CN112815070A - Fixed-point conjugated 3-twisted-blade volume rotor pair and power bevel gear pair - Google Patents

Fixed-point conjugated 3-twisted-blade volume rotor pair and power bevel gear pair Download PDF

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CN112815070A
CN112815070A CN202110097501.6A CN202110097501A CN112815070A CN 112815070 A CN112815070 A CN 112815070A CN 202110097501 A CN202110097501 A CN 202110097501A CN 112815070 A CN112815070 A CN 112815070A
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twisted
pair
rotor
blade
angle
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李玉龙
任茂文
臧勇
赵宏顺
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Suqian College
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/17—Toothed wheels
    • 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
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/082—Details specially related to intermeshing engagement type pumps
    • F04C18/084—Toothed wheels
    • 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
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C18/18—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with similar tooth forms
    • 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
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • 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
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/001—Radial sealings for working fluid
    • F04C27/004—Radial sealing elements specially adapted for intermeshing-engagement type pumps, e.g. gear pumps
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F30/00—Computer-aided design [CAD]
    • G06F30/10—Geometric CAD
    • G06F30/17—Mechanical parametric or variational design
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F2119/00—Details relating to the type or aim of the analysis or the optimisation
    • G06F2119/14—Force analysis or force optimisation, e.g. static or dynamic forces

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
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  • Mathematical Analysis (AREA)
  • Mathematical Optimization (AREA)
  • Pure & Applied Mathematics (AREA)
  • Computer Hardware Design (AREA)
  • Evolutionary Computation (AREA)
  • Rotary Pumps (AREA)

Abstract

The invention discloses a fixed-point conjugate 3-twisted-blade rotor volume pair and a helical tooth power pair, wherein the 3-twisted-blade rotor volume pair comprises two non-contact 3-twisted-blade rotors with the same end surface profile, opposite spiral directions and the same helical angle, the helical tooth power pair comprises two contact type standard involute cylindrical helical gears with the same end surface profile, opposite spiral directions and the same helical angle, the end surface pitch circle radii and the helical angles of the 3-twisted-blade rotor volume pair and the helical tooth power pair are equal, and the helical directions of the 3-twisted-blade rotor and the standard involute cylindrical helical gears on the same axis are opposite. The invention has the advantages of maximized shape coefficient and volume utilization coefficient, smaller radial leakage rate and conjugate leakage rate, and no theoretical flow pulsation and axial force.

