CN110285051B - Synchronous inner-meshing double-rotor structure and rotor pump based on same - Google Patents
Synchronous inner-meshing double-rotor structure and rotor pump based on same Download PDFInfo
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- CN110285051B CN110285051B CN201910587227.3A CN201910587227A CN110285051B CN 110285051 B CN110285051 B CN 110285051B CN 201910587227 A CN201910587227 A CN 201910587227A CN 110285051 B CN110285051 B CN 110285051B
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- 230000001360 synchronised effect Effects 0.000 title claims abstract description 90
- 239000012530 fluid Substances 0.000 claims abstract description 49
- 238000000034 method Methods 0.000 claims abstract description 30
- PEDCQBHIVMGVHV-UHFFFAOYSA-N Glycerine Chemical compound OCC(O)CO PEDCQBHIVMGVHV-UHFFFAOYSA-N 0.000 claims description 10
- 238000005192 partition Methods 0.000 claims description 5
- 238000007599 discharging Methods 0.000 claims description 3
- 239000007788 liquid Substances 0.000 claims description 3
- 230000002093 peripheral effect Effects 0.000 claims description 2
- 238000007789 sealing Methods 0.000 abstract description 4
- 238000006243 chemical reaction Methods 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000009977 dual effect Effects 0.000 description 1
- 230000037361 pathway Effects 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
- 238000004804 winding Methods 0.000 description 1
Classifications
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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
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
- F04C2/101—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with a crescent-shaped filler element, located between the inner and outer intermeshing members
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- General Engineering & Computer Science (AREA)
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Abstract
A synchronous inner-meshing double-rotor structure and a rotor pump based on the same. The invention provides a synchronous inner-meshing double-rotor structure and a rotor pump based on the same, and relates to the technical field of rotor pumps. The synchronous internal-meshing double-rotor structure is characterized in that the two rotors are respectively provided with a TC unit structure consisting of C-shaped plates and T-shaped plates, the TC units of the two rotors are arranged at intervals and are connected front and back to form a TC unit encircling combination, the T-shaped plate month plate of each rotor is positioned in the C-shaped plate of the other rotor in front and meshed with each other, and in the synchronous rotation process of the two rotors, each pair of meshed C-shaped plates and T-shaped plates drive fluid to flow into the TC unit encircling combination from the TC unit encircling combination or flow into the TC unit encircling combination from the TC unit. Compared with the existing rotor pump, the rotor pump based on the structure is better in sealing performance and simpler in structure.
Description
Technical Field
The invention relates to the technical field of fluid pumps, in particular to a rotor pump.
Background
Currently, fluid pumps in widespread use are mainly of the piston and turbine types. The piston type fluid pump has good sealing performance, can bear high pressure difference and has high functional conversion efficiency, but adopts an opening and closing valve to lead the structure to be complex, the reciprocating motion generates vibration, and the friction force exists between the piston and the cylinder wall. The turbine type fluid pump has a simple structure and a centrosymmetric structure with high-speed rotation stability, but the function conversion efficiency is reduced under the condition of overhigh pressure difference, and the turbine type fluid pump cannot be applied to the aspects of hydraulic output of high pressure difference and the like.
Accordingly, the skilled artisan is continually striving to invent a rotor pump having the advantages of both types described above, but many practical problems exist with existing inventive designs. Such as cam rotor pumps and internal gear pumps, have poor sealing properties, complex structures and low efficiency, and cannot be widely applied.
Disclosure of Invention
The invention aims to provide a synchronous inner-meshing double-rotor structure and a rotor pump based on the same, so as to solve the practical application problem of the existing rotor pump.
The invention provides a synchronous inner-meshing double-rotor structure for a rotor pump, which comprises an active rotor and a passive rotor, wherein the active rotor shaft and the passive rotor shaft are parallel, the wheelbase d is more than 0 (hereinafter, the wheelbase of the double rotors is uniformly referred to as a double-rotor wheelbase), and the two rotors are in inner meshing and synchronous in the process of rotating around the respective rotor shafts.
