Patent ID: 12215932

DETAILED DESCRIPTION

Embodiments of this application are described in detail below, and examples of the embodiments are shown in the accompanying drawings. The embodiments described below with reference to the accompanying drawings are examples, and are intended to explain this application, but shall not be understood as a limitation on this application. In the description of this application, it should be understood that an orientation or positional relationship indicated by the term “center”, “longitudinal”, “transverse”, “length”, “width”, “thickness”, “upper”, “lower”, “front”, “back”, “left”, “right”, “vertical”, “horizontal”, “top”, “bottom”, “internal”, “external”, “clockwise”, “counterclockwise”, “axial direction”, “radial direction”, “circumferential direction”, or the like is based on an orientation or positional relationship shown in the accompanying drawings, and is merely for ease of describing this application and simplifying the description, but does not indicate or imply that an apparatus or an element fixture referred to must have a specific orientation or be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation to this application.

When a multi-channel heat exchanger works and exchanges heat in a refrigeration and air-conditioning system, refrigerant flows through an inner channel of the multi-channel heat exchanger, and airflow exchanges heat with the refrigerant in the heat exchanger through a surface of the heat exchanger. As shown inFIG.19, the refrigeration and air-conditioning system includes a compressor100, a first heat exchanger200, a throttle member300, a second heat exchanger400, and a fan500. The compressor100, the first heat exchanger200, the throttle member300, and the second heat exchanger400are connected in series to form a circulation loop. A fan500is aligned with the first heat exchanger200to blow air to the first heat exchanger200, and another fan500is aligned with the second heat exchanger400to blow air to the second heat exchanger400. Either or each of the heat exchanger200and the heat exchanger400may be a heat exchanger1in this application.

The following describes a heat exchanger1according to an embodiment in an aspect of this application with reference toFIG.1toFIG.18.

As shown inFIG.1toFIG.18, the heat exchanger1in this embodiment of this application includes a first pipe10, a second pipe20, a plurality of heat exchange tubes30, and a first member40.

The first pipe10includes a circumferential wall and a main channel101surrounded by the circumferential wall. The heat exchanger1further includes an inlet/outlet pipe60, and the inlet/outlet pipe60is connected to the first pipe10. As shown inFIG.1andFIG.2, both the first pipe10and the second pipe20extend in a left-right direction, and the first pipe10and the second pipe20are spaced apart in a front-rear direction. The inlet/outlet pipe60is located on the right side of the first pipe10, and a right end of the first pipe10is connected to a left end of the inlet/outlet pipe60.

An end of the heat exchange tube30is connected to the first pipe10, and the other end of the heat exchange tube30is connected to the second pipe20. The heat exchange tube30is connected to the first pipe10and the second pipe20. The heat exchange tube30includes a plurality of channels301(two or more channels301) arranged to be spaced apart. The channel301is connected to the first pipe10and the second pipe20. The plurality of channels301include a first channel and a second channel. On the cross section of the heat exchange tube30, a flow cross-sectional area of the first channel is greater than a flow cross-sectional area of another channel301different from the first channel in the plurality of channels301, and a flow cross-sectional area of the second channel is less than a flow cross-sectional area of another channel301different from the second channel in the plurality of channels301.

As shown inFIG.1andFIG.2, the heat exchange tube30extends in the front-rear direction, and the plurality of heat exchange tubes30are arranged to be spaced apart between the first pipe10and the second pipe20in the left-right direction. A front end of the heat exchange tube30is connected to the first pipe10, and a rear end of the heat exchange tube30is connected to the second pipe20. As shown inFIG.4andFIG.5, each heat exchange tube30is formed with a plurality of channels301arranged to be spaced apart in an up-down direction, and the channel301extends in the front-rear direction. A front end of the channel301is connected to the first pipe10, and a rear end of the channel301is connected to the second pipe20. A channel301of the plurality of channels301that has a largest flow cross-sectional area is a first channel, and a channel301of the plurality of channels301that has a smallest flow cross-sectional area is a second channel. It should be noted that, in this technical solution, there may be a plurality of first channels and a plurality of second channels, and flow cross-sectional areas of the plurality of channels301may be completely different or partially the same.

In some embodiments of the present disclosure, the plurality of channels301may include only two groups of channels, namely one group of first channels and the other group of second channels. That is, the plurality of channels301only include the first channel and the second channel. The flow cross-sectional area of the first channel is larger than the flow cross-sectional area of the second channel. It may be understood that the group of first channels may include one or more first channels, and the group of second channels may also include one or more second channels.

