阅读说明：本技术 冷媒分配器以及包含该冷媒分配器的蒸发器 (Refrigerant distributor and evaporator comprising same ) 是由 程嫚 徐峰 周杰 马新 罗雄 于 2019-08-22 设计创作，主要内容包括：本申请实施例提供一种冷媒分配器以及包含该冷媒分配器的蒸发器,冷媒分配器(4)具有：盒体(42)；冷媒入口(41),其设置在所述盒体(42)的上表面(421)；出液孔(46),其均匀设置在所述盒体(42)的下表面(422)；以及端板,其设置于所述盒体(42)的长度方向的两端,从所述两端封闭所述盒体(42),其中,在从所述下表面(422)指向所述上表面(421)的高度方向上,在从所述下表面(422)起的预定高度范围内,所述盒体(42)的宽度逐渐增大；盒体(42)内设预分配器(3)。本实施例有利于冷媒的均匀分配,从而改善蒸发器的换热效果。(The embodiment of the application provides a refrigerant distributor and contain this refrigerant distributor's evaporimeter, refrigerant distributor (4) have: a case (42); a refrigerant inlet (41) provided on an upper surface (421) of the case (42); liquid outlet holes (46) uniformly arranged on the lower surface (422) of the box body (42); and end plates provided at both ends of the case (42) in a longitudinal direction thereof, the case (42) being closed from the both ends, wherein a width of the case (42) is gradually increased within a predetermined height range from the lower surface (422) in a height direction from the lower surface (422) toward the upper surface (421); the box body (42) is internally provided with a pre-distributor (3). This embodiment is favorable to the evenly distributed of refrigerant to improve the heat transfer effect of evaporimeter.)

1. Refrigerant distributor, characterized in that the refrigerant distributor (4) has:

a case (42);

a refrigerant inlet (41) provided on an upper surface (421) of the case (42);

liquid outlet holes (46) uniformly arranged on the lower surface (422) of the box body (42);

end plates provided at both ends of the box body (42) in the longitudinal direction, the box body (42) being closed from the both ends; and

a pre-distributor (3) disposed inside the box body (42), a length direction of the pre-distributor (3) being parallel to a length direction of the box body (42), the pre-distributor (3) having an inlet (31) for a refrigerant to flow in,

wherein the content of the first and second substances,

the width of the box body (42) is gradually increased within a predetermined height range from the lower surface (422) in a height direction from the lower surface (422) to the upper surface (421) of the box body (41).

2. The refrigerant distributor as claimed in claim 1, further comprising:

a ventilation groove (45) provided on an upper surface (421) of the box body (42); and

a wire mesh separator (47) covering above the ventilation groove (45), the wire mesh separator (47) having an area greater than or equal to the area of the ventilation groove (45).

3. The refrigerant distributor as claimed in claim 1 or 2,

the shape of the box body (42) on the cross section perpendicular to the length direction is octagonal.

4. The refrigerant distributor as claimed in claim 1, further comprising:

a support plate (44) provided inside the case (42) to extend in a width direction of the case (42), the support plate (44) being hermetically connected to the lower surface (422) and a side surface (423) adjacent to the lower surface, the number of the support plates (44) being at least two,

the pre-distributor (3) is supported at an upper end of the support plate (44).

5. The refrigerant distributor as claimed in claim 4,

the upper portion of the support plate (44) has a through hole (441).

6. Refrigerant distributor according to claim 1, characterized in that the pre-distributor (3) has: a distribution box (32), and a cover plate (34) covering the upper part of the distribution box (32),

the inlet (31) is arranged on the cover plate (34),

the distribution box (32) has side walls (321) at both sides in the length direction,

a first predistributor aperture (33) is formed on the side wall (321), the first predistributor aperture (33) being at a distance from the inlet (31) greater than a predetermined threshold,

and, in the height direction, the distance of at least a part of the first predistributor aperture (33) to the bottom of the portion capsule (32) is less than half the height of the portion capsule (32) and greater than zero.

7. The refrigerant distributor as claimed in claim 6,

the area of the cover plate (34) is larger than the area of the bottom of the distribution box (32), and a bent part (341) bent towards the distribution box (32) is formed at the edge of the cover plate (34).

8. The refrigerant distributor as claimed in claim 6,

the distribution box (32) has an octagonal, quadrangular or other figure of straight line sections in a cross section parallel to the cover plate (34).

9. The refrigerant distributor as claimed in claim 1,

the pre-distributor (3a) having a distribution pipe (32a), the inlet (31) being arranged at the top of a pipe wall (321a) of the distribution pipe (32a),

a second predistributor aperture (33a) is formed in the tube wall (321a),

in the height direction, the distance of at least a part of the second predistributor aperture (33a) to the bottom of the distribution pipe (32a) is less than half the height of the distribution pipe (32a) and greater than zero.

10. The refrigerant distributor as claimed in claim 9,

the pre-distributor (3a) further has a second cover plate (34a) arranged at the upper part of the distribution pipe (32a),

the second cover plate (34a) has an area larger than a sectional area of the distribution pipe (32a) parallel to the longitudinal direction.

