WO2021184828A1 - 喷射器及空气调节装置 - Google Patents
喷射器及空气调节装置 Download PDFInfo
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- WO2021184828A1 WO2021184828A1 PCT/CN2020/133248 CN2020133248W WO2021184828A1 WO 2021184828 A1 WO2021184828 A1 WO 2021184828A1 CN 2020133248 W CN2020133248 W CN 2020133248W WO 2021184828 A1 WO2021184828 A1 WO 2021184828A1
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- resistant
- ejector
- anechoic chamber
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- 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
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
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- 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
- F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
- F25B2341/001—Ejectors not being used as compression device
- F25B2341/0012—Ejectors with the cooled primary flow at high pressure
Definitions
- the invention belongs to the technical field of air conditioning equipment, and in particular relates to an ejector and an air conditioning device using the ejector.
- capillary air conditioners use capillary tubes as throttling devices (capillary air conditioners for short).
- a liquid distributor is connected downstream of the capillary tube, and each branch of the liquid distributor is then connected to each branch of the evaporator. Since capillary throttling efficiency is the least efficient of all throttling forms, in order to improve throttling efficiency, ejectors are gradually used to replace capillary tubes in the prior art.
- the ejector uses an isentropic process to expand the high-pressure refrigerant (main flow) to eliminate the loss during the expansion process, and increase the pressure of the mortgage refrigerant (suction flow) discharged from the evaporator outlet to reduce the power consumption of the system .
- the nozzle in the prior art adopts the structure shown in Fig. 1, and the throttling principle of the nozzle is explained by Bernoulli equation.
- the Bernoulli equation between section 1-1 and section 2-2 is:
- ⁇ The local resistance coefficient of the fluid from section 1-1 to section 2-2
- the nozzle has throttling capability. Because the streamline and conical nozzles have the highest flow coefficients, for the original intention of reducing energy-saving losses, it is preferable to design the ejector to be streamlined or conical. Due to the difficulty of processing streamline jets, the conical convergent nozzle shown in Figure 1 is usually selected at present. The actual processing flow coefficient of the nozzle is between 0.9-0.95, and it is necessary to maintain a high level of internal surface finish to improve Nozzle flow coefficient and wear resistance
- the prior art fully considers flow absorption and energy conversion efficiency, it does not consider the problem of noise suppression. Since the ejector needs to be installed in conjunction with the indoor heat exchanger, that is, the evaporator, the cone-shaped nozzle will produce a lot of noise, which directly affects the user, especially at night, it will interfere with sleep and reduce the user's experience.
- the present invention designs and discloses a brand-new ejector.
- An ejector includes: an inlet section connected to a liquid separator; an outlet section connected to an indoor heat exchanger; and a resistant anechoic chamber formed in the Between the inlet section and the outlet section, the cross-sectional area of the resistant anechoic chamber is larger than the cross-sectional area of the inlet section.
- the inlet section includes: a conical pipe section having a first end and a second end, wherein the cross-sectional diameter of the first end is greater than The cross-sectional diameter of the second end and the diameter of the resistant anechoic chamber are larger than the cross-sectional diameter of the second end.
- the resistant anechoic chamber includes: an interference part, one end of the interference part is fixedly arranged on the inner wall of the resistant anechoic chamber, and the other end extends in a direction perpendicular to the direction of refrigerant flow Or extend obliquely along the refrigerant flow direction; the interference part and the inner wall of the resistant anechoic chamber jointly enclose a refrigerant flow path.
- any two adjacent interference portions are arranged in sequence along the refrigerant flow direction and extend toward each other.
- the interference part can be designed in a spiral shape.
- the interference part includes: a first interference plate, the upper end of the first interference plate is fixedly arranged on the inner wall of the resistant anechoic chamber, and the first interference The lower end of the plate extends from top to bottom, the lower end of the first interference plate and the inner wall of the resistant anechoic chamber jointly enclose a refrigerant flow path; and a second interference plate, the second interference plate being arranged on the Downstream of the first interference plate, the lower end of the second interference plate is fixedly arranged on the inner wall of the resistant anechoic chamber, the upper end of the second interference plate extends upward from the bottom, and the upper end of the second interference plate Together with the inner wall of the resistant anechoic chamber, a refrigerant flow path is enclosed.
- outlet section is a straight pipe section, and the cross-sectional diameter of the outlet section is smaller than the cross-sectional diameter of the resistant anechoic chamber.
