CN103967789A - Two-stage enthalpy-added compressor and air conditioner with two-stage enthalpy-added compressor - Google Patents
Two-stage enthalpy-added compressor and air conditioner with two-stage enthalpy-added compressor Download PDFInfo
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- 230000003584 silencer Effects 0.000 claims description 8
- 230000002093 peripheral effect Effects 0.000 claims description 4
- 230000009467 reduction Effects 0.000 abstract description 5
- 230000000694 effects Effects 0.000 abstract description 4
- 238000005457 optimization Methods 0.000 abstract 1
- 238000010586 diagram Methods 0.000 description 7
- 239000003507 refrigerant Substances 0.000 description 7
- 230000006835 compression Effects 0.000 description 6
- 238000007906 compression Methods 0.000 description 6
- 238000009434 installation Methods 0.000 description 5
- 238000005192 partition Methods 0.000 description 5
- 239000007788 liquid Substances 0.000 description 4
- 238000004378 air conditioning Methods 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 2
- 230000006872 improvement Effects 0.000 description 2
- 238000005096 rolling process Methods 0.000 description 2
- 230000008859 change Effects 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 230000007812 deficiency Effects 0.000 description 1
- 238000002474 experimental method Methods 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 230000007774 longterm Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
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Abstract
Description
技术领域technical field
本发明涉及制冷领域，特别是涉及一种滚动转子式双级增焓压缩机。The invention relates to the refrigeration field, in particular to a rolling rotor type two-stage enthalpy-increasing compressor.
背景技术Background technique
随着人们生活水平的不断提高，消费者对空调系统的要求越来越高。滚动转子式双级增焓压缩机运行平稳、低温制热及高温制冷能力强、能效高，因而越来越广泛的应用于空调和热泵热水系统中。With the continuous improvement of people's living standards, consumers have higher and higher requirements for air-conditioning systems. The rolling rotor double-stage enthalpy-increasing compressor runs smoothly, has strong low-temperature heating and high-temperature cooling capabilities, and high energy efficiency, so it is more and more widely used in air-conditioning and heat pump hot water systems.
目前的双级增焓压缩机（如图1）所示：主要由壳体组件、上盖组件、下盖组成的密闭腔、热套在壳体组件内部的电机定子组件、拖动压缩机旋转的曲轴、热套在曲轴上的电机转子组件、支撑曲轴的上法兰和下法兰、低压级气缸与低压级滚子和低压级滑片共同组成的低压级压缩腔、高压级气缸与高压级滚子和高压级滑片共同组成的高压级压缩腔、将高压级压缩腔和低压级压缩腔分隔开的中隔板、形成中压腔的中压零件、深入低压级气缸与低压级压缩腔连通的气液分离器、对中压腔进行补气的增焓结构组件。The current two-stage enthalpy-increasing compressor (as shown in Figure 1) is as follows: a closed cavity mainly composed of a shell assembly, an upper cover assembly, and a lower cover, a motor stator assembly that is shrunk inside the shell assembly, and a compressor that is driven to rotate The crankshaft, the motor rotor assembly shrunk on the crankshaft, the upper flange and the lower flange supporting the crankshaft, the low-pressure stage compression chamber composed of the low-pressure stage cylinder, the low-pressure stage roller and the low-pressure stage slide vane, the high-pressure stage cylinder and the high-pressure stage High-pressure stage rollers and high-pressure stage slides form a high-pressure stage compression chamber, an intermediate partition that separates the high-pressure stage compression chamber from the low-pressure stage compression chamber, medium-pressure parts that form the medium-pressure chamber, and deep low-pressure stage cylinders and low-pressure stage A gas-liquid separator connected to the compression chamber, and an enthalpy-increasing structural component for supplying air to the medium-pressure chamber.
