Built-in oil separator, condenser and refrigeration unit

Abstract

The present application provides a built-in oil separator, which includes: a shell, a separation zone is provided in the shell, and an air inlet and an air outlet are provided on the shell, the air inlet connects the separation zone with the compressor exhaust port so that the gaseous refrigerant discharged from the compressor flows to the separation zone, the air outlet connects the separation zone with the condensation zone of the condenser so that the refrigerant flows from the separation zone to the condensation zone via the air outlet and exchanges heat with the condensation tube in the condensation zone; and at least two heat exchange tubes, at least a portion of each heat exchange tube is located in the separation zone to exchange heat with the refrigerant flowing from the air inlet to the air outlet, wherein the outer diameter d of the heat exchange tube satisfies: Based on this, the single-phase heat exchange intensity of the condenser can be improved.

Description

Technical Field

[0001] The present application relates to the technical field of refrigeration equipment, and in particular to a built-in oil separator, a condenser and a refrigeration device. Background Art

[0002] In refrigeration devices such as commercial water-cooled screw units, the heat exchange process of the superheated (the exhaust gas has a superheat of 4-10°C under nominal operating conditions) refrigerant gas discharged from the compressor exhaust port in the condenser is first de-superheating and then condensing. That is, the superheated refrigerant first realizes single-phase flow heat exchange to reach a saturated state, and then realizes condensation phase change heat transfer.

[0003] In the related art, the above-mentioned single-phase heat exchange and condensation phase change heat exchange processes are both realized by the condenser tubes of the condenser, and the heat exchange efficiency is poor. In particular, the condenser is usually designed based on the principle of enhanced condensation heat exchange, and the degree of enhancement of the single-phase flow heat transfer process of the gas is limited, resulting in low single-phase heat exchange intensity and a larger required heat exchange area, which affects energy efficiency.

[0004] Therefore, how to improve the single-phase heat exchange intensity of the superheated gas in the condenser is an important issue currently facing the improvement of condenser energy efficiency. Summary of the invention

[0005] A technical problem to be solved by the present application is to improve the single-phase heat exchange strength of the condenser.

[0006] In order to solve the above technical problems, the first aspect of the present application provides a built-in oil component, which includes:

[0007] A shell, a separation zone is provided in the shell, and an air inlet and an air outlet are provided on the shell, the air inlet connects the separation zone with the exhaust port of the compressor so that the gaseous refrigerant discharged from the compressor flows to the separation zone, and the air outlet connects the separation zone with the condensation zone of the condenser so that the refrigerant flows from the separation zone to the condensation zone via the air outlet to exchange heat with the condensation pipe in the condensation zone; and

[0008] at least two heat exchange tubes, at least a portion of each heat exchange tube being located in the separation zone to exchange heat with the refrigerant flowing from the air inlet to the air outlet;

[0009] Among them, the outer diameter of the heat exchange tube is d, and d satisfies the following relationship:

[0010]

[0011]

[0012] Among them, T in T is the temperature of the gaseous refrigerant at the inlet of the air inlet; out T is the temperature of the gaseous refrigerant at the outlet of the gas outlet; wallis the average temperature of the outer surface of the heat exchange tube located in the shell; ρ is the gas density; D is the inner diameter of the air inlet; v is the flow rate of the gaseous refrigerant at the inlet entrance; L is the length of the heat exchange tube in the built-in oil separator; n is the number of heat exchange tubes in the built-in oil separator; λ is the thermal conductivity of the refrigerant gas at the average temperature; Cp is the specific heat capacity of the refrigerant gas at the average temperature; μ is the viscosity of the refrigerant gas at the average temperature; u w is the viscosity of the refrigerant gas at the wall temperature of the heat exchange tube located inside the shell; ε is a constant with a value of 15 to 200; d e P is the equivalent diameter of the heat exchange tube; t is the tube spacing of the heat exchange tubes.

[0013] In some embodiments, the built-in oil separator includes at least two baffles, and the at least two baffles are arranged in the separation area to make the refrigerant flow in a baffled manner when flowing through the heat exchange tube.

[0014] In some embodiments, the baffle is provided with ventilation holes for the refrigerant to flow through.

[0015] In some embodiments, the diameter of the vent holes is 2 mm to 8 mm; and / or the total flow area of ​​all vent holes on the baffle accounts for 1 / 8 to 3 / 4 of the total area of ​​the baffle.

[0016] In some embodiments, the baffle is provided with tube holes, and the heat exchange tubes pass through the baffle via the tube holes.

[0017] In some embodiments, the average hydraulic diameter of at least two baffles is D d , and in the length direction of the heat exchange tube, the distance between two adjacent baffles is l b , D d and l b Satisfies the following relationship:

[0018]

[0019]

[0020] Wherein, ΔP is the pressure drop of the built-in oil separator inlet and outlet; C is a constant with a value of 0.3 to 1.5; ρ is the density of the gaseous refrigerant; v 0 is the average flow velocity of the gaseous refrigerant flowing through at least two baffles; D is the inner diameter of the air inlet; v is the flow velocity of the gaseous refrigerant at the entrance of the air inlet; n is the number of heat exchange tubes in the built-in oil separator; d is the outer diameter of the heat exchange tube.

[0021] In some embodiments, the built-in oil separator includes an air equalizing plate, which is arranged in the shell and located between the heat exchange tube and the air outlet. The air equalizing plate has an opening area, and the opening area is provided with air equalizing holes. The refrigerant after heat exchange with the heat exchange tube flows to the air outlet through the air equalizing holes.

[0022] In some embodiments, the air equalizing plate has a non-perforated area, in which no air equalizing holes are arranged, and corresponds to the area where the baffle plate in the separation area is located, and the perforated area is located on the side of the non-perforated area away from the air inlet portion.

[0023] In some embodiments, the ratio of the length L1 of the opening area to the length L2 of the non-opening area is 1 / 10 to 1 / 2.

[0024] In some embodiments, a plurality of air equalizing holes are provided on the air equalizing plate, and the plurality of air equalizing holes include a first air equalizing hole and a second air equalizing hole, and a diameter of the first air equalizing hole is greater than a diameter of the second air equalizing hole.

[0025] In some embodiments, the diameter of the first air-distributing pores is 12 mm to 20 mm; and / or the diameter of the second air-distributing pores is 6 mm to 12 mm.

[0026] In some embodiments, the second air uniformizing holes are closer to the edge of the air uniformizing plate in the width direction relative to the first air uniformizing holes, and the ratio of the width of the area where the first air uniformizing holes are located to the width of the area where the second air uniformizing holes are located is 3-10.

[0027] In some embodiments, two air inlets are provided on the shell, the two air inlets are located on both sides of the air outlet, and both are connected to the separation zone.

[0028] In some embodiments, the built-in oil separator includes a partition, which is disposed in the separation zone and divides the separation zone into two sub-separation zones, and the two sub-separation zones correspond one-to-one to the two air inlets.

[0029] In some embodiments, baffles are provided in both sub-separation zones.

