CN117108442A - Inner curve radial plunger motor with obliquely-installed plunger and installation method thereof - Google Patents
Inner curve radial plunger motor with obliquely-installed plunger and installation method thereof Download PDFInfo
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- CN117108442A CN117108442A CN202311054192.XA CN202311054192A CN117108442A CN 117108442 A CN117108442 A CN 117108442A CN 202311054192 A CN202311054192 A CN 202311054192A CN 117108442 A CN117108442 A CN 117108442A
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- 238000000034 method Methods 0.000 title claims abstract description 22
- 238000009434 installation Methods 0.000 title claims abstract description 20
- 230000033001 locomotion Effects 0.000 claims abstract description 33
- 238000006243 chemical reaction Methods 0.000 claims abstract description 19
- 238000005299 abrasion Methods 0.000 claims abstract description 14
- 230000001050 lubricating effect Effects 0.000 claims abstract description 5
- 230000008569 process Effects 0.000 claims abstract description 5
- 238000004458 analytical method Methods 0.000 claims description 10
- 230000001133 acceleration Effects 0.000 claims description 9
- 230000009471 action Effects 0.000 claims description 9
- 230000007423 decrease Effects 0.000 claims description 6
- 230000010349 pulsation Effects 0.000 claims description 3
- 238000005096 rolling process Methods 0.000 claims description 3
- 238000005461 lubrication Methods 0.000 claims 1
- 230000001154 acute effect Effects 0.000 abstract description 2
- 238000010586 diagram Methods 0.000 description 3
- 230000007547 defect Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 230000002035 prolonged effect Effects 0.000 description 2
- 229920002148 Gellan gum Polymers 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
Classifications
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- 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
- F03C1/22—Reciprocating-piston liquid engines with movable cylinders or cylinder
- F03C1/24—Reciprocating-piston liquid engines with movable cylinders or cylinder in which the liquid exclusively displaces one or more pistons reciprocating in rotary cylinders
- F03C1/2407—Reciprocating-piston liquid engines with movable cylinders or cylinder in which the liquid exclusively displaces one or more pistons reciprocating in rotary cylinders having cylinders in star or fan arrangement, the connection of the pistons with an actuated element being at the outer ends of the cylinders
- F03C1/2423—Reciprocating-piston liquid engines with movable cylinders or cylinder in which the liquid exclusively displaces one or more pistons reciprocating in rotary cylinders having cylinders in star or fan arrangement, the connection of the pistons with an actuated element being at the outer ends of the cylinders with two or more series radial piston-cylinder units
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
- B23P—METAL-WORKING NOT OTHERWISE PROVIDED FOR; COMBINED OPERATIONS; UNIVERSAL MACHINE TOOLS
- B23P19/00—Machines for simply fitting together or separating metal parts or objects, or metal and non-metal parts, whether or not involving some deformation; Tools or devices therefor so far as not provided for in other classes
- B23P19/04—Machines for simply fitting together or separating metal parts or objects, or metal and non-metal parts, whether or not involving some deformation; Tools or devices therefor so far as not provided for in other classes for assembling or disassembling 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
- F03C1/002—Reciprocating-piston liquid engines details; components parts
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- Combustion & Propulsion (AREA)
- General Engineering & Computer Science (AREA)
- Hydraulic Motors (AREA)
Abstract
The application discloses an inner curve radial plunger motor with a plunger obliquely arranged and an installation method thereof, wherein a roller in the plunger motor is arranged in a plunger hole, the plunger is assembled on the circumference of a rotor cylinder body, the plunger aperture on the rotor cylinder body is arranged along the rotation opposite direction of the rotor cylinder body by an inclination angle theta of 14 degrees, the plunger is easier to throw out in the rotation process of a main shaft and is more closely attached to the inner surface of an inner curve stator guide rail, the acute angle-pressure angle clamped between the stress direction and the movement direction can be reduced, the reaction force of the inner curve stator guide rail to the roller is further reduced, the lateral force born by the plunger is reduced, meanwhile, a pressure equalizing groove is processed on the side wall of the plunger, so that oil flows into the side wall of the plunger to play a lubricating role, the movement of the plunger in the plunger hole of the rotor cylinder body is facilitated, the abrasion quantity of the plunger and the plunger hole on the rotor cylinder body is reduced, the output performance and the working efficiency of the motor are further improved, and the inner curve radial plunger motor can better meet the market demands.
