CN215373056U

CN215373056U - Distributor and air conditioner

Info

Publication number: CN215373056U
Application number: CN202121660725.5U
Authority: CN
Inventors: 郜哲明; 刘艳涛
Original assignee: GD Midea Air Conditioning Equipment Co Ltd
Current assignee: GD Midea Air Conditioning Equipment Co Ltd
Priority date: 2021-07-20
Filing date: 2021-07-20
Publication date: 2021-12-31
Anticipated expiration: 2031-07-20

Abstract

The utility model discloses a distributor and an air conditioner, wherein the distributor is provided with a main flow channel and a plurality of branch flow channels, the main flow channel comprises a contraction section, the inner diameter of the contraction section is gradually reduced in the direction close to the branch flow channels, the small-diameter end of the contraction section is communicated with the branch flow channels, and the inner wall surface of the contraction section is in an arc shape extending along the length direction of the main flow channel. The technical scheme of the utility model can improve the shunting uniformity.

Description

Distributor and air conditioner

Technical Field

The utility model relates to the technical field of air conditioners, in particular to a distributor and an air conditioner.

Background

The present invention relates to a multi-flow path heat exchanger, and more particularly to a multi-flow path heat exchanger for an air conditioner, which employs a distributor to distribute a refrigerant to a plurality of flow paths of the heat exchanger, wherein the distributor is installed in a non-vertical manner, when a two-phase refrigerant entering the distributor is an unstable intermittent flow or a spring-like flow, large air bubbles or large air bubbles in the refrigerant enter a distribution cavity from an inlet pipe, and the refrigerant is gathered above the distribution cavity under the action of buoyancy, and a liquid phase is gathered below the distribution cavity under the action of gravity. When two-phase refrigerant flows to each outlet pipe, the outlet pipe at the upper part is mainly occupied by gas phase, and the outlet pipe at the lower part is mainly occupied by liquid phase, so that the flow rate of the refrigerant flowing into the branch of the heat exchanger from each outlet pipe of the distributor is greatly different, and the distribution uniformity is seriously reduced.

SUMMERY OF THE UTILITY MODEL

The utility model mainly aims to provide a distributor, aiming at improving the distribution uniformity.

In order to achieve the above purpose, the distributor provided by the present invention is provided with a main flow channel and a plurality of branch flow channels, wherein the main flow channel comprises a contraction section, the inner diameter of the contraction section gradually decreases in a direction close to the branch flow channels, the small diameter end of the contraction section is communicated with the plurality of branch flow channels, and the inner wall surface of the contraction section is in an arc shape extending along the length direction of the main flow channel.

Optionally, the inner wall surface of the contraction section is a convex arc surface protruding towards the axis of the main flow channel.

Optionally, the inner wall surface of the contraction section is a concave arc surface which is concave towards the direction away from the axis of the main flow passage.

Optionally, the radius of the arc surface of the inner wall surface of the contraction section is greater than or equal to 15mm and less than or equal to 25 mm.

Optionally, the length of the constriction is greater than or equal to 5mm and less than or equal to 10 mm; and/or the presence of a gas in the gas,

the inner diameter of the small-diameter end of the contraction section is greater than or equal to 2mm and less than or equal to 6 mm; and/or the presence of a gas in the gas,

the inner diameter of the large-diameter end of the contraction section is greater than or equal to 4mm and less than or equal to 8 mm.

Optionally, the main runner further includes a steady flow section, the steady flow section is connected to the large diameter end of the contraction section, and the inner wall surface of the steady flow section is cylindrical.

Optionally, the length of the steady flow section is greater than or equal to 5mm and less than or equal to 15 mm.

Optionally, the distributor is provided with a connection port, the plurality of branch channels are connected to the connection port, the main channel further includes a transition section, one end of the transition section is connected to the small diameter end of the contraction section, and the other end of the transition section is connected to the connection port.

Optionally, the inner wall surface of the transition section is cylindrical.

Optionally, the transition section includes a first section and a second section connected to each other, the first section is connected to the small-diameter end of the contraction section, and the inner diameter of the first section gradually decreases in a direction away from the contraction section, and the second section is connected to the connection port, and the inner diameter of the second section gradually increases in a direction away from the contraction section.

Optionally, the inner wall surface of the first section is a convex arc surface protruding towards the axis of the main flow channel; and/or the presence of a gas in the gas,

the inner wall surface of the second section is in a convex arc surface shape protruding towards the axis of the main runner; and/or the presence of a gas in the gas,

the joint of the first section and the second section is in circular arc transition.

Optionally, the inner wall surface of the first section and the inner wall surface of the second section are both convex cambered surface shapes protruding towards the axis of the main flow channel, and the radius of the cambered surface of the first section and/or the second section is greater than or equal to 6mm and less than or equal to 10 mm; and/or the presence of a gas in the gas,

the inner wall surface of the second section is in a convex arc surface shape facing the axis of the main runner, and the sub-runner extends along the tangential direction of the second section at the connecting port.

Optionally, the minimum inner diameter at the junction of the first section and the second section is greater than or equal to 1mm and less than or equal to 3 mm; or the minimum inner diameter of the joint of the first section and the second section is greater than or equal to the product of the inner diameter of the large-diameter end of the contraction section and 0.3, and is less than or equal to the product of the inner diameter of the branch channel and 0.6.

Optionally, the length of the transition section is greater than or equal to 4mm and less than or equal to 6 mm; and/or the presence of a gas in the gas,

the inner diameter of the connecting through opening is greater than or equal to 2mm and less than or equal to 5 mm.

The utility model also provides a heat exchanger comprising the distributor.

