CN114810596A - Rotary vane compressor cylinder body and molded line design method thereof - Google Patents
Rotary vane compressor cylinder body and molded line design method thereof Download PDFInfo
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
- F04C18/344—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
- F04C18/3446—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along more than one line or surface
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
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Abstract
本公开涉及压缩机技术领域，尤其涉及一种旋叶式压缩机缸体及其型线设计方法，该缸体具有前后贯通的腔体，所述腔体中心对称设置，按照叶片转动的方向该腔体的内壁线型依次包括第一圆弧段、组合摆线段、反演型线段和第二圆弧段；其中，所述第一圆弧段和第二圆弧段为圆弧线型；所述组合摆线段为组合摆线，包括加速摆线段、运动摆线段、减速摆线段和过渡摆线段；所述反演型线段的线型通过压缩过程的压力曲线反演推导得出。本公开通过在吸气阶段采用组合摆线和过渡摆线，在保证密封段弧度的同时保证了曲线光滑，避免了凸点的产生，且本公开通过反演法推导气缸型线，可以充分延长压缩过程并改善型线特性，降低叶片在工作过程中与气缸的相互作用力，减少摩擦损耗和噪音。
The present disclosure relates to the technical field of compressors, and in particular to a rotary vane compressor cylinder block and a profile design method thereof. The cylinder block has a front and rear through cavity, and the center of the cavity is symmetrically arranged. The line shape of the inner wall of the cavity sequentially includes a first circular arc segment, a combined cycloid segment, an inversion line segment and a second circular arc segment; wherein, the first circular arc segment and the second circular arc segment are circular arc segments; The combined cycloid segment is a combined cycloid, including an acceleration cycloid segment, a motion cycloid segment, a deceleration cycloid segment and a transition cycloid segment; the line shape of the inversion type segment is derived by inversion of the pressure curve in the compression process. By adopting the combined cycloid and transition cycloid in the suction stage, the present disclosure ensures the smoothness of the curve while ensuring the radian of the sealing section, and avoids the generation of bumps, and the present disclosure derives the cylinder profile through the inversion method, which can fully extend the Compression process and improve profile characteristics, reduce the interaction force between the blade and the cylinder during operation, reduce friction loss and noise.
Description
Technical Field
The disclosure relates to the technical field of compressors, in particular to a rotary vane compressor cylinder and a molded line design method thereof.
Background
The rotary vane compressor is mainly applied to an automobile air conditioning system, suction compression is realized by the rotation of the vane in the cavity of the cylinder body, in the working process, the line type of the cavity of the cylinder body plays a crucial role, and the poor cylinder line has salient points, so that the vane generates strong rigid impact or flexible impact during working, the abrasion of the vane and the cylinder generates noise, and even the vane is emptied and generates cavity leakage, thereby affecting the working performances of the compressor, such as volumetric efficiency, refrigeration power and the like;
in the related art known in the invention, the cylinder profile of the rotary vane compressor mainly includes a simple harmonic profile, a parabolic profile, an elliptic curve, a trigonometric function curve and the like, and the curves adjust the linear characteristics by adjusting and controlling part of parameters of the curve, thereby indirectly influencing the performance of the compressor in the processes of air suction, compression and exhaust, however, the required target parameters cannot be directly and effectively obtained due to the characteristics of the curve.
The information disclosed in this background section is only for enhancement of understanding of the general background of the disclosure and should not be taken as an acknowledgement or any form of suggestion that this information forms the prior art that is known to a person skilled in the art.
Disclosure of Invention
In view of at least one of the above technical problems, the present disclosure provides a cylinder body of a vane rotary compressor and a method for designing a profile thereof, which derive a target profile of the cylinder by inversion from a pressure curve of a compression process of the compressor, so as to optimize the profile of the vane rotary compressor.
According to a first aspect of the present disclosure, a rotary vane compressor cylinder is provided, the cylinder has a cavity running through from front to back, the cavity is arranged in a central symmetry manner, and the inner wall line of the cavity sequentially includes a first arc section, a combined pendulum section, an inversion type line section and a second arc section according to the rotating direction of the vane;
the first arc section and the second arc section are of an arc line type;
the combined cycloid segment is a combined cycloid and comprises an acceleration cycloid segment, a motion cycloid segment, a deceleration cycloid segment and a transition cycloid segment;
the line type of the inversion line segment is obtained by pressure curve inversion derivation in the compression process.
