discharge port (not shown) to allow gaseous working fluid discharged from the compressor to flow to the gas cooling chamber C2. The desuperheating box gas outlet 501B communicates the gas cooling chamber C2 with the condensing chamber 3C of the condenser such that the refrigerant flows from the gas cooling chamber C2 into the condensing chamber 3C via the desuperheating box gas outlet 501B to exchange heat with the second heat exchange tube 4 in the condensing chamber 3C. The desuperheater tube section 5031 of the first heat exchange tube 503 is positioned within the gas cooling chamber C2 to exchange heat with the refrigerant flowing from the desuperheater gas inlet 501A to the desuperheater gas outlet 501B.

According to the embodiment of the disclosure, the first heat exchange tube 503 is arranged on the desuperheating component 5, and the desuperheating tube section 5031 of the first heat exchange tube 503 is utilized to perform single-phase heat exchange with the refrigerant in advance before the refrigerant flows to the second heat exchange tube 4, so that the single-phase heat exchange strength of the condenser can be effectively improved, the desuperheating heat exchange strength of the condenser is enhanced, and the energy efficiency of the condenser is improved.

Meanwhile, the first heat exchange tube 503 is arranged in the desuperheating component 5 to improve the single-phase heat exchange strength, and the oil-gas separation function can be realized in the desuperheating component 5. Since the first heat exchange tube 503 is provided, the area of the desuperheating component 5 for collision separation with the refrigerant can be increased, and thus the desuperheating component 5 has a better oil-gas separation effect.

In addition, the first heat exchange tube 503 is located inside the desuperheating box 501 of the desuperheating assembly 5, which does not need to occupy extra space, thus being beneficial to realizing the miniaturization of the condenser and preventing the reduction of the tube distribution space in the condenser from influencing the energy efficiency of the condenser due to solving the problem of intensified heat exchange of overheated gas.

Therefore, the condenser of the embodiment of the disclosure adopts the desuperheating component 5 of the embodiment of the disclosure, and the refrigerant can exchange heat through the first heat exchange tube 503 and the second heat exchange tube 4 in two stages in the process of flowing through the condenser, so that the single-phase heat exchange strength of the condenser can be improved, and the condenser is miniaturized, thereby effectively improving the overall energy efficiency of the condenser. The oil-gas separation function of the gaseous refrigerant can be realized.

In order to further enhance the energy efficiency of the condenser, referring to fig. 23, the desuperheating assembly 5 further includes at least two baffles 506, and the at least two baffles 506 are disposed in the gas cooling chamber C2 and deflect the refrigerant flowing through the first heat exchange tube 503.

Baffle 506 is configured to form a baffle flow path P within gas cooling cavity C2. The inlet end PA of the baffle flow path P communicates with the desuperheater box gas inlet 501A. The condensing chamber 3C communicates with the outlet end PB of the baffle flow passage P. The first heat exchange tube 503 includes a desuperheating tube section 5031 positioned within the gas cooling chamber C2 of the desuperheating box chamber 501C to cool the gaseous working fluid within the desuperheating box chamber 501C, at least a portion of the desuperheating tube section 5031 being positioned within the baffle flow path P.

As shown in fig. 23, the inlet end PA of the baffle flow path P is located at an end portion of the desuperheating box inner chamber 501C in the axial direction of the first heat exchange tube 503, and the outlet end PB of the baffle flow path P is located at a middle portion of the desuperheating box inner chamber 501C in the axial direction of the first heat exchange tube 503.

Wherein the baffles 506 in the desuperheating assembly 5 are arranged side by side in the extending direction (first direction) of the first heat exchange tube 503, and the baffles 506 are staggered in the intersecting direction (e.g. the height direction or width direction of the desuperheating assembly 5, i.e. the up-down direction or front-back direction of fig. 23) with the adjacent baffles 506 in the first direction of the first heat exchange tube 503, so that the refrigerant returns back and forth when flowing through the first heat exchange tube 503, forming a wave-like baffling flow.

Due to the baffle plate 506, the flow area in the gas cooling cavity C2 can be reduced, the gas flow rate of the cross tube bundle is improved (the flow area is reduced and the flow rate is increased on the premise of unchanged total flow), and the angle between the gas flow direction and the first heat exchange tube 503 is reduced, so that the gas flow direction originally parallel to the first heat exchange tube 503 is changed to be inclined relative to the first heat exchange tube 503, thereby improving the heat exchange sufficiency between the gaseous refrigerant and the first heat exchange tube 503, effectively improving the heat exchange strength of the overheated gaseous refrigerant at the first heat exchange tube 503, realizing further enhancement of the single-phase heat exchange strength, and further improving the energy efficiency of the condenser.

Meanwhile, the baffle plate 506 can also increase the collision separation area of oil drops, so that the oil-gas separation efficiency is improved, and the energy efficiency of the condenser is improved.

It can be seen that by further arranging the baffle plate 506 in the gas cooling cavity C2, the single-phase heat exchange strength and the oil-gas separation efficiency can be further improved, so that the energy efficiency of the condenser is further improved.

Fig. 24 and 25 further illustrate the structure of baffle 506.

Referring to fig. 24 to 25 in combination with fig. 23, a through hole 506A is provided in the baffle 506, and the first heat exchange tube 503 passes through the baffle 506 via the through hole 506A. At this time, the first heat exchange tube 503 can play a supporting role on the baffle plate 506, so that the structural stability is effectively improved, and moreover, as the baffle plate 506 is integrated on the first heat exchange tube 503, the baffle plate 506 is more convenient to be matched with the first heat exchange tube 503, and the single-phase heat exchange intensity and the oil-gas separation efficiency are effectively improved.

In addition, referring to fig. 24 and 25, in some embodiments, a vent 506B is provided in the baffle 506 for the flow of refrigerant therethrough.

Although the baffle 506 may not be provided with the vent 506B, after the vent 506B is provided, a part of the gaseous working medium may be allowed to pass through the baffle 506 via the vent 506B, so that the baffle pressure drop of the gaseous working medium may be reduced to a certain extent, and the excessive pressure drop of the gaseous working medium flowing out after the baffle is effectively prevented.

In the case that the baffle 506 is provided with the vent holes 506B, the size and the number of the vent holes 506B can be designed to control the total flow area of the vent holes 506B, thereby realizing better baffle effect and better anti-depressurization effect. For example, in some embodiments, the diameter of the vent holes 506B is 2 mm-8 mm; and/or the total flow area of all of the vents 506B on the baffle 506 is 1/8 to 3/4 of the total area of the baffle 506. In this way, the pressure drop can be effectively reduced, and a better baffling effect can be realized, so that the baffling effect of the baffle plate 506 is not affected due to the fact that the vent holes 506B are too large and/or too many.

At least two baffles 506 having an average hydraulic diameter D _d And in the extending direction (first direction) of the first heat exchange tube 503, the distance between two adjacent baffles 506 is l _b ，D _d And l _b The following relationship is satisfied:

c is a constant, and the value is 0.3-1.5;

d is the diameter of the through-flow portion at the inlet hole of the desuperheating box gas inlet 501A, i.e., the inner diameter of the inlet pipe 505, in m;

n is the number of first heat exchange tubes 503;

d is the outer diameter of the first heat exchange tube 503 in m.