The synchronous inner-meshing double rotors are provided with bent plate structures with the shape of letter C, hereinafter referred to as C-shaped plates, one ends of the baffle plates are connected to concave surfaces of the moon plate to form structures with the shape of letter T, hereinafter referred to as T-shaped plates, the other ends of the baffle plates of one T-shaped plate are connected to the outer wall of one C-shaped plate, the two plates form a basic structural unit of the synchronous inner-meshing double rotors, hereinafter referred to as TC units, and the TC units are fixedly connected to respective rotor shafts.
On the synchronous inner-meshed double rotors, one or more TC units are respectively arranged on the driving rotor and the driven rotor, the number of the TC units is the same, the T-shaped plates on the TC units are used as front C-shaped plates and are used as positive directions, and then all the TC units form a surrounding combination on a rotating plane along the clockwise or anticlockwise direction, and the surrounding combination is hereinafter called TC unit surrounding combination. The TC unit annular windings are closed, the TC units of the driving rotors and the TC units of the driven rotors are arranged at intervals, the T-shaped plate moon plate of each driving rotor is positioned in the C-shaped plate of the front driven rotor and meshed with each other, and the T-shaped plate moon plate of each driven rotor is positioned in the C-shaped plate of the front driving rotor and meshed with each other.
The synchronous inner-meshed double rotors are characterized in that the curved surfaces sigma （C） of the inner walls of the C-shaped plates and the curved surfaces sigma (T) of the inner moon plates of the T-shaped plates relative to the inner walls of the C-shaped plates are a pair of conjugate tooth surfaces, namely conjugate curved surfaces, on each pair of the C-shaped plates and the T-shaped plates which are meshed with each other. The pair of conjugate curved surfaces Σ （C） and Σ (T) satisfies the following engagement relationship and shape condition: in the meshing process, the common normal line of the conjugate curved surfaces sigma （C） and sigma (T) at the meshing point is parallel to the central connecting line of the double rotors, and the curvature radius of the conjugate curved surface sigma （C） at the meshing point is equal to the sum of the curvature radius of the conjugate curved surface sigma (T) and the distance d between the double rotors; the tangent line at the end point of each curved surface moves to the other end point of the curved surface, the tangent line is always at one side of the curved surface and the tangent line deflects 360 degrees.
During rotation of the synchronous inner-meshing double rotors, except for the tangential contact of the conjugate curved surfaces sigma （C） and sigma (T), the other surfaces of each pair of the mutually-meshed C-shaped plates and the T-shaped plates are not in contact with the other surfaces of the T-shaped plates in the synchronous inner-meshing double rotors, and a fluid channel between the conjugate curved surfaces sigma （C） and sigma (T) is reserved.
In the process of rotating the synchronous inner-meshing double rotor along a certain direction, the conjugate curved surfaces sigma （C） and sigma (T) of each pair of mutually meshed C-shaped plates and T-shaped plates take the two curved surface end points overlapped at the initial meshing point as two front conjugate end points, and the other two curved surface end points overlapped at the final meshing point as two rear conjugate end points, and as known from the meshing relationship and the shape conditions of the conjugate curved surfaces sigma （C） and sigma (T), the two rear conjugate end points of the conjugate curved surfaces sigma （C） and sigma (T) are overlapped when the last meshing process is ended, the two front conjugate end points are overlapped at the same time, the next meshing process is started, and the conjugate curved surfaces sigma （C） and sigma (T) are kept meshed at any time, namely the C-shaped plates and the T-shaped plates of each pair of mutually meshed are kept meshed at any time.
In the process of rotating the synchronous inner-meshing double rotor in a certain direction, conjugate curved surfaces sigma （C） and sigma (T) on each pair of mutually meshed C-shaped plates and T-shaped plates start to mesh and continue, two front conjugate end points are separated, the meshing parts on the two conjugate curved surfaces are increased, the volume between the meshing parts on the two conjugate curved surfaces is increased to suck fluid, the two rear conjugate end points are separated, the non-meshing parts on the two conjugate curved surfaces are reduced, the volume between the non-meshing parts on the two conjugate curved surfaces is reduced to discharge fluid, and the conjugate curved surfaces sigma （C） and sigma (T) finish the one-time meshing process, and meanwhile finish the fluid sucking process and the fluid discharging process.