The first member40is located in the main channel101of the first pipe10, and the first member40extends by a specific distance along a length direction of the first pipe10. A length of the first member40in the main channel101of the first pipe10is less than or equal to a length of the first pipe10. The main channel101includes a first flow channel1011and a second flow channel1012, and the first member40is located between the first flow channel1011and the second flow channel1012. The first flow channel1011is connected to the inlet/outlet pipe60, and the second flow channel1012is connected to the heat exchange tube30. The first member40includes a plurality of through-holes401, and the through-hole401connects the first flow channel1011and the second flow channel1012.

As shown inFIG.2andFIG.3, the first member40penetrates through the main channel101in the left-right direction, and the first member40is provided with through-holes401spaced apart in the left-right direction. Both the first flow channel1011and the second flow channel1012extend in the left-right direction, and the first member40separates the first flow channel1011from the second flow channel1012. A right end of the first flow channel1011is connected to the inlet/outlet pipe, and the second flow channel1012is connected to front ends of the plurality of heat exchange tubes30. It may be understood that refrigerant may flow into the first flow channel1011along the inlet/outlet pipe, and the refrigerant in the first flow channel1011flows into the second flow channel1012through the through-holes401on the first member40, and flows into the heat exchange tube30through connection between the second flow channel1012and the heat exchange tube30for further heat exchange.

The flow cross-sectional area of the first channel on the cross section of the heat exchange tube30is A1, the flow cross-sectional area of the second channel on the cross section of the heat exchange tube30is A2, and the A1 and A2 satisfy the following expression: 0.15≤(A1−A2)*N/A3≤3.8. A3 is a sum of flow cross-sectional areas of the plurality of through-holes401of the first member40, and N is a quantity of the heat exchange tubes30connected to the main channel101.

In related technologies, the first member40(such as a distribution pipe) is not provided in the main channel, and flow cross-sectional areas of the plurality of channels in the heat exchange tube are consistent. A heat exchanger in related technologies has problems of uneven distribution of refrigerant in the heat exchange tubes and low heat exchange efficiency. As shown inFIG.15,FIG.16, andFIG.18, it is found by the applicant that when the first member is arranged in the main channel and flow cross-sectional areas of the plurality of channels in the heat exchange tube are inconsistent, it helps improve heat exchange performance of the heat exchanger, and balance a degree of superheat at an outlet of the heat exchanger.

On this basis, it is also found by the applicant that, for distribution of refrigerant in channels of the heat exchanger, a larger difference between flow cross-sectional areas of the plurality of channels in the heat exchange tube, for example, a larger flow cross-sectional area difference between the channel with the largest flow cross-sectional area and the channel with the smallest flow cross-sectional area, better helps improve heat exchange performance. In some embodiments of the present disclosure, flow cross-sectional areas of every two of at least three channels301in the plurality of channels301are not equal to each other on a cross section of the heat exchange tube30. For example, the plurality of channels301may include three or more groups of channels, i.e. one group of first channels, one group of second channels, and one or more groups of other channels. Further, the flow cross-sectional area of the first channel is larger than the flow cross-sectional area of the second channel, and the flow cross-sectional area of the other channel is less than the flow cross-sectional area of the first channel and larger than the flow cross-sectional area of the second channel. It may be understood that the group of first channels may include one or more first channels, the group of second channels may also include one or more second channels, and the one or more groups of other channels each may include one or more other channels.

In addition, a total area of the through-holes on the first member is related to the distribution of the refrigerant in the heat exchange tubes. Moreover, the area of the through-holes affects a flow rate of the refrigerant flowing out of the first member. A larger flow rate better helps evenly mix gas-liquid two-phase refrigerant and better helps improve heat exchange performance. However, if the total area of the through-holes is too large, it hinders mixing of two-phase refrigerant, resulting in aggravated gas-liquid separation and reduced heat exchange performance. If the total area of the through-holes is too small, a pressure drop is large when the refrigerant flows, which also affects heat exchange performance. Therefore, the area of the through-hole on the first member needs to be designed based on a status of the heat exchanger.

When a plurality of heat exchange tubes with channels of different areas are used in cooperation with the first member, distribution of the refrigerant among the heat exchange tubes and distribution among the channels of the heat exchange tube affect each other. For example, the first member distributes refrigerant in the first pipe, and if there is no more refrigerant entering the channel with the largest flow cross-sectional area or refrigerant is evenly distributed among the channels of the heat exchange tube, it is detrimental to heat exchange performance. On the contrary, if distribution of the refrigerant in the first pipe is not even, through design of the channels of the heat exchange tube, distribution of the refrigerant in the channels of the heat exchange tube can adjust a degree of superheat of the refrigerant at the outlet of the heat exchanger and mitigate impact on heat exchange performance.