11. The refrigerant distributor according to claim 6 or 9,

the larger the size and/or the larger the distribution density of the first predistributor aperture (33) or the second predistributor aperture (33a) the closer to the inlet (31).

12. The refrigerant distributor according to claim 6 or 9,

the distribution of the first predistributor apertures (33) or the second predistributor apertures (33a) is asymmetrical with respect to the opening (31) in the length direction.

13. The refrigerant distributor as claimed in claim 12,

the first predistributor apertures (33) or the second predistributor apertures (33a) on one side and the other side of the opening (31) are distributed staggered with respect to the opening (31) in the length direction, centered on the opening (31).

14. Evaporator, characterized in that the evaporator (10) has a refrigerant distributor (4) according to any of claims 1 to 13,

wherein the evaporator (10) further has: an evaporator shell (1), a liquid inlet pipe (2), an air suction port (9) and a heat exchange pipe bundle (5),

the refrigerant distributor (4) is positioned above the heat exchange tube bundle (5),

the liquid inlet pipe (2) is connected to the refrigerant inlet (41) through the evaporator case (1),

the air suction port (9) is arranged at the top of the evaporator shell (1).

15. The evaporator of claim 14,

the evaporator (10) further has:

a heat exchange tube bundle support plate (6) located below the refrigerant distributor (4) to support the heat exchange tube bundle (5);

the side baffle plates (7) are positioned below the refrigerant distributor (4) and positioned at two sides of the heat exchange tube bundle (5);

a mist trap (8) located between the side baffle (7) and the evaporator shell (1) supported by the heat exchanger tube bundle support plate (6).

Technical Field

The application relates to the technical field of air conditioning equipment, in particular to a refrigerant distributor and an evaporator comprising the same.

Background

The refrigeration system mainly comprises a compressor, an evaporator, a condenser and a throttling device, wherein the evaporator structure of the main flow comprises a flooded type evaporator and a falling film type evaporator. With the increasing requirements for energy conservation and environmental protection, the research on water chilling units has been carried out in the direction of high performance and low refrigerant filling amount, and a flooded evaporator cannot effectively control the refrigerant filling amount of the water chilling units on the premise of meeting the high performance. The falling film evaporator is widely applied to a central air-conditioning refrigerating unit, and the heat exchanger has the advantages of small refrigerant filling amount, compact structure, high heat transfer efficiency, small refrigerant filling amount, stable heat exchange and the like.

In the falling film evaporator, a refrigerant distributor is a key component. In order to uniformly distribute the refrigerant to the evaporator tube bundle, a sufficient pressure difference between the inside and the outside of the refrigerant distributor is generally required, for example, in a refrigeration system using a medium-high pressure refrigerant such as R134a, the pressure drop of the distributor is usually more than 60kpa, so that the refrigerant can be uniformly scattered on the heat exchange tube bundle.

Nowadays, in order to meet higher performance and environmental protection requirements at home and abroad, low-pressure refrigerants such as R123, R1233zd and R1233ze are increasingly applied to the air conditioning industry.

Under the typical working condition that the evaporation temperature is 6 ℃ and the condensation temperature is 37 ℃, the pressure difference between the condenser and the evaporator of the low-pressure refrigerant R1233zd (e) is only 23.1 percent of the pressure difference between the condenser and the evaporator of the traditional refrigerant R134 a.

It should be noted that the above background description is only for the sake of clarity and complete description of the technical solutions of the present invention and for the understanding of those skilled in the art. Such solutions are not considered to be known to the person skilled in the art merely because they have been set forth in the background section of the invention.

Disclosure of Invention

The inventor of the application finds that the low-pressure refrigerant is easier to change the phase due to smaller pressure difference, so that the requirements on gas-liquid separation, distribution uniformity and the like of the refrigerant distributor in the falling film evaporator are greatly changed in a heat exchange system using the low-pressure refrigerant. For example: the refrigerant throttled by the throttling device of the heat exchange system has the dryness of about 10-20%, namely the refrigerant entering the liquid inlet pipe of the evaporator is gas-liquid two-phase, particularly for low-pressure refrigerants, the volume fraction of the gaseous refrigerant can account for about 80% of that of the gas-liquid two-phase refrigerant at the inlet, and the existence of the gaseous refrigerant causes the pressure drop in the distributor to be overhigh, thereby generating great influence on the uniform distribution of the refrigerant in the falling film evaporator and further influencing the heat exchange effect of the refrigerant.

The application provides a refrigerant distributor to and contain this refrigerant distributor's evaporimeter, the width of this refrigerant distributor's box body is in the predetermined height within range crescent from the box body bottom, from this, the width of crescent can effectively reduce the velocity of flow of gas-liquid mixture state refrigerant, is favorable to the separation of gaseous state refrigerant and liquid refrigerant, and reduces the pressure drop in the distributor, is favorable to liquid refrigerant by evenly distributed in the distributor.

