CN117267122A - Compact multiple speed ratio large-displacement envelope curve rotor hydraulic pump/motor - Google Patents

Compact multiple speed ratio large-displacement envelope curve rotor hydraulic pump/motor Download PDF

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Publication number
CN117267122A
CN117267122A CN202311203993.8A CN202311203993A CN117267122A CN 117267122 A CN117267122 A CN 117267122A CN 202311203993 A CN202311203993 A CN 202311203993A CN 117267122 A CN117267122 A CN 117267122A
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CN
China
Prior art keywords
envelope
rotor
fixed gear
cylinder body
cover plate
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
CN202311203993.8A
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Chinese (zh)
Inventor
周俊杰
廖文博
李雪原
荆崇波
武艺
秦山
赵慧鹏
马三喜
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Beijing Institute of Technology BIT
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Beijing Institute of Technology BIT
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Publication date
Application filed by Beijing Institute of Technology BIT filed Critical Beijing Institute of Technology BIT
Priority to CN202311203993.8A priority Critical patent/CN117267122A/en
Publication of CN117267122A publication Critical patent/CN117267122A/en
Pending legal-status Critical Current

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Classifications

    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C2/00—Rotary-piston engines
    • F03C2/22—Rotary-piston engines of internal-axis type with equidirectional movement of co-operating members at the points of engagement, or with one of the co-operating members being stationary, the inner member having more teeth or tooth- equivalents than the outer member
    • 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
    • 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
    • F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
    • F04C15/0061—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • 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
    • F04C15/06—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • 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
    • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
    • F04C2/084—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
    • F04C2240/00—Components
    • F04C2240/20—Rotors
    • 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
    • F04C2240/30—Casings or housings

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Rotary Pumps (AREA)

Abstract

The invention discloses a compact multi-speed-ratio large-displacement envelope curve rotor hydraulic pump/motor, wherein cylinder bodies are symmetrically connected to two sides of a supporting plate; an envelope rotor capable of eccentrically and circumferentially moving and rotating is arranged in the cylinder body; the cover plate is fixedly connected to the surface of one side of the cylinder body, which is away from the supporting plate; the fixed gear sleeve is fixedly arranged on the surface of one side, away from the supporting plate, of the cover plate, and a protruding fixed gear is arranged on one side, facing the supporting plate, of the fixed gear sleeve; the outer contour of the envelope rotor is formed by connecting n envelope surfaces which are uniformly distributed along the circumferential direction of the envelope rotor; the cylinder body and the envelope rotor are divided into 2 (n-1) closed working cavities; the ratio of the eccentricity of the crankshaft, the pitch circle radius of the fixed gear, the pitch circle radius of the ring gear, and the maximum generating radius of the envelope rotor is 1 (n-1): n:2n. The hydraulic pump/motor has an extremely compact mounting profile and can meet high flow conditions during low speed rotation.

