EVAPORATOR, WIND WALL APPARATUS, AND AIR CONDITIONING DEVICE

Abstract

The present disclosure discloses an evaporator, a wind wall apparatus, and an air conditioning device, where a long edge of a windward side of the evaporator is arranged along a first direction. The evaporator includes a manifold assembly and a heat exchange tube assembly. The manifold assembly includes a first manifold having a liquid inlet hole and a second manifold having a liquid outlet hole. The second manifold and the first manifold are arranged at intervals along a second direction, and the second direction intersects with the first direction. The heat exchange tube assembly has a first end and a second end arranged opposite to each other, where the first end is communicated with the liquid inlet hole through an inner cavity of the first manifold, and the second end is communicated with the liquid outlet hole through an inner cavity of the second manifold.

Description

CROSSREFERENCE TO RELATED APPLICATION

This application claims priority to Chinese Patent Application No. 202311000509.1, titled “EVAPORATOR, WIND WALL APPARATUS, AND AIR CONDITIONING DEVICE” and filed to the China National Intellectual Property Administration on August 9, the entire contents of which are incorporated herein by reference.

TECHNICAL FIELD

Embodiments of the present disclosure relate to the field of data center heat dissipation technology, and more particularly, to an evaporator, a wind wall apparatus, and an air conditioning device.

BACKGROUND

With the advent of the big data era, amount of data processing is constantly increasing, and power consumption of data centers for data processing is also increasing year by year. Therefore, how to reduce power usage effectiveness (PUE) of the entire data centers has become a hot research topic in the industry. As essential refrigeration devices for the data centers, high energy efficiency and miniaturization of computer room air conditioners play a crucial role in reducing the PUE of the data centers.

In related technologies, ends of the computer room air conditioners are getting closer and closer to server cabinets to improve efficiency of heat capture. As a manifestation of the ends of the computer room air conditioners, back panel wind walls are arranged on opposite sides of cabinet servers. The back panel wind walls can reduce temperature of air by means of the evaporators, and blow the cooled air towards cabinets.

However, the air blown out from the back panel wind walls has a temperature stratification of “cold below and hot above”, which is not conducive to cooling the cabinet servers.

SUMMARY

Objectives of embodiments of the present disclosure are to provide an evaporator, a wind wall apparatus, and an air conditioning device, which can solve the problem that temperature stratification of “cold above and hot below” in air blown out from back panel wind walls in related technologies is not conducive to cooling cabinet servers.

To achieve the above objectives, one aspect of the embodiments of the present disclosure provides an evaporator, where a long edge of a windward side of the evaporator is arranged along a first direction. The evaporator includes a manifold assembly and a heat exchange tube assembly. The manifold assembly includes a first manifold having a liquid inlet hole and a second manifold having a liquid outlet hole. The second manifold and the first manifold are arranged at intervals along a second direction, and the second direction intersects with the first direction. The heat exchange tube assembly has a first end and a second end arranged opposite to each other, where the first end is communicated with the liquid inlet hole through an inner cavity of the first manifold, and the second end is communicated with the liquid outlet hole through an inner cavity of the second manifold.

In one possible embodiment, the second direction is perpendicular to the first direction.

In one possible embodiment, the manifold assembly is communicated at one end of the heat exchange tube assembly along the first direction. The heat exchange tube assembly forms a semiannular inner channel, where two ends of the semiannular inner channel are communicated with the inner cavity of the first manifold and the inner cavity of the second manifold, respectively.

In one possible embodiment, the heat exchange tube assembly includes a plurality of flat tubes and a steering tube, where the steering tube and the manifold assembly are arranged at intervals along the first direction, and the plurality of flat tubes are communicated between the steering tube and the manifold assembly. The plurality of flat tubes include a first flat tube and a second flat tube, where the first flat tube is communicated between the steering tube and the first manifold, and the second flat tube is communicated between the steering tube and the second manifold. The first flat tube, the steering tube, and the second flat tube form the semiannular inner channel.

In one possible embodiment, the heat exchange tube assembly includes a plurality of semiannular flat tubes arranged at intervals, the plurality of semiannular flat tubes are nested layer by layer, and each of the plurality of semiannular flat tubes has the semiannular inner channel.

In one possible embodiment, the second direction is perpendicular to a plane formed by the first direction and a direction where air passes through the evaporator.

In one possible embodiment, the second direction is arranged along a direction where the air passes through the evaporator, and the first manifold is positioned on an air outlet side of the evaporator.

In one possible embodiment, both the first manifold and the second manifold are arranged along the first direction, and the second direction is perpendicular to a plane formed by the first direction and a direction where the air passes through the evaporator. The heat exchange tube assembly includes a plurality of heat exchange flat tubes, and each of the plurality of heat exchange flat tubes is communicated between the first manifold and the second manifold.

Another aspect of the embodiments of the present disclosure also provides a wind wall apparatus, which includes a fan and the evaporator as described above. The fan is positioned on one side of the evaporator and is configured to guide the air to pass through the evaporator.

Still another aspect of the embodiments of the present disclosure also provides an air conditioning device, which includes a compressor, a condenser, and the wind wall apparatus as described above. A liquid inlet hole of the evaporator of the wind wall apparatus is communicated with an outflow end of the condenser, a liquid outlet hole of the evaporator of the wind wall apparatus is communicated with an inflow end of the compressor, and an outflow end of the compressor is communicated with an inflow end of the condenser.