- the outer side of the resistance anechoic chamber is covered with a resistance sound-absorbing material, and the resistance sound-absorbing material is mineral wool, glass wool, felt or wood.
- the resistance sound-absorbing material is mineral wool, glass wool, felt or wood.
- a housing is provided outside the resistant anechoic chamber, the housing and the outer wall of the resistant anechoic chamber jointly enclose an anechoic cavity, and the resistive sound-absorbing material is filled in the anechoic cavity .
- an air conditioning device including an ejector; the ejector includes: an inlet section, the inlet section is connected to a liquid separator; an outlet section, the outlet section is connected to an indoor heat exchanger;
- the resistant anechoic chamber is formed between the inlet section and the outlet section, and the cross-sectional area of the resistant anechoic chamber is larger than the cross-sectional area of the inlet section.
- the noise generated by the gas-liquid two-phase refrigerant causes impedance changes during the propagation process, resulting in reflection and interference of sound energy ,
- the ejector provided by the present invention is not only a thermodynamic throttling device, but also a mechanical vibration and noise reduction device, and has dual functions.
- Figure 1 is a schematic diagram of the structure of an ejector in the prior art
- Figure 2 is a schematic structural diagram of a first specific embodiment of the ejector disclosed in the present invention.
- Figure 3 is a schematic structural diagram of a second specific embodiment of the ejector disclosed in the present invention.
- Fig. 4 is a schematic diagram of a refrigeration cycle of an air conditioning device using the ejector shown in Fig. 2 or Fig. 3.
- the terms “upper”, “lower”, “left”, “right”, “vertical”, “horizontal”, “inner”, “outer”, etc. indicate directions or positions The term of relationship is based on the direction or position relationship shown in the drawings, which is only for ease of description, and does not indicate or imply that the device or element must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as Restrictions on the present invention.
- the terms “first” and “second” are only used for descriptive purposes, and cannot be understood as indicating or implying relative importance.
- the ejector 10 is preferably designed to be composed of three parts: an inlet section 11, an outlet section 17 and a resistant anechoic chamber 14, wherein the inlet section 11 is arranged in the distributor 20 Downstream and connected with the dispenser 20, as shown in FIG. 4.
- the liquid separator 20 is used before the evaporator to evenly distribute the gas-liquid two-phase refrigerant to each branch of the evaporator.
- an ejector 10 is provided for each evaporator branch, that is, the inlet section 11 of each ejector 10 is connected to a branch of the liquid distributor 20 respectively.
- the outlet section 17 of the ejector 10 is connected to the indoor heat exchanger 30, and the throttled refrigerant in a gas-liquid two-phase state flows into the indoor heat exchanger 30, that is, each branch of the evaporator through the multiple ejectors 10.
- a resistant anechoic chamber 14 is also formed between the inlet section 11 and the outlet section 17, and the cross-sectional area of the resistant anechoic chamber 14 is larger than the cross-sectional area of the inlet section 11.
- the noise causes the impedance change during the propagation process to produce the reflection and interference of sound energy, thereby reducing the resistance of the anechoic chamber 14, that is, the entire ejector. 10 Sound energy radiated to the outside, so as to achieve the purpose of noise reduction.
- This ejector is not only a thermodynamic throttling device, but also a mechanical vibration and noise reduction device. A single component achieves a dual function, which can reduce the number of parts of the entire refrigeration system and save more use and design space for the product.
- the ejector 10 has the following specific structure, wherein the inlet section 11 includes a conical pipe section, and the conical pipe section has a first end 12 and a second end 13, wherein the cross-sectional diameter of the first end 12 is larger than that of the second end
- the cross-sectional diameter of 13, that is, along the direction of refrigerant flow, the conical pipe section is arranged from large to small.
- the diameter of the resistant anechoic chamber 14 is larger than the cross-sectional area of the second end 13, that is, relative to the diameter of the conical pipe section, the resistant anechoic chamber The diameter of 14 suddenly expands, causing a sudden change in the acoustic impedance in the channel.
- an interference part is also provided in the resistant anechoic chamber 14.
- One end of the interference part is fixedly arranged on the inner wall of the resistant anechoic chamber 14, and the other end extends in a direction perpendicular to the direction of the refrigerant flow and encloses the refrigerant flow path together with the inner wall of the resistant anechoic chamber 14.
- the interference portion can also extend obliquely along the refrigerant flow direction, and together with the inner wall of the resistant anechoic chamber 14 enclose the refrigerant flow path.