Description

Compact multiple speed ratio large-displacement envelope curve rotor hydraulic pump/motor
Technical Field
The invention relates to the technical field of hydraulic pressure, in particular to a compact multi-speed-ratio large-displacement envelope curve rotor hydraulic pump/motor.
Background
Hydraulic technology is not available in all engineering fields and heavy machinery equipment occasions. The hydraulic pump is a hydraulic core element, and the hydraulic motor is a very important hydraulic rotation executing element. Common hydraulic pumps/motors include gear pumps/motors, vane pumps, plunger pumps, screw pumps, and other hydraulic pumps; based on certain special conditions, partial transmission operation requires a compact, high-flow pump/motor, and currently common pump/motor products do not cover such an operation scenario well.
Common positive displacement hydraulic pump/motors are limited by the constitution of mechanical structures, the gear pump/motor and the vane pump/motor cannot meet the low-speed large-displacement requirement, the axial plunger pump/motor also has the problems of low displacement mass ratio and high economic cost when realizing the large-displacement working condition, and the radial plunger pump/motor can meet the large-displacement requirement, but the radial dimension is also larger. The concrete steps are as follows:
the limitations of gear pumps are mainly: the pressure pulsation is large, the shaft sealing is poor, the external gear pump has the phenomenon of oil trapping, and large flow cannot be provided; the limitations of vane pumps are mainly: the pressure is low, and large flow cannot be provided; the limitations of axial plunger pumps are: the cleaning sensitivity to oil is high, the self-absorption performance is poor, and the cost is high; the limitations of radial plunger pumps are: the radial profile is redundant and requires a severe installation space.
Common hydraulic motors are mainly axial plunger motors, radial cycloid plunger motors, gear motors and vane motors. Because the size is compact, the axial plunger motor is widely applied, but is limited by the characteristic of smaller displacement, the axial plunger motor is often required to be matched with a multistage planetary gear reducer for use, so as to meet the working condition requirement of a large-flow low-rotation-speed compact installation space.
In summary, the existing common hydraulic pump does not cover the working conditions of compact installation size and large displacement well. The existing common hydraulic motors do not cover the working conditions of compact installation size, large displacement and low rotation speed well.
Disclosure of Invention
The present invention provides a compact multiple speed ratio high displacement envelope rotary hydraulic pump/motor having an extremely compact mounting profile and capable of meeting high flow conditions during low speed rotation.
The invention adopts the following specific technical scheme:
the hydraulic pump/motor comprises a supporting plate, a front cylinder body, a rear cylinder body, a front envelope rotor, a rear envelope rotor, a crankshaft, a front cover plate, a rear cover plate, a front fixed gear sleeve and a rear fixed gear sleeve;
the front cylinder body and the rear cylinder body are symmetrically connected to the two sides of the supporting plate; the front envelope rotor capable of eccentrically and circumferentially moving and rotating is arranged in the front cylinder body; the envelope rotor capable of eccentrically and circumferentially moving and rotating is arranged in the rear cylinder body; the front cover plate is fixedly connected to the surface of one side of the front cylinder body, which faces away from the supporting plate; the rear cover plate is fixedly connected to the surface of one side of the rear cylinder body, which faces away from the supporting plate; the front fixed gear sleeve is fixedly arranged on the surface of one side, facing away from the supporting plate, of the front cover plate, and a protruding front fixed gear is arranged on one side, facing towards the supporting plate; the rear fixed gear sleeve is fixedly arranged on the surface of one side, facing away from the supporting plate, of the rear cover plate, and a protruding rear fixed gear is arranged on one side, facing towards the supporting plate; one end of the crankshaft is arranged in the rear fixed gear sleeve through a bearing, and the other end of the crankshaft extends out of the front fixed gear sleeve and is subjected to friction sealing through a shaft seal to position the crankshaft, so that the crankshaft can only rotate in one direction;