Still another aspect of the embodiments of the present disclosure also provides a data center, which includes a cabinet server and the air conditioning device as described above, where the wind wall apparatus of the air conditioning device is arranged on one side of the cabinet server.

As can be seen from above, in the evaporator, the wind wall apparatus, and the air conditioning device provided in the embodiments of the present disclosure, a manifold assembly and a heat exchange tube assembly are provided. The manifold assembly includes a first manifold and a second manifold, where the first end of the heat exchange tube assembly is communicated with the liquid inlet hole through an inner cavity of the first manifold, and the second end of the heat exchange tube assembly is communicated with the liquid outlet hole through an inner cavity of the second manifold, such that a heat transfer medium flows into the inner cavity of the first manifold through the liquid inlet hole, then flows from the first end of the heat exchange tube assembly into the heat exchange tube assembly through the inner cavity of the first manifold, then flows from the second end of the heat exchange tube assembly into the inner cavity of the second manifold, and flows out of the second manifold from the liquid outlet hole. That is, the heat transfer medium flows from the first manifold to the second manifold in the heat exchange tube assembly. When hotter air passes through the heat exchange tube assembly, it may exchange heat with the colder heat transfer medium in the heat exchange tube assembly and thus is cooled down.

In addition, the long edge of the evaporator provided in the embodiments of the present disclosure is arranged along the first direction, the first manifold and the second manifold are arranged at intervals along the second direction, and the second direction intersects with the first direction. In this way, the first end and the second end of the heat exchange tube assembly are arranged at intervals along the second direction, such that a supercooled region formed by a region near the first end of the heat exchange tube assembly and a superheated region formed by a region near the second end of the heat exchange tube assembly are arranged at intervals along the second direction. That is, the supercooled region and the superheated region are not arranged at intervals along the first direction. In this way, a temperature gradient along the first direction is reduced for the air passing through the supercooled region and the air passing through the superheated region, thereby avoiding the temperature stratification of “hot above and cold below” appeared in the related technologies, which is conducive to cooling the cabinet server.

BRIEF DESCRIPTION OF THE DRAWINGS

To describe the technical solutions of the embodiments of the present disclosure more clearly, the accompanying drawings required in the description of the embodiments will be briefly introduced below. Apparently, the accompanying drawings in the following description are merely some embodiments of the present disclosure. To those of ordinary skills in the art, other accompanying drawings may also be derived from these accompanying drawings without creative efforts.

FIG. 1 is a schematic diagram of a server and a back panel wind wall in related technologies;

FIG. 2 is a front view of a heat exchanger shown in FIG. 1;

FIG. 3 is a schematic diagram of a data center according to an embodiment of the present disclosure;

FIG. 4 is a schematic diagram of an air conditioning device according to an embodiment of the present disclosure;

FIG. 5 is a front view of a first type of evaporator according to an embodiment of the present disclosure;

FIG. 6 is a side view of a second type of evaporator according to an embodiment of the present disclosure;

FIG. 7 is a front view of a third type of evaporator according to an embodiment of the present disclosure;

FIG. 8 is a side view of a fourth type of evaporator according to an embodiment of the present disclosure; and

FIG. 9 is a side view of a fifth type of evaporator according to an embodiment of the present disclosure.

Reference Numerals in the Accompanying Drawings

air conditioning device 1000; evaporator 100; inlet wind surface 101; outlet wind surface 102; manifold assembly 10; first manifold 11; second manifold 12; heat exchange tube assembly 20; first flat tube 21′; second flat tube 21″; steering tube 22; semiannular flat tube 23; heat exchange flat tube 24; liquid inlet pipe 30; liquid outlet pipe 40; wing plate 50; compressor 200; condenser 300; fan 400; cabinet server 2000; back panel wind wall 3000; heat exchanger 3100; first manifold 3101; second manifold 3102; heat exchange tube 3103; exhaust fan 3200; server 4000; air inlet 4100; and air outlet 4200.

DETAILED DESCRIPTION

As described in the background technology, air blown out of a back panel wind wall in related technologies has a problem of temperature stratification of “cold below and hot above”, which is not conducive to cooling cabinet servers. Based on inventors' research, it is found that reasons for this problem are as follows.

FIG. 1 is a schematic diagram of a server 4000 and a back panel wind wall 3000 in the related technologies. Referring to FIG. 1, the server 4000 is a cabinet server, and is shaped like a rectangular solid. An end surface of a long edge of the server 4000 may be placed towards a support surface, and there exists a certain height between other end surface of the long edge of the server 4000 and the support surface. That is, the cabinet server 4000 stands upright on the support surface, and a direction of the long edge of the cabinet server 4000 is a vertical direction perpendicular to the support surface. In addition, an air inlet 4100 and an air outlet 4200 are respectively arranged on two opposite surfaces of the cabinet of the server 4000 along its thickness direction.

Arrows shown in FIG. 1 represent a direction of air flow. Referring to FIG. 1, the back panel wind wall 3000 in the related technologies may include a heat exchanger 3100 and an exhaust fan 3200. Hotter air may be cooled down into colder air by exchanging heat with the heat exchanger 3100 under the guidance of the exhaust fan 3200, and then is blown towards the server 4000 to cool down a plurality of computing nodes in the cabinet of the server 4000.