[0030] A second aspect of the present application provides a condenser, which includes a shell and a condenser tube, and also includes a built-in oil separator according to an embodiment of the present application. The built-in oil separator is arranged in the shell, and an area in the shell where the built-in oil separator is not arranged forms a condensation zone, and at least a part of the condenser tube is located in the condensation zone.

[0031] The third aspect of the present application further provides a refrigeration device, which includes a compressor and also includes a condenser according to an embodiment of the present application, wherein an air inlet of the condenser is connected to an exhaust port of the compressor.

[0032] By arranging heat exchange tubes in the built-in oil separator, single-phase heat exchange is performed with the refrigerant before the refrigerant flows to the condenser tube, and a calculation formula for the size parameters of the heat exchange tube is provided, the single-phase heat exchange intensity of the condenser can be effectively improved.

[0033] Other features and advantages of the present application will become apparent from the following detailed description of exemplary embodiments of the present application with reference to the accompanying drawings. BRIEF DESCRIPTION OF THE DRAWINGS

[0034] In order to more clearly illustrate the embodiments of the present application or the technical solutions in the prior art, the drawings required for use in the embodiments or the description of the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present application. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative labor.

[0035] Figure 1 The overall structure of the condenser in the embodiment of the present application is shown.

[0036] Figure 2 It is a side view of the combined structure of the built-in oil separator and the cylinder in the embodiment of the present application.

[0037] Figure 3 A three-dimensional diagram showing the built-in oil component in an embodiment of the present application.

[0038] Figure 4 The internal structure of the built-in oil component in the embodiment of the present application is shown.

[0039] Figure 5 The structure of the first baffle in the embodiment of the present application is shown.

[0040] Figure 6 The structure of the second baffle in the embodiment of the present application is shown.

[0041] Figure 7 It is a side view of the air equalizing plate in the embodiment of the present application.

[0042] Figure 8 1 is a top view of the air equalizing plate in the embodiment of the present application.

[0043] Fig. 9 A schematic diagram showing the distribution of air equalizing holes on a single plate body of the air equalizing plate in an embodiment of the present application is shown.

[0044] Description of reference numerals:

[0045] 100, condenser; 101, shell; 102, built-in oil separator; 103, condenser tube; 104, condensation area; 105, cylinder; 106, tube sheet; 107, flange; 108, water chamber; 109, liquid collecting part;

[0046] 1. Shell; 11. End plate; 12. Side plate; 13. Closing plate; 14. Connecting plate; 15. Frame;

[0047] 2. Air intake; 21. Air intake pipe;

[0048] 3. Air outlet; 31. Filter;

[0049] 4. air equalizing plate; 41. opening area; 42. non-opening area; 43. air equalizing hole; 44. first air equalizing hole; 45. second air equalizing hole; 46. oil leakage port;

[0050] 5. Heat exchange tube;

[0051] 6. baffle; 61. first baffle; 62. second baffle; 63. tube hole; 64. vent hole;

[0052] 71. partition; 72. baffle; 73. oil leak plate;

[0053] 8. Oil outlet pipe;

[0054] 91. Chamber; 92. Oil storage area; 93. Filtration area; 94. Separation area; 95. Sub-separation area. DETAILED DESCRIPTION

[0055] The following will be combined with the drawings in the embodiments of the present application to clearly and completely describe the technical solutions in the embodiments of the present application. Obviously, the described embodiments are only part of the embodiments of the present application, rather than all of the embodiments. The following description of at least one exemplary embodiment is actually only illustrative and is by no means intended to limit the present application and its application or use. Based on the embodiments in the present application, all other embodiments obtained by ordinary technicians in this field without carrying out creative work are within the scope of protection of this application.

[0056] Technologies, methods, and equipment known to ordinary technicians in the relevant art may not be discussed in detail, but where appropriate, the technologies, methods, and equipment should be considered as part of the specification.

[0057] In the description of the present application, it should be understood that the directions or positional relationships indicated by directional words such as "front, back, up, down, left, right", "lateral, vertical, perpendicular, horizontal" and "top, bottom" are usually based on the directions or positional relationships shown in the drawings, and are only for the convenience of describing the present application and simplifying the description. Unless otherwise specified, these directional words do not indicate or imply that the device or element referred to must have a specific direction or be constructed and operated in a specific direction, and therefore cannot be understood as limiting the scope of protection of the present application; the directional words "inside and outside" refer to the inside and outside relative to the contours of each component itself.

[0058] In the description of the present application, it should be understood that the use of terms such as "first" and "second" to limit components is only for the convenience of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore cannot be understood as limiting the scope of protection of the present application.

[0059] In addition, the technical features involved in the different embodiments of the present application described below can be combined with each other as long as they do not conflict with each other.

[0060] For refrigeration devices such as commercial water-cooled screw units, the refrigerant entering the condenser is usually superheated gas, which needs to undergo single-phase flow heat exchange in the condenser to remove superheat, and then undergo condensation phase change heat exchange.

[0061] In the related art, the single-phase heat exchange of superheated refrigerant gas and the condensation phase change heat transfer process are both realized by the condenser tube of the condenser. However, the condenser in the related art has a limited degree of enhancement of the single-phase flow heat transfer process, resulting in low single-phase heat transfer intensity and a larger required heat exchange area. For example, in some condensers, the single-phase heat transfer coefficient is much lower than the phase change heat transfer coefficient (a difference of 10 to 20 times), and the single-phase heat exchange load only accounts for 4% to 8% of the overall load of the heat exchanger, but it needs to occupy 25%-40% of the tube bundle heat exchange area, affecting the overall energy efficiency of the condenser.

[0062] Therefore, how to improve the single-phase heat exchange intensity of the superheated gas in the condenser is an important issue currently facing the improvement of condenser energy efficiency.

[0063] In view of the above situation, in order to improve the single-phase heat exchange intensity of the condenser to the superheated gas, and thus improve the energy efficiency of the condenser, the present application improves the structure of the condenser, and mainly improves the structure of the oil-gas separator of the condenser.

[0064] The oil-gas separator is used to separate oil droplets from the gaseous refrigerant in the refrigeration device. The principles include impact inertial separation, screening and adsorption, etc. It aims to prevent oil droplets in the compressor exhaust from entering the condenser and then the evaporator, affecting the overall energy efficiency of the unit.

[0065] There are two main ways to set up the oil-gas separator: internal and external. Compared with the external oil-gas separator, the internal oil-gas separator (i.e., internal oil separator) is set inside the shell of the condenser, without occupying the external space of the condenser separately, and has fewer connecting pipes, which is conducive to achieving better oil-gas separation effect.

[0066] This application mainly improves the structure of the built-in oil separator to improve the single-phase heat exchange intensity of the condenser to the superheated gas, thereby improving the energy efficiency of the condenser.

[0067] Figure 1-Figure 9 The structure of the condenser and its built-in oil of the present application is shown as an example. Figure 1 The shell is made perspective to clearly show the structure inside the shell.

