CN201221468Y

CN201221468Y - Screw compressor rotor

Info

Publication number: CN201221468Y
Application number: CNU2008201209813U
Authority: CN
Inventors: 董端兵
Original assignee: NINGBO XINDA SCREW COMPRESSOR CO Ltd
Current assignee: NINGBO XINDA SCREW COMPRESSOR CO Ltd
Priority date: 2008-07-07
Filing date: 2008-07-07
Publication date: 2009-04-15
Anticipated expiration: 2018-07-07

Abstract

The utility model discloses a helical-lobe compressor rotor, comprising a female rotor (2) and a male rotor (1) engaged with each other. The tooth number ratio of the female rotor (2) and the male rotor (1) is 6:5; the tooth forms of the male rotor (1) are successively circular envelope curve FD, circular arc DA1, circular envelope curve A1H, elliptical envelope curve HJ and circular envelope curve JM; the tooth forms of the female rotors (2) are successively circular arc GB, circular envelope curve BA2, circular arc A2C, ellipse CE and circular arc EK; and the circular center O of the circular arc A2C is not located on the node. When the structure is adopted, the engagement is more stable, i.e. the female rotor and the male rotor engage and disengage slowly; thereby, the combination properties of the host machine is improved and the noise during engagement is lowered.

Description

Rotor of helical lobe compressor

Technical field

The utility model relates to Machine Design and manufacture field, specifically is a kind of rotor of helical lobe compressor.

Background technique

In the at present domestic air compressor industry, helical-lobe compressor is with in the distinct advantages aspect the combination property, and the proportion in the market share is increasing.The a large amount of manpower and materials of each big numerous and confused input of compressor producer are carried out the development of screw air compressor, core component as helical-lobe compressor, head, it is the emphasis of research and development always, and the component of most critical are screw rotors among the head, its molded lines is the key point of its main frame combination property of decision, and developing efficiently, screw molded lines is the striving direction of each big producer always.In the main frame molded lines design of existing helical-lobe compressor, for molded lines constitutes simple, common male rotor tooth top transition position therein, design has pin tooth circular arc, promptly the home position of this circular arc is positioned at the node place of pitch circle, and then its corresponding female rotor arc envelope line also is a pin tooth circular arc, causes like this when the negative and positive rotor operation, can produce instantaneous engagement and disengagement at this segment type line place, therefore theoretic working pressure angle is for a bit.And this is for the higher helical lobe compressor host of working pressure, can be because long molded lines produce bigger pneumatic noise at the critical place of high low pressure because of instantaneous engagement and disengagement, thus influence the combination property of main frame.

The model utility content

Technical problem to be solved in the utility model is, overcomes above the deficiencies in the prior art, provides that a kind of noise is low, the good comprehensive properties rotor of helical lobe compressor.

For solving the problems of the technologies described above, the utility model provides a kind of rotor of helical lobe compressor, comprise intermeshing female rotor and male rotor, the gear ratio of negative and positive rotor is 6: 5, the profile of tooth composition of described male rotor is followed successively by arc envelope line FD, circular arc DA1, arc envelope line A1H, oval envelope HJ, arc envelope line JM, the profile of tooth composition of described female rotor is followed successively by circular arc GB, arc envelope line BA2, circular arc A2C, oval CE, circular arc EK, and the center of circle O of the circular arc A2C section on the described female rotor is not on the node of pitch circle.

After adopting above structure, because the center of circle O of the circular arc A2C section of female rotor is not or not the node place of pitch circle, it promptly not pin tooth circular arc in the past, its corresponding male rotor arc envelope line A1H section is instantaneous engagement no longer just with the line of contact of its generation like this, and promptly working pressure angle no longer is a bit, but an angular range, so just make that engagement is more steady, be that the negative and positive rotor is that slowly engagement is slowly thrown off, therefore help the raising of main frame combination property, and the noise during engagement is low.

As improvement, the Pitch radius R1j=0.35D0 of described male rotor, the Pitch radius R2j=0.42D0 of described female rotor, its negative and positive centre of rotor is apart from A=0.77D0, and wherein, the D0 in the formula is a nominal diameter.The tooth depth R=0.2D0 of described male rotor, the radius R 3=0.03D0 of described male rotor circular arc DA1 section; The radius R 4=0.012D0 of described female rotor circular arc GB section, the radius R 5=0.18D0 of circular arc A2C section, the radius R 6=0.43D0 of circular arc EK section.After adopting this structure, make the engagement of negative and positive rotor more steady, more can improve the combination property of main frame, especially the less radius chosen of male rotor tooth top circular arc DA1 section, make that this section circular arc can be more near housing with the line of contact summit of the arc envelope line generation of its female rotor correspondence, make that the leakage triangle area is littler, thereby reduce internal leakage, improve the volumetric efficiency of main frame.