Based on the analysis above, it is found by the applicant that, on the cross section of the heat exchange tube, the channel with the largest flow cross-sectional area is used as the first channel, the flow cross-sectional area of the first channel is defined as A1, the channel with the smallest flow cross-sectional area is used as the second channel, the flow cross-sectional area of the second channel is defined as A2, the quantity of heat exchange tubes connected to the main channel is N, the sum of the flow cross-sectional areas of the plurality of through-holes of the first member is A3, and there is a design relationship: (A1−A2)*N/A3. As shown inFIG.14, when (A1−A2)*N/A3≤0.15 or (A1−A2)*N/A3≥3.8, heat exchange performance of the heat exchanger decreases. When 0.15≤(A1−A2)*N/A3≤3.8, the design of the heat exchanger adjusts distribution of the refrigerant among the heat exchange tubes and distribution among the channels of a same heat exchange tube, which helps improve heat exchange performance of the heat exchanger1.

Therefore, according to the heat exchanger in this embodiment of this application, the first member is arranged in the main channel of the first pipe to define the first flow channel and the second flow channel in the main channel, and flow cross-sectional areas of the plurality of channels in the heat exchange tube are inconsistent, so that the flow cross-sectional area A1 of the first channel on the cross section of the heat exchange tube, the flow cross-sectional area A2 of the second channel on the cross section of the heat exchange tube, and the quantity N of heat exchange tubes connected to the second flow channel satisfy: 0.15≤(A1−A2)*N/A3≤3.8. This can adjust distribution of refrigerant in the heat exchanger, improve heat exchange performance of the heat exchanger, and adjust a degree of superheat at the outlet of the heat exchanger, to reduce fluctuation of opening of an expansion valve and improve running stability of the refrigeration and air-conditioning system.

In some embodiments, as shown inFIG.2andFIG.3, the first member40is a third pipe (a distribution pipe), and the third pipe includes a third circumferential wall. The third circumferential wall is located between the first flow channel1011and the second flow channel1012, and the third circumferential wall has through-holes401penetrating through the circumferential wall. The through-hole401connects the first flow channel1011and the second flow channel1012, and the third pipe is connected to the inlet/outlet pipe60or the third pipe includes the inlet/outlet pipe.

As shown inFIG.2, the third pipe is a round pipe and penetrates through the main channel101in the left-right direction. A length of a section of the third pipe is equal to a length of the first pipe10. The circumferential wall of the third pipe has the through-holes401that are spaced apart in the left-right direction and that penetrate through the circumferential wall. The second flow channel1012is formed between the circumferential wall of the third pipe and an inner circumferential wall of the first pipe10, the first flow channel1011(a third channel of the third pipe) is formed in the third pipe, and the first flow channel1011and the second flow channel1012are connected through the through-hole401.

Specifically, refrigerant flows into the first flow channel1011along the inlet/outlet pipe60, and the refrigerant in the first flow channel1011flows into the second flow channel1012through the through-holes401on the third pipe, and flows into the heat exchange tube30through connection between the second flow channel1012and the heat exchange tube30. The refrigerant is in the heat exchanger1for heat exchange.

In some embodiments, as shown inFIG.4andFIG.5, a side of the heat exchanger1located upstream in a wind direction during heat exchange is defined as a windward side, and a downstream side of the wind direction of the heat exchanger1is defined as a leeward side. For example, as shown inFIG.10toFIG.12, a side of through-holes401located upstream is the windward side, and a side of through-holes401located downstream is the leeward side. A direction facing an inlet of a channel of the heat exchange tube30is considered 0 degrees. An angle formed between a through-hole401located upstream and an inlet direction of the channel301of the heat exchange tube30is considered as a1. An angle formed between a through-hole401located downstream and the inlet direction of the channel301of the heat exchange tube30is considered as a2. An angle range of a1 is 0 to 180 degrees (including 0 degrees and 180 degrees), and an angle range of a2 is 180 to 360 degrees.

The first channel in the plurality of channels301is located on the windward side, and at least some of the plurality of through-holes are located on the leeward side. Therefore, flow resistance of the refrigerant passing through the first channel is relatively small, so that more refrigerant can flow to the windward side, and a temperature difference between the air flow on the windward side and the refrigerant is large, thereby improving heat exchange performance.