[0068] See also Figure 1-Figure 9In the present application, the built-in oil separator 102 is an oil-gas separator arranged inside the shell 101 of the condenser 100, which includes a shell 1 and a heat exchange tube 5. A separation zone 94 is provided inside the shell 1, and an air inlet 2 and an air outlet 3 are provided on the shell 1. The air inlet 2 connects the separation zone 94 with the compressor exhaust port (not shown in the figure) so that the gaseous refrigerant discharged from the compressor flows to the separation zone 94. The air outlet 3 connects the separation zone 94 with the condensation zone 104 of the condenser 100 so that the refrigerant flows from the separation zone 94 to the condensation zone 104 via the air outlet 3 and exchanges heat with the condensation tube 103 in the condensation zone 104. At least part of the heat exchange tube 5 is located in the separation zone 94 to exchange heat with the refrigerant flowing from the air inlet 2 to the air outlet 3.

[0069] In the related art, the heat exchange tube 5 is not arranged in the built-in oil separator 102 of the condenser 100. When the refrigerant flows through the built-in oil separator 102 for oil-gas separation, no heat exchange is performed. Instead, after the refrigerant flows out from the built-in oil separator 102 to the condensation area 104, single-phase heat exchange and condensation phase change heat exchange are performed at the condensation tube 103 in the condensation area 104. That is to say, in the related art, single-phase heat exchange and condensation phase change heat exchange are both realized by the condensation tube 103. In this case, the single-phase heat exchange intensity is low, which affects the energy efficiency of the condenser 100.

[0070] The present application adds a heat exchange tube 5 in the built-in oil separator 102, and uses the heat exchange tube 5 to perform single-phase heat exchange with the refrigerant before the refrigerant flows through the condenser tube 103, thereby effectively improving the single-phase heat exchange intensity of the condenser 100, enhancing the de-overheating heat exchange intensity of the condenser 100, and improving the energy efficiency of the condenser 100.

[0071] At the same time, adding a heat exchange tube 5 in the built-in oil separator 102 to improve the single-phase heat exchange intensity does not affect the realization of the conventional oil-gas separation function of the built-in oil separator 102. On the contrary, since the added heat exchange tube 5 can increase the area of ​​the built-in oil separator 102 used for collision and separation with the refrigerant, it will not only not affect the realization of the normal oil-gas separation function of the built-in oil separator 102, but will improve the oil-gas separation efficiency of the built-in oil separator 102 and improve the oil-gas separation effect of the built-in oil separator 102.

[0072] Furthermore, since the added heat exchange tubes 5 are located inside the shell 1 with the built-in oil separator 102 and do not require additional space, it is also beneficial to miniaturize the condenser 100 and can prevent the reduction of the pipe layout space inside the condenser 100 due to solving the problem of enhanced heat exchange of superheated gas, thereby affecting the energy efficiency of the condenser 100.

[0073] It can be seen that the present application creatively integrates the built-in oil separator 102 and the heat exchange tube 5 into one, so that the refrigerant can undergo two-stage heat exchange, namely, the heat exchange tube 5 and the condenser tube 103, when flowing through the condenser 100. This not only realizes and improves the oil-gas separation function of the built-in oil separator 102, but also realizes the improvement of the single-phase heat exchange intensity of the condenser 100 and the miniaturization of the condenser 100, thereby effectively improving the overall energy efficiency of the condenser 100.

[0074] In the present application, the built-in oil separator 102 may include at least two heat exchange tubes 5, and the outer diameter of the heat exchange tube 5 is d, and d satisfies the following relationship:

[0075]

[0076]

[0077] Among them, T in is the temperature of the gaseous refrigerant at the inlet of the air inlet 2; T out is the temperature of the gaseous refrigerant at the outlet of the gas outlet 3; T wall is the average temperature of the outer surface of the portion of the heat exchange tube 5 located in the shell 1; ρ is the gas density; D is the inner diameter of the air inlet 2; v is the flow rate of the gaseous refrigerant at the inlet of the air inlet 2; L is the length of the heat exchange tube 5 in the built-in oil separator 102; n is the number of heat exchange tubes 5 in the built-in oil separator 102; λ is the thermal conductivity of the refrigerant gas at the average temperature; Cp is the specific heat capacity of the refrigerant gas at the average temperature; μ is the viscosity of the refrigerant gas at the average temperature; u w is 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; ε is a constant, ranging from 15 to 200; d e P is the equivalent diameter of the heat exchange tube 5; t is the tube spacing of the heat exchange tube 5.

[0078] Based on the above formula, it is convenient to design the heat exchange tube 5, and it is convenient to design a built-in oil separator 102 that can effectively remove overheating. Specifically, by reasonably designing D, d, L, d e and P t The values ​​of the same size parameters can achieve a better desuperheating effect for the built-in oil separator 102. In the case where the built-in oil separator 102 is provided with a baffle 6 as described below, the specific value of ε can be determined according to the design of the baffle 6. When the inlet and outlet temperature difference remains unchanged, ε is proportional to the desuperheating heat transfer coefficient of the built-in oil separator 102, and the desuperheating heat transfer coefficient increases with the increase of ε.

[0079] It can be seen that by arranging the heat exchange tube 5 in the built-in oil separator 102, and making the inner diameter D of the air intake portion 2 of the built-in oil separator 102, the outer diameter d of the heat exchange tube 5, the length L of the heat exchange tube 5 in the built-in oil separator 102, and the equivalent pipe diameter d of the heat exchange tube 5 e and the tube spacing P of the heat exchange tube 5 t If the above formula is satisfied, the single-phase heat exchange intensity of the condenser 100 can be effectively improved, and the energy efficiency of the condenser 100 can be improved.

[0080] In order to further improve the energy efficiency of the condenser 100, see Figure 4 In some embodiments, the built-in oil separator 102 includes not only the shell 1 and the heat exchange tube 5, but also at least two baffles 6. The at least two baffles 6 are arranged in the separation area 94, and the refrigerant flows through the heat exchange tube 5 to perform baffle flow. The baffles 6 in the built-in oil separator 102 are arranged side by side in the length direction of the heat exchange tube 5, and the baffles 6 are connected to the adjacent baffles 6 in the direction intersecting with the length direction of the heat exchange tube 5 (for example, the height direction or width direction of the built-in oil separator 102, that is, Figure 4 The heat exchange tubes 5 are staggered in an up-down direction or a front-to-back direction to make the refrigerant flow back and forth when flowing through the heat exchange tubes 5, forming a wave-like baffle flow.

[0081] Due to the baffle 6 that is set, the flow area in the separation zone 94 can be reduced, the gas flow rate across the tube bundle can be increased (under the premise that the total flow rate remains unchanged, the flow area is reduced and the flow rate is increased), and the angle between the gas flow direction and the heat exchange tube 5 can be reduced, so that the gas flow direction originally parallel to the heat exchange tube 5 becomes inclined relative to the heat exchange tube 5. Therefore, the heat exchange sufficiency between the refrigerant gas and the heat exchange tube 5 can be improved, and the heat exchange intensity of the superheated refrigerant gas at the heat exchange tube 5 can be effectively improved, so as to further enhance the single-phase heat exchange intensity, thereby further improving the energy efficiency of the condenser 100.