目前的两级增焓压缩机，上法兰设置有用于高压级气缸排气的上法兰排气孔；下法兰(或下气缸，或中隔板)上设置有用于低压级气缸排气的下法兰排气孔；消音器安装在上法兰上，其设置有消音器排气孔。现有双级增焓压缩机上消音器排气孔与上、下法兰排气孔的等效直径比值过小，压缩机整体的能效降低；上消音器排气孔与上、下法兰排气孔的等效直径比值过大，上消音器的降噪效果变差。In the current two-stage enthalpy-increasing compressor, the upper flange is provided with an upper flange exhaust hole for the exhaust of the high-pressure cylinder; the lower flange (or lower cylinder, or middle partition) is provided with an exhaust hole for the low-pressure cylinder. The exhaust hole of the lower flange; the muffler is installed on the upper flange, which is provided with a muffler exhaust hole. The equivalent diameter ratio between the exhaust hole of the upper muffler and the exhaust holes of the upper and lower flanges of the existing two-stage enthalpy-increasing compressor is too small, and the overall energy efficiency of the compressor is reduced; the exhaust hole of the upper muffler and the exhaust holes of the upper and lower flanges If the equivalent diameter ratio of the air hole is too large, the noise reduction effect of the upper muffler will be deteriorated.
发明内容Contents of the invention
本发明的目的是为了克服现有技术的不足，而提供一种在不使压缩机整体能效降低的同时保证降噪效果的双级增焓压缩机。The object of the present invention is to overcome the deficiencies of the prior art and provide a two-stage enthalpy-increasing compressor that ensures noise reduction while not reducing the overall energy efficiency of the compressor.
本发明技术方案如下：Technical scheme of the present invention is as follows:
一种双级增焓压缩机，包括外壳、设置在外壳内的电机和泵体组件，所述泵体组件包括曲轴、高压级气缸和低压级气缸，所述泵体组件还包括上法兰、下法兰和消音器；A two-stage enthalpy-increasing compressor, comprising a shell, a motor arranged in the shell, and a pump body assembly, the pump body assembly includes a crankshaft, a high-pressure stage cylinder, and a low-pressure stage cylinder, and the pump body assembly also includes an upper flange, Lower flange and silencer;
所述上法兰设置在所述高压级气缸上，所述上法兰上设置有连通所述高压级气缸的上法兰排气孔；The upper flange is arranged on the high-pressure cylinder, and the upper flange is provided with an upper flange exhaust hole communicating with the high-pressure cylinder;
所述下法兰设置在所述低压级气缸上，所述下法兰上设置有连通所述低压级气缸的下法兰排气孔；The lower flange is arranged on the low-pressure stage cylinder, and the lower flange is provided with a lower flange exhaust hole communicating with the low-pressure stage cylinder;
所述消音器设置在所述上法兰上，所述消音器上设有安装孔，所述曲轴穿过所述安装孔；The muffler is arranged on the upper flange, the muffler is provided with a mounting hole, and the crankshaft passes through the mounting hole;
所述消音器上设置有的排气口；The exhaust port provided on the muffler;
所述排气口的等效直径D3与所述上法兰排气孔的等效直径D1的比值α为1～2；The ratio α of the equivalent diameter D3 of the exhaust port to the equivalent diameter D1 of the upper flange exhaust hole is 1-2;
所述排气口的等效直径D3与所述下法兰排气孔的等效直径D2的比值β为1～1.5。The ratio β of the equivalent diameter D3 of the exhaust port to the equivalent diameter D2 of the lower flange exhaust hole is 1˜1.5.
较优地，所述上法兰排气孔径向截面为圆形或D字形；Preferably, the radial cross-section of the exhaust hole on the upper flange is circular or D-shaped;
所述下法兰排气孔径向截面为圆形或D字形。The radial cross-section of the exhaust hole of the lower flange is circular or D-shaped.
较优地，所述排气口径向截面为圆形，设置在所述安装孔的周侧。Preferably, the exhaust port has a circular cross-section in radial direction and is arranged on the peripheral side of the installation hole.
