CN109931262B - Non-circular gear driven synchronous rotary compressor - Google Patents
Non-circular gear driven synchronous rotary compressor Download PDFInfo
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- CN109931262B CN109931262B CN201910282616.5A CN201910282616A CN109931262B CN 109931262 B CN109931262 B CN 109931262B CN 201910282616 A CN201910282616 A CN 201910282616A CN 109931262 B CN109931262 B CN 109931262B
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Abstract
The invention discloses a synchronous rotary compressor driven by a non-circular gear. The invention comprises a main transmission shaft, wherein two ends of the main transmission shaft are supported on an outer box body through bearings, a box shell of a compressor is arranged in the outer box body, an air cylinder is arranged in the box shell of the compressor, a rotor is arranged in the air cylinder, and two ends of an air cylinder shaft and two ends of a rotor shaft are respectively supported on the outer box body and the box shell of the compressor through bearings; the cylinder shaft and the rotor shaft are not on the same straight line; the main transmission shaft is provided with a circular gear and a non-circular gear on two sides of the shell of the compressor respectively, the non-circular gear and the conjugate non-circular gear are meshed to drive the air cylinder, the circular gear and the conjugate circular gear are meshed to drive the rotor, or the non-circular gear and the conjugate non-circular gear are meshed to drive the rotor, the circular gear and the conjugate circular gear are meshed to drive the air cylinder, the sliding sheet is hinged on the air cylinder and inserted into a sliding sheet groove on the rotor. The invention solves the problems of large slide blade load, small exhaust volume and certain pulsation of outlet pressure of the synchronous rotary compressor.
Description
The technical field is as follows:
the invention relates to the field of air compressors, in particular to a synchronous rotary compressor driven by a non-circular gear.
Background art:
the sliding vane compressor has the advantages of simple structure, few parts, convenience in maintenance and high volume efficiency, and is widely applied to many fields. Traditional gleitbretter compressor, the cylinder is static, and the relative speed between gleitbretter and rotor and the cylinder is big, causes serious frictional wear between gleitbretter and the cylinder, between rotor and the cylinder, and frictional wear has not only reduced the life of compressor, has also reduced the energy utilization of compressor. The synchronous rotary compressor, also called as rotary cylinder sliding vane compressor, overcomes the defect of the traditional sliding vane compressor. In the synchronous rotary compressor, a slip sheet is simultaneously connected with a rotor and a cylinder, and the rotor and the cylinder realize synchronous rotation under the action of the slip sheet. Therefore, the relative speed between the rotor and the cylinder is greatly reduced, and the friction and the abrasion between the rotor and the cylinder are reduced. However, in the synchronous rotary compressor, the sliding vane is required to bear not only the pressure difference between the suction chamber and the discharge chamber but also the power transmission, so that the sliding vane is required to bear a larger load, which results in that the frictional wear on the sliding vane is still high. In order to avoid further deterioration of the force applied to the sliding vane, in the prior synchronous rotary compressor, the eccentricity between the rotor and the cylinder is generally controlled below 10mm, and the exhaust volume is limited. In addition, the exhaust state is only a small part of the time in one rotation of the rotor, so that certain pulsation exists in the outlet pressure.
Disclosure of Invention
The invention aims to provide a non-circular gear driven synchronous rotary compressor aiming at the problems of large slide sheet load, small exhaust volume and certain pulsation of outlet pressure of the existing synchronous rotary compressor. In the invention, the synchronous rotation of the rotor and the cylinder is realized by external non-circular gear transmission. Therefore, the sliding vane is only used for separating the suction cavity and the exhaust cavity and is not used for synchronous driving any more, the load of the sliding vane and the friction wear caused by the load are reduced, and the service life of the sliding vane and the energy utilization rate of the compressor are improved. The reduction in vane load allows for the use of a greater eccentricity, increasing the discharge capacity of the compressor. In addition, the external non-circular gear transmission easily realizes the operation of a plurality of compressors according to a given phase difference, so that the air displacement of a compressor system can be further improved at a low rotating speed, and the pulsation of outlet pressure can be reduced.