FIG. 2 is a front view of the heat exchanger shown in FIG. 1, and arrows in FIG. 2 indicate flow directions of a heat transfer medium. Referring to FIG. 2, the back panel wind wall 3000 in the related technologies includes a first manifold 3101, a second manifold 3102, and a plurality of heat exchange tubes 3103. The first manifold 3101 and the second manifold 3102 are arranged at intervals, and the plurality of heat exchange tubes 3103 are communicated between the first manifold 3101 and the second manifold 3102. The heat transfer medium for exchanging heat with the air may first enter the heat exchange tube 3103 through the first manifold 3101, then enter the second manifold 3102 through the heat exchange tube 3103, and then flow out of the second manifold 3102.

Referring to FIG. 1, the server 4000 is shaped like a rectangular solid, where a surface where the air inlet 4100 or the air outlet 4200 of the server 4000 is positioned is rectangular, and a long edge direction of a surface where the air inlet 4100 of the server 4000 is positioned is a vertical direction. When the heat exchanger 3100 is used as an evaporator and used for cooling the server 4000, an outlet wind surface (or inlet wind surface) of the heat exchanger 3100 is opposite and parallel to the surface where the air inlet 4100 (or the air outlet 4200) of the server 4000 is positioned, and the outlet wind surface (or inlet wind surface) of the heat exchanger 3100 is rectangular. A length direction of the outlet wind surface (or inlet wind surface) of the heat exchanger 3100 is parallel to a length direction of the server 4000. That is, the long edge direction of the outlet wind surface (or inlet wind surface) of the heat exchanger 3100 is set along the vertical direction. Referring to FIG. 1 and FIG. 2, the first manifold 3101 and the second manifold 3102 are placed at intervals along the vertical direction, and the first manifold 3101 is positioned above the second manifold 3102. The heat transfer medium flows in heat exchange tube 3103 along the vertical direction.

The heat transfer medium may undergo phase transition in the process of flowing in the heat exchange tube. Referring to FIG. 2, the heat transfer medium positioned in a lower section of the heat exchange tube 3103 is liquid, and may form a supercooled region. The heat transfer medium positioned in an upper section of the heat exchange tube 3103 gradually becomes gaseous, and may form a superheated region. The heat transfer medium positioned in a middle section of the heat exchange tube 3103 is a gas-liquid mixture, which may form a two-phase region. The gaseous heat transfer medium has a larger volume, and the heat exchange tube 3103 has a smaller inner diameter, such that the heat transfer medium in the superheated region has a higher flow speed, resulting in a greater decrease in pressure drop, which in turn leads to a higher temperature of the heat transfer medium in the superheated region, resulting in a problem that the air blown out from the back panel wind wall 3000 in the related technologies has a temperature stratification of “cold below and hot above”, such that the computing node above the cabinet is higher in temperature than the computing node below the cabinet, which is not conducive to cooling the cabinet server 4000.

For the aforementioned technical problem, inventors of the embodiments of the present disclosure have come up with an idea that the temperature stratification of “cold below and hot above” can be avoided if the supercooled region and the superheated region are not arranged along the vertical direction. In view of this, in the evaporator provided in the embodiments of the present disclosure, the second manifold and the first manifold are arranged at intervals along a second direction, which intersects with a direction of a long edge of an inlet wind surface (or outlet wind surface) of the evaporator. The supercooled region formed near the first manifold and the superheated region formed near the second manifold may not be arranged along the vertical direction, thereby avoiding longitudinal temperature gradients and the temperature stratification of “cold below and hot above”, which is conducive to cooling the cabinet server.

To make the objectives, technical solutions, and advantages of the embodiments of the present disclosure clearer, the technical solutions in the embodiments of the present disclosure will be described clearly and completely below, in conjunction with the accompanying drawings in the embodiments of the present disclosure. Apparently, the described embodiments are some but not all of the embodiments of the present disclosure.

All other embodiments obtained by a person of ordinary skill in the art based on the embodiments of the present disclosure without creative efforts shall fall within the protection scope of the present disclosure. The following embodiments and features thereof may be combined with each other on a non-conflict basis.

FIG. 3 is a schematic diagram of a data center according to an embodiment of the present disclosure. Referring to FIG. 3, the data center provided in the embodiments of the present disclosure may include a cabinet server 2000 and an air conditioning device 1000. The cabinet server 2000 may include a cabinet and a plurality of computing nodes housed in an inner cavity of the cabinet. The air conditioning device 1000 may include a wind wall apparatus, which may include an evaporator 100 and a fan 400. The evaporator 100 may have an inner cavity for flow of the heat transfer medium. Air may be guided by the fan 400 to pass through the evaporator 100 along a third preset direction and exchange heat with the heat transfer medium in the inner cavity of the evaporator 100 to reduce the temperature of the air.

The air may flow into the evaporator 100 through an inlet wind surface 101 of the evaporator 100 and flow out of the evaporator 100 through an outlet wind surface 102 of the evaporator 100. The air flowing out of the outlet wind surface 102 of the evaporator 100 may flow into the inner cavity of the cabinet through an air inlet on an inlet wind end surface of the cabinet, and may flow out of the inner cavity of the cabinet through an air outlet of the cabinet after exchanging heat with the plurality of computing nodes in the inner cavity of the cabinet. It is to be understood that the colder air passing through the evaporator 100 may take away heat from the computing nodes when passing through the computing nodes, to reduce temperature of the computing nodes.

