CN218544891U

CN218544891U - Liquid distributor, heat exchanger and air conditioner

Info

Publication number: CN218544891U
Application number: CN202222746059.8U
Authority: CN
Inventors: 游浩亮; 王小勇; 胡海利; 胡东兵
Original assignee: Gree Electric Appliances Inc of Zhuhai
Current assignee: Gree Electric Appliances Inc of Zhuhai
Priority date: 2022-10-18
Filing date: 2022-10-18
Publication date: 2023-02-28
Anticipated expiration: 2032-10-18

Abstract

The utility model discloses a liquid distributor, heat exchanger and air conditioner, wherein, the liquid distributor includes: the top plate is provided with a liquid inlet; the two side plates are oppositely arranged and connected with the top plate; the sealing plates are connected to the side plates, a liquid inlet channel is defined by the top plate, the two side plates and the sealing plates, and the sealing plates are provided with overflowing holes; the liquid inlet channel is communicated with the liquid inlet and the overflowing hole; along the direction from the liquid inlet to the overflowing hole, the overflowing area of the liquid inlet channel is gradually increased. The utility model provides a liquid distributor, heat exchanger and air conditioner have solved effectively that the liquid distributor occupation space in the heat exchanger is great among the prior art, have arranged the restriction to the inside heat exchange tube of heat exchanger, have reduced the problem of the efficiency of heat exchanger.

Description

Liquid distributor, heat exchanger and air conditioner

Technical Field

The utility model relates to a refrigeration technology field particularly, relates to a liquid distributor, heat exchanger and air conditioner.

Background

In recent years, with the high-speed promotion of urbanization in China, the urban space value is higher and higher, and under the condition of limited space, the occupied space of the air conditioning unit is continuously reduced, and the air conditioner with smaller occupied space has higher market competitiveness.

The evaporator is one of the core components of the commercial machine, the heat exchange capacity of the evaporator directly influences the capacity and the energy efficiency of the air conditioning unit, and the appearance of the evaporator also directly determines the appearance size of the air conditioning unit. The evaporator of the commercial air conditioning unit mainly has three structural forms of a falling film type, a flooded type and a dry type, wherein the falling film type evaporator has the advantages of good heat exchange performance, small refrigerant filling amount and the like, and is widely applied to machine types such as a water cooling screw rod, an air cooling screw rod, a centrifugal machine and the like at present. The liquid distributor of the falling film evaporator is of a rectangular porous plate structure, occupies a large space in the shell of the evaporator, and limits the internal heat exchange tubes to a certain extent. Simultaneously for flooded and dry-type evaporators, falling film evaporator structure is comparatively complicated, needs to optimize falling film evaporator structure urgently, promotes falling film evaporator processing and assembly efficiency.

Referring to fig. 5, in the existing falling film evaporator of the prior art, the inner space of the shell 11' is limited, while the liquid distributor 12' of the prior art is of a rectangular porous plate structure, and the liquid distributor of the rectangular porous plate structure needs to be hung inside by connecting pieces, so that it can be seen that the occupied space of the liquid distributor is large, which causes great limitation on the arrangement mode and the arrangement number of the heat exchangers 13' inside the evaporator, which directly affects the energy efficiency of the evaporator.

In conclusion, in the prior art, the liquid distributor in the heat exchanger occupies a large space, and has a limiting effect on the arrangement of the heat exchange tubes in the heat exchanger, so that the energy efficiency of the heat exchanger is reduced.

SUMMERY OF THE UTILITY MODEL

The embodiment of the utility model provides an in the embodiment provide a liquid distributor, heat exchanger and air conditioner to it is great to solve the liquid distributor occupation space in the heat exchanger among the prior art, has arranged the restriction to the heat exchange tube of heat exchanger inside, has reduced the problem of the efficiency of heat exchanger.

In order to achieve the above object, the utility model provides a liquid distributor, include: the top plate is provided with a liquid inlet; the two side plates are oppositely arranged and connected with the top plate; the sealing plates are connected to the side plates, a liquid inlet channel is defined by the top plate, the two side plates and the sealing plates, and the sealing plates are provided with overflowing holes; the liquid inlet channel is communicated with the liquid inlet and the overflowing hole; along the direction from the liquid inlet to the overflowing hole, the overflowing area of the liquid inlet channel is gradually increased; the side plates and the seal plates are positioned through rivets and are fixedly connected.