the inner wall of the front envelope rotor is provided with a front matching surface which is close to one side of the supporting plate and is in rolling fit with the crankshaft, and a front annular gear which is close to one side of the front fixed gear and is meshed with the front fixed gear;
the inner wall of the rear envelope rotor is provided with a rear matching surface which is close to one side of the supporting plate and is in rolling fit with the crankshaft, and a rear annular gear which is close to one side of the rear fixed gear and is meshed with the rear fixed gear;
the outer contours of the front envelope rotor and the rear envelope rotor are formed by connecting n envelope surfaces which are uniformly distributed along the circumferential direction of the front envelope rotor and the rear envelope rotor, and n is a natural number greater than 2;
the cylinder walls of the front cylinder body and the rear cylinder body are respectively provided with n-1 oil suction ports and oil discharge ports which are in one-to-one correspondence with the oil suction ports; the front cylinder body and the front envelope rotor, and the rear cylinder body and the rear envelope rotor are separated into 2 (n-1) closed working chambers;
the ratio of the eccentricity of the crankshaft, the pitch circle radius of the front fixed gear or the rear fixed gear, the pitch circle radius of the front annular gear or the rear annular gear, and the maximum generation radius of the front envelope rotor or the rear envelope rotor is 1 (n-1): n:2n.
Still further, the both side surfaces of preceding envelope rotor and back envelope rotor all are provided with the gray circle groove to install gray circle in gray circle groove, make preceding envelope rotor with between backup pad and the preceding apron, and back envelope rotor with between backup pad and the back apron all form dynamic seal.
Furthermore, the rear fixed gear sleeve is connected with the rear cover plate, and the front fixed gear sleeve is connected with the front cover plate through fastening bolts.
Still further, the backup pad with preceding cylinder body, backup pad with back cylinder body, preceding cylinder body with preceding apron, preceding side fixed gear cover with preceding apron, back cylinder body with back apron, back side fixed gear cover with back apron all seal through O shape circle between.
Still further, the front cover plate, the front cylinder block, the support plate, the rear cylinder block, and the rear cover plate are connected by a plurality of fastening assemblies distributed in a circumferential direction.
Still further, the fastening assembly is comprised of a threaded rod and nut that are threadably connected.
Further, a threaded hole for lifting is formed in the top of the supporting plate.
Further, the outer contour line of the front envelope rotor is obtained by reversely enveloping the inner wall surface of the front cylinder body;
and the outer contour line of the rear envelope rotor is obtained by reversely enveloping the inner wall surface of the rear cylinder body.
Further, the oil suction port and the oil discharge port are waist-shaped holes.
Still further, the cylinder wall profile of the front cylinder and the rear cylinder is calculated by the following formula:
x(t)＝esin(nt)+2nesin(t)；
y(t)＝ecos(nt)+2necos(t)；
in the above formula, e is the eccentricity of the crankshaft; t is an angle, the value of which is 0-360 DEG, and is a parameter; n is the number of envelopes.
The beneficial effects are that:
the hydraulic pump/motor is characterized in that a cylinder body and an envelope rotor are symmetrically arranged on two sides of a supporting plate, the envelope rotor is driven by a crankshaft, an inner gear ring of the envelope rotor is meshed with a fixed gear of a fixed gear sleeve, the outer contour of the envelope rotor is formed by connecting n envelope surfaces uniformly distributed along the circumferential direction of the envelope rotor, n-1 oil suction ports and n-1 oil discharge ports are arranged on the cylinder wall of the cylinder body, and 2 (n-1) closed working cavities are separated between the cylinder body and the envelope rotor by the outer contour of the envelope rotor; the ratio of the eccentricity of the crankshaft, the pitch circle radius of the fixed gear and the pitch circle radius of the annular gear is 1 (n-1): n; the envelope rotor divides the working cavity into 2 (n-1) working cavities in real time through the envelope of the outer contour of the envelope rotor and the inner wall of the cylinder body, the engine or the motor drives the crankshaft to rotate and drives the rotor to unidirectionally rotate along the unique degree of freedom, no friction occurs between the envelope rotor and the cylinder body through controlling the dimensional tolerance of the envelope surface of the inner wall surface of the cylinder body and the envelope surface of the envelope rotor, and the ratio of the angular velocity of the crankshaft to the angular velocity of the envelope rotor is n:1, namely: the reduction ratio from the crankshaft to the envelope rotor is 3, the crankshaft rotates for one circle, the envelope rotor rotates for 1/3 circle, and 2 (n-1) working cavities all complete one-period oil sucking and discharging actions. Thus, the hydraulic pump/motor adopting the above structure realizes the high-volume displacement to mechanism volume ratio operating characteristic; as a pump or a motor, the pump or the motor can realize the working characteristics of compact installation size, large flow and self-provided n times speed reduction ratio.
Drawings
FIG. 1 is a schematic diagram of the overall construction of a large displacement envelope rotor hydraulic pump/motor of the present invention;
FIG. 2 is a cross-sectional view of the large displacement envelope rotor hydraulic pump/motor of FIG. 1;
FIG. 3 is a schematic diagram of an exploded construction of the large displacement envelope rotary hydraulic pump/motor of FIG. 1;
FIG. 4 is a cross-sectional view of an envelope rotor hydraulic pump/motor with a triple speed ratio;
FIG. 5 is a schematic illustration of a three-speed ratio envelope rotor hydraulic pump/motor with the front cover removed;
FIG. 6 is a cylinder wall curve and rotor envelope of a five-speed ratio envelope rotor hydraulic pump/motor;
FIG. 7 is a cylinder wall curve and rotor envelope for a nine speed ratio envelope rotor hydraulic pump/motor;
FIG. 8 is a schematic diagram of cylinder wall curves and rotor envelope dimensional parameters of a three-speed ratio envelope rotor hydraulic pump/motor;
fig. 9a-9f are exploded views of different moments of the completion of a stroke.
Wherein, 1-supporting plate, 2-front cylinder, 3-rear cylinder, 4-front envelope rotor, 5-rear envelope rotor, 6-crank shaft, 7-front cover plate, 8-rear cover plate, 9-front side fixed gear sleeve, 10-rear side fixed gear sleeve, 11-fastening bolt, 12-fastening component, 13-bearing, 14-shaft seal, 15-front inner gear ring, 16-front fixed gear, 17-envelope surface, 18-oil suction port, 19-oil discharge port and 20-working cavity
Detailed Description
The following description of the embodiments of the present invention will be made clearly and completely with reference to the accompanying drawings, in which it is apparent that the embodiments described are only some embodiments of the present invention, but not all embodiments. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.
