CN108869224B - Design method of high-rotation-speed conical plunger pump or motor - Google Patents

Design method of high-rotation-speed conical plunger pump or motor Download PDF

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CN108869224B
CN108869224B CN201810610914.8A CN201810610914A CN108869224B CN 108869224 B CN108869224 B CN 108869224B CN 201810610914 A CN201810610914 A CN 201810610914A CN 108869224 B CN108869224 B CN 108869224B
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plunger
line
center
hole
mean
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CN108869224A (en
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王晋芝
安维亮
杨华
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AVIC Liyuan Hydraulic Co Ltd
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AVIC Liyuan Hydraulic Co Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F04B1/2014—Details or component parts
    • 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
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/06—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis
    • F03C1/0602—Component parts, details
    • F03C1/0605—Adaptations of pistons
    • 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
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/06—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis
    • F03C1/0602—Component parts, details
    • F03C1/0607—Driven means
    • 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
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/06—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis
    • F03C1/0636—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F03C1/0639—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block having two or more sets of cylinders or pistons
    • F03C1/0642—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block having two or more sets of cylinders or pistons inclined on main shaft axis
    • 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
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/06—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis
    • F03C1/0636—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F03C1/0644—Component parts
    • F03C1/0652—Cylinders
    • 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
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/06—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis
    • F03C1/0636—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F03C1/0644—Component parts
    • F03C1/0663—Casings, housings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/122—Details or component parts, e.g. valves, sealings or lubrication means
    • F04B1/124—Pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/128—Driving means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F04B1/2014—Details or component parts
    • F04B1/2035—Cylinder barrels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F04B1/2014—Details or component parts
    • F04B1/2064—Housings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F04B1/22—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block having two or more sets of cylinders or pistons
    • F04B1/24—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block having two or more sets of cylinders or pistons inclined to the main shaft axis
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F30/00—Computer-aided design [CAD]
    • G06F30/10—Geometric CAD
    • G06F30/17—Mechanical parametric or variational design

Abstract

The invention discloses a design method of a high-speed cone plunger pump or motor, which is characterized in that five parameters of Rz, Rg, L, β and α are adjusted to simultaneously meet the following two conditions that the minimum value M of the rotation angle difference between a main shaft (3) and a cylinder body (4) approaches to zero, ② is on the rotating surface of the cylinder body (4), and the average mean value (D) of the included angle between the line A and the line B is the mean valueAB) mean tends to 90 degrees, the line A is a connecting straight line between a point K and the center of the plunger hole (8), the point K is a contact point between the plunger (9) and the plunger hole (8), the line B is a connecting straight line between the midpoint of the center hole (7) and the center of the plunger hole (8), Rz is the reference circle radius of the plunger ball socket (6) on the main shaft (3), Rg is the reference circle radius of the plunger hole (8) on the cylinder body (4), and L is the distance from the center of the plunger drum part (12) to the center of the plunger ball head (11). The inclined shaft conical plunger pump or motor designed by the invention has the advantage of long service life.

