WO2018098991A1 - 蒸发器的管路、蒸发器及空调器 - Google Patents

蒸发器的管路、蒸发器及空调器 Download PDF

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Publication number
WO2018098991A1
WO2018098991A1 PCT/CN2017/082617 CN2017082617W WO2018098991A1 WO 2018098991 A1 WO2018098991 A1 WO 2018098991A1 CN 2017082617 W CN2017082617 W CN 2017082617W WO 2018098991 A1 WO2018098991 A1 WO 2018098991A1
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WIPO (PCT)
Prior art keywords
pipe
heat exchange
pipe section
refrigerant
pipeline
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PCT/CN2017/082617
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English (en)
French (fr)
Inventor
赵夫峰
Original Assignee
美的集团武汉制冷设备有限公司
美的集团股份有限公司
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Priority claimed from CN201621303819.6U external-priority patent/CN206222755U/zh
Priority claimed from CN201611075098.2A external-priority patent/CN106403394A/zh
Application filed by 美的集团武汉制冷设备有限公司, 美的集团股份有限公司 filed Critical 美的集团武汉制冷设备有限公司
Publication of WO2018098991A1 publication Critical patent/WO2018098991A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
    • F24F13/30—Arrangement or mounting of heat-exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators

Definitions

  • the invention relates to the technical field of household appliances, in particular to a pipeline, an evaporator and an air conditioner of an evaporator.
  • the present invention aims to solve at least one of the technical problems in the related art to some extent.
  • the invention proposes a pipeline of an evaporator, which has the advantages of simple structure and good heat exchange effect.
  • the invention also proposes an evaporator having a conduit for the evaporator described above.
  • Another object of the present invention is to provide an air conditioner having the above-described evaporator.
  • a pipeline of an evaporator having an inlet and an outlet and comprising: a first pipe section for circulating a liquid refrigerant, the inlet being located at one end of the first pipe section, the first pipe section being located at The windward side of the pipeline and the diameter of the pipe is D1; the second pipe segment, one end of the second pipe segment is in communication with the other end of the first pipe segment and is located on the leeward side of the pipeline, and the pipe of the second pipe segment a diameter D2, wherein D1>D2; and a third pipe segment for the gas-phase refrigerant to circulate, one end of the third pipe segment is in communication with the other end of the second pipe segment, and the outlet is located at the other end of the third pipe segment .
  • the flow velocity and heat exchange efficiency of the refrigerant can be controlled by the change of the pipe diameter, and different pipe diameters are reasonably selected on the windward side and the leeward side.
  • the pipe section can effectively improve the heat exchange efficiency of the evaporator, thereby effectively improving the heat exchange performance of the evaporator in the limited space of the evaporator, thereby improving the overall performance of the product.
  • the diameter of the first pipe section ranges from 6 mm ⁇ D1 ⁇ 7.5 mm.
  • the diameter of the second pipe section ranges from 3 mm ⁇ D2 ⁇ 6.5 mm.
  • the first pipe section has a plurality of first straight pipe sections extending in a straight line, and a vertical distance between two of the first straight pipe sections adjacent to each other is P, the third pipe section With multiple segments extending in a straight line
  • the outlet is located on the leeward side of the pipeline.
  • the conduit includes a plurality of U-tubes in sequence, each of the two straight sections of the U-tube being at a distance M.
  • An evaporator includes: a post-steaming heat exchange portion; a first pre-steaming heat exchange portion, the first pre-steaming heat exchange portion is connected to the post-steaming heat exchange portion; and the second pre-steaming heat exchange portion And the second pre-steaming heat exchange portion is connected to the first pre-steaming heat exchange portion; and the pipeline of the evaporator described above, at least a portion of the first pipe segment of the pipeline is arranged a windward heat exchange portion and a windward side of the first pre-steaming heat exchange portion, at least a portion of the second pipe section of the pipeline being arranged in the post-steaming heat exchange portion and the first front steaming At the leeward side of the hot portion, at least a portion of the third tube section of the conduit is disposed on the second pre-steaming heat exchange portion.
  • a flow path structure with different pipe diameters is designed reasonably, and the small pipe is fully utilized in the gas-liquid two-phase mixing zone.
  • the fast flow rate of the refrigerant in the bore and the small flow path of the small pipe diameter improve the heat transfer performance of the refrigerant in the gas-liquid two-phase mixing zone; the flow pipe section mainly composed of gas phase refrigerant and the flow pipe segment mainly composed of liquid phase refrigerant
  • the use of a single pipe diameter with a large pipe diameter reduces the flow path and reduces the flow rate of the refrigerant, and increases the heat exchange area between the air and the refrigerant, and improves the flow pipe section mainly composed of the gas phase refrigerant and the liquid phase refrigerant.
  • the heat exchange efficiency between the refrigerant and the air in the main flow pipe section improves the overall heat exchange performance of the evaporator.
  • the post-steaming heat exchange portion, the first pre-steaming heat exchange portion, and the second pre-steaming heat exchange portion are equal in width.
  • the air conditioner has the evaporator described above.
  • a flow path structure with different pipe diameters is designed reasonably, and the small pipe is fully utilized in the gas-liquid two-phase mixing zone.
  • the fast flow rate of the refrigerant in the bore and the small flow path of the small pipe diameter improve the heat transfer performance of the refrigerant in the gas-liquid two-phase mixing zone; the flow pipe section mainly composed of gas phase refrigerant and the flow pipe segment mainly composed of liquid phase refrigerant
  • the use of a single pipe diameter with a large pipe diameter reduces the flow path and reduces the flow rate of the refrigerant, and increases the heat exchange area between the air and the refrigerant, and improves the flow pipe section mainly composed of the gas phase refrigerant and the liquid phase refrigerant.
  • the heat exchange efficiency between the refrigerant and the air in the main flow pipe section improves the overall heat exchange performance of the evaporator.
  • FIG. 1 is a schematic structural view of a piping of an evaporator according to an embodiment of the present invention
  • FIG. 2 is a schematic structural view showing an unfolded state of a pipe of an evaporator according to an embodiment of the present invention
  • FIG. 3 is a schematic structural view of a pipeline of an evaporator according to an embodiment of the present invention.