In some embodiments of the present disclosure, the coordinate point of the inversion-type line segment profile is obtained by performing elementary volume difference iterative computation on a cavity pressure-rotation angle expression of a compression process.
In some embodiments of the present disclosure, a high-order polynomial smoothing process is used to smooth the coordinate intersection position of the second circular arc segment and the inversion-type line segment.
According to a second aspect of the present disclosure, there is provided the method for designing a profile of a cylinder block of a vane rotary compressor according to any one of the first aspects, comprising the steps of:
determining the sealing arc angle of the first arc segment and the second arc segment, and establishing a molded line equation of the sealing arc angle;
establishing a combined cycloid equation of a combined cycloid segment, and calculating a combined cycloid segment element volume-corner expression through an element volume calculation model;
determining the maximum primitive volume and the inspiration end angle;
setting a compression process angle and a starting exhaust angle, and combining the suction pressure and the exhaust pressure to obtain a cavity pressure-corner expression of the inversion type line segment;
obtaining a primitive volume-corner expression of an inversion type line segment through thermodynamic calculation;
obtaining the linear coordinates of the inversion line segments through element volume difference iterative computation;
and carrying out smooth transition correction on the molded line.
In some embodiments of the present disclosure, the profile equations of the first arc segment and the second arc segment are:
in the formula: rho is the polar diameter of the molded line, r is the radius of the cylinder rotor, theta is the polar angle, theta 1 Is the end angle of the arc segment at the initial end of the molded line, theta 0 The starting angle of the arc segment at the end of the molded line.
In some embodiments of the present disclosure, the combined cycloid segment has a combined cycloid equation of:
in the formula: h is 1 For maximum lift of the profile, h 2 For transition lift, k 1 And k 2 Is the coefficient of cycloid, theta 2 、θ 3 、θ 4 、θ 5 The end angles of the first to fourth cycloids are respectively.
In some embodiments of the present disclosure, the primitive volume-corner expression for the inverted line segment is:
in the formula, p 0 Is the suction pressure;
for turning the rotor at an angle of
Elementary volume of time;
for rotor to rotateThe angle is
Cell volume pressure of time; k is a polytropic index and is obtained according to the working conditions of air intake and exhaust of the working medium;
setting differential angle step length, and calculating element volume and element volume difference under different polar angles;
and setting the next calculation angle polar diameter value from the compression stage, bringing the next calculation angle polar diameter value into the elementary volume calculation model for iterative solution, and outputting the polar diameter value according to the calculation result.
The beneficial effect of this disclosure does: according to the air suction device, the combination cycloid and the transition cycloid are adopted in the air suction stage, the radian of the sealing section is guaranteed, meanwhile, the curve is smooth, and the generation of convex points is avoided. In addition, according to the method, the end angle of the compression process is set in the compression stage, the molded line of the air cylinder is deduced through an inversion method according to the theoretical pressure curve of the cavity, the compression process can be fully prolonged, the molded line characteristic is improved, the interaction force between the blade and the air cylinder in the working process is reduced, and the friction loss and the noise are reduced.
Drawings
In order to more clearly illustrate the embodiments of the present disclosure or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, it is obvious that the drawings in the following description are only some embodiments described in the present disclosure, and other drawings can be obtained by those skilled in the art without creative efforts.
FIG. 1 is a schematic structural diagram of a cylinder of a vane compressor according to an embodiment of the present disclosure;
FIG. 2 is a schematic view of a profile structure of a cylinder of a rotary vane compressor (including a rotor and a vane) according to an embodiment of the present disclosure;
FIG. 3 is a schematic view of a profile structure of a cylinder of a vane rotary compressor (including a schematic view of a rotor) according to an embodiment of the present disclosure;
FIG. 4 is a flowchart illustrating steps of a method for designing a profile of a cylinder of a vane-type compressor according to an embodiment of the present disclosure;
fig. 5 is a schematic view of a profile structure of a first arc segment and a second arc segment in an embodiment of the present disclosure;
FIG. 6 is a schematic structural diagram of a profile of a combined cycloid segment in an embodiment of the present disclosure;
FIG. 7 is a schematic view of a profile structure of an inversion profile segment in an embodiment of the present disclosure;
8-11 are differential schematic views of the cross-sectional area occupied by the blades in an embodiment of the present disclosure;
FIG. 12 is a graph of a pressure curve of a profile within a compressor cylinder versus a reference profile in an embodiment of the present disclosure.