The above purpose is realized by the following technical scheme:
a non-circular gear driven synchronous rotary compressor comprises a main transmission shaft, wherein two ends of the main transmission shaft are supported on an outer box body through bearings, a box shell of the compressor is arranged in the outer box body, an air cylinder is arranged in the box shell of the compressor, a rotor is arranged in the air cylinder, and two ends of an air cylinder shaft and two ends of a rotor shaft are respectively supported on the outer box body and the box shell of the compressor through bearings; the cylinder shaft and the rotor shaft are not on the same straight line; the main transmission shaft is provided with a circular gear and a non-circular gear respectively positioned at two sides of the shell of the compressor, when the non-circular gear is meshed with a conjugate non-circular gear to drive a cylinder and the circular gear is meshed with a conjugate circular gear to drive a rotor, the conjugate non-circular gear is arranged on a cylinder shaft, and the conjugate circular gear is arranged on a rotor shaft; when the non-circular gear and the conjugate non-circular gear are meshed to drive the rotor and the circular gear and the conjugate circular gear are meshed to drive the cylinder, the conjugate non-circular gear is arranged on a rotor shaft, and the conjugate circular gear is arranged on a cylinder shaft; in the compressor shell, the cylinder runs with the cylinder shaft, the rotor runs with the rotor shaft, the sliding sheet is hinged on the cylinder and inserted into the sliding sheet groove on the rotor.
The average transmission ratio of the cylinder and the rotor of the non-circular gear driven synchronous rotary compressor is 1: 1. Correspondingly, the average transmission ratio of the non-circular gear to the conjugate non-circular gear is equal to the transmission ratio of the circular gear to the conjugate circular gear;
the rotation angle relation of the rotor and the cylinder is as follows:
wherein beta is a rotor corner, theta is a cylinder corner, the starting positions of beta and theta are in the direction from the cylinder rotation center to the rotor rotation center, R is the distance between the center of the cylinder and the hinged rotation center of the sliding sheet, and e is the eccentric distance between the rotor and the cylinder;
the transmission ratio of the rotor to the cylinder is further obtained from equation 1:
the transmission ratio of the circular gear to the conjugate circular gear is recorded as iC. When the circular gear and the conjugate circular gear are adopted to drive the rotor and the non-circular gear and the conjugate non-circular gear drive the cylinder, the transmission ratio of the non-circular gear to the conjugate non-circular gear is iNC＝i×iC(ii) a When the circular gear and the conjugate circular gear are adopted to drive the cylinder, the non-circular gear and the conjugate non-circular gear drive the rotor, the transmission ratio of the non-circular gear to the conjugate non-circular gear is iNC＝iC/i；
The pitch curve expression of the non-circular gear and the conjugate non-circular gear is as follows:
wherein the content of the first and second substances,for non-circular gears at polar angles ofWhen the utility model is moved in the radial direction,
for conjugate non-circular gears at polar angles ofWhen the utility model is moved in the radial direction,
all in oneCorresponding, i.e. non-circular gear wheel turning over
Time-conjugate non-circular gear wheelaNCThe center distance between the non-circular gear and the conjugate non-circular gear.
The main transmission shaft drives one compressor through gear transmission or simultaneously drives a plurality of synchronous rotary compressors with the same parameters.
When the main transmission shaft simultaneously drives even number of synchronous rotary compressors with the same parameters, the compressors are uniformly distributed around the main transmission shaft, the phase difference between adjacent compressors is 360 degrees/n, and n is the number of the compressors.