  • FIG. 4 is a schematic structural view of an unfolded state of a pipe of an evaporator according to an embodiment of the present invention.
  • the first pre-steaming heat exchange unit 220 The first pre-steaming heat exchange unit 220,
  • the second pre-steaming heat exchange unit 230 The second pre-steaming heat exchange unit 230,
  • first and second are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated.
  • features defining “first” or “second” may include at least one of the features, either explicitly or implicitly.
  • the meaning of "a plurality” is at least two, such as two, three, etc., unless specifically defined otherwise.
  • the terms “installation”, “connected”, “connected”, “fixed” and the like shall be understood broadly, and may be either a fixed connection or a detachable connection, unless explicitly stated and defined otherwise. Or in one; can be
  • the mechanical connections may also be electrically connected or communicated with each other; they may be directly connected or indirectly connected through an intermediate medium, and may be internal communication of two elements or an interaction relationship of two elements unless explicitly defined otherwise.
  • the specific meanings of the above terms in the present invention can be understood on a case-by-case basis.
  • a line 100, an evaporator, and an air conditioner of an evaporator according to an embodiment of the present invention will be described below with reference to Figs.
  • a pipeline 100 has an inlet 10 and an outlet 20 and includes: a first pipe section 30, a second pipe section 40, and a third pipe section 50.
  • the first pipe section 30 is for circulating liquid refrigerant, the inlet 10 of the pipeline 100 is located at one end of the first pipe section 30, the first pipe section 30 is located on the windward side X of the pipe 100, and the pipe diameter of the first pipe section 30 is D1.
  • One end of the second pipe section 40 communicates with the other end of the first pipe section 30 and is located on the leeward side Y of the pipe 100, and the pipe diameter of the second pipe section 40 is D2.
  • the third pipe section 50 is for gas-phase refrigerant to flow, one end of the third pipe section 50 is in communication with the other end of the second pipe section 40, and the outlet 20 of the pipe line 100 is located at the other end of the third pipe section 50.
  • the direction indicated by the arrow is the flow direction of the refrigerant in the pipe 100.
  • the refrigerant flows from the inlet 10 of the pipeline 100 into the pipeline 100 and sequentially flows through the first pipe section 30, the second pipe section 40 and the third pipe section 50, and the liquid refrigerant gradually evaporates and absorbs heat during the flow in the pipe 100.
  • the gaseous refrigerant finally flows out from the outlet 20.
  • the flowing refrigerant is mainly liquid refrigerant.
  • the flowing refrigerant is a refrigerant mixed with a gaseous refrigerant and a liquid refrigerant, in the third pipe section.
  • the flowing refrigerant is mainly gaseous refrigerant.
  • the refrigerant When the refrigerant is converted into a gaseous state from a liquid state, a large amount of heat is absorbed from the periphery of the pipe 100, so that the refrigeration function of the evaporator can be achieved.
  • the flow rate and heat exchange efficiency of the refrigerant can be controlled by the change of the pipe diameter, and on the windward side X Reasonable selection of different pipe diameter segments with the leeward side Y can effectively improve the heat exchange efficiency of the evaporator, thereby effectively improving the heat transfer performance of the evaporator in the space occupied by the evaporator, thereby improving the overall performance of the product.
  • the diameter of the first pipe section 30 ranges from 6 mm ⁇ D1 ⁇ 7.5 mm. It has been experimentally verified that when the diameter of the first pipe section 30 satisfies: 6 mm ⁇ D1 ⁇ 7.5 mm, the heat exchange efficiency of the evaporator pipe 100 can be effectively improved.
  • the first pipe segment 30 is located at the windward side X, and the air entering the evaporator is first contacted with the first pipe segment 30, and the refrigerant flowing in the first pipe segment 30 is mainly liquid refrigerant, and the first pipe segment 30 is diameter.
  • the larger setting can increase the effective area of the heat exchange surface of the air and the refrigerant, thereby improving the heat exchange efficiency of the evaporator.
  • the diameter of the second pipe section 40 ranges from 3 mm ⁇ D2 ⁇ 6.5 mm. It has been experimentally verified that when the diameter of the second pipe section 40 satisfies: 3 mm ⁇ D2 ⁇ 6.5 mm, the flow rate and the phase change rate of the refrigerant can be effectively increased, so that the heat exchange efficiency of the evaporator pipe 100 can be further improved. It is to be understood that, in the process of flowing the refrigerant from the first pipe section 30 into the second pipe section 40, the pipe diameter of the second pipe section 40 is designed to be smaller than the pipe diameter of the first pipe section 30.
  • the flow rate of the refrigerant will be When the flow rate is increased, the heat exchange rate between the refrigerant and the outside air is accelerated, thereby further increasing the evaporator line 100.
  • the heat exchange rate, and the phase change rate of the refrigerant is accelerated, and the conversion rate of the refrigerant from the liquid state to the gaseous state is accelerated, thereby improving the refrigeration effect of the evaporation and heat absorption of the refrigerant.
  • D3 D1
  • the pipe diameter of the third pipe section 50 is equal to the pipe diameter of the first pipe section 30, on the one hand, the processing and manufacture of the evaporator pipe 100 can be facilitated, thereby reducing the production cost.
  • the refrigerant flows from the second pipe section 40 to the third pipe section 50, most of the gas-liquid two-phase mixed refrigerant is converted into a gaseous refrigerant, and the pipe diameter of the third pipe section 50 is correspondingly designed to be large, and the pipeline 100 can be reduced.
  • the flow path branch optimizes the layout of the pipeline 100, and increases the effective heat exchange area between the gaseous refrigerant and the outside air to improve the heat exchange efficiency of the evaporator line 100.
  • the first pipe section 30 has a plurality of first straight straight pipe sections 310 extending in a straight line, and a vertical distance between two first straight straight pipe sections 310 adjacent to each other
  • the first pipe section 30 is arranged as a plurality of first straight straight pipe sections 310 extending in a straight line
  • the third pipe section 50 is arranged to have a plurality of second straight straight pipe sections 510 extending in a straight line, which is advantageous for maintaining the refrigerant in the pipeline 100.