Detailed Description
The technical solutions in the embodiments of the present disclosure will be clearly and completely described below with reference to the drawings in the embodiments of the present disclosure, and it is obvious that the described embodiments are only a part of the embodiments of the present disclosure, and not all of the embodiments.
It will be understood that when an element is referred to as being "secured to" another element, it can be directly on the other element or intervening elements may also be present. When an element is referred to as being "connected" to another element, it can be directly connected to the other element or intervening elements may also be present. The terms "vertical," "horizontal," "left," "right," and the like as used herein are for illustrative purposes only and do not represent the only embodiments.
Unless defined otherwise, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this disclosure belongs. The terminology used in the description of the disclosure herein is for the purpose of describing particular embodiments only and is not intended to be limiting of the disclosure. As used herein, the term "and/or" includes any and all combinations of one or more of the associated listed items.
The inventor of the present disclosure finds, during research, that if a pressure curve of a compression process of a compressor can be used, a target profile of a cylinder body is inversely derived, that is, a pressure curve of a compression process of a vane compressor is designed, and a cylinder profile is inversely derived, so that a vane obtains good characteristics;
for the convenience of understanding of the present disclosure, a description is first given to a vane-type compressor, such as a vane-type compressor cylinder shown in fig. 1 to 3, where the cylinder has a cavity 1 penetrating front and back, and as shown in fig. 2, the cavity 1 is arranged in a central symmetry manner, where the central symmetry means symmetry with the rotation center of a rotor as a symmetry point, and as shown in fig. 3, the inner wall of the cavity 1 includes, in a linear manner, a first arc segment 10, a combined cycloid segment 20, an inversion-type line segment 30, and a second arc segment 40 in sequence according to the rotation direction of a blade; in the embodiment of the present disclosure, please refer to fig. 1 and 2, an exhaust hole attached by a spring plate is provided on a side wall of the cylinder body, and the exhaust hole is opened when the pressure reaches a set value; at the position of the first arc segment 10 of the cylinder, there is generally an air inlet on the front bearing of the compressor, the air enters into the cavity when the blades rotate; along with the rotation of the blades, the gas entering the cavity 1 is compressed until the exhaust holes are opened to enter an exhaust preparation stage;
in the embodiment of the present disclosure, only one part of the cavity 1 with central symmetry is introduced, please refer to fig. 2 and 3, and with the counterclockwise rotation of the blade, the blade sequentially passes through four stages, namely, a first arc segment 10, a combined cycloid segment 20, an inversion type segment 30, and a second arc segment 40, and the four stages are sequentially connected to form a half-shaped line of the inner wall of the cavity 1;
as shown in fig. 3 in particular, the first arc segment 10 and the second arc segment 40 are arc-shaped; in order to maintain sealing, the sealing ring needs to be attached to the outer wall of the rotor, so that the sealing ring is in an arc shape to ensure sealing performance;
the combined cycloid segment 20 is a combined cycloid and comprises an accelerating cycloid segment 21, a moving cycloid segment 22, a decelerating cycloid segment 23 and a transition cycloid segment 24; in the embodiment of the present disclosure, the combined cycloid segment 20 is also referred to as a first to a fourth cycloid in sequence; the line shape of the inverted line segment 30 is derived by pressure curve inversion during compression.