Description

Design method of high-rotation-speed conical plunger pump or motor
Technical Field
The invention belongs to the field of inclined shaft conical plunger pumps or motors, and particularly relates to a design method of a high-rotation-speed conical plunger pump or motor.
Background
As shown in figures 1 and 2, the oblique axis cone plunger pump or the motor comprises a first shell and a second shell which are connected in series, an included angle of α degrees is formed between the first shell and the second shell, a coaxial spindle is arranged in the first shell, a coaxial cylinder body is arranged in the second shell, a central ball socket is arranged in the bottom center of the spindle towards the cylinder body, a plurality of plungers are arranged in the central circumferential direction, a central hole is arranged in the cylinder body in the upward direction, plunger holes with the same number as that of the plunger ball sockets are arranged in the circumferential direction of the central hole, the spindle and the cylinder body are connected through the plungers and the central rod, the plunger comprises a plunger rod, the taper angle of β degrees is arranged in the axial direction, the small end of the plunger ball socket is provided with a plunger piston connected with the plunger ball socket, the large end of the plunger piston ball socket is arranged in the plunger piston hole, the plunger piston rod is connected with the plunger piston and the central rod of the plunger piston, the plunger piston is connected with a plunger piston, the plunger piston rod is arranged in the central plunger piston ball socket, the plunger piston hole, the plunger piston rod is arranged in the plunger piston ball socket, the plunger piston hole, the plunger piston is connected with the plunger piston, the plunger piston is a plunger piston, the plunger piston is arranged in the plunger piston hole of the plunger piston, the plunger piston is connected with the plunger piston, the plunger piston is arranged in the plunger piston, the plunger piston is connected with the plunger piston, the plunger piston is arranged in the plunger piston hole of the plunger piston, the plunger piston is connected with the plunger piston, the plunger piston is connected.
Although the existing inclined shaft cone plunger pump or motor has the functions of high rotating speed and high pressure, the problem that the contact surface of materials is easy to peel off and damage is caused because the plunger acts on the wall of the plunger hole of the cylinder body and the friction pair is excessively stressed in the high rotating speed and high pressure process of the existing inclined shaft cone plunger pump or motor, and the service life of the product is short. The plunger applies excessive force to a friction pair acting on the wall of the plunger hole of the cylinder body, part of the reason is that pressure compressed by a spring exists between the cylinder body and an oil distribution disc, damping torque is applied to the oil distribution disc in the rotating process of the cylinder body, and transmission between the plunger and the cylinder body needs to overcome the damping torque.
Therefore, the existing inclined shaft cone plunger pump or motor has the problem of short service life.
Disclosure of Invention
The invention aims to provide a design method of a high-speed cone plunger pump or a high-speed cone plunger motor. The inclined shaft conical plunger pump or motor designed by the invention has the advantage of long service life.
The technical scheme includes that the design method of the high-speed cone plunger pump or motor enables the following two conditions to be simultaneously met by adjusting the five parameters of Rz, Rg, L, β and α, wherein the minimum value M of the rotation angle difference between a ① main shaft and a cylinder body approaches to zero, ② is on a rotating surface of the cylinder body, and the average mean value (D) of the included angle between a line A and a line B is the mean value of the included angle between a line A and a line BAB)meanThe angle is close to 90 degrees, the line A is a connecting straight line of a point K and the center of a plunger hole, the point K is a contact point of a plunger and the plunger hole, the line B is a connecting straight line of the center point of a center hole and the center of the plunger hole, Rz is the reference circle radius of a plunger ball socket on a main shaft, Rg is the reference circle radius of the plunger hole on a cylinder body, L is the distance from the center of a plunger drum part to the center of a plunger ball head, β is the taper of the plunger rod, and α is the included angle between a first shell and a second shell.
The motion of the plurality of plungers causes a geometric envelope equation of the rotational angle difference between the main shaft and the cylinder. Because the line A is a straight line connecting the K point and the center of the plunger hole, and the invention is provided with a plurality of plungers and a plurality of plunger holes, the invention actually has a plurality of lines A which are equal to the number of the plungers, and a plurality of lines B corresponding to the lines A, and an included angle value D is formed between each group of lines A and BAB，(DAB)meanNamely the corresponding plunger DABAverage value of (D) of the plungerABThe value is the contact included angle value of the plunger and the cylinder body in a small continuous range when the plunger rotates for one circle, so that the maximum contact value and the minimum contact value exist, the conical surface of the plunger is not in contact with the wall of the cylinder body on the corner of the main shaft, after the first plunger is in contact, the other plunger is in contact with the other wall of the cylinder body, the process is repeated, and the posture process is the same. Because the contact attitude process of all the plungers and the cylinder body is the same, only one D needs to be calculatedABThe average value of (1) is just required.
In the design method of the high-speed cone plunger pump or motor, the five parameters of Rz, Rg, L, β and α are adjusted, so that the following two conditions are simultaneously met, namely ① that the main shaft and the cylinder are connectedMinimum rotation angle difference of 0.002 degree or more and M degree or more and 0 degree, ② mean included angle between line A and line B (D) on the rotating surface of cylinderAB) mean ranges from 90 degrees plus or minus 0.5 degrees, the line A is a connecting straight line between a K point and the center of a plunger hole, the point K is a contact point between a plunger and the plunger hole, the line B is a connecting straight line between the midpoint of a center hole and the center of the plunger hole, Rz is the reference circle radius of a plunger ball socket on a main shaft, Rg is the reference circle radius of the plunger hole on a cylinder body, and L is the distance from the center of a plunger drum part to the center of a plunger ball head.
In the design method of the high-speed cone plunger pump or motor, the five parameters Rz, Rg, L, β and α are adjusted according to the adjustment equation, so that the minimum value M of the rotation angle difference between the main shaft and the cylinder approaches zero, and the average mean value (D) of the included angle between the line a and the line B is obtainedAB)meanTends to 90 °; adjustment equation of minimum value M of rotation angle difference between main shaft and cylinder body: m is Mmin (N)0，N1，N2，N3，N4，N5，N6，……，Nn)，
Wherein
Figure BDA0001695542350000031
Wherein the content of the first and second substances,
Figure BDA0001695542350000032
mean angle of line A and line B (D)AB)meanThe adjustment equation of (1):
Figure BDA0001695542350000041
wherein the content of the first and second substances,