The outlet wind surface 102 of the evaporator 100 and an end surface (the inlet wind end surface of the cabinet) of the cabinet where the air inlet is provided may be arranged opposite to each other. That is, the inlet wind end surface of the cabinet is perpendicular to the third preset direction, and a projection of the outlet wind surface 102 of the evaporator 100 on the inlet wind end surface of the cabinet along the third preset direction at least partially overlaps with the inlet wind end surface of the cabinet. In this way, a flow path of the air between the evaporator 100 and the cabinet may be reduced to decrease losses.

It is worth noting that the cabinet of the cabinet server 2000 is shaped like a rectangular solid, and the inlet wind end surface of the cabinet is shaped like a rectangle. A long edge direction of the rectangle is set along a first direction X, and the plurality of computing nodes in the inner cavity of the cabinet are arranged at intervals along the first direction X. To dissipate heat from these computing nodes, a long edge of the outlet wind surface 102 of the evaporator 100 may be placed parallel to a long edge of the inlet wind end surface of the cabinet. That is, the long edge of the outlet wind surface 102 of the evaporator 100 is arranged along the first direction X.

For example, the cabinet server 2000 is placed upright on a support surface. That is, the long edge (the first direction X) of the inlet wind end surface of the cabinet is arranged along the vertical direction. The evaporator 100 is placed upright on the support surface, or the evaporator 100 is hung upright on a vertical wall surface such as a wall. That is, the long edge of the outlet wind surface 102 of the evaporator 100 is arranged along the vertical direction.

A cross-section of the evaporator 100 may be obtained by cutting off the evaporator 100 along the first direction X. The cross-section of the evaporator 100 may be shaped like a rectangle, or the cross-section of the evaporator 100 may be L-shaped, V-shaped, N-shaped, W-shaped or the like formed by at least two rectangles spliced at an angle. When the cross-section of the evaporator 100 is rectangular, the outlet wind surface 102 of the evaporator 100 is a plane. When the cross-section of the evaporator 100 is other shapes, the outlet wind surface 102 of the evaporator 100 is formed by a plurality of planes spliced at an angle. The specific structure of the evaporator 100 is described below by taking an example where the cross-section of the evaporator 100 is rectangular. The structure of the evaporator 100 whose cross-section is in other shapes may be known by reference to the following, and thus is not to be described in detail here.

FIG. 4 is a schematic diagram of an air conditioning device 1000 according to an embodiment of the present disclosure. Referring to FIG. 4, the air conditioning device 1000 provided in the embodiments of the present disclosure may also include a compressor 200 and a condenser 300. A liquid inlet hole of the evaporator 100 may be communicated with an outflow end of the condenser 300 through a pipeline, a liquid outlet hole of the evaporator 100 may be communicated with an inflow end of the compressor 200 through a pipeline, and an outflow end of the compressor 200 may be communicated with an inflow end of the condenser 300. In this way, a loop shown in FIG. 4 for flow of the heat transfer medium is formed between the evaporator 100, the compressor 200, and the condenser 300. A power apparatus such as a water pump may be arranged in the loop, such that the heat transfer medium circulates in the loop.

The compressor 200 can compress the gaseous heat transfer medium into a high-temperature and high-pressure heat transfer medium. The high-temperature and high-pressure heat transfer medium may enter the condenser 300 and is liquefied after dissipating heat at the condenser 300. The liquid heat transfer medium enters the evaporator 100 and absorbs a large amount of heat at the evaporator 100, then is transformed into a gaseous heat transfer medium, and next the gaseous heat transfer medium enters the compressor 200 for recirculation.

A throttling apparatus may be connected between the condenser 300 and the evaporator 100. A specific structure of the throttling apparatus includes but is not limited to an electronic expansion valve, a thermal expansion valve, and a capillary tube, etc. The throttling apparatus is employed to throttle and reduce pressure of the high-pressure liquid heat transfer medium to ensure a pressure difference between the condenser 300 and the evaporator 100, such that the liquid heat transfer medium in the evaporator 100 evaporates and absorbs heat at a required lower pressure. In this way, the objective of refrigeration and cooling is achieved. Meanwhile, the throttling apparatus can adjust a flow rate of the heat transfer medium supplied to the evaporator 100 to adapt to changes in heat load of the evaporator 100, thereby ensuring the air conditioning system to operate more effectively.

Referring to FIG. 5, the evaporator 100 provided in the embodiments of the present disclosure may include a manifold assembly 10, a heat exchange tube assembly 20, and a wing plate 50. The manifold assembly 10 may include a first manifold 11 and a second manifold 12. The second manifold 12 and the first manifold 11 may be arranged at intervals along a second direction Y, where the second direction Y intersects with the first direction X. That is, the first manifold 11 and the second manifold 12 are independent of each other, an inner cavity of the first manifold 11 and an inner cavity of the second manifold 12 are independent of each other, and a certain distance is provided between the first manifold 11 and the second manifold 12 in the second direction Y.

In addition, the first manifold 11 may have the inner cavity and a liquid inlet hole communicated with each other, where the liquid inlet hole of the first manifold 11 may be communicated with a liquid inlet pipe 30, and an end of the liquid inlet pipe 30 far from the liquid inlet hole may be communicated with the outflow end of the condenser 300. The second manifold 12 may have the inner cavity and a liquid outlet hole communicated with each other, where the liquid outlet hole of the second manifold 12 may be communicated with a liquid outlet pipe 40, and an end of the liquid outlet pipe 40 far from the liquid outlet hole may be communicated with the inflow end of the compressor 200.