Description

Fixed-point conjugated 3-twisted-blade volume rotor pair and power bevel gear pair
Technical Field
The invention belongs to the technical field of rotor pumps, and particularly relates to a 3-twisted blade profile structure which has high volume efficiency and theoretically no pulsation and is used as a volume auxiliary rotor, and a power auxiliary helical gear which is determined by the coupling of the theoretical axial force and the volume auxiliary rotor which are mutually offset.
Background
The rotor pump is a volume device which utilizes two identical rotors, namely rotor volume pairs, and in the non-contact conjugated rotation process, the generated inlet vacuum suction force can be used for conveying a medium to an outlet, and the rotary power of the rotor pair is provided by another helical tooth power pair with a helical angle of 8-20 degrees in the axial direction. High volumetric efficiency and low noise are two main pursuits of the rotor pump, and the American Petroleum institute API676 standard and SH/T3151-.
High volumetric efficiency is achieved primarily by the configuration of the profile that maximizes the volumetric utilization factor and minimizes internal leakage, and the volumetric utilization factor maximization is equivalent to the configuration of the rotor's shape factor (i.e., rotor tip radius/end face pitch radius) maximization profile. The flow pulsation and pressure pulsation caused by the contour structure are main sources of noise generation, although the flow pulsation can be reduced by the large blade number or twisted blades, the shape coefficient of the rotor is greatly reduced while the pulsation improvement of the large blade number is limited, and the method usually belongs to an indirect method of unreliable; although the processing difficulty of the twisted blade is increased, the flow pulsation and the pressure pulsation can be greatly reduced on the premise of not changing the shape coefficient, and even the theoretical pulsation-free effect is achieved, so that the twisted blade belongs to a direct method which is quick and effective.
For a conventional rotor with a shape factor completely determined by the conjugate profile segment of the rotor, the curve types of the conjugate profile segment with the maximized shape factor are arc and involute, and the upper limits are 2 leaves, 3 leaves, and 1.670, 1.477, 1.368, 1.618, 1.464 and 1.366 under 4 leaves, respectively, but the problem of the maximum shape factor of all the curve types of the conjugate profile segment is not solved. The conjugate contour segment is usually composed of two part contour segments of outer conjugate of pitch circle and inner conjugate of pitch circle.
The internal leakage of the rotor pump mainly consists of three parts of radial leakage, axial leakage and conjugate zone leakage, and although the axial leakage is slightly influenced by the configuration of the rotor profile, the radial leakage and the conjugate leakage can be effectively inhibited through the profile improvement of the equal-gap seal in the radial direction of the inner circular surface of the pump shell and the multi-point position seal of the conjugate zone (similar to the multi-meshing point in the gear transmission with the contact ratio of more than 1).
Although the multi-point sealing of the conjugate zone of the straight-blade rotor pair easily causes the pressure impact of the oil trapping phenomenon of the gear pump of the internal medium, the axial conjugate gap length of the twisted-blade rotor is changed, as long as the axial stagger angle and the width ratio (axial width/end face pitch circle diameter) of the profiles at two ends are properly designed, and the non-contact clearance and the not-too high rotating speed exist between the rotors, so that the so-called oil trapping phenomenon cannot be caused, but the generated harmful axial force needs to be counteracted or partially counteracted, otherwise, the friction loss in the device is increased, and the service life is shortened.
Disclosure of Invention
The invention provides a 3-twisted-blade rotor with an end face profile having the maximum shape coefficient, radial equal sealing gaps, conjugate-zone multi-point seals, 60-twisted-blade stagger angles and 17.5-18.5-helical angles of the rotor two-end face profiles in all conjugate profile curve types and determination of a standard involute cylindrical helical gear with the same 17.5-18.5-helical angles, which is mutually offset with a volume pair in terms of theoretical axial force, and aims at higher volume efficiency and no theoretical flow pulsation and axial force expected by a rotor pump in the background technology, and the design requirements of a fixed-point geometric relationship of contraction of a conjugate profile section in a pitch circle and a 60-twisted-blade stagger angle of the rotor two-end profiles and a contained angle structure of a pump shell required by no theoretical flow pulsation.
In order to achieve the purpose, the technical solution of the invention is as follows:
the utility model provides a 3 twist reverse leaf rotor volume of fixed point conjugation is vice and skewed tooth power is vice which characterized in that: the 3 twisted blade rotor volume pairs comprise two non-contact 3 twisted blade rotors with the same end surface profile, opposite spiral directions and the same spiral angle, the helical tooth power pairs comprise two contact type standard involute cylindrical helical gears with the same end surface profile, opposite spiral directions and the same spiral angle, the end surface pitch circle radius and the spiral angle of the 3 twisted blade rotor volume pairs and the helical tooth power pairs are equal, and the spiral directions of the 3 twisted blade rotors and the standard involute cylindrical helical gears are opposite on the same axis.
The spiral angles of the 3 twisted blade rotor and the standard involute cylindrical helical gear are between 17.5 and 18.5 degrees, the tooth number and the normal face modulus of the standard involute cylindrical helical gear are determined by the spiral angle of 18 degrees, and then the specific spiral angle between 17.5 and 18.5 degrees is determined by the equal radius of the pitch circle of the end faces of the 3 twisted blade rotor and the standard involute cylindrical helical gear.