Furthermore, the bending angle formed between the side plate and the top plate is 120-150 degrees.

Furthermore, the cross section of the liquid inlet channel is trapezoidal, the top plate is located at the upper bottom of the trapezoid, and the sealing plate is located at the lower bottom of the trapezoid.

Further, still include: the liquid homogenizing plate is arranged in the liquid inlet channel and is provided with liquid homogenizing holes.

Further, the liquid inlet channel is divided into a first cavity and a second cavity by the liquid equalizing plate; the first cavity is communicated with the liquid inlet and the second cavity through the liquid equalizing hole; the second chamber is in communication with the flowthrough orifice.

Further, the side plate is provided with a folding edge which extends away from the liquid inlet channel, and the folding edge is provided with an auxiliary overflowing hole.

Further, the sum of the areas of all the auxiliary overflowing holes is equal to 50% -80% of the area of the folded edge.

Furthermore, connecting plates are arranged at two ends of the sealing plate and are parallel to the side plates, the side plates are positioned by rivets, and the connecting plates are fixedly connected with the side plates by spot welding or intermittent welding.

According to another aspect of the present invention, a heat exchanger is provided, which comprises the above liquid distributor.

Further, the heat exchanger includes the casing, and the inside heat exchange tube that is provided with of casing, the setting of liquid distributor is inside the casing.

Furthermore, the side plate is provided with a folded edge extending away from the liquid inlet channel, and the folded edge is provided with an auxiliary overflowing hole; the folded edge is connected with the inner wall of the shell.

Furthermore, the heat exchanger is provided with an air suction port, a first area is arranged at the position, corresponding to the air suction port, of the folded edge, the number of the auxiliary overflowing holes is multiple, at least part of the auxiliary overflowing holes are located in the first area, and the diameter of the auxiliary overflowing holes located in the first area is smaller than that of the auxiliary overflowing holes located outside the first area.

Further, the heat exchanger is a falling film evaporator.

Further, the relationship between the cross-sectional area of the liquid distributor and the cold energy of the falling film evaporator is as follows: s1=0.0006x +1, s2=0.00022x +1.0065, s1 is less than or equal to s2; s is the cross-sectional area of the liquid distributor in m ² (ii) a x is the cold energy of the falling film evaporator and unit RT.

Furthermore, the cross section of the liquid inlet channel is trapezoidal, the top plate is positioned at the upper bottom of the trapezoid, and the sealing plate is positioned at the lower bottom of the trapezoid;

the width of the sealing plate is W1, and the unit is mm; the tube distribution width of the heat exchange tube is W2, and the unit is mm; w1 is more than or equal to W2+6mm.

Further, the distance between the top plate and the sealing plate is H, and the unit is mm; w1 x 20% or more and H1 x 40% or less.

Further, the liquid distributor also comprises a liquid homogenizing plate, the liquid homogenizing plate is arranged in the liquid inlet channel, and liquid homogenizing holes are formed in the liquid homogenizing plate; the length of the liquid homogenizing plate is L2, and the unit is mm; the length of the sealing plate is L, and the unit is mm; l2= L-100mm.

Further, the liquid inlet channel is divided into a first cavity and a second cavity by the liquid equalizing plate; the first cavity is communicated with the liquid inlet and the second cavity through the liquid equalizing hole; the second chamber is communicated with the overflowing hole; the height of the first chamber is H1, and the unit is mm; the distance between the top plate and the sealing plate is H, and the unit is mm; h1= H × 50%, H1 ≧ 15mm.

Further, the sum of the flow areas of all the auxiliary flow holes is s3; the heat exchanger is provided with an air outlet, and the diameter of the air outlet is s4; s3 is more than or equal to s4.

Further, the width of the folded edge extending away from the liquid inlet channel is L1, and the unit is mm; the bending angle formed between the side plate and the top plate is alpha 1; the diameter of the heat exchange tube is d1, and the unit is mm; l1 ≧ (d 1 × 1.21+ 10mm) ÷ sin (180 ° - α 1).

According to another aspect of the present invention, an air conditioner is provided, which includes the above-mentioned heat exchanger.