According to the technical scheme, the contraction section is arranged in the distributor, so that the two-phase refrigerant firstly passes through the contraction section and then is distributed to the branch channels, when the two-phase refrigerant flows through the contraction section, the cross-sectional area of the two-phase refrigerant flowing through under the same pressure condition is gradually reduced, the flow velocity of the two-phase refrigerant can be increased, the gas phase and the liquid phase in the two-phase refrigerant are mixed more sufficiently and uniformly, when the two-phase refrigerant rapidly flows to each branch channel, the refrigerant flowing into each branch channel is the two-phase refrigerant with the gas phase and the liquid phase mixed uniformly, and the distribution uniformity is improved. And compare in the structure that the inner wall face of shrink section personally submits the circular conical surface, so with the internal face setting of shrink section be the cambered surface shape that extends along the length direction of sprue, can make the one end (entry end or exit end) of shrink section and the runner smooth transition that corresponds the connection, and at shrink section back end circular arc comparatively gentle, can play certain stationary flow effect. Therefore, the arc transition section can be used for increasing the speed of two-phase refrigerants and stabilizing the flowing state before flow splitting. The risk that the flow state of the two-phase refrigerant is changed violently due to large inner diameter change when the two-phase refrigerant enters the contraction section or flows out of the contraction section can be reduced, the flow state of the two-phase refrigerant flowing through the contraction section is relatively stable, the shunting uniformity is favorably improved, and the noise of the refrigerant is reduced.

Drawings

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

FIG. 1 is a schematic structural diagram of an embodiment of a dispenser according to the present invention;

FIG. 2 is a cross-sectional view of the dispenser of FIG. 1;

FIG. 3 is a schematic structural view of another embodiment of the dispenser of the present invention;

fig. 4 is a cross-sectional view of the dispenser of fig. 3.

The reference numbers illustrate:

the implementation, functional features and advantages of the objects of the present invention will be further explained with reference to the accompanying drawings.

Detailed Description

The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.

It should be noted that if directional indications (such as up, down, left, right, front, and back … …) are involved in the embodiment of the present invention, the directional indications are only used to explain the relative positional relationship between the components, the movement situation, and the like in a specific posture, and if the specific posture is changed, the directional indications are changed accordingly.

In addition, if there is a description of "first", "second", etc. in an embodiment of the present invention, the description of "first", "second", etc. is for descriptive purposes only and is not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one such feature. In addition, the meaning of "and/or" appearing throughout is to include three juxtapositions, exemplified by "A and/or B," including either the A or B arrangement, or both A and B satisfied arrangement. In addition, technical solutions between various embodiments may be combined with each other, but must be realized by a person skilled in the art, and when the technical solutions are contradictory or cannot be realized, such a combination should not be considered to exist, and is not within the protection scope of the present invention.

The utility model provides a distributor for an air conditioner, which can be used for an evaporator of the air conditioner and also can be used for a condenser.

In an embodiment of the present invention, referring to fig. 1 and 2, or fig. 3 and 4, the distributor 10 includes a main flow passage 11 and a plurality of branch flow passages 12, the main flow passage 11 includes a contraction section 112, an inner diameter of the contraction section 112 gradually decreases in a direction close to the branch flow passages 12, a small-diameter end of the contraction section 112 is communicated with the plurality of branch flow passages 12, and an inner wall surface of the contraction section 112 is an arc surface extending along a length direction of the main flow passage 11.

In this embodiment, when the inner wall surface of the contraction section 112 is an arc surface extending along the length direction of the main flow passage 11, that is, the inner wall surface of the contraction section 112 is a convex arc surface protruding toward the axis of the main flow passage 11 (see the dotted line X in fig. 2 or the dotted line X in fig. 4), or the inner wall surface of the contraction section 112 is a concave arc surface recessed toward the direction away from the axis of the main flow passage 11.

According to the technical scheme, the contraction section 112 is arranged in the distributor 10, so that two-phase refrigerants firstly pass through the contraction section 112 and then are distributed to the branch channels 12, when the two-phase refrigerants flow through the contraction section 112, the cross-sectional area of the two-phase refrigerants flowing through under the same pressure condition is gradually reduced, the flow velocity of the two-phase refrigerants can be increased, gas-liquid two phases in the two-phase refrigerants are mixed more sufficiently and uniformly, when the two-phase refrigerants rapidly flow to the branch channels 12, the refrigerants flowing into the branch channels 12 are the two-phase refrigerants with the gas-liquid two phases mixed uniformly, and the distribution uniformity is improved. Compared with the structure that the inner wall surface of the contraction section 112 is a conical surface, the inner wall surface of the contraction section 112 is provided with an arc surface extending along the length direction of the main runner 11, so that one end (inlet end or outlet end) of the contraction section 112 and the correspondingly connected runner are in smooth transition, and the arc at the rear section of the contraction section 112 is relatively gentle, so that a certain flow stabilizing effect can be achieved. Therefore, the arc transition section 113 can increase the speed of the two-phase refrigerant and stabilize the flow state before the split flow. The risk that the flow state of the two-phase refrigerant is changed violently due to large inner diameter change when the two-phase refrigerant enters the contraction section 112 or flows out of the contraction section 112 can be reduced, the flow state of the two-phase refrigerant flowing through the contraction section 112 is relatively stable, the flow distribution uniformity is favorably further improved, and the noise of the refrigerant is reduced.