In the process of rotating the synchronous inner-meshing double rotors along a certain direction, as known from the synchronous inner-meshing relationship and the relative motion principle of the double rotors, in the synchronous inner-meshing double rotors, each rotor moves horizontally along a circle with a radius d relative to the other rotor and is opposite to the rotating direction of the double rotors along the circle, further, in each pair of mutually meshed C-shaped plates and T-shaped plates, the T-shaped plates move horizontally along the circle with the radius d relative to the C-shaped plates and are opposite to the rotating direction of the double rotors, if the rotating direction of the double rotors is the same as the encircling direction of the TC units (the front C-shaped plate on the TC units is the rear C-shaped plate as the positive direction), each pair of mutually meshed C-shaped plates and T-shaped plates start to mesh from one end of the TC unit encircling combination, driving fluid flows into the TC unit encircling combination from the outside, and if the rotating direction of the double rotors is opposite to the encircling direction of the TC unit, the mutually meshed C-shaped plates and the T-shaped plates start to mesh from one end of the TC unit encircling combination.
The invention provides a synchronous inner-meshing double-rotor pump, which comprises a cylindrical pump chamber and a synchronous inner-meshing double-rotor structure, wherein a driven rotor of the synchronous inner-meshing double-rotor is arranged on a fixed shaft at the inner bottom surface and the outer bottom surface of the pump chamber through a bearing, a driving rotor shaft of the synchronous inner-meshing double-rotor is arranged at the inner bottom surface and extends out of the pump chamber through a bearing, and the cylindrical pump chamber is respectively provided with a fluid port in the center and the outer periphery of a TC unit surrounding combination separation.
The synchronous internal meshing double-rotor pump can drive fluid to enter from one port and flow out from the other port by rotating the driving rotor shaft.
The invention provides an eccentric rotor pump based on an improved structure of a synchronous inner-gearing double rotor, which comprises a cylindrical pump chamber, a stator and an eccentric rotor, wherein the stator is equivalent to fixing a TC unit of a driving rotor of the synchronous inner-gearing double rotor between two bottom surfaces in the pump chamber, the axis of the driving rotor is the axis of the stator, the eccentric rotor is equivalent to mounting a driven rotor of the synchronous inner-gearing double rotor on an eccentric shaft through a bearing, the eccentric distance of the eccentric shaft is equivalent to the axial distance d of the synchronous inner-gearing double rotor, the rotation axis of the eccentric shaft is collinear with the axis of the stator, the rotation shaft of the eccentric shaft is mounted on the bottom surface of the cylindrical pump chamber through the bearing and extends out of the pump chamber, and the cylindrical pump chamber is respectively provided with a fluid port in the center and the peripheral two areas of the TC unit which are circumferentially separated.
In the above-mentioned synchronous inner-gearing double rotors, the driven rotor and the driving rotor are in circular translation along the radius d, and it is known that in the above-mentioned eccentric rotor pump, the relative motion relationship between the eccentric rotor and the stator is identical to the relative motion relationship between the two rotors in the above-mentioned synchronous inner-gearing double rotors, i.e. the engagement relationship between the eccentric rotor and the stator is identical to the engagement relationship between the two rotors in the above-mentioned synchronous inner-gearing double rotors.
The eccentric rotor pump rotates the rotating shaft of the eccentric shaft, so that fluid can be driven to enter from one port and flow out from the other port.
The synchronous inner gearing double rotor structure, the synchronous inner gearing double rotor pump and the eccentric rotor pump can be used as devices driven by power to convey gas and liquid and can also be used as devices driven by liquid and gas to output power.
Compared with the existing rotor pump, the invention has the beneficial effects that: (1) Compared with the existing rotor pumps such as a cam rotor pump and a crescent gear pump, the invention has better sealing performance. If the cam rotor pump is used for driving fluid by keeping sliding contact between the two cams except the mutual engagement between the two cams, the internal gear pump is used for driving fluid by keeping sliding contact between the two gears except the mutual engagement between the two gears. The synchronous inner-meshing double-rotor structure can drive fluid only by mutual meshing of the two rotors; (2) Compared with the existing rotor pumps such as cam rotor pumps and internal gear pumps, the invention has simpler structure. For example, two cams of a cam rotor pump can be meshed by external two-gear driving, and an internal gear pump can be driven by cooperation of tooth plates besides the meshing of two gears. The synchronous inner-meshing double-rotor structure can drive fluid by mutual meshing of the two rotors without other structure cooperation.