For a detailed understanding of the inversion derivation process of the pressure curve in the embodiments of the present disclosure, the following is introduced in conjunction with the method for designing the profile of the rotary vane compressor cylinder;
the method for designing the profile of the rotary vane compressor cylinder as shown in fig. 4 comprises the following steps:
s10: determining the sealing arc angles of the first arc section 10 and the second arc section 40, and establishing a molded line equation of the sealing arc angles;
s20: establishing a combined cycloid equation of the combined cycloid segment 20, and calculating a primitive volume-rotation angle expression of the combined cycloid segment 20 through a primitive volume calculation model;
s30: determining the maximum primitive volume and the inspiration end angle;
s40: setting a compression process angle and a starting exhaust angle, and combining the suction pressure and the exhaust pressure to obtain a cavity pressure-corner expression of the inversion type line segment 30;
s50: obtaining a primitive volume-corner expression of the inversion type line segment 30 through thermodynamic calculation;
s60: obtaining the linear coordinates of the inversion type line segment 30 through element volume difference iterative computation;
s70: and carrying out smooth transition correction on the molded line.
As shown in fig. 5, since the first arc segment 10 and the second arc segment 40 in the cylinder are in the shape of arc with a radius close to the radius of the rotor, in the embodiment of the present disclosure, the profile equations of the first arc segment 10 and the second arc segment 40 are as follows:
in the formula: rho is the polar diameter of the molded line, r is the radius of the cylinder rotor, theta is the polar angle, theta 1 Is the end angle of the arc segment at the initial end of the molded line, theta 0 The starting angle of the arc segment at the end of the molded line. In the disclosed embodiment, r is 25mm, θ 1 ＝3°，θ 0 ＝174°
As shown in fig. 6, the profile equation of the inspiration process adopts a combined cycloid, which is divided into four segments, namely a first segment cycloid (acceleration segment), a second segment cycloid (motion segment), a third segment cycloid (deceleration segment), and a fourth segment cycloid (transition segment), and the profile equation thereof is:
in the formula: h is 1 For maximum lift of the profile, h 2 For transition lift, k 1 And k 2 Is the coefficient of cycloid, theta 2 、θ 3 、θ 4 、θ 5 The end angles of the first to fourth cycloids are respectively. It is to be noted here that in the formula of the embodiment of the present disclosure, θ 2 、θ 3 、θ 5 For distinguishing the range of the variable theta; furthermore, the maximum lift refers to the difference between the maximum value and the minimum value of the profile pole diameter, and the transition lift refers to the difference between the profile pole diameters at the beginning and the end of the transition, wherein the lifts are absolute values. In the embodiments of the present disclosure h 1 ＝8.55，h 2 ＝1.5，k 1 ＝10，
θ 2 ＝12°，θ 3 ＝66°，θ 4 ＝75°，θ 5 ＝42°
Wherein k is 1 、θ 1 And theta 2 Satisfies the following relation:
the corresponding velocity and acceleration expressions are:
the maximum elementary volume is calculated as V m The end angle of suction is theta 5 . In thatIn the embodiment of the disclosure, the following is calculated: v m ＝5.038ml，θ 5 ＝124°。
In the embodiment of the present disclosure, as shown in fig. 7, the compression process end angle θ is set 6 And 197 degrees, and reasonably setting a cavity pressure-corner expression by combining the suction and exhaust pressure and the compression process angle. In the embodiment of the present disclosure, the elementary volume-rotation angle expression of the inversion-type line segment 30 is obtained through thermodynamic calculation, and the process is as follows:
in the formula: p is a radical of 0 Is the suction pressure;
for turning the rotor at an angle of
Elementary volume of time;
for a rotor turning angle of
Cell volume pressure; k is a polytropic index and is obtained according to the working conditions of air intake and exhaust of the working medium.
