CN115559901A - Claw type vacuum pump rotor and vacuum pump - Google Patents
Claw type vacuum pump rotor and vacuum pump Download PDFInfo
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- CN115559901A CN115559901A CN202211566339.9A CN202211566339A CN115559901A CN 115559901 A CN115559901 A CN 115559901A CN 202211566339 A CN202211566339 A CN 202211566339A CN 115559901 A CN115559901 A CN 115559901A
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- 230000000149 penetrating effect Effects 0.000 claims description 9
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- 235000019096 Proboscidea parviflora Nutrition 0.000 claims description 7
- 230000006835 compression Effects 0.000 abstract description 14
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- 230000005540 biological transmission Effects 0.000 abstract description 2
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- 235000013305 food Nutrition 0.000 description 1
- 230000000737 periodic effect Effects 0.000 description 1
- 239000003208 petroleum Substances 0.000 description 1
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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
- F04C18/08—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
- F04C18/123—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 radially or approximately radially from the rotor body extending tooth-like elements, co-operating with recesses in the other rotor, e.g. one tooth
-
- 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
- F04C25/00—Adaptations of pumps for special use of pumps for elastic fluids
- F04C25/02—Adaptations of pumps for special use of pumps for elastic fluids for producing high vacuum
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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
- F04C2240/00—Components
- F04C2240/20—Rotors
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
The invention discloses a claw type vacuum pump rotor and a vacuum pump, belonging to the technical field of dry type gas transmission pumps, wherein the rotor comprises a pitch circle and a claw, and the linear form of the claw is formed by seven sections of curves connected end to end: long amplitude epicycloid A of front claw tip 1 A 2 Arc section A at the bottom of the claw 2 A 3 A transition arc section A 3 A 4 Arc section A of bottom claw tip 4 A 5 Conjugate curve A of arc segment of tip of bottom claw 6 A 7 Conjugate curve A of transition circular arc section 7 A 8 Arc segment A of the top of the claw 8 A 1 The line type of the pitch circle is a pitch circle arc section A 5 A 6 The claws are connected with the molded lines of the pitch circles end to end, and two adjacent sections of circular arcs are in smooth transition; the rotor profile has better meshing closure and higher gas deliveryThe efficiency and the volume utilization rate are high, the whole section of curve is smoothly connected, other sharp corner points are not arranged except for the tips of the front claws, the stress concentration points are fewer, and the mechanical property is better; meanwhile, the compression cavities formed by the two rotors and the pump cavity are continuous, and compressed air can be discharged completely and smoothly through the exhaust port, so that the efficiency of the claw pump is improved.
Description
Technical Field
The invention relates to the technical field of dry-type gas transmission pumps, in particular to a claw-type vacuum pump rotor and a vacuum pump.
Background
The claw type vacuum pump has the advantages of high pumping speed, stable operation and the like as a double-rotary vacuum pump, realizes the pressurized conveying of gas through a compression cavity formed by two rotors, and is widely applied to the fields of food, chemical industry, medicine, petroleum and the like.
The most important part in the claw vacuum pump is two rotors which are meshed with each other in a conjugate mode and do synchronous opposite-direction double-rotation motion, the two rotors have the same curve in geometry, gas is compressed through a cavity formed by the two rotors meshed with each other in the periodic rotation process, the gas inlet-compression-exhaust process is achieved, and pressurized conveying of the gas is completed. A pair of rotors meshed with each other of the claw type vacuum pump is composed of a plurality of sections of curves, wherein the curves comprise various curve forms such as cycloid curves, circular arcs, conjugate curves and the like, and it is particularly important to reasonably select each section of curve and determine the conjugate curve of the curve in the rotating process. The profile of the claw pump rotor and its intermeshing behavior therefore directly determine the behavior of the claw pump for delivering gas.