[0082] At the same time, the baffle plate 6 provided can also increase the collision and separation area of ​​the oil droplets, thereby improving the oil-gas separation efficiency and enhancing the energy efficiency of the condenser 100 .

[0083] It can be seen that by further arranging the baffle plate 6 in the separation zone 94 , the single-phase heat exchange intensity and the oil-gas separation efficiency can be further improved, thereby achieving a further improvement in the energy efficiency of the condenser 100 .

[0084] Figure 5 and Figure 6 The structure of the baffle 6 is further shown.

[0085] See also Figure 5-Figure 6 , and combined with Figure 4In some embodiments, the baffle plate 6 is provided with a tube-through hole 63, and the heat exchange tube 5 passes through the baffle plate 6 via the tube-through hole 63. At this time, the heat exchange tube 5 can support the baffle plate 6, effectively improving the structural stability. Moreover, since the baffle plate 6 is integrated on the heat exchange tube 5, it is easier for the baffle plate 6 to cooperate with the heat exchange tube 5, effectively improving the single-phase heat exchange strength and oil-gas separation efficiency.

[0086] Also, see Figure 5 and Figure 6 In some embodiments, the baffle plate 6 is provided with air holes 64 for the refrigerant to flow through.

[0087] Although the vent holes 64 may not be provided on the baffle plate 6, providing the vent holes 64 may allow part of the refrigerant gas to pass through the baffle plate 6 via the vent holes 64. Therefore, the baffle pressure drop of the refrigerant gas can be reduced to a certain extent, effectively preventing excessive pressure drop of the gaseous refrigerant flowing out after baffle.

[0088] In the case where the baffle plate 6 is provided with vent holes 64, the size and number of the vent holes 64 can be designed to control the total flow area of ​​the vent holes 64, thereby achieving a better baffle effect and a better pressure drop prevention effect at the same time. For example, in some embodiments, the diameter of the vent holes 64 is 2 mm to 8 mm; and / or the total flow area of ​​all vent holes 64 on the baffle plate 6 accounts for 1 / 8 to 3 / 4 of the total area of ​​the baffle plate 6. In this way, the pressure drop can be effectively reduced and a better baffle effect can be achieved, and the baffle effect of the baffle plate 6 will not be affected by the vent holes 64 being too large and / or too many.

[0089] In some embodiments, the average hydraulic diameter of all baffles 6 is D d , and in the length direction of the heat exchange tube 5, the distance between two adjacent baffles 6 is l b , D d and l b Satisfies the following relationship:

[0090]

[0091]

[0092] Wherein, ΔP is the inlet and outlet pressure drop of the built-in oil separator 102; C is a constant, with a value of 0.3 to 1.5; ρ is the density of the gaseous refrigerant; v 0 is the average flow velocity of the gaseous refrigerant flowing through at least two baffles 6; D is the inner diameter of the air inlet 2; v is the flow velocity of the gaseous refrigerant at the entrance of the air inlet 2; n is the number of heat exchange tubes 5 in the built-in oil separator 102; and d is the outer diameter of the heat exchange tube 5.

[0093] Based on the above formula, it is convenient to design the heat exchange tube 5 and the baffle 6, so as to design a built-in oil separator 102 that can more effectively remove overheating.

[0094] The pressure drop △P is proportional to C and increases with the increase of C. By controlling the value of C and influencing the average flow velocity v of the gaseous refrigerant flowing through all baffles 6 0 The size of can be used to comprehensively control the pressure drop and heat exchange performance of the built-in oil separator 102. Specifically, by reasonably designing the values ​​of the size parameters such as D, and d, the pressure drop of the built-in oil separator 102 can be minimized when the heat exchange performance is optimal.

[0095] Back to Figure 4 In some embodiments, the built-in oil separator 102 includes not only a shell 1 and a heat exchange tube 5, but also an air equalizing plate 4. The air equalizing plate 4 is arranged in the shell 1 and is located between the heat exchange tube 5 and the air outlet 3. The air equalizing plate 4 has an opening area 41, and the opening area 41 is provided with air equalizing holes 43. The refrigerant after heat exchange with the heat exchange tube 5 flows to the air outlet 3 through the air equalizing holes 43.

[0096] Due to the arrangement of the air equalizing plate 4, the flow field can be uniformed, so that the refrigerant gas flowing from the heat exchange tube 5 to the air outlet 3 is more evenly distributed, and the collision with the oil droplets in the refrigerant can be increased, thereby enhancing the impact separation ability of the built-in oil separator 102. Therefore, the oil-gas separation efficiency of the built-in oil separator 102 can be effectively improved.

[0097] Furthermore, if Figure 4 and Figure 7-Figure 8 As shown, in some embodiments, the air equalizing plate 4 not only has an opening area 41, but also has a non-opening area 42. The non-opening area 42 is not provided with air equalizing holes 43, and corresponds to the area where the baffle plate 6 in the separation area 94 is located. The opening area 41 is located on the side of the non-opening area 42 away from the air inlet part 2.

[0098] Based on the above settings, the gas equalizing plate 4 does not have holes in the area corresponding to the baffle plate 6, but only has holes in the part behind the baffle plate 6, which can give full play to the baffle effect of the baffle plate 6 and effectively improve the single-phase heat exchange intensity and oil and gas separation efficiency.

[0099] Specifically, see Figure 8 In some embodiments, the ratio of the length L1 of the perforated area 41 to the length L2 of the non-perforated area 42 is 1 / 10 to 1 / 2. At this time, the ratio of the perforated area 41 to the non-perforated area 42 is relatively suitable, which can provide sufficient baffle length to enhance heat exchange and separate oil droplets while achieving a good gas equalization effect, and make the pressure drop of the refrigerant after passing through the gas equalization plate 4 relatively suitable and not too large.

[0100] Also, see Fig. 9In some embodiments, the gas equalizing plate 4 is provided with a plurality of gas equalizing holes 43, and the plurality of gas equalizing holes 43 include a first gas equalizing hole 44 and a second gas equalizing hole 45, and the diameter of the first gas equalizing hole 44 is greater than the diameter of the second gas equalizing hole 45. At this time, the gas equalizing holes 43 with different diameters are provided on the gas equalizing plate 4, which is convenient for separating oil droplets of different particle sizes and is conducive to controlling the pressure drop within a reasonable range.

[0101] Specifically, in some embodiments, the diameter of the first air pore 44 is 12 mm to 20 mm; and / or the diameter of the second air pore 45 is 6 mm to 12 mm. In this case, the diameters of the first air pore 44 and the second air pore 45 are more suitable, convenient for processing, and can effectively control the pressure drop within a reasonable range while meeting the requirements for separation of oil droplets of different particle sizes.