Has the advantages that:
compared with the prior art, the invention adopts the non-circular gear mechanism to realize the synchronous rotation of the rotor and the air cylinder in the synchronous rotary compressor, reduces the load of the sliding vane and the friction wear caused by the load, and improves the service life of the sliding vane and the energy utilization rate of the compressor. The reduction in vane load allows for the use of a greater eccentricity, increasing the discharge capacity of the compressor. In addition, the external non-circular gear transmission easily realizes the operation of a plurality of compressors according to a given phase difference, thereby not only further improving the displacement of the compressor system, but also reducing the pulsation of outlet pressure.
Drawings
FIG. 1 is a schematic diagram of the mechanism of the present invention;
FIG. 2 is a schematic diagram of a structural cross-sectional view of two sets of cylinder rotor sets and an initial position of a hinged sliding vane in the present invention;
FIG. 3 is a diagram of an example of pitch curves of a non-circular gear and a conjugate non-circular gear according to the present invention.
In the drawings, each reference numeral represents: the compressor comprises a shell, an outer box, a non-circular gear, a cylinder shaft, a rotor, a cylinder, a compressor box shell, a rotor shaft, a non-circular gear, a cylinder shaft, a compressor box shell, a rotor shaft, a non-circular gear, a main transmission shaft, a coupler, a motor and a hinged.
Detailed Description
The invention is further described with reference to the following figures and examples.
It should be noted that, based on the technical solution of the present invention, the rotor may be driven by engaging a circular gear, the cylinder may be driven by engaging a non-circular gear, or the rotor may be driven by engaging a non-circular gear, and the cylinder may be driven by engaging a circular gear. In the present embodiment, a non-circular gear engagement driving cylinder is selected, but this is not intended to limit the scope of the present invention. In addition, the main transmission shaft can drive one synchronous rotary compressor through gear transmission, and can also drive a plurality of synchronous rotary compressors with the same parameter at the same time. When a plurality of synchronous rotary compressors are driven, the compressors are uniformly distributed around a main transmission shaft, the phase difference between adjacent compressors is 360 degrees/n, and n is the number of the compressors. In the present embodiment and the drawings, two synchronous rotary compressors having a phase difference of 180 ° are simultaneously driven, but this is not intended to limit the scope of the present invention.
As shown in fig. 1, the non-circular gear driven synchronous rotary compressor includes a driving part and a rotary compressor part.
The driving component comprises an outer box 1, a non-circular gear 2, a conjugate non-circular gear 3, a circular gear 10, a conjugate circular gear 9, a cylinder shaft 4, a rotor shaft 8 and a main transmission shaft 11. The motor 13 is connected with the main transmission shaft 11 through a coupler 12, and two ends of the main transmission shaft 11 are supported on the outer box body 1 through bearings. Both ends of the cylinder shaft 4 and the rotor shaft 8 are supported on the outer casing 1 and the casing 7 of the compressor, respectively, through bearings. The cylinder shaft 4 and the rotor shaft 8 are not collinear. The circular gear 10 and the conjugate circular gear 9 are respectively fixedly arranged on the main transmission shaft 11 and the rotor shaft 8, and the circular gear 10 is meshed with the conjugate circular gear 9. The non-circular gear 2 and the conjugate non-circular gear 3 are respectively and fixedly arranged on the main transmission shaft 11 and the cylinder shaft 4, and the non-circular gear 2 is meshed with the conjugate non-circular gear 3. As schematically shown in fig. 1, the number of the non-circular conjugate gears, the cylinder shafts, and the rotor shafts is equal to the number of the compressors, and for the sake of brevity of description, in the following description, the non-circular conjugate gears 3 replace all the non-circular conjugate gears symmetrically arranged, and the rest are similar.
As shown in fig. 2, in the rotary compressor, the cylinder 6 operates with the cylinder shaft 4, and the rotor 5 operates with the rotor shaft 8. The sliding piece 14 is hinged on the cylinder 6 and inserted into the sliding piece groove on the rotor 5.