As shown in fig. 1, in the form of a rotor profile of a typical single claw pump and a matching type of an inlet and an outlet, air enters a pump chamber from an inlet 100, is compressed by rotation of a rotor, and is discharged from an outlet 200. The experiment to current claw formula vacuum pump discovers, and to the pressurization transport of gas, claw formula vacuum pump's efficiency is not high, and the analysis can know that there is certain defect on the current claw formula pump rotor profile, and space utilization is low, leads to efficiency to reduce, and has a plurality of acute angle cusps, leads to stress concentration, mechanical properties relatively poor. In the process of compressing gas by the rotor of the original curve, the obtuse-angle point of the back of the front claw divides the compression cavity into two parts, namely a cavity A and a cavity B, wherein one part of the gas can be smoothly conveyed through the exhaust port 200, while the other part of the gas can be discharged into the low-pressure cavity through the rotation of the subsequent rotor, even if the shape of the exhaust port 200 is improved, the part of the gas cannot be discharged, for example, the part of the cavity B between the two rotors in fig. 1 cannot be discharged through the improvement of the exhaust port 200, and the compression efficiency of the claw pump is reduced due to the defect of the rotor profile. Therefore, it is very urgent to further optimize the rotor profile of the claw vacuum pump.
Disclosure of Invention
In order to overcome the problems that the space utilization rate of a claw type pump rotor in the prior art is low, the efficiency is reduced, a plurality of sharp points exist, the stress is concentrated, the mechanical property is poor, and gas in a part of cavities cannot be discharged through the improvement of an exhaust port, the invention provides a claw type vacuum pump rotor, wherein the rotor comprises a pitch circle and claws, and the line type of the claws is formed by seven sections of curves connected end to end: long-amplitude epicycloid A of front claw tip 1 A 2 Arc section A at the bottom of the claw 2 A 3 A transition arc section A 3 A 4 Arc section A of bottom claw tip 4 A 5 Conjugate curve A of arc segment of tip of bottom claw 6 A 7 Conjugate curve A of transition circular arc section 7 A 8 Arc segment A of the top of the claw 8 A 1 The line type of the pitch circle is a pitch circle arc section A 5 A 6 The claw is connected with the molded line of the pitch circle end to end, and two adjacent sections of circular arcs are in smooth transition;
and the radius of the claw top arc section of the rotor profile is R 1 Of circular arc section at the bottom of the clawRadius R 2 The radius of the pitch circle is R 0 ：
At the center O of a pitch circle 1 As dots, with O 1 A 2 The straight line is used as the X axis to form a coordinate system XO 1 In Y, the long-amplitude epicycloid A of the front claw tip 1 A 2 At any point on
The following formula is satisfied:
arc segment A at the bottom of the claw 2 A 3 At any point on
The following formula is satisfied:
wherein R is 2 Is the radius of the bottom circle of the claw,
is A 2 A 3 The central angle corresponding to the curve is a designable variable;
transition arc section A 3 A 4 At any point on
The following formula is satisfied:
wherein R is 3 Is a designable variable with a value range of
；
Is A 3 A 4 The central angle of the circle corresponding to the curve,
；
arc section A of bottom claw tip 4 A 5 At any point on
The following formula is satisfied:
wherein R is 4 Derived from known variables, i.e.