[0102] Also, see Fig. 9 In some embodiments, the second air pore 45 is closer to the edge of the air pore 44 in the width direction of the air pore 44, and the width of the area where the first air pore 44 is located (see Fig. 9 , is 2H1) and the width of the area where the second air balancing hole 45 is located (see Fig. 9 , 2H2) ratio is 3 to 10. At this time, the distribution range of the first gas balancing pores 44 and the second gas balancing pores 45 is relatively reasonable, which can effectively control the pressure drop within a reasonable range while meeting the requirements for separation of oil droplets of different particle sizes.

[0103] Back to Figure 4 In some embodiments, two air inlets 2 are provided on the housing 1, and the two air inlets 2 are located on both sides of the air outlet 3 and are both connected to the separation zone 94. In this way, the refrigerant can enter the built-in oil separator 102 from the air inlets 2 on both sides, and flow out from the air outlet 3 in the middle to the outside of the built-in oil separator 102, and in the process of flowing from both sides to the middle, it flows through the heat exchange tubes 5 in the separation zone 94, performs single-phase heat exchange, and removes overheating. At this time, the heat exchange efficiency and oil-gas separation efficiency are both high.

[0104] In the case where two air inlets 2 are provided on the housing 1, see Figure 4 In some embodiments, the built-in oil separator 102 includes a partition 71, which is disposed in the separation zone 94 and divides the separation zone 94 into two sub-separation zones 95, and the two sub-separation zones 95 correspond to the two air inlets 2. In this way, the refrigerants in the two sub-separation zones 95 do not interfere with each other, and a more efficient single-phase heat exchange and oil-gas separation process can be achieved.

[0105] Also, see Figure 4 In some embodiments, baffles 6 are provided in both sub-separation zones 95. In this way, baffles can be provided in both sub-separation zones 95, and the single-phase heat exchange intensity and oil-gas separation efficiency are higher.

[0106] Next, Figure 1-Figure 9 The illustrated embodiment is further described.

[0107] like Figure 1-9 As shown, in this embodiment, the condenser 100 is a horizontal condenser, which includes a housing 101 and a condensing tube 103, and also includes a built-in oil separator 102. The built-in oil separator 102 is arranged in the housing 101. The area in the housing 101 where the built-in oil separator 102 is not arranged forms a condensation area 104. At least part of the condensing tube 103 is located in the condensation area 104.

[0108] Specifically, the shell 101 includes a cylinder 105, a tube sheet 106, a flange 107 and a water chamber 108. The cylinder 105 is roughly in the shape of a hollow cylinder, and the axis is roughly horizontal and along the left-right direction. A liquid collecting portion 109 is provided at the lower part of the side wall of the cylinder 105, and the liquid collecting portion 109 is connected to the condensation area 104 to collect the condensed liquid. Tube sheets 106, flanges 107 and water chambers 108 are provided at both axial ends of the cylinder 105 to seal the axial ends of the cylinder 105, so that a closed space is formed inside the shell 101. Among them, the tube sheet 106 is connected to the axial end of the cylinder 105 through the flange 107, and is used to support the condenser 103 and the heat exchange tube 5 with the built-in oil separator 102. The water chamber 108 is connected to the side of the tube sheet 106 away from the flange 107.

[0109] The built-in oil separator 102 and the condenser 103 are both arranged in the housing 101. The built-in oil separator 102 is arranged on the upper side of the housing 101. The area in the housing 101 where the built-in oil separator 102 is not arranged forms a condensation area 104. The condenser 103 is arranged in the condensation area 104 and is located in the lower middle side of the housing 101 to exchange heat with the refrigerant flowing out of the built-in oil separator 102 to achieve condensation of the refrigerant. Specifically, Figure 1 As shown, in this embodiment, a plurality of condensing tubes 103 are provided in the condensing zone 104. These condensing tubes 103 all penetrate the condensing zone 104 along the axial direction of the cylinder 105 (which is also the length direction of the built-in oil separator 102), and both ends are supported by the tube sheets 106 on both sides of the cylinder 105.

[0110] Next, the structure of the built-in oil separator 102 will be described in detail.

[0111] like Figure 3-Figure 9 As shown, in this embodiment, the built-in oil component 102 is roughly symmetrical in the length direction and the width direction, and the overall cross-section is V-shaped.

[0112] Specifically, Figure 3 and Figure 4As shown, the built-in oil separator 102 of this embodiment includes a shell 1, a filter 31, two air inlet pipes 21, an air equalizing plate 4, a heat exchange tube 5, a baffle 6, a partition 71, a baffle 72 and an oil leakage plate 73.

[0113] The housing 1 is used to provide a mounting base for other structural components of the built-in oil separator 102, and to protect the structural components disposed therein. Figure 3 and Figure 4 It can be seen that in this embodiment, the housing 1 includes two end plates 11, two side plates 12, two sealing plates 13, two connecting plates 14 and a frame 15. The two end plates 11 are arranged in a longitudinal direction (i.e. Figure 3 and Figure 4 The two side panels 12 are arranged opposite to each other in the left and right directions and are roughly fan-shaped. The two side panels 12 are roughly V-shaped, and the two are Figure 3 and Figure 4 The two sealing plates 13 are arranged opposite to each other in the front-to-back direction) and are connected to the front and rear edges of the two end plates 11. The two sealing plates 13 are both polygonal (for example, having 5 folded edges), and are arranged between the two end plates 11 and spaced apart in the length direction, and are respectively connected to the two side plates 12 and the end plates 11 on the corresponding sides. The two connecting plates 14 are respectively connected to the sides of the two sealing plates 13 away from the end plates 11. The frame 15 is arranged between the two connecting plates 14 and is connected to the two connecting plates 14 and the two side plates 12. In this way, the two end plates 11, the two side plates 12, the two sealing plates 13, the two connecting plates 14 and the frame 15 enclose a shell 1 that is V-shaped as a whole and has a chamber 91 inside, wherein the two end plates 11 and the two side plates 12 together form the surrounding and bottom contours of the shell 1, and the two sealing plates 13, the two connecting plates 14 and the frame 15 together form the upper contour of the shell 1.

[0114] The frame 15 is used to support the filter 31. The filter 31 is arranged on the frame 15 and is located below the frame 15, forming the air outlet 3 of the built-in oil separator 102, which is used to connect the chamber 91 with the condensation area 104 of the condenser 100. The refrigerant flowing out of the built-in oil separator 102 flows through the filter 31 and the frame 15, enters the condensation area 104 of the condenser 100, and exchanges heat with the condensation tube 103 in the condensation area 104. When the refrigerant flows through the filter 31, it can be filtered by the filter 31 to further separate the oil and gas. The middle part of the frame 15 is hollowed out, so it will not form a barrier to the refrigerant flowing out of the filter 31.

[0115] Since the frame 15 is located in the middle of the length direction of the built-in oil separator 102 , the filter 31 arranged on the frame 15 is also located in the middle of the length direction of the built-in oil separator 102 , so that the air outlet 3 is located in the middle of the length direction of the built-in oil separator 102 .