Based on the above formula, the first heat exchange tube 503 and the baffle 506 are conveniently designed, so that the overheating removing component 5 which can remove overheating more effectively is conveniently designed.

Wherein the pressure drop ΔP is proportional to C, and increases with increasing C. The pressure drop and heat exchange performance of the built-in oil 102 are comprehensively controlled by controlling the value of C and affecting the average flow velocity v0 of the gaseous refrigerant flowing through all baffles 6. Specifically, the pressure drop of the built-in oil 102 is smaller when the heat exchange performance is optimal by reasonably designing the values of the dimensional parameters such as D, D and the like.

D is the diameter of the through-flow part at the air inlet hole of the desuperheating box air inlet 501A, for example, the inner diameter of the air inlet pipe 505 connected with the gaseous working medium inlet 3A, and the unit is m;

l is the length of the desuperheater pipe section 5031, and the unit is m;

n is the number of first heat exchange tubes 503;

Epsilon is a constant and takes a value of 15 to 200;

d _e the equivalent diameter of the first heat exchange tube 503 is given by m;

P _t the unit is m for the tube pitch of the first heat exchange tube 503.

Based on the above formula, the first heat exchange tube 503 is conveniently designed, so that the overheating removing component 5 which can remove overheating more effectively is conveniently designed. In particular, D, d, L, d can be reasonably designed _e And P _t The values of the equal-size parameters are adopted to realize better desuperheating effect of the built-in oil 102. Where baffles 506 are provided in desuperheating assembly 5, the particular value of ε may be determined based on the design of baffles 506. Under the condition that the temperature difference between the inlet and the outlet is unchanged, epsilon is in direct proportion to the superheating heat exchange coefficient of the built-in oil 102, and the superheating heat exchange coefficient is increased along with the increase of epsilon.

Referring to fig. 23, the desuperheating component 5 further includes an air outlet air-equalizing plate 507, the air outlet air-equalizing plate 507 is disposed in the desuperheating box 501 and located between the first heat exchange tube 503 and the desuperheating box air outlet 501B, and the air outlet air-equalizing plate 507 has an air outlet orifice area 5072, the air outlet orifice area 5072 is provided with air outlet air-equalizing holes, and the refrigerant after heat exchange with the first heat exchange tube 503 flows to the desuperheating box air outlet 501B through the air outlet air-equalizing holes.

Because the air outlet and homogenizing plate 507 can uniformly flow field, the gaseous refrigerant flowing to the overheat box removing air outlet 501B through the first heat exchange tube 503 is more uniformly distributed, and the collision with oil drops in the refrigerant can be increased, the impact separation capability of the overheat removing assembly 5 is enhanced, and therefore, the oil-gas separation efficiency of the overheat removing assembly 5 can be effectively improved.

As shown in fig. 23 and fig. 26 to fig. 27, the outlet gas uniformity plate 507 further has an outlet baffle region 5071, and the outlet baffle region 5071 is not provided with outlet gas uniformity holes and corresponds to the region where the baffle 506 in the gas cooling chamber C2 is located, and the outlet orifice region 5072 is located on a side of the outlet baffle region 5071 away from the desuperheating box gas inlet 501A.

Based on the above arrangement, the gas outlet and homogenizing plate 507 is not provided with holes on the part corresponding to the area of the baffle plate 506, but is provided with holes on the part behind the baffle plate 506, so that the baffle effect of the baffle plate 506 can be fully exerted, and the effective improvement of the single-phase heat exchange intensity and the oil-gas separation efficiency is realized.

Specifically, referring to fig. 27, the ratio of the length L1 of the outlet orifice region 5072 to the length L2 of the outlet baffle region 5071 is 1/10 to 1/2. At this time, the ratio of the air outlet hole plate region 5072 to the air outlet baffle region 5071 is relatively suitable, so that a relatively good air homogenizing effect can be achieved, sufficient baffling length is provided for enhanced heat exchange and oil drop separation, and the pressure drop of the refrigerant flowing through the air outlet air homogenizing plate 507 is relatively suitable and is not excessively large.

In addition, referring to fig. 28, in some embodiments, a plurality of air outlet holes are provided on the air outlet plate 507, and the plurality of air outlet holes include a first air outlet hole 507A and a second air outlet hole 507B, and the diameter of the first air outlet hole 507A is greater than the diameter of the second air outlet hole 507B. At this time, the air outlet and air equalizing plate 507 is provided with air outlet and air equalizing holes with different diameters, so that oil drops with different particle sizes can be conveniently separated, and the pressure drop can be conveniently controlled within a reasonable range.

The diameter of the first air outlet and equalizing hole 507A is 12 mm-20 mm; and/or the diameter of the second air outlet and equalizing hole 507B is 6 mm-12 mm. At this time, the diameters of the first air outlet air equalizing holes 507A and the second air outlet air equalizing holes 507B are more suitable, the processing is convenient, and the pressure drop can be effectively controlled within a reasonable range while the separation requirements of oil drops with different particle sizes are met.

Referring to fig. 28, in some embodiments, the second air outlet holes 507B are close to the edges of the air outlet holes 507A in the width direction of the air outlet plate 507, and the ratio of the width of the area where the first air outlet holes 507A are located (see fig. 28, 2H 1) to the width of the area where the second air outlet holes 507B are located (see fig. 28, 2H 2) is 3 to 10. At this time, the distribution ranges of the first air outlet air equalizing holes 507A and the second air outlet air equalizing holes 507B are reasonable, and the pressure drop can be effectively controlled within a reasonable range while the separation requirements of oil drops with different particle sizes are met.

Referring to fig. 23, the desuperheating box gas inlet 501A of the desuperheating box 501 includes two third gas inlet holes at both ends in the length direction thereof, both of which communicate with the gas cooling chamber C2. In this way, the refrigerant can enter the desuperheating component 5 from the desuperheating box gas inlets 501A at two sides and flow out of the desuperheating component 5 from the desuperheating box gas outlets 501B at the middle part, and flow through the desuperheating pipe sections 5031 of the first heat exchange pipes 503 in the gas cooling cavity C2 to perform single-phase heat exchange and desuperheat in the process of flowing from two sides to the middle part. At this time, the heat exchange efficiency and the oil-gas separation efficiency are both higher.

In the case that two third air inlets are provided on the desuperheating box 501, referring to fig. 23, in some embodiments, the desuperheating assembly 5 includes a first partition 508, and the first partition 508 is disposed in the gas cooling chamber C2 and divides the gas cooling chamber C2 into two sub-cooling chambers, which are in one-to-one correspondence with the two third air inlets. Therefore, the refrigerants in the two sub-cooling cavities are not interfered with each other, and more efficient single-phase heat exchange and oil-gas separation processes can be realized.

Also, with continued reference to FIG. 23, in some embodiments, baffles 506 are provided within both sub-cooling chambers. Therefore, the two sub-cooling cavities can be baffled, and the single-phase heat exchange strength and the oil-gas separation efficiency are higher.