Description
Technical Field
The application belongs to the technical field of hydraulic equipment, and particularly relates to an inner curve radial plunger motor with a plunger obliquely installed and an installation method thereof.
Background
With the continuous rise of engineering demands, hydraulic drives are increasingly used in various fields. Hydraulic motors are important actuators in hydraulic systems, whose performance and function are critical to the control and movement of the machine. An inner curve radial plunger motor is a typical representation of a hydraulic motor and has many advantageous features such as high torque output at low speed operation, high rated pressure, high efficiency, long life, etc. Therefore, the method is widely applied to various high-power engineering machinery and ship industries.
The existing plunger mounting mode adopted by the inner curve radial plunger motor has the defect of larger lateral force. Larger friction force is generated between the plunger and the inner wall of the plunger hole of the rotor cylinder body, so that abrasion is increased, the problem of leakage of the plunger cavity flow is increased, and motor vibration and noise are increased. Meanwhile, overturning moment can be generated on the rotor cylinder body, so that the output performance and the working efficiency of the motor are affected, the service life of the motor is reduced, and the inner curve radial plunger motor is difficult to adapt to market demands.
Therefore, it is necessary to provide an inner curve radial plunger motor with a plunger mounted obliquely and a mounting method thereof, so as to solve the above technical problems.
Disclosure of Invention
The application provides an inner curve radial plunger motor with a plunger obliquely installed and an installation method thereof, which are used for solving the problems of unstable output performance, serious abrasion of a plunger hole of a rotor cylinder body, low service life and large vibration noise of the high-torque inner curve radial plunger motor in the prior art.
In order to solve the problems, the technical scheme provided by the application is as follows:
the embodiment of the application provides an inner curve radial plunger motor with a plunger obliquely arranged, which comprises a motor shell (1), an inner curve stator guide rail (2), a rotor cylinder body (3), a main shaft (4), a plunger (5), a roller (6) and a Gellan ring (7); the inner curve stator guide rail (2) is arranged on the inner side of a coaxial line of the motor shell (1), the rotor cylinder body (3) is arranged on the inner side of the inner curve stator guide rail (2), and the center of the rotor cylinder body (3) is connected with the main shaft (4) through a spline; the plunger (5) is arranged in a plunger hole on the rotor cylinder body (3), the roller (6) is arranged in a groove of the plunger (5), and the aperture of the plunger on the rotor cylinder body (3) is arranged along the inclination angle theta of the rotor cylinder body (3) in the opposite direction of rotation, wherein the theta is 14 degrees; the plunger (5) is provided with a pressure equalizing groove (8) on the circumferential side wall of the plunger, a Gelai ring (7) is arranged on the plunger, and the Gelai ring (7) is used for preventing oil from leaking between the plunger (5) and a plunger hole on the rotor cylinder body (3).
According to an alternative embodiment of the application, the number of the plungers (5) is 8, and 8 plungers (5) are uniformly fitted in plunger holes in the circumferential direction of the rotor cylinder (3).
According to an alternative embodiment of the application, two adjacent plungers (5) are spaced at an angle of 45 ° to each other.
According to an alternative embodiment of the application, a plunger cavity (9) is arranged on the edge of the plunger (5), and an oil inlet and outlet (10) is arranged on the central position of the plunger cavity (9) towards one side of the main shaft (4).
According to an alternative embodiment of the application, the number of the pressure equalizing grooves (8) on the circumferential side wall of each plunger (5) is 5, each pressure equalizing groove (8) is an annular rectangular groove and surrounds the plunger (5) for one circle, and the pressure equalizing grooves (8) are used for enabling oil to flow into the side wall of the plunger (5) to perform a lubricating function, so that the movement of the plunger (5) in the plunger hole of the rotor cylinder body (3) is facilitated, and the output characteristic of the motor is facilitated to be improved.