When the main channel 11 is connected to a refrigerant pipe of an air conditioner, it is difficult to ensure that the inner diameter of the refrigerant pipe is consistent with the inner diameter of the main channel 11, and generally, the inner diameter of the joint of the refrigerant pipe and the main channel 11 changes, thereby causing the flowing state of the refrigerant flowing into the main channel 11 to change. In order to ensure that the refrigerant can stably flow through the contraction section 112, in an embodiment, the main flow passage 11 further includes a flow stabilizing section 111, the flow stabilizing section 111 is connected to the large-diameter end of the contraction section 112, and an inner wall surface of the flow stabilizing section 111 is a cylindrical surface. That is, when the two-phase refrigerant flows into the main flow passage 11, the two-phase refrigerant flows through the steady flow section 111 first and then flows to the contraction section 112, and when the inner wall surface of the steady flow section 111 is cylindrical, that is, the inner diameter of the steady flow section 111 is kept constant in the length direction of the main flow passage 11, so that after the two-phase refrigerant flows into the steady flow section 111, the inner diameter of the steady flow section 111 along the length direction is kept constant, thereby avoiding the situation that the steady flow section 111 changes the flow state of the two-phase refrigerant, gradually bringing the two-phase refrigerant to a stable flow state, and further enabling the two-phase refrigerant to stably flow to the contraction section 112, so as to ensure that the two-phase refrigerant entering the contraction section 112 can be gradually pressurized in a stable flow state, which is beneficial to further improving the gas-liquid two-phase mixing degree of the two-phase refrigerant in the contraction section 112, and further improving the distribution uniformity. Of course, in other embodiments, other configurations of the interior of the flow stabilizer 111 may be used while maintaining the same cross-sectional area throughout the flow stabilizer 111 along its length. In addition, in other embodiments, the flow stabilizing section 111 may not be provided.

When the flow stabilizing section 111 is provided, if the length of the flow stabilizing section 111 is too small, it is difficult to achieve the flow stabilizing effect, and if the length of the flow stabilizing section 111 is too large, the length of the distributor 10 is too long, and the distance from the contraction section 112 to the inlet of the main flow passage 11 is too long, which increases the difficulty in molding the contraction section 112. Therefore, in order to ensure that the steady flow section 111 can better play a role of stabilizing the flow and avoid the situation that the molding difficulty of the contraction section 112 is too large due to the too long length of the steady flow section 111, in an embodiment, the length of the steady flow section 111 is greater than or equal to 5mm and less than or equal to 15 mm. Specifically, the length of the flow stabilizing section 111 may be 5mm, 6mm, 7mm, 8mm, 9mm, 10mm, 11mm, 12mm, 13mm, 14mm, 15mm, or the like. Of course, in other embodiments, the length of the flow stabilizer 111 may be less than 5mm or greater than 15 mm.

In one embodiment, the inner diameter of the flow stabilizer 111 is greater than or equal to 4mm and less than or equal to 8 mm. By the arrangement, the flow stabilizing section 111 can be adapted to more refrigerant pipes with different sizes, and the difference between the inner diameter of each refrigerant pipe and the inner diameter of the flow stabilizing section 111 is avoided. Wherein, the inner diameter of the steady flow section 111 can be 4mm, 5mm, 6mm, 7mm or 8mm, etc. Of course, in other embodiments, the inner diameter of the flow stabilizer 111 may be less than 4mm or greater than 8 mm.

Referring to fig. 2, in an embodiment, the inner wall surface of the contraction section 112 is a convex arc surface protruding toward the axis of the main flow passage 11 (see the dashed line X in fig. 2). Specifically, the molded line (bus) of the inner wall surface of the contraction section 112 extending along the length direction of the main channel 11 is a convex arc line protruding toward the axis of the main channel 11, so that the change of the inner diameter of the inlet portion (the portion of the contraction section 112 away from the branch channels 12) of the contraction section 112 is large, thereby enabling the two-phase refrigerant to enter the contraction section 112 and then be rapidly pressurized, and the change of the inner diameter of the outlet portion (the portion of the contraction section 112 close to the branch channels 12) of the contraction section 112 is small, when the two-phase refrigerant flows to the outlet portion of the contraction section 112, the speed change rate of the two-phase refrigerant can be reduced, so that the flow speed of the two-phase refrigerant tends to be stable, thereby ensuring that the two-phase refrigerant is distributed to each branch channel 12 in a relatively stable flowing state, and facilitating improvement of distribution uniformity. Moreover, the condition that bubbles are broken due to rapid pressure change of the two-phase refrigerant at the outlet part of the contraction section 112 can be reduced, and the flow channel noise during the flow division of the two-phase refrigerant can be reduced. Optionally, the distributor 10 is provided with a connecting port 13, the plurality of branch channels 12 are all connected to the connecting port 13, that is, the inlets of the plurality of branch channels 12 are concentrated at the connecting port 13, and the contraction section 112 is connected to the connecting port 13, that is, the small diameter end of the contraction section 112 is directly connected to the connecting port 13. Of course, in other embodiments, a transition section 113 may be provided between the small diameter end of the contraction section 112 and the connection port 13, and the small diameter end of the contraction section 112 is communicated with the connection port 13 through the transition section 113.

Referring to fig. 4, in another embodiment, the inner wall surface of the contraction section 112 is a concave arc surface recessed in a direction away from the axis of the main flow passage 11 (see the dotted line X in fig. 4). Specifically, the molded line (bus) of the inner wall surface of the contraction section 112 extending along the length direction of the main runner 11 is a concave arc line protruding towards the direction away from the axis of the main runner 11, so that the change of the inner diameter of the inlet part (the part of the contraction section 112 away from the branch runner 12) of the contraction section 112 is small, the change of the flow speed of the two-phase refrigerant when the two-phase refrigerant starts to enter the contraction section 112 is small, the two-phase refrigerant can be better connected with the steady flow section 111 when the steady flow section 111 is arranged, and the condition that the inner diameter of the two-phase refrigerant is too large when the two-phase refrigerant flows from the steady flow section 111 to the contraction section 112 is avoided. When the two-phase refrigerant gradually flows from the inlet portion to the outlet portion of the contraction section 112 (the portion of the contraction section 112 close to the branch channel 12), the flow rate of the two-phase refrigerant is gradually increased, and the flow rate change rate of the two-phase refrigerant is gradually increased, which is also beneficial to gradually increase the flow rate of the two-phase refrigerant in the contraction section 112 in a relatively stable state.

