CN115930491A - Built-in oil separation, condenser and refrigerating device - Google Patents

Abstract

The present application provides a built-in oil composition, comprising: the shell is internally provided with a separation area, and the shell is provided with an air inlet part and an air outlet part, wherein the air inlet part is used for communicating the separation area with an exhaust port of the compressor so as to enable gaseous refrigerant discharged from the compressor to flow to the separation area; and at least two heat exchange tubes, every heat exchange tube at least part be located the disengagement zone to with the refrigerant heat transfer by inlet portion flow direction portion of giving vent to anger, wherein, the external diameter d of heat exchange tube satisfies:

based on this, can improve the single-phase heat transfer intensity of condenser.

Description

Built-in oil separation, condenser and refrigerating device

Technical Field

The application relates to the technical field of refrigeration equipment, in particular to a built-in oil content, a condenser and a refrigeration device.

Background

In refrigeration devices such as commercial water-cooled screw units and the like, the heat exchange process of superheated refrigerant gas (with the superheat degree of 4-10 ℃ in exhaust under the nominal working condition) exhausted from an exhaust port of a compressor in a condenser is to firstly remove superheat and then condense, namely, the superheated refrigerant firstly realizes single-phase flow heat exchange to reach a saturated state and then realizes condensation phase change heat exchange.

In the related art, the single-phase heat exchange and the condensation phase-change heat exchange processes are realized by the condenser pipe of the condenser, the heat exchange efficiency is poor, particularly, the condenser is usually designed based on the principle of intensified condensation heat exchange, the intensification degree of the flowing heat transfer process of the single-phase flow of the gas is limited, the single-phase heat exchange strength is low, the required heat exchange area is large, and the energy efficiency is influenced.

Therefore, how to improve the single-phase heat exchange strength of the superheated gas of the condenser is an important problem faced by the improvement of the energy efficiency of the condenser.

Disclosure of Invention

One technical problem to be solved by the present application is: the single-phase heat exchange strength of the condenser is improved.

In order to solve the above technical problem, a first aspect of the present invention provides a built-in oil composition, including:

the shell is internally provided with a separation area, and the shell is provided with an air inlet part and an air outlet part, wherein the air inlet part is used for communicating the separation area with an exhaust port of the compressor so as to enable gaseous refrigerant discharged from the compressor to flow to the separation area; and

at least two heat exchange tubes, at least part of each heat exchange tube is positioned in the separation region to exchange heat with a refrigerant flowing from the air inlet part to the air outlet part;

wherein, the external diameter of heat exchange tube is d, and d satisfies following relation:

wherein, T _in The temperature of the gaseous refrigerant at the inlet of the air inlet part; t is _out The temperature of the gaseous refrigerant at the outlet of the air outlet part; t is a unit of _wall Is the average temperature of the outer surface of the portion of the heat exchange tube within the housing; ρ is the gas density; d is the inner diameter of the air inlet part; v is the flow speed of the gaseous refrigerant at the inlet of the air inlet part; l is the length of the heat exchange tube in the built-in oil component; n is the number of heat exchange tubes in the built-in oil component; lambda is the heat conductivity coefficient of the refrigerant gas at the average temperature; cp is the specific heat capacity of the refrigerant gas at the average temperature; mu is the viscosity of the refrigerant gas at the average temperature; u. of _w The viscosity of the refrigerant gas at the temperature of the tube wall of the part of the heat exchange tube positioned in the shell; epsilon is a constant and takes a value of 15-200; d _e The equivalent diameter of the tube distribution of the heat exchange tube; p is _t The tube pitch of the heat exchange tubes.

In some embodiments, the internal oil component comprises at least two baffles, and the at least two baffles are arranged in the separation region and enable the refrigerant to flow in a baffled manner when flowing through the heat exchange tubes.

In some embodiments, the baffle plate is provided with vent holes through which the refrigerant flows.

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

In some embodiments, the baffle plate is provided with through holes, and the heat exchange tube passes through the baffle plate through the through holes.

In some embodiments, the at least two baffles have an average hydraulic diameter D _d And the distance between two adjacent baffle plates is l in the length direction of the heat exchange tube _b ，D _d And l _b The following relationship is satisfied:

wherein, the delta P is the pressure drop of the built-in oil inlet and outlet; c is a constant and takes a value of 0.3-1.5; rho is the density of the gaseous refrigerant; v. of ₀ The average flow velocity of the gaseous refrigerant flowing through the at least two baffle plates is obtained; d is the inner diameter of the air inlet part; v is the flow speed of the gaseous refrigerant at the inlet of the air inlet part; n is the number of heat exchange tubes in the built-in oil component; d is the outer diameter of the heat exchange tube.

In some embodiments, the built-in oil component includes a gas-homogenizing plate disposed in the casing and located between the heat exchange tube and the gas outlet portion, the gas-homogenizing plate has an open region, the open region is provided with a gas-homogenizing hole, and a refrigerant after exchanging heat with the heat exchange tube flows to the gas outlet portion through the gas-homogenizing hole.

In some embodiments, the gas homogenizing plate has a non-opening area, the non-opening area is not provided with the gas homogenizing holes and corresponds to the area where the baffle plate is located in the separation area, and the opening area is located on one side of the non-opening area, which is far away from the gas inlet portion.

In some embodiments, the ratio of the length L1 of the open region to the length L2 of the non-open region is 1/10 to 1/2.

In some embodiments, a plurality of air equalizing holes are arranged on the air equalizing plate, the air equalizing holes comprise a first air equalizing hole and a second air equalizing hole, and the diameter of the first air equalizing hole is larger than that of the second air equalizing hole.

In some embodiments, the first gas homogenizing hole has a diameter of 12mm to 20mm; and/or the diameter of the second uniform air hole is 6 mm-12 mm.

In some embodiments, the second air equalizing hole is close to the edge of the air equalizing plate in the width direction relative to the first air equalizing hole, and the ratio of the width of the area where the first air equalizing hole is located to the width of the area where the second air equalizing hole is located is 3-10.

In some embodiments, the housing is provided with two air inlet portions, and the two air inlet portions are located on two sides of the air outlet portion and are both communicated with the separation region.

In some embodiments, the built-in oil component includes a partition plate disposed in the separation region and dividing the separation region into two sub-separation regions, the two sub-separation regions corresponding to the two inlet portions one-to-one.

In some embodiments, baffles are disposed within both of the sub-separation zones.

The second aspect of the present application provides a condenser, which includes a housing and a condensation pipe, and further includes the built-in oil component of the embodiments of the present application, the built-in oil component is disposed in the housing, a condensation zone is formed in a region where the built-in oil component is not disposed in the housing, and at least a portion of the condensation pipe is located in the condensation zone.

The third aspect of the present application also provides a refrigeration device comprising a compressor, and further comprising a condenser of an embodiment of the present application, an air inlet of the condenser being connected to an air outlet of the compressor.