[0116] The two air intake pipes 21 are both used as the air intake section 2, so that the built-in oil separator 102 has two air intake sections 2. Figure 3 and Figure 4 As shown, in this embodiment, two air inlet pipes 21 are respectively arranged on two sealing plates 13, so that the two air inlet parts 2 are located on both sides of the air outlet part 3. In addition, the lower ends of the two air inlet pipes 21 pass through the corresponding sealing plates 13 and extend into the chamber 91, and communicate with the chamber 91. At the same time, the upper ends of the two air inlet pipes 21 pass through the corresponding sealing plates 13 and extend to the outside of the cylinder 105, and are used to connect with the exhaust port of the compressor (not shown in the figure) to communicate the exhaust port of the compressor with the chamber 91, so that the exhaust of the compressor flows into the built-in oil separator 102 through the two air inlet pipes 21.

[0117] Under the action of the filter 31 and the two air inlet pipes 21 , the refrigerant can flow into the chamber 91 from both sides in the length direction, and flow out to the outside of the chamber 91 from the middle in the length direction to exchange heat with the condensation tube 103 in the condensation area 104 .

[0118] The gas balancing plate 4 , the heat exchange tube 5 , the baffle plate 6 , the partition plate 71 , the baffle plate 72 and the oil leakage plate 73 are all arranged in the chamber 91 .

[0119] Among them, the air equalizing plate 4 and the oil leakage plate 73 are arranged in sequence from top to bottom, and cooperate with the shell 1 to divide the chamber 91 into an oil storage area 92, a separation area 94 and a filtration area 93, so as to realize the functions of oil storage, oil and gas separation and refrigerant filtration respectively.

[0120] Specifically, Figure 4 As shown, in this embodiment, the oil leakage plate 73 is arranged at the lower part of the chamber 91, and the edges around it are in contact with the two end plates 11 and the two side plates 12, so that the oil leakage plate 73 and the shell 1 together enclose an oil storage area 92 located below the oil leakage plate 73 to collect the oil obtained by oil and gas separation. The edge of the oil leakage plate 73 is provided with an oil leakage port 46, and the oil obtained by oil and gas separation falls into the oil storage area 92 through the oil leakage port 46. The oil storage area 92 is provided with an oil outlet pipe 8. The oil outlet pipe 8 extends from one side of the oil storage area 92 to facilitate the extraction of the collected oil.

[0121] The air equalizing plate 4 is arranged at the upper part of the chamber 91 and is located directly below the filter 31. The edges of the air equalizing plate 4 are in contact with the two connecting plates 14 and the two side plates 12. In this way, the air equalizing plate 4 and the two connecting plates 14, the two side plates 12 and the filter 31 enclose a filtration area 93, and the air equalizing plate 4 and the two end plates 11, the two side plates 12, the two sealing plates 13 and the two connecting plates 14 enclose a separation area 94. The separation area 94 is located between the filtration area 93 and the oil storage area 92, and is used to realize the oil and gas separation function of the built-in oil separator 102. The filtration area 93 is located on the side of the separation area 94 away from the oil storage area 92, and is used to realize the refrigerant filtration function of the built-in oil separator 102.

[0122] Figure 7-Figure 9 The structure of the air homogenizing plate 4 is further shown.

[0123] like Figure 7-Figure 9 As shown, in this embodiment, the air equalizing plate 4 is roughly V-shaped and adopts a symmetrical layout in the length direction and the width direction. Specifically, oil leaks 46 are provided on the edges on both sides of the width direction of the air equalizing plate 4 to facilitate the dripping of oil. In addition, the air equalizing plate 4 is provided with two non-perforated areas 42 in the length direction and a perforated area 41 located between the two non-perforated areas 42. Among them, the two non-perforated areas 42 are located at both ends of the length direction of the air equalizing plate 4, and correspond one-to-one to the two sub-separation areas 95. The two non-perforated areas 42 are of equal length, both L2, and neither of them has a hole. The perforated area 41 is located in the middle of the length direction of the air equalizing plate 4, with a length of L1. There are holes in the perforated area 41. Specifically, two hole units are provided in the perforated area 41, and the two hole units are symmetrically arranged in the length direction, and each hole unit includes a plurality of first air equalizing holes 44 with larger diameters and a plurality of second air equalizing holes 45 with smaller diameters. All first air equalizing holes 44 are evenly arranged in the middle of the air equalizing plate 4 near the width direction, and are symmetrically arranged about the V-shaped bending line of the air equalizing plate 4, so that each hole unit includes two groups of first air equalizing holes 44 symmetrically distributed in the width direction. A plurality of evenly distributed second air equalizing holes 45 are provided on both sides of the width direction of the area where all the first air equalizing holes 44 are located, so that each hole unit includes two groups of second air equalizing holes 45 symmetrically distributed in the width direction. Among them, the length ratio L1 / L2 of the perforated area 41 and the non-perforated area 42 is approximately 1 / 10 to 1 / 2, the diameter of the first air equalizing hole 44 is approximately 12mm to 20mm, the diameter of the second air equalizing hole 45 is approximately 6mm to 12mm, and the width ratio H1 / H2 of the area where the first air equalizing hole 44 is located and the area where the second air equalizing hole 45 is located is approximately 3 to 10. It can be understood that L1 is the total length across the two hole units.

[0124] The heat exchange tube 5 , the baffle plate 6 , the partition plate 71 and the baffle plate 72 are all arranged in the separation area 94 to achieve the oil-gas separation and the enhanced heat exchange function of the built-in oil separator 102 .

[0125] Specifically, Figure 4 As shown, in this embodiment, the partition 71 is arranged in the middle of the length direction of the separation zone 94, and the top end is connected to the middle of the air equalization plate 4. Under the action of the partition 71, the separation zone 94 is divided into two sub-separation zones 95 arranged side by side along the length direction. The two sub-separation zones 95 are connected to the two air inlet pipes 21 one by one, so that the refrigerant can enter the two sub-separation zones 95 respectively through the two air inlet pipes 21. Figure 4 and Figure 8It can be seen that in this embodiment, the portion of the air-distributing plate 4 between the two hole units is connected to the partition 71, and the width L3 of the portion of the air-distributing plate 4 for mounting the partition 71 is approximately 2 mm to 20 mm. In this case, the aforementioned L1 includes L3, specifically, L1 is the sum of the lengths of the two hole units and L3.

[0126] The heat exchange tube 5 passes through the two sub-separation zones 95, so that the heat exchange tube 5 passes through the entire separation zone 94. Specifically, Figure 4 As shown, in this embodiment, a plurality of heat exchange tubes 5 are arranged side by side in the separation zone 94, and all pass through the two sub-separation zones 95. The two ends of the heat exchange tubes 5 in the length direction (i.e., axial direction) pass through the two end plates 11 and are supported by the two tube plates 106 of the condenser 100. Moreover, when passing through the two sub-separation zones 95, the heat exchange tubes 5 pass through the partition 71, the two baffles 72, and the baffle 6, so that the portion between the two ends of the heat exchange tubes 5 is supported by the partition 71, the baffle 72, and the baffle 6.