When the inner wall surface of the contraction section 112 is a concave arc surface that is concave in the direction away from the axis of the main flow passage 11, in an embodiment, the arc surface radius of the inner wall surface of the contraction section 112 is greater than or equal to 15mm and less than or equal to 25 mm. That is, the radius of the molded line (generatrix) extending along the length direction of the main runner 11 from the inner wall surface of the contraction section 112 is greater than or equal to 15mm and less than or equal to 25 mm. Specifically, if the radius of the arc surface of the inner wall surface of the constriction section 112 is too small, that is, the change in curvature of the inner wall surface of the constriction section 112 in the longitudinal direction of the main flow passage 11 is too large, the two-phase refrigerant easily collides with the inner wall surface of the constriction section 112 to generate noise. If the radius of the arc surface of the inner wall surface of the contraction section 112 is too large, the change of the inner diameters of the large-diameter end and the small-diameter end of the contraction section 112 is too small, the increase of the flow velocity of the two-phase refrigerant flowing through the contraction section 112 under the same pressure condition is small, and the gas-liquid two-phase mixing effect is poor. When the radius of the arc surface of the inner wall surface of the contraction section 112 is set to be between 15mm and 25mm, the flow velocity of the two-phase refrigerant flowing through the contraction section 112 under the same pressure condition is increased greatly, the gas-liquid two-phase mixing effect is good, and the condition that the two-phase refrigerant impacts the inner wall surface of the contraction section 112 to generate noise can be well prevented. The radius of the arc surface of the inner wall surface of the contraction section 112 may be 15mm, 16mm, 17mm, 18mm, 19mm, 20mm, 21mm, 22mm, 23mm, 24mm or 25 mm. Of course, in other embodiments, the radius of the arc of the inner wall surface of the constricted section 112 may be less than 15mm or greater than 25 mm.

In one embodiment, the length of the constriction 112 is greater than or equal to 5mm and less than or equal to 10 mm. Specifically, when the radius of the arc surface of the inner wall surface of the contraction section 112 is not changed, if the length of the contraction section 112 is too small, the change rate of the inner diameters of the large-diameter end and the small-diameter end of the contraction section 112 is too small, the flow velocity of the two-phase refrigerant flowing through the contraction section 112 under the same pressure is increased less, and the gas-liquid two-phase mixing effect is poor. If the length of the necked portion 112 is too large, the amount of work done on the necked portion 112 may be increased, which may increase the manufacturing difficulty and cost of the dispenser 10 and may also result in an overall length of the dispenser 10. When the length of the contraction section 112 is set between 5mm and 10mm, the flow velocity of two-phase refrigerants can be ensured to be increased greatly when flowing through the contraction section 112 under the same pressure condition, the gas-liquid two-phase mixing effect is good, the increase of the processing amount of the contraction section 112 due to the overlarge length of the contraction section 112 can be avoided, and the manufacturing difficulty and the cost of the distributor 10 are increased. The length of the contraction section 112 may be 5mm, 6mm, 7mm, 8mm, 9mm, 10mm, or the like. Of course, in other embodiments, the length of the constriction 112 may be less than 5mm or greater than 10 mm.

In one embodiment, the inner diameter of the small diameter end of the constriction section 112 is greater than or equal to 1mm and less than or equal to 6 mm. Specifically, the inner diameter of the large-diameter end of the contraction section 112 is usually set according to the size of the refrigerant pipe to avoid an excessive difference between the inner diameter of the large-diameter end of the contraction section 112 and the inner diameter of the refrigerant pipe, so when the inner diameter of the large-diameter end of the contraction section 112 is not changed, if the inner diameter of the small-diameter end of the contraction section 112 is too small, the resistance of the two-phase refrigerant flowing through the distributor 10 is increased, the amount of the refrigerant flowing to the heat exchanger is reduced, and the load of the compressor is increased. If the inner diameter of the small-diameter end of the contraction section 112 is too large, the change rate of the inner diameters of the small-diameter end and the large-diameter end of the contraction section 112 is too small, the flow velocity of the two-phase refrigerant flowing through the contraction section 112 under the same pressure condition is increased slightly, and the gas-liquid two-phase mixing effect is poor. When the inner diameter of the small-diameter end of the contraction section 112 is set between 2mm and 6mm, the flow velocity of the two-phase refrigerant flowing through the contraction section 112 under the same pressure condition can be increased greatly, the gas-liquid two-phase mixing effect is good, and the situation that the resistance of the two-phase refrigerant flowing through the distributor 10 is increased due to the fact that the inner diameter of the small-diameter end of the contraction section 112 is too small can be avoided. In this embodiment, the inner diameter of the small-diameter end of the contraction section 112 is greater than or equal to 2mm and less than or equal to 6 mm. The inner diameter of the small-diameter end of the constricted section 112 may be 1mm, 2mm, 2.5mm, 3mm, 3.5mm, 4mm, 4.5mm, 5mm, 5.5mm, or 6 mm. Of course, in other embodiments, the inner diameter of the small diameter end of the constriction section 112 may be greater than 6 mm.

When the steady flow section 111 is provided, in an embodiment, the inner diameter of the large diameter end of the contraction section 112 is the same as the inner diameter of the steady flow section 111, that is, the inner diameter of the large diameter end of the contraction section 112 is greater than or equal to 4mm and less than or equal to 8mm, wherein the inner diameter of the large diameter end of the contraction section 112 is greater than the inner diameter of the small diameter end of the contraction section 112. Of course, in other embodiments, the inner diameter of the large diameter end of the constriction section 112 may be greater than or less than the inner diameter of the flow stabilizer 111.