Through set up the heat exchange tube in built-in oil branch, carry out single-phase heat transfer with the refrigerant before the refrigerant flows to the condenser pipe to provide the computational formula of heat exchange tube size parameter, can effectively improve the single-phase heat transfer intensity of condenser.

Further features of the present application and advantages thereof will become apparent from the following detailed description of exemplary embodiments thereof, which is to be read in connection with the accompanying drawings.

Drawings

In order to more clearly illustrate the embodiments of the present application or the technical solutions in the prior art, the drawings needed to be used in the description of the embodiments or the prior art will be briefly introduced below, and it is obvious that the drawings in the following description are only some embodiments of the present application, and it is obvious for those skilled in the art that other drawings can be obtained according to the drawings without inventive exercise.

Fig. 1 shows the overall structure of a condenser in the embodiment of the present application.

Fig. 2 is a side view of the combined structure of the built-in oil and the cylinder in the embodiment of the present application.

Fig. 3 is a perspective view of the oil component incorporated in the embodiment of the present application.

Fig. 4 shows an internal structure of the built-in oil in the embodiment of the present application.

Fig. 5 shows the structure of the first baffle plate in the embodiment of the present application.

Fig. 6 shows the structure of the second baffle plate in the embodiment of the present application.

FIG. 7 is a side view of a gas distribution plate in an embodiment of the present application.

FIG. 8 is a top view of a gas distribution plate in an embodiment of the present application.

Fig. 9 shows a distribution diagram of the gas-homogenizing holes on the single plate body of the gas-homogenizing plate in the embodiment of the application.

Description of the reference numerals:

100. a condenser; 101. a housing; 102. oil is filled in; 103. a condenser tube; 104. a condensation zone; 105. a barrel; 106. a tube sheet; 107. a flange; 108. a water chamber; 109. a liquid collection part;

1. a housing; 11. an end plate; 12. a side plate; 13. closing the plate; 14. a connecting plate; 15. a frame;

2. an air intake portion; 21. an air inlet pipe;

3. an air outlet part; 31. filtering with a screen;

4. a gas homogenizing plate; 41. opening the hole area; 42. a non-apertured region; 43. air equalization holes; 44. a first air equalizing hole; 45. a second air equalizing hole; 46. an oil leakage port;

5. a heat exchange tube;

6. a baffle plate; 61. a first baffle plate; 62. a second baffle plate; 63. perforating the tube hole; 64. a vent hole;

71. a partition plate; 72. a baffle plate; 73. an oil leakage plate;

8. an oil outlet pipe;

91. a chamber; 92. an oil storage area; 93. a filtration zone; 94. a separation zone; 95. a sub-separation zone.

Detailed Description

The technical solutions in the embodiments of the present application will be described clearly and completely with reference to the drawings in the embodiments of the present application, and it is obvious that the described embodiments are only some embodiments of the present application, and 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 application, its application, or uses. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without any inventive step, are within the scope of the present disclosure.

Techniques, methods, and apparatus known to those of ordinary skill in the relevant art may not be discussed in detail but are intended to be part of the specification where appropriate.

In the description of the present application, it is to be understood that the orientation or positional relationship indicated by the directional terms such as "front, rear, upper, lower, left, right", "lateral, vertical, horizontal" and "top, bottom", etc., are generally based on the orientation or positional relationship shown in the drawings, and are used for convenience of description and simplicity of description only, and in the case of not making a reverse description, these directional terms do not indicate and imply that the device or element being referred to must have a particular orientation or be constructed and operated in a particular orientation, and therefore, should not be considered as limiting the scope of the present application; the terms "inner and outer" refer to the inner and outer relative to the profile of the respective component itself.

In the description of the present application, it should be understood that the terms "first", "second", etc. are used to define the components, and are used only for the convenience of distinguishing the corresponding components, and if not otherwise stated, the terms have no special meaning, and thus, should not be construed as limiting the scope of the present application.

In addition, the technical features mentioned in the different embodiments of the present application described below may be combined with each other as long as they do not conflict with each other.

For refrigeration devices such as commercial water-cooled screw units, the refrigerant entering the condenser is usually superheated gas, and single-phase flow heat exchange, superheat removal and condensation phase change heat exchange are required to be carried out in the condenser.

In the related art, the single-phase heat exchange and the condensation phase-change heat exchange of the superheated refrigerant gas are realized by the condenser pipe of the condenser, however, the enhancement degree of the condenser in the related art to the single-phase flow flowing heat transfer process is limited, so that the single-phase heat exchange strength is low, and the required heat exchange area is large, for example, in some condensers, the single-phase heat transfer coefficient is far lower than the phase-change heat transfer coefficient (the difference is 10-20 times), the single-phase heat exchange load only accounts for 4% -8% of the whole load of the heat exchanger, but 25% -40% of the heat exchange area of the pipe bundle is required to be occupied, and the whole energy efficiency of the condenser is influenced.

Therefore, how to improve the strength of single-phase heat exchange of the superheated gas of the condenser is an important problem faced by the current condenser energy efficiency improvement.

To above-mentioned condition, in order to promote condenser to superheated gas's single-phase heat transfer intensity, and then to promote the efficiency of condenser, the structure of condenser is improved to this application to mainly improve the oil and gas separator's of condenser structure.

The oil-gas separator plays a role in separating oil drops in gaseous refrigerants in the refrigerating device, the principle comprises impact inertia separation, screening action, adsorption action and the like, and the oil drops in compressor exhaust are prevented from entering the condenser and then entering the evaporator to influence the overall energy efficiency of the unit.

The arrangement mode of the oil-gas separator mainly comprises an internal mode and an external mode. Wherein, for external oil and gas separator, built-in oil and gas separator (built-in oil content promptly) sets up inside the shell of condenser, need not to occupy condenser exterior space alone, and connecting line is less, is favorable to realizing better oil-gas separation effect.

This application mainly improves through the structure to built-in oil content, promotes the condenser to superheated gas's single-phase heat transfer intensity, and then promotes the efficiency of condenser.

Fig. 1 to 9 exemplarily show a condenser and a structure of an oil content built therein according to the present application. In fig. 1, the housing is processed in a perspective manner to clearly show the structure inside the housing.

Referring to fig. 1 to 9, in the present application, the built-in oil 102 is an oil separator provided inside a casing 101 of a condenser 100, and includes a shell 1 and a heat exchange pipe 5. The shell 1 is provided with a separation area 94, and the shell 1 is provided with an air inlet part 2 and an air outlet part 3. The inlet portion 2 communicates the separation region 94 with a compressor discharge port (not shown) so that the gaseous refrigerant discharged from the compressor flows to the separation region 94. The gas outlet 3 connects the separation region 94 with the condensation region 104 of the condenser 100, so that the refrigerant flows from the separation region 94 to the condensation region 104 through the gas outlet 3, and exchanges heat with the condensation pipe 103 in the condensation region 104. At least a portion of the heat exchange tubes 5 are positioned in the separation region 94 to exchange heat with the refrigerant flowing from the inlet portion 2 to the outlet portion 3.