The twisted blade stagger angle of the profiles at the two ends of the 3 twisted blade rotor is 60 degrees, and the axial stagger angle of the profiles at the two ends of the standard involute cylindrical helical gear is 360 degrees/tooth number.
According to a twisted blade rule of 60-degree stagger angles of outlines at two ends of a 3 twisted blade rotor and a helical angle xi between 17.5 degrees and 18.5 degrees, the width-diameter ratio of the 3 twisted blade rotor is as follows:
Figure BDA0002914438580000031
the end surface pitch circle radius r is uniquely determined by a rated flow Q, a rated rotating speed n, a volumetric efficiency eta and a volume utilization coefficient lambda and a shape coefficient epsilon of a 3-twisted-blade rotor which are given by a rotor pump and a helical angle xi between 17.5 degrees and 18.5 degrees as follows:
Figure BDA0002914438580000032
the tooth number z and the normal modulus m of the standard involute cylindrical helical gearnThe method comprises the steps of firstly designing a gear by a helix angle xi of 18 degrees, an end face pitch circle radius r (xi), a standard normal face pressure angle of 20 degrees, a tooth crest height coefficient of 1 and a normal face top clearance coefficient of 0.25 according to a cylindrical gear module for GB/T1357 + 2008 general machinery and heavy machinery and a basic tooth profile of GB1356-88 involute cylindrical gear, and combining the following formula
2r(ξ)×cosξ＝mnz≈2r(18°)×cos(18°) (3)
Is determined by approximately equality of, thenThe specific helical angle xi between 17.5 degrees and 18.5 degrees is uniquely determined by the absolute equal radius of the pitch circle of the end surface of the 3 twisted blade rotor and the standard involute cylindrical helical gear, and finally the corresponding specific width-diameter ratio phi is determined by the formulas (1) and (2)rotor(ξ) and the end face pitch radius r (ξ).
According to the axial angle staggering rule of 360 DEG of the outline of two ends of the standard involute cylindrical helical gear/the number of teeth and the specific helical angle xi between 17.5 and 18.5 DEG, the width-diameter ratio is defined by
Figure BDA0002914438580000033
Determination of the degree of overlap of the end faces εtFrom the determined number of teeth z and normal modulus mnThe specific helix angle xi between 17.5 degrees and 18.5 degrees and the standard normal face pressure angle of 20 degrees, the addendum coefficient of 1 and the normal face tip clearance coefficient of 0.25 are uniquely determined.
The end face theoretical profile of the half blade of the 3-twisted blade rotor consists of four parts, namely a top concentric circular arc, an outer conjugate profile section, an inner transition profile section and a valley concentric circular arc which are connected end to end, wherein corresponding end points and connecting points sequentially comprise a peak point, a middle node, a root point and a valley point which are positioned on a peak symmetry axis, wherein the peak point, the middle node and the root point are positioned on a valley symmetry axis, the two boundaries of the half blade profile are the peak symmetry axis and the valley symmetry axis, an included angle of the peak symmetry axis and the valley symmetry axis is 60 degrees, a middle line of the 60-degree included angle is a middle axis, and an intersection point of the middle axis and.
And the central angle of the pitch arc circle from the intersection point of the normal line and the pitch circle at the top point of the outer conjugate contour section to the middle node is a top pitch angle beta.
The outer conjugate profile segment is a conjugate trajectory line of a middle node of the paired rotor on the rotor.
The inner transition profile section is a swept trajectory line of the vertex of the paired rotor on the rotor.
The top concentric circular arc and the valley concentric circular arc are two circular arcs taking the center of the rotor as the center of a circle, r epsilon and r x (2-epsilon) are respectively radiuses, and the central angles are both top seal angles alpha.
The apex seal angle alpha, the shape coefficient epsilon and the volume utilization coefficient lambda of the rotor are all determined by the following formula of the apex pitch angle beta:
Figure BDA0002914438580000041
uniquely, if the relevant data under the condition that the beta is 45-60 degrees is shown in table 1, the shape coefficient of the 3-twisted-blade rotor is larger than the upper limit shape coefficient 1.477 of the existing common circular arc rotor with the same blade number, even the effect of the upper limit shape coefficient of 2 blades 1.67 is achieved, and the maximum shape coefficient is the maximum shape coefficient in all conjugate profile curve types,
top seal angle, shape coefficient and volume utilization coefficient under top pitch angle of 145-60 degrees
Figure BDA0002914438580000042
The 3-twisted-blade rotor volume pair has 5 sealing point positions on 2 conjugate points +2 vertexes +1 concentric circular arcs in a [0, alpha ] interval, has 3 sealing point positions on 2 conjugate points +1 vertexes in a (alpha, beta-30 DEG) interval, has 1 conjugate point sealing point position in a (beta-30 DEG, 30 DEG) interval, and is relative to a common rotor which only has 1 sealing point position in the whole course.
Compared with the prior art, the invention has the following beneficial effects:
the fixed-point conjugate 3-twisted-blade volume rotor pair and the power helical gear pair have the advantages of maximized shape coefficient and volume utilization coefficient, smaller radial leakage rate and conjugate leakage rate, and no theoretical flow pulsation and axial force.
Drawings
Other features, objects and advantages of the present invention will become more apparent upon reading of the following detailed description of non-limiting embodiments thereof, with reference to the accompanying drawings.
FIG. 1 is a schematic coaxial view of a 3 twisted lobe volumetric rotor pair and a power bevel gear pair.
Fig. 2 is a schematic view of a half-wheel profile configuration for a 3 twist rotor.
FIG. 3 is a schematic diagram of the number of seal dot bits in different intervals.