  • the stability during the flow process so that the refrigerant and the outside air have a stable heat exchange rate, which is beneficial to ensure the heat transfer performance of the evaporator.
  • the vertical distance P between the first straight pipe sections 310 and the vertical distance E between the second straight pipe sections 510 are equal, which facilitates the processing and layout optimization of the pipeline 100, and is advantageous for reducing the production cost.
  • the outlet 20 is located on the leeward side Y of the line 100.
  • the cooling amount of the refrigerant in the pipe 100 can be sufficiently transmitted and utilized, thereby improving the heat exchange efficiency of the evaporator.
  • the outside air flows into the evaporator from the windward side X of the evaporator, and exchanges heat with the refrigerant flowing in the evaporator line 100, and the air after the heat exchange flows out from the leeward side Y to the evaporator.
  • the outlet 20 of the pipeline 100 is disposed on the leeward side Y of the pipeline 100, so that the refrigerant in the pipeline 100 and the air in the evaporator have the longest contact time in a limited space to ensure sufficient air and refrigerant.
  • the heat exchange so that the cooling capacity of the refrigerant is fully utilized, improves the heat exchange performance of the evaporator.
  • the conduit 100 includes a plurality of U-tubes in sequence, each of which has a distance M between the two straight sections. Therefore, the pipeline 100 which is connected by a plurality of U-shaped tubes can recirculate the refrigerant in the pipeline 100, thereby effectively extending the flow distance of the refrigerant, thereby prolonging the heat exchange time between the refrigerant and the air, and improving the evaporation. Heat exchange efficiency. Moreover, the distance between the two straight pipe sections of each U-shaped pipe is M, which facilitates the processing and manufacturing of the pipe 100, thereby simplifying the manufacturing process and reducing the production cost.
  • the evaporator may include: a post-steaming heat exchange portion 210, a first pre-steaming heat exchange portion 220, a second pre-steaming heat exchange portion 230, and the above The line 100 of the evaporator.
  • the first pre-steaming heat exchange unit 220 is connected to the post-steaming heat exchange unit 210
  • the second pre-steaming heat exchange unit 230 is connected to the first pre-steaming heat exchange unit 220.
  • Pipeline At least a portion of the first tube section 30 of the 100 is disposed on the windward side X of the post-steaming heat exchange portion 210 and the first pre-steaming heat exchange portion 220, and at least a portion of the second tube portion 40 of the line 100 is disposed in the post-steaming heat exchange portion 210 And the leeward side Y of the first pre-steaming heat exchange portion 220, at least a portion of the third pipe section 50 of the line 100 is arranged on the second pre-steaming heat exchange portion 230.
  • a flow path structure with different pipe diameters is designed reasonably, and the small pipe is fully utilized in the gas-liquid two-phase mixing zone.
  • the fast flow rate of the refrigerant in the bore and the small flow path of the small pipe diameter improve the heat transfer performance of the refrigerant in the gas-liquid two-phase mixing zone; the flow pipe section mainly composed of gas phase refrigerant and the flow pipe segment mainly composed of liquid phase refrigerant
  • the use of a single pipe diameter with a large pipe diameter reduces the flow path and reduces the flow rate of the refrigerant, and increases the heat exchange area between the air and the refrigerant, and improves the flow pipe section mainly composed of the gas phase refrigerant and the liquid phase refrigerant.
  • the heat exchange efficiency between the refrigerant and the air in the main flow pipe section improves the overall heat exchange performance of the evaporator.
  • the widths of the post-steaming heat exchange portion 210, the first pre-steaming heat exchange portion 220, and the second pre-steaming heat exchange portion 230 are equal.
  • Embodiment 1 is a diagrammatic representation of Embodiment 1:
  • the evaporator includes a post-steaming heat exchange portion 210, a first pre-steaming heat exchange portion 220, a second pre-steaming heat exchange portion 230, and a line 100 of the evaporator.
  • the pipeline 100 has an inlet 10 and an outlet 20 , and the pipeline 100 includes a first pipe section 30 , a second pipe section 40 and a third pipe section 50 .
  • the inlet 10 of the line 100 is located at one end of the first pipe section 30.
  • the refrigerant flowing in the first pipe section 30 is mainly liquid refrigerant, and the first pipe section 30 is located on the windward side X of the pipe 100.
  • the second pipe section 40 is located on the leeward side Y of the pipeline 100.
  • the second pipe section 40 flows the ventilating liquid two-phase mixed refrigerant, and one end of the second pipe section 40 communicates with the other end of the first pipe section 30.
  • One end of the third pipe section 50 communicates with the other end of the second pipe section 40, the outlet 20 of the pipe 100 is located at the other end of the pipe 100, and the refrigerant flowing in the third pipe section 50 is mainly composed of a gaseous refrigerant.
  • the first pipe section 30, the second pipe section 40 and the third pipe section 50 comprise a plurality of sequentially connected U-shaped pipes, and the first pipe section 30 has a plurality of first straight straight pipe sections 310 extending in a straight line, adjacent to each other.
  • the vertical distance between the two first straight pipe sections 310 is P
  • the third pipe section 50 has a plurality of second straight pipe sections 510 extending in a straight line
  • the vertical distance between the two second straight pipe sections 510 adjacent to each other is E
  • E P
  • the second pipe section 40 has a plurality of third straight straight pipe sections 410 extending in a straight line
  • the vertical distance between the two third straight straight pipe sections 510 adjacent to each other is F.
  • the diameter of the first pipe section 30 is D1, which satisfies: 6 mm ⁇ D1 ⁇ 7.5 mm
  • the pipe diameter of the second pipe section 40 is D2, which satisfies: 3 mm ⁇ D2 ⁇ 6.5 mm
  • the cross section of the first pre-steaming heat exchange portion 220, the second pre-steaming heat exchange portion 230, and the post-steaming heat exchange portion 210 of the evaporator is a polygonal structure, and the first pre-steaming heat exchange portion of the evaporator One end of 220 is connected to the end of the post-steaming heat exchange portion 210, and the other end of the first pre-steaming heat exchange portion 220 is connected to the second pre-steaming heat exchange portion 230, and the first pre-steaming heat exchange portion 220 and the post-steaming heat exchange portion
  • the connecting faces of the portion 210 and the second pre-steaming heat exchange portion 230 are preferably of equal area design, thereby facilitating the fixed connection, and the connection manner may be by snapping, welding or other connection.