The heat exchange tube assembly 20 may have a first end and a second end arranged opposite to each other. The first end of the heat exchange tube assembly 20 is communicated with the liquid inlet hole through the inner cavity of the first manifold 11, such that the heat transfer medium flowing from the liquid inlet hole may flow, through the inner cavity of the first manifold 11, to the first end of the heat exchange tube assembly 20. The second end of the heat exchange tube assembly 20 is communicated with the liquid outlet hole through the inner cavity of the second manifold 12, such that the heat transfer medium flowing out of the second end of the heat exchange tube assembly 20 may flow to the liquid outlet hole through the inner cavity of the first manifold 11.

In summary, the heat transfer medium flowing into the evaporator 100 from the liquid inlet hole may sequentially flow, through the inner cavity of the first manifold 11, the first end of the heat exchange tube assembly 20, an inner channel of the heat exchange tube assembly 20, the second end of the heat exchange tube assembly 20, and the inner cavity and the liquid outlet hole of the second manifold 12, out of the evaporator 100. In the embodiments of the present disclosure, the first end of the heat exchange tube assembly 20 and the second end of the heat exchange tube assembly 20 are arranged at intervals along the second direction Y, and the second direction Y intersects with the first direction X. In this way, a supercooled region formed by a region near the first end of the heat exchange tube assembly 20 and a superheated region formed by a region near the second end of the heat exchange tube assembly 20 are arranged at intervals along the second direction Y. That is, the supercooled region and the superheated region are not arranged at intervals along the first direction X. In this way, a temperature gradient along the first direction X is reduced for the air passing through the supercooled region and the air passing through the superheated region, thereby avoiding the temperature stratification of “hot above and cold below” appeared in the related technologies, which is conducive to cooling the cabinet server.

To further avoid the temperature stratification of “hot above and cold below”, the second direction Y may be perpendicular to the first direction X. For example, in FIG. 5, FIG. 7, and FIG. 9, the second direction Y is perpendicular to a plane formed by the first direction X and a direction where the air passes through the evaporator 100. In FIG. 6 and FIG. 8, the second direction Y follows the direction where the air passes through the evaporator 100.

Alternatively, a shape of the inner channel of the heat exchange tube assembly 20 may be U-shaped, as shown in FIGS. 5 to 8; or the shape of the inner channel of the heat exchange tube assembly 20 is a straight line as shown in FIG. 9. How to form the U-shaped inner channel of the heat exchange tube assembly 20 is first described below.

Referring to FIGS. 5 to 8, the manifold assembly 10 may be communicated to one end of the heat exchange tube assembly 20 along the first direction X. That is, one end of the heat exchange tube assembly 20 along the first direction X may be communicated with the manifold assembly 10. In addition, the heat exchange tube assembly 20 may form a semiannular inner channel, and two ends of the semiannular inner channel are communicated with the inner cavity of the first manifold 11 and the inner cavity of the second manifold 12, respectively. “Semiannular” may be understood in a broad sense, which may not only refer to half of a closed ring, but also refer to figures that exceed half of the closed ring but are not closed, or figures that do not exceed half of the closed ring and have steering sections. A common characteristic of these graphics is that they all have the steering sections. A characteristic of the “steering section” is that the heat transfer medium flowing in the semiannular inner channel flows forward before passing through the steering section, and then flows backward along an opposite direction after passing through the steering section. A shape of the steering section may be straight or curved. In addition, when the semi ring refers to half of the closed ring, the first manifold 11 and the second manifold 12 are positioned at a same height. When the semi ring does not refer to half of the closed ring, the first manifold 11 and the second manifold 12 are positioned at different heights.

Several ways to form the semiannular inner channel are described as below.

Referring to FIG. 5, in an example of forming the semiannular inner channel, the heat exchange tube assembly 20 may include a plurality of flat tubes and a steering tube 22. The steering tube 22 and the manifold assembly 10 may be arranged at intervals along the first direction X, and the plurality of flat tubes may be communicated between the steering tube 22 and the manifold assembly 10. Specifically, the plurality of flat tubes may include a first flat tube 21′ and a second flat tube 21″, where the first flat tube 21′ may be communicated between the steering tube 22 and the first manifold 11, and the second flat tube 21″ may be communicated between the steering tube 22 and the second manifold 12.

The heat transfer medium may flow into the inner cavity of the first manifold 11 through the liquid inlet hole, then flow into the inner cavity of the steering tube 22 through the inner cavity of the first flat tube 21′, then flow into the inner cavity of the second manifold 12 through the inner cavity of the steering tube 22, then flow into the second manifold 12 through the inner cavity of the second manifold 12, and then flow out of the second manifold 12 through the liquid outlet hole.

The heat transfer medium flows in the heat exchange tube assembly 20 along the above flow path, which can ensure the heat exchange tube assembly 20 to form the supercooled region, the two-phase region, and the superheated region in sequence along the flow path. For example, in FIG. 5, a region of the first flat tubes 21′ between a marked line a and the first manifold 11 forms the supercooled region, a region of the first flat tubes 21′ and the second flat tubes 21″ between the marked line a and a marked line b forms the two-phase region, and a region of the second flat tubes 21″ between the marked line b and the second manifold 12 forms the superheated region. The marked line a and the marked line b in FIG. 5 are virtual lines marked for ease of understanding.