The condenser of the disclosed embodiment comprises a desuperheating assembly 5; the refrigeration system includes a condenser of the present disclosure.

A third embodiment shown in fig. 10 to 28 will be further described. As shown in fig. 20 to 28, in this embodiment, the condenser is a horizontal condenser, which includes a deshell 3 and a second heat exchange tube 4, and further includes a desuperheating assembly 5. The desuperheating component 5 is disposed within the housing 3. The region of the housing 3 where the desuperheating assembly 5 is not disposed forms a condensation chamber 3C. The second heat exchange tube 4 is located in the condensation chamber 3C.

The housing 3 has a substantially hollow cylindrical shape with an axis substantially horizontal, and is directed in the left-right direction in the drawing. The bottom of the housing 3 is provided with a liquid collecting portion 11, and the liquid collecting portion 11 communicates with the condensation chamber 3C to collect condensed liquid.

The desuperheating assembly 5 and the second heat exchange tube 4 are both disposed in the housing 3. Wherein the desuperheating assembly 5 is disposed at an upper side of the interior of the housing 3. The region of the shell 3, which is not provided with the desuperheating component 5, forms a condensation cavity 3C, and the second heat exchange tube 4 is arranged in the condensation cavity 3C and is positioned at the middle lower side of the interior of the shell 3 so as to exchange heat with the refrigerant flowing out of the desuperheating component 5, thereby realizing the condensation of the refrigerant. As shown in fig. 20, in this embodiment, a plurality of second heat exchange tubes 4 are provided in the condensation chamber 3C, and these second heat exchange tubes 4 each penetrate the condensation chamber 3C in the axial direction of the housing 3 (also the first direction of the desuperheating assembly 5), and are supported at both ends by the left-side tube sheet 2 and the right-side tube sheet 7.

As shown in fig. 22 to 28, the desuperheating unit 5 is substantially symmetrical in the longitudinal direction and the width direction, and has a V-shaped overall cross section.

As shown in fig. 22 and 23, the desuperheating assembly 5 includes a desuperheating box 501, a filter screen 510, two inlet pipes 505, an outlet gas-equalizing plate 507, a first heat exchange pipe 503, a baffle 506, a first partition 508, a second partition 509, and a liquid-blocking plate 511.

The desuperheating box 501 is used for providing a mounting base for other structural components of the desuperheating assembly 5 and protecting the structural components arranged inside the desuperheating box. As can be seen from fig. 22 and 23, in this embodiment, the desuperheating box 501 includes two mounting hole plate portions 5014 "in the form of two sealing plates, two side plates 5011", two sealing plates 5013", two connecting plates 5012", and a frame 5015". The two attachment hole plate portions 5014″ are disposed opposite each other in the longitudinal direction (i.e., the left-right direction in fig. 22 and 23, i.e., the first direction), and have a substantially fan shape. Both side plates 5011″ are substantially V-shaped, are disposed opposite each other in the width direction (i.e., the front-rear direction of fig. 22 and 23), and are connected to the front-rear edges of both attachment hole plate portions 5014″. The two sealing plates 5013″ are polygonal (e.g., have 5 folds), are disposed between the two mounting hole plate portions 5014″ and are disposed at intervals in the longitudinal direction, and are respectively connected to the two side plates 5011″ and the mounting hole plate portions 5014″ on the corresponding sides. Two connecting plates 5012 "are respectively connected to one side of the two sealing plates 5013" away from the mounting hole plate portion 5014 ". The frame 5015″ is disposed between the two connecting plates 5012″ and connected to both the two connecting plates 5012″ and the two side plates 5011″. In this way, the two mounting hole plate portions 5014", the two side plates 5011", the two sealing plates 5013", the two connecting plates 5012" and the frame 5015 "are enclosed to form a desuperheating box 501 which is V-shaped as a whole and is internally provided with a desuperheating box inner cavity 501C. Wherein, two mounting hole plate portions 5014 "and two side plates 5011" together form the periphery and bottom profile of the desuperheating box 501, and two sealing plates 5013", two connecting plates 5012" and a frame 5015 "together form the upper profile of the desuperheating box 501.

The frame 5015″ forms a desuperheater gas outlet 501B of the desuperheater assembly 5 for communicating the desuperheater chamber 501C with the condensing chamber 3C of the condenser. The frame 5015 "is used for supporting the filter screen 510, and the filter screen 510 is disposed on the frame 5015" and below the frame 5015 ". The refrigerant flowing out of the desuperheating component 5 flows through the filter screen 510 and the frame 5015″ and enters the condensation chamber 3C of the condenser to exchange heat with the second heat exchange tube 4 in the condensation chamber 3C. The refrigerant may be filtered by the filter 510 as it flows through the filter 510 for further oil-gas separation. Because the middle of the frame 5015″ is hollowed out, the refrigerant flowing out of the filter screen 510 is not blocked.

Since the frame 5015″ is located at the middle of the desuperheating assembly 5 in the first direction (length direction), the desuperheating box gas outlet 501B is located at the middle of the desuperheating assembly 5 in the first direction. Thus, the screen 510 disposed on the frame 5015″ is also located at the middle of the de-superheating assembly 5 in the length direction.

The two intake pipes 505 are connected to the two third intake holes of the desuperheating box gas inlet 501A, respectively. As shown in fig. 22 and 23, two air intake pipes 505 are provided on two sealing plates 5013″ respectively. And, the lower ends of the two air inlet pipes 505 pass through the corresponding sealing plates 5013″ and extend into the desuperheating box inner chamber 501C to communicate with the desuperheating box inner chamber 501C, and at the same time, the upper ends of the two air inlet pipes 505 pass through the corresponding sealing plates 5013″ and extend to the outside of the desuperheating box 501 for connection with the exhaust ports of the compressor (not shown in the drawing) to communicate the exhaust ports of the compressor with the desuperheating box inner chamber 501C so that the compressor exhaust gas flows into the desuperheating assembly 5 via the two air inlet pipes 505.

Under the action of the filter screen 510 and the two air inlet pipes 505, the refrigerant can flow into the desuperheating box inner cavity 501C from two sides in the length direction, flow out of the desuperheating box inner cavity 501C from the middle part in the length direction, and exchange heat with the second heat exchange tube 4 of the condensation cavity 3C.

The outlet gas equalization plate 507, the first heat exchange tube 503, the baffle 506, the first separator 508, the second separator 509, and the liquid separator 511 are all disposed in the desuperheater box cavity 501C.

Wherein, go out and evenly arrange in proper order along the orientation from top to bottom by gas-phase plate 507 and separating board 511 to with remove overheated box 501 cooperation, will remove overheated box inner chamber 501C and separate into liquid collecting chamber C4, gas cooling chamber C2 and go out and evenly air chamber C3, in order to realize fluid storage, oil-gas separation and refrigerant filtering capability respectively.