In the related art, the heat exchange tube 5 is not arranged in the built-in oil content 102 of the condenser 100, and the refrigerant does not exchange heat in the process of oil-gas separation when flowing through the built-in oil content 102, but carries out single-phase heat exchange and condensation phase-change heat exchange at the condenser pipe 103 of the condensation area 104 after flowing out of the built-in oil content 102 to the condensation area 104, that is, in the related art, the single-phase heat exchange and the condensation phase-change heat exchange are both realized by the condenser pipe 103, and in this case, the single-phase heat exchange strength is low, which affects the energy efficiency of the condenser 100.

And this application is through set up heat exchange tube 5 in built-in oil content 102, utilizes heat exchange tube 5 to come before the refrigerant flows through flow direction condenser pipe 103, carries out single-phase heat transfer with the refrigerant in advance, can effectively promote condenser 100's single-phase heat transfer intensity, strengthens condenser 100's the strength of removing overheated heat transfer, promotes condenser 100's efficiency.

Meanwhile, the heat exchange tube 5 is additionally arranged in the built-in oil content 102 to improve the single-phase heat exchange strength, the realization of the conventional oil-gas separation function of the built-in oil content 102 is not influenced, and on the contrary, the area of the built-in oil content 102 for collision separation with a refrigerant can be increased due to the additionally arranged heat exchange tube 5, so that the realization of the normal oil-gas separation function of the built-in oil content 102 is not influenced, the oil-gas separation efficiency of the built-in oil content 102 is improved, and the oil-gas separation effect of the built-in oil content 102 is improved.

In addition, the added heat exchange tube 5 is positioned inside the shell 1 with the oil component 102 inside, so that additional occupied space is not needed, the condenser 100 is favorably miniaturized, and the phenomenon that the energy efficiency of the condenser 100 is influenced due to the fact that the tube distribution space in the condenser 100 is reduced because the problem of intensified heat exchange of the superheated gas is solved can be prevented.

It can be seen that, this application creatively fuses built-in oil content 102 and heat exchange tube 5 into one for the refrigerant can be through heat exchange tube 5 and condenser pipe 103 two-stage heat transfer at the in-process of condenser 100 of flowing through, not only can realize and promote the oil-gas separation function of built-in oil content 102, can also realize the promotion of condenser 100 single-phase heat transfer intensity simultaneously to and the miniaturization of condenser 100, thereby effectively promote condenser 100's whole efficiency.

Wherein, in this application, built-in oil 102 can include at least two heat exchange tubes 5, and the external diameter of heat exchange tube 5 is d, and d satisfies following relation:

wherein, T _in The temperature of the gaseous refrigerant at the inlet of the air inlet part 2; t is a unit of _out The temperature of the gaseous refrigerant at the outlet of the gas outlet part 3; t is a unit of _wall Is the average temperature of the outer surface of the portion of the heat exchange tube 5 located inside the casing 1; ρ is the gas density; d is the inner diameter of the inlet 2; v is the flow velocity of the gaseous refrigerant at the inlet of the air inlet part 2; l is the length of the heat exchange tube 5 in the built-in oil 102; n is the number of the heat exchange tubes 5 in the built-in oil component 102; lambda is the heat conductivity coefficient of the refrigerant gas at the average temperature; cp is the specific heat capacity of the refrigerant gas at the average temperature; mu is the viscosity of the refrigerant gas at the average temperature; u. of _w The viscosity of the refrigerant gas at the tube wall temperature of the part of the heat exchange tube 5 positioned in the shell 1; epsilon is a constant and takes a value of 15-200; d _e The equivalent diameter of the heat exchange tube 5 is; p _t The tube pitch of the heat exchange tubes 5.

Based on the above formula, the heat exchange tube 5 is conveniently designed, the built-in oil component 102 which can effectively remove overheat can be conveniently designed, and particularly, the D, D, L and D can be reasonably designed _e And P _t The value of the size parameter is equal, so that the built-in oil 102 can realize better overheating removing effect. Wherein if the oil component 102 is provided with baffles 6 as described below, the epsilon willThe volume value can be determined according to the design condition of the baffle plate 6. Under the condition that the temperature difference between the inlet and the outlet is not changed, epsilon is in direct proportion to the coefficient of superheat removal heat exchange of the built-in oil component 102, and the coefficient of superheat removal heat exchange is increased along with the increase of epsilon.

It can be seen that the heat exchange tube 5 is provided in the internal oil 102, and the inner diameter D of the inlet 2 of the internal oil 102, the outer diameter D of the heat exchange tube 5, the length L of the heat exchange tube 5 in the internal oil 102, and the equivalent diameter D of the heat exchange tube 5 are set _e And tube pitch P of heat exchange tube 5 _t And the like, the single-phase heat exchange strength of the condenser 100 can be effectively improved, and the energy efficiency of the condenser 100 is improved.

In order to further improve the energy efficiency of the condenser 100, referring to fig. 4, in some embodiments, the internal oil component 102 includes not only the shell 1 and the heat exchange tube 5, but also at least two baffles 6, and the at least two baffles 6 are disposed in the separation region 94 and make the refrigerant flow in a baffled manner when flowing through the heat exchange tube 5. The baffles 6 in the internal oil component 102 are arranged side by side in the length direction of the heat exchange tube 5, and the baffles 6 adjacent to the baffles 6 are arranged in a staggered manner in the direction intersecting the length direction of the heat exchange tube 5 (for example, the height direction or the width direction of the internal oil component 102, that is, the up-down direction or the front-back direction in fig. 4), so that the refrigerant turns back and forth when flowing through the heat exchange tube 5, and a baffled flow similar to a wave shape is formed.

Because the baffling board 6 that sets up, can reduce the through-flow area in the separation region 94, promote the gas flow rate of violently glancing over the tube bank (under the unchangeable prerequisite of total flow, the through-flow area reduces, the velocity of flow increases), and reduce the angle between gas flow direction and the heat exchange tube 5, make the gas flow direction that is on a parallel with the heat exchange tube 5 originally become for heat exchange tube 5 slope, consequently, can improve the heat transfer sufficiency between refrigerant gas and the heat exchange tube 5, effectively promote the heat transfer intensity of overheated refrigerant gas in heat exchange tube 5 department, realize the further reinforcing to single-phase heat transfer intensity, thereby further promote the efficiency of condenser 100.

Meanwhile, the baffle plate 6 can increase the collision separation area of oil drops, so that the oil-gas separation efficiency is improved, and the energy efficiency of the condenser 100 is improved.

It can be seen that, by further arranging the baffle plate 6 in the separation region 94, the single-phase heat exchange strength and the oil-gas separation efficiency can be further improved, so that the energy efficiency of the condenser 100 is further improved.

Fig. 5 and 6 further illustrate the structure of the baffle 6.