[0127] The two sub-separation zones 95 are both provided with baffles 6 and baffles 72. Figure 4 As shown, in each sub-separation area 95, the baffle 72 is located between the end plate 11 and the connecting plate 14, and the top end is connected to the sealing plate 13, so that the refrigerant entering the sub-separation area 95 through the air inlet pipe 21 can first pass through the baffle 72. In addition, in each sub-separation area 95, at least two baffles 6 are provided, and the at least two baffles 6 are located directly below the non-perforated area 42 of the gas equalizing plate 4, and are arranged at intervals along the length direction of the sub-separation area 95 (which is also the length direction of the shell 1, the built-in oil separator 102 and the condenser 100), and the adjacent two baffles 6 are arranged in an upper and lower staggered manner, so that between the baffles 6 in the sub-separation area 95, a baffle channel is formed to guide the refrigerant in the sub-separation area 95 to baffle flow.

[0128] Figure 5-Figure 6 The structure of the baffle 6 is further shown.

[0129] in, Figure 5 The structure of the baffle plate 6 which is the upper one of any two adjacent baffle plates 6 in the sub-separation zone 95 is shown. Figure 6 The structure of the lower baffle 6 of any two adjacent baffles 6 in the sub-separation zone 95 is shown.

[0130] For the convenience of description, the upper baffle 6 of any two adjacent baffles 6 in the sub-separation zone 95 is called the first baffle 61, and the lower baffle 6 of any two adjacent baffles 6 in the sub-separation zone 95 is called the second baffle 62.

[0131] Combination Figure 5 and Figure 6It can be seen that in this embodiment, the first baffle 61 and the second baffle 62 are both roughly V-shaped, and the first baffle 61 and the second baffle 62 are both provided with a plurality of tube holes 63 and a plurality of vent holes 64. The plurality of tube holes 63 are divided into two groups, which are respectively located on the two plates of the baffle 6 (the first baffle 61 or the second baffle 62) that are relatively bent to form a V-shape, so that the heat exchange tube 5 can pass through, so that the built-in oil separator 102 includes a plurality of holes 63 and a plurality of vent holes 64 along the width direction (i.e., Figure 3 and Figure 4 Two groups of heat exchange tubes 5 are arranged at intervals (in the front-to-back direction), and the two groups of heat exchange tubes 5 are 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 air vents 64 are located between the two groups of through-tube holes 63 for the refrigerant to pass through. In this embodiment, the diameters of the air vents 64 on the first baffle 61 and the second baffle 62 are the same, both of which are 2 mm to 8 mm. At the same time, the total flow area of ​​the air vents 64 on the first baffle 61 and the second baffle 62 accounts for 1 / 8 to 3 / 4 of the total area of ​​the corresponding baffle 6.

[0132] In this embodiment, the structural parameters of the heat exchange tube 5 and the inlet and outlet temperatures of the built-in oil separator 102 satisfy the following relationship:

[0133]

[0134]

[0135] Among them, T in is the temperature of the gaseous refrigerant at the inlet of the air inlet 2, in K; T out is the temperature of the gaseous refrigerant at the outlet of the gas outlet 3, in K; T wall is the average temperature of the outer surface of the heat exchange tube 5 located inside the shell 1, in K; ρ is the gas density, in kg / m 3 ; D is the inner diameter of the air inlet 2, in m; v is the flow rate of the gaseous refrigerant at the inlet of the air inlet 2, in m / s; L is the length of the heat exchange tube 5 in the built-in oil separator 102, in m; n is the number of heat exchange tubes 5 in the built-in oil separator 102; d is the outer diameter of the heat exchange tube 5, in m; λ is the thermal conductivity of the refrigerant gas at the average temperature, in W / (m*K); Cp is the specific heat capacity of the refrigerant gas at the average temperature, in kJ / (kg*K); μ is the viscosity of the refrigerant gas at the average temperature, in Pa*s; u w is the viscosity of the refrigerant gas at the tube wall temperature of the part of the heat exchange tube 5 located in the shell 1, in units of Pa*s; ε is a constant, ranging from 15 to 200; d e P is the equivalent diameter of the heat exchange tube 5, specifically, in this embodiment, it is the equivalent diameter of each group of heat exchange tubes 5, and the unit is m; tis the tube spacing of the heat exchange tube 5, in m. The average temperature is T in With T out The average value of .

[0136] In this embodiment, the structural parameters of the baffle 6 and the heat exchange tube 5 and the inlet and outlet pressure drop ΔP of the built-in oil separator 102 satisfy the following relationship:

[0137]

[0138]

[0139] Wherein, ΔP is the inlet and outlet pressure drop of the built-in oil separator 102, in Pa; C is a constant, with a value of 0.3 to 1.5; ρ is the density of the gaseous refrigerant, in kg / m 3 ;v 0 is the average flow velocity of the gaseous refrigerant flowing through at least two baffles 6, in m / s; D is the inner diameter of the air inlet 2, in m; D d is the average hydraulic diameter of the baffle 6, in m; l b is the distance between two adjacent baffles 6 in the length direction of the heat exchange tube 5, in m; v is the flow velocity of the gaseous refrigerant at the inlet of the air inlet 2, in m / s; n is the number of heat exchange tubes 5 in the built-in oil separator 102; d is the outer diameter of the heat exchange tube 5, in m.

[0140] Based on the built-in oil separator 102 of this embodiment, when the condenser 100 is working, the superheated gaseous refrigerant carries the refrigeration oil from the two air inlet pipes 21 and enters the two sub-separation areas 95 respectively, and first passes through the baffle 72 in the sub-separation area 95 before entering the area where the baffle 6 is located, and finally passes through the gas equalizing plate 4, flows out from the upper filter 31, and enters the condensation area 104. In this process, after collision and separation with the baffle 72, the baffle 6, the heat exchange tube 5, the gas equalizing plate 4, the filter 31 and the oil leakage plate 73, the oil droplets in the refrigerant accumulate and separate, fall from the oil leakage port 46 at the edge of each component, and gather in the oil storage area 92, so as to achieve the separation of the oil droplets. At the same time, the superheated gaseous refrigerant performs single-phase heat exchange with the heat exchange tube 5, so that the temperature of the superheated gaseous refrigerant is reduced to the saturated state and then enters the condensation area 104 for phase change heat exchange, so as to achieve its de-superheating process.

[0141] Since the refrigerant entering the condenser 100 passes through two stages of heat exchange, namely the heat exchange tube 5 in the built-in oil separator 102 and the condenser tube 103 in the condensation area 104, the heat exchange tube 5 can enhance the single-phase heat exchange of the superheated refrigerant gas. Therefore, the de-superheating heat exchange intensity of the condenser 100 can be effectively improved, thereby improving the overall energy efficiency of the condenser 100.

[0142] Moreover, on the basis of the heat exchange tube 5, a baffle 6 is further provided to further enhance the single-phase heat exchange intensity.