As shown in fig. 23, in this embodiment, the liquid-blocking plate 511 is disposed at the lower portion of the desuperheating box cavity 501C, and the peripheral edge is in contact with the two mounting hole plate portions 5014 "and the two side plates 5011", so that the liquid-blocking plate 511 and the desuperheating box 501 are enclosed together to form a liquid-collecting cavity C4 under the liquid-blocking plate 511 to collect oil-gas separated oil. The edge of the liquid separation plate 511 is provided with a liquid separation plate liquid passing port 511A, and oil obtained by oil-gas separation falls into the liquid collection cavity C4 through the liquid separation plate liquid passing port 511A. The plenum C4 communicates with the outlet tube 512. The drain pipe 512 is connected to the desuperheating box liquid outlet 501D of the desuperheating box 501 and extends from one side of the liquid collecting chamber C4 to facilitate the extraction of the collected oil.

The air outlet and homogenizing plate 507 is disposed at the upper part of the inner cavity 501C of the desuperheating box and below the filter screen 510. The peripheral edges of the air outlet and homogenizing plate 507 are in contact with two connecting plates 5012 'and two side plates 5011'. In this way, the air outlet and homogenizing plate 507 and the two connecting plates 5012", the two side plates 5011" and the filter screen 510 enclose each other to form an air outlet and homogenizing cavity C3, and the air outlet and homogenizing plate 507 and the two mounting hole plate portions 5014", the two side plates 5011", the two sealing plates 5013 "and the two connecting plates 5012" enclose each other to form a gas cooling cavity C2. The gas cooling cavity C2 is positioned between the gas outlet and uniform air cavity C3 and the liquid collecting cavity C4 and is used for realizing the gas cooling and oil-gas separation functions of the desuperheating component 5. The air outlet and homogenizing cavity C3 is positioned on one side of the air cooling cavity C2 far away from the liquid collecting cavity C4 and is used for realizing the functions of homogenizing air and filtering refrigerant of the overheating component 5.

As shown in fig. 23, the desuperheater cartridge 501 is configured to divide the desuperheater cartridge cavity 501C into a gas cooling cavity C2 and a gas outlet plenum cavity C3 in communication with the gas cooling cavity C2. The desuperheater box gas inlet 501A communicates with the gas cooling chamber C2. Baffles 506 and de-superheating pipe sections 5031 are disposed within gas cooling chamber C2. The inlet end PA of the baffle flow path P communicates with the desuperheater box gas inlet 501A. The air outlet and homogenizing cavity C3 is communicated with the outlet end PB of the baffling flow channel P. The desuperheating box gas outlet 501B on the desuperheating box 501 communicates with the gas outlet equalization chamber C3 and the condensation chamber 3C.

Fig. 26 to 28 further show the structure of the outlet gas uniformity plate 507.

As shown in fig. 26 to 28, the outlet gas equalization plate 507 has a substantially V-shape and is arranged symmetrically in the longitudinal direction and the width direction. The two side edges of the air outlet and air equalizing plate 507 in the width direction are provided with liquid separating plate liquid passing holes 511A so as to facilitate the dripping of oil. Also, the gas outlet gas uniformity plate 507 is provided with two gas outlet baffle regions 5071 in the length direction, and a gas outlet orifice region 5072 located between the two gas outlet baffle regions 5071. Wherein, two air outlet baffle areas 5071 are positioned at two ends of the air outlet uniform air plate 507 in the length direction and correspond to the two sub cooling cavities one by one. The two vent baffle areas 5071 are equal in length, are L2, and are not perforated. The gas outlet orifice region 5072 is located at the middle part of the gas outlet uniform gas plate 507 in the length direction, and the length is L1. The air outlet pore plate region 5072 is provided with air outlet uniform pores. Two hole units are arranged on the air outlet hole plate region 5072, the two hole units are symmetrically arranged in the length direction, and each hole unit comprises a plurality of first air outlet air equalizing holes 507A with larger diameters and a plurality of second air outlet air equalizing holes 507B with smaller diameters. All the first air outlet and air equalizing holes 507A are uniformly arranged in the middle part of the air outlet and air equalizing plate 507 close to the width direction and are symmetrically arranged about the V-shaped bending line of the air outlet and air equalizing plate 507, so that each hole unit comprises two groups of first air outlet and air equalizing holes 507A symmetrically distributed in the width direction. A plurality of second air outlet and air equalizing holes 507B which are uniformly distributed are arranged on two sides of the width direction of the area where all the first air outlet and air equalizing holes 507A are located, so that each hole unit comprises two groups of second air outlet and air equalizing holes 507B which are symmetrically distributed in the width direction. Wherein the length ratio L1/L2 of the gas outlet orifice region 5072 and the gas outlet baffle region 5071 is about 1/10 to 1/2, the diameter of the first gas outlet gas equalizing hole 507A is about 12mm to 20mm, the diameter of the second gas outlet gas equalizing hole 507B is about 6mm to 12mm, and the width ratio H1/H2 of the region where the first gas outlet gas equalizing hole 507A is located to the region where the second gas outlet gas equalizing hole 507B is located is about 3 to 10. It will be appreciated that L1 is the total length across the two aperture units.

The first heat exchange tube 503, the baffle 506, the first separator 508 and the second separator 509 are all disposed in the gas cooling chamber C2, so as to realize the oil-gas separation and the enhanced heat exchange function of the desuperheating component 5.

As shown in fig. 23, a first separator 508 is provided at the middle of the gas cooling chamber C2 in the first direction, and the top end is connected to the middle of the gas outlet gas uniformity plate 507. The gas cooling chamber C2 is partitioned into two sub-cooling chambers arranged side by side in the length direction by the first partition 508. The two sub-cooling chambers are communicated with the two air inlet pipes 505 in a one-to-one correspondence manner, so that the refrigerant can enter the two sub-cooling chambers through the two air inlet pipes 505 respectively. As is clear from fig. 23 and 27, the portion of the outlet gas equalization plate 507 located between the two hole units is connected to the first separator 508, and the width L3 of the portion of the outlet gas equalization plate 507 for mounting the first separator 508 is about 2mm to 20mm. In this case, the aforementioned L1 is a group including L3, and specifically, L1 is the sum of the lengths of two hole units and L3.

The first heat exchange tube 503 penetrates through the two sub-cooling chambers such that the first heat exchange tube 503 penetrates through the entire gas cooling chamber C2. Specifically, as shown in fig. 23, a plurality of first heat exchange tubes 503 are disposed in the gas cooling chamber C2 side by side, and each penetrate through two sub-cooling chambers. Both ends of these first heat exchange tubes 503 in the first direction (i.e., the axial direction of the housing 3) are penetrated out from the two mounting hole plate portions 5014″ and supported by the two tube plates of the condenser. And, when penetrating the two sub-cooling chambers, the first heat exchange pipe 503 penetrates the first partition 508, the two second partitions 509, and the baffle 506 such that a portion between both ends of the first heat exchange pipe 503 is supported by the first partition 508, the second partition 509, and the baffle 506.