After obtaining the primitive volume-rotation angle expression of the inversion line segment 30, in the embodiment of the present disclosure, a suitable differential angle step δ θ is set, and the value is taken to obtain the primitive volume V under different polar angles i,pre Obtaining the elementary volume difference delta V under different polar angles i,pre To more clearly express the calculation process, as shown in FIG. 8, the distance from the center of the rotor to the blade tip seal surface is represented by the radial oa 1 The radial oa represents the distance from the sealing end face of another adjacent blade to the center of the rotor in the rotating direction of the blade 2 The intersection points of the blades and the rotor are b 1 And b 2 The calculation process is as follows:
from sagittal axis oa 1 Radial oa of the vector 2 And the difference of the sectional area of the area enclosed by the inner wall of the cylinder:
in the formula: rho f,i The ith profile pole diameter at the front blade; rho f,i-1 The i-1 molded line pole diameter at the front blade is obtained; rho b,i The ith profile pole diameter of the blade is located; rho b,i-1 The i-1 molded line polar diameter at the rear blade is obtained; delta theta f,i Is the ith polar angle difference at the leading blade; delta theta b,i Is the ith polar angle difference at the leading blade;
referring to fig. 8, in the embodiment of the present disclosure, the radial oa 1 And oa 2 The intersection points with the rotor are respectively c 1 And c 2 As shown in fig. 9, the difference in cross-sectional area of the region enclosed by the radius oc1, the radius oc2, and the rotor outer wall:
as shown in fig. 10, the difference in cross-sectional area of the region surrounded by the line segments a2b2, a2c2, and the circular arc b2c 2:
in the formula: e is the eccentricity of the rotor;
the extension length of the ith blade of the rear blade is the extension length of the ith blade of the rear blade;
the extension length of the ith-1 blade of the rear blade is equal to the extension length of the second blade;
with reference to fig. 10, the difference in cross-sectional area of the region enclosed by the line segments a1b1, a1c1 and the arc b1c1 is:
in the formula:
the extension length of the ith blade of the front blade;
the extension length of the i-1 th blade of the front blade;
on the basis of the above calculation formula, as shown in fig. 11, the difference in the sectional area occupied by the blade is:
thus, the cell volume difference at any position can be expressed as:
in the formula: b is the cylinder height, in the disclosed embodiment, 19 mm.
From the compression stage, let the polar diameter value of the next calculation angle be ρ f,temp Substituting into the elementary volume calculation model to solve the delta V iteratively temp,i The allowable error of iteration is delta V error . If the decision formula | delta V is satisfied temp,i -δV pre,i |＜δV error Then, the cell volume difference δ V at this time is described temp,i Volume difference delta V from target cell i,pre Is less than the allowable error. At this time, the value of the polar diameter ρ f,temp Meet the requirement of solution, and apply rho f,temp Is given as rho f,i Output polar diameter value rho f,i (ii) a Further, here, the value of the pole diameter ρ f,i The decision formula is used to define the maximum allowable error of the solution, and the smaller the error value, the closer the value of the solution is to the true value. The polar diameter values here correspond to coordinate points on the inversion profile 30;
in addition, in the embodiment of the present disclosure, at the joint position of the line coordinates of the second circular arc segment 40 and the inverted line segment 30, a high-order polynomial is used for smoothing.
In the embodiment of the disclosure, by adopting the combined cycloid and the transition cycloid at the air suction stage, the radian of the sealing section is ensured, the curve is ensured to be smooth, and the generation of convex points is avoided. In addition, according to the method, the compression process ending angle is set in the compression stage, the molded line of the air cylinder is deduced through an inversion method according to the theoretical pressure curve of the accommodating cavity, the compression process can be fully prolonged, the molded line characteristic is improved, the interaction force between the blade and the air cylinder in the working process is reduced, and the friction loss and the noise are reduced.
As shown in table 1 below, the characteristics of the cylinder line of the rotary vane compressor in the embodiment of the present disclosure are compared with the reference line:
as shown in table 1 and fig. 12, the molded lines of the cylinder body of the vane-type compressor of the present disclosure can shorten the exhaust process, prolong the compression process, sufficiently reduce the interaction force between the blades of the compression process and the cylinder during the operation, reduce the friction loss and noise, and simultaneously improve the maximum elementary volume of the vane-type compressor and improve the operation performance.
It will be understood by those skilled in the art that the present disclosure is not limited to the embodiments described above, which are presented solely for purposes of illustrating the principles of the disclosure, and that various changes and modifications may be made to the disclosure without departing from the spirit and scope of the disclosure, which is intended to be covered by the claims. The scope of the disclosure is defined by the appended claims and equivalents thereof.