The application also provides an installation method of the inner curve radial plunger motor for obliquely installing the plunger, wherein the inner curve radial plunger motor adopts the inner curve radial plunger motor in the embodiment, and the installation method of the plunger comprises the following steps:
step S1, calculating the installation inclination angle theta of the plunger (5) by carrying out stress analysis on the plunger (5) -roller (6), wherein the concrete calculation process is as follows:
hydraulic pressure generated by pressure oil flowing into a plunger cavity (9) of the plunger (5) from an oil inlet and outlet (10):
in the formula (1), d is the diameter of the plunger 5, and P is the pressure of the plunger cavity 9;
inertial force generated by the movement of the plunger (5) -roller (6) relative to the rotor cylinder 3:
in the formula (2), m is the mass of a plunger (5) -a roller (6), ω is the angular velocity of a motor rotor cylinder (3), ρ is the polar diameter from the center of the pole of the inner curve stator guide rail (2) to the center of the roller (6),an angle of rotation for the rotor cylinder (3);
centrifugal force generated by the movement of the plunger (5) -roller (6) relative to the rotor cylinder (3):
F b ＝mω 2 ρ g (3)
in formula (3), ρ g The pole diameter from the pole center of the inner curve stator guide rail (2) to the mass center of the plunger (5) -roller (6);
motor angular acceleration causes inertial forces:
F c ＝mρ g ε (4)
in the formula (4), epsilon is motor angular acceleration;
the plunger (5) -roller (6) motion is a dragging motion, and the inertial force generated by the God acceleration:
friction force generated by the movement of the roller (5) on the inner curve stator guide rail (2):
F f3 ＝f 2 F n (6)
in the formula (6), f 2 Is the rolling friction coefficient between the roller (6) and the inner curve stator guide rail (2), F n The reaction force of the inner curve stator guide rail (2) to the roller (6);
reaction force F of inner curve stator guide rail (2) to roller (6) n Decomposed into tangential force F t And radial force F r
F t ＝F n sinβ (7)
F r ＝F n cosβ (8)
In the formulas (7) and (8), beta is a pressure angle, beta=gamma-theta, gamma is a pressure angle when the plunger (5) is not obliquely installed,θ is the plunger inclination angle;
lateral force N of plunger (5) and plunger hole inner wall of rotor cylinder body (3) 1 And N 2 And N 1 And N 2 Induced friction force F f1 And F f2 ；
F f1 ＝f 1 N 1 (9)
F f2 ＝f 1 N 2 (10)
F1 in the formulas (9) and (10) is a friction factor between the plunger (5) and the plunger hole of the rotor cylinder body (3);
simplifying all forces towards the centre of the roller (6) to obtain a force and moment balance equation set, i.e
F t -F f3 cosβ-F c cosθ+F b sinθ-F a sinθ-F d +N 1 -N 2 ＝0 (11)
-F r -F f3 sinβ+F b cosθ-F a cosθ+F c sinθ+F p -F f1 -F f2 ＝0 (12)
-F f3 R-N 1 (L 1 -(L 4 -L 3 )/3)+N 2 (L 1 -L 4 +L 3 /3)-F f1 d/2+F f2 d/2+(F c cosθ+F d )L 2 ＝0 (13)
In the formulas (11), (12) and (13), θ is the inclination angle of the plunger hole of the rotor cylinder (3) relative to the radius rotation reverse direction of the rotor cylinder (3), L 1 For the nominal length of the plunger (5) -roller (6), L 2 Is the distance from the center of mass of the plunger (5) -roller (6) to the center of the roller (6), L 3 Is N 2 Length of action of (L) 4 -L 3 ) Is N 2 Length of action, L 4 For the contact length of the plunger (5) in the plunger hole of the rotor cylinder (3), the contact length is changed along with the movement of the plunger (5) and has L 4 ＝L 0 +ρ-ρ min Wherein L is 0 Is the shortest contact length ρ when the roller (6) is at the maximum diameter position min The minimum pole diameter of the inner curve stator guide rail (2), R is the radius of the roller (6);
because the equation set has four unknowns, one equation is added to solve, so according to the triangle similarity principle, the method can be used for obtaining:
since this type of motor is characterized by a high torque at low speed and stable rotation at very low rotational speeds, it generates negligible inertial and centrifugal forces, while the rollers (6) run on the inner curved stator rail (2) to generate a friction force F f3 Much less than other forces, negligible; solving for N based on the above assumption 1 And N 2 Induced friction force F f1 And F f2 Reaction force F of inner curve stator guide rail (2) to roller (6) n ；
Bringing equation (14) into equation (13) to solve for L 3 ；
Wherein, K is a structural parameter,