Baffles 506 and a second partition 509 are disposed within each of the sub-cooling chambers. As shown in fig. 23, in each sub-cooling chamber, the second partition 509 is located between the mounting orifice 5014 "and the connecting plate 5012", and the top end is connected to the sealing plate 5013", so that the refrigerant entering the sub-cooling chamber through the intake pipe 505 can pass through the baffling effect of the second partition 509. The second partition 509 divides the gas cooling chamber C2 into a first gas cooling chamber C21 and a second gas cooling chamber C22. A communication port for communicating the first gas cooling chamber C21 and the second gas cooling chamber C22 is provided on the second partition plate 509 or between the second partition plate 509 and the desuperheating box 501. And, at least two baffles 506 are disposed in each sub-cooling cavity, and the at least two baffles 506 are located below the air outlet baffle area 5071 of the air outlet air homogenizing plate 507 and are arranged at intervals along the first direction (along the first direction of the desuperheating box 501, the desuperheating assembly 5 and the condenser) of the sub-cooling cavity, and the two adjacent baffles 506 are arranged in a vertically staggered manner, so that a baffle channel for guiding the refrigerant in the sub-cooling cavity to flow in a baffling manner is formed between the baffles 506 in the sub-cooling cavity.

Fig. 24 and 25 further illustrate the structure of baffle 506.

Wherein fig. 24 shows the configuration of the upper one 506 of any two adjacent baffles 506 within the sub-cooling chamber. Fig. 25 shows the structure of the lower one 506 of any adjacent two baffles 506 in the sub-cooling chamber.

For convenience of description, the upper one 506 of any two adjacent baffles 506 in the sub-cooling chamber is referred to as a first baffle, and the lower one 506 of any two adjacent baffles 506 in the sub-cooling chamber is referred to as a second baffle.

As can be seen from fig. 24 and 25, the first baffle plate and the second baffle plate are both substantially V-shaped, and the first baffle plate and the second baffle plate are each provided with a plurality of through holes 506A and a plurality of ventilation holes 506B. The plurality of tube penetrating holes 506A are divided into two groups, and are respectively located on two plate bodies of the baffle 506 (the first baffle or the second baffle) which are bent relatively to form a V shape, so that the first heat exchanging tube 503 passes through, so that the desuperheating assembly 5 includes two groups of first heat exchanging tubes 503 which are arranged at intervals along the width direction (i.e., the front-rear direction of fig. 22 and 23), and the two groups of first heat exchanging tubes 503 are symmetrical to each other in the width direction. The first heat exchange tubes 503 in each group of the first heat exchange tubes 503 are arranged in a triangle shape, that is, the first heat exchange tubes 503 in each group of the first heat exchange tubes 503 are arranged in a triangle shape. A plurality of ventilation holes 506B are located between the two sets of through holes 506A for the refrigerant to pass through. In this embodiment, the diameters of the vent holes 506B on the first and second baffles are the same and are both 2 mm-8 mm, and the total flow area of the vent holes 506B on the first and second baffles is 1/8-3/4 of the total area of the corresponding baffles 506.

In this embodiment, the structural parameters of the first heat exchange tube 503 and the inlet and outlet temperatures of the desuperheating assembly 5 satisfy the following relationship:

the parameters involved therein participate in the foregoing description of the present embodiment.

The following relationship is satisfied between the structural parameters of the baffle 506 and the first heat exchange tube 503 and the inlet-outlet pressure drop Δp of the desuperheating assembly 5:

Based on the desuperheating component 5 of this embodiment, when the condenser works, the overheated gaseous working medium carries oil drops to enter the two sub-cooling cavities from the two air inlet pipes 505 respectively, and enters the first gas cooling cavity C21 in the sub-cooling cavity, is baffled by the second baffle 509, enters the second gas cooling cavity C22 where the baffle 506 is located, finally passes through the air outlet air equalizing plate 507, flows out from the upper filter screen 510, and enters the condensation cavity 3C. In this process, through the collision separation with the second separator 509, the baffle 506, the first heat exchange tube 503, the air outlet and homogenizing plate 507, the filter screen 510 and the liquid separation plate 511, the oil droplets in the refrigerant accumulate and separate, fall from the liquid separation plate liquid passing opening 511A at the edge of each component, and are collected in the liquid collection cavity C4, so as to realize the separation of the oil droplets. Meanwhile, the overheated gaseous working medium performs single-phase heat exchange with the first heat exchange tube 503, so that the temperature of the overheated gaseous working medium is reduced to a saturated state and then enters the condensation cavity 3C for phase change heat exchange, and the overheating removal process is realized.

The refrigerant entering the condenser sequentially passes through the first heat exchange tube 503 in the superheating assembly 5 and the second heat exchange tube 4 in the condensing cavity 3C to exchange heat in two stages, and the first heat exchange tube 503 can strengthen the single-phase heat exchange of the superheated gaseous refrigerant, so that the superheating heat exchange strength of the condenser can be effectively improved, and the overall energy efficiency of the condenser is improved.

Furthermore, on the basis of the first heat exchange tube 503, a baffle plate 506 is further arranged, so that the single-phase heat exchange strength can be further improved.

Meanwhile, the first heat exchange tube 503 and the baffle plate 506 can increase the collision separation area of oil drops, and improve the oil-gas separation efficiency.

In addition, the first heat exchange tube 503 and the baffle plate 506 are both arranged in the desuperheating assembly 5, so that no extra space is required, and the condenser is miniaturized.

It can be seen that the condenser and the desuperheating assembly 5 of this embodiment can achieve effective improvement of single-phase heat exchange strength and oil-gas separation efficiency based on a simpler structure and a smaller volume, which is advantageous for improving the energy efficiency of the condenser.

Based on the desuperheating assembly 5 and condenser of the presently disclosed embodiments, the presently disclosed embodiments also provide a refrigeration system that includes a compressor, and further includes the condenser of the presently disclosed embodiments, with the desuperheating box gas inlet 501A of the condenser being connected to the exhaust of the compressor.

Since the energy efficiency of the desuperheating assembly 5 and the condenser is improved, the energy efficiency of the refrigeration system can be effectively improved.

Finally, it should be noted that: the above embodiments are merely for illustrating the technical solution of the present disclosure and are not limiting thereof; although the present disclosure has been described in detail with reference to preferred embodiments, those of ordinary skill in the art will appreciate that: modifications may be made to the specific embodiments of the disclosure or equivalents may be substituted for part of the technical features that are intended to be included within the scope of the claims of the disclosure.

Claims

1. A desuperheating assembly (5) for a condenser, comprising:

a desuperheater cartridge (501), the desuperheater cartridge (501) having a desuperheater cartridge cavity (501C) and having a desuperheater cartridge gas inlet (501A) in communication with the desuperheater cartridge cavity (501C) for receiving gaseous working fluid and a desuperheater cartridge gas outlet (501B) for outputting the gaseous working fluid, the desuperheater cartridge cavity (501C) comprising a gas cooling cavity (C2) in communication with the desuperheater cartridge gas inlet (501A) and the desuperheater cartridge gas outlet (501B); and

-a first heat exchange tube (503) mounted on the desuperheating box (501), the first heat exchange tube (503) comprising a desuperheating tube section (5031) located within the gas cooling chamber (C2), the desuperheating tube section (5031) being configured to cool the gaseous working fluid within the gas cooling chamber (C2).