。
Is A 4 A 5 The arc angle corresponding to the curve is formed,
；
conjugate curve A of arc segment of bottom claw tip 6 A 7 At any point on
The following formula is satisfied:
wherein:
wherein x is 1 And y 1 Is A 6 A 7 Curve in static coordinate system X 1 O 1 Y 1 Coordinate of lower, x 2 And y 2 Is A 6 A 7 Curve in static coordinate system X 2 O 2 Y 2 Coordinates of the following, and
and
is A 6 A 7 Curve in moving coordinate system XO 1 The coordinates under Y are given by the coordinates of,
is A 6 A 7 Curve in moving coordinate system XO 1 Angle of parameters under Y, moving coordinate system XO 1 Y is lower than A 6 A 7 Coordinates of the curve i.e. A 6 A 7 A parametric equation for the curve;
wherein, the moving coordinate system XO 1 Y is rotor O 1 A coordinate system with the center of the circle as the origin and rotating along with the rotation of the rotor; x 1 O 1 Y1、X 2 O 2 Y 2 Respectively is a rotor O 1 Center of circle and rotor O 2 The circle center is a static coordinate system of the origin, the Y-axis directions of the two static coordinate systems are the same, the X-axis directions are opposite, and the X-axis directions of the two static coordinate systems are opposite 1 O 1 Y 1 In the X-axis direction of the driven rotor O 1 Circle center to rotor O 2 Circle center direction, stationary coordinate system X 2 O 2 Y 2 In the X-axis direction of the driven rotor O 2 Circle center to rotor O 1 The direction of the circle center;
conjugate curve A of transition arc segment 7 A 8 At any point on
The following formula is satisfied:
wherein,
wherein x is 3 And y 3 Is A 7 A 8 Curve in static coordinate system X 1 O 1 Y 1 Coordinate of lower, x 4 And y 4 Is A 7 A 8 Curve in static coordinate system X 2 O 2 Y 2 Coordinates of the following, and
and
is A 7 A 8 Curve in moving coordinate system XO 1 The coordinates under the Y-coordinate system of the coordinate system,
is A 7 A 8 Curve in moving coordinate system XO 1 Angle of parameters under Y, moving coordinate system XO 1 Y is lower than A 7 A 8 Coordinates of the curve i.e. A 7 A 8 A parametric equation for the curve;
arc section A of claw top 8 A 1 At any point on
The following formula is satisfied:
preferably, the rotor is a single claw, one claw profile is connected with the profile of the pitch circle end to end, and the pitch circle arc segment a 5 A 6 At any point on
Satisfies the following formulaFormula (II):
preferably, the rotor is a double claw, and the pitch circle arc segment A 5 A 6 At any point on
The following formula is satisfied:
，
Preferably, the rotor is a three-jaw rotor, and the pitch circle arc segment A 5 A 6 At any point on
The following formula is satisfied:
，
three claw molded lines are respectively connected with the molded line pitch circle arc segment A of the pitch circle 5 A 6 The upper three arc sections are connected end to end.
Preferably, the radius R of the claw-tip arc segment of the rotor profile is 1 Radius R of arc segment at bottom of claw 2 Satisfies the following conditions:
1.5R 2 ≤R 1 ≤4R 2 。
the invention also provides a vacuum pump, which comprises a pump body, wherein a pump cavity penetrating through the pump body is formed in the pump body, the cross section profile of the pump cavity is formed by overlapping two top circles with the same diameter, two rotating shafts are arranged in parallel at the centers of the two top circles on the cross section of the pump cavity, and the length direction of the rotating shafts is the same as the penetrating direction of the pump cavity; the two rotors are respectively fixed on the two rotating shafts, cover plates are formed at two ends of the pump cavity in the penetrating direction, shaft holes are formed in the positions, corresponding to the two rotating shafts, of the cover plates, and the rotating shafts are installed on the cover plates through the shaft holes; at least one cover plate is provided with a special-shaped exhaust hole, and an air inlet is formed on the side wall of the pump cavity.
Has the advantages that:
the technical scheme of the invention has the following beneficial effects: compared with the rotor molded line of the claw type pump used in the past, the rotor molded line of the claw type pump has the advantages of better meshing closure, higher gas conveying efficiency, high volume utilization rate, smooth connection of the whole section of curve, no other sharp corner points except the front claw tip, fewer stress concentration points and better mechanical property. Meanwhile, the compression cavities formed by the two rotors and the pump cavity are continuous, and compressed air can be discharged completely and smoothly through the exhaust port, so that the efficiency of the claw pump is improved.
Drawings
In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings that are required to be used in the embodiments will be briefly described below, it should be understood that the following drawings only illustrate some embodiments of the present invention and therefore should not be considered as limiting the scope, and for those skilled in the art, other related drawings can be obtained according to the drawings without inventive efforts.