Wherein: o, a rotor center, O', a paired rotor center, 0, a peak point, 1, a vertex, 2, a middle node, 3, a root point, 4, a valley point, O0, a peak symmetry axis, O2, a middle axis, O4, a valley symmetry axis, 01, a top concentric circular arc, 12, an outer conjugate contour section, 23, an inner transition contour section, 34, a valley concentric circular arc, r, an end face pitch circle radius, epsilon, a shape coefficient, alpha, a top seal angle, beta, a top pitch angle, 5, a rotor volume pair, 6, an oblique tooth power pair, 7, a driving shaft, 8 and a driven shaft.
Detailed Description
In order to make the technical means, the creation characteristics, the achievement purposes and the effects of the invention easy to understand, the invention is further described with the specific embodiments.
As shown in fig. 1 to 3, the twisted blade rotor volume pair and the power helical gear pair are fixed-point conjugated, the twisted blade rotor volume pair includes two non-contact 3 twisted blade rotors with the same end surface profile, opposite spiral directions and the same spiral angle between 17.5 ° and 18.5 °, the twisted blade stagger angle of the profiles at the two ends of the rotors is 60 °, the helical gear power pair includes two contact standard involute cylindrical helical gears with the same end surface profile, opposite spiral directions and the same spiral angle between 17.5 ° and 18.5 °, the axial stagger angle of the profiles at the two ends of the standard involute cylindrical helical gears is 360 °/tooth number, the end surface pitch circle radius and the spiral angle of the twisted blade rotor volume pair and the helical gear power pair are equal, and the spiral directions of the coaxial twisted blade rotor and the standard involute cylindrical helical gears are opposite.
The end face theoretical profile of the half blade of the 3-twisted-blade volume rotor consists of four parts, namely a top concentric circular arc 01, an outer conjugate profile section 12, an inner transition profile section 23 and a valley concentric circular arc 34 which are connected end to end, wherein corresponding end points and connecting points sequentially comprise a peak point 0, a peak point 1, a middle node 2, a root point 3 and a valley point 4 which are positioned on a peak symmetry axis O0 and a valley symmetry axis O4, wherein two boundaries of the half blade profile are a peak symmetry axis O0 and a valley symmetry axis O4, an included angle between the peak symmetry axis O0 and the valley symmetry axis O4 is 60 degrees, a middle line of the included angle of 60 degrees is a middle axis O2, and an intersection point between the middle axis O2 and a pitch circle is a middle node 2; the central angle of the pitch arc circle from the intersection point of the normal line and the pitch circle at the top point of the outer conjugate contour section 12 to the middle node 2 is a top pitch angle beta; the outer conjugate profile segment 12 is the conjugate trajectory line of the middle node 2 of the paired rotor on the rotor; the inner transition profile section 23 is the swept trajectory line of the apex 1 of the mating rotor on the rotor.
Example rated flow 1010mm3The shape coefficient of the 3-twisted-blade volumetric rotor is much larger than the shape coefficient of the conventional common-blade-number circular-arc rotor with the restriction of 1.477, and therefore, the maximum shape coefficient is realized.
The tooth number z and the normal modulus m of the standard involute cylindrical helical gearnThe method is characterized in that a helix angle xi of 18 degrees, an end face pitch circle radius r (xi), a standard normal face pressure angle of 20 degrees, an addendum height coefficient of 1 and a normal face top clearance coefficient of 0.25 are combined with the following formula according to a gear design method of cylindrical gear module for GB/T1357-2008 universal machinery and heavy machinery and a basic tooth profile of GB1356-88 involute cylindrical gear:
Figure BDA0002914438580000061
is approximately equal to determine mnThe specific value xi of the spiral angle between 17.5 degrees and 18.5 degrees is determined by the equal pitch radius of the end surface of the rotor and the standard involute cylindrical helical gear as 4 and z as 113, and finally the corresponding specific width ratio phi is determined by the formulas (1), (2) and (4)rotor(xi) 1.612, end face pitch radius r (xi) 237.62mm, end face overlap ratio epsilontWidth ratio phi between 1.72 and standard involute cylindrical bevel geargear(ξ)＝0.147。
The top concentric circular arc 01 and the valley concentric circular arc 34 are two circular arcs with the center O of the rotor as the center, r epsilon is 237.62 × 1.66 ═ 394.45mm, r (2-epsilon) ═ 237.62 × (2-1.66) ═ 80.79mm as the radius respectively, and the central angles are all alpha ═ 4 degrees; the 3-twisted-blade rotor volume pair has 5 sealing points in total on 2 middle nodes +2 vertexes + concentric circular arcs in a [0, 4 DEG ] interval, 3 sealing points in total on 2 middle nodes +1 vertexes in a (4 DEG, 25.9 DEG) interval, and sealing points of 1 middle node in a (25.9 DEG, 30 DEG) interval, wherein the sealing points are compared with a common rotor which only has 1 sealing point in the whole course, and the sealing interval ratio of multiple points reaches 86.4 percent, so that the invention realizes smaller conjugate leakage rate, and the invention realizes smaller radial equal gap sealing of a top sealing angle of the whole blade 2 alpha being 8 degrees, and therefore, the invention realizes smaller radial equal gap sealing.
While there have been shown and described what are at present considered the fundamental principles and essential features of the invention and its advantages, it will be apparent to those skilled in the art that the invention is not limited to the details of the foregoing exemplary embodiments, but is capable of other specific forms without departing from the spirit or essential characteristics thereof. The present embodiments are therefore to be considered in all respects as illustrative and not restrictive, the scope of the invention being indicated by the appended claims rather than by the foregoing description, and all changes which come within the meaning and range of equivalency of the claims are therefore intended to be embraced therein.