According to an aspect of the embodiments of the present application, there is provided a refrigerant distributor (4) having: a case (42); a refrigerant inlet (41) provided on an upper surface (421) of the case (42); a liquid outlet hole (46) arranged on the lower surface (422) of the box body (42); and end plates provided at both ends of the case (42) in a longitudinal direction thereof, the case (42) being closed from the both ends, wherein a width of the case (42) is gradually increased within a predetermined height range from a lower surface (422) in a height direction pointing from the lower surface (422) to an upper surface (421). The refrigerant distributor is also provided with a pre-distributor (3) which is arranged inside the box body (42), the length direction of the pre-distributor (3) is parallel to the length direction of the box body (42), and the pre-distributor (3) is provided with an inlet (31) for the refrigerant to flow into.

One of the beneficial effects of this application lies in: the width of the box body of the refrigerant distributor is gradually increased within a preset height range from the bottom of the box body, therefore, the gradually-increased width can effectively reduce the flow velocity of the gaseous refrigerant, separation of the gaseous refrigerant and the liquid refrigerant is facilitated, pressure drop in the distributor is reduced, uniform distribution of the liquid refrigerant in the distributor is facilitated, a pre-distributor is arranged in the box body of the refrigerant distributor, the pre-distributor collides with the inner side wall of the box body to form a rotational flow along the gas-liquid mixed refrigerant jetted from the through holes in the two side walls of the length direction, liquid drops are enabled to fall off from the air flow, and the liquid drops fall back to the bottom of the box body under the action of gravity.

Specific embodiments of the present application are disclosed in detail with reference to the following description and drawings, indicating the manner in which the principles of the application may be employed. It should be understood that the embodiments of the present application are not so limited in scope. The embodiments of the application include many variations, modifications and equivalents within the spirit and scope of the appended claims.

Drawings

The accompanying drawings, which are included to provide a further understanding of the embodiments of the application, are incorporated in and constitute a part of this specification, illustrate embodiments of the application and together with the description serve to explain the principles of the application. It is obvious that the drawings in the following description are only some embodiments of the application, and that for a person skilled in the art, other drawings can be derived from them without inventive effort. In the drawings:

fig. 1 is a schematic perspective view of a refrigerant distributor according to an embodiment of the present application;

FIG. 2a is a schematic view of a cross-section of cassette 42 perpendicular to length direction L;

fig. 2b, 2c, 2d, 2e, 2f, 2g are schematic views of different shapes of the box 42 in a cross section perpendicular to the length direction L, respectively;

fig. 3a, 3b, 3c are schematic views of different shapes of the cartridge body 42 in a cross section perpendicular to the length direction L, respectively;

fig. 4 is another perspective view of the refrigerant distributor according to the embodiment of the present application;

FIG. 5 is a schematic view of the support plate 44 as viewed along the length L;

fig. 6 is another perspective view of the refrigerant distributor according to the embodiment of the present application;

FIG. 7 is a perspective view of the pre-distributor 3 of the present application;

FIG. 8 is a side view of FIG. 7;

FIG. 9 is a top view of FIG. 7;

FIG. 10 is another perspective view of the pre-distributor 3 of an embodiment of the present application;

FIG. 11 is a side view of FIG. 10;

FIG. 12 is a top view of FIG. 11;

FIG. 13 is another perspective view of a pre-dispenser of an embodiment of the present application;

FIG. 14 is a side view of FIG. 13;

FIG. 15 is another perspective view of the pre-distributor 3a of an embodiment of the present application;

FIG. 16 is a side view of FIG. 15;

fig. 17 is a schematic view of the refrigerant flow field distribution in the case 42 according to the present embodiment;

FIG. 18 is a schematic perspective view of an evaporator according to embodiment 2 of the present application;

fig. 19 is a schematic cross-sectional view of fig. 18 taken perpendicular to the length direction.

Detailed Description

The foregoing and other features of the present application will become apparent from the following description, taken in conjunction with the accompanying drawings. In the description and drawings, particular embodiments of the application are disclosed in detail as being indicative of some of the embodiments in which the principles of the application may be employed, it being understood that the application is not limited to the described embodiments, but, on the contrary, is intended to cover all modifications, variations, and equivalents falling within the scope of the appended claims.

In the following description of the present application, for the sake of convenience of description, a direction extending about a central axis of the evaporator case is referred to as an "axial direction", a radial direction about the axis is referred to as a "radial direction", and a circumferential direction about the axis is referred to as a "circumferential direction". A direction directed from the lower surface of the case of the dispenser to the upper surface is referred to as an "upper direction", a direction opposite to the "upper direction" is referred to as a "lower direction", and a side of each member of the refrigerant dispenser and the evaporator directed to the "upper direction" is referred to as an "upper side", and a side opposite to the upper side is referred to as a "lower side". The above definitions of the upper direction, the lower direction, the upper side and the lower side are only for convenience of description, and do not limit the directions of the refrigerant distributor and the evaporator in use.