FIG. 1 is a schematic view of a rotor profile and a matching structure of an air inlet and an air outlet of a single-claw type pump in the prior art;
FIG. 2 is a schematic view of the rotor of the single claw type vacuum pump according to the present invention;
FIG. 3 is a first view of the rotor assembly of the two single claw type vacuum pumps according to the present invention;
FIG. 4 is a schematic view of the rotor of the dual claw type vacuum pump according to the present invention;
FIG. 5 is a schematic view of a preferred single claw vacuum pump of the present invention;
FIG. 6 is a schematic structural diagram illustrating a stage of forming an air cavity of a vacuum pump according to an embodiment of the present invention;
FIG. 7 is a schematic structural diagram of an intake end stage of an air cavity A of a vacuum pump according to an embodiment of the present invention;
FIG. 8 is a schematic diagram of a compression stage of an air chamber A of a vacuum pump according to an embodiment of the present invention;
FIG. 9 is a first schematic view of an exhaust stage of a vacuum pump air chamber A according to a first embodiment of the present invention;
FIG. 10 is a schematic structural diagram of an exhaust stage of an air cavity A of a vacuum pump according to a first embodiment of the present invention;
FIG. 11 is a schematic structural diagram of an exhaust stage of an air cavity A of a vacuum pump according to a first embodiment of the present invention;
FIG. 12 is a fourth schematic view illustrating an exhaust stage of the vacuum pump air chamber A according to the first embodiment of the present invention;
FIG. 13 is a schematic view of a structure for completing the evacuation of the air chamber A of the vacuum pump in the first embodiment of the present invention;
FIG. 14 is a schematic diagram illustrating a stage of forming an air chamber of a vacuum pump according to a second embodiment of the present invention;
FIG. 15 is a schematic diagram of the structure of the air cavity of the vacuum pump in the second embodiment of the present invention at the compression stage;
FIG. 16 is a schematic diagram of a first stage of the air-cavity exhausting process of the vacuum pump according to the second embodiment of the present invention;
FIG. 17 is a schematic diagram of a second stage of the air chamber of the vacuum pump according to the second embodiment of the present invention.
Detailed Description
In order to make the objects, technical solutions and advantages of the embodiments of the present invention more apparent, the technical solutions of the embodiments of the present invention will be described clearly and completely with reference to the accompanying drawings of the embodiments of the present invention, and it is obvious that the described embodiments are some, but not all embodiments of the present invention. All other embodiments, which can be obtained by a person skilled in the art without any inventive step based on the embodiments of the present invention, are within the scope of the present invention. Thus, the following detailed description of the embodiments of the present invention, presented in the figures, is not intended to limit the scope of the invention, as claimed, but is merely representative of selected embodiments of the invention.
As shown in fig. 2 to 4, a claw vacuum pump rotor, wherein the rotor comprises a pitch circle 41 and claws 42, and the linear shape of the claws 42 is formed by seven curves connected end to end: long amplitude epicycloid A of front claw tip 1 A 2 Arc section A at the bottom of the claw 2 A 3 A transition arc section A 3 A 4 Arc section A of tip of bottom claw 4 A 5 Conjugate curve A of arc segment of tip of bottom claw 6 A 7 Conjugate curve A of transition circular arc section 7 A 8 Arc segment A of the top of the claw 8 A 1 The line type of the pitch circle is a pitch circle arc section A 5 A 6 The claw is connected with the molded line of the pitch circle end to end, and two adjacent sections of circular arcs are in smooth transition;
and the radius of the claw top arc section of the rotor molded line is R 1 The radius of the arc section at the bottom of the claw is R 2 The radius of the pitch circle is R 0 ：
At the center O of the pitch circle 1 As dots, with O 1 A 2 The straight line is used as the X axis to form a coordinate system XO 1 In Y, the long-amplitude epicycloid A of the front claw tip 1 A 2 At any point on
The following formula is satisfied:
arc segment A at the bottom of the claw 2 A 3 At any point on
The following formula is satisfied:
，
wherein R is 2 Is the radius of the bottom circle of the claw,
is A 2 A 3 The central angle corresponding to the curve is a designable variable;
transition arc section A 3 A 4 At any point on
The following formula is satisfied:
wherein R is 3 Is a designable variable with a value range of
；
Is A 3 A 4 The central angle of the circle corresponding to the curve,
；
arc segment A of bottom claw tip 4 A 5 At any point on
The following formula is satisfied:
wherein R is 4 Derived from known variables, i.e.