较优地，所述消音器上的安装孔为凸圆孔，所述排气口为所述安装孔容纳所述曲轴后的剩余部分。Preferably, the mounting hole on the muffler is a convex hole, and the exhaust port is the remaining part after the crankshaft is accommodated in the mounting hole.
较优地，所述排气口包括第一排气口和第二排气口；Preferably, the exhaust port includes a first exhaust port and a second exhaust port;
所述第一排气口的径向截面为圆形，设置在所述消声器上的安装孔的周侧；The radial section of the first exhaust port is circular, and is arranged on the peripheral side of the installation hole on the muffler;
所述安装孔为凸圆孔，所述第二排气口为所述安装孔容纳所述曲轴后的剩余部分。The mounting hole is a convex hole, and the second exhaust port is the remaining part after the crankshaft is accommodated in the mounting hole.
较优地，所述排气口的等效直径D3与所述上法兰排气孔的等效直径D1的比值为1.4；Preferably, the ratio of the equivalent diameter D3 of the exhaust port to the equivalent diameter D1 of the upper flange exhaust hole is 1.4;
较优地，所述排气口的等效直径D3与所述下法兰排气孔的等效直径的D2比值为1.3。Preferably, the ratio of the equivalent diameter D3 of the exhaust port to the equivalent diameter D2 of the exhaust hole of the lower flange is 1.3.
还涉及一种空调器，所述空调器包括上述任意一项技术特征的双级增焓压缩机。It also relates to an air conditioner, which includes a two-stage enthalpy-increasing compressor with any one of the above-mentioned technical features.
本发明的有益效果为：The beneficial effects of the present invention are:
能降低压缩机的排气阻力，降低排气噪声，同时还有消音器制作成本低、结构简单、安装方便等有益效果。The exhaust resistance of the compressor can be reduced, the exhaust noise can be reduced, and the muffler has the beneficial effects of low production cost, simple structure, convenient installation and the like.
附图说明Description of drawings
图1为本发明的双级增焓压缩机一实施例示意图；Fig. 1 is a schematic diagram of an embodiment of a two-stage enthalpy increasing compressor of the present invention;
图2为图1所示泵体组件与曲轴配合示意图；Fig. 2 is a schematic diagram of cooperation between the pump body assembly shown in Fig. 1 and the crankshaft;
图3为排气阻力损失、排气噪声随比值α的变化曲线图；Figure 3 is a graph showing the variation of exhaust resistance loss and exhaust noise with the ratio α;
图4为排气阻力损失、排气噪声随比值β的变化曲线图；Figure 4 is a graph showing the variation of exhaust resistance loss and exhaust noise with the ratio β;
图5为图2所示消音器的实施例一示意图；Fig. 5 is a schematic diagram of Embodiment 1 of the muffler shown in Fig. 2;
图6为图2所示消音器的实施例二示意图；Fig. 6 is a schematic diagram of Embodiment 2 of the muffler shown in Fig. 2;
图7为图2所示消音器的实施例三示意图；Fig. 7 is a schematic diagram of Embodiment 3 of the muffler shown in Fig. 2;
图8为图2所示上法兰排气孔结构局部示意图；Fig. 8 is a partial schematic diagram of the vent hole structure of the upper flange shown in Fig. 2;
图9为排气孔为圆形的图2所示上法兰俯视示意图；Fig. 9 is a schematic top view of the upper flange shown in Fig. 2 with the exhaust hole being circular;
图10为排气孔为D型的图2所示上法兰形状图；Fig. 10 is a shape diagram of the upper flange shown in Fig. 2 with a D-type exhaust hole;
其中，in,
1外壳；2压缩电机；3增焓部件；4气缸组件；5分液器部件；6曲轴；7上法兰；8高压级气缸；9泵体隔板；10低压级气缸；11下法兰；12端盖；13消音器；14排气口；15安装孔；16阀片；17阀片挡板；18上法兰排气孔。1 Shell; 2 Compression motor; 3 Enthalpy increasing parts; 4 Cylinder assembly; 5 Liquid distributor part; 6 Crankshaft; 7 Upper flange; 8 High pressure cylinder; ; 12 end cover; 13 muffler; 14 exhaust port; 15 mounting hole; 16 valve; 17 valve baffle;
具体实施方式Detailed ways
为了使本发明的目的、技术方案及优点更加清楚明白，以下结合附图及实施例对本发明的双级增焓压缩机进行进一步详细说明。应当理解，此处所描述的具体实施例仅用以解释本发明，并不用于限定本发明。In order to make the purpose, technical solution and advantages of the present invention clearer, the two-stage enthalpy-increasing compressor of the present invention will be further described in detail below in conjunction with the accompanying drawings and embodiments. It should be understood that the specific embodiments described here are only used to explain the present invention, not to limit the present invention.