As shown in the structure of fig. 1, the embodiment of the present invention provides a compact multiple speed ratio large displacement envelope rotor hydraulic pump/motor comprising a support plate 1, a front cylinder 2, a rear cylinder 3, a front envelope rotor 4, a rear envelope rotor 5, a crankshaft 6, a front cover plate 7, a rear cover plate 8, a front side fixed gear sleeve 9 and a rear side fixed gear sleeve 10; the front cylinder body 2 and the rear cylinder body 3, the front envelope rotor 4 and the rear envelope rotor 5, the front cover plate 7 and the rear cover plate 8 are symmetrically arranged on the supporting plate 1 and adopt the same structure, in this embodiment, the envelope rotor hydraulic pump/motor of the two-layer cylinder is taken as an example, that is, as shown in fig. 3, a front cylinder body 2 is arranged on the left side of the supporting plate 1, a rear cylinder body 3 is arranged on the right side of the supporting plate 1, a front envelope rotor 4 is arranged in the front cylinder body 2, a rear envelope rotor 5 is arranged in the rear cylinder body 3, and the front envelope rotor 4 and the rear envelope rotor 5 are taken as an example and are uniformly distributed with 3 envelope surfaces 17 along the circumferential direction; in actual use, two or more front cylinders 2 may be arranged side by side between the support plate 1 and the front cover plate 7, two or more rear cylinders 3 may be arranged side by side between the support plate 1 and the rear cover plate 8, one front envelope rotor 4 is arranged in each front cylinder 2, and one rear envelope rotor 5 is arranged in each rear cylinder 3;
as shown in the structures of fig. 2 and 3, a front cylinder 2 and a rear cylinder 3 are symmetrically connected to both sides of the support plate 1; a front envelope rotor 4 capable of rotating in an eccentric circumferential motion is arranged in the front cylinder body 2; an envelope rotor capable of eccentrically and circumferentially moving and rotating is arranged in the rear cylinder body 3; the front cover plate 7 is fixedly connected to the surface of one side of the front cylinder body 2, which faces away from the support plate 1; the rear cover plate 8 is fixedly connected to the surface of one side of the rear cylinder body 3, which faces away from the support plate 1; the front cover plate 7, the front cylinder body 2, the support plate 1, the rear cylinder body 3 and the rear cover plate 8 are connected through a plurality of fastening assemblies 12 distributed along the circumferential direction; the fastening assembly 12 may be formed of a threaded rod and nut that are threadably connected; sealing is carried out between the support plate 1 and the front cylinder body 2, between the support plate 1 and the rear cylinder body 3, between the front cylinder body 2 and the front cover plate 7, between the front side fixed gear sleeve 9 and the front cover plate 7, between the rear cylinder body 3 and the rear cover plate 8, and between the rear side fixed gear sleeve 10 and the rear cover plate 8 through O-shaped rings;
the front fixed gear sleeve 9 is fixedly arranged on the surface of one side of the front cover plate 7, which is away from the supporting plate 1, and a protruding front fixed gear 16 is arranged on one side of the front cover plate facing the supporting plate 1; the rear fixed gear sleeve 10 is fixedly arranged on the surface of one side, facing away from the support plate 1, of the rear cover plate 8, and a protruding rear fixed gear is arranged on one side, facing towards the support plate 1; the rear fixed gear sleeve 10 is connected with the rear cover plate 8, and the front fixed gear sleeve 9 is connected with the front cover plate 7 through fastening bolts 11; the two side surfaces of the front envelope rotor 4 and the rear envelope rotor 5 are respectively provided with a gray ring groove, and gray rings are arranged in the gray ring grooves, so that dynamic seals are formed between the front envelope rotor 4 and the support plate 1 and the front cover plate 7, and between the rear envelope rotor 5 and the support plate 1 and the rear cover plate 8;
one end of the crankshaft 6 is arranged in the rear fixed gear sleeve 10 through a bearing 13, and the other end extends out of the front fixed gear sleeve 9 and is subjected to friction sealing through a shaft seal 14 to position the crankshaft 6, so that the crankshaft 6 can only rotate in one direction;
