CN218934718U - Full-meshing low-abrasion gear molded line - Google Patents

Full-meshing low-abrasion gear molded line Download PDF

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CN218934718U
CN218934718U CN202223360880.2U CN202223360880U CN218934718U CN 218934718 U CN218934718 U CN 218934718U CN 202223360880 U CN202223360880 U CN 202223360880U CN 218934718 U CN218934718 U CN 218934718U
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rotor
meshing
gear ring
gear
molded line
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许静
吴鑫燚
梁钧
周镐哲
罗俊豪
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Shanghai Fuhuite Pump Manufacturing Co ltd
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Shanghai Yuesheng Zhikong Environmental Technology Co ltd
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    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
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Abstract

The utility model discloses a full-meshing low-abrasion gear molded line, which is formed by meshing an inner rotor and an outer rotor; the molded line of the inner rotor is formed by connecting an arc section AB and an arc section BC end to end; the molded line of the outer rotor is formed by connecting an arc section DE and an arc section EF end to end. The utility model not only can reduce the impact contact load in the gear meshing process, improve the speed slip value caused by the relative motion of the inner tooth and the outer tooth, correct the pressure impact of the inner tooth and the outer tooth meshing dead area, but also can reduce the contact stress, and further reduce the noise and abrasion generated in the meshing process.

