CN102062503B

CN102062503B - Pipeline distributing system of compressor and air conditioner with same

Info

Publication number: CN102062503B
Application number: CN 200910230173
Authority: CN
Inventors: 张智春; 张守信; 陈运东; 董元伟
Original assignee: Qingdao Haier Air Conditioner Gen Corp Ltd; Haier Group Corp
Current assignee: Qingdao Haier Air Conditioner Gen Corp Ltd; Haier Group Corp
Priority date: 2009-11-16
Filing date: 2009-11-16
Publication date: 2012-11-07
Anticipated expiration: 2029-11-16
Also published as: CN102062503A

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

Compressor piping system and have the air-conditioner of this piping system

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, in the air-conditioner of 3 following power, is used widely 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 needs to adopt clay or blob of viscose as counterweight, and not only cost is high, design difficulty is 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; Said 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 adopts following technical scheme to be achieved:

A kind of compressor piping system comprises gas exhaust piping and return line, and said return line has a L shaped bend loss, and said L shaped bend loss is positioned at the bottom of said return line.

According to the present invention, the opening direction of said L shaped bend loss to increase the intensity of said return line, further reduces pipeline vibration towards compressor.

According to the present invention; For avoiding gas exhaust piping and compressor to produce resonance; Said gas exhaust piping downward projection forms drop shadow curve; In said drop shadow curve, the tangent line at starting point place and the tangent line of destination county and said drop shadow curve form closed curve, and angular range that the tangent line at said starting point place and the tangent line of said destination county form, that be positioned at the inner angle of said closed curve is 70-100 °.

Said angle optimized angle is 90 °.

According to the present invention, said gas exhaust piping has a U-bend section, and said U-bend section is positioned at the bottom of said gas exhaust piping.

According to the present invention, said 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 said compressor and the said air valve.For reducing the air-conditioner vibration, said return line has a L shaped bend loss, and said L shaped bend loss is positioned at the bottom of said return line; Said gas exhaust piping downward projection forms drop shadow curve; In said drop shadow curve; The tangent line at starting point place and the tangent line of destination county and said drop shadow curve form closed curve, and angular range that the tangent line at said starting point place and the tangent line of said destination county form, that be positioned at the inner angle of said closed curve 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; Improve 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

Below in conjunction with accompanying drawing the present invention is done further detailed explanation.

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 matees 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, in air-conditioner, is provided with power and is 3 single cylinder rotary compressor 1, and said compressor 1 is connected with fluid reservoir 2.Have exhaust outlet of compressor 11 on the top of said compressor 1, have compressor return air mouth 12 on the top of said fluid reservoir 2.Four-way change-over valve 3 as air valve also is set in the said air-conditioner; Between one of them valve port of said four-way change-over valve 3 and said exhaust outlet of compressor 11, be connected with gas exhaust piping 4; Between another valve port of said four-way change-over valve 3 and said compressor return air mouth 12, be connected with return line 5, said gas exhaust piping 4 and said return line 5 have constituted the piping system of said single cylinder rotary compressor 1.

Said embodiment avoids piping system and said single cylinder rotary compressor 1 to produce the vibration of resonating, reducing piping system as far as possible, and said return line 5 has all been carried out particular design with said gas exhaust piping 4.Be specially:

For improving the rigidity of said 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 said 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 said L shaped bend loss 51, be that L shaped depression position is towards said 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; Said embodiment is for solving said gas exhaust piping 4 and the inboard stress problem of said compressor 1 connecting place, the effectiveness in vibration suppression of the whole piping system of raising; Designing requirement to said gas exhaust piping 4 is: said gas exhaust piping 4 downward projections form the AA ' CB ' B of drop shadow curve; In the said AA ' CB ' B of drop shadow curve; The tangent line AA ' at starting point A place and the tangent line BB ' and the said AA ' CB ' B of drop shadow curve at terminal point B place form closed curve, and the tangent line AA ' at said starting point A place is 80 ° with angle tangent line BB ' formation, that be positioned at the inner angle of said closed curve at said terminal point B place.

In addition, said 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 be according to the concrete designing requirement of reality, specifically 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 said gas exhaust piping 4, the nearest inboard selected point a of 180 ° of bending of the said exhaust outlet of compressor of distance 11; On said return line 5, the nearest inboard selected point b of 180 ° of bending of the said 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 following:

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.Can know that from above-mentioned each transfer curve figure compressor operating is when 50Hz, the strain that a point and b are ordered/excitation displacement is explained 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, the abscissa express time, ordinate is represented dependent variable.From these two curve maps, can know that the time domain dependent variable that a point and b are ordered satisfies the damping property requirement all less than 1.0E-4.

According to 3 and the single cylinder rotary compressor piping system of above power of conceptual design according to the invention, its pipe arrangement pipeline is short, cost is lower, and 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 pointed out 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 improvement and retouching, these improvement and retouching also should be regarded as protection scope of the present invention.

Claims

1. a compressor piping system comprises gas exhaust piping and return line, it is characterized in that, said return line has a L shaped bend loss, and said L shaped bend loss is positioned at the bottom of said return line, and the opening direction of said L shaped bend loss is towards compressor.

2. compressor piping system according to claim 1; It is characterized in that; Said gas exhaust piping downward projection forms drop shadow curve; In said drop shadow curve, the tangent line at starting point place and the tangent line of destination county and said drop shadow curve form closed curve, and angular range that the tangent line at said starting point place and the tangent line of said destination county form, that be positioned at the inner angle of said closed curve is 70-100 °.

3. compressor piping system according to claim 2 is characterized in that, the angle of said angle is 90 °.

4. compressor piping system according to claim 2 is characterized in that, said gas exhaust piping has a U-bend section, and said U-bend section is positioned at the bottom of said gas exhaust piping.

5. compressor piping system according to claim 1 is characterized in that, said compressor is the single cylinder rotary compressor more than 3 or 3.

6. air-conditioner; Comprise compressor and air valve; And be connected gas exhaust piping and the return line between said compressor and the said air valve, it is characterized in that said return line has a L shaped bend loss; Said L shaped bend loss is positioned at the bottom of said return line, and the opening direction of said L shaped bend loss is towards said compressor.

7. air-conditioner according to claim 6; It is characterized in that; Said gas exhaust piping downward projection forms drop shadow curve; In said drop shadow curve, the tangent line at starting point place and the tangent line of destination county and said drop shadow curve form closed curve, and angular range that the tangent line at said starting point place and the tangent line of said destination county form, that be positioned at the inner angle of said closed curve is 70-100 °.

8. air-conditioner according to claim 6 is characterized in that, said air valve is a four-way change-over valve.