The utility model discloses a liquid distributor regards roof, curb plate and shrouding as major structure. Wherein, this one side of roof that has the inlet, whole narrower and inlet channel's the surface of overflowing is less, and this one side of shrouding that has the discharge orifice, whole broad and inlet channel overflow great. The liquid distributor is wholly in a shape with a narrow top and a wide bottom, when the liquid distributor in the shape is placed inside a shell of a heat exchanger, a narrow top plate can be closer to the inner wall of the shell, and the whole shape with the narrow top and the wide bottom is also more attached to the top space inside the shell of the heat exchanger. Therefore, the space occupied by the liquid distributor in the heat exchanger is reduced, and the saved space can be used for arranging more heat exchange tubes. Moreover, more spaces can be used for the heat exchange tubes to carry out optimal arrangement, so that the refrigerant can achieve the optimal efficiency of heat exchange when passing through the heat exchange tubes, and the energy efficiency of the heat exchanger is effectively improved. Moreover, the curb plate compresses tightly the back with the shrouding assembly, fixes a position the tensioning through the rivet with curb plate and shrouding earlier, and form fixed connection such as welding again can effectively guarantee the joint strength of curb plate through this scheme. The side plates and the sealing plates are fixedly connected and sealed, so that the whole sealing in a cavity formed by the upper cover plate and the sealing plates is achieved.

Drawings

Fig. 1 is a schematic view of the internal structure of a liquid distributor according to an embodiment of the present invention;

FIG. 2 is an exploded view of the liquid distributor according to the embodiment of the present invention;

fig. 3 is a perspective view illustrating the structure of a liquid distributor according to an embodiment of the present invention;

FIG. 4 is an exploded perspective view of the liquid distributor according to the embodiment of the present invention;

FIG. 5 is a schematic view of the internal structure of a heat exchanger according to the prior art;

fig. 6 is a schematic view of the internal structure of the heat exchanger according to the embodiment of the present invention;

fig. 7 is a partial schematic structural view of a heat exchanger according to an embodiment of the present invention.

Detailed Description

The present invention will be described in further detail with reference to the following drawings and specific examples, which should not be construed as limiting the invention.

Referring to fig. 1 to 4, according to an embodiment of the present invention, a liquid distributor is provided, which includes a top plate 10, two side plates 20 and a sealing plate 30, wherein the top plate 10 is provided with a liquid inlet 11, and the two side plates 20 are oppositely disposed and connected to the top plate 10; the sealing plate 30 is connected to the side plates 20, a liquid inlet channel 40 is defined by the top plate 10, the two side plates 20 and the sealing plate 30, and an overflowing hole 31 is formed in the sealing plate 30; the liquid inlet channel 40 is communicated with the liquid inlet 11, and the liquid inlet channel 40 is communicated with the overflowing hole 31. Along the direction from the liquid inlet 11 to the overflowing hole 31, the overflowing area of the liquid inlet channel 40 is gradually increased, the side plate 20 and the sealing plate 30 are positioned through rivets, and the side plate 20 is fixedly connected with the sealing plate 30.

The liquid distributor of the utility model takes the top plate, the side plate and the sealing plate as the main structure. The side of the top plate having the liquid inlet is narrow and the flow surface of the liquid inlet channel 40 is small, and the side of the sealing plate having the flow holes 31 is wide and the flow of the liquid inlet channel 40 is large. The liquid distributor is integrally in a shape with a narrow top and a wide bottom, when the liquid distributor in the shape is placed in a shell of a heat exchanger (an evaporator), a narrow top plate can be closer to the inner wall of the shell, and the overall shape with the narrow top and the wide bottom is more attached to the top space inside the shell of the heat exchanger, which is shown in fig. 6. Therefore, the space occupied by the liquid distributor in the heat exchanger is reduced, and the saved space can be used for arranging more heat exchange tubes. Moreover, more spaces can be used for the heat exchange tubes to carry out optimal arrangement, so that the refrigerant can achieve the optimal efficiency of heat exchange when passing through the heat exchange tubes, and the energy efficiency of the heat exchanger is effectively improved. Moreover, the curb plate compresses tightly the back with the shrouding assembly, fixes a position the tensioning with curb plate and shrouding through the rivet earlier, and form fixed connection such as welding again can effectively guarantee the joint strength of curb plate by this scheme. The side plates are fixedly connected with the sealing plate in a sealing manner, so that the cavity formed by the upper cover plate and the sealing plate is internally and integrally sealed.