as shown in fig. 5, the inner wall of the front envelope rotor 4 is provided with a front mating surface near the side of the support plate 1 and in rolling engagement with the crankshaft 6, and a front ring gear 15 near the side of the front fixed gear 16 and in meshing engagement with the front fixed gear 16;
the inner wall of the rear envelope rotor 5 is provided with a rear matching surface which is close to one side of the supporting plate 1 and is in rolling fit with the crankshaft 6 and a rear annular gear which is close to one side of the rear fixed gear and is meshed with the rear fixed gear;
the outer contours of the front envelope rotor 4 and the rear envelope rotor 5 are formed by connecting n envelope surfaces 17 which are uniformly distributed along the circumferential direction, n is a natural number which is more than 2, and n can be 3, 4, 5 and 6 … …; as shown in fig. 3 and 4, n is 3; as shown in fig. 6, n is 5; as shown in fig. 7, n is 9;
the cylinder walls of the front cylinder body 2 and the rear cylinder body 3 are respectively provided with n-1 oil suction ports 18 and oil discharge ports 19 which are in one-to-one correspondence with the oil suction ports 18; the oil suction port 18 and the oil discharge port 19 can be waist-shaped holes; the front cylinder body 2 and the front envelope rotor 4, and the rear cylinder body 3 and the rear envelope rotor 5 are divided into 2 (n-1) sealed working chambers 20; when n is 3, the cylinder walls of the front cylinder body 2 and the rear cylinder body 3 are respectively provided with 2 oil suction ports 18 and 2 oil discharge ports 19 which are communicated with the cavity in the cylinder body, and the inner cavity of the cylinder body is divided into 4 closed working cavities 20 by corresponding envelope rotors;
the ratio of the eccentricity of the crankshaft 6, the pitch circle radius of the front fixed gear 16 or the rear fixed gear, the pitch circle radius of the front ring gear 15 or the rear ring gear, and the maximum generating radius of the front envelope rotor 4 or the rear envelope rotor 5 is 1 (n-1): n:2n, when n is 3, the ratio is 1:2:3:6, and the hydraulic pump/motor is 3 times the ratio; when n is 5, the ratio is 1:4:5:10, and the hydraulic pump/motor is 5 times of the ratio; when n is 9, the ratio is 1:8:9:18, and the hydraulic pump/motor is 9 times of the ratio; as shown in FIG. 8, O 1 Is the center of the front envelope rotor 4, O 2 Is the center of the front fixed gear 16, O 1 O 2 For the eccentricity e, r of the crankshaft 6 1 Is the pitch circle radius r of the front ring gear 15 and the rear ring gear 2 The pitch circle radius of the front stator gear 16 or the rear stator gear, R is the maximum generating radius of the front envelope rotor 4 and the rear envelope rotor 5, R root Is the minimum radius of the front envelope rotor 4 and the rear envelope rotor 5. The ratio of the angular velocity of the crankshaft 6 to the angular velocity of the envelope rotor is n 1, i.e. the crankshaft 6 rotates one revolution while the envelope rotor rotates only 1/n revolution, each working chamber 20 completes a cycle of oil suction and extraction stroke; when the envelope rotor rotates one revolution, each working chamber 20 can complete the oil sucking and discharging stroke of three cycles, so that the rotation speed of the crankshaft 6 can be reduced.
As shown in fig. 8, the cylinder wall profile of the front cylinder block 2 and the rear cylinder block 3 can be calculated by the following formula:
x(t)＝esin(nt)+2nesin(t)；
y(t)＝ecos(nt)+2necos(t)；
in the above formula, e is the eccentricity of the crankshaft 6; t is an angle, the value of which is 0-360 DEG, and is a parameter; n is the number of envelope surfaces 17; x (t) is the abscissa of the cylinder wall profile; y (t) is the ordinate of the cylinder wall profile; origin of abscissa and ordinate is O 2 。
After the cylinder wall molded line is calculated by adopting the formula, the outer contour molded line of the front envelope rotor 4 is obtained by reversely enveloping the inner wall surface of the front cylinder body 2; the outer contour line of the rear envelope rotor 5 is obtained by reversely enveloping the inner wall surface of the rear cylinder 3.