Figure BDA0001695542350000042
wherein the content of the first and second substances,
Nirefer to the ithThe value of i in the equation is i-1, for example, when the 5 th plunger is calculated, the value of i in the equation is 5-1-4; miRefers to the elliptical radius of the ith plunger on the cylinder rotation surface; thetazIs the rotation angle of the main shaft. M0< > M, when M is calculated as a comparison function0When > M, (M)0＜＞M)＝1；M0When the content is less than or equal to M, (M)0＜＞)＝0，M0Refers to the M of the 1 st plunger calculation starting at angle 0iThe value is obtained.
Compared with the prior art, the invention provides a limit target for the five parameters of Rz, Rg, L, β and α on the basis of the prior art, so that the speed difference between the plunger and the cylinder is smaller, the friction impact of the plunger on the plunger hole is smaller, and the possibility of peeling and damage of the contact surface of the plunger and the plunger hole material is reduced.
Further, by limiting (D)AB)meanAnd the interval range of the M value, the distribution position of the contact point K can be effectively controlled, so that the service life of the invention is ensured to be longer.
Furthermore, five parameters of Rz, Rg, L, β and α are substituted into an equation for checking or adjusting, so that the design scientificity and the high performance of the product are improved.
Therefore, the inclined shaft cone plunger pump or the motor designed by the invention has the advantage of long service life.
Drawings
Fig. 1 is a schematic structural view of the present invention.
Fig. 2 is a schematic view of the structure of the plunger.
Fig. 3 is a schematic diagram of the trajectory of the spindle, ram and cylinder movements.
FIG. 4 is a diagram showing the projection speed in the cylinder rotation plane.
Fig. 5 is a schematic view of a projection angle of a main shaft rotation angle in a cylinder rotation plane and a cylinder rotation angle caused by a structural size.
The labels in the figures are: 1-a first shell, 2-a second shell, 3-a main shaft, 4-a cylinder, 5-a central ball socket, 6-a plunger ball socket, 7-a central hole, 8-a plunger hole, 9-a plunger, 10-a central rod, 11-a plunger ball head, 12-a plunger drum part, 13-a central rod ball head, 14-a spring and 15-an oil distribution disc.
Detailed Description
The invention is further illustrated by the following figures and examples, which are not to be construed as limiting the invention.
The embodiment discloses a design method of a high-rotation-speed cone plunger pump or motor, which adjusts the five parameters of Rz, Rg, L, β and α according to the following equation, so that the following two conditions are simultaneously met, namely that the minimum value of 0.002 degrees and more than or equal to M and more than or equal to 0 degrees in the rotation angle difference of a ① plunger 9, and the average median value of the included angles of a line A and a line B on the rotation surface of a cylinder 4 is ②
Figure BDA0001695542350000051
Is in the range of 90 +/-0.5 degrees, wherein the line A is a connecting straight line between a point K and the center of the plunger hole 8, the point K is a contact point between the plunger 9 and the plunger hole 8, the line B is a connecting straight line between the midpoint of the central hole 7 and the center of the plunger hole 8, Rz is the reference circle radius of the plunger ball socket 6 on the main shaft 3, Rg is the reference circle radius of the plunger hole 8 on the cylinder 4, L is the distance from the center of the plunger drum part 12 to the center of the plunger ball socket 6, β is the taper of the plunger rod, α is the included angle between the first shell 1 and the second shell 2, and the minimum value M in the rotation angle difference of the plunger 9 is M Mmin (N is the adjustment equation of the minimum value M of the rotation angle difference of the plunger 90，N1，N2，N3，N4，N5，N6，……，Nn)，
Wherein
Figure BDA0001695542350000061
Wherein the content of the first and second substances,
Figure BDA0001695542350000062
mean angle of line A and line B (D)AB)meanIs adjusted toThe process:
Figure BDA0001695542350000063
wherein the content of the first and second substances,
Figure BDA0001695542350000064
wherein the content of the first and second substances,
Figure BDA0001695542350000065
the following table is an example of three sets of dimensions for two motors designed according to the method described above:
Figure BDA0001695542350000066
the working principle of the invention is as follows: as shown in fig. 3 and 4, when M ═ Mmin (N)0，N1，N2，N3，N4，……，Nn) When the angle is approximately equal to 0 degree, a change curve of a rotation angle theta projected to a rotation surface of the cylinder 4 by the main shaft 3 tends to be consistent with a change curve of the rotation angle of the cylinder 4, the main shaft 3, the plunger 9 and the cylinder 4 tend to be in synchronous space transmission, the force of interaction between the plunger 9 and the cylinder 4 is minimum at the moment, and the possibility of peeling and damage of a material contact surface of the plunger 9 and the plunger hole 8 is minimum.
As shown in fig. 5, on the rotating surface of the cylinder 4, the included angle between the line a and the line B approaches to 90 °, the force arm of the poking force is maximized, the poking force required for overcoming the damping torque between the cylinder 4 and the oil distribution disc 15 is minimized, the abrasion between the plunger 9 and the plunger hole 8 is reduced, the service life is prolonged, and the energy conversion efficiency of the input end and the output end of the invention is improved.
The prior art inclined shaft plunger pump and the motor can not aim at M and D at the beginning of designAB)meanControlled to obtain M values of 0.1 deg. or more, and obtained (D)AB)meanAnd confusion results show that some products are distributed at 150 degrees, some products are distributed at 40 degrees, and the distribution positions of contact points cannot be effectively controlled. The invention can be designed and controlled to be more than or equal to M in the angle of 0.002 degreesmin≥0.0°，(DAB)meanControlled at 90 ° ± 0.5 °.
The reduction of the rotation angle difference between the main shaft and the cylinder (the rotation angle difference between the main shaft and the cylinder reflects the rotation speed difference between the main shaft and the cylinder), and the result is no speed difference between the plunger and the cylinder in order to ensure the space synchronous transmission of the main shaft and the cylinder. The above equations and methods are all defined by the rotation angle difference between the main shaft and the cylinder, so the rotation angle difference between the main shaft and the cylinder is written in the above, the rotation angle difference between the plunger is not written, because the rotation angle difference between the plunger and the cylinder hole does not exist, but exists a rotation speed difference, and the rotation angle difference between the plunger and the cylinder hole is the taper angle of the plunger and is a fixed value.
The invention provides a limit design optimization method for the hydraulic element of the structure. The two points of limit optimization herein are space transmission and minimum toggle torque. And (4) providing an optimization target according to the two points, and further forming an equation. Although the rotation angle of the main shaft is independent variable, the rotation angle difference is not a single point but a continuous curve, the scientificity of design is improved, and the performance of the product is extremely high.
Therefore, the inclined shaft cone plunger pump or the motor designed by the invention has the advantage of long service life.