- the interference part can be designed in the form of an interference plate, or it can be designed in a spiral shape.
- the helical interference part has a smaller flow resistance, and on the other hand, it can also achieve the purpose of noise reduction.
- the interference plate includes a first interference plate 15 and a second interference plate 16.
- the upper end of the first interference plate 15 is fixedly arranged on the inner wall of the resistant anechoic chamber 14, the lower end of the first interference plate 15 extends from top to bottom, and the lower end of the first interference plate 15 is common with the inner wall of the resistant anechoic chamber 14. Enclose the refrigerant flow path.
- the second interference plate 16 is arranged downstream of the first interference plate 15.
- the lower end of the second interference plate 16 is fixedly arranged on the inner wall of the resistant anechoic chamber 14, and the upper end of the second interference plate 16 extends upward from the bottom.
- the upper end of 16 and the inner wall of the resistant anechoic chamber 14 jointly enclose a refrigerant flow path.
- the first interference plate 15 and the second interference plate 16 can cause sound waves to be reflected and interfered to achieve the purpose of reducing noise.
- An outlet section 17 is provided downstream of the resistant anechoic chamber 14.
- the outlet section 17 is preferably designed as a straight pipe section, and the cross-sectional area diameter of the outlet section 17 is smaller than the cross-sectional diameter of the resistant anechoic chamber 14, and is further preferably designed to be proportional to the flow rate of the refrigerant flowing through the ejector 10.
- the outer side of the resistant anechoic chamber 14 is covered with a resistive sound-absorbing material 19.
- a housing 18 is provided outside the resistant anechoic chamber 14.
- the shell 18 and the outer wall of the resistant anechoic chamber 14 jointly enclose an anechoic cavity, and the anechoic absorbing material 19 is filled in the anechoic cavity, thereby combining the anti-noise and resistive anechoic effects.