The outer profile of the front envelope rotor 4 and the rear envelope rotor 5 can be calculated by the following formula:
x(t)＝esin(c)+esin(nt-0.5c)+2nesin(t-0.5c)；
y(t)＝ecos(c)+ecos(nt-0.5c)+2necos(t-0.5c)；
in the above formula, e is the eccentricity of the crankshaft 6; t is an angle, the value is 0-360 degrees, and the angle is a parameter; c is the angle of envelope deflection, the value range is 0-360 degrees, the values are taken one by one, c 2 -c 1 The smaller the value of (2), the smoother the envelope surface; n is the number of envelope surfaces 17; x (t) is the abscissa of the envelope rotor; y (t) is the ordinate of the envelope rotor; origin of abscissa and ordinate is O 1 。
The hydraulic pump/motor is symmetrically provided with a cylinder body and an envelope rotor at two sides of a supporting plate 1, the envelope rotor is driven by a crankshaft 6, an inner gear ring of the envelope rotor is meshed with a fixed gear of a fixed gear sleeve, the outer contour of the envelope rotor is formed by connecting n envelope surfaces 17 uniformly distributed along the circumferential direction of the envelope rotor, the cylinder wall of the cylinder body is provided with n-1 oil suction ports 18 and n-1 oil discharge ports 19, and 2 (n-1) sealed working cavities 20 are separated between the cylinder body and the envelope rotor by the outer contour of the envelope rotor; the ratio of the eccentricity of the crankshaft 6, the pitch circle radius of the fixed gear and the pitch circle radius of the inner gear ring is 1 (n-1): n; the envelope rotor divides the working cavity 20 into 2 (n-1) working cavities 20 which are airtight in real time through the envelope of the outer contour of the envelope rotor and the inner wall of the cylinder body, the engine or the motor drives the crankshaft 6 to rotate and drives the rotor to unidirectionally rotate along the unique degree of freedom, no friction occurs between the envelope rotor and the cylinder body through controlling the dimensional tolerance of the envelope surface 17 of the inner wall surface of the cylinder body and the envelope rotor, and the ratio of the angular speeds of the crankshaft 6 and the envelope rotor is n:1, namely: the reduction ratio from the crankshaft 6 to the envelope rotor is 3, the crankshaft 6 rotates one circle, the envelope rotor rotates 1/3 circle, and 2 (n-1) working chambers 20 all complete one-cycle oil sucking and discharging actions. Thus, the hydraulic pump/motor adopting the above structure realizes the high-volume displacement to mechanism volume ratio operating characteristic; as a pump or a motor, the pump or the motor can realize the working characteristics of compact installation size, large flow and self-provided n times speed reduction ratio.
In order to facilitate the handling of the whole hydraulic pump/motor, the top of the support plate 1 is provided with a threaded hole for lifting.
Fig. 9a-9f show exploded views of the envelope rotor at different times when the envelope rotor completes a stroke, as shown in fig. 9a, when the envelope rotor is in an original state, as shown in fig. 9b, when the envelope rotor rotates clockwise by 30 °, as shown in fig. 9c, when the envelope rotor rotates clockwise by 60 °, as shown in fig. 9d, when the envelope rotor rotates clockwise by 77 °, as shown in fig. 9e, when the envelope rotor rotates clockwise by 103 °, as shown in fig. 9f, when the envelope rotor rotates clockwise by 120 °, in each of which the dark color represents a high pressure state in the working chamber 20 and the light color represents a low pressure state in the working chamber 20.
It will be apparent to those skilled in the art that various modifications and variations can be made to the embodiments of the present invention without departing from the spirit and scope of the invention. Thus, it is intended that the present invention also include such modifications and alterations insofar as they come within the scope of the appended claims or the equivalents thereof.