Referring to fig. 5-6 in conjunction with fig. 4, in some embodiments, the baffles 6 are provided with through-holes 63, and the heat exchange tubes 5 pass through the baffles 6 via the through-holes 63. At this moment, heat exchange tube 5 can play the supporting role to baffling board 6, effectively improves structural stability, moreover, because baffling board 6 is integrated on heat exchange tube 5, consequently, the baffling board 6 of being more convenient for cooperates with heat exchange tube 5, effectively promotes single-phase heat transfer intensity and oil-gas separation efficiency.

In addition, referring to fig. 5 and 6, in some embodiments, the baffle plate 6 is provided with a vent hole 64 for the refrigerant to flow through.

Although the vent holes 64 may not be formed in the baffle plate 6, after the vent holes 64 are formed, part of the refrigerant gas can be allowed to pass through the baffle plate 6 through the vent holes 64, so that the baffling pressure drop of the refrigerant gas can be reduced to a certain extent, and the gaseous refrigerant flowing out after baffling is effectively prevented from being excessively large in pressure drop.

Under the condition that the vent holes 64 are formed in the baffle plate 6, the size and the number of the vent holes 64 can be designed to control the total flow area of the vent holes 64, so that a better baffling effect and a better pressure reduction prevention effect are achieved at the same time. For example, in some embodiments, the diameter of the vent 64 is 2mm to 8mm; and/or the total flow area of all the vent holes 64 on the baffle plate 6 accounts for 1/8-3/4 of the total area of the baffle plate 6. Therefore, the pressure drop can be effectively reduced, and a better baffling effect can be realized, so that the baffling effect of the baffle plate 6 is not influenced by overlarge and/or too much vent holes 64.

In some embodiments, the average hydraulic diameter of all baffles 6 is D _d And the distance between two adjacent baffle plates 6 in the length direction of the heat exchange tube 5 is l _b ，D _d And l _b The following relationship is satisfied:

wherein, Δ P is the pressure drop of the inlet and outlet of the built-in oil 102; c is a constant and takes a value of 0.3-1.5; rho is the density of the gaseous refrigerant; v. of ₀ The average flow velocity of the gaseous refrigerant flowing through at least two baffle plates 6; d is the inner diameter of the intake part 2; v is the flow velocity of the gaseous refrigerant at the inlet of the air inlet part 2; n is the number of the heat exchange tubes 5 in the built-in oil component 102; d is the outer diameter of the heat exchange tube 5.

Based on the formula, the heat exchange pipe 5 and the baffle plate 6 are conveniently designed, and the built-in oil component 102 which can effectively remove overheat is conveniently designed.

Wherein the pressure drop Δ P is proportional to C, increasing with increasing C. The average flow velocity v of the gaseous refrigerant flowing through all the baffle plates 6 is influenced by controlling the value of C ₀ To comprehensively control the pressure drop and heat exchange performance of the internal oil component 102. Specifically, the pressure drop of the internal oil component 102 when the heat exchange performance is optimal can be smaller by reasonably designing the values of the dimensional parameters such as D and D.

Referring back to fig. 4, in some embodiments, the internal oil component 102 includes not only the casing 1 and the heat exchange tube 5, but also the gas-homogenizing plate 4, the gas-homogenizing plate 4 is disposed in the casing 1 and located between the heat exchange tube 5 and the gas outlet portion 3, the gas-homogenizing plate 4 has an open area 41, the open area 41 is provided with a gas-homogenizing hole 43, and the refrigerant after heat exchange with the heat exchange tube 5 flows to the gas outlet portion 3 through the gas-homogenizing hole 43.

The gas homogenizing plate 4 can homogenize a flow field, so that refrigerant gas flowing from the heat exchange tube 5 to the gas outlet part 3 is more uniformly distributed, the collision with oil drops in the refrigerant can be increased, and the impact separation capacity of the built-in oil content 102 is enhanced, so that the oil-gas separation efficiency of the built-in oil content 102 can be effectively improved.

Further, as shown in fig. 4 and fig. 7 to 8, in some embodiments, the gas homogenizing plate 4 not only has the opening area 41, but also has the non-opening area 42, the non-opening area 42 is not provided with the gas homogenizing holes 43 and corresponds to the area where the baffle plate 6 in the separation area 94 is located, and the opening area 41 is located on the side of the non-opening area 42 away from the gas inlet 2.

Based on the above arrangement, the gas-homogenizing plate 4 is not provided with holes in the part of the corresponding area of the baffle plate 6, and only the part behind the baffle plate 6 is provided with holes, so that the baffling effect of the baffle plate 6 can be fully exerted, and the single-phase heat exchange strength and the oil-gas separation efficiency are effectively improved.

Specifically, referring to fig. 8, in some embodiments, the ratio of the length L1 of the open area 41 to the length L2 of the non-open area 42 is 1/10 to 1/2. At this time, the proportion of the open pore region 41 and the non-open pore region 42 is appropriate, so that the good gas equalizing effect can be realized, and simultaneously, the sufficient baffling length is provided to perform enhanced heat exchange and oil drop separation, and the pressure drop of the refrigerant flowing through the gas equalizing plate 4 is appropriate and not too large.

In addition, referring to fig. 9, in some embodiments, a plurality of air equalizing holes 43 are formed in the air equalizing plate 4, and the plurality of air equalizing holes 43 includes a first air equalizing hole 44 and a second air equalizing hole 45, and a diameter of the first air equalizing hole 44 is larger than a diameter of the second air equalizing hole 45. At this moment, the gas-homogenizing plate 4 is provided with the gas-homogenizing holes 43 with different diameters, so that oil drops with different particle sizes can be conveniently separated, and the pressure drop can be favorably controlled within a reasonable range.

Specifically, in some embodiments, the first leveling holes 44 have a diameter of 12mm to 20mm; and/or the diameter of the second uniform air hole 45 is 6 mm-12 mm. At this moment, the diameter size of first gas pore 44 and the equal gas pore 45 of second is comparatively suitable, and convenient processing just can satisfy the oil drop separation demand of different particle size, and effective control pressure drop is in reasonable scope.

In addition, referring to fig. 9, in some embodiments, the second uniform air holes 45 are located near the edge of the first uniform air holes 44 in the width direction of the uniform air plate 4, and the ratio of the width of the area where the first uniform air holes 44 are located (2H 1 in fig. 9) to the width of the area where the second uniform air holes 45 are located (2H 2 in fig. 9) is 3 to 10. At this time, the distribution range of the first air equalizing holes 44 and the second air equalizing holes 45 is reasonable, and the pressure drop can be effectively controlled within a reasonable range while the requirement of separating oil drops with different particle sizes is met.

Returning to fig. 4, in some embodiments, two inlet portions 2 are provided on the housing 1, and the two inlet portions 2 are located on both sides of the outlet portion 3 and both communicate with the separation region 94. Thus, the refrigerant can enter the internal oil 102 from the inlet parts 2 at both sides and flow out of the internal oil 102 from the outlet part 3 at the middle part, and in the process of flowing from both sides to the middle part, the refrigerant flows through the heat exchange tubes 5 in the separation zone 94 to perform single-phase heat exchange and remove superheat. At the moment, the heat exchange efficiency and the oil-gas separation efficiency are both high.