The temperature of the heat transfer medium in the supercooled region is lower than that of the heat transfer medium in the two-phase region, and the heat transfer medium in the supercooled region is liquid. The temperature of the heat transfer medium in the two-phase region is lower than that of the heat transfer medium in the superheated region. The heat transfer medium in the two-phase region transforms from liquid to gas, and the heat transfer medium in the superheated region is mostly gaseous. The air flows through the evaporator 100 along a direction perpendicular to a paper surface. The air passing through the supercooled region has the lowest temperature, the air passing through the superheated region has the highest temperature, and the temperature of the air passing through the two-phase region is between the lowest temperature and the highest temperature. Compared to the related technologies where the supercooled region and the superheated region in FIG. 2 are arranged along the first direction X, a temperature difference between the supercooled region and the superheated region is greater, resulting in a greater temperature difference of the air passing through the evaporator 100 along the first direction X in the related technologies. The supercooled region and the two-phase region of the evaporator 100 in the embodiments of the present disclosure are arranged along the first direction X, and the superheated region and the two-phase region are arranged along the first direction X. The temperature difference between the supercooled region and the two-phase region and the temperature difference between the superheated region and the two-phase region are both smaller than the temperature difference between the supercooled region and the superheated region. In this way, the temperature difference of the air passing through the evaporator 100 in the first direction X can be reduced to facilitate heat dissipation of the cabinet server 2000.

It is worth noting that in the embodiments of the present disclosure, there is no requirement for number of the first flat tubes 21′ and number of the second flat tubes 21″, which may be equal or not equal, as long as there is at least one first flat tube 21′ and at least one second flat tube 21″. In addition, when there are a plurality of first flat tubes 21′ (or second flat tubes 21″), the wing plate 50 may be provided between two adjacent first flat tubes 21′ (or second flat tubes 21″). The wing plate 50 may also be provided between the first flat tube 21′ and the second flat tube 21″ adjacent to each other, and the air may pass through pores between the wing plate 50 and the first flat tube 21′ or second flat tube 21″ to dissipate heat.

In addition, the first manifold 11 and the second manifold 12 are arranged at intervals along the second direction Y. The second direction Y may be perpendicular to a plane formed by the first direction X and a direction where the air passes through the evaporator 100, as shown in FIG. 5. Alternatively, the second direction Y may also be set along the direction where the air passes through the evaporator 100, as shown in FIG. 6. That is, the second direction Y may be along the third preset direction as shown in FIG. 3. Referring to FIG. 6, to further reduce the temperature of the air passing through the evaporator 100, the first manifold 11 may be positioned on an air outlet side of the evaporator 100, such that in the second direction Y, the air may sequentially pass through the superheated region and the supercooled region, and sequentially pass through the hotter two-phase region formed by the second flat tube 21″ and the colder two-phase region formed by the first flat tube 21′.

Referring to FIG. 7, in another example of forming the semiannular inner channel, the heat exchange tube assembly 20 may include a plurality of semiannular flat tubes 23. The plurality of semiannular flat tubes 23 may be arranged at intervals, and the plurality of semiannular flat tubes 23 may be nested layer by layer, and each of the plurality of semiannular flat tubes 23 may have the semiannular inner channel.

Specifically, “Semiannular” of the semiannular flat tube 23 may be understood in a broad sense, which may not only refer to half of a closed ring, but also refer to figures that exceed half of the closed ring but are not closed, or figures that do not exceed half of the closed ring and have steering sections. In addition, the semiannular flat tube 23 may have an inflow end and an outflow end, where the inflow end of the semiannular flat tube 23 is communicated with the first manifold 11, and the outflow end of the semiannular flat tube 23 is communicated with the second manifold 12.

The heat transfer medium may flow into the inner cavity of the first manifold 11 through the liquid inlet hole, then flow into the second manifold 12 through a left side and a right side of the semiannular flat tube 23, and then flow out of the second manifold 12 through the liquid outlet hole. The heat transfer medium flows in the heat exchange tube assembly 20 along the above flow path, which can ensure the heat exchange tube assembly 20 to form the supercooled region, the two-phase region, and the superheated region in sequence along the flow path. For example, in FIG. 7, a region at a lower-left side of the semiannular flat tubes 23 between the marked line a and the first manifold 11 forms the supercooled region, a region at an upper-left side and an upper-right side of the semiannular flat tubes 23 between the marked line a and the marked line b forms the two-phase region, and a region at a lower-right side of the semiannular flat tubes 23 between the marked line b and the second manifold 12 forms the superheated region. The marked line a and the marked line b in FIG. 7 are virtual lines marked for ease of understanding. By adopting the above method, the temperature difference of the air passing through the evaporator 100 in the first direction X can also be reduced, to facilitate the heat dissipation of the cabinet server 2000.