- the resistive sound-absorbing material 19 is preferably mineral wool, glass wool, felt or wood wool sound-absorbing board.
- Another aspect of the present invention provides an air conditioning device.
- Including ejector For the specific structure and function of the ejector, please refer to the detailed description of the above-mentioned embodiment, which will not be repeated here.
- the air conditioning device provided with the above-mentioned ejector can achieve the same technical effect.
- the air conditioning device may be a wall-mounted air conditioner, a window air conditioner, a vertical air conditioner, a heat pump device, and so on.
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Abstract
一种喷射器（10），包括：入口段（11），所述入口段（11）连接分液器（20）；出口段（17），所述出口段（17）连接室内换热器（30）；和抗性消声室（14），所述抗性消声室（14）形成在所述入口段（11）和出口段（17）之间，所述抗性消声室（14）的截面面积大于所述入口段（11）的截面面积。同时还提供一种采用此种喷射器的空气调节装置。提供的喷射器（10），由于抗性消声室（14）的截面面积相对于入口段（11）发生突变，气液两相制冷剂所产生的噪声在传播过程中引起阻抗的改变而产生声能的反射、干涉，从而降低由抗性消声室（14），即整个喷射器向外辐射的声能，从而达到消声目的，室内侧的用户不会受到干扰，提高了整个产品的使用舒适度。提供的喷射器（10）既是一个热力学节流器件，也是一个机械振动减噪器件，具有双重功能。
Description
本发明属于空气调节设备技术领域，尤其涉及一种喷射器，以及一种采用此种喷射器的空气调节装置。
传统的空调器采用毛细管作为节流装置(简称毛细管空调)。在毛细管空调的制冷循环中，毛细管的下游连接分液器，分液器的每一个支路再连接蒸发器的各个支路。由于毛细管节流效率是所有节流形式中效率最低的一种，为了提高节流效率，现有技术中逐渐采用喷射器取代毛细管。
喷射器(喷嘴)利用等熵过程使得高压的制冷剂(主流动)膨胀从而消除膨胀过程中的损失，并增加从蒸发器出口排出的抵押制冷剂(吸入流动)的压力而减少系统的功耗。现有技术中的喷嘴采用如图1所示的结构，喷嘴的节流原理采用伯努利方程说明，在截面1-1与2-2截面之间的伯努利方程为：
式中:
P
1,υ
1:截面1-1处的压力和速度；
P
2,υ
2:截面2-2处的压力和速度；
ξ:流体从截面1‐1到截面2‐2处的局部阻力系数
ρ:液体密度
喷嘴节流压差通用公式：
从中可以看出，喷嘴具有节流能力，由于流线型和圆锥型喷嘴流量系数最高，所以，出于降低节能损耗的初衷，优选将喷射器设计为流线型或者圆锥型。由于流线型喷射器的加工难度大，因此，目前通常选择如图1所示的圆锥型收敛喷嘴，喷嘴的实际加工流量系数在0.9-0.95之间，且需要保持高水准的内表面光洁度，以提高喷嘴的流量系数和耐磨性
现有技术虽然充分考虑了流量吸收与能量转换效率，但没有考虑噪声抑制问题。由于喷射器需要与室内换热器，即蒸发器配套安装，圆锥形的喷嘴会产生较大的噪声，噪声直接对用户产生影响，尤其是夜间会干扰睡眠，降低用户的使用体验。
发明内容
本发明针对现有技术中的喷射器没有考虑节流相变，容易产生流体噪声的问题，设计并公开一种全新的喷射器。
为实现上述发明目的，本发明采用下述技术方案予以实现：
一种喷射器，包括：入口段，所述入口段连接分液器；出口段，所述出口段连接室内换热器；和抗性消声室，所述抗性消声室形成在所述入口段和出口段之间，所述抗性消声室的截面面积大于所述入口段的截面面积。
为保持较高的节流效率并起到高效低噪的双重效果，所述入口段包括：圆锥管段，所述圆锥管段具有第一端和第二端，其中所述第一端的截面直径大于所述第二端的截面直径,所述抗性消声室的直径大于所述第二端的截面直径。
为提高消声性能，所述抗性消声室包括：干涉部，所述干涉部的一端固定设置在所述抗性消声室的内壁上，另一端沿垂直于制冷剂流动方向的方向延伸或沿制冷剂流动方向倾斜延伸；所述干涉部与所述抗性消声室的内壁共同围成制冷剂流动路径。
优选的，所述干涉部设置为两个或两个以上，任意两个相邻干涉部沿制冷剂流动方向依次布设并相向延伸。
为同时达到消声降噪和更小的流阻的目的，所述干涉部可以设计为螺旋状。