Preferably, referring to fig. 2, a bending angle α 1 formed between the side panel 20 and the top panel 10 is 120 ° to 150 °. The size of the bending angle alpha 1 between the side plate 20 and the top plate 10 determines the overall shape of the liquid distributor, the specific angle setting can be adjusted according to the size and shape of the heat exchanger, when the bending angle alpha 1 is within the range, the liquid distributing effect of the liquid distributor is best and the occupied space is minimum, and under the condition that the inner space of the heat exchanger is limited, the energy efficiency of the heat exchanger is improved to the maximum extent. The side plate 20 and the top plate 10 are of an integrally formed structure and can also be connected in a welding way; the side plates are positioned at two ends of the top plate and connected with the top plate, and the side plates and the top plate jointly form an upper cover plate structure of the liquid distributor. The top of the upper cover plate structure is provided with a liquid baffle plate, which can be seen from the corresponding structures shown in fig. 2 and fig. 3, and the liquid baffle plate is positioned at two ends of the upper cover plate structure in the length direction.

Preferably, the cross section of the liquid inlet channel 40 is trapezoid, the top plate 10 is located at the upper bottom position of the trapezoid, and the sealing plate 30 is located at the lower bottom position of the trapezoid. Because the refrigerant that gets into the liquid distributor is vapour-liquid coexistence attitude, the inlet channel that the cross section personally submits trapezoidal can reduce the influence of gas to liquid refrigerant liquid distribution, promotes the equal liquid effect of liquid distributor. Wherein, the effect of controlling the trapezoidal folding angle alpha 2 between 30 and 60 degrees is better.

Note that the trapezoidal folding angle α 2 is a base angle in the trapezoid. The sealing plate 30 main body is a flat plate structure, the sealing plate 30 and the side plate 20 are welded through a connecting plate, the connecting plate is parallel to the side plate and attached to the side plate, and the connecting plate can be welded with the sealing plate or integrally formed. In fig. 2, a trapezoidal folding angle α 2 is formed between the sealing plate and the connecting plate. The two ends of the sealing plate 30 are provided with connecting plates 32, the connecting plates 32 are parallel to the side plates 20, the side plates 20 are positioned with the connecting plates 32 through rivets, and the connecting plates 32 are fixedly connected with the side plates 20 through spot welding or intermittent welding. The purpose that sets up like this makes things convenient for shrouding 30 and 20 rivet locations with the curb plate, spot welding or intermittent welding can avoid the shrouding full weld to connect the deformation that leads to moreover, and the welding work volume is little, has promoted production efficiency effectively.

The liquid distributor further comprises a liquid equalizing plate 50, the liquid equalizing plate 50 is arranged in the liquid inlet channel 40, and liquid equalizing holes are formed in the liquid equalizing plate 50. The liquid equalizing plate 50 is arranged in the liquid inlet channel for equalizing liquid, and the liquid equalizing effect of the liquid distributor is improved.

As shown in fig. 1, fig. 2 and fig. 4, the liquid homogenizing plate 50 divides the liquid inlet channel 40 into a first chamber 41 and a second chamber 42; the first cavity 41 is communicated with the liquid inlet 11, and the first cavity 41 is communicated with the second cavity 42 through a liquid equalizing hole; the second chamber 42 communicates with the overflow aperture 31. After the gas-liquid coexisting refrigerant subjected to throttling flows in from the liquid inlet, the gas-liquid coexisting refrigerant enters the first cavity firstly, then the first liquid equalizing of the liquid refrigerant is realized through the liquid equalizing plate, the first liquid equalizing flows into the second cavity from the liquid equalizing hole of the liquid equalizing plate, and the second liquid equalizing is realized through the overflowing hole in the sealing plate.

The shape of the liquid-equalizing plate 50 is not particularly limited, the shape of the liquid-equalizing plate 50 can be set according to the shapes of the top plate and the side plates, and the number of liquid-equalizing holes in the liquid-equalizing plate can be adjusted according to actual needs. In the present embodiment shown in the drawings, the liquid-uniforming plate 50 has the following specific shape: the bottom of the liquid homogenizing plate is provided with the liquid homogenizing hole, the top of the liquid homogenizing plate is provided with a rectangular notch, the rectangular notch is aligned to the top of the liquid homogenizing plate as much as possible, and the sectional area of the first cavity in the width direction of the liquid distributor is not less than 0.5 time of the flow area of the liquid inlet; the cross-sectional area of the rectangular gap is not less than 2 times of the liquid inlet flow area.

