CN102062503A - Pipeline distributing system of compressor and air conditioner with same - Google Patents
Pipeline distributing system of compressor and air conditioner with same Download PDFInfo
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- CN102062503A CN102062503A CN2009102301731A CN200910230173A CN102062503A CN 102062503 A CN102062503 A CN 102062503A CN 2009102301731 A CN2009102301731 A CN 2009102301731A CN 200910230173 A CN200910230173 A CN 200910230173A CN 102062503 A CN102062503 A CN 102062503A
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- return line
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- piping system
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Abstract
The invention discloses a pipeline distributing system of a compressor and an air conditioner with the same. The pipeline distributing system comprises an air discharging pipeline and an air returning pipeline, wherein the air returning pipeline is provided with an L-shaped bent pipeline section which is positioned at the bottom of the air returning pipeline. Without adopting additional balance weight, the pipeline distributing system has shorter distributed pipeline and favorable vibration attenuation.
Description
Technical field
The present invention relates to a kind of compressor piping system, specifically, relate to a kind of piping system of the single cylinder rotary compressor more than 3 and 3, belong to the air-conditioner technical field of structures.
Background technology
Because single cylinder rotary compressor Energy Efficiency Ratio is higher, manufacturing cost is relatively low, is applied in and reduces air-conditioner cost, raising household air-conditioner in the air-conditioner.For the single cylinder rotary compressor of 3 following power, because its power output is less relatively, the vibration that produces during work is little, and is little with the piping system structural design difficulty of its coupling, is used widely in the air-conditioner of 3 following power at present.For the air-conditioner of 3 and 3 above power, if adopt the single cylinder rotary compressor, can produce bigger vibration during work, to higher with the piping system structural requirement of its coupling, design difficulty is bigger.If the piping system design is unreasonable, the covibration of as easy as rolling off a log generation compressor and piping system causes air-conditioner to reduce greatly service life.Therefore, existing air-conditioner more than 3 and 3 adopts two-spool compressor mostly, and its cost is higher.Though also there is utmost point individual product to adopt the single cylinder rotary compressor, but there are a plurality of U-shaped bendings in its pipe arrangement pipeline, pipeline is longer, and need to adopt clay or blob of viscose as counterweight, not only cost height, design difficulty are big, and clay or the long-time use of blob of viscose come off easily, influences the overall performance of air-conditioner.
Summary of the invention
The present invention is directed in the prior art that the design difficulty that 3 and above single cylinder rotary compressor piping system exist is big, complex structure, cost problem of higher, a kind of compressor piping system is provided, described piping system is simple in structure, rigidity is strong, and the pipe arrangement pipeline is shorter, and damping property is better.
For solving the problems of the technologies described above, the present invention is achieved by the following technical solutions:
A kind of compressor piping system comprises gas exhaust piping and return line, and described return line has a L shaped bend loss, and described L shaped bend loss is positioned at the bottom of described return line.
According to the present invention, the opening direction of described L shaped bend loss to increase the intensity of described return line, further reduces pipeline vibration towards compressor.
According to the present invention, for avoiding gas exhaust piping and compressor to produce resonance, described gas exhaust piping downward projection forms drop shadow curve, in described drop shadow curve, the tangent line at starting point place and the tangent line of destination county and described drop shadow curve form closed curve, and the tangent line at described starting point place and the tangent line of described destination county angular range that form, that be positioned at the angle α of described closed curve inside is 70-100 °.
Described angle α optimized angle is 90 °.
According to the present invention, described gas exhaust piping has a U-bend section, and described U-bend section is positioned at the bottom of described gas exhaust piping.
According to the present invention, described compressor refers in particular to the single cylinder rotary compressor more than 3 or 3.
The present invention also provides a kind of air-conditioner, comprises compressor and air valve, and is connected gas exhaust piping and return line between described compressor and the described air valve.For reducing the air-conditioner vibration, described return line has a L shaped bend loss, and described L shaped bend loss is positioned at the bottom of described return line; Described gas exhaust piping downward projection forms drop shadow curve, in described drop shadow curve, the tangent line at starting point place and the tangent line of destination county and described drop shadow curve form closed curve, and the tangent line at described starting point place and the tangent line of described destination county angular range that form, that be positioned at the angle α of described closed curve inside is 70-100 °.
Compared with prior art, advantage of the present invention and good effect are:
1, design only has the return line of L shaped bend loss in the bottom, reduced the weight of return line, improved its rigidity, solved the inboard stress problem of return line and compressor return air mouth connecting place effectively, avoided the generation of return line and compressor covibration, reduce the vibration of return line, thereby reduced the vibration of whole piping system.