s2, for an inner curve radial plunger motor, analyzing the problem of inclined installation of a plunger (5) -a roller (6) mainly in an oil inlet area; when high-pressure oil output by the hydraulic pump flows into the plunger cavity (9) of the motor through various control valves, the bottom of the plunger (5) is under the action of the high-pressure oil, so that the plunger (5) -the roller (6) are pushed by the plunger to cling to the inner surface of the inner curve stator guide rail (2) to extend outwards; however, when the plunger (5) -roller (6) is radially mounted in the plunger hole of the rotor cylinder (3), the lateral force applied to the plunger (5) -roller (6) is larger due to the larger pressure angle beta, so in order to reduce the problem that the lateral force applied to the plunger (5) -roller (6) is larger, the plunger (5) -roller (6) is mounted along the rotation opposite direction inclined angle theta of the rotor cylinder (3), and the lateral force N is smaller 1 And N 2 The inclination angle theta gradually decreases as the value increases, but there is also a problem in that the reaction force F of the inner curve stator rail (2) to the roller (6) n Also gradually decreases as the value of the inclination angle θ increases, the reaction force F n The tangential component force of the (2) is the power for pushing the rotor cylinder body 3 to rotate, so that the inclination angle theta cannot be increased limitlessly, and the output efficiency of the inner curve radial plunger motor needs to be comprehensively considered;
step S3, selecting the inclination angle theta of the plunger according to the inclination angle of the vane pump vane, wherein the inclination angle of the vane pump is generally 1/2 of the maximum pressure angle, and the maximum pressure angle of the inner curve radial plunger motor is 27.9 degrees through the calculation and analysis of the formulas (1) to (18) in the step S1, so that 14 degrees are selected as the inclination angle theta of the plunger (5) under comprehensive consideration;
step S4, a pressure equalizing groove (8) is formed in the circumferential side wall of the plunger (5), so that oil can flow into the side wall of the plunger (5) to achieve a lubricating effect, movement of the plunger (5) in a plunger hole of the rotor cylinder body (3) is facilitated, and friction factors f of the plunger (5) and the plunger hole side wall of the rotor cylinder body (3) are reduced 1 As can be seen from the analyses of the above formulas (1) - (18), after the plunger (5) improved at the same position is obliquely installed, the contact force N of the plunger (5) -roller (6) in the plunger hole inner wall of the rotor cylinder body (3) 1 And N 2 Smaller than in radial mounting, so that the friction force F caused thereby f1 And F f2 The design reduces friction and impact between the plunger (5) and the plunger hole of the rotor cylinder body (3), reduces energy loss of the motor and abrasion of the plunger (5) and the plunger hole of the rotor cylinder body (3), optimizes leakage condition of the plunger cavity (9), enables pressure flow pulsation of the plunger cavity (9) to be more stable, greatly improves movement condition of the plunger (5) -roller (6), and accordingly reduces noise and vibration generation of the system, improves comfort of working environment and reduces mechanical fatigue of mechanical equipment.
Compared with the prior art, the application has the beneficial effects that:
(1) The impact load level is reduced as follows: the plunger is provided with the pressure equalizing grooves, so that the plunger is in a good stress balance state, and the impact load level is greatly reduced. Because the effect of pressure equalizing groove makes it receive more balanced strength distribution around the plunger, its stress state obtains effective balance, adopts gray circle to seal on the plunger simultaneously, is favorable to preventing the leakage of fluid between plunger and the rotor cylinder body plunger hole. Because the fluctuation of the flow rate and the pressure of the plunger cavity is large, the force applied by the plunger-roller is suddenly increased, so that the plunger can generate impact load on the inner curve stator guide rail, and the impact load on the hydraulic motor can be reduced by the structure. The innovative design enables the impact load of the plunger in the movement process to be remarkably reduced, so that the reliability and stability of the whole system are improved. Whether noise is reduced, vibration is slowed down, or the service life of system components is prolonged, providing the plunger with a pressure equalizing groove and mounting the gurley as an inner curve radial plunger motor provides considerable benefits.