针对气液两相制冷剂的特定噪声频率，所述干涉部包括：第一干涉板，所述第一干涉板的上端固定设置在所述抗性消声室的内壁上，所述第一干涉板的下端自上向下延伸，所述第一干涉板的下端与所述抗性消声室的内壁共同围成制冷剂流动路径；和第二干涉板，所述第二干涉板设置在所述第一干涉板下游，所述第二干涉板的下端固定设置在所述抗性消声室的内壁上，所述第二干涉板的上端自下向上延伸，所述第二干涉板的上端与所述抗性消声室的内壁共同围成制冷剂流动路径。
进一步的，所述出口段为直管段，所述出口段的截面直径小于所述抗性消声室的截面直径。
为达到阻性消声和抗性消声的双重结果，所述抗性消声室的外侧包覆有阻性吸声材料，所述阻性吸声材料为矿棉、玻璃棉、毛毡或木丝吸声板。
进一步的，所述抗性消声室外侧设置有壳体，所述壳体与所述抗性消声室的外壁共同围成消声腔，所述阻性吸声材料填充在所述消声腔中。
本发明的另一个方面提供一种空气调节装置，包括喷射器；所述喷射器包括：入口段，所述入口段连接分液器；出口段，所述出口段连接室内换热器；和抗性消声室，所述抗性消声室形成在所述入口段和出口段之间，所述抗性消声室的截面面积大于所述入口段的截面面积。
与现有技术相比，本发明的优点和积极效果是：
本发明所提供的喷射器，由于抗性消声室的截面面积相对于入口段发生突变，气液两相制冷剂所产生的噪声在传播过程中引起阻抗的改变而产生声能的反射、干涉，从而降低由抗性消声室，即整个喷射器向外辐射的声能，从而达到消声目的，室内侧的用户不会受到干扰，提高了整个产品的使用舒适度。本发明所提供的喷射器既是一个热力学节流器件，也是一个机械振动减噪器件，具有双重功能。
结合附图阅读本发明的具体实施方式后，本发明的其他特点和优点将变得更加清楚。
为了更清楚地说明本发明实施例中的技术方案，下面将对实施例中所需要使用的附图作一简单地介绍，显而易见地，下面描述中的附图是本发明的一些实施例，对于本领域普通技术人员来讲，在不付出创造性劳动的前提下，还可以根据这些附图获得其他的附图。
图1为现有技术中的喷射器的结构示意图；
图2为本发明所公开的喷射器第一种具体实施例的结构示意图；
图3为本发明所公开的喷射器第二种具体实施例的结构示意图；
图4为采用如图2或图3所示的喷射器的空气调节装置的制冷循环示意图。
为了使本发明的目的、技术方案及优点更加清楚明白，以下将结合附图和实施例，对本发明作进一步详细说明。
需要说明的是，在本发明的描述中，术语“上”、“下”、“左”、“右”、“竖”、“横”、“内”、“外”等指示的方向或位置关系的术语是基于附图所示的方向或位置关系，这仅仅是为了便于描述，而不是指示或暗示所述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。
一种应用于空气调节装置的喷射器如图2所示。出于兼顾能量转换效率和噪音抑制的双重需求，喷射器10优选设计为由入口段11、出口段17和抗性消声室14三个部分组成，其中入口段11设置在分液器20的下游并与分液器20连接，如图4所示。分液器20使用于蒸发器前，将气液两相的制冷剂均匀的分配到蒸发器各个支路中。优选的，为每一个蒸发器支路配套设置一个喷射器10，即每一个喷射器10的入口段11分别与分液器20的一个支路连接。喷射器10的出口段17连接室内换热器30，经过节流后的呈气液两相状态的制冷剂经由 多个喷射器10流入室内换热器30，即蒸发器的各个支路中。在入口段11和出口段17之间还形成有抗性消声室14，抗性消声室14的截面面积大于入口段11的截面面积。由于抗性消声室14的截面面积相对于入口段11发生突变，噪声在传播过程中引起阻抗的改变而产生声能的反射、干涉，从而降低由抗性消声室14，即整个喷射器10向外辐射的声能，从而达到消声目的。这种喷射器既是一个热力学节流器件，也是一个机械振动减噪器件，由一个部件实现了双重功能，可以降低整个制冷系统的零部件数量，为产品节省更多的使用和设计空间。
如图2所示，喷射器10具有以下的具体结构，其中，入口段11包括圆锥管段，圆锥管段具有第一端12和第二端13，其中，第一端12的截面直径大于第二端13的截面直径，即沿制冷剂流动方向，圆锥管段自大向小布设，抗性消声室14的直径大于第二端13的截面面积，即相对于圆锥管段的直径，抗性消声室14的直径突然扩张，造成通道内声阻抗突变，这样，沿制冷剂管道传播的某些频率的声波通不过喷射器10而反射回声源，从而达到消声的目的。同时，圆锥管段可以保持较高的节流效率，起到高效低噪的双重效果。
为提高消声性能，抗性消声室14中还设置由干涉部。干涉部的一端固定设置在抗性消声室14的内壁上，另一端沿垂直于制冷剂流动方向的方向延伸且与抗性消声室14的内壁共同围成制冷剂流动路径。除垂直的设置方式外，干涉部还可以沿制冷剂流动方向倾斜延伸，并与抗性消声室14的内壁共同围成制冷剂流动路径。根据气液两相制冷剂流动噪音的频率范围，干涉部设置两个或两个以上，任意两个相邻干涉部沿制冷剂流动方向依次布设并相向延伸。干涉部可以设计为干涉板的形式，还可以设计为螺旋状。螺旋状的干涉部一方面具有更小的流阻，另一方面也可以同样起到消声降噪的目的。处于对特定频率噪音抑制的目的，如图2所示，干涉板包括第一干涉板15和第二干涉板16。第一干涉板15的上端固定设置在抗性消声室14的内壁上，第一干涉板15的下端自上向下延伸，第一干涉板15的下端与抗性消声室14的内壁共同围成制冷剂流动 路径。第二干涉板16设置在第一干涉板15下游，第二干涉板16的下端固定设置在抗性消声室14的内壁上，第二干涉板16的上端自下向上延伸，第二干涉板16的上端与抗性消声室14的内壁共同围成制冷剂流动路径。针对气液两相制冷剂特定的噪音频率范围，第一干涉板15和第二干涉板16可以使得声波发生反射和干涉，达到降低噪音的目的。