。 
Is A 4 A 5 The arc angle corresponding to the curve is formed,
；
conjugate curve A of arc segment of bottom claw tip 6 A 7 At any point on
The following formula is satisfied:
wherein:
；
wherein x is 1 And y 1 Is A 6 A 7 Curve in static coordinate system X 1 O 1 Y 1 Coordinate of lower, x 2 And y 2 Is A 6 A 7 Curve in static coordinate system X 2 O 2 Y 2 Coordinates of the following, and
and
is A 6 A 7 Curve in moving coordinate system XO 1 The coordinates under Y are given by the coordinates of,
is A 6 A 7 Curve in moving coordinate system XO 1 Angle of parameters under Y, moving coordinate system XO 1 Y is lower than A 6 A 7 Coordinates of the curve, i.e. A 6 A 7 A parametric equation for the curve;
wherein, the moving coordinate system XO 1 Y is rotor O 1 A coordinate system which takes the circle center as an origin and rotates along with the rotation of the rotor; x 1 O 1 Y 1 、X 2 O 2 Y 2 Respectively is a rotor O 1 Center of circle and rotor O 2 The circle center is a static coordinate system of the origin, the Y-axis directions of the two static coordinate systems are the same, the X-axis directions are opposite, and the X-axis directions of the two static coordinate systems are opposite 1 O 1 Y 1 In the X-axis direction of the driven rotor O 1 Circle center to rotor O 2 Circle center direction, stationary coordinate system X 2 O 2 Y 2 In the X-axis direction of the driven rotor O 2 Circle center to rotor O 1 The direction of the circle center;
conjugate curve A of transition arc segment 7 A 8 At any point on
The following formula is satisfied:
wherein,
wherein x is 3 And y 3 Is A 7 A 8 Curve in static coordinate system X 1 O 1 Y 1 Coordinate of lower, x 4 And y 4 Is A 7 A 8 Curve in static coordinate system X 2 O 2 Y 2 Coordinates of the lower, and
and
is A 7 A 8 Curve in moving coordinate system XO 1 The coordinates under Y are given by the coordinates of,
is A 7 A 8 Curve in moving coordinate system XO 1 Angle of parameters under Y, moving coordinate system XO 1 Y is lower than A 7 A 8 The coordinates of the curveIs A 7 A 8 A parametric equation of the curve;
arc section A of claw top 8 A 1 At any point on
The following formula is satisfied:
。
as a preferred embodiment, the rotor is a single claw, one claw profile is connected with the profile of the pitch circle end to end, and the pitch circle arc segment a is a single claw 5 A 6 At any point on
The following formula is satisfied:
。
in a preferred embodiment, the rotor is a double claw, and the pitch circle arc segment a 5 A 6 At any point on
The following formula is satisfied:
In a preferred embodiment, the rotor is a three-jaw rotor, and the pitch circle arc segment a 5 A 6 At any point on
The following formula is satisfied:
，
three claw molded lines are respectively connected with the molded line pitch circle arc segment A of the pitch circle 5 A 6 The upper three arc sections are connected end to end.
Here, A 3 A 4 The curve corresponds to a central angle of
，A 4 A 5 The curve corresponds to a central angle of
，A 6 A 7 The curve corresponds to a central angle of
，A 7 A 8 The curve corresponds to a central angle of
. Wherein, A 3 A 4 And A 7 A 8 The curves being conjugate curves of each other, A 4 A 5 And A 6 A 7 The curves are conjugate curves, then
And
the angles of the two angles are conjugate angles with each other,
and
are conjugate angles to each other. From curve A 3 A 4 And
a unique conjugate angle can be determined
Similarly, curve A 4 A 5 And
a unique conjugate angle can be determined
. Further, the four central angles have the following relationship:
。
as a preferred embodiment, the radius R of the claw-tip arc segment of the rotor profile is 1 Radius R of arc segment at bottom of claw 2 Satisfies the following conditions:
1.5R 2 ≤R 1 ≤4R 2 。
the radius R of the claw top arc section of the rotor profile is determined 1 Is controlled in the radius R of the arc segment at the bottom of the claw 2 1.5-4 times of the working efficiency of the vacuum pump in the range, and the working efficiency of the vacuum pump can reach a higher level.