In some embodiments, a sum of flow cross-sectional areas of channels located on the windward side among the plurality of channels301is greater than a sum of flow cross-sectional areas of channels located on the leeward side among the plurality of channels301, and at least some of the plurality of through-holes401are located on the leeward side.

Specifically, the wind may blow through the heat exchange tubes30from upstream to downstream. As shown inFIG.4, the first channel is located upstream on the windward side, and some of the plurality of through-holes401are located downstream on the leeward side.

Therefore, some channels with a smaller sum of flow cross-sectional areas can be arranged on the leeward side of the heat exchange tube, other channels with a larger sum of flow cross-sectional areas can be arranged on the windward side of the heat exchange tube, and at least some of the through-holes are arranged on the leeward side of the heat exchange tube. Rebounding of an inner wall of the first pipe can be utilized, to help more refrigerant flow to the windward side, so as to adjust a degree of superheat at the outlet of the heat exchanger, and improve heat exchange performance of the heat exchanger. For example, all the through-holes401are located on the leeward side, and heat exchange performance of the heat exchanger is better.

In some embodiments, some through-holes of the plurality of through-holes401of the third pipe are located on the windward side, other through-holes of the plurality of through-holes401are located on the leeward side, and a sum of flow cross-sectional areas of the through-holes401on the windward side is less than a sum of flow cross-sectional areas of the through-holes401on the leeward side.

Therefore, some through-holes with a smaller sum of flow cross-sectional areas can be arranged on the leeward side of the heat exchange tube, and other through-holes with a larger sum of flow cross-sectional areas can be arranged on the windward side of the heat exchange tube. This can increase a through-hole area on the windward side and reduce a through-hole area on the leeward side, thereby allowing more refrigerant to flow to the windward side, reducing a difference between degrees of superheat of refrigerant on the windward side and the leeward side, improving refrigerant distribution of the heat exchanger, and improving heat exchange performance of the heat exchanger.

In some embodiments, (A1−A2)/A4≤0.09, where A4 is a largest flow cross-sectional area of the third pipe. As shown inFIG.17, when (A1−A2)/A4≤0.09, heat exchange performance of the heat exchanger1gradually increases with the increase of (A1−A2)/A4. For example, when (A1−A2)/A4=0.09, heat exchange performance of the heat exchanger1is the largest.

In some embodiments, as shown inFIG.3, in a length direction of the third pipe, a distance I between at least two adjacent through-holes401satisfies: 20 mm≤I≤150 mm. Therefore, a quantity of the through-holes401can be properly set, to avoid that a total area of the through-holes is too large or too small, and improve reliability and uniformity of refrigerant distribution by the third pipe. For example, when 20 mm≤I≤150 mm, a distribution effect of the refrigerant is better.

It should be noted that the first member40is not limited to the third pipe shown inFIG.2andFIG.3. For example, as shown inFIG.8andFIG.9, the first member40may alternatively be a plate penetrating through the main channel101in the left-right direction, and the plate is provided with through-holes401that are arranged to be spaced apart in the left-right direction and that penetrate through the plate. The plate defines, in the main channel101, a second flow channel1012located on the rear side of the plate and a first flow channel1011located on the front side of the plate. The refrigerant flows into the first flow channel1011through the inlet/outlet pipe60. The refrigerant in the first flow channel1011flows into the second flow channel1012on the rear side of the plate through the through-holes401on the plate.

In some embodiments, as shown inFIG.1andFIG.2, the first pipe10includes a first end surface, a through-hole401of the plurality of through-holes401that is adjacent to the first end surface (a right end surface of the first pipe10inFIG.2) of the first pipe10in the length direction (the left-right direction inFIG.2) of the first pipe10is a first through-hole, and a heat exchange tube30of the plurality of heat exchange tubes30that is adjacent to the first end surface of the first pipe10is a first heat exchange tube.

The plurality of heat exchange tubes30include a second heat exchange tube, a quantity of heat exchange tubes30located between the first heat exchange tube and the second heat exchange tube in the length direction of the first pipe10is greater than or equal to 10 and less than 30, and a smallest distance between the first through-hole and the first end surface50of the first pipe10in the length direction of the first pipe10is less than a smallest distance between the second heat exchange tube30and the first end surface50of the first pipe10in the length direction of the first pipe10.