In one embodiment, the distributor 10 is provided with a connection port 13, the plurality of branch channels 12 are connected to the connection port 13, and the main channel 11 further includes a transition section 113, one end of the transition section 113 is connected to the small-diameter end of the contraction section 112, and the other end is connected to the connection port 13. That is, the inlets of the plurality of branch channels 12 are gathered at the connection through-opening 13, and it is equivalent to that the inlets of the plurality of branch channels 12 are overlapped to form the connection through-opening 13, that is, the axes of the plurality of branch channels 12 are inclined with respect to the axis of the main channel 11, and the interval between the branch channels 12 is gradually increased in the direction away from the main channel 11. The transition section 113 connects the small-diameter end of the contraction section 112 and the connection through-opening 13, so that the main channel 11 and the connection part of the main channel 11 and the branch channel 12 can be prevented from forming a step structure, and the conditions that noise is generated and the flow pattern of two-phase refrigerants is disturbed when the two-phase refrigerants collide on the step structure can be avoided. When the two-phase refrigerant flows out of the contraction section 112 and flows to the connection port 13 through the transition section 113, the two-phase refrigerant can be directly distributed to each branch runner 12, and the possibility of overlarge flow pattern change of the two-phase refrigerant can be reduced. Optionally, the length of the convergent section 112 is greater than the length of the transition section 113. In other embodiments, the transition section 113 may not be provided, and the small-diameter end of the contraction section 112 may be directly connected to the connection port 13.

In an embodiment, the included angle between the axis of each branch flow channel 12 and the axis of the main flow channel 11 is greater than or equal to 15 °, and less than or equal to 25 °, the included angle between the axes of the branch flow channels 12 respectively arranged on two opposite sides of the axis of the main flow channel 11 is greater than or equal to 30 °, and less than or equal to 50 °, so that the distance between the outlets of the branch flow channels 12 is larger while the better distribution effect is ensured, and the refrigerant pipeline is convenient to install. Wherein, the included angle between the axis of each branch flow channel 12 and the axis of the main flow channel 11 can be 15 °, 16 °, 17 °, 17.5 °, 18 °, 18.5 °, 19 °, 19.5 °, 20 °, 21 °, 22 °, 23 °, 24 ° or 25 °. Of course, in other embodiments, the axis of each sub-channel 12 may also be less than 15 ° or greater than 25 ° from the axis of the main channel 11.

The transition section 113 may have various configurations, for example, in one embodiment, the inner wall of the transition section 113 is cylindrical (not shown). That is, the inner diameter of the transition section 113 is kept constant in the length direction of the main flow channel 11, so that after the two-phase refrigerant flows into the transition section 113, because the inner diameter of the transition section 113 along the length direction thereof is kept constant, the two-phase refrigerant gradually tends to a stable flowing state when flowing towards the connection through port 13, and thus the two-phase refrigerant can be stably distributed to each branch flow channel 12, which is beneficial to improving the distribution uniformity. Of course, in other embodiments, other configurations of the interior of the transition section 113 are possible while maintaining the same cross-sectional area throughout the transition section 113 along its length.

Referring to fig. 4, in another embodiment, the transition section 113 includes a first section 114 and a second section 115 connected with each other, the first section 114 is connected with the small-diameter end of the contraction section 112, the inner diameter of the first section 114 is gradually reduced in a direction away from the contraction section 112, the second section 115 is connected with the connection port 13, and the inner diameter of the second section 115 is gradually increased in a direction away from the contraction section 112. Specifically, the inner diameter of the transition section 113 decreases and then increases in the refrigerant flow direction. The change rate of the inner diameter of the first section 114 is smaller than that of the small-diameter end of the contraction section 112, so that although the flow rate of the two-phase refrigerant is in a gradually increasing state when the two-phase refrigerant flows into the transition section 113 from the contraction section 112, the flow acceleration of the two-phase refrigerant is gradually reduced, the condition that the flow acceleration of the two-phase refrigerant is suddenly changed can be avoided, and the transition section 113 and the contraction section 112 are better connected. When the plurality of branch channels 12 are connected to the connection through-port 13, that is, the axes of the plurality of branch channels 12 are inclined with respect to the axis of the main channel 11, the distance between the branch channels 12 gradually increases in the direction away from the main channel 11. When the inner diameter of the second segment 115 is gradually increased in the direction away from the contraction segment 112, the included angle between the extending direction of the inner wall surface of the second segment 115 and the extending direction of the branch runner 12 can be reduced, and even the extending direction of the inner wall surface of the second segment 115 can be consistent with the extending direction of the branch runner 12, so that when two-phase refrigerant flows from the first end to the second segment 115, the two-phase refrigerant can better flow to each branch runner 12 along the second segment 115, and the possibility that the two-phase refrigerant impacts the inner wall of the branch runner 12 to generate noise can be reduced.

In one embodiment, the inner wall surface of the first section 114 is convexly curved towards the axis of the primary flow channel 11. Specifically, a profile (a generatrix) of the inner wall surface of the first segment 114 extending in the longitudinal direction of the main flow passage 11 is a convex arc line projecting toward the axis of the main flow passage 11. Therefore, the inner diameter change rate of the outlet portion (the portion close to the second section 115) of the first section 114 is gradually reduced, and when the two-phase refrigerant flows to the outlet portion of the first section 114, the flow velocity of the two-phase refrigerant tends to be stable, so that the two-phase refrigerant can be ensured to flow to the second section 115 in a relatively stable flowing state. Of course, in other embodiments, the inner wall surface of the first section 114 may also be a conical surface.