The motor 13 transmits power to the circular gear 10 and the non-circular gear 2 through the coupler 12 and the main transmission shaft 11. The circular gear 10 is meshed with the conjugate circular gear 9, the non-circular gear 2 is meshed with the conjugate non-circular gear 3, the conjugate circular gear 9 transmits power to the rotor 5 through the rotor shaft 8, and the conjugate non-circular gear 3 transmits power to the air cylinder 6 through the air cylinder shaft 4. Synchronous revolution of the rotor 5 and the cylinder 6 is realized.
As shown in fig. 2, parameters and structures of the cylinder 6, the rotor 5 and the hinged sliding vane 14 in the two rotary compressors are completely consistent, the two compressors are symmetrically arranged by taking the main transmission shaft 11 as a center, and the phase difference between the two compressors is 180 degrees, so that the two compressors alternately exhaust, the exhaust volume of the compressor system is improved, and the pulsation of outlet pressure is reduced.
The average gear ratio of the cylinder 6 to the rotor 5 is 1: 1. Accordingly, the average gear ratio of the non-circular gear 2 to the conjugated non-circular gear 3 is equal to the gear ratio of the circular gear 10 to the conjugated circular gear 9.
The rotation angle relationship between the rotor 5 and the cylinder 6 is as follows:
wherein, beta is the rotor corner, theta is the cylinder corner, is beta and theta's initial position from cylinder centre of rotation to rotor centre of rotation direction, and R is the distance of cylinder centre of a circle and the articulated centre of rotation of gleitbretter, and the value is 80mm, and e is the eccentricity of rotor and cylinder, and the value is 10 mm. The transmission ratio of the rotor 5 to the cylinder 6 is further obtained from equation 1:
for convenience, the transmission ratio i of the circular gear 10 to the conjugate circular gear 9 is taken hereC1, the transmission ratio i of the non-circular gear 2 to the conjugate non-circular gear 3NC＝i。
The center distance b between the circular gear 10 and the conjugate circular gear 9 is 110 mm. The non-circular gear 2 and the conjugate non-circular gear 3 have a center distance a in consideration of the eccentricity between the rotor and the cylinderNCB + e 120 mm. The pitch curve expression of the non-circular gear 2 and the conjugate non-circular gear 3 is as follows:
wherein the content of the first and second substances,
for non-circular gears 2 at polar angles ofTime-direction radial;
for conjugate non-circular gears 3 in the same plane
Corresponding polar angleThe radial direction is formed. The conjugate non-circular gear 3 and the air cylinder are fixedly connected on the air cylinder shaft 4, so that
In the present embodiment, the gear ratio of the circular gear 10 to the conjugate circular gear 9 is 1, and therefore
Is numerically equal to beta, such that
And
the correspondence relationship therebetween can be obtained by equation 1. Fig. 3 shows the pitch curve of the non-circular gear 2 and the conjugate non-circular gear 3.
The foregoing shows and describes the general principles and features of the present invention, together with the advantages thereof. It will be understood by those skilled in the art that the present invention is not limited to the embodiments described above, which are described in the specification and illustrated only to illustrate the principle of the present invention, but that various changes and modifications may be made therein without departing from the spirit and scope of the present invention, which fall within the scope of the invention as claimed. The scope of the invention is defined by the appended claims and equivalents thereof.
Claims (4)
1. A non-circular gear driven synchronous rotary compressor comprises a main transmission shaft, wherein two ends of the main transmission shaft are supported on an outer box body through bearings, a box shell of the compressor is arranged in the outer box body, an air cylinder is arranged in the box shell of the compressor, a rotor is arranged in the air cylinder, and two ends of an air cylinder shaft and two ends of a rotor shaft are respectively supported on the outer box body and the box shell of the compressor through bearings; the method is characterized in that:
the cylinder shaft and the rotor shaft are not on the same straight line; the main transmission shaft is provided with a circular gear and a non-circular gear respectively positioned at two sides of the shell of the compressor, when the non-circular gear is meshed with a conjugate non-circular gear to drive a cylinder and the circular gear is meshed with a conjugate circular gear to drive a rotor, the conjugate non-circular gear is arranged on a cylinder shaft, and the conjugate circular gear is arranged on a rotor shaft; when the non-circular gear and the conjugate non-circular gear are meshed to drive the rotor and the circular gear and the conjugate circular gear are meshed to drive the cylinder, the conjugate non-circular gear is arranged on a rotor shaft, and the conjugate circular gear is arranged on a cylinder shaft; in the compressor shell, the cylinder runs with the cylinder shaft, the rotor runs with the rotor shaft, the sliding sheet is hinged on the cylinder and inserted into the sliding sheet groove on the rotor.