Drawings
The drawings used in the preferred embodiments of the present invention are for further understanding of the technical aspects of the present invention and are not to be construed as unduly limiting the present invention, and the drawings used in the preferred embodiments of the present invention are presented in brief.
Fig. 1 is a schematic view of a synchronous inner gearing dual rotor structure according to a first preferred embodiment of the present invention.
Fig. 2 is a schematic diagram showing the internal structure of a synchronous internal-gearing double rotor pump according to a second preferred embodiment of the present invention.
Fig. 3 is an external view of a synchronous ring gear twin rotor pump according to a second preferred embodiment of the present invention.
Fig. 4 is a schematic view showing an internal structure of an eccentric rotor pump according to a third preferred embodiment of the present invention.
Fig. 5 is an external view of an eccentric rotor pump according to a third preferred embodiment of the present invention.
Reference numerals illustrate: 1-a driving rotor; 2-a passive rotor; 3.7, 9, 11-C templates; 4-a separator; 5-month plate; 6. 8, 10, 12-T templates; 13-synchronous internal engaged twin-rotor pump chamber; 14—passive rotor fixed shaft; 15-an active rotor shaft; 16-a fluid inlet; 17-fluid outlet; 18-eccentric rotor pump chamber; 19-a stator; 20-eccentric rotor; 21-an eccentric shaft; 22-a rotation axis; 23-fluid inlet; 24-fluid outlet.
Detailed Description
The preferred embodiments of the present invention are used for clearly and completely describing the technical solution of the present invention, and are not the only embodiments of the present invention.
According to a first preferred embodiment of the present invention.
Fig. 1 is a schematic view of a synchronous inner-meshing double-rotor structure according to a first preferred embodiment of the present invention, as shown in fig. 1, the present embodiment provides a synchronous inner-meshing double-rotor structure for a rotor pump, which includes a driving rotor 1 and a driven rotor 2, the driving rotor 1 and the driven rotor 2 are parallel in axis and have an axial distance d >0 (hereinafter, collectively referred to as double-rotor axial distance), and the driving rotor 1 and the driven rotor 2 are inner-meshed and synchronous during a counterclockwise rotation about their respective rotor axes.
On the synchronous inner gearing double rotor shown in fig. 1, a C-shaped plate 3 with a shape like a letter C is arranged, one end of a partition plate 4 is connected with the concave surface of a moon plate 5 to form a T-shaped plate 6 with a shape like a letter T, the other end of the partition plate 4 is connected with the outer wall of the C-shaped plate 3, and the C-shaped plate 3 and the T-shaped plate 6 form a basic structural unit of the synchronous inner gearing double rotor structure, hereinafter referred to as a TC unit. The TC units are fixedly connected to the respective rotor shafts.
On the synchronous inner gearing double rotors shown in fig. 1, two TC units are respectively arranged on the active rotor 1 and the passive rotor 2, a T-shaped plate on the TC units is used as a front C-shaped plate and is used as a rear positive direction, and then all TC units form a surrounding combination along a counterclockwise direction on a rotation plane, and hereinafter referred to as TC unit surrounding combination. The TC units are circularly wound, TC units of the driving rotor 1 and TC units of the driven rotor 2 are arranged at intervals, moon plates of T-shaped plates 8 and 12 of the driving rotor 1 are respectively positioned in C-shaped plates 9 and 3 of the front driven rotor 2 and meshed with each other, and moon plates of T-shaped plates 6 and 10 of the driven rotor 2 are respectively positioned in C-shaped plates 7 and 11 of the front driving rotor 1 and meshed with each other.