The side plate 20 is provided with a folding edge 21 extending away from the liquid inlet channel 40, and the folding edge 21 is provided with an auxiliary overflowing hole 21a. Referring to fig. 1 and 2, the folded edge 21 extends outwards, and the top plate, the side plate and the folded edge on the side plate are integrally in a structure like a Chinese character ji or a structure like a Chinese character pi. The auxiliary overflowing hole 21a is used for the gaseous refrigerant to pass through, and the air-conditioning unit can be effectively prevented from sucking air and carrying liquid.

Further, the sum of the areas of all the auxiliary overflowing holes 21a is equal to 50% -80% of the area of the folded edge 21. The area of the auxiliary overflowing hole 21a is set, so that air suction and liquid entrainment can be further prevented.

The side plates 20 and the sealing plate 30 are positioned by rivets, and the side plates 20 and the sealing plate 30 are fixedly connected. In this embodiment, the sealing plate 30 main part is the flat plate structure, and through connecting plate welding between sealing plate 30 and the curb plate 20, the connecting plate is parallel with the curb plate and pastes on the curb plate, and the connecting plate can be with sealing plate welding or integrated into one piece, and specific structure refers to fig. 2. For making curb plate and connecting plate laminating inseparabler, open waist shape rivet hole and rectangular welding groove on the curb plate, the curb plate compresses tightly the back with the shrouding assembly, fixes a position earlier through self-plugging rivet with curb plate and shrouding taut, again through welding form reinforced connection in the rectangular welding groove, the joint strength of curb plate can effectively be guaranteed to this scheme. The side plates and the sealing plate are sealed in a welding mode, so that the cavity (namely the liquid inlet channel) formed by the upper cover plate and the sealing plate is integrally sealed.

For conventional liquid distributor among the prior art, the liquid distributor's of this embodiment roof and curb plate have compromise upper cover plate, gas homogenizing plate, the side liquid baffle function and the structure of liquid distributor among the prior art, effectively retrench liquid distributor spare part quantity. Simultaneously because the coolant volume that flows from the liquid distributor shrouding is great, for preventing that the coolant from spilling over from side fender liquid board and shrouding junction and causing the gas absorption to take liquid, the side fender liquid board and the shrouding of conventional rectangle porous plate structure liquid distributor adopt full weld to be connected in length direction, and welding work volume is big and easily causes shrouding department welding deformation. This welding process can be saved completely to the liquid distributor of this embodiment, effectively promotes production efficiency, can avoid the shrouding welding deformation simultaneously.

The utility model also provides an embodiment of heat exchanger, refer to fig. 6, the heat exchanger includes the liquid distributor of above-mentioned embodiment. The heat exchanger of this embodiment is a falling film evaporator, and is exemplified by a falling film evaporator.

The heat exchanger includes casing 61, and casing 61 is inside to be provided with heat exchange tube 62, and the liquid distributor setting is inside casing 61, and the liquid distributor is one, and the heat exchange tube is a plurality of. The liquid distributor is positioned above the heat exchange tube 62, and the overflowing holes 31 of the closing plate are opposite to the top of the heat exchange tube. Refrigerant entering the second chamber. The overflowing holes of the sealing plates are uniformly distributed on the heat exchange surface of the uppermost layer of the heat exchange tube, and the heat exchange tube is dripped and evaporated layer by layer.

When part air conditioning unit operation heat pump operating mode (air conditioning unit is through the cross valve switching-over, and the evaporimeter uses as the condenser, and gaseous state refrigerant gets into from the top air inlet, and with heat exchange tube heat transfer phase transition condensation), if adopt conventional rectangle perforated plate structure liquid distributor, the refrigerant that gets into the casing from the gas outlet is blockked by liquid distributor and side fender liquid board, and the regional heat exchange tube in top can't fully contact with gaseous state refrigerant, consequently influences whole condensation effect relatively poor. The liquid distributor in the heat exchanger can completely ignore the influence of the liquid baffle on the side.

Referring to fig. 6, the side plate 20 has a folded edge 21 extending away from the liquid inlet passage 40, and the folded edge 21 is provided with an auxiliary overflowing hole 21a; the flange 21 is connected to the inner wall of the housing 61. The position and the structure of the side plate 20 can be directly connected with the inner wall of the shell 61, and the folded edge 21 is not only used for gaseous refrigerant to pass through, but also can be used as a mounting part of the liquid distributor so as to fix the liquid distributor and achieve the effect of multiple purposes.