Description

Full-meshing low-abrasion gear molded line
Technical Field
The utility model relates to the technical field of fluid conveying, in particular to a full-meshing low-abrasion gear molded line.
Background
The refrigerant pump is a device for pumping refrigerant, and the pumped refrigerant is used for transmitting energy to the refrigerant such as ammonia or freon through the pump so as to increase the kinetic energy and the pressure energy of the refrigerant.
In the process of conveying the refrigerants such as ammonia or freon, the refrigerant pump in the prior art is easy to cause the increase of impact contact load in the gear meshing process due to the defects related to the structure, and the pressure impact of the inner and outer gear meshing dead areas is large, so that the contact stress is increased, the friction and abrasion of gears are increased, and larger noise is generated.
Disclosure of Invention
The utility model aims to provide a technical scheme of a full-meshing low-wear gear molded line, which aims at overcoming the defects of the prior art, and the full-meshing low-wear gear molded line not only can reduce impact contact load in the gear meshing process, improve the speed sliding value caused by relative movement of inner teeth and outer teeth, correct pressure impact in the inner and outer tooth meshing dead zone, but also can reduce contact stress and further reduce noise and wear generated in the meshing process.
In order to solve the technical problems, the utility model adopts the following technical scheme:
full-meshing low-wear gear molded line is characterized in that: the full-meshing low-wear gear molded line is formed by meshing an inner rotor and an outer rotor;
the molded line of the inner rotor is formed by connecting an arc section AB and an arc section BC end to end, wherein the equation of the arc section AB is that
Figure BDA0003995669230000011
The equation of the arc segment BC is
Figure BDA0003995669230000012
The molded line of the outer rotor is formed by connecting an arc segment DE and an arc segment EF end to end, wherein the equation of the arc segment DE is
Figure BDA0003995669230000021
The equation of the arc segment EF is
Figure BDA0003995669230000022
Figure BDA0003995669230000023
Wherein R is 1 Radius of base circle, r 1 Is the radius of the second concave hole, r2 is the radius of the first concave hole, e is the eccentricity, z 1 For the number of teeth of the outer gear ring, z 2 For the number of teeth of the inner gear ring, z 2 ＝z 1 +1, t1 is the rotation angle of the second concave hole, and the range is (0, pi/z) 1 ) T is the rotation angle of the first concave hole, and the range of the rotation angle is (-pi/z) 1 ,0). The full-meshing low-abrasion gear molded line not only can reduce impact contact load in the gear meshing process, improve the speed slip value caused by relative movement of the inner tooth and the outer tooth, correct pressure impact in the inner tooth and the outer tooth meshing dead area, but also can reduce contact stress, and further reduce noise and abrasion generated during meshing. />
Further, the inner rotor and the outer rotor form a continuously variable cavity during engagement, and the cavity is used for absorbing or discharging liquid.
Further, an outer gear ring is arranged on the inner rotor, an inner gear ring meshed with the outer gear ring is arranged on the outer rotor, and a cavity is arranged between the outer gear ring and the inner gear ring.
Further, be equipped with shaft hole and recess on the inner rotor, the tip of inner rotor is located to two recesses, shaft hole intercommunication recess, the assembly of being convenient for.
Further, the terminal surface of inner rotor is equipped with the first shrinkage pool that is annular distribution, and first shrinkage pool is located and is close to the radial outside convex one side on the outer ring gear, and the degree of depth of first shrinkage pool is 1 ~ 3mm, is convenient for store partial liquid, improves its lubrication effect, reduces frictional wear.
Further, the distance between the first concave hole and the outer gear ring of the inner rotor is 3-5 mm, so that the first concave hole can effectively store liquid.
Further, the terminal surface of external rotor is equipped with the second shrinkage pool that is annular distribution, and the second shrinkage pool is located and is close to the radial inward convex one side on the ring gear, and the degree of depth of second shrinkage pool is 1 ~ 3mm, is convenient for store partial liquid, improves its lubrication effect, reduces frictional wear.
Further, the distance between the second concave hole and the inner gear ring of the outer rotor is 3-5 mm, so that the second concave hole can effectively store liquid.
Further, the end face of the outer rotor is provided with an annular groove, the depth of the annular groove is 1-3 mm, so that partial liquid can be conveniently stored, the lubricating effect of the outer rotor is improved, and friction and abrasion are reduced.
Due to the adoption of the technical scheme, the utility model has the following beneficial effects:
the full-meshing low-abrasion gear molded line can reduce impact contact load in the gear meshing process, improve speed slip value caused by relative movement of inner teeth and outer teeth, correct pressure impact of the inner and outer tooth meshing dead area, reduce contact stress and further reduce noise and abrasion generated during meshing.
Description of the drawings:
the utility model is further described below with reference to the accompanying drawings:
FIG. 1 is a graph showing the effect of the full mesh low wear gear profile of the present utility model when the inner and outer rotors mesh;
FIG. 2 is a schematic diagram of the connection between the inner rotor, outer rotor and pump body in the present utility model;
FIG. 3 is a top view of FIG. 2;
FIG. 4 is a schematic diagram of an inner rotor according to the present utility model;
FIG. 5 is a schematic view of the structure of the outer rotor according to the present utility model;
FIG. 6 is a graph of contact stress versus radians in the present utility model;
FIG. 7 is a graph of slip ratio versus radians in the present utility model;
FIG. 8 is a stress diagram of a double cycloid rotor profile obtained by stress simulation in the present utility model;
FIG. 9 is a graph of deformation of a double cycloid rotor profile obtained by stress simulation in the present utility model;
FIG. 10 is a stress diagram of an elliptical rotor profile obtained by stress simulation in accordance with the present utility model;
FIG. 11 is a graph of deformation of an elliptical rotor profile obtained by stress simulation in the present utility model;
FIG. 12 is a stress diagram of an arc rotor profile obtained by stress simulation in the present utility model;
FIG. 13 is a graph of deformation of an arc rotor profile obtained by stress simulation in the present utility model;
in the figure: 1-a pump body;
2-inner rotor; 201-an outer gear ring; 202-shaft holes; 203-grooves; 204-a first concave hole;
3-outer rotor; 301-an inner gear ring; 302-a second recess; 303-an annular groove;
4-die cavity.
Detailed Description
It should be noted that, in the case of no conflict, the embodiments and features in the embodiments may be combined with each other. The utility model will be described in detail below with reference to the drawings in connection with embodiments.
In order that those skilled in the art will better understand the present utility model, a technical solution in the embodiments of the present utility model will be clearly and completely described below with reference to the accompanying drawings in which it is apparent that the described embodiments are only some embodiments of the present utility model, not all embodiments. All other embodiments, which can be made by those skilled in the art based on the embodiments of the utility model without making any inventive effort, shall fall within the scope of the utility model.
It should be noted that the terms "first," "second," and the like in the description and claims of the present utility model and in the above-described figures are used for distinguishing between similar objects and not necessarily for describing a particular sequential or chronological order. Furthermore, the terms "comprise" and "have," as well as any variations thereof, are intended to cover a non-exclusive inclusion.
As shown in fig. 1 to 5, the full-mesh low-wear gear molded line of the present utility model is formed by meshing an inner rotor 2 and an outer rotor 3; the outer rotor 3 is rotatably connected in the pump body 1, and the inner rotor 2 is in meshed connection in the outer rotor 3. The inner rotor 2 and the outer rotor 3 form a continuously changing cavity 4 during engagement, the cavity 4 being intended for absorbing or discharging liquid. The inner rotor 2 is provided with an outer gear ring 201, the outer rotor 3 is provided with an inner gear ring 301 meshed with the outer gear ring 201, and the cavity 4 is positioned between the outer gear ring 201 and the inner gear ring 301. The inner rotor 2 is provided with the shaft hole 202 and the grooves 203, the two grooves 203 are arranged at the end part of the inner rotor 2, and the shaft hole 202 is communicated with the grooves 203, so that the assembly is convenient.
The terminal surface of inner rotor 2 is equipped with the first shrinkage pool 204 that is annular distribution, and first shrinkage pool 204 is located and is close to the outside convex one side in radial outside on the outer ring gear 201, and the degree of depth of first shrinkage pool 204 is 1 ~ 3mm, is convenient for store partial liquid, improves its lubrication effect, reduces frictional wear, and the interval between first shrinkage pool 204 and the outer ring gear 201 of inner rotor 2 is 3 ~ 5mm, guarantees that first shrinkage pool 204 can effectively store liquid. The end face of the outer rotor 3 is provided with second concave holes 302 distributed in an annular shape, the second concave holes 302 are positioned on one side close to the inner gear ring 301 protruding inwards in the radial direction, the depth of the second concave holes 302 is 1-3 mm, so that partial liquid can be conveniently stored, the lubrication effect of the liquid is improved, friction and abrasion are reduced, the distance between the second concave holes 302 and the inner gear ring 301 of the outer rotor 3 is 3-5 mm, and the second concave holes 302 can be guaranteed to effectively store the liquid.
The end face of the outer rotor 3 is provided with an annular groove 303, the depth of the annular groove 303 is 1-3 mm, so that partial liquid can be conveniently stored, the lubricating effect is improved, and friction and abrasion are reduced.
The molded line of the inner rotor 2 is formed by connecting an arc section AB and an arc section BC end to end, wherein the equation of the arc section AB is that
Figure BDA0003995669230000051
The equation of the arc segment BC is
Figure BDA0003995669230000052
The molded line of the outer rotor 3 is formed by connecting an arc segment DE and an arc segment EF end to end, wherein the equation of the arc segment DE is that