(2) Plunger and plunger bore wear is reduced, leakage is reduced, as follows: the traditional plunger radial installation mode is easy to increase the lateral force between the plunger and the plunger hole of the rotor cylinder body, the abrasion between the plunger and the plunger hole is increased, the leakage of oil in a plunger cavity is caused, the innovative plunger installation mode greatly improves the defect of the transmission mode of an inner curve radial plunger motor, the plunger aperture on the rotor cylinder body is arranged along the inclination angle theta of the rotor cylinder body in the opposite direction of rotation, the theta angle is 14 degrees, and the problems of overlarge lateral force, serious friction and abrasion of the plunger and the plunger Kong Jian on the rotor cylinder body are effectively solved. The application optimizes the flow leakage of the plunger cavity, realizes more stable pressure flow output and obviously improves the movement condition of the plunger assembly. The innovation not only reduces system noise and vibration, but also has important significance for improving motor performance, and meets the increasing demands on motor performance in the market.
(3) The low-speed state is stable, and the working performance is good, as follows: the lateral force between the plunger and the plunger hole of the rotor cylinder body can lead to abrasion of the plunger and the plunger hole wall of the rotor cylinder body, the gap between the plunger and the plunger hole wall of the rotor cylinder body is increased, leakage of oil is caused, meanwhile, friction between the plunger and the plunger hole wall of the rotor cylinder body can generate heat, certain influence can be caused on the oil, and leakage of the oil is also easy to cause. In the application, the pressure equalizing grooves and the Gelai rings are arranged on the circumferential side wall of the plunger, and the plunger is obliquely arranged, so that the abrasion between the plunger and the wall of the plunger hole of the rotor cylinder body can be optimized, the fluctuation of the flow in the plunger cavity of the rotor cylinder body can be effectively slowed down, and the fluctuation of the output rotating speed of the motor is further optimized, so that the motor can stably operate in a low-speed state, and the structural working performance is good.
Drawings
In order to more clearly illustrate the embodiments or the technical solutions in the prior art, the following description will briefly introduce the drawings that are needed in the embodiments or the description of the prior art, it is obvious that the drawings in the following description are only some embodiments of the application, and that other drawings can be obtained according to these drawings without inventive effort for a person skilled in the art.
Fig. 1 is a schematic structural view of an inner curve radial plunger motor with a plunger mounted obliquely according to an embodiment of the present application.
Fig. 2 is a schematic diagram of a plunger-roller structure of a motor according to an embodiment of the present application.
Fig. 3 is a schematic view of a rotor cylinder plunger hole tilting structure according to an embodiment of the present application.
Fig. 4 is a schematic diagram of a plunger-roller force analysis according to an embodiment of the present application.
Fig. 5 illustrates the effect of a plunger tilt mounting on lateral and reaction forces provided by an embodiment of the present application.
In the figure: the motor comprises a motor shell 1, an inner curve stator guide rail 2, a rotor cylinder body 3, a main shaft 4, a plunger 5, a roller 6, a Gelai ring 7, a pressure equalizing groove 8, a plunger cavity 9 and an oil inlet and outlet 10.
Detailed Description
The technical solutions in the embodiments of the present application will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present application. It will be apparent that the described embodiments are only some, but not all, embodiments of the application. All other embodiments, which can be made by those skilled in the art based on the embodiments of the application without making any inventive effort, are intended to fall within the scope of the application.
Aiming at the problems that the friction force of a plunger in a plunger hole of a rotor cylinder body is increased to cause the loss of motor energy and the abrasion of the wall of the plunger hole due to the overlarge lateral force of the plunger in the radial plunger motor of the inner curve, the application changes the traditional plunger and the radial installation method of the plunger hole of the rotor cylinder body, designs a novel radial plunger motor with the plunger obliquely installed in the inner curve, and the rollers in the plunger hole of the rotor cylinder body are arranged along the inclination angle theta in the rotation reverse direction of the rotor cylinder body, thereby reducing the lateral force of the motor, reducing the friction force and abrasion, reducing the risk of leakage of the flow of the plunger cavity, further improving the output performance and the working efficiency of the motor, optimizing the output characteristic of the motor and prolonging the service life of the motor, and ensuring that the radial plunger motor with the inner curve can better meet the market demand.