As shown inFIG.2,FIG.3, andFIG.13, the rightmost heat exchange tube30of the plurality of heat exchange tubes30is the first heat exchange tube. The 10thheat exchange tube30or the 30thheat exchange tube30counted from right to left, starting from the first heat exchange tube as the 1stheat exchange tube30, is the second heat exchange tube. The right rightmost through-hole401of the plurality of through-holes401is the first through-hole, and a distance between a right edge of an outer circumferential wall of the first through-hole and the right end surface of the first pipe10in the left-right direction is less than a distance between a right side surface of the second heat exchange tube and the right end surface of the first pipe10in the left-right direction.

In some embodiments, as shown inFIG.5, on the cross section of the heat exchange tube30, the flow cross-sectional areas of the plurality of channels301gradually vary along a width direction of the heat exchange tube30(the up-down direction inFIG.5). Therefore, differences in the flow cross-sectional areas of the plurality of channels can be utilized to increase a flow cross-sectional area of the channels on the windward side and reduce a flow cross-sectional area of the channels on the leeward side, so that more refrigerant flows to the windward side, thereby optimizing distribution of holes of the heat exchange tubes, and improving heat exchange performance.

In some embodiments, as shown inFIG.5, on the cross section of the heat exchange tube30, spacings between two adjacent channels301in the width direction (the up-down direction inFIG.5) of the heat exchange tube30are equal to each other, and flow cross-sectional areas of the two adjacent channels301are not equal to each other. In other words, in the width direction of the heat exchange tube30, the plurality of channels301are evenly spaced, that is, thicknesses of a spacing wall between the through-holes are equal, so as to further optimize distribution of the refrigerant in the heat exchange tube30.

In some embodiments, as shown inFIG.8, an outer circumferential contour of the cross-section of the heat exchange tube30is roughly quadrilateral, and an inner diameter of the second pipe20is 1.1 times or more of a width of the heat exchange tube30. Therefore, when refrigerant in the channels flows into the second pipe, pressure of the refrigerant can be reduced, so as to adjust distribution of the refrigerant in the channels. In addition, pressure on a suction side of the air-conditioning and refrigeration system can be reduced, and performance of the air-conditioning and refrigeration system can be improved.

In some embodiments, as shown inFIG.3, the heat exchange tube30includes a first side surface and a second side surface arranged in parallel in a thickness direction (the left-right direction inFIG.3) of the heat exchange tube30. A smallest distance between the channel301and the first side surface of the heat exchange tube30in the thickness direction of the heat exchange tube30is a first distance, and first distances of the plurality of channels301are equal to each other. A smallest distance between the channel301and the second side surface of the heat exchange tube30in the thickness direction of the heat exchange tube30is a second distance, and second distances of the plurality of channels301are equal to each other.

In other words, edges of the plurality of channels301are aligned in the thickness direction of the heat exchange tube30, so that channels301with different flow cross-sectional areas can be formed only by setting dimensions of the plurality of channels301in the width direction of the heat exchange tube30to be different, which facilitates non-uniform design of the plurality of channels301. For example, the first distance of the channel301is equal to the second distance of the channel301.

The following describes a heat exchanger1according to another embodiment in an aspect of this application with reference toFIG.1toFIG.18.

The heat exchanger1according to this embodiment of the present invention includes a first pipe10, a second pipe20, a plurality of heat exchange tubes30, and a first member40. The first pipe10includes a circumferential wall and a main channel101surrounded by the circumferential wall. An end in a length direction of the first pipe10is a first end (a right end of the first pipe10inFIG.2), and the first end of the first pipe10includes a first end surface50. The heat exchanger1further includes an inlet/outlet pipe60, and the inlet/outlet pipe60is connected to the first pipe10.

As shown inFIG.1andFIG.2, both the first pipe10and the second pipe20extend in a left-right direction, and the first pipe10and the second pipe20are spaced apart in a front-rear direction. The right end of the first pipe10includes a first end surface. The inlet/outlet pipe is located on the right side of the first pipe10, and the right end of the first pipe10is connected to a left end of the inlet/outlet pipe60.

An end of the heat exchange tube30is connected to the first pipe10, and the other end of the heat exchange tube30is connected to the second pipe20. The heat exchange tube30is connected to the first pipe10and the second pipe20. The heat exchange tube30includes a plurality of channels301arranged to be spaced apart. The channel301is connected to the first pipe10and the second pipe20. The plurality of channels301include a first channel and a second channel. On the cross section of the heat exchange tube30, a flow cross-sectional area of the first channel is greater than a flow cross-sectional area of another channel different from the first channel in the plurality of channels, and a flow cross-sectional area of the second channel is less than a flow cross-sectional area of another channel different from the second channel in the plurality of channels.