The synchronous inner gearing double rotor shown in fig. 1, on each pair of the mutually engaged C-shaped plate and T-shaped plate, the curved surface Σ （C） of the inner wall of the C-shaped plate and the curved surface Σ (T) of the inner wall of the T-shaped plate opposite to the inner wall of the C-shaped plate are a pair of conjugate tooth surfaces, namely conjugate curved surfaces. The pair of conjugate curved surfaces Σ （C） and Σ (T) satisfies the following engagement relationship and shape condition: in the meshing process, the common normal line of the conjugate curved surfaces sigma （C） and sigma (T) at the meshing point is parallel to the central connecting line of the double rotors, and the curvature radius of the conjugate curved surface sigma （C） at the meshing point is equal to the sum of the curvature radius of the conjugate curved surface sigma (T) and the distance d between the double rotors; the tangent line at the end point of each curved surface moves to the other end point of the curved surface, the tangent line is always at one side of the curved surface and the tangent line deflects 360 degrees.
During counter-clockwise rotation of the synchronous intermeshing double rotors shown in FIG. 1, each pair of intermeshing C-shaped plates and T-shaped plates, except for the conjugate curved surfaces Sigma （C） and Sigma (T), are in tangential contact, the remaining faces of the C-shaped plates do not contact the remaining faces of the T-shaped plates therein and leave fluid pathways between the conjugate curved surfaces Sigma （C） and Sigma (T).
In the counterclockwise rotation process of the synchronous inner-meshing double rotor shown in fig. 1, the two curved surface endpoints of the initial meshing point are two front conjugated endpoints, the other two curved surface endpoints of the final meshing point are two rear conjugated endpoints, and as known from the meshing relationship and the shape conditions of the conjugated curved surfaces Σ （C） and Σ (T), the two rear conjugated endpoints of the conjugated curved surfaces Σ （C） and Σ (T) are coincident when the last meshing process is terminated, the two front conjugated endpoints are coincident and the next meshing process is started, and the conjugated curved surfaces Σ （C） and Σ (T) are kept in meshing at any moment, namely, the meshing of each pair of the intermeshing C-shaped plates and the T-shaped plates is kept at any moment.
During counter-clockwise rotation of the synchronous internally-toothed double rotor shown in fig. 1, the conjugate curved surfaces Σ （C） and Σ (T) on each pair of intermeshed C-shaped plates and T-shaped plates initially mesh and continue, so that the two front conjugate end points are separated, the meshing portions on the two conjugate curved surfaces are increased, the volume between the meshing portions on the two conjugate curved surfaces is increased to suck fluid, the two rear conjugate end points are separated, the non-meshing portions on the two conjugate curved surfaces are reduced, the volume between the non-meshing portions on the two conjugate curved surfaces is reduced to discharge fluid, and the conjugate curved surfaces Σ （C） and Σ (T) complete the one-time meshing process, and simultaneously complete the fluid sucking process and the fluid discharging process.
In the process of anticlockwise rotation of the synchronous inner-meshing double rotors shown in fig. 1, as known from the synchronous inner-meshing relationship and the relative motion principle of the double rotors, in the synchronous inner-meshing double rotors shown in fig. 1, each rotor translates clockwise along a circle with a radius d relative to the other rotor, and further, in each pair of intermeshing C-shaped plates and T-shaped plates, the T-shaped plates translate clockwise along the circle with the radius d relative to the C-shaped plates, the rotation direction of the synchronous inner-meshing double rotors shown in fig. 1 is the same as the encircling direction of the TC unit (taking the T-shaped plate on the TC unit as the front C-shaped plate and then as the positive direction), and each pair of intermeshing C-shaped plates and T-shaped plates are engaged from one end of the two in the encircling combination of the TC unit, so that driving fluid flows into the TC unit encircling combination. The dashed arrows shown in fig. 1 indicate the flow direction of the fluid relative to the C-plate.
A second preferred embodiment of the present invention.