Specifically, as shown in fig. 1, 2 and 3, an embodiment of the present application provides a schematic structural diagram of an inner curve radial plunger motor with a plunger mounted obliquely. The inner curve radial plunger motor comprises a motor housing 1, an inner curve stator rail 2, a rotor cylinder 3, a main shaft 4, a plunger 5, rollers 6 and a gurley 7. The inner curve stator guide rail 2 is arranged on the inner side of the coaxial line of the motor shell 1, the inner side of the inner curve stator guide rail 2 is provided with a rotor cylinder body 3, and the center of the rotor cylinder body 3 is connected with the main shaft 4 through a spline; the plunger 5 is mounted in a plunger hole in the rotor cylinder 3, and the roller 6 is mounted inside a groove of the plunger 5. As shown in fig. 3, the plunger aperture on the rotor cylinder 3 is set along the rotation opposite direction of the rotor cylinder 3 by an inclination angle θ, which is an angle between the line connecting the center position of the edge of the plunger 5 with the center position of the spindle 4 and the line connecting the center position of the edge of the plunger 5 with the center position of the roller 6, and is preferably 14 °. In the embodiment, the plunger hole diameter on the rotor cylinder body 3 is inclined by a certain angle along the rotation reverse direction of the rotor, so that the plunger 5 is easier to throw out and is more closely attached to the inner surface of the inner curve stator guide rail 2, and the impact of a plunger 5 assembly on the inner surface of the stator guide rail is reduced.
In fig. 2, in combination with fig. 1, the number of plungers 5 is 8, and 8 plungers 5 are uniformly fitted in plunger holes in the circumferential direction of the rotor cylinder (3); adjacent plungers 5 are spaced at an angle of 45 deg. to each other. In this embodiment, the plunger 5 is provided with a pressure equalizing groove 8 on the circumferential side wall thereof, and a gray ring 7 is installed, and the gray ring 7 is used for preventing leakage of oil between the plunger 5 and the plunger hole on the rotor cylinder 3, thereby further improving energy-saving efficiency. The pressure equalizing groove 8 is arranged to lubricate the friction between the plunger and the plunger hole of the rotor cylinder, and meanwhile, the high-pressure oil in the plunger cavity of the rotor cylinder flows into the pressure equalizing groove, so that the pressure applied to the plunger is the same on the same circumference of the plunger, the hydraulic clamping force is reduced, the abrasion between the plunger and the plunger hole of the rotor cylinder is reduced, and the service life of the plunger and the rotor cylinder is prolonged.
The number of the pressure equalizing grooves 8 is preferably 5, each pressure equalizing groove 8 is an annular rectangular groove and rotates around the plunger 5 for one circle, and the pressure equalizing grooves 8 are designed to enable oil to flow into the side wall of the plunger 5 to achieve a lubricating effect, so that the movement of the plunger 5 in the plunger hole of the rotor cylinder body 3 is facilitated, and the output characteristic of a motor is improved. Wherein, friction force calculation formula is: f=fn, where F is the coefficient of friction and N is the lateral force of the plunger against the inner wall of the plunger hole of the rotor cylinder.
As shown in fig. 3, a plunger cavity 9 is arranged on the edge of the plunger 5, an oil inlet and outlet 10 is arranged on the central position of one side of the plunger cavity 9 facing the main shaft 4, and flow passages corresponding to the oil inlet and outlet 10 are arranged inside the inner curve radial plunger motor. In the embodiment, oil in a plunger cavity of the hydraulic motor flows in from an oil inlet and outlet 10, the plunger 5-roller 6 is acted by high-pressure oil, and is tightly adhered to the inner surface of the inner curve stator guide rail 2 to extend outwards, and meanwhile, the inner curve stator guide rail 2 gives a reaction force to the plunger 5-roller 6 to push the rotor cylinder body 3 to rotate so as to drive the main shaft 4 to rotate. The inclination angle of the plunger hole on the rotor cylinder body 3 can reduce the acute angle-pressure angle clamped between the stress direction and the movement direction, and further reduce the reaction force of the inner curve stator guide rail to the roller, so that the lateral force born by the plunger is reduced, the abrasion loss of the plunger and the plunger hole of the rotor cylinder body is reduced, and the inclination angle of the plunger hole on the rotor cylinder body 3 is 14 degrees.