In an embodiment, the inner wall surface of the second section 115 is a convex arc surface protruding toward the axis of the main flow channel 11, and specifically, a molded line (a bus) of the inner wall surface of the second section 115 extending along the length direction of the main flow channel 11 is a convex arc line protruding toward the axis of the main flow channel 11, so that the two-phase refrigerant flowing to the second section 115 can better flow along the extending direction of the sub-flow channel 12 under the action of the coanda, and the possibility of noise generated by the two-phase refrigerant impacting the inner wall of the sub-flow channel 12 can be reduced. And when the inner wall surface of the first section 114 is a convex arc surface protruding towards the axis of the main runner 11, the connection between the second section 115 and the first end can be smooth, so that the two-phase refrigerant flowing from the first section 114 to the second section 115 can better flow along the extension direction of the branch runner 12 under the action of the attaching wall, wherein the arc surface radius of the first section 114 and the arc surface radius of the second section 115 can be the same or different. Of course, in other embodiments, the inner wall surface of the second section 115 may also be a conical surface.

In an embodiment, the connection between the first segment 114 and the second segment 115 is in a circular arc transition, so that the connection between the second segment 115 and the first end can be in a smooth transition, so that two-phase refrigerant flowing to the connection between the first segment 114 and the second segment 115 can better flow to the second segment 115 under the action of the coanda, the amount of refrigerant impacting the inner wall between the branched runners 12 can be reduced, and noise reduction is facilitated.

The inner wall surface of the first section 114 is in a convex arc surface shape facing the axis of the main flow channel 11, the inner wall surface of the second section 115 is in a convex arc surface shape facing the axis of the main flow channel 11, and the arc transition of the joint of the first section 114 and the second section 115 can make the joint of the second section 115 and the first end more smooth, so that the condition that bubbles are broken due to the rapid change of pressure between the first section 114 and the second section 115 of the two-phase refrigerant can be reduced, and the flow channel noise during the flow distribution of the two-phase refrigerant can be reduced.

In one embodiment, the inner wall surface of the first segment 114 is a convex arc surface protruding toward the axis of the main flow passage 11, the inner wall surface of the contraction segment 112 is a concave arc surface recessed away from the axis of the main flow passage 11, and the inner wall surface of the first segment 114 is tangent to the inner wall surface of the contraction segment 112. This allows the two-phase refrigerant to transition smoothly at the junction between the first section 114 and the contraction section 112. Of course, in other embodiments, the inner wall surface of the first segment 114 and the inner wall surface of the contraction segment 112 may also be in transition through a circular arc.

When the inner wall surface of the first segment 114 and the inner wall surface of the second segment 115 are both convex arc surfaces protruding toward the axis of the main flow passage 11, in an embodiment, the arc surface radius of the first segment 114 and/or the second segment 115 is greater than or equal to 6mm and less than or equal to 10 mm. Namely, the radius of the cambered surface of the first section 114 is greater than or equal to 6mm and less than or equal to 10 mm; and/or the cambered surface radius of the second section 115 is greater than or equal to 6mm and less than or equal to 10 mm.

The radius of the arc surface of the inner wall surface of the first section 114 is greater than or equal to 6mm and less than or equal to 10 mm. That is, the radius of the profile (generatrix) of the first section 114 extending along the length direction of the main flow passage 11 is greater than or equal to 6mm and less than or equal to 10 mm. Specifically, if the radius of the arc surface of the inner wall surface of the first stage 114 is too small, that is, the change in curvature of the inner wall surface of the first stage 114 in the longitudinal direction of the main flow passage 11 is too large, the two-phase refrigerant easily collides with the inner wall surface of the first stage 114 to generate noise. If the radius of the arc surface of the inner wall surface of the first section 114 is too large, the connection effect between the first end and the contraction section 112 is poor, that is, the smooth transition effect when the two-phase refrigerant flows through the connection between the first end and the contraction section 112 is poor. When the radius of the arc surface of the inner wall surface of the first section 114 is set between 6mm and 10mm, the possibility of noise generation caused by impact of two-phase refrigerants on the inner wall surface of the first section 114 can be reduced, and the two-phase refrigerants can be ensured to be in smooth transition at the connection position of the first end and the contraction section 112 well. The radius of the arc surface of the inner wall surface of the first section 114 may be 6mm, 7mm, 8mm, 9mm, 10mm, or the like. Of course, in other embodiments, the radius of the camber of the inner wall surface of the first segment 114 may be less than 6mm or greater than 10 mm.

The radius of the arc surface of the inner wall surface of the second section 115 is greater than or equal to 6mm and less than or equal to 10 mm. That is, the radius of the molded line (generatrix) extending along the longitudinal direction of the main flow channel 11 from the inner wall surface of the second segment 115 is not less than 6mm, and not more than 10 mm. Specifically, if the radius of the arc surface of the inner wall surface of the second stage 115 is too small, that is, the change in curvature of the inner wall surface of the second stage 115 in the longitudinal direction of the main flow passage 11 is too large, the two-phase refrigerant easily collides with the inner wall surface of the second stage 115, and noise is generated. If the radius of the arc surface of the inner wall surface of the first segment 114 is too large, when the second segment 115 and the first segment 114 are in relatively smooth transition, the inclination angle between the extending direction of the inner wall surface of the second segment 115 and the extending direction of the branch runner 12 is relatively large, so that the possibility that the two-phase refrigerant impacts the inner wall surface of the branch runner 12 to generate noise is increased. When the radius of the arc surface of the inner wall surface of the second section 115 is set between 6mm and 10mm, it can be ensured that the second section 115 and the first section 114 realize smooth transition well, and it can also be ensured that the angle between the extension direction of the inner wall surface of the second section 115 and the extension direction of the branch runner 12 is small, and the possibility of noise generation caused by impact of two-phase refrigerants on the inner wall surface of the branch runner 12 is reduced, wherein the radius of the arc surface of the inner wall surface of the second section 115 can be specifically 6mm, 7mm, 8mm, 9mm or 10mm, and the like. Alternatively, the radius of camber of the inner wall surface of the first segment 114 is the same as the radius of camber of the inner wall surface of the second segment 115. Of course, in other embodiments, the radius of the arc of the inner wall surface of the second segment 115 may be less than 6mm or greater than 10 mm.