Description of drawings

Shown in Figure 1 is the meshing engagement structure schematic representation of the utility model rotor of helical lobe compressor;

Shown in Figure 2 is the mate enlarged diagram of the utility model rotor of helical lobe compressor.

Wherein, 1, male rotor; 2, female rotor; FD, arc envelope line; DA1, circular arc; A1H, arc envelope line; HJ, oval envelope; JM, arc envelope line; GB, circular arc; BA2, arc envelope line; A2C, circular arc; CE, ellipse; EK, circular arc; R1j, male rotor Pitch radius; R2j, female rotor Pitch radius; A, negative and positive rotor centre distance; The tooth depth of R, male rotor; The radius of R3, circular arc DA1 section; The radius of R4, circular arc GB section; The radius of R5, circular arc A2C section; The radius of R6, circular arc EK section; O, node; D0, nominal diameter.

Embodiment

Below in conjunction with the drawings and specific embodiments the utility model is done explanation in further detail.

By Fig. 1, the meshing engagement structure schematic representation of the utility model rotor of helical lobe compressor shown in Figure 2 as can be known, this rotor of helical lobe compressor, comprise intermeshing female rotor 2 and male rotor 1, the gear ratio of female rotor 2 and male rotor 1 is 6: 5, the profile of tooth composition of described male rotor 1 is followed successively by arc envelope line FD, circular arc DA1, arc envelope line A1H, oval envelope HJ, arc envelope line JM, the profile of tooth composition of described female rotor 2 is followed successively by circular arc GB, arc envelope line BA2, circular arc A2C, oval CE, circular arc EK, the center of circle O of the circular arc A2C section on the described female rotor is not on the node of pitch circle.

The Pitch radius R1j=0.35D0 of described male rotor 1, the Pitch radius R2j=0.42D0 of described female rotor 2, its negative and positive centre of rotor is apart from A=0.77D0, and wherein, the D0 in the formula is a nominal diameter.

The tooth depth R=0.2D0 of described male rotor 1, the radius R 3=0.03D0 of described male rotor 1 circular arc DA1 section; The radius R 4=0.012D0 of described female rotor 2 circular arc GB sections, the radius R 5=0.18D0 of circular arc A2C section, the radius R 6=0.43D0 of circular arc EK section.

When the negative and positive rotor meshes, at first be that male rotor 1 arc envelope line JM section is introduced into engagement with female rotor 2 circular arc EK sections; Then be that male rotor 1 oval envelope HJ section enters engagement with female rotor 2 oval CE sections, meanwhile, male rotor 1 circular arc DA1 section enters engagement with female rotor 2 arc envelope line BA2 sections; The arc envelope line FD section that is male rotor 1 then enters engagement with female rotor 2 circular arc GB sections, and meanwhile, male rotor 1 arc envelope line A1H section enters engagement with female rotor 2 circular arc A2C sections.So just finished the engagement of a pair of negative and positive rotor tooth.After a pair of tooth has been finished engagement, enter down the engagement circulation of a pair of tooth, the negative and positive rotor circulates by such engagement and carries out work.

Claims

1, a kind of rotor of helical lobe compressor, comprise intermeshing female rotor (2) and male rotor (1), the gear ratio of negative and positive rotor (2,1) is 6: 5, it is characterized in that: the profile of tooth composition of described male rotor (1) is followed successively by arc envelope line FD, circular arc DA1, arc envelope line A1H, oval envelope HJ, arc envelope line JM, the profile of tooth composition of described female rotor (2) is followed successively by circular arc GB, arc envelope line BA2, circular arc A2C, oval CE, circular arc EK, and the center of circle O of the circular arc A2C section on the described female rotor (2) is not on the node of pitch circle.

2, rotor of helical lobe compressor according to claim 1, it is characterized in that: the Pitch radius R1j=0.35D0 of described male rotor (1), the Pitch radius R2j=0.42D0 of described female rotor (2), its negative and positive centre of rotor is apart from A=0.77D0, wherein, the D0 in the formula is a nominal diameter.

3, rotor of helical lobe compressor according to claim 1 is characterized in that: the tooth depth R=0.2D0 of described male rotor (1), the radius R 3=0.03D0 of described male rotor (1) circular arc DA1 section; The radius R 4=0.012D0 of described female rotor (2) circular arc GB section, the radius R 5=0.18D0 of circular arc A2C section, the radius R 6=0.43D0 of circular arc EK section.