Figure BDA0003995669230000053
The equation of the arc segment EF is
Figure BDA0003995669230000054
Figure BDA0003995669230000056
Wherein R is 1 Radius of base circle, r 1 Is the radius of the second concave hole, r2 is the radius of the first concave hole, e is the eccentricity, z 1 For the number of teeth of the outer gear ring, z 2 For the number of teeth of the inner gear ring, z 2 ＝z 1 +1, t1 is the rotation angle of the second concave hole, and the range is (0, pi/z) 1 ) T is the rotation angle of the first concave hole, and the range of the rotation angle is (-pi/z) 1 ，0)。
The full-meshing low-abrasion gear molded line not only can reduce impact contact load in the gear meshing process, improve the speed slip value caused by relative movement of the inner tooth and the outer tooth, correct pressure impact in the inner tooth and the outer tooth meshing dead area, but also can reduce contact stress, and further reduce noise and abrasion generated during meshing.
Equation for arc segment AB
Figure BDA0003995669230000055
And the equation of the arc segment BC
Figure BDA0003995669230000061
By means of coordinate transformation
Figure BDA0003995669230000062
Figure BDA0003995669230000063
Figure BDA0003995669230000064
Figure BDA0003995669230000065
Figure BDA0003995669230000066
Figure BDA0003995669230000067
Figure BDA0003995669230000068
Figure BDA0003995669230000069
/>
Figure BDA00039956692300000610
Obtaining
Figure BDA00039956692300000611
Figure BDA00039956692300000612
The present application takes the case where the number of teeth of the inner rotor is 7 and the number of teeth of the outer rotor is 8 as an example
As shown in fig. 8 and 9, the maximum deformation of the double cycloid rotor profile reaches 0.08575mm and the maximum stress reaches 143.4MPa during rotation.
As shown in fig. 10 and 11, the maximum deformation of the elliptic rotor profile during rotation reaches 0.08599mm and the maximum stress reaches 316.9MPa.
As shown in fig. 12 and 13, the maximum deformation of the arc rotor profile reaches 0.08599mm and the maximum stress reaches 218.9MPa during rotation.
The stress strain between the rotors is obtained through stress simulation, so that the stress strain of the rotors is found to be very small, and the friction and abrasion of the rotors can be indicated to be small.
The optimization method of the full-meshing low-wear gear molded line comprises the following steps:
s1, determining the eccentricity e and the base radius R between the inner rotor and the outer rotor 1 Radius r of first concave hole 1 And a rotation angle t 1 Radius r of the second concave hole 2 And rotation angle t, number of teeth z of external gear 1 And tooth number z of inner gear ring 2 The method comprises the steps of carrying out a first treatment on the surface of the The utility model uses R 1 ＝32mm；r 1 ＝28mm；r 2 ＝30mm；e＝4mm；z 1 ＝7；z 2 ＝8；t 1 =0:0.01:pi/7; t= -pi/7:0.01:0; tooth thickness b=34 mm is an example.
S2, determining the area change of the inner rotor and the outer rotor in the meshing process through the displacement q=z 1 ×B×(Smax
Smin), the flow rate of the cavity is determined: q=q×n, where B is tooth thickness;
displacement volume: q=z 1 ×B×(Smax-Smin)＝7×34×198.6＝47266.8，
Flow rate: q=q×n= 47266.8 ×1450×60×10 -9 ＝4.11m 3 /h。
S3, determining the slip rate and the contact stress of the rotor;
the slip ratio of the inner rotor is
Figure BDA0003995669230000071
The slip ratio of the outer rotor is
Figure BDA0003995669230000072
The slip ratio is the ratio of the speed difference of the inner rotor and the outer rotor to the speed of the inner rotor and the outer rotor relative to the base circle.
Figure BDA0003995669230000073
(hertz formula);
Figure BDA0003995669230000074
Figure BDA0003995669230000075
/>
Figure BDA0003995669230000076
(1) Ed is the elastic modulus of the two contact bodies, E1 and E2 are the elastic modulus of the inner rotor and the outer rotor, and are 78400MPa respectively;
(2)a 0 the radius a of the outer rotor is 7.8mm, and ρ is the actual tooth profile curvature radius of the cycloid gear;
(3) Tooth thickness b=34 mm;
(4) Pressure difference Δp=0.7 mpa, q displacement 40188;
as the rotation angle changes, the contact stress and the slippage rate are shown in a line graph as shown in figure 6, and the number of teeth of the double cycloid rotor is changed. The line diagram of the contact stress and the slip ratio with the change of the rotation angle is shown in fig. 7, in which the internal teeth are 7 and the external teeth are 8,q and 47266.8.
S4, parameter optimization is carried out, and the slip rate and the contact stress are calculated, so that an equation of the inner rotor and the outer rotor is obtained, and under the condition of a certain flow, the slip rate is small, the contact stress is small, the friction and the abrasion are small, and the rotor molded line is good;
s5, calculating and drawing the full-meshing low-abrasion gear profile.
Equation of arc segment AB
Figure BDA0003995669230000081
Arc segment BC equation
Figure BDA0003995669230000082
The equation of the arc segment DE is
Figure BDA0003995669230000083
The equation of the arc segment EF is
Figure BDA0003995669230000084
The above is only a specific embodiment of the present utility model, but the technical features of the present utility model are not limited thereto. Any simple changes, equivalent substitutions or modifications made on the basis of the present utility model to achieve substantially the same technical effects are included in the scope of the present utility model.