2. The desuperheating assembly (5) of claim 1, wherein the desuperheating assembly is configured to provide a desired heat transfer rate,

the desuperheating box gas inlet (501A) comprises a first gas inlet hole positioned at the middle of the desuperheating box (501) along a first direction, and the desuperheating box gas outlet (501B) comprises two first gas outlet holes positioned at two ends of the desuperheating box (501) along the first direction; or alternatively

The desuperheating box gas inlet (501A) comprises a second gas inlet hole positioned at the middle of the desuperheating box (501) along a first direction, and the desuperheating box gas outlet (501B) comprises a plurality of second gas outlet holes positioned at the desuperheating box (501) and distributed along the first direction; or,

the desuperheating box gas inlet (501A) comprises two third gas inlet holes at two ends of the desuperheating box (501) along the first direction, and the desuperheating box gas outlet (501B) comprises a third gas outlet hole at the middle of the desuperheating box (501) along the first direction.

3. The desuperheating assembly (5) of claim 1, wherein the desuperheating assembly is configured to provide a desired heat transfer rate,

-the desuperheater cartridge gas inlet (501A) is on the same side of the desuperheater cartridge (501) as the desuperheater cartridge gas outlet (501B); or (b)

-the desuperheater cartridge gas inlet (501A) and the desuperheater cartridge gas outlet (501B) are located on opposite sides of the desuperheater cartridge (501); or (b)

The desuperheating box gas inlet (501A) and the desuperheating box gas outlet (501B) are located on adjacent sides of the desuperheating box (501).

4. The desuperheating assembly (5) of claim 1, wherein the desuperheating cartridge (501) comprises a mounting orifice portion (5014, 5014',5014 "), the mounting orifice portion (5014, 5014', 5014") comprising a mounting hole (5014A), the first heat exchange tube (503) penetrating into the mounting hole (5014A) for mounting on the desuperheating cartridge (501).

5. The desuperheating assembly (5) of claim 4, wherein the desuperheating box (501) comprises two mounting orifice portions (5014, 5014',5014 ") disposed opposite each other, the first heat exchange tube (503) penetrating into the two mounting orifice portions (5014, 5014', 5014") simultaneously for mounting on the desuperheating box (501).

6. The desuperheating assembly (5) of claim 1, wherein the first heat exchange tube (503) further comprises a cooling tube segment (5032) located outside the desuperheating box (501).

7. The desuperheating assembly (5) of claim 1, wherein the desuperheating assembly (5) comprises a plurality of the first heat exchange tubes (503) disposed in a side-by-side, spaced relationship.

8. The desuperheating assembly (5) of claim 1, wherein the first heat exchange tube (503) is a straight tube extending in a first direction, the desuperheating assembly (5) is symmetrical with respect to a surface perpendicular to the first direction and/or the desuperheating assembly (5) is symmetrical with respect to a surface parallel to the first direction.

9. The desuperheating assembly (5) of claim 1, wherein the desuperheating box gas inlet (501A) comprises a first inlet aperture in a middle of the desuperheating box (501) in a first direction, and the desuperheating box gas outlet (501B) comprises two first outlet apertures at each end of the desuperheating box (501) in the first direction, the diameter of the first inlet aperture

Diameter +.>

Satisfy the following requirements/>

10. The desuperheating assembly (5) of claim 1, wherein the desuperheating assembly is configured to provide a desired heat transfer rate,

the desuperheating box inner cavity (501C) further comprises an air inlet and air equalizing cavity (C1), and the air inlet and air equalizing cavity (C1) is positioned between the desuperheating box air inlet (501A) and the air cooling cavity (C2) and is communicated with the desuperheating box air inlet (501A) and the air cooling cavity (C2);

The desuperheating component (5) further comprises an air inlet air homogenizing plate (502) positioned in the desuperheating box (501), and the air inlet air homogenizing plate (502) is positioned between the air inlet air homogenizing cavity (C1) and the air cooling cavity (C2) so as to separate the air inlet air homogenizing cavity (C1) and the air cooling cavity (C2), and a plurality of air inlet air homogenizing holes communicated with the air inlet air homogenizing cavity (C1) and the air cooling cavity (C2) are formed in the air inlet air homogenizing plate (502).

11. The desuperheating assembly (5) of claim 10, wherein the intake air equalizing plate (502) comprises an intake baffle region (5021) opposite the intake air direction and an intake orifice region (5022) connected to the intake baffle region (5021), the plurality of intake air equalizing holes being located on the intake orifice region (5022).

12. The desuperheating assembly (5) of claim 11, wherein the plurality of intake air equalizing holes are divided into a plurality of intake air equalizing hole groups in a direction from the intake baffle region (5021) to the intake orifice region (5022), wherein a diameter of a first intake air equalizing hole (502A) of the intake air equalizing hole group near the intake baffle region (5021) is smaller than a diameter of a second intake air equalizing hole (502B) of the intake air equalizing hole group far from the intake baffle region (5021).

13. The desuperheating assembly (5) of claim 12, wherein the inlet orifice region (5022) comprises twoThe diameter of a first air inlet and air equalizing hole (502A) of the air inlet and air equalizing hole group, which is close to the air inlet baffle zone (5021)

Diameter of a second air inlet and air equalizing hole (502B) of the air inlet and air equalizing hole group far away from the air inlet baffle area (5021)>

Satisfy->

14. The desuperheating assembly (5) of claim 13, wherein the desuperheating box gas inlet (501A) comprises a diameter of

Is provided with a first air inlet hole; the pressure drop delta P of the gaseous working medium flowing through the desuperheating component (5) is as follows:

ΔP＝Cρv ² ；

wherein ρ is the density of the gaseous working medium of the desuperheating box gas inlet (501A) with the unit of kg/m ³ ；

v is the flow velocity of the gaseous working medium at the gas inlet (501A) of the desuperheating box, and the unit is m/s;

n ₁ is of uniform pore diameter

The number of first air inlet and air equalizing holes (502A) of the air equalizing hole group;

n ₂ is of uniform pore diameter

The number of second air inlet and air equalizing holes (502B) of the air equalizing hole group;

and->

Is in m.

15. The desuperheating assembly (5) of claim 10, wherein the desuperheating assembly (5) comprises a gas baffle (504), the gas baffle (504) being located on an incoming side of the intake gas baffle (502) facing the gaseous working fluid.

16. The desuperheating assembly (5) of claim 1, wherein the desuperheating assembly is configured to provide a desired heat transfer rate,

/>

n is the number of the first heat exchange tubes (503);

d is the outer diameter of the first heat exchange tube (503) and the unit is m;

l is the length of the desuperheated pipe section (5031) in m;

T _in the unit is K for the temperature of the gaseous working medium at the gas inlet (501A) of the desuperheating box;

T _out the unit is K for the temperature of the gaseous working medium at the gas outlet (501B) of the desuperheating box;

T _wall the average temperature for the outer surface of the desuperheated pipe section (5031) is given in K.