In the case where two inlet portions 2 are provided on the casing 1, referring to fig. 4, in some embodiments, the built-in oil 102 includes a partition plate 71, and the partition plate 71 is disposed in the separation region 94 and divides the separation region 94 into two sub-separation regions 95, and the two sub-separation regions 95 correspond to the two inlet portions 2 one to one. Therefore, the refrigerants in the two sub-separation areas 95 are not interfered with each other, and a more efficient single-phase heat exchange and oil-gas separation process can be realized.

And, with continued reference to fig. 4, in some embodiments, baffles 6 are provided within both of the sub-separation zones 95. Like this, all can carry out the baffling in two sub-separation zones 95, single-phase heat transfer intensity and oil-gas separation efficiency are higher.

The embodiments shown in fig. 1-9 will be further described below.

As shown in fig. 1-9, in this embodiment, condenser 100 is a horizontal condenser, which includes a housing 101 and a condenser tube 103, and further includes a built-in oil 102. The internal oil 102 is provided in the casing 101. The region of the enclosure 101 where the oil 102 is not disposed forms a condensation zone 104. At least a portion of the condenser tube 103 is located within the condensing zone 104.

Specifically, the housing 101 includes a cylinder 105, a tube sheet 106, a flange 107, and a water chamber 108. The cylinder 105 has a substantially hollow cylindrical shape, and has a substantially horizontal axis in the left-right direction. The lower part of the side wall of the cylinder 105 is provided with a liquid collecting part 109, and the liquid collecting part 109 is communicated with the condensation zone 104 to collect the liquid obtained by condensation. The tube plate 106, the flange 107, and the water chamber 108 are provided at both axial ends of the cylinder 105 to seal both axial ends of the cylinder 105, so that a closed space is formed inside the casing 101. The tube plate 106 is connected to an axial end of the cylinder 105 through a flange 107, and supports the condensation tube 103 and the heat exchange tube 5 containing the oil 102. And the water chamber 108 is connected to the side of the tube sheet 106 remote from the flange 107.

The built-in oil 102 and the condensation pipe 103 are both provided in the casing 101. The internal oil 102 is provided on the upper side of the inside of the casing 101. The area without the built-in oil component 102 in the casing 101 forms a condensation area 104, and the condensation pipe 103 is arranged in the condensation area 104 and is positioned at the middle lower side in the casing 101 so as to exchange heat with the refrigerant flowing out of the built-in oil component 102 and realize condensation of the refrigerant. Specifically, as shown in fig. 1, in this embodiment, a plurality of condensation tubes 103 are provided in the condensation zone 104, and each condensation tube 103 penetrates the condensation zone 104 along the axial direction of the cylinder 105 (i.e., the longitudinal direction of the internal oil 102), and both ends of the condensation tube 103 are supported by tube plates 106 on both sides of the cylinder 105.

Next, the structure of the built-in oil 102 will be described with emphasis.

As shown in fig. 3 to 9, in this embodiment, the internal oil component 102 is substantially symmetrical in the longitudinal direction and the width direction, and has a V-shaped overall cross section.

Specifically, as shown in fig. 3 and 4, the internal oil 102 of this embodiment includes a casing 1, a screen 31, two air inlet pipes 21, an air-equalizing plate 4, a heat exchange pipe 5, a baffle plate 6, a partition plate 71, a baffle plate 72, and an oil leakage plate 73.

The housing 1 is used to provide a mounting base for other structural components of the built-in oil 102 and protect the structural components arranged therein to a certain extent. As can be seen from fig. 3 and 4, in this embodiment, the housing 1 includes two end plates 11, two side plates 12, two closing plates 13, two connecting plates 14, and a frame 15. The two end plates 11 are arranged opposite to each other in the longitudinal direction (i.e., the left-right direction in fig. 3 and 4), and are substantially fan-shaped. The two side plates 12 are each substantially V-shaped, are disposed opposite to each other in the width direction (i.e., the front-rear direction in fig. 3 and 4), and are connected to the front and rear edges of the two end plates 11. The two closing plates 13 are each polygonal (e.g., have 5 folded edges), are arranged between the two end plates 11, and are spaced apart in the longitudinal direction, and are connected to the two side plates 12 and the end plates 11 on the corresponding side, respectively. Two connecting plates 14 are connected to the side of the two closing plates 13 away from the end plate 11. The frame 15 is disposed between the two connecting plates 14, and is connected to both the two connecting plates 14 and the two side plates 12. So, two end plates 11, two curb plates 12, two shrouding 13, two connecting plates 14 and frame 15 enclose to close and form whole casing 1 that is the V style of calligraphy and inside cavity 91 that is equipped with, and wherein, two end plates 11 and two curb plates 12 form casing 1's all around and bottom profile together, and two shrouding 13, two connecting plates 14 and frame 15 then form casing 1's upper portion profile together.

The frame 15 is used to support the screen 31. The filter screen 31 is disposed on the frame 15 and below the frame 15, and forms the air outlet 3 with the oil 102 therein, for communicating the chamber 91 with the condensation area 104 of the condenser 100. The refrigerant flowing out of the built-in oil 102 flows through the filter screen 31 and the frame 15, enters the condensation area 104 of the condenser 100, and exchanges heat with the condensation pipe 103 in the condensation area 104. The refrigerant flowing through the screen 31 may be filtered by the screen 31 for further oil-gas separation. The frame 15 is hollow, so that the refrigerant flowing out of the filter screen 31 is not blocked.

Since the frame 15 is positioned at the middle of the built-in oil 102 in the longitudinal direction, the screen 31 provided in the frame 15 is also positioned at the middle of the built-in oil 102 in the longitudinal direction, and the gas outlet 3 is positioned at the middle of the built-in oil 102 in the longitudinal direction.

Both intake pipes 21 serve as the intake portions 2, so that the built-in oil 102 has two intake portions 2. As shown in fig. 3 and 4, in this embodiment, two inlet pipes 21 are respectively provided on the two closing plates 13 so that the two inlet portions 2 are located on both sides of the outlet portion 3. The lower ends of the two air inlet pipes 21 penetrate through the corresponding sealing plates 13 and extend into the cavity 91 to be communicated with the cavity 91, and the upper ends of the two air inlet pipes 21 penetrate through the corresponding sealing plates 13 and extend outside the cylinder 105 to be connected with an air outlet of a compressor (not shown in the figure) so as to communicate the air outlet of the compressor with the cavity 91, so that the air exhausted by the compressor flows into the internal oil 102 through the two air inlet pipes 21.

Under the action of the screen 31 and the two inlet pipes 21, the refrigerant can flow into the chamber 91 from two sides in the length direction, flow out of the chamber 91 from the middle part in the length direction, and exchange heat with the condensation pipe 103 of the condensation area 104.