It is worth noting that the wing plate 50 may be provided between two adjacent semiannular flat tubes 23, and the air may pass through pores between the wing plate 50 and the semiannular flat tubes 23 to dissipate heat. In addition, the first manifold 11 and the second manifold 12 are arranged at intervals along the second direction Y. The second direction Y may be perpendicular to a plane formed by the first direction X and a direction where the air passes through the evaporator 100, as shown in FIG. 7. Of course, the second direction Y may also be set along the direction where the air passes through the evaporator 100, as shown in FIG. 8. That is, the second direction Y may be along the third preset direction as shown in FIG. 3. Referring to FIG. 8, to further reduce the temperature of the air passing through the evaporator 100, the first manifold 11 may be positioned on an air outlet side of the evaporator 100, such that in the second direction Y, the air may sequentially pass through the superheated region and the supercooled region, and sequentially pass through the hotter two-phase region and the colder two-phase region.

It is described a case where the inner channel of the heat exchange tube assembly 20 is U-shaped with reference to FIGS. 5 to 8 above. Below, it is to be described a case where the inner channel of the heat exchange tube assembly 20 is shaped like a straight line with reference to FIG. 9.

Referring to FIG. 9, both the first manifold 11 and the second manifold 12 may be arranged along the first direction X. That is, both the first manifold 11 and the second manifold 12 extend along the first direction X, and both an axial direction of the first manifold 11 and an axial direction of the second manifold 12 are the first direction X. In addition, the first manifold 11 and the second manifold 12 are arranged at intervals along the second direction Y. That is, a distance is provided between the first manifold 11 and the second manifold 12 along the second direction Y. The second direction Y may be perpendicular to a plane formed by the first direction X and a direction where the air passes through the evaporator 100. That is, the second direction Y is perpendicular to the direction where the air passes through the evaporator 100, and the second direction Y is also perpendicular to the first direction X. For example, in FIG. 9, the air passes through the evaporator 100 along a direction perpendicular to the paper surface.

With continued reference to FIG. 9, the heat exchange tube assembly 20 may include a plurality of heat exchange flat tubes 24. Each of the plurality of heat exchange flat tubes 24 may be communicated between the first manifold 11 and the second manifold 12, and a flow direction of the heat transfer medium in the inner cavity of the each heat exchange flat tube 24 is from the first manifold 11 to the second manifold 12 along the second direction Y, such that the heat exchange tube assembly 20 sequentially forms the supercooled region, the two-phase region, and the superheated region along the flow direction of the heat transfer medium. For example, in FIG. 9, a left region of the heat exchange tube assembly 20 between the marked line a and the first manifold 11 forms the supercooled region, a middle region of the heat exchange tube assembly 20 between the marked line a and the marked line b forms the two-phase region, and a right region of the heat exchange tube assembly 20 between the marked line b and the second manifold 12 forms the superheated region. The marked line a and the marked line b in FIG. 9 are virtual lines marked for ease of understanding. By adopting the above method, the temperature difference of the air passing through the evaporator 100 in the first direction X can also be reduced, to facilitate the heat dissipation of the cabinet server 2000.

In addition, the wing plate 50 may be provided between two adjacent heat exchange flat tubes 24, and the air can pass through the pores between the wing plate 50 and the heat exchange flat tubes 24 to dissipate heat.

The terms such as “upper” and “lower” used to describe relative positional relationships of various structures in the drawings are merely for the purpose of concise description rather than limiting the implementable scope of the present disclosure. The changes or adjustments of the relative relationship without a substantial modification to the technical solutions are regarded as being covered by the implementable scope of the present disclosure.

It is to be noted that in the present disclosure, unless specified or limited otherwise, a first feature “on” or “below” a second feature may include an embodiment in which the first feature is in direct contact with the second feature, and may also include an embodiment in which the first feature and the second feature are in indirect contact via an intermediary. Furthermore, a first feature “on,” “above,” or “on top of” a second feature may include an embodiment in which the first feature is right or obliquely “on,” “above,” or “on top of” the second feature, or just means that the first feature is at a height higher than that of the second feature. A first feature “below,” “under,” or “on bottom of” a second feature may include an embodiment in which the first feature is right or obliquely “below,” “under,” or “on bottom of” the second feature, or just means that the first feature is at a height lower than that of the second feature.

In addition, in the present disclosure, unless specified or limited otherwise, terms “mounted”, “connected”, “coupled”, “fixed” and so on should be understood in a broad sense, which may be, for example, a fixed connection, a detachable connection or integrated connection, a direct connection or indirect connection by means of an intermediary, an internal communication between two elements or an interaction relationship between two elements. The specific significations of the above terms in the present disclosure may be understood in the light of specific conditions by persons of ordinary skill in the art.

Reference throughout this specification to the terms “an embodiment,” “some embodiments,” “an exemplary embodiment,” “an example,” “a specific example,” or “some examples,” means that a specific feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the present disclosure. The schematic representation of the above terms throughout this specification is not necessarily referring to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics set forth may be combined in any suitable manner in one or more embodiments or examples.

Finally, it should be noted that the foregoing embodiments are merely intended for describing the technical solutions of the present disclosure, but not for limiting the present disclosure. Although the present disclosure is described in detail with reference to the foregoing embodiments, persons of ordinary skill in the art should understand that they may still make modifications to the technical solutions described in the foregoing embodiments or make equivalent replacements to some or all technical features thereof, which does not make corresponding technical solutions in essence depart from the scope of the technical solutions of the embodiments of the present disclosure.