  • At least a portion of the first tube section 30 of the line 100 is disposed on the windward side X of the post-steaming heat exchange portion 210 and the first pre-steaming heat exchange portion 220, and at least a portion of the second tube portion 40 of the line 100
  • At least the third tube section 50 of the line 100 is disposed on the leeward side Y of the post-steaming heat exchange portion 210 and the first pre-steaming heat exchange portion 220, and is disposed on the second pre-steaming heat exchange portion 230.
  • the outside air flows from the windward side X into the interior of the evaporator, and after passing through the gap between the evaporator tubes 100 and the refrigerant in the pipeline 100, the air is ventilated from the leeward side.
  • the direction indicated by the arrow is the flow direction of the refrigerant in the pipe 100.
  • the refrigerant flows from the inlet 10 of the pipeline 100 into the pipeline 100 and sequentially flows through the first pipe section 30, the second pipe section 40 and the third pipe section 50, and the liquid refrigerant gradually evaporates and absorbs heat during the flow in the pipe 100.
  • the gaseous refrigerant finally flows out from the outlet 20.
  • the flowing refrigerant is mainly liquid refrigerant.
  • the flowing refrigerant is a refrigerant mixed with a gaseous refrigerant and a liquid refrigerant, in the third pipe section.
  • the flowing refrigerant is mainly gaseous refrigerant.
  • the pipe 100 may include a long U pipe and a semicircular pipe.
  • the long U pipe includes: two straight pipe segments and an elbow pipe segment.
  • the two ends of the elbow pipe segment communicate with the ends of the two straight pipe segments respectively to form a U.
  • the type of pipeline structure the other end of the straight pipe section opposite to the curved pipe section is the free end of the straight pipe section.
  • the adjacent two long U tubes may be connected by a semicircular tube, wherein one end of the semicircular tube communicates with the free end of one of the straight tube sections of one of the long U tubes, and the other end of the semicircular tube and the other long U tube The free end of one of the straight sections is connected. As can be seen from FIG. 1 and FIG.
  • the refrigerant flows from the inlet 10 into the first pre-steaming heat exchange portion 220 and the post-steaming heat exchange portion 210, it sequentially flows through the first pipe section 30 and the second pipe section 40, and the refrigerant passes through the full length.
  • the flow is divided into four ways to flow into the second pre-steaming heat exchange portion 230, and the second pre-steaming heat exchange portion 230 can be disposed in the obliquely long U-tube layout, and the refrigerant is further carried out in the second pre-steaming heat exchange portion 230.
  • the final four-way flow out from the outlet 20 of the line 100.
  • the "positive long U tube and the oblique insertion long U tube” herein are based on the positional relationship of the long U tube with respect to the windward side X and the leeward side Y.
  • the leeward side wall surface of the second pre-steaming heat exchange portion 230 is Z
  • the plane of the two straight flat tubes defining the long U tube is T
  • the plane T is parallel to the leeward side wall surface Z
  • the plane T has an oblique angle with the leeward side wall surface Z, it is obliquely inserted into the long U tube (as shown in FIG. 1).
  • the flow path structure in the gas-liquid two-phase mixing zone, fully utilizes the characteristics of the fast flow rate of the refrigerant in the small pipe diameter and the small flow path of the small pipe diameter, thereby improving the heat exchange performance of the refrigerant in the pipe section of the gas-liquid two-phase mixing zone;
  • the gas phase refrigerant-based flow tube section and the liquid phase refrigerant-based flow tube section use a single tube diameter with a larger diameter, which reduces the flow path and reduces the flow rate of the refrigerant, and increases the heat exchange area between the air and the refrigerant.
  • the heat exchange efficiency between the refrigerant and the air in the flow tube section mainly composed of the gas phase refrigerant and the flow tube section mainly composed of the liquid phase refrigerant is improved, thereby improving the overall heat exchange performance of the evaporator.
  • Embodiment 2 is a diagrammatic representation of Embodiment 1:
  • the heat exchange tubes in the second pre-steaming heat exchange portion 230 are arranged in a long-length U-tube.
  • the flow path of the refrigerant in the pipeline is different, the direction of the arrow shown in FIG. 3 is the flow direction of the refrigerant in the pipeline 100, the refrigerant flows from the pipeline inlet 10 into the pipeline 100, and the refrigerant is in the first pre-evaporation heat exchange.
  • the portion 220 and the post-steaming heat exchange portion 210 sequentially flow through the first pipe segment 30 and the second pipe segment 40 for sufficient heat exchange, and are summarized as two channels flowing from the middle of the second pre-steaming heat exchange portion 230 to the second heat exchange tube.
  • the steaming heat exchange portion 230 finally flows out from the outlet 20 of the second pre-steaming heat exchange portion 230, whereby the piping process can be simplified, thereby reducing the production cost.
  • the air conditioner has the evaporator described above.
  • a flow path structure with different pipe diameters is designed reasonably, and the small pipe is fully utilized in the gas-liquid two-phase mixing zone.
  • the fast flow rate of the refrigerant in the bore and the small flow path of the small pipe diameter improve the heat transfer performance of the refrigerant in the gas-liquid two-phase mixing zone; the flow pipe section mainly composed of gas phase refrigerant and the flow pipe segment mainly composed of liquid phase refrigerant
  • the use of a single pipe diameter with a large pipe diameter reduces the flow path and reduces the flow rate of the refrigerant, and increases the heat exchange area between the air and the refrigerant, and improves the flow pipe section mainly composed of the gas phase refrigerant and the liquid phase refrigerant.
  • the heat exchange efficiency between the refrigerant and the air in the main flow pipe section improves the overall heat exchange performance of the evaporator.