17. The desuperheating assembly (5) of claim 1, further comprising a baffle (506), the baffle (506) disposed within the gas cooling cavity (C2) and configured to form a baffle flow path (P) within the gas cooling cavity (C2), an inlet end (PA) of the baffle flow path (P) in communication with the desuperheating box gas inlet (501A), an outlet end (PB) of the baffle flow path (P) in communication with the desuperheating box gas outlet (501B), at least a portion of the desuperheating pipe section (5031) being located within the baffle flow path (P).

18. The desuperheating assembly (5) of claim 17, wherein a plurality of baffles (506) are spaced apart within the gas cooling chamber (C2) along the direction of extension of the first heat exchange tube (503).

19. The desuperheating assembly (5) of claim 18, wherein the desuperheating assembly,

the inlet end (PA) of the baffling flow channel (P) is positioned at the middle part of the gas cooling cavity (C2) along the axial direction of the first heat exchange tube (503), and the outlet end (PB) of the baffling flow channel (P) is positioned at the end part of the gas cooling cavity (C2) along the axial direction of the first heat exchange tube (503); or alternatively

The inlet end (PA) of the baffling flow channel (P) is positioned at the end part of the gas cooling cavity (C2) along the axial direction of the first heat exchange tube (503), and the outlet end (PB) of the baffling flow channel (P) is positioned at the middle part of the gas cooling cavity (C2) along the axial direction of the first heat exchange tube (503).

20. The desuperheating assembly (5) of claim 19, wherein the desuperheating assembly (5) comprises two of the baffling flow channels (P) arranged in an axial direction of the first heat exchange tube (503).

21. The desuperheating assembly (5) of claim 17, wherein the baffle (506) is disposed at an angle to an axis of the desuperheating pipe section (5031), the baffle (506) having a through-hole (506A) therein through which the desuperheating pipe section (5031) passes.

22. The desuperheating assembly (5) of any of claims 1-21, wherein the desuperheating box inner chamber (501C) comprises an outlet gas plenum (C3), the outlet gas plenum (C3) being located between the gas cooling chamber (C2) and the desuperheating box gas outlet (501B) and in communication with the gas cooling chamber (C2) and the desuperheating box gas outlet (501B).

23. The desuperheating assembly (5) of claim 22, wherein at least a portion of the wall of the desuperheating box (501) is a double wall comprising an inner wall (5012 ') and an outer wall (5016') disposed outside of the inner wall (5012 '), and the chamber wall of the gas-out plenum (C3) comprises at least a portion of the inner wall (5012') and at least a portion of the outer wall (5016 '), the desuperheating box gas outlet (501B) being disposed on the outer wall (5016').

24. The desuperheating assembly (5) of claim 23, wherein the desuperheating box gas outlet (501B) comprises a plurality of second gas outlet holes distributed on the outer-layer wall (5016').

25. The desuperheating assembly (5) of claim 24, wherein the plurality of second gas outlet holes form a plurality of gas outlet hole groups of successively decreasing diameter from a side proximate to the desuperheating box gas inlet (501A) to a side distal to the desuperheating box gas inlet (501A).

26. The condenser according to claim 17, wherein the desuperheating assembly (5) satisfies:

ε＝0.1-0.5；

wherein T is _in The unit is K for the temperature of the gaseous working medium at the gas inlet (501A) of the desuperheating box;

T _wall -an average temperature in K for the outer surface of the desuperheated pipe section (5031);

ρ is the density of the gaseous working medium at the desuperheating box gas inlet (501A), kg/m ³ ；

D is the diameter of a through-flow part at the air inlet hole of the desuperheating box air inlet (501A), and the unit is m;

l is the length of the desuperheated pipe section (5031) in m;

n is the number of the first heat exchange tubes (503);

d _k the equivalent diameter of the tube distribution of the first heat exchange tube (503) is m;

λ is the coefficient of thermal conductivity of the gaseous working medium in the desuperheating box inner cavity (501C) at the average temperature, and the unit is W/(m×k);

cp is the specific heat capacity of the gaseous working medium in the inner cavity (501C) of the desuperheating box at the average temperature, and the unit is kJ/(kg x K);

mu is the viscosity of the gaseous working medium in the inner cavity (501C) of the desuperheating box at the average temperature, and the unit is Pa;

μ _w The viscosity of the gaseous working medium in the inner cavity (501C) of the desuperheating box at the average temperature of the pipe wall of the desuperheating pipe section (5031) is expressed as P _a *s；

P _t The unit is m for the tube spacing of the first heat exchange tube (503);

D _k the unit is m for the inner diameter of the shell (3) of the condenser where the desuperheating box (5) is located;

l _b is the spacing of adjacent baffles (506) in m;

P _r is the Plantt number;

epsilon is a constant and takes a value of 0.1-0.5.

27. The desuperheating assembly (5) of claim 26, wherein the number of baffles (506) satisfies:

/>

wherein,,

Δp is the pressure drop generated by the flow of gaseous working fluid through the desuperheating assembly (5);

n _b is the total number of baffles (506);

c is a constant and takes a value of 0.02-0.25.

28. The desuperheating assembly (5) of claim 17, wherein the baffle (506) is provided with a vent (506B) through which the gaseous working fluid flows.

29. The desuperheating assembly (5) of claim 28, wherein the vent hole (506B) has a diameter of 2mm to 8mm; and/or the total flow area of all the vent holes (506B) on the baffle plate (506) accounts for 1/8-3/4 of the total area of the baffle plate (506).

30. The desuperheating assembly (5) of claim 28, wherein the desuperheating assembly (5) comprises at least two baffles (506), the at least two baffles (506) having an average hydraulic diameter D _d And in the extending direction of the first heat exchange tube (503), the distance between two adjacent baffle plates (506) is l _b ，D _d And l _b The following relationship is satisfied:

wherein Δp is the pressure drop generated by the flow of the gaseous working fluid through the desuperheating assembly (5);

c is a constant, and the value is 0.3-1.5;

ρ is the density of the gaseous working medium of the desuperheating box gas inlet (501A) with the unit of kg/m ³ ；

v ₀ For the average flow rate of the gaseous working medium through the at least two baffles (506), the unit is m/s;

d is the diameter of the through-flow part at the desuperheating box gas inlet (501A) and is expressed as m;

n is the number of the first heat exchange tubes (503);

d is the outer diameter of the first heat exchange tube (503) and the unit is m.

31. The desuperheating assembly (5) of claim 28, wherein the first heat exchange tube (503) has an outer diameter d that satisfies the relationship:

T _wall an average temperature in K for the outer surface of the desuperheated pipe section (5301);

v is the flow velocity of the gaseous working medium at the gas inlet (501A) of the desuperheating box, and the unit is m/s; l is the length of the desuperheated pipe section (5031) in m;

n is the number of the first heat exchange tubes (503);

mu is the viscosity of the gaseous working medium in the inner cavity (501C) of the desuperheating box at the average temperature, and the unit is P _a *s；

Epsilon is a constant and takes a value of 15 to 200;

d _e the equivalent diameter of the tube distribution of the first heat exchange tube (503) is m;

P _t the unit is m for the tube pitch of the first heat exchange tube (503).