As shown inFIG.1andFIG.2, the heat exchange tube30extends in the front-rear direction, and the plurality of heat exchange tubes30are arranged to be spaced apart between the first pipe10and the second pipe20in the left-right direction. A front end of the heat exchange tube30is connected to the first pipe10, and a rear end of the heat exchange tube30is connected to the second pipe20. As shown inFIG.4andFIG.5, each heat exchange tube30is formed with a plurality of channels301arranged to be spaced apart in an up-down direction, and the channel301extends in the front-rear direction. A front end of the channel301is connected to the first pipe10, and a rear end of the channel301is connected to the second pipe20. A channel301of the plurality of channels301that has a largest flow cross-sectional area is a first channel, and a channel301of the plurality of channels301that has a smallest flow cross-sectional area is a second channel.

It should be noted that, as shown inFIG.6andFIG.7, flow cross-sectional areas of the plurality of channels301are different, and the plurality of channels301may include a large channel and a small channel (as shown inFIG.6), or may include a group of large channels and a group of small channels (as shown inFIG.7), or flow cross-sectional areas of the plurality of channels301vary gradually along a width direction of the heat exchange tube30(as shown inFIG.5), or flow cross-sectional areas of the channels301vary in proportion to the width direction of the heat exchange tube30. Certainly, flow cross-sectional areas of the channels301may alternatively vary according to a specific rule, such as a polynomial rule or an exponential rule along the width direction of the heat exchange tube30.

In some embodiments of the present disclosure, the plurality of channels301may include only two groups of channels, namely one group of first channels and the other group of second channels. That is, the plurality of channels301only include the first channel and the second channel. The flow cross-sectional area of the first channel is larger than the flow cross-sectional area of the second channel. It may be understood that the group of first channels may include one or more first channels, and the group of second channels may also include one or more second channels.

In some embodiments of the present disclosure, flow cross-sectional areas of at least three channels301are not equal to each other on a cross section of the heat exchange tube30. For example, the plurality of channels301may include three or more groups of channels, i.e. one group of first channels, one group of second channels, and one or more groups of other channels. Further, the flow cross-sectional area of the first channel is larger than the flow cross-sectional area of the second channel, and the flow cross-sectional area of the other channel is less than the flow cross-sectional area of the first channel and larger than the flow cross-sectional area of the second channel. It may be understood that the group of first channels may include one or more first channels, the group of second channels may also include one or more second channels, and the one or more groups of other channels each may include one or more other channels.

The first member40is located in the main channel101of the first pipe10, and the first member40extends by a specific distance along a length direction of the first pipe10. The main channel101includes a first flow channel1011and a second flow channel1012, and the first member40is located between the first flow channel1011and the second flow channel1012. The first flow channel1011is connected to the inlet/outlet pipe60, and the second flow channel1012is connected to the heat exchange tube30. The first member40includes a plurality of through-holes401, and the through-hole401connects the first flow channel1011and the second flow channel1012.

As shown inFIG.2andFIG.3, the first member40penetrates through the main channel101in the left-right direction, and the first member40is provided with through-holes401spaced apart in the left-right direction. Both the first flow channel1011and the second flow channel1012extend in the left-right direction, and the first member40separates the first flow channel1011from the second flow channel1012. A right end of the first flow channel1011is connected to the inlet/outlet pipe60, and the second flow channel1012is connected to front ends of the plurality of heat exchange tubes30. It may be understood that refrigerant may flow into the first flow channel1011along the inlet/outlet pipe60, and the refrigerant in the first flow channel1011flows into the second flow channel1012through the through-holes401on the first member40, and flows into the heat exchange tube30through connection between the second flow channel1012and the heat exchange tube30for further heat exchange.

A through-hole401of the plurality of through-holes401that is adjacent to the first end surface50of the first pipe10is a first through-hole. That is, a through-hole401of the plurality of through-holes401that has a smallest distance to the first end surface50of the first pipe10is the first through-hole. The smallest distance between the first through-hole and the first end surface50of the first pipe10in the length direction of the first pipe10is d3, and d3<(10d1+9d2)*A1/A2, where d1 is a thickness of the heat exchange tube30, d2 is a smallest distance between adjacent heat exchange tubes30in the length direction of the first pipe10, A1 is a flow cross-sectional area of the first channel on the cross section of the heat exchange tube30, and A2 is a flow cross-sectional area of the second channel on the cross section of the heat exchange tube30.