Example 1

The embodiment of the application provides a refrigerant distributor, and fig. 1 is a schematic perspective view of the refrigerant distributor according to the embodiment of the application.

As shown in fig. 1, the refrigerant distributor 4 includes: a box 42, a refrigerant inlet 41, a liquid outlet 46 and an end plate (not shown in fig. 1).

As shown in fig. 1, the refrigerant inlet 41 is provided on the upper surface 421 of the case 42; the liquid outlet holes 46 are arranged on the lower surface 422 of the box body 42, the liquid outlet holes 46 can be uniformly distributed on the lower surface 422, and each liquid outlet hole 46 penetrates through the lower surface 422, so that the liquid in the box body 42 can flow out from the liquid outlet hole 46 and drip on the surface of the heat exchange tube; the end plates may be disposed at two ends of the box 42 in the length direction L, and seal the two ends of the box 42, so that an accommodating space for accommodating the refrigerant is formed inside the box 42.

In this embodiment, the gas-liquid mixed refrigerant may enter the box 42 through the refrigerant inlet 41, the gas refrigerant and the liquid refrigerant are separated from each other in the box 42, and the liquid refrigerant flows out through the liquid outlet holes 46 of the lower surface 422, thereby distributing the refrigerant.

Fig. 2a is a schematic view of a cross section of the cassette body 42 perpendicular to the length direction L. As shown in fig. 2a, the width D of the box 42 gradually increases over a predetermined height H1 from the lower surface 421 in the height H direction from the lower surface 422 to the upper surface 421. Because the width D of the box 42 is gradually increased, the gradually increased width can effectively reduce the flow rate of the gaseous refrigerant, facilitate the separation of the gaseous refrigerant and the liquid refrigerant, reduce the pressure drop in the distributor, and facilitate the uniform distribution of the liquid refrigerant in the distributor.

In the present embodiment, as shown in fig. 2a, the sectional shape of the box 42 is, for example, an octagon, which has the following advantages: the octagonal shape is narrow at the upper end and the lower end and wide in the middle, two-phase refrigerants enter the box body 42, the space in the box body is large, the speed of a gaseous refrigerant in the middle of the box body is effectively reduced, the liquid refrigerant is more easily separated and settled under the action of gravity, a liquid level is formed at the bottom of the box body, and the gaseous refrigerant carries part of the liquid refrigerant to move upwards; meanwhile, the octagonal shape has large internal space and high height, so that the situation of air suction and liquid carrying when gaseous refrigerants flow can be effectively prevented, and the phenomenon of wave motion of liquid refrigerants in the box under the drive of high-speed fluid can be prevented;

in addition, the octagonal shape has strong inclusion, the eight corners are obtuse angles, the processing is convenient, pre-distributors with various shapes can be arranged in the box body, the shape of the pre-distributors is not limited, the heights of the vertical edges at the two sides of the octagonal shape can be randomly set according to the size and the position of each part in the box body 42, and the size of the upper and lower closing-in openings is not influenced; in addition, when the refrigerant distributor 4 is disposed in the falling film evaporator, the refrigerant distributor 4 may cover as many heat exchange tube bundles as possible due to the wide bottom of the octagonal shape, which is helpful for uniform distribution of the refrigerant on the heat exchange tube bundles.

In the present embodiment, in the octagonal shape shown in fig. 2a, the two side vertical edges are longer, the upper mouth-off is smaller, and the lower mouth-off is larger, which is suitable for the case where the inner parts of the box body 42 are higher. The octagonal shape of the present embodiment is not limited thereto, for example, in the octagonal shape shown in fig. 2b, the vertical sides are shorter, the upper mouth-in is larger, and the lower mouth-in is smaller, or the upper and lower mouth-in of the octagonal shape may be equally large.

In addition, the present embodiment may not be limited thereto, and the shape of the cross section of the box 42 perpendicular to the longitudinal direction L may be other figures composed of straight line segments and/or curved line segments. For example, fig. 2c, 2d, 2e, 2f, 2g are schematic views of different shapes of the box 42 in a cross-section perpendicular to the length direction L, respectively, wherein: in fig. 2c, the cross-section is hexagonal in shape; in fig. 2d, the cross-section has the shape of an inverted trapezoid; in fig. 2e, the cross-section is pentagonal in shape; in fig. 2f, the cross section has a shape with upper and lower straight line segments and left and right curved line segments; in fig. 2g, the cross section has a curved lower end and straight left and right sides and an upper end.

In this embodiment, the lower surface 422 of the cartridge body 42 may be a planar configuration or a non-planar configuration. The non-planar shape is, for example, an arc, an inverted cone, an inverted trapezoid, or the like. Fig. 3a, 3b, and 3c are schematic views of different shapes of the cross section of case 42 perpendicular to longitudinal direction L, and in fig. 3a to 3c, lower ends 301 of the different shapes have different shapes, and the shape of the lower ends corresponds to the shape of lower surface 422. Fig. 3a, 3b, and 3c correspond to the case where the lower surface 422 of the case 42 is curved, inverted conical, or inverted trapezoidal, respectively.