如图1、2所示，本发明的双级增焓压缩机一实施例包括外壳1、分液器部件5、增焓部件3、设置在外壳1内电机2和泵体组件，泵体组件包括曲轴6、高压级气缸和低压级气缸，泵体组件还包括上法兰、下法兰和消音器；曲轴6上设置有第一偏心部和第二偏心部，电机2带动曲轴6转动；气缸组件4包括高压级气缸8、低压级压缸10、设置在高压级气缸8和低压级气缸10之间的泵体隔板9、设置在高压级气缸8上的上法兰7、设置在上法兰7上的消音器13、设置在低压级气缸10上的下法兰11、设置在下法兰11上的端盖12；As shown in Figures 1 and 2, an embodiment of the two-stage enthalpy-increasing compressor of the present invention includes a casing 1, a liquid separator part 5, an enthalpy-increasing part 3, a motor 2 and a pump body assembly arranged in the casing 1, and the pump body assembly Including a crankshaft 6, a high-pressure cylinder and a low-pressure cylinder, the pump body assembly also includes an upper flange, a lower flange and a muffler; the crankshaft 6 is provided with a first eccentric part and a second eccentric part, and the motor 2 drives the crankshaft 6 to rotate; The cylinder assembly 4 includes a high-pressure stage cylinder 8, a low-pressure stage cylinder 10, a pump body partition 9 arranged between the high-pressure stage cylinder 8 and the low-pressure stage cylinder 10, an upper flange 7 arranged on the high-pressure stage cylinder 8, and a The muffler 13 on the upper flange 7, the lower flange 11 arranged on the low-pressure stage cylinder 10, and the end cover 12 arranged on the lower flange 11;
第一偏心部（未示出）设置在高压级气缸8内，与高压级气缸8配合，第二偏心部（未示出）设置地低压级气缸10内，与低压级气缸10配合；消音器13与上法兰7配合形成连通高压级气缸排气孔的高压腔；下法兰11上设置有环形槽，环形槽与端盖12配合形成中压腔；The first eccentric part (not shown) is arranged in the high-pressure stage cylinder 8 and cooperates with the high-pressure stage cylinder 8, and the second eccentric part (not shown) is arranged in the low-pressure stage cylinder 10 and cooperates with the low-pressure stage cylinder 10; the muffler 13 cooperates with the upper flange 7 to form a high-pressure chamber connected to the exhaust hole of the high-pressure cylinder; the lower flange 11 is provided with an annular groove, and the annular groove cooperates with the end cover 12 to form a medium-pressure chamber;
下法兰11上设有用于连接增焓部件3的增焓口，增焓口连通中压腔；增焓口也可设置在泵体隔板9上；The lower flange 11 is provided with an enthalpy-increasing port for connecting the enthalpy-increasing component 3, and the enthalpy-increasing port is connected to the medium-pressure chamber; the enthalpy-increasing port can also be arranged on the pump body partition 9;
如图9、10所示，上法兰7上设置有连通高压腔的上法兰排气孔18；上法兰排气孔18形状为圆形或D字形；As shown in Figures 9 and 10, the upper flange 7 is provided with an upper flange vent 18 connected to the high-pressure chamber; the upper flange vent 18 is circular or D-shaped;
下法兰11上设置有连通中压腔的下法兰排气孔（未示出）；下法兰排气孔形状为圆形或D字形。The lower flange 11 is provided with a lower flange vent hole (not shown) communicating with the medium-pressure chamber; the shape of the lower flange vent hole is circular or D-shaped.