As shown inFIG.2,FIG.3, andFIG.13, the rightmost through-hole401of the plurality of through-holes401is the first through-hole, and a distance between a right edge of an outer circumferential wall of the first through-hole and the right end surface of the first pipe10in the left-right direction is less than a distance between a right side surface of the second heat exchange tube and the right end surface of the first pipe10in the left-right direction, and is the smallest distance d3 between the first through-hole and the right end surface (the first end surface) of the first pipe10in the left-right direction.

It is found that the distance d3 from the first through-hole of the first member to the end of the first pipe affects distribution of refrigerant among tubes. The end of the first pipe is adjacent to the inlet/outlet pipe. When the distance exceeds a specified value, the refrigerant accumulates at the end, which affects a degree of superheat of a heat exchange tube near the inlet/outlet pipe, thereby resulting in a severe imbalance in distribution of refrigerant among the heat exchange tubes and a decrease in heat exchange performance.

On this basis, it is found that, the heat exchanger has high heat exchange performance when the thickness d1 of the heat exchange tube, the smallest distance d2 between adjacent heat exchange tubes in the length direction of the first pipe, the flow cross-sectional area A1 of the first channel on the cross section of the heat exchange tube, and the flow cross-sectional area A2 of the second channel on the cross-section of the heat exchange tube satisfy the expression: (10d1+9d2)*A1/A2 and d3<(10d1+9d2)*A1/A2.

Therefore, according to the heat exchanger in this embodiment of the present invention, the first member having a plurality of through-holes is arranged in the main channel of the first pipe to define the first flow channel and the second flow channel in the main channel, and flow cross-sectional areas of the plurality of channels in the heat exchange tube are inconsistent, so that the flow cross-sectional area A1 of the first channel on the cross section of the heat exchange tube, the flow cross-sectional area A2 of the second channel on the cross section of the heat exchange tube, the thickness d1 of the heat exchange tube, the smallest distance d2 between adjacent heat exchange tubes in the length direction of the first pipe, and the distance d3 between the first through-hole of the first member and the end of the first pipe satisfy: d3(10d1+9d2)*A1/A2. This can make degrees of superheat of the heat exchange tubes even, so that distribution of refrigerant among the heat exchange tubes is appropriate, and improves performance of the heat exchanger.

In some embodiments, an end of a third pipe is connected to the inlet/outlet pipe60, the other end of the third pipe has a hole, and a flow cross-sectional area of the hole is less than a flow cross-sectional area of the third pipe. In this way, internal flow of the first pipe is promoted, distribution of refrigerant among the tubes is more even, and heat exchange performance is improved.

In some embodiments, a hydraulic diameter of the second pipe20is greater than or equal to 1.1 times of a hydraulic diameter of the first pipe10. Therefore, a pressure drop in the heat exchange tubes and the first pipe can be balanced, distribution of refrigerant among the heat exchange tubes can be more even, and a pressure drop on a suction side of a refrigeration system can be reduced, to improve performance of the refrigeration system.

In some embodiments, an outer circumferential contour of the cross-section of the heat exchange tube30is roughly quadrilateral, and an inner diameter of the second pipe20is 1.1 times or more of a width of the heat exchange tube30. Therefore, a pressure drop in the heat exchange tubes and the first pipe can be balanced, distribution of refrigerant among the heat exchange tubes can be more even, and a pressure drop on a suction side of a refrigeration system can be reduced, to improve performance of the refrigeration system.

The following describes a heat exchanger1according to some examples of this application with reference toFIG.1toFIG.13.

In some examples, as shown inFIG.1toFIG.13, a heat exchanger1includes a first pipe10, a second pipe20, a third pipe, an inlet/outlet pipe60, and a plurality of heat exchange tubes30.

Both the first pipe10and the first pipe10extend in a left-right direction, and the first pipe10and the second pipe20are spaced apart in a front-rear direction. The plurality of heat exchange tubes30connect the first pipe10and the second pipe20, and the plurality of heat exchange tubes30are arranged to be spaced apart in the left-right direction. Front ends of the plurality of heat exchange tubes30are connected to the first pipe10, and rear ends of the plurality of heat exchange tubes30are connected to the second pipe20.

The first pipe10includes a first end surface50and a main channel extending in the left-right direction. The third pipe penetrates through the main channel in the left-right direction. A first flow channel1011is formed inside the third pipe, and a second flow channel1012is formed between a circumferential wall of the third pipe and an inner circumferential wall of the first pipe10. The front end of the heat exchange tube30is connected to the second flow channel1012. The circumferential wall of the third pipe is provided with a plurality of through-holes401that are arranged to be spaced apart in a length direction of the third pipe and that pass through the circumferential wall of the third pipe.