Claims (9)

1. Full-meshing low-wear gear molded line is characterized in that: the full-meshing low-wear gear molded line is formed by meshing an inner rotor and an outer rotor;
the molded line of the inner rotor is formed by connecting an arc section AB and an arc section BC end to end, wherein the equation of the arc section AB is that
Figure FDA0003995669220000011
The equation of the arc segment BC is
Figure FDA0003995669220000012
The molded line of the outer rotor is formed by connecting an arc segment DE and an arc segment EF end to end, wherein the equation of the arc segment DE is that
x 3 ＝(R 1 -r 1 )×cos(z 1 ×t 1 /z 2 )+r 1 ×cos((R 1 -r 1 )×t 1 /r 1 +1/z 2 ×t 1 )+e×cos(-z 1 /z 2 ×t 1 )
y 3 ＝(R 1 -r 1 )×sin(z 1 ×t 1 /z 2 )-r 1 ×sin((R 1 -r 1 )×t 1 /r 1 +1/z 2 ×t1 ) -e×sin(-z 1 /z 2 ×t 1 )；
The equation of the arc segment EF is
x 4 ＝(R 1 +r 2 )×cos(z 1 ×t/z 2 )-r 2 ×cos((R 1 +r 2 )×t/r 2 -1/z 2 ×t)+e×cos(-z 1 /z 2 ×t)
y 4 ＝(R 1 +r 2 )×sin(z 1 ×t/z 2 )-r 2 ×sin((R 1 +r 2 )×t/r 2 -1/z 2 ×t)-e×sin(-z 1 /z 2 ×t)；
Wherein R is 1 Radius of base circle, r 1 Is the radius of the second concave hole, r2 is the radius of the first concave hole, e is the eccentricity, z 1 For the number of teeth of the outer gear ring, z 2 For the number of teeth of the inner gear ring, z 2 ＝z 1 +1, t1 is the rotation angle of the second concave hole, and the range is (0, pi/z) 1 ) T is the rotation of the first concave holeAngle in the range (-pi/z) 1 ，0)。
2. The full mesh low wear gear profile of claim 1, wherein: the inner rotor and the outer rotor form a continuously variable cavity in the meshing process, and the cavity is used for absorbing or discharging liquid.
3. The full mesh low wear gear profile of claim 2, wherein: the inner rotor is provided with an outer gear ring, the outer rotor is provided with an inner gear ring meshed with the outer gear ring, and the cavity is positioned between the outer gear ring and the inner gear ring.
4. The full mesh low wear gear profile of claim 1, wherein: the inner rotor is provided with a shaft hole and grooves, the two grooves are formed in the end portion of the inner rotor, and the shaft hole is communicated with the grooves.
5. A full mesh low wear gear profile as in claim 3, wherein: the end face of the inner rotor is provided with first concave holes which are distributed in an annular mode, and the first concave holes are located on one side, close to the outer gear ring, protruding outwards in the radial direction.
6. The full mesh low wear gear profile of claim 5, wherein: the distance between the first concave hole and the outer gear ring of the inner rotor is 3-5 mm.
7. A full mesh low wear gear profile as in claim 3, wherein: the end face of the outer rotor is provided with second concave holes which are distributed in an annular mode, and the second concave holes are located on one side, close to the inner gear ring, protruding inwards in the radial direction.
8. The full mesh low wear gear profile of claim 7, wherein: the distance between the second concave hole and the inner gear ring of the outer rotor is 3-5 mm.
9. The full mesh low wear gear profile of claim 7, wherein: an annular groove is formed in the end face of the outer rotor.
CN202223360880.2U 2023-03-13 2023-03-13 Full-meshing low-abrasion gear molded line Active CN218934718U (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN117703746A (en) * 2024-01-16 2024-03-15 南京孚奥智能技术有限公司 Internal gear pump

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN117703746A (en) * 2024-01-16 2024-03-15 南京孚奥智能技术有限公司 Internal gear pump

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Address after: Room 8180, building C, 555 Dongchuan Road, Minhang District, Shanghai 201100

Patentee after: Shanghai Fuhuite Pump Manufacturing Co.,Ltd.

Address before: Room 8180, building C, 555 Dongchuan Road, Minhang District, Shanghai 201100

Patentee before: Shanghai Yuesheng Zhikong Environmental Technology Co.,Ltd.