The embodiment also provides a vacuum pump, which comprises a pump body 1, wherein a pump cavity 2 penetrating through the pump body 1 is formed in the pump body 1, the cross section profile of the pump cavity 2 is formed by overlapping two top circles with the same diameter, two rotating shafts 3 are arranged in parallel at the circle centers of the two top circles on the cross section of the pump cavity 2, and the length direction of each rotating shaft 3 is the same as the penetrating direction of the pump cavity 2; the two rotors 4 are respectively fixed on the two rotating shafts 3, cover plates (not shown in the figure) are formed at two end parts of the pump cavity 2 in the penetrating direction, shaft holes are formed in the positions, corresponding to the two rotating shafts 3, of the cover plates, and the rotating shafts 3 are installed on the cover plates through the shaft holes; at least one cover plate is provided with a special-shaped exhaust hole 11, and the side wall of the pump cavity is provided with an air inlet 12.
The rotor profile has good meshing closure, high conveying efficiency for compressed gas, high volume utilization rate, smooth connection of the whole section of curve, elimination of two acute angle points except the front claw tip, fewer stress concentration points and good stress performance; meanwhile, the compression cavities formed by the two rotors are continuous, compressed gas can be discharged completely and smoothly through the exhaust port, and the efficiency of the claw pump is improved.
Here, the radius R of the arc segment of the claw top is taken 1 =120, radius of arc segment of claw bottom R 2 =40, radius of pitch circle R 0 =80. The variable α =10 ° is designed to obtain the single-claw rotor profile shown in fig. 5 and the double-claw rotor profile shown in fig. 14, and the pressure delivery process of the claw pump rotor to the gas will be described by taking the single-claw rotor profile shown in fig. 5 and the double-claw rotor profile shown in fig. 14 as an example.
The first embodiment is as follows:
the initial position of the single-claw rotor is in the "hugging" position of the two rotors as shown in fig. 5, the front claw tips of the two rotors being respectively located on the claw base circles of the other rotor, and then O 1 The rotor rotates counterclockwise O 2 The rotor rotates clockwise.
With rotation of the rotor, O 2 Front claw tip of rotor is at O 1 A of the rotor 1 A 2 The curves are meshed to form two parts of air cavities, namely an air cavity A and an air cavity B; as shown in fig. 6, the front claw tips of the two rotors rotate to be meshed with the claw top circle, the air cavity a ends the air inlet process, and the air cavity B starts air inlet; as shown in fig. 7, the air chamber a finishes the air intake process, starts to compress air, and continues to intake air.
As shown in fig. 8, the air chamber a is compressed, i.e. will communicate with the air outlet, and the air chamber B continues to intake air. When the claw pump rotors are rotated to the position shown in figure 10, the air chamber a is between the two rotors. O is 1 Front claw tip and O of rotor 2 A of the rotor 1 A 2 Forming a first meshing point, O, on the cycloid 1 A of the rotor 6 A 7 Curve and O 2 A of the rotor 4 A 5 The curve forms a second meshing point, and a compression cavity formed by the two meshing points compresses the gas and discharges the gas from the gas outlet. When the claw pump rotor rotates from the position shown in fig. 9 to the position shown in fig. 10, two meshing points of the two rotors gradually approach each other, and a compression chamber formed between the two meshing points compresses gas and discharges the gas from the gas discharge port.
When the claw pump rotor is rotated to the position shown in fig. 11, the compression chamber is always connected to the exhaust port to ensure gas discharge while being close to O 1 A of the rotor 8 A 1 Curve and O 2 A of the rotor 2 A 3 The area of the second meshing point formed by the curve decreases rapidly and approaches O 1 Front claw tip and O of rotor 2 A of the rotor 1 A 2 The area reduction speed of the first meshing point side formed on the cycloid is slow, and the first meshing point side is always connected with the exhaust port, so that the compressed gas can be discharged through the exhaust port, and the gas pressurization conveying process can be efficiently finished.