Fig. 2 is a schematic view showing an internal structure of a synchronous ring gear twin-rotor pump according to a second preferred embodiment of the present invention, and fig. 3 is an external view of the synchronous ring gear twin-rotor pump according to the second preferred embodiment of the present invention. As shown in fig. 2 and 3, the present embodiment provides a rotor pump based on a synchronous inner-gearing double-rotor structure, which comprises a cylindrical pump chamber 13 and a synchronous inner-gearing double-rotor structure, wherein the passive rotor of the synchronous inner-gearing double-rotor is mounted on a fixed shaft 14 at the inner bottom surface and the outer bottom surface of the pump chamber through a bearing, a driving rotor shaft 15 is mounted at the inner upper bottom surface of the pump chamber through a bearing and extends out of the pump chamber, and the cylindrical pump chamber is respectively provided with a fluid inlet 16 and a fluid outlet 17 at the center and the outer periphery of the TC unit, which are divided around the combination.
The synchronous, internally meshed, twin rotor pump shown in fig. 2, rotates the active rotor shaft 15 counter-clockwise to drive fluid from the inlet 16 into and out of the outlet 17.
A third preferred embodiment of the present invention.
Fig. 4 is a schematic view showing an internal structure of an eccentric rotor pump according to a third preferred embodiment of the present invention, and fig. 5 is an external view of the eccentric rotor pump according to the third preferred embodiment of the present invention. As shown in fig. 4 and 5, this embodiment provides an improved eccentric rotor pump based on a synchronous inner-gearing double-rotor structure, which comprises a cylindrical pump chamber 18, a stator 19 and an eccentric rotor 20, wherein the stator 19 is equivalent to fixing a TC unit of a driving rotor of the synchronous inner-gearing double-rotor structure between two bottom surfaces in the pump chamber, the axis center of the driving rotor is the axis center of the stator 19, the eccentric rotor 20 is equivalent to mounting a driven rotor of the synchronous inner-gearing double-rotor structure on an eccentric shaft 21 through a bearing, the eccentricity of the eccentric shaft 21 is equivalent to the axial distance d of the synchronous inner-gearing double-rotor, the axis center of a rotary shaft 22 of the eccentric shaft 21 is collinear with the axis center of the stator 19, the rotary shaft 22 of the eccentric shaft 21 is mounted on the bottom surface of the cylindrical pump chamber through a bearing and extends outside the pump chamber, and the cylindrical pump chamber is respectively provided with a fluid inlet 23 and a fluid outlet 24 in two areas of the center and the periphery of the TC unit which are divided around the combination.
In the eccentric rotor pump shown in fig. 4, the eccentric rotor 20 translates along a circle with a radius d relative to the stator 19, and in the synchronous inner-gearing double-rotor, the passive rotor translates along a circle with a radius d relative to the active rotor, and it is known that in the eccentric rotor pump, the relative motion relationship between the eccentric rotor 20 and the stator 19 is the same as the relative motion relationship between the two rotors in the synchronous inner-gearing double-rotor, and the meshing relationship between the eccentric rotor 20 and the stator 19 is the same as the meshing relationship between the two rotors in the synchronous inner-gearing double-rotor.
In the eccentric rotor pump shown in fig. 4, the rotation shaft 22 of the eccentric shaft 21 is rotated clockwise, so that the fluid is driven to flow from the inlet 23 into and out of the outlet 24.
The foregoing description of the preferred embodiments of the present invention has been presented to clearly and fully illustrate the inventive principles of the present invention. In particular, the synchronous inner gearing double-rotor structure in the invention can be equally exchanged between an active rotor and a passive rotor. Various modifications and variations of the present invention will be apparent to those skilled in the art, and it is intended to cover all such modifications, equivalents, and alternatives falling within the spirit and scope of the present invention.