A right end of the third pipe is provided with an opening, and the opening of the third pipe is connected to an inlet of the first pipe10. Refrigerant may flow into the first flow channel through the inlet of the first pipe10, and the refrigerant in the first flow channel1012flows into the second flow channel1012through the through-holes401. The refrigerant in the second flow channel1012may flow into the heat exchange tube30for heat exchange.

The heat exchange tube30has a plurality of channels301arranged to be spaced apart in an up-down direction, and the plurality of channels301extend in the front-rear direction. Flow cross-sectional areas of the plurality of channels301gradually vary along the up-down direction. Through-holes401with a larger sum of flow cross-sectional areas are arranged on a lower side (a windward side) of the heat exchange tube30, and through-holes401with a smaller sum of flow cross-sectional areas are arranged on an upper side (a leeward side) of the heat exchange tube30. Edges of the plurality of channels301are aligned in a thickness direction of the heat exchange tube30, and smallest distances between adjacent channels301in the plurality of channels301in the up-down direction are equal to each other.

In the left-right direction, the rightmost heat exchange tube30of10heat exchange tubes30closest to the first end surface50is a first heat exchange tube30, and the plurality of heat exchange tubes30include a second heat exchange tube. In a length direction of the first pipe10, a quantity of heat exchange tubes30located between the first heat exchange tube and the second heat exchange tube is greater than or equal to 10 and less than 30. The rightmost through-hole401of the plurality of through-holes401is a first through-hole, and the first through-hole is located between the first heat exchange tube30and the second heat exchange tube30.

In some other examples, as shown inFIG.8andFIG.9, a first member40is a plate penetrating through the main channel101in the left-right direction, and the plate is provided with through-holes401that are arranged to be spaced apart in the left-right direction and that penetrate through the plate. The plate defines, in the main channel101, a second flow channel1012located on the rear side of the plate and a first flow channel1011located on the front side of the plate. The refrigerant flows into the first flow channel1011through the inlet/outlet pipe60. The refrigerant in the first flow channel1011flows into the second flow channel1012on the rear side of the plate through the through-holes401on the plate.

In the description of this specification, descriptions with reference to the term such as “an embodiment”, “some embodiments”, “example”, “specific example”, or “some examples” mean that specific features, structures, materials, or characteristics described with reference to the embodiment or example are included in at least one embodiment or example of this application. In this specification, illustrative descriptions of the foregoing terms do not necessarily refer to a same embodiment or example. Moreover, the described specific features, structures, materials, or characteristics can be combined in any one or more embodiments or examples in an appropriate manner. In addition, those skilled in the art can combine different embodiments or examples described in the specification and features of the different embodiments or examples without contradicting each other.

The terms “first”, “second”, and the like in the description of this application are merely used for the purpose of description, and cannot be understood as indicating or implying relative importance. In the description of this application, “a plurality of” means at least two, such as two or three, unless otherwise specifically defined.

In this application, unless otherwise expressly specified and defined, terms such as “install”, “connect”, “connected to”, and “fasten” should be understood in a broad sense. For example, unless otherwise expressly defined, a “connection” may be a fixed connection, may be a detachable connection, or may be an integrated connection; or may be a mechanical connection, or an electrical connection or, mutually communicative connection; or may be a direct connection, or an indirect connection through an intermediate medium; or may be an inner connection between two elements, or interaction between two elements. A person of ordinary skill in the art may understand specific meanings of the foregoing terms in this application with reference to specific circumstances.

In this application, unless otherwise expressly specified and defined, that a first feature is “above” or “below” a second feature means that the first feature and the second feature are in direct contact, or are in indirect contact through an intermediate medium. Moreover, that the first feature is “over”, “above”, or “on” the second feature may mean that the first feature is over or obliquely above the second feature, or merely mean that the first feature is higher than the second feature in terms of heights. That the first feature is “under”, “below”, “under”, or “beneath” the second feature may mean that the first feature is under or obliquely below the second feature, or merely mean that the first feature is lower than the second feature in terms of heights.

Although the embodiments of this application are shown and described above, it can be understood that the foregoing embodiments are examples and shall not be construed as a limitation on this application. A person of ordinary skill in the art may make changes, modifications, substitutions, and variants based on the foregoing embodiments within the scope of this application.