When the claw pump rotor rotates to the position of fig. 12, the second mesh point stops at O 2 The second meshing point has not yet reached the end point, the compression chamber is still in communication with the exhaust port, and the gas is still being delivered. When the claw pump rotors rotate to the position of fig. 13, the compression chamber between the two rotors disappears, the gas conveying process is finished, and the next cycle of the gas pressurized conveying process is started.
The second embodiment:
as shown in fig. 14 to 17, for the double claw rotor, the rotation meshing process is substantially the same as that of the single claw rotor, but the meshing process of the double claw rotor is performed in a cycle in which the rotor rotates through 180 °, and the pressurized feed process of the cycle and the intake process of the next cycle are performed in one cycle.
The initial position of the rotors is in the "hugging" position of the two rotors as shown in fig. 14, the front tips of the two rotors being respectively on the jaw base circle of the other rotor, and then O 1 The rotor rotates counterclockwise O 2 The rotor rotates clockwise.
As the rotors rotate, the two rotors gradually compress the air chambers of the hatched portions, as shown in fig. 15.
As shown in fig. 16, the compressed air chamber communicates with the exhaust port, and the compressed air starts to be discharged through the exhaust port.
As shown in fig. 17, two meshing points formed by the two rotors are gradually closed to continuously compress the air cavity, so that the compressed air can be discharged through the exhaust port, and the air pressurization conveying process is efficiently completed.
Subsequently, the compression chamber between the two rotors disappears, the gas delivery process ends, and the next cycle of the gas pressurized delivery process begins.
The above description is only a preferred embodiment of the present invention, and is not intended to limit the present invention, and various modifications and changes may be made to the present invention by those skilled in the art. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (6)
1. A claw type vacuum pump rotor is characterized by comprising a pitch circle and claws, wherein the claws are in a line shape formed by seven curves connected end to end: long-amplitude epicycloid A of front claw tip 1 A 2 Arc section A at the bottom of the claw 2 A 3 A transition arc section A 3 A 4 Arc section A of bottom claw tip 4 A 5 Conjugate curve A of arc segment of tip of bottom claw 6 A 7 Conjugate curve A of transition circular arc section 7 A 8 Arc segment A of the top of the claw 8 A 1 The line type of the pitch circle is a pitch circle arc section A 5 A 6 The claw is connected with the molded line of the pitch circle end to end, and two adjacent sections of circular arcs are in smooth transition;
and the radius of the claw top arc section of the rotor profile is R 1 The radius of the arc section at the bottom of the claw is R 2 The radius of the pitch circle is R 0 ：
At the center O of the pitch circle 1 As dots, with O 1 A 2 The straight line is used as the X axis to form a coordinate system XO 1 Y middle, front claw tip long amplitude epicycloid A 1 A 2 At any point on
The following formula is satisfied:
arc segment A of claw bottom 2 A 3 At any point on
The following formula is satisfied:
wherein R is 2 Is the radius of the bottom circle of the claw,
is A 2 A 3 The central angle corresponding to the curve is a designable variable;
transition arc segment A 3 A 4 At any point on
The following formula is satisfied:
wherein R is 3 Is a designable variable with a value range of [ R 0 -R 2 ，
]；
Is A 3 A 4 The central angle of the circle corresponding to the curve,
；
arc segment A of bottom claw tip 4 A 5 At any point on
The following formula is satisfied:
wherein R is 4 Derived from known variables, i.e.