Claims (10)
1. A rotary vane compressor cylinder body is characterized in that the cylinder body is provided with a cavity which is through from front to back, the cavity is arranged in a centrosymmetric manner, and the inner wall line of the cavity sequentially comprises a first arc section, a combined pendulum line section, an inversion line section and a second arc section according to the rotating direction of a vane;
the first arc section and the second arc section are of an arc line type;
the combined cycloid segment is a combined cycloid and comprises an acceleration cycloid segment, a motion cycloid segment, a deceleration cycloid segment and a transition cycloid segment;
the line type of the inversion line segment is obtained by pressure curve inversion derivation in the compression process.
2. The cylinder block of a rotary vane compressor of claim 1 wherein the profile equations of the first and second arc segments are:
in the formula: rho is the polar diameter of the molded line, r is the radius of the cylinder rotor, theta is the polar angle, theta 1 Is the ending angle of the arc segment at the initial end of the molded line, theta 0 The starting angle of the arc segment at the end of the molded line.
3. The cylinder block of a rotary vane compressor as claimed in claim 1 wherein the profile equation of the combined cycloid segment is:
in the formula: h is 1 For maximum lift of the profile, h 2 For transition lift, k 1 And k 2 Is the coefficient of cycloid, theta 2 、θ 3 、θ 4 、θ 5 End angles of first to fourth cycloids, respectively, where k 1 、θ 1 And theta 2 Satisfies the following relation:
4. the rotary vane compressor cylinder body according to claim 1, wherein the coordinate point of the inversion type line segment profile is obtained by performing elementary volume difference iterative calculation on a cavity pressure-rotation angle expression in a compression process.
5. The cylinder block of a rotary vane compressor as claimed in claim 4 wherein the pressure-angle expression of the cavity is:
in the formula: p is a radical of 0 Is the suction pressure;
for turning the rotor at an angle of
Elementary volume of time;
for turning the rotor at an angle of
Cell volume pressure of time; k is a polytropic index obtained according to the working conditions of air intake and exhaust of the working medium.
6. The cylinder block of a rotary vane compressor according to claim 4, wherein a high-order polynomial smoothing is applied to a coordinate connection position of the second circular arc segment and the inversion-type line segment.
7. A method for designing a profile of a rotary vane compressor cylinder according to any one of claims 1 to 6, comprising the steps of:
determining the sealing arc angle of the first arc segment and the second arc segment, and establishing a molded line equation of the sealing arc angle;
establishing a combined cycloid equation of a combined cycloid segment, and calculating a combined cycloid segment element volume-corner expression through an element volume calculation model;
determining the maximum primitive volume and the inspiration end angle;
setting a compression process angle and a starting exhaust angle, and combining the suction pressure and the exhaust pressure to obtain a cavity pressure-corner expression of the inversion type line segment;
obtaining a primitive volume-corner expression of an inversion type line segment through thermodynamic calculation;
obtaining the linear coordinates of the inversion line segments through element volume difference iterative computation;
and carrying out smooth transition correction on the molded line.
8. The mold line design method of claim 7, wherein the mold line equations of the first and second arc segments are:
in the formula: rho is the polar diameter of the molded line, r is the radius of the cylinder rotor, theta is the polar angle, theta 1 Is the end angle of the arc segment at the initial end of the molded line, theta 0 The starting angle of the arc segment at the end of the molded line.
9. The method of profile design according to claim 7, wherein the combined cycloid curve equation of the combined cycloid curve segment is:
in the formula: h is 1 For maximum lift of the profile, h 2 For transition lift, k 1 And k 2 Is the coefficient of cycloid, theta 2 、θ 3 、θ 4 、θ 5 The end angles of the first to fourth cycloids are respectively.
10. The profile design method of claim 7, wherein the primitive volume-corner expression for the inverted profile segment is:
in the formula, p 0 Is the suction pressure;
for turning the rotor at an angle of
Elementary volume of time;
for turning the rotor at an angle of
Cell volume pressure of time; k is a polytropic index and is obtained according to the working conditions of air intake and exhaust of the working medium;
setting differential angle step length, and calculating element volume and element volume difference under different polar angles;
and setting the next calculation angle polar diameter value from the compression stage, bringing the next calculation angle polar diameter value into the elementary volume calculation model for iterative solution, and outputting the polar diameter value according to the calculation result.
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Application publication date: 20220729 |