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Abstract

一种蒸发器的管路（100），具有进口（10）和出口（20），并且包括：第一管段（30）、第二管段（40）和第三管段（50）。其中，第一管段（30）供液相冷媒流通，管路（100）的进口（10）位于第一管段（30）的一端，第一管段（30）位于管路的迎风侧且管径为D1；第二管段（40）的一端与第一管段（30）的另一端连通且位于管路的背风侧，第二管段（40）的管径为D2；第三管段（50）供气相冷媒流通，第三管段（50）的一端与第二管段（40）的另一端连通，管路（100）的出口（20）位于第三管段（50）的另一端。

Description

蒸发器的管路、蒸发器及空调器 技术领域
本发明涉及家用电器技术领域，具体而言，尤其涉及一种蒸发器的管路、蒸发器及空调器。
背景技术
随着空调器技术的不断发展，空调能效等级要求越来越高，但是对室内机尺寸明显限制，除了压缩机之外，最有效的方式增加室内机换热器。如何在小空间内实现能效突破，换热器设计需要重大技术创新。相关技术中采用拼接方式将不同管径组合，该方式制造效率低。
发明内容
本发明旨在至少在一定程度上解决相关技术中的技术问题之一。为此，本发明提出一种蒸发器的管路，所述蒸发器的管路具有结构简单、换热效果好的优点。
本发明还提出一种蒸发器，所述蒸发器具有上述所述的蒸发器的管路。
本发明的另一个目的在于提出一种空调器，所述空调器具有上述所述的蒸发器。
根据本发明实施例的蒸发器的管路，管路具有进口和出口且包括：供液相冷媒流通的第一管段，所述进口位于所述第一管段的一端，所述第一管段位于所述管路的迎风侧且管径为D1；第二管段，所述第二管段的一端与所述第一管段的另一端连通且位于所述管路的背风侧，所述第二管段的管径为D2，其中D1＞D2；和供气相冷媒流通的第三管段，所述第三管段的一端与所述第二管段的另一端连通，所述出口位于所述第三管段的另一端。
根据本发明实施例的蒸发器的管路，通过设置不同管径的管路管段，可以通过管径的变化控制冷媒的流速和换热效率，并且在迎风侧和背风侧合理选择不同的管径管段，可以有效提高蒸发器的换热效率，从而在蒸发器有限的空间内有效提高了蒸发器的换热性能，进而提高了产品的整体性能。
根据本发明的一些实施例，所述第一管段的管径范围为6mm≤D1≤7.5mm。
根据本发明的一些实施例，所述第二管段的管径范围为3mm≤D2≤6.5mm。
根据本发明的一些实施例，所述第三管段的管径为D3，其中，D3＝D1。
根据本发明的一些实施例，所述第一管段具有多段沿直线延伸的第一平直管段，彼此邻近的两个所述第一平直管段之间的垂直距离为P，所述第三管段具有多段沿直线延伸的 第二平直管段，彼此邻近的两个所述第二平直管段之间的垂直距离为E，其中E＝P。
根据本发明的一些实施例，所述出口位于所述管路的背风侧。
根据本发明的一些实施例，所述管路包括多个依次连通U型管，每个所述U型管的两个直管段之间的距离均为M。
根据本发明实施例的蒸发器，包括：后蒸换热部；第一前蒸换热部，所述第一前蒸换热部与所述后蒸换热部连接；第二前蒸换热部，所述第二前蒸换热部与所述第一前蒸换热部连接；和上述所述的蒸发器的管路，所述管路的至少部分所述第一管段排布在所述后蒸换热部和所述第一前蒸换热部的迎风侧，所述管路的至少部分所述第二管段排布在所述后蒸换热部和所述第一前蒸换热部的背风侧，所述管路的至少部分所述第三管段排布在所述第二前蒸换热部上。
根据本发明实施例的蒸发器，根据冷媒不同相态在不同管径的换热特点，合理设计了一种不同管径相互配合的流路结构，在气液两相混合区，充分利用小管径内冷媒流速快和小管径流路较多的特点，提高了冷媒在气液两相混合区管段内的换热性能；在以气相冷媒为主的流动管段和以液相冷媒为主的流动管段，使用管径较大的单一管径，减少了流路并降低了冷媒流速，而且增大了空气与冷媒的换热面积，提高了在以气相冷媒为主的流动管段和以液相冷媒为主的流动管段内冷媒与空气的热交换效率，从而提高了蒸发器的整体热交换性能。
根据本发明的一些实施例，所述后蒸换热部、所述第一前蒸换热部和所述第二前蒸换热部的宽度相等。
根据本发明实施例的空调器，所述空调器具有上述所述的蒸发器。
根据本发明实施例的空调器，根据冷媒不同相态在不同管径的换热特点，合理设计了一种不同管径相互配合的流路结构，在气液两相混合区，充分利用小管径内冷媒流速快和小管径流路较多的特点，提高了冷媒在气液两相混合区管段内的换热性能；在以气相冷媒为主的流动管段和以液相冷媒为主的流动管段，使用管径较大的单一管径，减少了流路并降低了冷媒流速，而且增大了空气与冷媒的换热面积，提高了在以气相冷媒为主的流动管段和以液相冷媒为主的流动管段内冷媒与空气的热交换效率，从而提高了蒸发器的整体热交换性能。
附图说明
本发明的上述和/或附加的方面和优点从结合下面附图对实施例的描述中将变得明显和容易理解，其中：
图1是根据本发明实施例的蒸发器的管路的结构示意图；
图2是根据本发明实施例的蒸发器的管路的展开状态的结构示意图；
图3是根据本发明实施例蒸发器的管路的结构示意图；
图4是根据本发明实施例的蒸发器的管路的展开状态的结构示意图。
附图标记：
管路100，
进口10，出口20，
第一管段30，第一平直管段310，
第二管段40，第三平直管段410，
第三管段50，第二平直管段510，
后蒸换热部210，
第一前蒸换热部220，
第二前蒸换热部230,
迎风侧X,背风侧Y，背风侧壁面Z，
第一管段管径D1，第二管段管径D2，第三管段管径D3，
第一平直管段之间的垂直距离P，
第二平直管段之间的垂直距离E，
第三平直管段之间的垂直距离F。
具体实施方式