Claims (2)

1. A design method of a high-speed cone plunger pump or motor is characterized in that the following two conditions are simultaneously met by adjusting the five parameters of Rz, Rg, L, β and α:
Figure 983583DEST_PATH_IMAGE002
the minimum value M of the rotation angle difference between the shaft (3) and the cylinder body (4) approaches zero;
Figure 841818DEST_PATH_IMAGE004
on the rotating surface of the cylinder body (4), the mean value (D) of the included angle between the line A and the line BAB）meanThe angle is about 90 degrees, the line A is a connecting straight line of a point K and the center of a plunger hole (8), the point K is a contact point of a plunger (9) and the plunger hole (8), the line B is a connecting straight line of a midpoint of a center hole (7) and the center of the plunger hole (8), Rz is a reference circle radius of a plunger ball socket (6) on a main shaft (3), Rg is the reference circle radius of the plunger hole (8) on a cylinder (4), L is the distance from the center of a plunger drum part (12) to the center of a plunger ball head (11), β is the taper of the plunger rod, and α is the included angle between a first shell (1) and a second shell (2);
adjusting the five parameters of Rz, Rg, L, β and α according to an adjusting equation so that the minimum value M of the rotation angle difference between the main shaft (3) and the cylinder (4) approaches zero, and the average mean value (D) of the included angle between the line A and the line BAB）meanTends to 90 °; adjustment equation of minimum value M of rotation angle difference between main shaft and cylinder body: m = Mmin (
Figure 860590DEST_PATH_IMAGE006
，……，Nn)，
，
Figure 629011DEST_PATH_IMAGE008
，
Mean angle of line A and line B (D)AB）meanThe adjustment equation of (1):，
Figure 531425DEST_PATH_IMAGE010
，
Figure 165669DEST_PATH_IMAGE011
，
when in use
Figure 528517DEST_PATH_IMAGE012
= 1; when in use
Figure 564606DEST_PATH_IMAGE013
=0。
2. The design method of the high-speed cone plunger pump or motor as claimed in claim 1, wherein the five parameters Rz, Rg, L, β and α are adjusted so that the following two conditions are satisfied simultaneously:
Figure DEST_PATH_IMAGE014
the minimum value of the rotation angle difference between the main shaft (3) and the cylinder body (4) is more than or equal to 0.002 degrees and more than or equal to 0 degree;on the rotating surface of the cylinder body (4), the mean value (D) of the included angle between the line A and the line BAB）Of meanThe range is between 90 + -0.5 deg..
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Application publication date: 20181123

Assignee: Suzhou Liyuan Hydraulic Co.,Ltd.

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Denomination of invention: A Design Method for High Speed Cone Plunger Pump or Motor

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Record date: 20230710