2, the opening direction of the L shaped bend loss of return line is towards compressor, thereby whole return line is formed base for supporting, further strengthened the bulk strength of return line, reduced the vibration of return line.
3, within the specific limits with the angle design of the tangent line of the tangent line at starting point place in the gas exhaust piping downward projection curve and destination county, efficiently solve the inboard stress problem of gas exhaust piping and compressor junction, avoided the generation of gas exhaust piping and compressor covibration, reduce the vibration of gas exhaust piping, thereby reduced the vibration of whole piping system.
4, whole piping system does not need clay or blob of viscose as counterweight, has avoided the hidden danger of quality that comes off and cause because of clay or blob of viscose, has improved the overall operation performance of using the air-conditioner of piping system.
Description of drawings
Fig. 1 is the structural representation with embodiment of air-conditioner of compressor piping system of the present invention;
Fig. 2 is the structural representation of piping system among Fig. 1;
Fig. 3 is the structural representation of return line and compressor relative position relation among Fig. 1;
Fig. 4 is the structural representation of gas exhaust piping and compressor relative position relation among Fig. 1;
Fig. 5 is the downward projection figure of gas exhaust piping among Fig. 1;
Fig. 6 is the strain transfer curve figure of gas exhaust piping stress test point on the Y direction among Fig. 2;
Fig. 7 is the strain transfer curve figure of gas exhaust piping stress test point on directions X among Fig. 2;
Fig. 8 is the strain transfer curve figure of return line stress test point on the Y direction among Fig. 2;
Fig. 9 is the strain transfer curve figure of return line stress test point on directions X among Fig. 2;
Figure 10 is the time-domain response curve figure of gas exhaust piping stress test point among Fig. 2;
Figure 11 is the time-domain response curve figure of return line stress test point among Fig. 2.
The specific embodiment
The present invention is further detailed explanation below in conjunction with accompanying drawing.
The problem that the single cylinder rotary compressor PIPING DESIGN difficulty that the present invention is directed in the prior art 3 and above power is big, be easy to generate compressor and piping system covibration has successfully been designed the piping system of the single cylinder rotary compressor that mates 3 and above power.
See also illustrated in figures 1 and 2ly, wherein, Fig. 1 is the structural representation with embodiment of air-conditioner of compressor piping system of the present invention, and Fig. 2 is the structural representation of piping system among Fig. 1.
This embodiment is that 3 air-conditioner is an example with power, is provided with power and is 3 single cylinder rotary compressor 1 in air-conditioner, and described compressor 1 is connected with fluid reservoir 2.Have exhaust outlet of compressor 11 on the top of described compressor 1, have compressor return air mouth 12 on the top of described fluid reservoir 2.Also be provided as the four-way change-over valve 3 of air valve in the described air-conditioner, between one of them valve port of described four-way change-over valve 3 and described exhaust outlet of compressor 11, be connected with gas exhaust piping 4, be connected with return line 5 between another valve port of described four-way change-over valve 3 and described compressor return air mouth 12, described gas exhaust piping 4 and described return line 5 have constituted the piping system of described single cylinder rotary compressor 1.
Described embodiment avoids piping system and described single cylinder rotary compressor 1 to produce the vibration of resonating, reducing piping system as far as possible, and described return line 5 and described gas exhaust piping 4 have all been carried out particular design.Be specially:
For improving the rigidity of described return line 5, this embodiment changes that return line has the method for designing of at least two bend loss in the conventional design, only in the bottom design of described return line 5 a L shaped bend loss 51, reduced the curved number of return line 5, promptly reduced pipeline weight.
With reference to the return line shown in Figure 3 and the structural representation of compressor relative position relation, the opening direction of described L shaped bend loss 51, be that L shaped depression position is towards described compressor 1, thereby whole return line 5 is played the effect of base support, increased the bulk strength of return line 5.And because L shaped bend pipe structure has changed the flow direction of air-flow in return line 5, increased the suction noise ability of pipeline, further improved the effectiveness in vibration suppression of piping system.