Claims

1. An evaporator, wherein a long edge of a windward side of the evaporator is arranged along a first direction; and the evaporator comprises: a manifold assembly comprising a first manifold and a second manifold, wherein the first manifold has a liquid inlet hole, and the second manifold has a liquid outlet hole; the second manifold and the first manifold are arranged at intervals along a second direction, and the second direction intersects with the first direction; anda heat exchange tube assembly having a first end and a second end arranged opposite to each other, wherein the first end is communicated with the liquid inlet hole through an inner cavity of the first manifold, and the second end is communicated with the liquid outlet hole through an inner cavity of the second manifold.

2. The evaporator according to claim 1, wherein the second direction is perpendicular to the first direction.

3. The evaporator according to claim 2, wherein the manifold assembly is communicated at one end of the heat exchange tube assembly along the first direction; and the heat exchange tube assembly forms a semiannular inner channel, and two ends of the semiannular inner channel are communicated with the inner cavity of the first manifold and the inner cavity of the second manifold, respectively.

4. The evaporator according to claim 3, wherein the heat exchange tube assembly comprises a plurality of flat tubes and a steering tube, the steering tube and the manifold assembly are arranged at intervals along the first direction, the plurality of flat tubes are communicated between the steering tube and the manifold assembly, the plurality of flat tubes comprise a first flat tube and a second flat tube, the first flat tube is communicated between the steering tube and the first manifold, the second flat tube is communicated between the steering tube and the second manifold, and the first flat tube, the steering tube, and the second flat tube form the semiannular inner channel.

5. The evaporator according to claim 3, wherein the heat exchange tube assembly comprises a plurality of semiannular flat tubes arranged at intervals, the plurality of semiannular flat tubes are nested layer by layer, and each of the plurality of semiannular flat tubes has the semiannular inner channel.

6. The evaporator according to claim 5, wherein the second direction is perpendicular to a plane formed by the first direction and a direction where air passes through the evaporator.

7. The evaporator according to claim 5, wherein the second direction is arranged along a direction where air passes through the evaporator, and the first manifold is positioned on an air outlet side of the evaporator.

8. The evaporator according to claim 2, wherein both the first manifold and the second manifold are arranged along the first direction, and the second direction is perpendicular to a plane formed by the first direction and a direction where air passes through the evaporator; and the heat exchange tube assembly comprises a plurality of heat exchange flat tubes, and each of the plurality of heat exchange flat tubes is communicated between the first manifold and the second manifold.

9. A wind wall apparatus, comprising a fan and a evaporator, wherein the fan is arranged on a side of the evaporator and is configured to guide air to pass through the evaporator; the evaporator, wherein a long edge of a windward side of the evaporator is arranged along a first direction; and the evaporator comprises:a manifold assembly comprising a first manifold and a second manifold, wherein the first manifold has a liquid inlet hole, and the second manifold has a liquid outlet hole; the second manifold and the first manifold are arranged at intervals along a second direction, and the second direction intersects with the first direction; anda heat exchange tube assembly having a first end and a second end arranged opposite to each other, wherein the first end is communicated with the liquid inlet hole through an inner cavity of the first manifold, and the second end is communicated with the liquid outlet hole through an inner cavity of the second manifold.

10. The wind wall apparatus according to claim 9, wherein the second direction is perpendicular to the first direction.

11. The wind wall apparatus according to claim 10, wherein the manifold assembly is communicated at one end of the heat exchange tube assembly along the first direction; and the heat exchange tube assembly forms a semiannular inner channel, and two ends of the semiannular inner channel are communicated with the inner cavity of the first manifold and the inner cavity of the second manifold, respectively.

12. The wind wall apparatus according to claim 11, wherein the heat exchange tube assembly comprises a plurality of flat tubes and a steering tube, the steering tube and the manifold assembly are arranged at intervals along the first direction, the plurality of flat tubes are communicated between the steering tube and the manifold assembly, the plurality of flat tubes comprise a first flat tube and a second flat tube, the first flat tube is communicated between the steering tube and the first manifold, the second flat tube is communicated between the steering tube and the second manifold, and the first flat tube, the steering tube, and the second flat tube form the semiannular inner channel.

13. The wind wall apparatus according to claim 12, wherein the heat exchange tube assembly comprises a plurality of semiannular flat tubes arranged at intervals, the plurality of semiannular flat tubes are nested layer by layer, and each of the plurality of semiannular flat tubes has the semiannular inner channel.

14. The wind wall apparatus according to claim 13, wherein the second direction is perpendicular to a plane formed by the first direction and a direction where air passes through the evaporator.

15. The wind wall apparatus according to claim 13, wherein the second direction is arranged along a direction where air passes through the evaporator, and the first manifold is positioned on an air outlet side of the evaporator.

16. The wind wall apparatus according to claim 10, wherein both the first manifold and the second manifold are arranged along the first direction, and the second direction is perpendicular to a plane formed by the first direction and a direction where air passes through the evaporator; and the heat exchange tube assembly comprises a plurality of heat exchange flat tubes, and each of the plurality of heat exchange flat tubes is communicated between the first manifold and the second manifold.

17. An air conditioning device, comprising a compressor, a condenser, and the wind wall apparatus as claimed in claim 9, wherein a liquid inlet hole of the evaporator of the wind wall apparatus is communicated with an outflow end of the condenser, a liquid outlet hole of the evaporator of the wind wall apparatus is communicated with an inflow end of the compressor, and an outflow end of the compressor is communicated with an inflow end of the condenser.