，
Is A 4 A 5 The arc angle corresponding to the curve is formed,
；
conjugate curve A of arc segment of bottom claw tip 6 A 7 At any point on
The following formula is satisfied:
wherein:
wherein x is 1 And y 1 Is A 6 A 7 Curve in static coordinate system X 1 O 1 Y 1 Coordinate of lower, x 2 And y 2 Is A 6 A 7 Curve in static coordinate system X 2 O 2 Y 2 Coordinates of the following, and
and
is A 6 A 7 Curve in moving coordinate system XO 1 The coordinates under the Y-coordinate system of the coordinate system,
is A 6 A 7 Curve in moving coordinate system XO 1 Angle of parameters under Y, moving coordinate system XO 1 Y is lower than A 6 A 7 Coordinates of the curve, i.e. A 6 A 7 A parametric equation for the curve;
wherein, the moving coordinate system XO 1 Y is rotor O 1 A coordinate system with the center of the circle as the origin and rotating along with the rotation of the rotor; x 1 O 1 Y 1 、X 2 O 2 Y 2 Respectively is a rotor O 1 Center of circle and rotor O 2 The circle center is a static coordinate system of the origin, the Y-axis directions of the two static coordinate systems are the same, the X-axis directions are opposite, and the X-axis directions of the two static coordinate systems are opposite 1 O 1 Y 1 In the X-axis direction of the driven rotor O 1 Circle center to rotor O 2 Circle center direction, stationary coordinate system X 2 O 2 Y 2 In the X-axis direction of the driven rotor O 2 Circle center to rotor O 1 The direction of the circle center;
conjugate curve A of transition arc segment 7 A 8 At any point on
The following formula is satisfied:
wherein,
wherein x is 3 And y 3 Is A 7 A 8 Curve in static coordinate system X 1 O 1 Y 1 Coordinate of lower, x 4 And y 4 Is A 7 A 8 Curve in static coordinate system X 2 O 2 Y 2 Coordinates of the lower, and
and
is A 7 A 8 Curve in moving coordinate system XO 1 The coordinates under Y are given by the coordinates of,
is A 7 A 8 Curve in moving coordinate system XO 1 Angle of parameters under Y, moving coordinate system XO 1 Y is lower than A 7 A 8 Coordinates of the curve, i.e. A 7 A 8 A parametric equation for the curve;
arc section A of claw top 8 A 1 At any point on
The following formula is satisfied:
2. a claw vacuum pump rotor as claimed in claim 1, wherein said rotor is a single claw, one of said claw profiles being connected end to end with said pitch circle profile, said pitch circle segment beingA 5 A 6 At any point on
The following formula is satisfied:
。
3. a claw vacuum pump rotor as claimed in claim 1, wherein said rotor is a double claw, said pitch circle segment a 5 A 6 At any point on
The following formula is satisfied:
，
4. A claw vacuum pump rotor as claimed in claim 1, wherein said rotor is a three-claw, said pitch circle segment a 5 A 6 At any point on
The following formula is satisfied:
three claw molded lines are respectively connected with the molded line pitch circle arc segment A of the pitch circle 5 A 6 The upper three arc sections are connected end to end.
5. According to claim 1The claw type vacuum pump rotor is characterized in that the radius R of the claw top arc section of the rotor profile 1 Radius R of arc segment at bottom of claw 2 Satisfies the following conditions:
1.5R 2 ≤R 1 ≤4R 2 。
6. a vacuum pump is characterized by comprising a pump body, wherein a pump cavity penetrating through the pump body is formed in the pump body, the cross section profile of the pump cavity is formed by overlapping two top circles with the same diameter, two rotating shafts are arranged in parallel at the centers of the two top circles on the cross section of the pump cavity, and the length direction of each rotating shaft is the same as the penetrating direction of the pump cavity; two rotors according to any one of claims 1 to 5, respectively fixed to the two rotary shafts, cover plates formed at both ends of the pump chamber in a penetrating direction, shaft holes formed in the cover plates at positions corresponding to the two rotary shafts, and the rotary shafts mounted to the cover plates through the shaft holes; at least one cover plate is provided with a special-shaped exhaust hole, and an air inlet is formed on the side wall of the pump cavity.
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| CN202211566339.9A CN115559901B (en) | 2022-12-07 | 2022-12-07 | Claw type vacuum pump rotor and vacuum pump |
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| CN202211566339.9A CN115559901B (en) | 2022-12-07 | 2022-12-07 | Claw type vacuum pump rotor and vacuum pump |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN117150686A (en) * | 2023-10-30 | 2023-12-01 | 上海盛剑半导体科技有限公司 | Claw type rotor, end surface molded line drawing method and vacuum pump |
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