下面详细描述本发明的实施例，所述实施例的示例在附图中示出。下面通过参考附图描述的实施例是示例性的，旨在用于解释本发明，而不能理解为对本发明的限制。
在本发明的描述中，需要理解的是，术语“宽度”、“上”、“下”、“前”、“后”、“左”、“右”、“竖直”“内”、“外”等指示的方位或位置关系为基于附图所示的方位或位置关系，仅是为了便于描述本发明和简化描述，而不是指示或暗示所指的装置或元件必须具有特定的方位、以特定的方位构造和操作，因此不能理解为对本发明的限制。
此外，术语“第一”、“第二”仅用于描述目的，而不能理解为指示或暗示相对重要性或者隐含指明所指示的技术特征的数量。由此，限定有“第一”、“第二”的特征可以明示或者隐含地包括至少一个该特征。在本发明的描述中，“多个”的含义是至少两个，例如两个，三个等，除非另有明确具体的限定。
在本发明中，除非另有明确的规定和限定，术语“安装”、“相连”、“连接”、“固定”等术语应做广义理解，例如，可以是固定连接，也可以是可拆卸连接，或成一体；可以是 机械连接，也可以是电连接或彼此可通讯；可以是直接相连，也可以通过中间媒介间接相连，可以是两个元件内部的连通或两个元件的相互作用关系，除非另有明确的限定。对于本领域的普通技术人员而言，可以根据具体情况理解上述术语在本发明中的具体含义。
下面参考图1-图4描述根据本发明实施例的蒸发器的管路100、蒸发器及空调器。
如图1-图4所示，根据本发明实施例的蒸发器的管路100，管路100具有进口10和出口20且包括：第一管段30、第二管段40和第三管段50。其中，第一管段30供液相冷媒流通，管路100的进口10位于第一管段30的一端，第一管段30位于管路100的迎风侧X且第一管段30的管径为D1。第二管段40的一端与第一管段30的另一端连通且位于管路100的背风侧Y，第二管段40的管径为D2。第三管段50供气相冷媒流通，第三管段50的一端与第二管段40的另一端连通，管路100的出口20位于第三管段50的另一端。
需要说明的是，如图1所示，箭头所示方向为冷媒在管路100内的流动方向。冷媒从管路100的进口10流进管路100并依次流经第一管段30、第二管段40和第三管段50，液态的冷媒在管路100内的流动过程中逐渐蒸发吸热并转化成气态冷媒，最后从出口20流出，在第一管段30内，流动的冷媒以液态冷媒为主，在第二管段40内，流动的冷媒为气态冷媒和液态冷媒混合的冷媒，在第三管段50内，流动的冷媒以气态冷媒为主。冷媒在由液态转化成气态时，将从管路100周围吸收大量的热量，从而可以实现蒸发器的制冷功能。
根据本发明实施例的蒸发器的管路100，通过在不同冷媒相态段设置不同管径的管路100管段，可以通过管径的变化控制冷媒的流速和换热效率，并且在迎风侧X和背风侧Y合理选择不同的管径管段，可以有效提高蒸发器的换热效率，从而在蒸发器有限占的空间内有效提高了蒸发器的换热性能，进而提高了产品的整体性能。
根据本发明的一些实施例，如图2和图4所示，第一管段30的管径范围为6mm≤D1≤7.5mm。经过实验验证，当第一管段30的管径范围满足：6mm≤D1≤7.5mm时，可以有效提高蒸发器管路100的换热效率。需要说明的是，第一管段30位于在迎风侧X的位置，进入蒸发器的空气首先与第一管段30接触，第一管段30内流动的冷媒以液态冷媒为主，将第一管段30径设置较大，可以增加空气与冷媒的热交换面的有效面积，从而提高蒸发器的换热效率。
根据本发明的一些实施例，如图2和图4所示，第二管段40的管径范围为3mm≤D2≤6.5mm。经过实验验证，当第二管段40的管径范围满足：3mm≤D2≤6.5mm时，可以有效提高冷媒的流动速率和相变速率，从而可以进一步提高蒸发器管路100的换热效率。值得理解的是，冷媒从第一管段30流入第二管段40的过程中，将第二管段40的管径设计为小于第一管段30的管径，根据流体力学质量守恒方程，冷媒的流速会得到提高，冷媒在流速提高的同时，会相应加快冷媒与外界空气的热量交换速率，从而进一步提高了蒸发器管路100 的热交换速率，而且加快了冷媒的相变速率，加快了冷媒从液态向气态的转化速率，从而提高了冷媒蒸发吸热的制冷效果。
根据本发明的一些实施例，如图2和图4所示，第三管段50的管径为D3，其中，D3＝D1。通过将第三管段50的管径设置为D3＝D1，使第三管段50的管径与第一管段30的管径相等，一方面可以便于蒸发器管路100的加工制造，以降低生产成本；另一方面，冷媒从第二管段40流向第三管段50时，气液两相混合冷媒大部分转化为气态冷媒，将第三管段50的管径相应采用较大设计，可以减少管路100的流路分支，优化管路100布局，而且，增大了气态冷媒与外界空气的有效换热面积，以提高蒸发器管路100的换热效率。
根据本发明的一些实施例，如图2和图4所示，第一管段30具有多段沿直线延伸的第一平直管段310，彼此邻近的两个第一平直管段310之间的垂直距离为P，第三管段50具有多段沿直线延伸的第二平直管段510，彼此邻近的两个第二平直管段510之间的垂直距离为E，其中E＝P。由此，将第一管段30设置为多段沿直线延伸的第一平直管段310、将第三管段50设置为具有多段沿直线延伸的第二平直管段510，有利于维持冷媒在管路100流动过程中的稳定性，从而使冷媒与外界空气具有稳的热交换速率，有利于保证蒸发器的换热性能。另外，令第一平直管段310之间的垂直距离P与第二平直管段510之间的垂直距离E相等，便于管路100的加工制造和布局优化，有利于降低生产成本。