As shown in fig. 6 and 7, the heat exchanger has a suction port 63, a first region 211 is provided at a position of the folded edge 21 corresponding to the suction port 63, a plurality of auxiliary overflowing holes 21a are provided, at least a part of the auxiliary overflowing holes 21a are located in the first region 211, and the diameter of the auxiliary overflowing hole 21a located in the first region 211 is smaller than the diameter of the auxiliary overflowing hole 21a located outside the first region 211. The first region 211 is set to further prevent the entrainment of the suction gas, and the auxiliary overflowing hole in the first region 211 is smaller than the auxiliary overflowing holes at other positions, so that the auxiliary overflowing hole near the suction port of the heat exchanger can only pass the gaseous refrigerant.

Preferably, the length of the first area arrangement in the length direction of the liquid distributor is L, the relation between the length of the first area arrangement L and the diameter phi 1 of the suction port 63 can be selected according to specific situations, for example, the value of L/phi 1 is required to be between 2 and 5, and is preferably 3. The diameter of the auxiliary overflowing hole in the first area can be controlled to be between 2 and 20 mm.

The relationship between the size of a liquid distributor in the heat exchanger and the cold quantity of the falling film heat exchanger can greatly influence the air suction and liquid carrying resistance and the cost of the heat exchanger. Based on this, the utility model discloses improve and optimize, the cross sectional area of liquid distributor and the relation between the cold volume of falling film evaporator are as follows:

s1＝0.0006x+1，s2＝0.00022x+1.0065，s1≤s≤s2；

s is the cross-sectional area of the liquid distributor in m ² (ii) a x is the cold energy of the falling film evaporator and the unit RT.

Preferably, the cross section of the liquid inlet channel 40 is trapezoidal, the top plate 10 is located at the upper bottom position of the trapezoid, and the sealing plate 30 is located at the lower bottom position of the trapezoid; the width of the sealing plate 30 is W1, and the unit is mm; the tube distribution width of the heat exchange tube 62 is W2, and the unit is mm; w1 is more than or equal to W2+6mm. In fig. 6, the width direction is the horizontal direction, and the width direction of the sealing plate 30 and the tube arrangement width of the heat exchange tube are both width values in the horizontal direction shown in fig. 6. The structure is matched in shape, so that the occupied space of the liquid distributor can be reduced, the space utilization efficiency of the heat exchanger is improved, and the original liquid distribution efficiency is ensured.

Preferably, the distance between the top plate 10 and the closing plate 30 is H in mm; w1 x 20% or more and H1 x 40% or less. The structure is matched in shape, so that the occupied space of the liquid distributor can be reduced, the space utilization efficiency of the heat exchanger is improved, and the original liquid distribution efficiency is ensured.

Preferably, the liquid distributor further comprises a liquid homogenizing plate 50, the liquid homogenizing plate 50 is arranged in the liquid inlet channel 40, and liquid homogenizing holes are formed in the liquid homogenizing plate 50; the length of the liquid homogenizing plate is L2, and the unit is mm; the length of the sealing plate is L, and the unit is mm; l2= L-100mm. The left-right direction in fig. 4 is the longitudinal direction of the above-mentioned length, and the length of the liquid-uniforming plate and the length of the sealing plate are both the values of the length in the left-right direction shown in fig. 4. The structure is matched in shape, so that the occupied space of the liquid distributor can be reduced, the space utilization efficiency of the heat exchanger is improved, and the original liquid distribution efficiency is ensured.

Preferably, the homogenizing plate 50 divides the liquid inlet channel 40 into a first chamber 41 and a second chamber 42; the first cavity 41 is communicated with the liquid inlet 11, and the first cavity 41 is communicated with the second cavity 42 through a liquid equalizing hole; the second chamber 42 communicates with the overflow aperture 31; the height of the first chamber 41 is H1 in mm; the distance between the top plate 10 and the sealing plate 30 is H, and the unit is mm; h1= H × 50%, H1 ≧ 15mm. The structure is matched in shape, so that the occupied space of the liquid distributor can be reduced, the space utilization efficiency of the heat exchanger is improved, and the original liquid distribution efficiency is ensured.

Preferably, the sum of the flow areas of all the auxiliary flow-through holes 21a is s3; the heat exchanger is provided with an air outlet, and the diameter of the air outlet is s4; s3 is more than or equal to s4. The structure is matched in shape, so that the occupied space of the liquid distributor can be reduced, the space utilization efficiency of the heat exchanger is improved, and the original liquid distribution efficiency is ensured.