2. The non-circular gear driven synchronous rotary compressor of claim 1 wherein the average transmission ratio of the cylinder to the rotor is 1:1, and accordingly the average transmission ratio of the non-circular gear to the conjugate non-circular gear is equal to the transmission ratio of the circular gear to the conjugate circular gear;
the rotation angle relation of the rotor and the cylinder is as follows:
wherein beta is a rotor corner, theta is a cylinder corner, the starting positions of beta and theta are in the direction from the cylinder rotation center to the rotor rotation center, R is the distance between the center of the cylinder and the hinged rotation center of the sliding sheet, and e is the eccentric distance between the rotor and the cylinder;
the transmission ratio of the rotor to the cylinder is further obtained from equation 1:
the transmission ratio of the circular gear to the conjugate circular gear is recorded as iCWhen the circular gear and the conjugate circular gear are adopted to drive the rotor, and the non-circular gear and the conjugate non-circular gear drive the cylinderThe transmission ratio of the non-circular gear to the conjugate non-circular gear is iNC＝i×iC(ii) a When the circular gear and the conjugate circular gear are adopted to drive the cylinder, the non-circular gear and the conjugate non-circular gear drive the rotor, the transmission ratio of the non-circular gear to the conjugate non-circular gear is iNC＝iC/i；
The pitch curve expression of the non-circular gear and the conjugate non-circular gear is as follows:
wherein the content of the first and second substances,
for non-circular gears at polar angles of
When the utility model is moved in the radial direction,
for conjugate non-circular gears at polar angles ofWhen the utility model is moved in the radial direction,all in one
Corresponding, i.e. non-circular gear wheel turning over
Time-conjugate non-circular gear wheel
aNCThe center distance between the non-circular gear and the conjugate non-circular gear.
3. Non-circular gear driven synchronous rotary compressor according to claim 1, wherein the main drive shaft drives one compressor or simultaneously drives a plurality of co-parameter synchronous rotary compressors through gear transmission.
4. The non-circular gear driven synchronous rotary compressor of claim 1, wherein when the main transmission shaft drives a plurality of synchronous rotary compressors of the same parameter at the same time, the compressors are uniformly distributed around the main transmission shaft, the phase difference between adjacent compressors is 360 °/n, and n is the number of compressors.
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| CN111396312B (en) * | 2020-03-11 | 2021-08-20 | 东南大学 | Synchronous rotary compressor adopting external drive |
| CN112983807B (en) * | 2021-04-19 | 2023-04-07 | 浙江水利水电学院 | Double-cavity differential pump driven by conjugate phase-variable non-circular gears and design method |
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| US10309222B2 (en) * | 2015-11-05 | 2019-06-04 | Pars Maina Sanayi Ve Ticaret Limited Sirketi | Revolving outer body rotary vane compressor or expander |
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| JPS50145915A (en) * | 1974-04-23 | 1975-11-22 | ||
| CN1267794A (en) * | 2000-04-28 | 2000-09-27 | 李辛沫 | Closed rotating compressor |
| CN200964949Y (en) * | 2006-09-22 | 2007-10-24 | 西安交通大学 | Synchronous turning type compressor driving device |
| CN204610274U (en) * | 2015-04-28 | 2015-09-02 | 大丰丰泰流体机械科技有限公司 | A kind of abreast-type synchronous revolving mixing pump |
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