如图8所示，上法兰排气孔和/或下法兰排气孔上还设置阀片17和阀片挡板1；As shown in Figure 8, a valve plate 17 and a valve plate baffle 1 are also arranged on the upper flange vent hole and/or the lower flange vent hole;
消音器13上设有安装孔15，曲轴6穿过安装孔15安装在气缸组件上；The muffler 13 is provided with a mounting hole 15, and the crankshaft 6 passes through the mounting hole 15 and is mounted on the cylinder assembly;
消音器13上设置有排气口14，高压级气缸8内压缩完成的冷媒通过高压级气缸8上的排气口被排放到消音器13和上法兰7形成的高压排气腔内，经过消音后通过排气口14排出至压缩机本体外；The muffler 13 is provided with an exhaust port 14, and the refrigerant compressed in the high-pressure stage cylinder 8 is discharged into the high-pressure exhaust chamber formed by the muffler 13 and the upper flange 7 through the exhaust port on the high-pressure stage cylinder 8. After the sound is silenced, it is discharged out of the compressor body through the exhaust port 14;
经过本发明人的长期研究和实验，发现排气口14的等效直径D3与上法兰排气孔18的等效直径D1的比值α为1～2时，压缩机的排气阻力以及排气噪音将得到有效的控制并降低，优选的，排气口14的等效直径D3与上法兰排气孔18的等效直径D1的比值α为1.4。After long-term research and experiments by the inventors, it is found that when the ratio α of the equivalent diameter D3 of the exhaust port 14 to the equivalent diameter D1 of the upper flange exhaust hole 18 is 1 to 2, the exhaust resistance and the discharge resistance of the compressor will be reduced. Gas noise will be effectively controlled and reduced. Preferably, the ratio α of the equivalent diameter D3 of the exhaust port 14 to the equivalent diameter D1 of the upper flange exhaust hole 18 is 1.4.
同时，排气口14的等效直径D3与下法兰排气孔的等效直径D2的比值β为1～1.5时，压缩机的排气阻力以及排气噪音将得到有效的控制并降低；优选地，排气口的等效直径D3与下法兰排气孔的等效直径的D2比值β为1.3；At the same time, when the ratio β of the equivalent diameter D3 of the exhaust port 14 to the equivalent diameter D2 of the lower flange exhaust hole is 1 to 1.5, the exhaust resistance and exhaust noise of the compressor will be effectively controlled and reduced; Preferably, the ratio β of the equivalent diameter D3 of the exhaust port to the equivalent diameter D2 of the lower flange exhaust hole is 1.3;
其中，等效直径计算公式为S为排气口面积。Among them, the equivalent diameter calculation formula is S is the exhaust port area.
较优地，如图5所示，作为一种可实施方式，消音器13上的曲轴安装孔为圆孔，排气口14的形状也为圆形，设置在安装孔的周侧。Preferably, as shown in FIG. 5 , as a possible implementation, the crankshaft mounting hole on the muffler 13 is a circular hole, and the exhaust port 14 is also circular in shape and is arranged around the mounting hole.
较优地，如图6所示，作为一种可实施方式，消音器13上的曲轴安装孔为凸圆孔，消音器13上的排气口为安装孔容纳曲轴6后的剩余部分。Preferably, as shown in FIG. 6 , as a possible implementation, the crankshaft installation hole on the muffler 13 is a convex hole, and the exhaust port on the muffler 13 is the remaining part after the crankshaft 6 is accommodated in the installation hole.