Preferably, the fold 21 extends away from the inlet channel 40 by a width L1 in mm; the bending angle formed between the side plate 20 and the top plate 10 is alpha 1; the heat exchange tube 62 has a diameter d1 in mm; l1 ≧ (d 1 × 1.21+ 10mm) sin (180 ° - α 1). The structure is matched in shape, so that the occupied space of the liquid distributor can be reduced, the space utilization efficiency of the heat exchanger is improved, and the original liquid distribution efficiency is ensured.

Compared with the liquid distributor in the prior art shown in fig. 5, the present embodiment has the following advantages:

the development of the liquid distributor with a compact structure for the falling film evaporator is as follows:

1. the evaporator with the shell of the same specification and length can improve the heat exchange capability of the evaporator on the premise of ensuring the high-efficiency and reliable operation of the evaporator.

2. General falling film evaporator uses for the refrigeration operating mode, the utility model provides a falling film evaporator can compromise the heating operating mode.

3. The falling film evaporator can effectively prevent the welding deformation of the liquid homogenizing plates by using the liquid distributor in the embodiment; meanwhile, the parts are effectively combined and optimized, so that the number of the parts is small, the welding workload is small, and the assembly efficiency can be effectively improved.

4. The hem structure of curb plate has further promoted the anti gas absorption of heat exchanger and has taken liquid ability.

5. On the premise of ensuring that the flow area of the gaseous refrigerant flow channels on the two sides is not changed, the top space of the shell of the falling film evaporator is effectively utilized, and the number of the shell heat exchange tubes in the same specification is increased, so that the heat exchange efficiency of the shell heat exchanger in the same gear is improved.

The utility model provides an embodiment of air conditioner, including the heat exchanger of above-mentioned embodiment.

It is noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of example embodiments according to the present application. As used herein, the singular is intended to include the plural unless the context clearly dictates otherwise, and it should be further understood that the terms "comprises" and/or "comprising," when used in this specification, specify the presence of features, steps, operations, devices, components, and/or combinations thereof.

It should be noted that the terms "first," "second," and the like in the description and claims of this application and in the accompanying drawings are used for distinguishing between similar elements and not necessarily for describing a particular sequential or chronological order. It is to be understood that the data so used is interchangeable under appropriate circumstances such that the embodiments of the application described herein are capable of operation in other sequences than those illustrated or described herein.

Of course, the above is the preferred embodiment of the present invention. It should be noted that, for a person skilled in the art, several modifications and decorations can be made without departing from the basic principle of the present invention, and these modifications and decorations are also considered to be within the scope of the present invention.

Claims

1. A liquid distributor, comprising:

the liquid inlet is formed in the top plate (10), and a liquid inlet (11) is formed in the top plate (10);

the two side plates (20) are oppositely arranged and connected with the top plate (10);

the sealing plate (30) is connected to the side plates (20), a liquid inlet channel (40) is defined among the top plate (10), the two side plates (20) and the sealing plate (30), and overflowing holes (31) are formed in the sealing plate (30); the liquid inlet channel (40) is communicated with the liquid inlet (11), and the liquid inlet channel (40) is communicated with the overflowing hole (31); the flow area of the liquid inlet channel (40) is gradually increased along the direction from the liquid inlet (11) to the overflowing hole (31);

the side plates (20) and the sealing plates (30) are positioned through rivets, and the side plates (20) are fixedly connected with the sealing plates (30).

2. The liquid distributor according to claim 1,

the bending angle (alpha 1) formed between the side plate (20) and the top plate (10) is 120-150 degrees.

3. The liquid distributor according to claim 2, characterized in that the cross section of the liquid inlet channel (40) is trapezoid, the top plate (10) is located at the upper bottom of the trapezoid, and the sealing plate (30) is located at the lower bottom of the trapezoid.

4. The liquid distributor according to claim 1, further comprising:

the liquid equalizing plate (50), the liquid equalizing plate (50) sets up in the inlet channel (40), be provided with the liquid equalizing hole on the liquid equalizing plate (50).

5. The liquid distributor according to claim 4, characterized in that the liquid homogenizing plate (50) divides the liquid inlet channel (40) into a first chamber (41) and a second chamber (42);

the first cavity (41) is communicated with the liquid inlet (11), and the first cavity (41) is communicated with the second cavity (42) through the liquid equalizing hole;

the second chamber (42) communicates with the overflow aperture (31).