Fig. 4 is another perspective view of the refrigerant distributor according to the embodiment of the present application. Fig. 4 is different from fig. 1 in that the refrigerant distributor 4 of fig. 4 has a ventilation groove 45 and a wire separator 47 in addition to all the structures of the refrigerant distributor 4 of fig. 3.

As shown in fig. 4, the air-permeable groove 45 may be provided on the upper surface 421 of the case body 42; the wire separator 47 may cover the upper side of the ventilation groove 45, and the area of the wire separator 47 is greater than or equal to the area of the ventilation groove 45. Therefore, the gaseous refrigerant in the box body 42 can be discharged from the box body 42 through the ventilation groove 45 and the silk screen separator 47; the wire separator 47 can filter the passing gaseous refrigerant again to filter the liquid refrigerant.

Since the refrigerant distributor 4 of fig. 4 has the ventilation grooves 45, the lower surface of the case 42 cannot be formed in a non-planar shape but in a planar shape. Due to the existence of the ventilation grooves, the pressure inside and outside the box body 42 is the same, and the liquid refrigerant is subjected to the action of gravity, so that the liquid level in the box body 42 is freely adjusted, therefore, the bottom surface of the box body 42 is in a planar shape, and the uniform flow rate of the fluid flowing out of the liquid outlet hole at the bottom of the box body 42 can be ensured.

As shown in fig. 4, the refrigerant distributor 4 may further include: a support plate 44. The support plate 44 may be disposed inside the case 42 to extend in the width direction of the case 42, and the support plate 44 is hermetically coupled to the lower surface 422 and the side surface 423 adjacent to the lower surface 422. For example, the support plate 44 may be hermetically connected to the lower surface 422 and the side surface 423 by full-welding. The number of the supporting plates 44 may be 2 or more, and may be uniformly arranged along the length direction of the distribution box.

Fig. 5 is a schematic view of the support plate 44 as viewed in the direction of the length L. As shown in fig. 5, the upper portion of the support plate 44 is formed with a through hole 441. Wherein, the upper portion of the support plate 44 may refer to a portion of the support plate 44 having a height greater than a predetermined value, which may be, for example, half the height of the support plate 44.

Due to the supporting plate 44, under the condition that the refrigerant distributor 4 is installed obliquely, the supporting plate 44 can prevent the refrigerant from flowing on the lower surface 422 of the box body 42, so that the liquid level of the liquid refrigerant is prevented from being seriously inclined, and the phenomenon that the liquid is seriously dried locally on the lower surface 422 is avoided. In addition, under the condition that the liquid level of the lower surface 422 has a certain height, the liquid refrigerant can flow through the through holes 441 on the supporting plate 44, and the liquidity of the liquid refrigerant is ensured.

The supporting plate 44 shown in fig. 4 may be provided in the refrigerant distributor 4 of fig. 1, and the above description of the supporting plate 44 is also applicable to the case where the supporting plate 44 is provided in the refrigerant distributor 4 of fig. 1.

In this embodiment, the refrigerant distributor 4 may further include a pre-distributor. In the following, a pre-distributor is provided in the refrigerant distributor 4 of fig. 4 as an example, and the same description applies to the case where a pre-distributor is provided in the refrigerant distributor 4 of fig. 1.

Fig. 6 is another perspective view of the refrigerant distributor according to the embodiment of the present application. As shown in fig. 6, the refrigerant distributor 4 may further include: a pre-dispenser 3. The predistributor 3 is disposed inside the case 42, supported by the upper end of the support plate 44, and the longitudinal direction of the predistributor 3 is parallel to the longitudinal direction L of the case 42. The predistributor 3 has an inlet 31 for the inflow of refrigerant.

FIG. 7 is a schematic perspective view of the pre-distributor 3 of the present application, FIG. 8 is a side view of FIG. 7, and FIG. 9 is a top view of FIG. 7.

As shown in fig. 7, the pre-dispenser 3 may be box-shaped. The pre-dispenser 3 may have: a dispenser box 32, and a cover plate 34 covering an upper portion of the dispenser box 32. The inlet 31 for the inflow of the refrigerant may be provided to the cover plate 34, for example, the inlet 31 may be provided to a central position of a dimension of the cover plate 34 in a length direction.

As shown in fig. 7, the distributor box 32 has side walls 321 on both sides in the longitudinal direction, and a first pre-distributor hole 33 is formed in the side walls 321. The number of first predistributor apertures 33 may be plural.

As shown in FIG. 7, the first predistributor aperture 33 may be spaced from the inlet 31 by a distance greater than a predetermined threshold, thereby avoiding the formation of the first predistributor aperture 33 in the vicinity of the inlet 31. Since the flow rate of the refrigerant near the inlet 31 is high, the first predistributor opening 33 is formed to avoid the vicinity of the inlet 31, which is advantageous for uniform distribution of the liquid refrigerant in the distributor box 32.