The gas-uniforming plate 4, the heat exchange tubes 5, the baffle 6, the partition 71, the baffle 72 and the oil leakage plate 73 are disposed in the chamber 91.

Wherein, gas homogenizing plate 4 and oil leak plate 73 are arranged along the direction from top to bottom in proper order to with casing 1 cooperation, separate cavity 91 for oil storage district 92, disengagement zone 94 and filtering area 93, in order to realize respectively that fluid stores, oil-gas separation and refrigerant filtering capability.

Specifically, as shown in fig. 4, in this embodiment, the oil leakage plate 73 is disposed at the lower part of the chamber 91, and the peripheral edges are in contact with the two end plates 11 and the two side plates 12, so that the oil leakage plate 73 and the housing 1 enclose an oil storage area 92 below the oil leakage plate 73 to collect oil separated from gas. An oil leakage port 46 is formed in the edge of the oil leakage plate 73, and oil obtained through oil-gas separation falls into the oil storage area 92 through the oil leakage port 46. A flowline 8 is located in the storage area 92. The outlet line 8 extends from one side of the oil reservoir region 92 to facilitate the extraction of the collected oil.

The gas homogenizing plate 4 is disposed at an upper portion of the chamber 91 and is located right below the screen 31. The peripheral edge of the gas distribution plate 4 is in contact with the two connecting plates 14 and the two side plates 12. So, enclose between gas board 4 and two connecting plates 14, two curb plates 12 and the filter screen 31 and close and form filtering area 93, and enclose between gas board 4 and two end plates 11, two curb plates 12, two shrouding 13 and two connecting plates 14 and close and form separation region 94. The separation region 94 is located between the filtering region 93 and the oil storage region 92, and is used for realizing the oil-gas separation function of the built-in oil 102. The filtering region 93 is located at a side of the separation region 94 away from the oil storage region 92, and is used for implementing a refrigerant filtering function of the built-in oil component 102.

Fig. 7-9 further illustrate the structure of the gas distribution plate 4.

As shown in fig. 7 to 9, in this embodiment, the gas distribution plate 4 is substantially V-shaped and adopts a symmetrical layout in the longitudinal direction and the width direction. Specifically, oil leakage ports 46 are provided on both side edges in the width direction of the gas uniforming plate 4, so as to facilitate the dropping of oil. The gas distribution plate 4 is provided with two non-perforated regions 42 and a perforated region 41 located between the two non-perforated regions 42 in the longitudinal direction. Wherein, the two non-opening regions 42 are located at two ends of the gas homogenizing plate 4 in the length direction and correspond to the two sub-separation regions 95 one by one. The two non-perforated regions 42 are of equal length and are both L2, and are not perforated. The open area 41 is located in the middle of the gas homogenizing plate 4 in the length direction, and the length is L1. The perforated region 41 is perforated. Specifically, the perforated region 41 is provided with two hole units, which are symmetrically arranged in the length direction, and each hole unit includes a plurality of first air equalizing holes 44 having a larger diameter and a plurality of second air equalizing holes 45 having a smaller diameter. All the first uniform air holes 44 are uniformly arranged in the middle of the uniform air plate 4 near the width direction and symmetrically arranged about the V-shaped bending line of the uniform air plate 4, so that each hole unit includes two sets of first uniform air holes 44 symmetrically distributed in the width direction. Both sides of the width direction of the region where all the first uniform air holes 44 are located are provided with a plurality of uniformly distributed second uniform air holes 45, so that each hole unit comprises two groups of second uniform air holes 45 which are symmetrically distributed in the width direction. Wherein, the length ratio L1/L2 of the opening area 41 and the non-opening area 42 is about 1/10-1/2, the diameter of the first uniform air holes 44 is about 12 mm-20 mm, the diameter of the second uniform air holes 45 is about 6 mm-12 mm, and the width ratio H1/H2 of the area where the first uniform air holes 44 are located and the area where the second uniform air holes 45 are located is about 3-10. It will be appreciated that L1 is the total length across the two aperture units.

The heat exchange tubes 5, the baffle plates 6, the partition plates 71 and the baffle plates 72 are all arranged in the separation area 94 to realize the oil-gas separation and enhanced heat exchange functions of the built-in oil component 102.

Specifically, as shown in fig. 4, in this embodiment, the partition plate 71 is disposed at the middle of the separation region 94 in the longitudinal direction, and the top end is connected to the middle of the gas uniforming plate 4. The separation zone 94 is divided into two sub-separation zones 95 arranged side by side along the length direction by the partition 71. The two sub-separation areas 95 are in one-to-one communication with the two inlet pipes 21, so that the refrigerant can enter the two sub-separation areas 95 through the two inlet pipes 21. As can be seen from fig. 4 and 8, in this embodiment, the portion of the gas distribution plate 4 located between the two hole units is connected to the partition plate 71, and the width L3 of the portion of the gas distribution plate 4 for mounting the partition plate 71 is approximately 2mm to 20mm. In this case, L1 mentioned above is L3 included, and specifically, L1 is the sum of the length of the two hole units and L3.

The heat exchange tube 5 penetrates the two sub-separation zones 95 such that the heat exchange tube 5 penetrates the entire separation zone 94. Specifically, as shown in fig. 4, in this embodiment, a plurality of heat exchange tubes 5 are disposed side by side in the separation zone 94, and each penetrate through two sub-separation zones 95. Both ends of these heat exchange tubes 5 in the longitudinal direction (i.e., axial direction) protrude out from the two end plates 11 and are supported by the two tube sheets 106 of the condenser 100. And, while passing through the two sub-separation zones 95, the heat exchange tube 5 passes through the partition plate 71, the two baffles 72 and the baffle 6 such that a portion between both ends of the heat exchange tube 5 is supported by the partition plate 71, the baffles 72 and the baffle 6.

Both the two sub-separation zones 95 are provided with baffles 6 and 72. Specifically, as shown in fig. 4, in each sub-separation area 95, the baffle plate 72 is located between the end plate 11 and the connecting plate 14, and the top end of the baffle plate is connected to the closing plate 13, so that the refrigerant entering the sub-separation area 95 through the inlet pipe 21 can first pass through the baffling effect of the baffle plate 72. In addition, at least two baffle plates 6 are provided in each sub-separation region 95, the at least two baffle plates 6 are positioned right below the non-opening region 42 of the gas-equalizing plate 4 and are arranged at intervals along the length direction of the sub-separation region 95 (also the length direction of the shell 1, the built-in oil 102 and the condenser 100), and two adjacent baffle plates 6 are arranged in a vertically staggered manner, so that a deflection channel for guiding the refrigerant in the sub-separation region 95 to flow in a deflected manner is formed between the baffle plates 6 in the sub-separation region 95.

Fig. 5-6 further illustrate the construction of the baffle 6.

In this regard, fig. 5 shows the structure of the upper baffle plate 6 of any two adjacent baffle plates 6 in the sub-separation region 95. Fig. 6 shows the structure of the lower baffle plate 6 of any two adjacent baffle plates 6 in the sub-separation region 95.