6. The liquid distributor according to claim 1,

the side plate (20) is provided with a folded edge (21) extending away from the liquid inlet channel (40), and the folded edge (21) is provided with an auxiliary overflowing hole (21 a).

7. The dispenser according to claim 6, characterized in that the sum of the areas of all the auxiliary overflow holes (21 a) is equal to 50-80% of the area of the flange (21).

8. The liquid distributor according to claim 1, characterized in that the closing plate (30) has connecting plates (32) at both ends, the connecting plates (32) are parallel to the side plates (20), the side plates (20) are positioned with the connecting plates (32) by rivets, and the connecting plates (32) are fixedly connected with the side plates (20) by spot welding or intermittent welding.

9. A heat exchanger, characterized in that it comprises a liquid distributor according to any one of claims 1 to 8.

10. The heat exchanger of claim 9,

the heat exchanger comprises a shell (61), wherein a heat exchange tube (62) is arranged in the shell (61), and the liquid distributor is arranged in the shell (61).

11. The heat exchanger of claim 10,

the side plate (20) is provided with a folded edge (21) extending away from the liquid inlet channel (40), and an auxiliary overflowing hole (21 a) is formed in the folded edge (21);

the folded edge (21) is connected with the inner wall of the shell (61).

12. The heat exchanger of claim 11,

the heat exchanger is provided with an air inlet (63), a first area (211) is arranged at the position, corresponding to the air inlet (63), of the folded edge (21), the number of the auxiliary overflowing holes (21 a) is multiple, at least part of the auxiliary overflowing holes (21 a) are located in the first area (211), and the diameter of the auxiliary overflowing holes (21 a) located in the first area (211) is smaller than that of the auxiliary overflowing holes (21 a) located outside the first area (211).

13. The heat exchanger of claim 9, wherein the heat exchanger is a falling film evaporator.

14. The heat exchanger of claim 13, wherein the relationship between the cross-sectional area of the liquid distributor and the cold capacity of the falling film evaporator is as follows:

s1＝0.0006x+1，s2＝0.00022x+1.0065，s1≤s≤s2；

s is the cross-sectional area of the liquid distributor in m ² (ii) a x is the cold energy of the falling film evaporator and unit RT.

15. The heat exchanger of claim 10,

the cross section of the liquid inlet channel (40) is trapezoidal, the top plate (10) is positioned at the upper bottom of the trapezoid, and the sealing plate (30) is positioned at the lower bottom of the trapezoid;

the width of the sealing plate (30) is W1, and the unit is mm; the tube distribution width of the heat exchange tube (62) is W2, and the unit is mm; w1 is more than or equal to W2+6mm.

16. The heat exchanger of claim 15,

the distance between the top plate (10) and the sealing plate (30) is H, and the unit is mm;

W1×20％≤H≤W1×40％。

17. the heat exchanger of claim 15,

the liquid distributor also comprises a liquid homogenizing plate (50), the liquid homogenizing plate (50) is arranged in the liquid inlet channel (40), and liquid homogenizing holes are formed in the liquid homogenizing plate (50);

the length of the liquid homogenizing plate (50) is L2, and the unit is mm; the length of the sealing plate (30) is L, and the unit is mm;

L2＝L-100mm。

18. the heat exchanger of claim 17,

the liquid equalizing plate (50) divides the liquid inlet channel (40) into a first chamber (41) and a second chamber (42); the first chamber (41) is communicated with the liquid inlet (11), and the first chamber (41) is communicated with the second chamber (42) through the liquid equalizing hole; the second chamber (42) communicates with the overflow aperture (31);

the height of the first chamber (41) is H1 in mm; the distance between the top plate (10) and the sealing plate (30) is H, and the unit is mm;

H1＝H×50％，H1≥15mm。

19. the heat exchanger of claim 12,

the sum of the flow areas of all the auxiliary through holes (21 a) is s3;

the heat exchanger is provided with an air outlet, and the diameter of the air outlet is s4;

s3≥s4。

20. the heat exchanger of claim 12,

the width of the folded edge (21) extending away from the liquid inlet channel (40) is L1, and the unit is mm; the bending angle formed between the side plate (20) and the top plate (10) is alpha 1;

the diameter of the heat exchange tube (62) is d1, and the unit is mm;

L1≥(d1×1.21+10mm)÷sin(180°-α1)。

21. an air conditioner characterized by comprising the heat exchanger of any one of claims 9 to 20.