The application also provides an installation method of the inner curve radial plunger motor for obliquely installing the plunger, wherein the inner curve radial plunger motor adopts the inner curve radial plunger motor in the embodiment, and the installation method of the plunger comprises the following steps:
step S1, calculating an installation inclination angle theta of the plunger 5 by carrying out stress analysis on the plunger 5-roller 6, wherein the inclination angle theta is shown in fig. 3, and is an included angle between a connecting line of the central position of the edge of the plunger 5 and the central position of the spindle 4 and a connecting line of the central position of the edge of the plunger 5 and the central position of the roller 6, and the specific calculation process is as follows, as shown in fig. 4:
hydraulic pressure generated by pressure oil flowing from the oil inlet/outlet port 10 into the plunger chamber 9 on the plunger 5:
in the formula (1), d is the diameter of the plunger 5, and P is the pressure of the plunger cavity 9;
inertial force generated by the movement of the plunger 5-roller 6 relative to the rotor cylinder 3:
in the formula (2), m is the mass of a plunger 5-roller 6, ω is the angular velocity of a motor rotor cylinder 3, ρ is the pole diameter from the center of the pole of the inner curve stator guide rail 2 to the center of the roller 6,an angle of rotation for the rotor cylinder 3;
centrifugal force generated by the movement of the plungers 5-rollers 6 relative to the rotor cylinder 3:
F b ＝mω 2 ρ g (3)
in formula (3), ρ g The pole diameter from the center of the pole of the inner curve stator guide rail 2 to the mass center of the plunger 5-roller 6;
motor angular acceleration causes inertial forces:
F c ＝mρ g ε (4)
in the formula (4), epsilon is motor angular acceleration;
the plunger 5-roller 6 motion is a pulling motion, and the inertial force generated by the coriolis acceleration:
friction generated by the movement of the rollers 5 on the inner curved stator rail 2:
F f3 ＝f 2 F n (6)
in the formula (6), f 2 For the rolling friction coefficient, F, between the rollers 6 and the inner curved stator rail 2 n Stator guide rail with inner curve2 reaction force against the roller 6;
reaction force F of inner curve stator guide rail 2 to roller 6 n Decomposed into tangential force F t And radial force F r
F t ＝F n sinβ (7)
F r ＝F n cosβ (8)
In the formulas (7) and (8), β is a pressure angle, β=γ—θ, γ is a pressure angle when the plunger 5 is not obliquely mounted,θ is the plunger inclination angle;
lateral force N of plunger 5 and plunger hole inner wall of rotor cylinder 3 1 And N 2 And N 1 And N 2 Induced friction force F f1 And F f2 ；
F f1 ＝f 1 N 1 (9)
F f2 ＝f 1 N 2 (10)
F1 in formulas (9) and (10) is the friction factor between the plunger 5 and the plunger hole of the rotor cylinder 3;
simplifying all forces towards the centre of the roller 6 to obtain a force and moment balance equation set, i.e
F t -F f3 cosβ-F c cosθ+F b sinθ-F a sinθ-F d +N 1 -N 2 ＝0 (11)
-F r -F f3 sinβ+F b cosθ-F a cosθ+F c sinθ+F p -F f1 -F f2 ＝0 (12)
-F f3 R-N 1 (L 1 -(L 4 -L 3 )/3)+N 2 (L 1 -L 4 +L 3 /3)-F f1 d/2+F f2 d/2+(F c cosθ+F d )L 2 ＝0 (13)
In the formulas (11), (12) and (13), θ is an inclination angle of the plunger hole of the rotor cylinder 3 in the opposite direction of the radial rotation of the rotor cylinder 3, L 1 L being the nominal length of the plunger 5-roller 6 2 L is the distance from the center of mass of the plunger 5-roller 6 to the center of the roller 6 3 Is N 2 Length of action of (L) 4 -L 3 ) Is N 2 Length of action, L 4 For the contact length of the plunger 5 in the plunger hole of the rotor cylinder 3, the contact length varies with the movement of the plunger 5, and has L 4 ＝L 0 +ρ-ρ min Wherein L is 0 For the shortest contact length (roller 6 is in the maximum radial position), ρ min The minimum pole diameter of the inner curve stator guide rail 2 is set, and R is the radius of the roller 6;
because the equation set is composed of four unknowns, one equation is added to solve, so according to the triangle similarity principle, the method can be used for obtaining:
since this type of motor is characterized by a high torque at low speed and stable rotation at very low rotational speeds, it generates negligible inertial and centrifugal forces, while the rollers 6 run on the inner curved stator rail 2 to generate a friction force F f3 Much less than other forces, negligible; solving for N based on the above assumption 1 And N 2 Induced friction force F f1 And F f2 Reaction force F of inner curve stator rail 2 to roller 6 n 。