For convenience of description, the upper baffle plate 6 of any two adjacent baffle plates 6 in the sub-separation region 95 is referred to as a first baffle plate 61, and the lower baffle plate 6 of any two adjacent baffle plates 6 in the sub-separation region 95 is referred to as a second baffle plate 62.

As can be seen from fig. 5 and 6, in this embodiment, the first baffle plate 61 and the second baffle plate 62 are substantially V-shaped, and the first baffle plate 61 and the second baffle plate 62 are provided with a plurality of through holes 63 and a plurality of vent holes 64. The plurality of through-holes 63 are divided into two groups, respectively located on the two plate bodies of the baffle plate 6 (the first baffle plate 61 or the second baffle plate 62) which are bent oppositely to form a V-shape, for the heat exchange tubes 5 to pass through, so that the built-in oil 102 includes two groups of heat exchange tubes 5 arranged at intervals in the width direction (i.e., the front-rear direction of fig. 3 and 4), the two groups of heat exchange tubes 5 being symmetrical to each other in the width direction. The heat exchange tubes 5 in each group of heat exchange tubes 5 are arranged in a triangular shape, that is, the heat exchange tubes 5 in each group of heat exchange tubes 5 are arranged in a triangular shape. A plurality of vent holes 64 are formed between the two sets of through holes 63 for the refrigerant to pass through. In this embodiment, the diameters of the vent holes 64 on the first baffle plate 61 and the second baffle plate 62 are the same, and are both 2mm to 8mm, and the total flow area of the vent holes 64 on the first baffle plate 61 and the second baffle plate 62 accounts for 1/8 to 3/4 of the total area of the corresponding baffle plate 6.

In this embodiment, the structural parameters of the heat exchange tube 5 and the inlet and outlet temperature of the internal oil component 102 satisfy the following relationship:

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wherein, T _in The temperature of the gaseous refrigerant at the inlet of the air inlet part 2 is expressed by K; t is _out The temperature of the gaseous refrigerant at the outlet of the air outlet part 3 is expressed by K; t is _wall Is the average temperature of the outer surface of the portion of the heat exchange tube 5 located inside the shell 1, and has the unit of K; rho is the gas density in kg/m ³ (ii) a D is the inner diameter of the air inlet part 2 and the unit is m; v is the flow velocity of the gaseous refrigerant at the inlet of the air inlet part 2, and the unit is m/s; l is the length of the heat exchange tube 5 in the built-in oil 102 in unitsIs m; n is the number of the heat exchange tubes 5 in the built-in oil component 102; d is the outer diameter of the heat exchange tube 5 and the unit is m; lambda is the heat conductivity coefficient under the average temperature of the refrigerant gas, and the unit is W/(m & ltK); cp is the specific heat capacity at the average temperature of the refrigerant gas, and the unit is kJ/(kg K); mu is the viscosity at the average temperature of the refrigerant gas, and the unit is Pa & s; u. of _w The viscosity of the refrigerant gas at the tube wall temperature of the portion of the heat exchange tube 5 located inside the shell 1 is expressed in Pa x s; epsilon is a constant and takes a value of 15-200; d _e The equivalent diameter of the heat exchange tubes 5, specifically in this embodiment, the equivalent diameter of each group of heat exchange tubes 5, is expressed in m; p _t The tube pitch of the heat exchange tubes 5 is given in m. The average temperature is denoted by T _in And T _out Average value of (a).

In the embodiment, the structural parameters of the baffle 6 and the heat exchange tube 5 and the inlet-outlet pressure drop Δ P of the built-in oil 102 satisfy the following relationship:

wherein, Δ P is the pressure drop of the inlet and outlet of the built-in oil 102, and the unit is Pa; c is a constant and takes a value of 0.3-1.5; rho is the density of the gaseous refrigerant and has the unit of kg/m ³ ；v ₀ The average flow speed of the gaseous refrigerant flowing through at least two baffle plates 6 is in m/s; d is the inner diameter of the air inlet part 2 and the unit is m; d _d Is the average hydraulic diameter of the baffle 6, in m; l _b The distance between two adjacent baffle plates 6 in the length direction of the heat exchange tube 5 is m; v is the flow velocity of the gaseous refrigerant at the inlet of the air inlet part 2, and the unit is m/s; n is the number of the heat exchange tubes 5 in the built-in oil component 102; d is the outer diameter of the heat exchange tube 5 in m.

Based on the built-in oil component 102 of this embodiment, when the condenser 100 works, the superheated gaseous refrigerant carrying the refrigeration oil enters the two sub-separation areas 95 from the two inlet pipes 21, and after being deflected by the baffle 72 in the sub-separation areas 95, the refrigerant enters the area where the baffle 6 is located, and finally passes through the gas-homogenizing plate 4, flows out of the upper screen 31, and enters the condensation area 104. In the process, through collision separation with the baffle 72, the baffle 6, the heat exchange tube 5, the gas-equalizing plate 4, the filter screen 31 and the oil leakage plate 73, oil drops in the refrigerant are accumulated and separated, fall from the oil leakage port 46 at the edge of each part and are gathered in the oil storage area 92, so that separation of the oil drops is realized. Meanwhile, the superheated gaseous refrigerant and the heat exchange tube 5 perform single-phase heat exchange, so that the temperature of the superheated gaseous refrigerant is reduced to a saturated state and then the superheated gaseous refrigerant enters the condensation area 104 for phase change heat exchange, and the desuperheating process is realized.

Because the refrigerant entering the condenser 100 passes through the two-stage heat exchange of the heat exchange tube 5 in the built-in oil component 102 and the condenser tube 103 in the condensing area 104, the heat exchange tube 5 can strengthen the single-phase heat exchange of the superheated refrigerant gas, so that the intensity of superheat removing heat exchange of the condenser 100 can be effectively improved, and the overall energy efficiency of the condenser 100 is improved.

Moreover, on the basis of the heat exchange tube 5, a baffle plate 6 is further arranged, so that the single-phase heat exchange strength can be further improved.

Meanwhile, the heat exchange tube 5 and the baffle plate 6 can increase the oil drop collision separation area and improve the oil-gas separation efficiency.

In addition, since the heat exchange tube 5 and the baffle 6 are both provided in the internal oil 102, an additional space is not required, which is advantageous for downsizing the condenser 100.

It can be seen that the condenser 100 and the built-in oil component 102 of the embodiment can realize effective improvement of single-phase heat exchange strength and oil-gas separation efficiency based on a simpler structure and a smaller volume, which is beneficial to improving the energy efficiency of the condenser 100.

Based on the built-in oil 102 and the condenser 100 of the present application, the present application also provides a refrigeration device, which comprises a compressor, and further comprises the condenser 100 of the embodiment of the present application, wherein the air inlet 2 of the condenser 100 is connected with the exhaust port of the compressor.

Since the energy efficiency of the internal oil 102 and the condenser 100 is improved, the energy efficiency of the refrigeration apparatus can be effectively improved.