As shown in fig. 7, the shape of the first predistributor aperture 33 is circular, but the embodiment is not limited thereto, and the first predistributor aperture 33 may also be other shapes, such as polygonal, elliptical, and the like.

In this embodiment, the cover plate 34 is sealingly connected to the distribution box 32. As shown in fig. 7, the cover plate 34 has an area larger than that of the bottom of the distribution box 32. The shape of the lid 34 may be the same as or different from the shape of the bottom of the distribution box 32.

In the present embodiment, the edge of the lid plate 34 is formed with a bent portion 341 bent toward the distribution box 32. The cover plate 34 can facilitate the liquid refrigerant to flow out of the first pre-distributor opening 33 without being influenced by the upward airflow; in addition, the bent portion 341 facilitates the liquid refrigerant collected on the surface of the cover plate 34 to flow down.

As shown in fig. 7 and 8, in the height direction, the distance of at least a portion of the first pre-dispenser aperture 33 to the bottom of the portion box 32 is less than half the height of the portion box 32 and greater than zero. That is, at least a portion of first predistributor aperture 33 is disposed on a lower half of sidewall 321. This facilitates the flow of the liquid refrigerant out of the first predistributor opening 33. Further, the location of the first predistributor aperture 33 may not be limited to such an arrangement.

In this embodiment, when the sectional shape of the box 42 of the refrigerant distributor 4 is an octagon, at least a part of the opening 33 of the first pre-distributor may be located within the height range of the vertical edges at both sides of the octagon in the height direction, so that the gas-liquid mixed refrigerant jetted from the through holes on the two side walls of the pre-distributor in the length direction collides with the inner side wall of the box 42, and two upper and lower rotational flows may be formed in the box 42, so as to promote the liquid drops to fall off from the air flow and fall back to the bottom of the box 42 under the action of gravity, thereby facilitating the refrigerant to fully perform gas-liquid separation.

In the present embodiment, as shown in fig. 8, the closer to the inlet 31, the larger the size and/or the higher the distribution density of the first predistributor holes 33 are, thereby making the flow velocity of the liquid refrigerant uniform in each first predistributor hole 33.

In the present embodiment, as shown in fig. 8, the distribution of the first predistributor apertures 33 is asymmetric with respect to the opening 31 in the longitudinal direction L, that is, in fig. 8, the plurality of first predistributor apertures 33 on the right and left sides of the opening 31 are asymmetrically distributed. For example, in the length direction L, the first predistributor apertures 33 on one side (e.g., left side) and the other side (e.g., right side) of the opening 31 may be staggered with respect to the opening 31, centered on the opening 31.

In the present embodiment, as shown in fig. 9, the distribution box 32 is octagonal in shape in a cross section parallel to the lid plate 34.

FIG. 10 is another perspective view of the pre-dispenser 3 of an embodiment of the present application, FIG. 11 is a side view of FIG. 10, and FIG. 12 is a top view of FIG. 11.

As shown in fig. 10 and 12, the portion box 32 of the predispenser 3 has a quadrangular shape in a section parallel to the cover plate 34. In addition, the present embodiment is not limited thereto, and the shape of the distribution box 32 of the predispenser 3 in a cross section parallel to the cover plate 34 may be other patterns composed of straight line segments.

As shown in fig. 10 and 11, the first predistributor aperture 33 of predistributor 3 is elongated in shape.

In a variation of this embodiment, the predistributor may be cylindrical.

Fig. 13 is another perspective view of a pre-dispenser of an embodiment of the present application, and fig. 14 is a side view of fig. 13.

As shown in fig. 13, the pre-distributor 3a has a distribution pipe 32 a. The inlet 31 may be disposed at the top of the pipe wall 321a of the distribution pipe 32 a; tube wall 321a may have a second predistributor aperture 33a formed therein.

In the height direction, the distance of at least a portion of the second pre-distributor aperture 33a to the bottom of the distribution pipe 32a is less than half the height of the distribution pipe 32a and greater than zero. That is, at least a portion of second predistributor aperture 33a is disposed in a lower half of sidewall wall 321 a. This facilitates the flow of the liquid refrigerant out of the second predistributor opening 33 a. Further, the position of the second predistributor aperture 33a may not be limited to such an arrangement.

As shown in fig. 13 and 14, the shape of the second predistributor opening 33a is circular, but the embodiment is not limited thereto, and the second predistributor opening 33a may have other shapes, such as a polygon, an ellipse, and the like.

In the present embodiment, the closer to the inlet 31, the larger the size and/or the higher the distribution density of the second predistributor holes 33a, thereby making the flow velocity of the liquid refrigerant uniform in each of the second predistributor holes 33 a.

In the present embodiment, the distribution of the second predistributor apertures 33a may be asymmetric with respect to the opening 31 in the length direction L, that is, the plurality of second predistributor apertures 33a on the left and right sides of the opening 31 in fig. 14 may be asymmetrically distributed. For example, in the length direction L, the second predistributor apertures 33a on one side (e.g., left side) and the other side (e.g., right side) of the opening 31 may be staggered with respect to the opening 31, centering on the opening 31.