The minimum inner diameter of the joint of the first section 114 and the second section 115, that is, the minimum inner diameter of the main flow channel 11, and the minimum inner diameter of the joint of the first section 114 and the second section 115 are smaller, so that the flow velocity of the two-phase refrigerant is larger, but the flow noise of the two-phase refrigerant is increased, and therefore, the improvement of the flow velocity of the two-phase refrigerant and the avoidance of the increase of the flow noise are considered comprehensively. In one embodiment, the minimum inner diameter at the junction of the first segment 114 and the second segment 115 is greater than or equal to 1mm and less than or equal to 3 mm. The minimum inner diameter of the joint of the first section 114 and the second section 115 may be 1mm, 1.5mm, 2mm, 2.5mm, or 3 mm. Of course, in other embodiments, the minimum inner diameter at the junction of the first segment 114 and the second segment 115 may be less than 1mm or greater than 3 mm.

In another embodiment, the minimum inner diameter at the junction of the first segment 114 and the second segment 115 is greater than or equal to the product of the inner diameter of the large diameter end of the converging segment 112 and 0.3, and less than or equal to the product of the inner diameter of the diverging passageway 12 and 0.6, other than the limits of the above numerical ranges. Therefore, the flow speed of the two-phase refrigerant can be improved, and the flowing noise is low.

In one embodiment, the length of the transition section 113 is greater than or equal to 4mm and less than or equal to 6 mm. Specifically, when the inner wall surface of the transition section 113 is a cylindrical surface, if the length of the transition section 113 is too small, the flow stabilizing effect is poor, and if the length of the transition section 113 is too large, the length of the distributor 10 is too long, and the distance from the transition section 113 to the inlet of the main flow passage 11 is too long, so that the difficulty in forming the transition section 113 is increased. When setting up the length setting of changeover portion 113 between 4mm to 6mm, can guarantee that changeover portion 113 can play the stationary flow effect betterly simultaneously, avoid leading to the too big condition of the shaping degree of difficulty of changeover portion 113 because of sprue 11 total length overlength.

When the transition section 113 includes the first section 114 and the second section 115, if the length of the transition section 113 is too small, that is, the length of the first section 114 and the second section 115 is also too small, the effect to be achieved when the first section 114 and the second section 115 are disposed is deteriorated, and if the length of the transition section 113 is too large, the length of the distributor 10 is too long, and the distance from the transition section 113 to the inlet of the main flow passage 11 is too long, so that the difficulty in molding the first section 114 and the second section 115 is increased. When setting up the length setting of changeover portion 113 between 4mm to 6mm, can guarantee first section 114 and second section 115's effect when better, avoid leading to the too big condition of the shaping degree of difficulty of changeover portion 113 because of sprue 11 total length overlength.

The length of the transition section 113 may be 4mm, 4.5mm, 5mm, 5.5mm, or 6 mm. Of course, in other embodiments, the length of the transition section 113 may be less than 4mm or greater than 6 mm.

In one embodiment, the inner diameter of the connection through-opening 13 is greater than or equal to 2mm and less than or equal to 5 mm. Specifically, when the inner diameter of the connection through-port 13 is too small, the inlets of the respective branch passages 12 become small, the flow rate of the refrigerant is restricted, and the heat exchange efficiency of the heat exchanger is reduced. If the inner diameter of the connection port 13 is too large, the difference between the inner diameters of the connection port 13 and the transition section 113 is large, and the difficulty in processing the second section 115 is increased. When the internal diameter of connecting the mouth 13 sets up between 2mm to 5mm, can guarantee to connect the meeting refrigerant flow demand that can connect the mouth 13, also can avoid connecting the mouth 13 and the interior diameter of changeover portion 113 and differed greatly and lead to the too big condition of the processing degree of difficulty of second section 115. The inner diameter of the connection through-hole 13 may be 2mm, 3mm, 4mm, or 5 mm. Of course, the inner diameter of the connection through-opening 13 may also be smaller than 2mm or larger than 5mm in other embodiments.

In one embodiment, the inner diameter of the runners 12 is greater than or equal to 1.5 and less than or equal to 4 mm. So as to ensure better shunting effect. The inner diameter of the sub-runners 12 may specifically be 1.5mm, 2mm, 2.5mm, 3mm, 3.5mm or 4 mm.

In one embodiment, the length of the runners 12 is greater than or equal to 10mm and less than or equal to 15 mm. This avoids the dispenser 10 being too long. The length of the sub-runners 12 may be 11mm, 12mm, 13mm, 14mm or 15 mm.

When the inner wall surface of the second segment 115 is in the shape of a convex arc surface protruding towards the axis of the main runner 11, in an embodiment the sub-runners 12 extend in the tangential direction of the second segment 115 at the connection through-opening 13. With such an arrangement, the extending direction of the inner wall surface of the second section 115 can be consistent with the extending direction of the branch runners 12, when two-phase refrigerant flows from the first end to the second section 115, the two-phase refrigerant can better flow to each branch runner 12 along the second section 115, and the possibility of noise generated by the two-phase refrigerant impacting the inner wall of the branch runners 12 is further reduced.