32. The desuperheating assembly (5) of claim 22, wherein the desuperheating assembly (5) comprises an air outlet air homogenizing plate (507), the air outlet air homogenizing plate (507) is arranged in the desuperheating box (501) and is positioned between the air cooling cavity (C2) and the air outlet air homogenizing cavity (C3), and air outlet air homogenizing holes which are communicated with the air cooling cavity (C2) and the air outlet air homogenizing cavity (C3) are formed in the air outlet air homogenizing plate (507).

33. The desuperheating assembly (5) of claim 32, wherein the gas outlet equalization plate (507) has a gas outlet baffle region (5071) and a gas outlet orifice region (5072), the gas outlet baffle region (5071) corresponding to a region of the baffle (506) within the gas cooling chamber (C2), the gas outlet orifice region (5072) being located on a side of the gas outlet baffle region (5071) remote from the desuperheating box gas inlet (501A).

34. The desuperheating assembly (5) of claim 33, wherein a ratio of a length L1 of the outlet aperture plate region (5072) to a length L2 of the outlet baffle region (5071) is 1/10-1/2 in a first direction of the desuperheating box (501).

35. The desuperheating assembly (5) of claim 32, wherein the gas-equalizing plate (507) is provided with a plurality of gas-equalizing holes, the plurality of gas-equalizing holes comprising a first gas-equalizing hole (507A) and a second gas-equalizing hole (507B), the diameter of the first gas-equalizing hole (507A) being larger than the diameter of the second gas-equalizing hole (507B).

36. The desuperheating assembly (5) of claim 35, wherein the first outlet gas equalization holes (507A) have a diameter of 12mm to 20mm; and/or the diameter of the second air outlet and equalizing hole (507B) is 6 mm-12 mm.

37. The desuperheating assembly (5) of claim 36, wherein the desuperheating box gas inlet (501A) comprises two third gas inlet holes at both ends of the desuperheating box (501) in a first direction, the desuperheating box gas outlet (501B) comprises a third gas outlet hole at a middle of the desuperheating box (501) in the first direction, the second gas outlet gas equalization holes (507B) are close to an edge of the gas outlet equalization plate (507) perpendicular to a second direction of the first direction relative to the first gas outlet equalization holes (507A), and a ratio of a length of the region of the first gas outlet equalization holes (507A) in the second direction to a length of the region of the second gas outlet equalization holes (507B) in the second direction is 3-10.

38. The desuperheating assembly (5) of claim 32, wherein the outlet gas equalization plate (507) further comprises an equalization plate liquid port (507C).

39. The desuperheating assembly (5) of claim 17, wherein the desuperheating box gas inlet (501A) comprises two third inlet holes at both ends of the desuperheating box (501) in the first direction, and the desuperheating box gas outlet (501B) comprises a third outlet hole in the middle of the desuperheating box (501) in the first direction; the desuperheating component (5) comprises a first partition plate (508), the first partition plate (508) is arranged in the gas cooling cavity (C2), the gas cooling cavity (C2) is divided into two sub-cooling cavities along the first direction, the two sub-cooling cavities are in one-to-one correspondence with the two third air inlet holes, and each sub-cooling cavity is internally provided with a baffle plate (506).

40. The desuperheating assembly (5) of claim 39, further comprising a second baffle (509) positioned within the sub-cooling chamber and separating the sub-cooling chamber into a first gas cooling chamber (C21) and a second gas cooling chamber (C22) in communication with the desuperheating box gas inlet (501A), wherein a communication port is provided on the second baffle (509) or between the second baffle (509) and the desuperheating box (501) in communication with the first gas cooling chamber (C21) and the second gas cooling chamber (C22), and wherein the baffle (506) is disposed within the second gas cooling chamber (C22).

41. The desuperheating assembly (5) of any of claims 1-21, further comprising a screen (510), the screen (510) disposed on the desuperheating box (501) at the desuperheating box gas outlet (501B) configured to separate liquid within a gaseous working fluid passing through the desuperheating box gas outlet (501B).

42. The desuperheating assembly (5) of any of claims 1-21,

the desuperheater cartridge (501) further comprises a desuperheater cartridge liquid outlet (501D);

the desuperheating box inner cavity (501C) further comprises a liquid collection cavity (C4), the liquid collection cavity (C4) being located between the gas cooling cavity (C2) and the desuperheating box liquid outlet (501D);

The desuperheating component (5) further comprises a liquid separation plate (511), and a liquid separation plate liquid passing port (511A) which is communicated with the gas cooling cavity (C2) and the desuperheating box liquid outlet (501D) is formed in the liquid separation plate (511).

43. The desuperheating assembly (5) of claim 42, further comprising a drain pipe (512), the drain pipe (512) connected to the desuperheating box (501) and in communication with the desuperheating box liquid outlet (501D).

44. The desuperheating assembly (5) of any of claims 1-21, further comprising an inlet pipe (505), the inlet pipe (505) being in communication with the desuperheating box gas inlet (501A).

45. A condenser, comprising:

a housing (3) having a gaseous working medium inlet (3A) and a liquid working medium outlet (3B);

the desuperheating assembly (5) of any of claims 1-44, the desuperheating assembly (5) being located within the housing (3), the desuperheating cartridge (501) forming a condensing chamber (3C) with the housing (3), the gaseous working fluid inlet (3A) being in communication with the desuperheating cartridge gas inlet (501A), the desuperheating cartridge gas outlet (501B) being in communication with the condensing chamber (3C), the liquid working fluid outlet (3B) being in communication with the condensing chamber (3C); and

And the second heat exchange tube (4) is positioned in the condensation cavity (3C) and is configured to condense the gaseous working medium entering the condensation cavity (3C) from the desuperheating box gas outlet (501B) into liquid working medium.

46. The condenser of claim 45, further comprising a support plate assembly (6) comprising a support plate (601) and a support rod (602), the desuperheater cartridge (501) being connected to the support plate (601), the support plate (601) being connected to the inner wall of the shell (3), the support rod (602) being connected to the support plate (601) and to a tube sheet for supporting the second heat exchange tube (4).

47. A condenser according to claim 46, wherein the housing (3) is cylindrical, the length direction of the desuperheating box (501) extends in the axial direction of the housing (3), and the first heat exchange tube (503) and the second heat exchange tube (4) extend in the axial direction of the housing (3).

48. The condenser of claim 47, wherein the condenser is configured to,

the desuperheating box (501) is arranged symmetrically with respect to a plane passing through the axis of the housing (3), wherein,

the ratio of the distance of the desuperheating box (501) in the radial direction of the shell (3) in the section of the plane to the inner diameter of the shell (3) is 0.1-0.35; and/or

The ratio of the length of the desuperheating box (501) to the length of the shell (3) is 0.4-1 along the axial direction of the shell.

49. The condenser according to any one of claims 45 to 48, wherein the ratio of the number of the first heat exchange tubes (503) to the sum of the numbers of the first heat exchange tubes (503) and the second heat exchange tubes (4) is 3 to 25%.

50. A refrigeration system comprising a compressor and a condenser, wherein the condenser is a condenser according to any one of claims 45 to 49, and wherein the exhaust port of the compressor is connected to the gaseous working medium inlet (3A) of the condenser.