[0143] At the same time, the heat exchange tube 5 and the baffle 6 can increase the oil droplet collision and separation area and improve the oil-gas separation efficiency.

[0144] Furthermore, since the heat exchange tubes 5 and the baffles 6 are both disposed in the built-in oil separator 102 , no additional space is required, which is beneficial to the miniaturization of the condenser 100 .

[0145] It can be seen that the condenser 100 and the built-in oil separator 102 of this embodiment can effectively improve the single-phase heat exchange intensity and the 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.

[0146] Based on the built-in oil separator 102 and condenser 100 of the present application, the present application also provides a refrigeration device, which includes a compressor and also includes the condenser 100 of an embodiment of the present application, and the air inlet 2 of the condenser 100 is connected to the exhaust port of the compressor.

[0147] Since the energy efficiency of the built-in oil 102 and the condenser 100 is improved, the energy efficiency of the refrigeration device can also be effectively improved.

[0148] The above description is only an exemplary embodiment of the present application and is not intended to limit the present application. Any modifications, equivalent substitutions, improvements, etc. made within the spirit and principles of the present application shall be included in the protection scope of the present application.

Claims

1. A built-in oil separator (102), characterized in that: include: A shell (1), wherein a separation zone (94) is provided in the shell (1), and an air inlet (2) and an air outlet (3) are provided on the shell (1), wherein the air inlet (2) connects the separation zone (94) with the exhaust port of a compressor so that the gaseous refrigerant discharged from the compressor flows to the separation zone (94), and the air outlet (3) connects the separation zone (94) with the condensation zone (104) of a condenser (100), so that the refrigerant flows from the separation zone (94) to the condensation zone (104) via the air outlet (3) and exchanges heat with a condensation pipe (103) in the condensation zone (104); and at least two heat exchange tubes (5), at least a portion of each heat exchange tube (5) being located in the separation zone (94) so ​​as to exchange heat with the refrigerant flowing from the air inlet (2) to the air outlet (3); The outer diameter of the heat exchange tube (5) is d, and d satisfies the following relationship: Among them, T in is the temperature of the gaseous refrigerant at the inlet of the air inlet portion (2); T out is the temperature of the gaseous refrigerant at the outlet of the gas outlet (3); T wall is the average temperature of the outer surface of the portion 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 (2); v is the flow rate of the gaseous refrigerant at the entrance of the air inlet (2); 0 is the length of the heat exchange tube (5) in the built-in oil component (102); n is the number of heat exchange tubes (5) in the built-in oil component (102); λ is the thermal conductivity of the refrigerant gas at the average temperature; Cp is the specific heat capacity of the refrigerant gas at the average temperature; μ is the viscosity of the refrigerant gas at the average temperature; u w is 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); ε is a constant, with a value of 15 to 200; d e is the equivalent diameter of the heat exchange tube (5); t is the tube spacing of the heat exchange tubes (5).

2. The built-in oil component (102) according to claim 1, characterized in that: The built-in oil separator (102) includes at least two baffles (6), and the at least two baffles (6) are arranged in the separation zone (94) and enable the refrigerant to flow in a baffled manner when flowing through the heat exchange tube (5).

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

4. The built-in oil component (102) according to claim 3, characterized in that: The diameter of the ventilation holes (64) is 2 mm to 8 mm; and / or the total flow area of ​​all the ventilation holes (64) on the baffle (6) accounts for 1 / 8 to 3 / 4 of the total area of ​​the baffle (6).

5. The built-in oil component (102) according to claim 2, characterized in that: The baffle plate (6) is provided with a tube penetration hole (63), and the heat exchange tube (5) passes through the baffle plate (6) via the tube penetration hole (63).

6. The built-in oil component (102) according to claim 2, characterized in that: The average hydraulic diameter of the at least two baffles (6) is D d , and in the length direction of the heat exchange tube (5), the distance between two adjacent baffles (6) is l b , D d and l b Satisfies the following relationship: Wherein, ΔP is the inlet and outlet pressure drop of the built-in oil separator (102); C is a constant, with a value of 0.3 to 1.5; ρ is the density of the gaseous refrigerant; v0 is the average flow velocity of the gaseous refrigerant flowing through the at least two baffles (6); D is the inner diameter of the air inlet (2); v is the flow velocity of the gaseous refrigerant at the inlet of the air inlet (2); n is the number of heat exchange tubes (5) in the built-in oil separator (102); and d is the outer diameter of the heat exchange tube (5).

7. The built-in oil component (102) according to any one of claims 1 to 6, characterized in that: The built-in oil separator (102) includes an air equalizing plate (4), which is arranged in the shell (1) and is located between the heat exchange tube (5) and the air outlet (3). The air equalizing plate (4) has an opening area (41), and the opening area (41) is provided with an air equalizing hole (43). The refrigerant after heat exchange with the heat exchange tube (5) flows to the air outlet (3) through the air equalizing hole (43).

8. The built-in oil component (102) according to claim 7, characterized in that: The air equalizing plate (4) has a non-perforated area (42), the non-perforated area (42) is not provided with the air equalizing hole (43), and corresponds to the area where the baffle plate (6) in the separation area (94) is located, and the perforated area (41) is located on the side of the non-perforated area (42) away from the air inlet part (2).

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

10. The built-in oil component (102) according to claim 7, characterized in that: The air equalizing plate (4) is provided with a plurality of air equalizing holes (43), the plurality of air equalizing holes (43) comprising a first air equalizing hole (44) and a second air equalizing hole (45), the diameter of the first air equalizing hole (44) being greater than the diameter of the second air equalizing hole (45).

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

12. The built-in oil component (102) according to claim 10, characterized in that: The second air equalizing holes (45) are located closer to the edge of the air equalizing plate (4) in the width direction relative to the first air equalizing holes (44), and the ratio of the width of the area where the first air equalizing holes (44) are located to the width of the area where the second air equalizing holes (45) are located is 3 to 10.

13. The built-in oil component (102) according to any one of claims 1 to 6, characterized in that: The shell (1) is provided with two air inlet parts (2), the two air inlet parts (2) are located on both sides of the air outlet part (3), and are both connected to the separation area (94).

14. The built-in oil component (102) according to claim 13, characterized in that: The built-in oil separator (102) comprises a partition (71), wherein the partition (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) correspond one-to-one to the two air inlet portions (2).

15. The built-in oil component (102) according to claim 14, characterized in that: Baffles (6) are provided in both sub-separation zones (95).

16. A condenser (100), comprising a housing (101) and a condenser tube (103), characterized in that: It also includes a built-in oil separator (102) as described in any one of claims 1 to 15, wherein the built-in oil separator (102) is arranged in the outer shell (101), and an area in the outer shell (101) where the built-in oil separator (102) is not arranged forms a condensation area (104), and at least a part of the condensation pipe (103) is located in the condensation area (104).

17. A refrigeration device comprising a compressor, characterized in that: It also includes the condenser (100) according to claim 16, wherein the air inlet (2) of the condenser (100) is connected to the exhaust port of the compressor.

Images