Claims (4)
1. A synchronous inner-meshed double-rotor structure is used for a rotor pump and is characterized in that,
The synchronous inner-meshed double rotors comprise a driving rotor and a driven rotor, wherein the driving rotor shaft and the driven rotor shaft are parallel and have a wheel base d >0, and the two rotors are in inner meshing and synchronous in the process of rotating around the respective rotor shafts;
The synchronous inner-meshing double rotors are provided with bent plate structures with the shape like a letter C, hereinafter referred to as C-shaped plates, one end of each partition plate is connected to the concave surface of the moon plate to form structures with the shape like a letter T, hereinafter referred to as T-shaped plates, the other end of each partition plate of one T-shaped plate is connected to the outer wall of one C-shaped plate, the two partition plates form a basic structural unit of the synchronous inner-meshing double rotors, hereinafter referred to as TC units, and the TC units are fixedly connected to respective rotor shafts;
On the synchronous inner-meshed double rotors, one or more TC units are respectively arranged on the driving rotor and the driven rotor, the number of the TC units is the same, a T-shaped plate on the TC unit is taken as a front C-shaped plate and is taken as a back direction, all the TC units form a surrounding combination on a rotating plane along a clockwise or anticlockwise direction, hereinafter called TC unit surrounding combination, the TC unit surrounding combination is closed, the TC units of the driving rotor and the TC units of the driven rotor are arranged at intervals, the T-shaped plate moon plate of each driving rotor is positioned in the C-shaped plate of the front driven rotor and is meshed with each other, and the T-shaped plate moon plate of each driven rotor is positioned in the C-shaped plate of the front driving rotor and is meshed with each other;
The synchronous inner-meshing double rotors are characterized in that on each pair of mutually meshed C-shaped plates and T-shaped plates, a curved surface Sigma （C） of the inner wall of the C-shaped plate and a curved surface Sigma (T) of the inner T-shaped plate corresponding to the inner wall of the C-shaped plate are a pair of conjugate tooth surfaces, namely conjugate curved surfaces, and the pair of conjugate curved surfaces Sigma （C） and Sigma (T) meet the following meshing relationship and shape conditions: in the meshing process, the common normal line of the conjugate curved surfaces sigma （C） and sigma (T) at the meshing point is parallel to the central connecting line of the double rotors, the curvature radius of the conjugate curved surface sigma （C） at the meshing point is equal to the sum of the curvature radius of the conjugate curved surface sigma (T) and the axial distance d of the double rotors, the tangent line at the end point of each curved surface moves to the other end point of the curved surface from the curved surface, and the tangent line is always at one side of the curved surface and deflects 360 degrees in the tangential direction;
In the rotating process of the synchronous inner-meshing double rotors, except for the contact of conjugate curved surfaces sigma （C） and sigma (T), the other surfaces of each pair of mutually meshed C-shaped plates and T-shaped plates are not in contact with the other surfaces of the T-shaped plates in the synchronous inner-meshing double rotors, and a fluid channel between the conjugate curved surfaces sigma （C） and sigma (T) is reserved for fluid to enter and exit;
In the process of rotating the synchronous inner-meshing double rotor along a certain direction, the conjugate curved surfaces sigma （C） and sigma (T) of each pair of mutually meshed C-shaped plates and T-shaped plates take two curved surface end points which are coincident with each other at an initial meshing point as two front conjugate end points, the other two curved surface end points which are coincident with each other at a final meshing point as two rear conjugate end points, the conjugate curved surfaces sigma （C） and sigma (T) are coincident with each other at two rear conjugate end points when the last meshing process is finished, the two front conjugate end points are coincident and the next meshing process is started, and the conjugate curved surfaces sigma （C） and sigma (T) are kept to be meshed at any moment, namely, the C-shaped plates and the T-shaped plates of each pair of mutually meshed C-shaped plates are kept to be meshed at any moment;
In the process of rotating the synchronous inner-meshing double rotor along a certain direction, the conjugate curved surfaces sigma （C） and sigma (T) on each pair of the mutually meshed C-shaped plate and T-shaped plate start to mesh and continue, so that two front conjugate end points are separated, the meshing parts on the two conjugate curved surfaces are increased, the volume between the meshing parts on the two conjugate curved surfaces is increased to suck fluid, the two rear conjugate end points are separated, the non-meshing parts on the two conjugate curved surfaces are reduced, the volume between the non-meshing parts on the two conjugate curved surfaces is reduced to discharge fluid, and the conjugate curved surfaces sigma （C） and sigma (T) finish the one-time meshing process, and meanwhile finish the fluid sucking process and the fluid discharging process;
In the process of rotating the synchronous inner-meshing double rotor along a certain direction, taking a T-shaped plate on the TC unit as a front C-shaped plate and then taking the front C-shaped plate as a TC unit encircling direction, if the rotating direction of the double rotor is the same as the TC unit encircling direction, each pair of the C-shaped plate and the T-shaped plate which are meshed with each other are meshed from one end of the TC unit encircling combination, driving fluid flows into the TC unit encircling combination, if the rotating direction of the double rotor is opposite to the TC unit encircling direction, each pair of the C-shaped plate and the T-shaped plate which are meshed with each other are meshed from one end of the TC unit encircling combination, and driving fluid flows into the TC unit encircling combination.