With reference to the gas exhaust piping shown in Figure 4 and the structural representation of compressor relative position relation, and the downward projection figure of gas exhaust piping shown in Figure 5, described embodiment is for solving the inboard stress problem of described gas exhaust piping 4 and described compressor 1 connecting place, improve the effectiveness in vibration suppression of whole piping system, designing requirement to described gas exhaust piping 4 is: described gas exhaust piping 4 downward projections form the AA ' CB ' B of drop shadow curve, in the described AA ' CB ' B of drop shadow curve, the tangent line BB ' at the tangent line AA ' at starting point A place and terminal point B place and the described AA ' CB ' B of drop shadow curve form closed curve, the tangent line BB ' formation at the tangent line AA ' at described starting point A place and described terminal point B place, the angle that is positioned at the angle α of described closed curve inside is 80 °.
In addition, described gas exhaust piping 4 also only in its bottom design a U-bend section 41, can satisfy the vibration damping requirement.
For the structure of other part line segments in gas exhaust piping 4 and the return line 5, can require according to actual specific design, carry out specific design with factors such as the assembly relation of compressor, whole assembly spaces, this embodiment does not do concrete qualification to this.
In the structure chart of piping system shown in Figure 2, on described gas exhaust piping 4, the nearest inboard selected point a of 180 ° of bending of the described exhaust outlet of compressor of distance 11, on described return line 5, the nearest inboard selected point b of 180 ° of bending of the described compressor return air mouth of distance 12, adopt the Nastran simulation software that above-mentioned a point and b point are carried out stress test and analysis then, analysis result is as follows:
Fig. 6 is the strain transfer curve figure of the stress test point a on the gas exhaust piping on the Y direction among Fig. 2, Fig. 7 is the strain transfer curve figure of the stress test point a on the gas exhaust piping on directions X among Fig. 2, Fig. 8 is the strain transfer curve figure of the stress test point b on the return line on the Y direction among Fig. 2, and Fig. 9 is the strain transfer curve figure of the stress test point b on the return line on directions X among Fig. 2.
In above-mentioned each transfer curve figure, abscissa is represented the intrinsic frequency of air-conditioner system, and ordinate is represented the strain/excitation displacement of test point.As can be known, compressor operating is when 50Hz from above-mentioned each transfer curve figure, and the strain that a point and b are ordered/excitation displacement illustrates the gas exhaust piping 4 at a point place and return line 5 better performances at b point place near 1.0E-4, satisfy the Vibration Absorption Designing requirement.
Figure 10 is the time-domain response curve figure of the stress test point a on the gas exhaust piping among Fig. 2, and Figure 11 is the time-domain response curve figure of the stress test point b on the return line among Fig. 2.
In above-mentioned time-domain curve figure, abscissa is represented the time, and ordinate is represented dependent variable.As can be known, the time domain dependent variable that a point and b are ordered satisfies the damping property requirement all less than 1.0E-4 from these two curve maps.
3 and the single cylinder rotary compressor piping system of above power according to conceptual design of the present invention, its pipe arrangement pipeline is short, cost is lower, damping property is better, pipeline intensity is higher, and do not need counterweights such as clay or blob of viscose, both alleviated the gross weight of piping system, avoided the hidden danger of quality that comes off and cause because of clay or blob of viscose again, significantly improve the whole aircraft reliability and the operation stability of the products such as air-conditioner of using this piping system, improved product competitiveness.
Certainly; the above only is a kind of preferred implementation of the present invention; should be understood that; for those skilled in the art; under the prerequisite that does not break away from the principle of the invention; can also make some improvements and modifications, these improvements and modifications also should be considered as protection scope of the present invention.
Claims (10)
1. a compressor piping system comprises gas exhaust piping and return line, it is characterized in that, described return line has a L shaped bend loss, and described L shaped bend loss is positioned at the bottom of described return line.
2. compressor piping system according to claim 1 is characterized in that the opening direction of described L shaped bend loss is towards compressor.
3. compressor piping system according to claim 1 and 2, it is characterized in that, described gas exhaust piping downward projection forms drop shadow curve, in described drop shadow curve, the tangent line at starting point place and the tangent line of destination county and described drop shadow curve form closed curve, and the tangent line at described starting point place and the tangent line of described destination county angular range that form, that be positioned at the angle α of described closed curve inside is 70-100 °.
4. compressor piping system according to claim 3 is characterized in that, the angle of described angle α is 90 °.
5. compressor piping system according to claim 3 is characterized in that, described gas exhaust piping has a U-bend section, and described U-bend section is positioned at the bottom of described gas exhaust piping.
6. compressor piping system according to claim 1 is characterized in that, described compressor is the single cylinder rotary compressor more than 3 or 3.
7. air-conditioner, comprise compressor and air valve, and be connected gas exhaust piping and return line between described compressor and the described air valve, it is characterized in that, described return line has a L shaped bend loss, and described L shaped bend loss is positioned at the bottom of described return line.