Claims (8)

1. The utility model provides a 3 twist reverse leaf rotor volume of fixed point conjugation is vice and skewed tooth power is vice which characterized in that: the 3 twisted blade rotor volume pairs comprise two non-contact 3 twisted blade rotors with the same end surface profile, opposite spiral directions and the same spiral angle, the helical tooth power pairs comprise two contact type standard involute cylindrical helical gears with the same end surface profile, opposite spiral directions and the same spiral angle, the end surface pitch circle radius and the spiral angle of the 3 twisted blade rotor volume pairs and the helical tooth power pairs are equal, and the spiral directions of the 3 twisted blade rotors and the standard involute cylindrical helical gears are opposite coaxially.
2. The fixed-point conjugate 3-twisted-blade rotor volume pair and helical tooth power pair as claimed in claim 1, wherein: the spiral angle of the 3 twisted blade rotor and the standard involute cylindrical helical gear is 17.5-18.5 degrees.
3. The fixed-point conjugate 3-twisted-blade rotor volume pair and helical tooth power pair as claimed in claim 1, wherein: the twisted blade stagger angle of the profiles at the two ends of the 3 twisted blade rotor is 60 degrees.
4. The fixed-point conjugate 3-twisted-blade rotor volume pair and helical tooth power pair as claimed in claim 1, wherein: the axial stagger angle of the profiles at the two ends of the standard involute cylindrical helical gear is 360 degrees/tooth number.
5. The fixed-point conjugate 3-twisted-blade rotor volume pair and helical tooth power pair as claimed in claim 1, wherein: the end face theoretical profile of the half blade of the 3-twisted blade rotor consists of four parts, namely a top concentric circular arc, an outer conjugate profile section, an inner transition profile section and a valley concentric circular arc which are connected end to end, wherein corresponding end points and connecting points sequentially comprise a peak point, a middle node, a root point and a valley point which are positioned on a peak symmetry axis, a valley symmetry axis, two boundaries of the half blade profile are the peak symmetry axis and the valley symmetry axis, an included angle between the peak symmetry axis and the valley symmetry axis is 60 degrees, a middle line of the 60-degree included angle is a middle axis, and an intersection point of the middle axis and a pitch circle is a middle node.
6. The fixed-point conjugate 3-twisted-blade rotor volume pair and helical tooth power pair as claimed in claim 5, wherein: the outer conjugate contour section is a conjugate trajectory line of a middle node of the paired rotor on the rotor, and a pitch arc central angle from a normal line at the vertex of the outer conjugate contour section to the middle node is a top pitch angle.
7. The fixed-point conjugate 3-twisted-blade rotor volume pair and helical tooth power pair as claimed in claim 5, wherein: the inner transition profile section is a swept trajectory line of the vertex of the paired rotor on the rotor.
8. The fixed-point conjugate 3-twisted-blade rotor volume pair and helical tooth power pair as claimed in claim 5, wherein: the top concentric circular arc and the valley concentric circular arc are circular arcs taking the center of the rotor as the center of a circle, r epsilon and r x (2-epsilon) are radiuses respectively, the central angle is two circular arcs of a top seal angle, r is the radius of a pitch circle of the end face, and epsilon is a shape coefficient.
CN202110097501.6A 2021-01-25 2021-01-25 Fixed-point conjugated 3-twisted-blade volume rotor pair and power bevel gear pair Pending CN112815070A (en)

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