The above description is only exemplary of the present application and should not be taken as limiting the present application, and any modifications, equivalents, improvements and the like that are made within the spirit and principle of the present application should be included in the protection scope of the present application.

Claims (17)

1. A built-in oil (102), comprising:

the air conditioner comprises a shell (1), wherein a separation area (94) is arranged in the shell (1), an air inlet part (2) and an air outlet part (3) are arranged on the shell (1), the air inlet part (2) is used for communicating the separation area (94) with an exhaust port of a compressor so that a gaseous refrigerant discharged from the compressor flows to the separation area (94), the air outlet part (3) is used for communicating the separation area (94) with a condensation area (104) of a condenser (100) so that the refrigerant flows from the separation area (94) to the condensation area (104) through the air outlet part (3) and exchanges heat with a condensation pipe (103) in the condensation area (104); and

at least two heat exchange tubes (5), wherein at least part of each heat exchange tube (5) is positioned in the separation region (94) to exchange heat with a refrigerant flowing from the air inlet part (2) to the air outlet part (3);

wherein, the outer diameter of the heat exchange tube (5) is d, and d satisfies the following relation:

wherein, T _in The temperature of the gaseous refrigerant at the inlet of the air inlet part (2); t is _out The temperature of the gaseous refrigerant at the outlet of the gas outlet part (3); t is _wall Is the average temperature of the outer surface of the part of the heat exchange tube (5) located inside the shell (1); ρ is the gas density; d is the inner diameter of the air inlet part (2); v is the flow speed of the gaseous refrigerant at the inlet of the air inlet part (2); 0 is the length of the heat exchange tube (5) in the built-in oil component (102)Degree; n is the number of the heat exchange tubes (5) in the built-in oil component (102); lambda is the heat conductivity coefficient of the refrigerant gas at the average temperature; cp is the specific heat capacity of the refrigerant gas at the average temperature; mu is the viscosity of the refrigerant gas at the average temperature; u. of _w The viscosity of the refrigerant gas at the tube wall temperature of the part of the heat exchange tube (5) positioned in the shell (1); epsilon is a constant and takes a value of 15-200; d _e The equivalent diameter of the heat exchange tube (5) is set; p is _t The tube pitch of the heat exchange tubes (5).

2. The internal oil content (102) of claim 1, wherein the internal oil content (102) comprises at least two baffles (6), and the at least two baffles (6) are disposed in the separation region (94) and deflect a refrigerant flowing through the heat exchange tubes (5).

3. The built-in oil component (102) according to claim 2, wherein the baffle plate (6) is provided with a vent hole (64) for the refrigerant to flow through.

4. The internal oil (102) according to claim 3, wherein the diameter of the vent (64) is 2mm to 8mm; and/or the total flow area of all the vent holes (64) on the baffle plate (6) accounts for 1/8-3/4 of the total area of the baffle plate (6).

5. A built-in oil (102) according to claim 2, wherein the baffle plate (6) is provided with a through-hole (63), and the heat exchange tube (5) passes through the baffle plate (6) via the through-hole (63).

6. The built-in oil (102) according to claim 2, wherein the at least two baffles (6) have an average hydraulic diameter D _d And the distance between two adjacent baffle plates (6) is l in the length direction of the heat exchange tube (5) _b ，D _d And l _b The following relationship is satisfied:

wherein, Δ P is the inlet-outlet pressure drop of the built-in oil component (102); c is a constant and takes a value of 0.3-1.5; rho is the density of the gaseous refrigerant; v. of ₀ The average flow speed of the gaseous refrigerant flowing through the at least two baffle plates (6) is obtained; d is the inner diameter of the air inlet part (2); v is the flow speed of the gaseous refrigerant at the inlet of the air inlet part (2); n is the number of heat exchange tubes (5) in the built-in oil component (102); d is the outer diameter of the heat exchange tube (5).

7. The built-in oil content (102) according to any one of claims 1-6, wherein the built-in oil content (102) comprises a gas homogenizing plate (4), the gas homogenizing plate (4) is arranged in the shell (1) and is positioned between the heat exchange tube (5) and the air outlet part (3), the gas homogenizing plate (4) is provided with an open area (41), the open area (41) is provided with a gas homogenizing hole (43), and a refrigerant after exchanging heat with the heat exchange tube (5) flows to the air outlet part (3) through the gas homogenizing hole (43).

8. The built-in oil (102) according to claim 7, wherein the gas homogenizing plate (4) has a non-opening area (42), the non-opening area (42) is not provided with the gas homogenizing hole (43) and corresponds to the area of the baffle plate (6) in the separation area (94), and the opening area (41) is positioned on the side of the non-opening area (42) far away from the air inlet part (2).

9. The built-in oil (102) according to claim 8, wherein the ratio of the length L1 of the open area (41) to the length L2 of the non-open area (42) is 1/10 to 1/2.

10. The built-in oil (102) according to claim 7, wherein the gas-homogenizing plate (4) is provided with a plurality of gas-homogenizing holes (43), the plurality of gas-homogenizing holes (43) comprise a first gas-homogenizing hole (44) and a second gas-homogenizing hole (45), and the diameter of the first gas-homogenizing hole (44) is larger than that of the second gas-homogenizing hole (45).

11. The built-in oil component (102) according to claim 10, wherein the diameter of the first air-equalizing hole (44) is 12mm to 20mm; and/or the diameter of the second air equalizing hole (45) is 6-12 mm.

12. The built-in oil (102) according to claim 10, wherein the second gas-homogenizing hole (45) is located closer to the edge of the gas-homogenizing plate (4) in the width direction than the first gas-homogenizing hole (44), and a ratio of a width of a region where the first gas-homogenizing hole (44) is located to a width of a region where the second gas-homogenizing hole (45) is located is 3 to 10.

13. The internal oil content (102) according to any one of claims 1 to 6, wherein the housing (1) is provided with two inlet portions (2), and the two inlet portions (2) are located on both sides of the outlet portion (3) and both communicate with the separation region (94).

14. The built-in oil content (102) according to claim 13, characterized in that the built-in oil content (102) comprises a partition plate (71), the partition plate (71) is arranged in the separation zone (94) and divides the separation zone (94) into two sub-separation zones (95), and the two sub-separation zones (95) are in one-to-one correspondence with the two inlet portions (2).

15. The built-in oil (102) according to claim 14, wherein baffles (6) are provided in both of the two sub-separation zones (95).

16. A condenser (100) comprising a housing (101) and a condenser tube (103), characterized by further comprising an internal oil content (102) according to any of claims 1-15, wherein the internal oil content (102) is arranged in the housing (101), wherein a region of the housing (101) where the internal oil content (102) is not arranged forms a condensation zone (104), and wherein at least part of the condenser tube (103) is located in the condensation zone (104).

17. A refrigeration appliance comprising a compressor, characterized in that it further comprises a condenser (100) according to claim 16, the intake (2) of said condenser (100) being connected to the discharge of said compressor.

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