根据本发明的一些实施例，如图1和图3所示，出口20位于管路100的背风侧Y。由此，可以使管路100内冷媒的冷量得到充分的传递利用，从而提高蒸发器的换热效率。可以理解的是，外界空气从蒸发器的迎风侧X流进蒸发器，与蒸发器管路100内流动的冷媒进行热交换后，经过热交换后的空气从背风侧Y流出至蒸发器，将管路100出口20设置在管路100的背风侧Y，可以使管路100内的冷媒与蒸发器内的空气在有限的空间内具有最长的接触时间，以保证空气与冷媒间进行充足的热交换，从而使冷媒的冷量的到充分的利用，提高了蒸发器的热交换性能。
根据本发明的一些实施例，如图2和图4所示，管路100包括多个依次连通U型管，每个U型管的两个直管段之间的距离均为M。由此，采用多个U型管连通的管路100，可以使冷媒在管路100内折回流动，有效延长了冷媒的流动距离，从而延长了冷媒与空气之间的热交换时间，提高了蒸发器的热交换效率。而且每个U型管的两个直管段之间的距离均为M，便于管路100的加工制造，以简化制造工艺，降低生产成本。
根据本发明实施例的蒸发器，如图1-图4所示，蒸发器可以包括：后蒸换热部210、第一前蒸换热部220、第二前蒸换热部230和上述的蒸发器的管路100。其中，第一前蒸换热部220与后蒸换热部210连接，第二前蒸换热部230与第一前蒸换热部220连接。管路 100的至少部分第一管段30排布在后蒸换热部210和第一前蒸换热部220的迎风侧X，管路100的至少部分第二管段40排布在后蒸换热部210和第一前蒸换热部220的背风侧Y，管路100的至少部分第三管段50排布在第二前蒸换热部230上。
根据本发明实施例的蒸发器，根据冷媒不同相态在不同管径的换热特点，合理设计了一种不同管径相互配合的流路结构，在气液两相混合区，充分利用小管径内冷媒流速快和小管径流路较多的特点，提高了冷媒在气液两相混合区管段内的换热性能；在以气相冷媒为主的流动管段和以液相冷媒为主的流动管段，使用管径较大的单一管径，减少了流路并降低了冷媒流速，而且增大了空气与冷媒的换热面积，提高了在以气相冷媒为主的流动管段和以液相冷媒为主的流动管段内冷媒与空气的热交换效率，从而提高了蒸发器的整体热交换性能。
根据本发明的一个实施例，如图1-图4所示，后蒸换热部210、第一前蒸换热部220和第二前蒸换热部230的宽度相等。由此，便于蒸发器各部分之间的布局优化，也可以优化蒸发器的制造工艺，从而降低生产成本。
下面参照图1-图4以两个具体的实施例详细描述根据本发明实施例的蒸发器。值得理解的是，下述描述仅是示例性说明，而不能理解为对本发明的具体限制。
实施例一：
如图1和图2所示，蒸发器包括：后蒸换热部210、第一前蒸换热部220、第二前蒸换热部230和蒸发器的管路100。
其中，如图1所示，管路100具有进口10和出口20，管路100包括：第一管段30、第二管段40和第三管段50。管路100的进口10位于第一管段30的一端，第一管段30内流动的冷媒以液态冷媒为主，第一管段30位于管路100的迎风侧X。第二管段40位于管路100的背风侧Y，第二管段40内流通气液两相混合冷媒，第二管段40的一端与第一管段30的另一端连通。第三管段50的一端与第二管段40的另一端连通，管路100的出口20位于管路100的另一端，第三管段50内流动的冷媒以气态冷媒为主。
如图2所示，第一管段30、第二管段40和第三管段50包括多个依次连通的U型管，第一管段30具有多段沿直线延伸的第一平直管段310，彼此邻近的两个第一平直管段310之间的垂直距离为P，第三管段50具有多段沿直线延伸的第二平直管段510，彼此邻近的两个第二平直管段510之间的垂直距离为E，其中E＝P，第二管段40具有多段沿直线延伸的第三平直管段410，彼此邻近的两个第三平直管段510之间的垂直距离为F。
如图2所示，第一管段30的管径为D1，满足：6mm≤D1≤7.5mm，第二管段40的管径为D2，满足：3mm≤D2≤6.5mm，第三管段50的管径为D3，满足：D3＝D1。
如图1所示，蒸发器的第一前蒸换热部220、第二前蒸换热部230和后蒸换热部210的横截面为多边形结构，蒸发器的第一前蒸换热部220的一端与后蒸换热部210的端部连接，第一前蒸换热部220的另一端与第二前蒸换热部230连接，第一前蒸换热部220与后蒸换热部210和第二前蒸换热部230的连接面优选面积相等设计，由此，便于固定连接，连接方式可以采用卡接、焊接或其他连接方式。如图1所示，管路100的至少部分第一管段30排布在后蒸换热部210和第一前蒸换热部220的迎风侧X，管路100的至少部分第二管段40排布在后蒸换热部210和第一前蒸换热部220的背风侧Y，管路100的至少部分第三管段50排布在第二前蒸换热部230上。
需要说明的是，如图1所示，外界的空气从迎风侧X流入到蒸发器内部，经过蒸发器管路100间的间隙与管路100内的冷媒进行热交换后，空气从背风侧Y流出。如图1所示，箭头所示方向为冷媒在管路100内的流动方向。冷媒从管路100的进口10流进管路100并依次流经第一管段30、第二管段40和第三管段50，液态的冷媒在管路100内的流动过程中逐渐蒸发吸热并转化成气态冷媒，最后从出口20流出，在第一管段30内，流动的冷媒以液态冷媒为主，在第二管段40内，流动的冷媒为气态冷媒和液态冷媒混合的冷媒，在第三管段50内，流动的冷媒以气态冷媒为主。冷媒在由液态转化成气态时，将从管路100周围吸收大量的热量，从而可以实现蒸发器的制冷功能。
管路100可以包括长U管和半圆管，其中，长U管包括：两根平直管段和弯管段，弯管段的两端分别与两根平直管段的端部连通，形成为U型管道结构，平直管段与弯管段相对的另一端为平直管段的自由端。相邻的两个长U管之间可以通过半圆管连通，其中半圆管的一端与其中一个长U管的一根平直管段的自由端连通，半圆管的另一端与另一个长U管的其中一根平直管段的自由端连通。从图1和图2中可以看出，冷媒从进口10流进第一前蒸换热部220和后蒸换热部210后，依次流经第一管段30和第二管段40，冷媒经过充分的换热后，分为四路流入到第二前蒸换热部230，第二前蒸换热部230内可以采用斜插长U管布局，冷媒在第二前蒸换热部230进一步进行热交换后最后分四路从管路100的出口20流出。采用该种冷媒流路管路100设计，可以使冷媒与空气间进行充足的热交换，从而进一步提高了蒸发器的制冷效果。