较优地，如图7所示，作为一种可实施方式，Preferably, as shown in FIG. 7, as an implementable manner,
消音器13上的排气口包括第一排气口和第二排气口；The exhaust port on the muffler 13 includes a first exhaust port and a second exhaust port;
所述第一排气口的形状为圆形，设置在消音器13上的安装孔的周侧；The shape of the first exhaust port is circular, and it is arranged on the peripheral side of the mounting hole on the muffler 13;
所述安装孔为凸圆孔，所述第二排气口为安装孔容纳曲轴后的剩余部分。The mounting hole is a convex hole, and the second exhaust port is the remaining part after the crankshaft is accommodated in the mounting hole.
压缩机的工作原理为：在电机2的驱动下，压缩机运转，从系统回来的冷媒通过分液器部件5进入低压级气缸10中，经压缩后排出至下法兰11中，另一部分冷媒从系统的另一回路回来进入增焓部件3，通过低压级气缸10上的增焓口流入下法兰11中，与经低压级气缸10压缩后排出至下法兰11中的冷媒混合，形成中压的混合冷媒，混合冷媒通过低压级气缸10上的流通孔经泵体隔板9后，被高压缸8吸入并压缩成高压冷媒，通过上法兰7和消音器13排出至壳体内部的上部空间，并从排气管排到系统。The working principle of the compressor is: driven by the motor 2, the compressor runs, and the refrigerant returned from the system enters the low-pressure stage cylinder 10 through the liquid separator part 5, and is discharged to the lower flange 11 after being compressed, and the other part of the refrigerant Come back from another circuit of the system and enter the enthalpy increasing part 3, flow into the lower flange 11 through the enthalpy increasing port on the low-pressure stage cylinder 10, and mix with the refrigerant compressed by the low-pressure stage cylinder 10 and discharged into the lower flange 11 to form Medium-pressure mixed refrigerant, the mixed refrigerant passes through the flow hole on the low-pressure stage cylinder 10, passes through the pump body partition 9, is inhaled by the high-pressure cylinder 8 and compressed into high-pressure refrigerant, and is discharged into the casing through the upper flange 7 and the muffler 13 headspace and exhaust from the exhaust pipe to the system.
采用以上实施例的双级增焓压缩机，排气阻力损失、排气噪声随比值α的变化曲线图如图3所示；排气阻力损失、排气噪声随比值β的变化曲线图如图Using the two-stage enthalpy-increasing compressor of the above embodiment, the curves of exhaust resistance loss and exhaust noise with the ratio α are shown in Figure 3; the curves of exhaust resistance loss and exhaust noise with the ratio β are shown in Figure 3.
4所示；由变化曲线图可以看出比值α在1-2、比值β在1-1.5时，消音器排气阻力小、降噪效果明显。4; it can be seen from the change curve that when the ratio α is 1-2 and the ratio β is 1-1.5, the exhaust resistance of the muffler is small and the noise reduction effect is obvious.
通过优化上法兰和下法兰的排气孔与消音器排气口的尺寸关系，可以达到降低压缩机排气阻力、降低排气噪声的效果。By optimizing the size relationship between the exhaust holes of the upper flange and the lower flange and the exhaust port of the muffler, the effects of reducing the exhaust resistance of the compressor and the exhaust noise can be achieved.
以上所述实施例仅表达了本发明的几种实施方式，其描述较为具体和详细，但并不能因此而理解为对本发明专利范围的限制。应当指出的是，对于本领域的普通技术人员来说，在不脱离本发明构思的前提下，还可以做出若干变形和改进，这些都属于本发明的保护范围。因此，本发明专利的保护范围应以所附权利要求为准。The above-mentioned embodiments only express several implementation modes of the present invention, and the description thereof is relatively specific and detailed, but should not be construed as limiting the patent scope of the present invention. It should be pointed out that those skilled in the art can make several modifications and improvements without departing from the concept of the present invention, and these all belong to the protection scope of the present invention. Therefore, the protection scope of the patent for the present invention should be based on the appended claims.
Claims (8)
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