2. A synchronous internal engaged double-rotor pump is characterized in that,
The synchronous inner-meshing double-rotor pump comprises a cylindrical pump chamber and a synchronous inner-meshing double-rotor structure according to claim 1, wherein a passive rotor of the synchronous inner-meshing double-rotor structure according to claim 1 is arranged on a fixed shaft at the inner bottom surface and the outer bottom surface of the pump chamber through a bearing, and an active rotor shaft of the synchronous inner-meshing double-rotor structure according to claim 1 is arranged at the inner upper bottom surface of the pump chamber through a bearing and extends out of the pump chamber, and the cylindrical pump chamber is respectively provided with a fluid port in the center area and the outer periphery area of the TC unit, which are divided in a surrounding manner;
The synchronous internal meshing double-rotor pump can drive fluid to enter from one port and flow out from the other port by rotating the driving rotor shaft.
3. An eccentric rotor pump is characterized in that,
The eccentric rotor pump comprises a cylindrical pump chamber, a stator and an eccentric rotor, wherein the stator is equivalent to fixing a TC unit of a driving rotor of the synchronous inner-gearing double-rotor structure according to claim 1 between two bottom surfaces in the pump chamber, the axis of the driving rotor is the axis of the stator, the eccentric rotor is equivalent to mounting a driven rotor of the synchronous inner-gearing double-rotor structure according to claim 1 on an eccentric shaft through a bearing, the eccentric distance of the eccentric shaft is equivalent to the axial distance d of the synchronous inner-gearing double-rotor structure according to claim 1, the rotation axis of the eccentric shaft is collinear with the axis of the stator, the rotation shaft of the eccentric shaft is mounted on the bottom surface of the cylindrical pump chamber through a bearing and extends out of the pump chamber, and the cylindrical pump chamber is respectively provided with a fluid port in the center and the peripheral two areas of the TC unit which are circumferentially separated;
the eccentric rotor pump rotates the rotating shaft of the eccentric shaft, so that fluid can be driven to enter from one port and flow out from the other port.
4. The synchronous double rotor structure according to claim 1, the synchronous double rotor pump according to claim 2, and the eccentric rotor pump according to claim 3, are used as means for outputting power driven by liquid or gas.
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| CN201910587227.3A CN110285051B (en) | 2019-07-03 | 2019-07-03 | Synchronous inner-meshing double-rotor structure and rotor pump based on same |
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Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH08312539A (en) * | 1995-05-15 | 1996-11-26 | Toyo A Tec Kk | Internal gear pump |
| US6783341B1 (en) * | 1999-09-05 | 2004-08-31 | David Taran | Pair of interacting gear rims of the rotary machine |
| DE102010009822A1 (en) * | 2010-03-02 | 2011-09-08 | Klaus Springer | Spiral compressor for conveying and compressing liquid and gaseous material, has eccentrically mounted shaft with spiral-shaped arms for compressing and conveying material within rotor |
| CN102705227A (en) * | 2012-06-13 | 2012-10-03 | 大连理工大学 | Multi-tooth difference internal gear pump |
-
2019
- 2019-07-03 CN CN201910587227.3A patent/CN110285051B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH08312539A (en) * | 1995-05-15 | 1996-11-26 | Toyo A Tec Kk | Internal gear pump |
| US6783341B1 (en) * | 1999-09-05 | 2004-08-31 | David Taran | Pair of interacting gear rims of the rotary machine |
| DE102010009822A1 (en) * | 2010-03-02 | 2011-09-08 | Klaus Springer | Spiral compressor for conveying and compressing liquid and gaseous material, has eccentrically mounted shaft with spiral-shaped arms for compressing and conveying material within rotor |
| CN102705227A (en) * | 2012-06-13 | 2012-10-03 | 大连理工大学 | Multi-tooth difference internal gear pump |
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