需要说明的是，这里的“正插长U管和斜插长U管”，是根据长U管相对于迎风侧X和背风侧Y的壁面位置关系而言的。以图1和图3中的示例为例，第二前蒸换热部230的背风侧壁面为Z，定义长U管两根直平管段所在平面为T，当平面T与背风侧壁面Z平行时，为正插长U管(如图3所示)；当平面T与背风侧壁面Z具有倾斜夹角时，为斜插长U管(如图1所示)。
由此，根据冷媒不同相态在不同管径的换热特点，合理设计了一种不同管径相互配合 的流路结构，在气液两相混合区，充分利用小管径内冷媒流速快和小管径流路较多的特点，提高了冷媒在气液两相混合区管段内的换热性能；在以气相冷媒为主的流动管段和以液相冷媒为主的流动管段，使用管径较大的单一管径，减少了流路并降低了冷媒流速，而且增大了空气与冷媒的换热面积，提高了在以气相冷媒为主的流动管段和以液相冷媒为主的流动管段内冷媒与空气的热交换效率，从而提高了蒸发器的整体热交换性能。
实施例二：
如图3和图4所示，与实施例一不同的是，在该实施例中，如图3所示，第二前蒸换热部230内的换热管采用正插长U管布局，并且冷媒在管路内的流路不同，如图3中所示的箭头方向为冷媒在管路100内的流动方向，冷媒从管路进口10流入管路100，冷媒在第一前蒸换热部220和后蒸换热部210依次流经第一管段30和第二管段40进行充分换热后，汇总为两路从第二前蒸换热部230中间排换热管流进第二前蒸换热部230，最后从第二前蒸换热部230的出口20流出，由此，可以简化管路工艺，从而降低生产成本。
根据本发明实施例的空调器，空调器具有上述所述的蒸发器。
根据本发明实施例的空调器，根据冷媒不同相态在不同管径的换热特点，合理设计了一种不同管径相互配合的流路结构，在气液两相混合区，充分利用小管径内冷媒流速快和小管径流路较多的特点，提高了冷媒在气液两相混合区管段内的换热性能；在以气相冷媒为主的流动管段和以液相冷媒为主的流动管段，使用管径较大的单一管径，减少了流路并降低了冷媒流速，而且增大了空气与冷媒的换热面积，提高了在以气相冷媒为主的流动管段和以液相冷媒为主的流动管段内冷媒与空气的热交换效率，从而提高了蒸发器的整体热交换性能。
在本说明书的描述中，参考术语“一个实施例”、“一些实施例”、“示例”、“具体示例”、或“一些示例”等的描述意指结合该实施例或示例描述的具体特征、结构、材料或者特点包含于本发明的至少一个实施例或示例中。在本说明书中，对上述术语的示意性表述不必须针对的是相同的实施例或示例。而且，描述的具体特征、结构、材料或者特点可以在任一个或多个实施例或示例中以合适的方式结合。此外，在不相互矛盾的情况下，本领域的技术人员可以将本说明书中描述的不同实施例或示例以及不同实施例或示例的特征进行结合和组合。
尽管上面已经示出和描述了本发明的实施例，可以理解的是，上述实施例是示例性的，不能理解为对本发明的限制，本领域的普通技术人员在本发明的范围内可以对上述实施例进行变化、修改、替换和变型。

Claims (10)

  1. 一种蒸发器的管路，其特征在于，所述管路具有进口和出口且包括：
    供液相冷媒流通的第一管段，所述进口位于所述第一管段的一端，所述第一管段位于所述管路的迎风侧且管径为D1；
    第二管段，所述第二管段的一端与所述第一管段的另一端连通且位于所述管路的背风侧，所述第二管段的管径为D2，其中D1＞D2；和
    供气相冷媒流通的第三管段，所述第三管段的一端与所述第二管段的另一端连通，所述出口位于所述第三管段的另一端。
  2. 根据权利要求1所述的蒸发器的管路，其特征在于，所述第一管段的管径范围为6mm≤D1≤7.5mm。
  3. 根据权利要求1或2所述的蒸发器的管路，其特征在于，所述第二管段的管径范围为3mm≤D2≤6.5mm。
  4. 根据权利要求1-3中任一项所述的蒸发器的管路，其特征在于，所述第三管段的管径为D3，其中，D3＝D1。
  5. 根据权利要求4所述的蒸发器的管路，其特征在于，所述第一管段具有多段沿直线延伸的第一平直管段，彼此邻近的两个所述第一平直管段之间的垂直距离为P，
    所述第三管段具有多段沿直线延伸的第二平直管段，彼此邻近的两个所述第二平直管段之间的垂直距离为E，其中E＝P。
  6. 根据权利要求1-5中任一项所述的蒸发器的管路，其特征在于，所述出口位于所述管路的背风侧。
  7. 根据权利要求1-6中任一项所述的蒸发器的管路，其特征在于，所述管路包括多个依次连通U型管，每个所述U型管的两个直管段之间的距离均为M。
  8. 一种蒸发器，其特征在于，包括：
    后蒸换热部；
    第一前蒸换热部，所述第一前蒸换热部与所述后蒸换热部连接；
    第二前蒸换热部，所述第二前蒸换热部与所述第一前蒸换热部连接；和
    根据权利要求1-7中任一项所述的蒸发器的管路，所述管路的至少部分所述第一管段排布在所述后蒸换热部和所述第一前蒸换热部的迎风侧，所述管路的至少部分所述第二管段排布在所述后蒸换热部和所述第一前蒸换热部的背风侧，所述管路的至少部分所述第三管段排布在所述第二前蒸换热部上。
  9. 根据权利要求8所述的蒸发器，其特征在于，所述后蒸换热部、所述第一前蒸换热部和所述第二前蒸换热部的宽度相等。
  10. 一种空调器，其特征在于，包括根据权利要求8或9所述的蒸发器。
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