FIG. 15 is another perspective view of a pre-dispenser 3a of an embodiment of the present application, and FIG. 16 is a side view of FIG. 15.

Fig. 15 differs from fig. 13 in that the predispenser 3a of fig. 15 also has a second cover plate 34 a. The second cover plate 34a is disposed above the distribution pipe 32a, and the area of the second cover plate 34a is larger than the cross-sectional area of the distribution pipe 32a parallel to the longitudinal direction L. The second cover plate 34a can facilitate the liquid refrigerant flowing out of the second predistributor opening 33a to be free from the upward air flow.

In addition, the second cover plate 34a may have a bent structure inclined with respect to the height direction, and the bent structure facilitates the liquid refrigerant collected on the surface of the second cover plate 34a to flow down.

In addition, reference may be made to the description relating to fig. 13 and 14 with regard to the description of the second predistributor aperture 33a in the predistributor 3a of fig. 15 and 16.

In fig. 13, 14, 15, and 16, the distance between the second predistributor opening 33a and the inlet 31 may be greater than a predetermined threshold value, so that the formation of the second predistributor opening 33a in the vicinity of the inlet 31 can be avoided.

According to the embodiment, when the pre-distributor 3 is not disposed in the box 42 of the refrigerant distributor 4, the gas-liquid mixed refrigerant enters the box 42 through the refrigerant inlet 41, and the width of the box 42 is gradually increased, so that the flow rate of the gaseous refrigerant is effectively reduced, the separation of the gaseous refrigerant and the liquid refrigerant is facilitated, the pressure drop in the distributor is reduced, and the liquid refrigerant is uniformly distributed in the distributor. The liquid refrigerant in the box 42 flows out through the liquid outlet holes 46 on the lower surface 422 of the box 42.

In the case where the pre-distributor 3 is provided in the case 42 of the refrigerant distributor 4, the gas-liquid mixed refrigerant is introduced into the interior of the pre-distributor 3 (or 3a) through a liquid inlet pipe connected to the inlet 31 of the pre-distributor 3 (or 3a) through the upper surface 421 of the case 42 from the refrigerant inlet 41. The mixed refrigerant is distributed in the pre-distributor 3 or (3a) along the length direction, and the mixed refrigerant which is preliminarily and uniformly distributed along the length direction flows out of the pre-distributor 3 or (3a) from the first pre-distributor open pore 33 (or the second pre-distributor open pore 33a) and enters the box body 42; the refrigerant in the box body 42 is subjected to gas-liquid separation, and because the width of the box body 42 is gradually increased, the flow rate of the gaseous refrigerant is effectively reduced, the separation of the gaseous refrigerant and the liquid refrigerant is facilitated, the pressure drop in the distributor is reduced, and the uniform distribution of the liquid refrigerant in the distributor is facilitated. Meanwhile, gas-liquid mixed refrigerant jetted from through holes 33a on two side walls in the length direction of the pre-distributor 3 collides with the inner side wall of the box body to form rotational flow, so that liquid drops are promoted to fall off from the gas flow and fall back to the bottom of the box body under the action of gravity; the liquid refrigerant in the box 42 flows out through the liquid outlet holes 46 on the lower surface 422 of the box 42.

Fig. 17 is a schematic view of the flow field distribution of the refrigerant in the case 42 according to the present embodiment. As shown in fig. 17, in the case that the sectional shape of the box 42 of the refrigerant distributor 4 is an octagon (for example, an octagon as shown in fig. 2a), at least a part of the first predistributor opening 33 or the second predistributor opening 33a may be located within the height range of the vertical sides 171 and 172 of the octagon in the height H direction.

As shown in fig. 17, when the high-speed gas-liquid mixed refrigerant flows out of the first predistributor opening 33 or the second predistributor opening 33a of the predistributor 3 or 3a, the refrigerant collides with the octagonal vertical walls 171 and 172 on both sides and is guided by the inclined surfaces on the upper and lower sides to form two upper and lower swirling flows 17a and 17 b. In the rotational flows 17a and 17b formed by the gas-liquid mixed refrigerant, the movement direction of the gaseous refrigerant is changed sharply, and the liquid refrigerant has a large droplet mass, a large inertia, and a large gravity, and thus easily drops off from the gaseous refrigerant and flows to the bottom of the case 42 along the vertical edges 171 and 172 on both sides, thereby improving the gas-liquid separation effect of the refrigerant.

In addition, due to the existence of the upper rotational flow 17a and the lower rotational flow 17b, the gas-liquid mixed refrigerant stays in the box body 42 for a longer time, and refrigerant liquid drops carried by high-speed airflow are easier to fall back to the bottom of the box body under the action of inertia and gravity and are difficult to flow out of a ventilation groove in the upper part of the box body 42, so that the risk of sucking air and carrying liquid is reduced.