抗性消声室14的下游设置有出口段17。出口段17优选设计为直管段，且出口段17的截面面积直径小于抗性消声室14的截面直径，并进一步优选设计为与流过喷射器10的制冷剂流量成比例。为进一步提高消声效果，抗性消声室14的外侧包覆有阻性吸声材料19。具体来说，如图3所示，在抗性消声室14外侧设置有壳体18。壳体18与抗性消声室14的外壁共同围成消声腔，阻性吸声材料19填充在消声腔中，从而结合抗性消声和阻性消声的消声效果。阻性吸声材料19优选为矿棉、玻璃棉、毛毡或木丝吸声板。
本发明的另一个方面提供一种空气调节装置。包括喷射器。喷射器的具体结构和功能参见上述实施例的详细描述，在此不再赘述，设置有上述喷射器的空气调节装置可以实现同样的技术效果。空气调节装置可以是壁挂式空调器、窗式空调器、立式空调器、热泵装置等等。
以上实施例仅用以说明本发明的技术方案，而非对其进行限制；尽管参照前述实施例对本发明进行了详细的说明，对于本领域的普通技术人员来说，依然可以对前述实施例所记载的技术方案进行修改，或者对其中部分技术特征进行等同替换；而这些修改或替换，并不使相应技术方案的本质脱离本发明所要求保护的技术方案的精神和范围。
Claims (10)
- 一种喷射器，其特征在于：包括：入口段，所述入口段连接分液器；出口段，所述出口段连接室内换热器；和抗性消声室，所述抗性消声室形成在所述入口段和出口段之间，所述抗性消声室的截面面积大于所述入口段的截面面积。
- 根据权利要求1所述的喷射器，其特征在于：所述入口段包括：圆锥管段，所述圆锥管段具有第一端和第二端，其中所述第一端的截面直径大于所述第二端的截面直径,所述抗性消声室的直径大于所述第二端的截面直径。
- 根据权利要求2所述的喷射器，其特征在于：所述抗性消声室包括：干涉部，所述干涉部的一端固定设置在所述抗性消声室的内壁上，另一端沿垂直于制冷剂流动方向的方向延伸或沿制冷剂流动方向倾斜延伸；所述干涉部与所述抗性消声室的内壁共同围成制冷剂流动路径。
- 根据权利要求3所述的喷射器，其特征在于：所述干涉部设置为两个或两个以上，任意两个相邻干涉部沿制冷剂流动方向依次布设并相向延伸。
- 根据权利要求4所述的喷射器，其特征在于：所述干涉部为螺旋形。
- 根据权利要求4所述的喷射器，其特征在于：所述干涉部包括：第一干涉板，所述第一干涉板的上端固定设置在所述抗性消声室的内壁上，所述第一干涉板的下端自上向下延伸，所述第一干涉板的下端与所述抗性消声 室的内壁共同围成制冷剂流动路径；和第二干涉板，所述第二干涉板设置在所述第一干涉板下游，所述第二干涉板的下端固定设置在所述抗性消声室的内壁上，所述第二干涉板的上端自下向上延伸，所述第二干涉板的上端与所述抗性消声室的内壁共同围成制冷剂流动路径。
- 根据权利要求5所述的喷射器，其特征在于：所述出口段为直管段，所述出口段的截面直径小于所述抗性消声室的截面直径。
- 根据权利要求1至7任一项所述的喷射器，其特征在于：所述抗性消声室的外侧包覆有阻性吸声材料；所述阻性吸声材料为矿棉、玻璃棉、毛毡或木丝吸声板。
- 根据权利要求8所述的喷射器，其特征在于，所述抗性消声室外侧设置有壳体，所述壳体与所述抗性消声室的外壁共同围成消声腔，所述阻性吸声材料填充在所述消声腔中。
- 一种空气调节装置，其特征在于，包括如权利要求1至9任一项所述的喷射器。
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Citations (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2342298Y (zh) * | 1998-08-24 | 1999-10-06 | 海尔集团公司 | 空调器制冷系统的消音器 |
| KR101164949B1 (ko) * | 2011-10-04 | 2012-07-12 | 여상근 | 항온 저습 유지 장치 |
| CN102829581A (zh) * | 2011-06-15 | 2012-12-19 | 江森自控空调冷冻设备(无锡)有限公司 | 用于压缩机组制冷系统的带消声功能的气体分流/汇流器 |
| CN203928503U (zh) * | 2014-04-25 | 2014-11-05 | 合肥美的电冰箱有限公司 | 一种降低冷媒噪声的蒸发器结构 |
| CN105020876A (zh) * | 2014-04-24 | 2015-11-04 | 青岛海信日立空调系统有限公司 | 消音过滤器及空调 |
| CN206207705U (zh) * | 2016-11-02 | 2017-05-31 | 青岛海尔空调器有限总公司 | 一种空调的消音器及空调 |
| CN107166822A (zh) * | 2017-07-06 | 2017-09-15 | 中国计量大学 | 空调电子膨胀阀噪音的调节方法 |