Claims (10)

1. The hydraulic pump/motor is characterized by comprising a supporting plate, a front cylinder body, a rear cylinder body, a front envelope rotor, a rear envelope rotor, a crankshaft, a front cover plate, a rear cover plate, a front fixed gear sleeve and a rear fixed gear sleeve;
the front cylinder body and the rear cylinder body are symmetrically connected to the two sides of the supporting plate; the front envelope rotor capable of eccentric circumferential movement is arranged in the front cylinder body; the envelope rotor capable of moving eccentrically and circumferentially is arranged in the rear cylinder body; the front cover plate is fixedly connected to the surface of one side of the front cylinder body, which faces away from the supporting plate; the rear cover plate is fixedly connected to the surface of one side of the rear cylinder body, which faces away from the supporting plate; the front fixed gear sleeve is fixedly arranged on the surface of one side, facing away from the supporting plate, of the front cover plate, and a protruding front fixed gear is arranged on one side, facing towards the supporting plate; the rear fixed gear sleeve is fixedly arranged on the surface of one side, facing away from the supporting plate, of the rear cover plate, and a protruding rear fixed gear is arranged on one side, facing towards the supporting plate; one end of the crankshaft is arranged in the rear fixed gear sleeve through a bearing, and the other end of the crankshaft extends out of the front fixed gear sleeve and is subjected to friction sealing through a shaft seal to position the crankshaft, so that the crankshaft can only rotate in one direction;
the inner wall of the front envelope rotor is provided with a front matching surface which is close to one side of the supporting plate and is in rolling fit with the crankshaft, and a front annular gear which is close to one side of the front fixed gear and is meshed with the front fixed gear;
the inner wall of the rear envelope rotor is provided with a rear matching surface which is close to one side of the supporting plate and is in rolling fit with the crankshaft, and a rear annular gear which is close to one side of the rear fixed gear and is meshed with the rear fixed gear;
the outer contours of the front envelope rotor and the rear envelope rotor are formed by connecting n envelope surfaces which are uniformly distributed along the circumferential direction of the front envelope rotor and the rear envelope rotor, and n is a natural number greater than 2;
the cylinder walls of the front cylinder body and the rear cylinder body are respectively provided with n-1 oil suction ports and oil discharge ports which are in one-to-one correspondence with the oil suction ports; the front cylinder body and the front envelope rotor, and the rear cylinder body and the rear envelope rotor are separated into 2 (n-1) closed working chambers;
the ratio of the eccentricity of the crankshaft, the pitch circle radius of the front fixed gear or the rear fixed gear, the pitch circle radius of the front annular gear or the rear annular gear, and the maximum generation radius of the front envelope rotor or the rear envelope rotor is 1 (n-1): n:2n.
2. The large displacement envelope rotor hydraulic pump/motor of claim 1, wherein both side surfaces of the front envelope rotor and the rear envelope rotor are provided with gurley grooves, and gurley is installed in the gurley grooves so that dynamic seals are formed between the front envelope rotor and the support plate and the front cover plate, and between the rear envelope rotor and the support plate and the rear cover plate.
3. The large displacement envelope curve rotor hydraulic pump/motor of claim 1, wherein the rear side fixed gear sleeve and the rear cover plate, and the front side fixed gear sleeve and the front cover plate are connected by fastening bolts.
4. The large displacement envelope curve rotor hydraulic pump/motor of claim 1, wherein the support plate and the front cylinder, the support plate and the rear cylinder, the front cylinder and the front cover plate, the front side fixed gear sleeve and the front cover plate, the rear cylinder and the rear cover plate, and the rear side fixed gear sleeve and the rear cover plate are all sealed by O-rings.
5. A large displacement envelope rotor hydraulic pump/motor as claimed in claim 3 wherein said front cover plate, said front cylinder, said support plate, said rear cylinder and said rear cover plate are connected by a plurality of circumferentially distributed fastening assemblies.
6. The large displacement envelope curve rotary fluid pump/motor of claim 5, wherein said fastening assembly is comprised of a threaded rod and nut.
7. The large displacement envelope rotor hydraulic pump/motor of claim 1, wherein a top of the support plate is provided with a threaded hole for lifting.
8. The large displacement envelope curve rotor hydraulic pump/motor as claimed in claim 1, wherein an outer contour line of said front envelope curve rotor is obtained by reversely enveloping an inner wall surface of said front cylinder;
and the outer contour line of the rear envelope rotor is obtained by reversely enveloping the inner wall surface of the rear cylinder body.
9. The large displacement envelope curve rotary fluid pump/motor of claim 1, wherein said fluid suction port and said fluid discharge port are each a kidney hole.
10. The large displacement envelope curve rotary fluid pump/motor of claim 1, wherein the cylinder wall profile of the front cylinder and the rear cylinder is calculated by the following formula:
x(t)＝esin(nt)+2nesin(t)；
y(t)＝ecos(nt)+2necos(t)；
in the above formula, e is the eccentricity of the crankshaft; t is an angle, the value of which is 0-360 DEG, and is a parameter; n is the number of envelopes.
CN202311203993.8A 2023-09-18 2023-09-18 Compact multiple speed ratio large-displacement envelope curve rotor hydraulic pump/motor Pending CN117267122A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN202311203993.8A CN117267122A (en) 2023-09-18 2023-09-18 Compact multiple speed ratio large-displacement envelope curve rotor hydraulic pump/motor

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN202311203993.8A CN117267122A (en) 2023-09-18 2023-09-18 Compact multiple speed ratio large-displacement envelope curve rotor hydraulic pump/motor

Publications (1)

Publication Number Publication Date
CN117267122A true CN117267122A (en) 2023-12-22

Family

ID=89217089

Family Applications (1)

Application Number Title Priority Date Filing Date
CN202311203993.8A Pending CN117267122A (en) 2023-09-18 2023-09-18 Compact multiple speed ratio large-displacement envelope curve rotor hydraulic pump/motor

Country Status (1)

Country Link
CN (1) CN117267122A (en)

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