Example 2

An embodiment 2 of the present application provides an evaporator, which includes the refrigerant distributor according to embodiment 1.

Fig. 18 is a schematic perspective view of an evaporator according to embodiment 2 of the present application, and fig. 19 is a schematic sectional view of fig. 18 perpendicular to the longitudinal direction, the evaporator being, for example, a falling film evaporator.

As shown in fig. 18 and 19, the evaporator 10 includes: refrigerant distributor 4, evaporator shell 1, liquid inlet pipe 2, suction port 9 and heat exchange tube bundle 5.

As shown in fig. 18 and 19, the liquid inlet pipe 2 is connected to the refrigerant inlet 41 through the evaporator case 1, for example: the liquid inlet pipe 2 penetrates through the evaporator shell 1 to enter the refrigerant distributor 4, is connected with an inlet 31 of the pre-distributor 3 in the refrigerant distributor 4, and injects the refrigerant into the pre-distributor 3; alternatively, in the absence of the pre-distributor 3, the inlet pipe 2 passes through the evaporator housing 1 into the refrigerant distributor 4, injecting refrigerant into the box 42 of the refrigerant distributor 4.

As shown in fig. 18 and 19, the refrigerant distributor 4 is located above the heat exchange tube bundle 5, and the liquid refrigerant flowing out of the refrigerant distributor 4 flows onto the heat exchange tube bundle 5 to exchange heat with the heat exchange tube bundle.

As shown in fig. 18 and 19, the suction port 9 is provided at the top of the evaporator case 1, and the gaseous refrigerant in the evaporator case 1 is discharged through the suction port 9. The suction port 9 may be connected to a supplementary port of a compressor, for example.

As shown in fig. 18 and 19, the evaporator 10 further includes: a heat exchange tube bundle support plate 6, a side baffle 7 and a mist catcher 8.

In this embodiment, a heat exchange tube bundle support plate 6 may be located below the refrigerant distributor 4 for supporting the heat exchange tube bundle 5, e.g., the heat exchange tube bundle 5 passes through the heat exchange tube bundle support plate 6. The side baffles 7 may be located below the refrigerant distributor 4 and on either side of the heat exchange tube bundle 5. The mist trap 8 is located between the side barrier 7 and the evaporator shell 1 in the width direction and is supported by the heat exchanger tube bundle support plate 6 in the height direction, wherein the mist trap 8 may be a wire mesh separator, for example.

In the present embodiment, as shown in fig. 18 and 19, the gas-liquid mixed refrigerant enters the refrigerant distributor 4 through the liquid inlet pipe 2, the gas-liquid mixed refrigerant is subjected to gas-liquid separation in the refrigerant distributor 4, the gas-liquid mixed refrigerant flows out from the air permeable groove 45 and the wire mesh separator 47 at the top of the box body 42 of the refrigerant distributor 4 after being separated, and the liquid refrigerant falls into the lower surface 422 (not shown in fig. 18 and 19) of the box body 42 under the action of gravity, is uniformly distributed from the liquid outlet holes 46 (not shown in fig. 18 and 19), and flows out to the outside of the heat exchange tube bundle 5 for membrane heat exchange. The gaseous refrigerant generated by heat exchange evaporation carries with part of liquid drops, flows through a channel between the side baffle 7 and the evaporator shell 1, interacts with the mist catcher 8 which is arranged on the heat exchange tube bundle supporting plate 6 and is positioned between the side baffle 7 and the evaporator shell 1, the liquid refrigerant carried with the gaseous refrigerant is filtered, and finally, the gaseous refrigerant generated by heat exchange in the evaporator and the gaseous refrigerant flowing out of the ventilating groove 45 of the distributor 4 and the wire mesh separator 47 flow out of the air suction port 9 of the evaporator under the suction action of the compressor.

In fig. 19, the gaseous refrigerant generated by heat exchange in the evaporator is indicated by a broken arrow a1, and the gaseous refrigerant flowing out of the ventilation grooves 45 and the wire separator 47 of the distributor 4 is indicated by a broken arrow a 2. As shown in fig. 19, the gas flow paths of the gaseous refrigerant indicated by the broken line arrow a1 and the broken line arrow a2 do not interfere with each other, and the gas-liquid separation effect is improved by the discharge of the gas.

In this embodiment, owing to adopted the refrigerant distributor of this application, the liquid refrigerant can be distributed to the heat exchanger tube bank more evenly, therefore the heat exchange efficiency of this evaporimeter improves.

The evaporator of this embodiment can be used in heat transfer system to, owing to adopted the evaporator of this embodiment, this heat transfer system's heat exchange efficiency improves, and can the effective control evaporimeter take liquid risk of breathing in, be favorable to the use of low pressure refrigerant in heat transfer system.

The present application has been described in conjunction with specific embodiments, but it should be understood by those skilled in the art that these descriptions are intended to be illustrative, and not limiting. Various modifications and adaptations of the present application may occur to those skilled in the art based on the spirit and principles of the application and are within the scope of the application.