Referring to fig. 4, in an embodiment, an inner diameter of the steady flow section 111 (an inner diameter of a large-diameter end of the contraction section 112) is 4.8mm, a length of the steady flow section 111 is 10mm, an inner diameter of the branch flow channel 12 is 2mm, a length of the branch flow channel 12 is 12mm, an included angle between an axis of the branch flow channel 12 and an axis of the main flow channel 11 is 18 °, an arc radius of an inner wall surface of the contraction section 112 is 9mm, a length of the contraction section 112 is 6.5mm, an inner diameter of a small-diameter end of the contraction section 112 (an inner diameter of a connection portion of the contraction section 112 and the transition section 113) is 2.5mm, an arc radius of an inner wall surface of the first section 114 and an arc radius of an inner wall surface of the second section 115 are both 8mm, a length of the transition section 113 is 5.5mm, a minimum inner diameter of a connection portion of the first section 114 and the second section 115 is 1.5mm, and an inner diameter of the connection through port 13 is 2.5 mm. This results in a better overall flow distribution of the dispenser 10.

Referring to fig. 2, when the inner wall surface of the contraction section 112 is a convex arc surface protruding toward the axis of the main flow channel 11, in an embodiment, the inner diameter of the flow stabilizing section 111 is 4.8mm, the length of the flow stabilizing section 111 is 10mm, the inner diameter of the branch flow channel 12 is 2mm, the length of the branch flow channel 12 is 12mm, an included angle between the axis of the branch flow channel 12 and the axis of the main flow channel 11 is 18 °, the arc radius of the inner wall surface of the contraction section 112 is 63mm, and the length of the contraction section 112 is 12 mm. Therefore, the whole flow distribution effect of the distributor 10 is better when the inner wall surface of the contraction section 112 is a convex arc surface protruding towards the axis of the main flow passage 11.

The present invention further provides an air conditioner, which includes a heat exchanger and a distributor 10, and the specific structure of the distributor 10 refers to the above embodiments, and since the air conditioner employs all technical solutions of all the above embodiments, the air conditioner at least has all the beneficial effects brought by the technical solutions of the above embodiments, and details are not repeated herein. The heat exchanger has a plurality of flow paths, and the inflow end of each flow path is correspondingly communicated with one of the branch channels 12. The heat exchanger can be an evaporator or a condenser.

The above description is only a preferred embodiment of the present invention, and is not intended to limit the scope of the present invention, and all modifications and equivalents of the present invention, which are made by the contents of the present specification and the accompanying drawings, or directly/indirectly applied to other related technical fields, are included in the scope of the present invention.

Claims

1. The utility model provides a distributor, its characterized in that, the distributor is equipped with sprue and a plurality of subchannel, the sprue includes the shrink section, the internal diameter of shrink section is being close to gradually reduce in the direction of subchannel, the path end and a plurality of shrink section the subchannel intercommunication, the inner wall face of shrink section is personally submitted and is followed the cambered surface shape that the length direction of sprue extended.

2. The dispenser of claim 1, wherein the inner wall surface of the constrictor defines a convex arc projecting toward the axis of the primary flow passage.

3. The distributor of claim 1, wherein the inner wall surface of the convergent section is in the form of a concave arc concave away from the axis of the primary flow passage.

4. The dispenser of claim 3, wherein the radius of the arc of the inner wall surface of the constriction is greater than or equal to 15mm and less than or equal to 25 mm.

5. The dispenser of claim 1, wherein the length of the constriction is greater than or equal to 5mm and less than or equal to 10 mm; and/or the presence of a gas in the gas,

6. The distributor of claim 1, wherein the main flow passage further comprises a flow stabilizer connected to the large diameter end of the convergent section, the flow stabilizer having an inner wall surface in the shape of a cylinder.

7. The dispenser of claim 6, wherein the flow stabilizer has a length greater than or equal to 5mm and less than or equal to 15 mm.

8. The distributor according to any one of claims 1 to 7, wherein the distributor is provided with a connection port, a plurality of the branch channels are connected to the connection port, and the main channel further comprises a transition section, one end of which is connected to the small diameter end of the contraction section, and the other end of which is connected to the connection port.

9. The dispenser of claim 8, wherein the inner wall surface of the transition section is cylindrical.

10. The dispenser of claim 8, wherein the transition section includes a first section and a second section connected, the first section being connected to the smaller diameter end of the constrictor and having an inner diameter that gradually decreases in a direction away from the constrictor, the second section being connected to the connection port and having an inner diameter that gradually increases in a direction away from the constrictor.

11. The distributor of claim 10, wherein the inner wall surface of the first segment is convexly curved toward the axis of the primary flow passage; and/or the presence of a gas in the gas,

12. The distributor according to claim 10, wherein the inner wall surface of the first section and the inner wall surface of the second section are each in the shape of a convex arc surface protruding toward the axis of the main flow channel, and the radius of the arc surface of the first section and/or the second section is greater than or equal to 6mm and less than or equal to 10 mm; and/or the presence of a gas in the gas,

13. The dispenser of claim 10, wherein the minimum inner diameter at the junction of the first section and the second section is greater than or equal to 1mm and less than or equal to 3 mm; or the minimum inner diameter of the joint of the first section and the second section is greater than or equal to the product of the inner diameter of the large-diameter end of the contraction section and 0.3, and is less than or equal to the product of the inner diameter of the branch channel and 0.6.

14. The dispenser of claim 10, wherein the length of the transition section is greater than or equal to 4mm and less than or equal to 6 mm; and/or the presence of a gas in the gas,

15. An air conditioner characterized by comprising the distributor according to any one of claims 1 to 14.