| CN110285496A (zh) * | 2019-07-29 | 2019-09-27 | 珠海格力电器股份有限公司 | 消音器、制冷系统及空调器 |
| CN209494682U (zh) * | 2019-01-16 | 2019-10-15 | 上海海立电器有限公司 | 压缩机储液器、压缩机及空调系统 |
| CN111351272A (zh) * | 2020-03-19 | 2020-06-30 | 青岛海尔空调器有限总公司 | 喷射器及空气调节装置 |
Family Cites Families (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE20205068U1 (de) * | 2002-03-30 | 2002-08-29 | FESTO AG & Co., 73734 Esslingen | Druckluft-Schalldämpfer |
| JP4069880B2 (ja) * | 2004-02-18 | 2008-04-02 | 株式会社デンソー | エジェクタ |
| CN201583069U (zh) * | 2010-01-11 | 2010-09-15 | 苏州恒兆空调节能科技有限公司 | 节流消音装置以及节流消音空调器 |
| CN202451476U (zh) * | 2012-01-18 | 2012-09-26 | 杭州隆达真空设备有限公司 | 一种多喷嘴式蒸汽喷射器 |
| CN103148629B (zh) * | 2013-02-28 | 2014-12-24 | 西安交通大学 | 用于双温直冷式电冰箱的气液两相流喷射器增效制冷系统 |
| JP6115345B2 (ja) * | 2013-06-18 | 2017-04-19 | 株式会社デンソー | エジェクタ |
| CN104089439A (zh) * | 2014-07-01 | 2014-10-08 | 浙江大学宁波理工学院 | 随蒸发温度自动调节面积比的喷射器及喷射式制冷机 |
| CN107024040A (zh) * | 2017-04-24 | 2017-08-08 | 美的集团股份有限公司 | 喷射器节流制冷系统和引流方法 |
| CN110455000A (zh) * | 2019-07-24 | 2019-11-15 | 中南大学 | 新型节能降噪制冷循环系统 |
| CN212253248U (zh) * | 2020-03-19 | 2020-12-29 | 青岛海尔空调器有限总公司 | 喷射器及空气调节装置 |
-
2020
- 2020-03-19 CN CN202010197165.8A patent/CN111351272A/zh active Pending
- 2020-12-02 WO PCT/CN2020/133248 patent/WO2021184828A1/zh not_active Ceased
Patent Citations (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2342298Y (zh) * | 1998-08-24 | 1999-10-06 | 海尔集团公司 | 空调器制冷系统的消音器 |
| CN102829581A (zh) * | 2011-06-15 | 2012-12-19 | 江森自控空调冷冻设备(无锡)有限公司 | 用于压缩机组制冷系统的带消声功能的气体分流/汇流器 |
| KR101164949B1 (ko) * | 2011-10-04 | 2012-07-12 | 여상근 | 항온 저습 유지 장치 |
| CN105020876A (zh) * | 2014-04-24 | 2015-11-04 | 青岛海信日立空调系统有限公司 | 消音过滤器及空调 |
| CN203928503U (zh) * | 2014-04-25 | 2014-11-05 | 合肥美的电冰箱有限公司 | 一种降低冷媒噪声的蒸发器结构 |
| CN206207705U (zh) * | 2016-11-02 | 2017-05-31 | 青岛海尔空调器有限总公司 | 一种空调的消音器及空调 |
| CN107166822A (zh) * | 2017-07-06 | 2017-09-15 | 中国计量大学 | 空调电子膨胀阀噪音的调节方法 |
| CN209494682U (zh) * | 2019-01-16 | 2019-10-15 | 上海海立电器有限公司 | 压缩机储液器、压缩机及空调系统 |
| CN110285496A (zh) * | 2019-07-29 | 2019-09-27 | 珠海格力电器股份有限公司 | 消音器、制冷系统及空调器 |
| CN111351272A (zh) * | 2020-03-19 | 2020-06-30 | 青岛海尔空调器有限总公司 | 喷射器及空气调节装置 |
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