8. air-conditioner according to claim 7 is characterized in that the opening direction of described L shaped bend loss is towards described compressor.
9. according to claim 7 or 8 described air-conditioners, it is characterized in that, described gas exhaust piping downward projection forms drop shadow curve, in described drop shadow curve, the tangent line at starting point place and the tangent line of destination county and described drop shadow curve form closed curve, and the tangent line at described starting point place and the tangent line of described destination county angular range that form, that be positioned at the angle α of described closed curve inside is 70-100 °.
10. air-conditioner according to claim 7 is characterized in that, described air valve is a four-way change-over valve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200910230173 CN102062503B (en) | 2009-11-16 | 2009-11-16 | Pipeline distributing system of compressor and air conditioner with same |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200910230173 CN102062503B (en) | 2009-11-16 | 2009-11-16 | Pipeline distributing system of compressor and air conditioner with same |
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| Publication Number | Publication Date |
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| CN102062503A true CN102062503A (en) | 2011-05-18 |
| CN102062503B CN102062503B (en) | 2012-11-07 |
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| CN 200910230173 Active CN102062503B (en) | 2009-11-16 | 2009-11-16 | Pipeline distributing system of compressor and air conditioner with same |
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Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103322627A (en) * | 2013-05-23 | 2013-09-25 | 江苏春兰制冷设备股份有限公司 | Tube of air conditioner outdoor unit |
| CN104501379A (en) * | 2014-12-19 | 2015-04-08 | 珠海格力电器股份有限公司 | Air suction pipe line, air suction structure, household appliance and dehumidifier |
| CN105205197A (en) * | 2014-06-30 | 2015-12-30 | 青岛海尔空调器有限总公司 | Vibration reduction method for blowdown pipeline of air-conditioner outdoor unit |
| CN106091330A (en) * | 2016-06-28 | 2016-11-09 | 山东中科能人工环境有限公司 | A kind of air-conditioner host equipment of novel damping noise reduction |
| CN106121965A (en) * | 2016-06-22 | 2016-11-16 | 青岛海信日立空调***有限公司 | Compressor air suction pipeline assembly and air-conditioner outdoor unit |
| CN108151378A (en) * | 2018-01-26 | 2018-06-12 | 奥克斯空调股份有限公司 | Pipeline, pipe-line system and air-conditioning |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101298953B (en) * | 2008-06-24 | 2010-09-01 | 广东美的电器股份有限公司 | Piping for air conditioner outdoor machine |
-
2009
- 2009-11-16 CN CN 200910230173 patent/CN102062503B/en active Active
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103322627A (en) * | 2013-05-23 | 2013-09-25 | 江苏春兰制冷设备股份有限公司 | Tube of air conditioner outdoor unit |
| CN105205197A (en) * | 2014-06-30 | 2015-12-30 | 青岛海尔空调器有限总公司 | Vibration reduction method for blowdown pipeline of air-conditioner outdoor unit |
| CN105205197B (en) * | 2014-06-30 | 2018-06-22 | 青岛海尔空调器有限总公司 | A kind of oscillation damping method of air-conditioner outdoor unit tonifying Qi pipeline |
| CN104501379A (en) * | 2014-12-19 | 2015-04-08 | 珠海格力电器股份有限公司 | Air suction pipe line, air suction structure, household appliance and dehumidifier |
| CN106121965A (en) * | 2016-06-22 | 2016-11-16 | 青岛海信日立空调***有限公司 | Compressor air suction pipeline assembly and air-conditioner outdoor unit |
| CN106121965B (en) * | 2016-06-22 | 2019-02-12 | 青岛海信日立空调***有限公司 | Compressor air suction pipeline component and air-conditioner outdoor unit |
| CN106091330A (en) * | 2016-06-28 | 2016-11-09 | 山东中科能人工环境有限公司 | A kind of air-conditioner host equipment of novel damping noise reduction |
| CN106091330B (en) * | 2016-06-28 | 2019-11-26 | 山东中科能人工环境有限公司 | A kind of air-conditioner host equipment of vibration and noise reducing |
| CN108151378A (en) * | 2018-01-26 | 2018-06-12 | 奥克斯空调股份有限公司 | Pipeline, pipe-line system and air-conditioning |
| CN108151378B (en) * | 2018-01-26 | 2023-08-01 | 奥克斯空调股份有限公司 | Pipeline, pipeline system and air conditioner |
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| Publication number | Publication date |
|---|---|
| CN102062503B (en) | 2012-11-07 |
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