Bringing equation (14) into equation (13) to solve for L 3 ；
Wherein, K is a structural parameter,
s2, for an inner curve radial plunger motor, analyzing the problem of inclined installation of a plunger 5-roller 6 mainly in an oil inlet area; when high-pressure oil output by the hydraulic pump flows into the plunger cavity 9 of the motor through various control valves, the bottom of the plunger 5 is under the action of the high-pressure oil to push the plunger 5-roller 6 to be clung to the inner surface of the inner curve stator guide rail 2 and extend outwards; however, when the plunger 5-roller 6 is radially mounted in the plunger hole of the rotor cylinder 3, since the pressure angle β is large and the lateral force applied to the plunger 5-roller 6 is also large, in order to reduce the problem that the lateral force applied to the plunger 5-roller 6 is large, the plunger 5-roller 6 is mounted along the rotation reverse direction inclination angle θ of the rotor cylinder 3, as shown in fig. 5, the lateral force N 1 And N 2 The inclination angle θ gradually decreases as the value increases, but there is also a problem in that the reaction force F of the inner curve stator rail 2 to the roller 6 n Also gradually decreases as the value of the inclination angle θ increases, the reaction force F n The tangential component force of the (2) is the power for pushing the rotor cylinder body 3 to rotate, so that the inclination angle theta cannot be increased limitlessly, and the output efficiency of the inner curve radial plunger motor needs to be comprehensively considered;
step S3, the inclination angle theta of the plunger is selected according to the inclination angle of the vane pump, the inclination angle of the vane pump generally takes 1/2 of the maximum pressure angle, and the maximum pressure angle of the inner curve radial plunger motor is 27.9 degrees through the calculation and analysis of the formulas (1) to (18) in the step S1, so that 14 degrees are selected as the inclination angle theta of the plunger 5 under comprehensive consideration;
step S4, the plunger 5 is obliquely arranged, so that the lateral force can be reduced, and the plunger 5-roller 6 can be more closely attached to the inner surface of the inner curve stator guide rail 2, and the impact of the plunger 5-roller 6 on the inner surface of the inner curve stator guide rail 2 is reduced; at the same timeThe pressure equalizing grooves 8 are formed in the circumferential side wall of the plunger 5, so that oil can flow into the side wall of the plunger 5 to lubricate the side wall of the plunger 5, movement of the plunger 5 in the plunger hole of the rotor cylinder 3 is facilitated, and friction factors f of the plunger 5 and the side wall of the plunger hole of the rotor cylinder 3 are reduced 1 As can be seen from the analyses of the above formulas (1) - (18), after the plunger 5 is obliquely installed at the same position, the contact force N of the plunger 5-roller 6 in the plunger hole inner wall of the rotor cylinder 3 1 And N 2 Smaller than in radial mounting, so that the friction force F caused thereby f1 And F f2 The design reduces friction and impact between the plunger 5 and the plunger hole of the rotor cylinder body 3, reduces energy loss of the motor and abrasion of the plunger 5 and the plunger hole of the rotor cylinder body 3, optimizes leakage condition of the plunger cavity 9, enables pressure flow pulsation of the plunger cavity 9 to be more stable, greatly improves movement condition of the plunger 5-roller 6, reduces noise and vibration generation of a system, improves comfort of working environment and reduces mechanical fatigue of mechanical equipment.
The present application is not limited to the above embodiments, and any modifications, equivalent substitutions and improvements made by those skilled in the art within the scope of the present application are intended to be included within the scope of the present application; various modifications and changes may be made by one skilled in the art without departing from the spirit and scope of the application, which is therefore intended to be covered by the appended claims.
Claims (6)
1. An inner curve radial plunger motor with a plunger obliquely arranged is characterized by comprising a motor shell (1), an inner curve stator guide rail (2), a rotor cylinder body (3), a main shaft (4), a plunger (5), a roller (6) and a Gelai ring (7); the inner curve stator guide rail (2) is arranged on the inner side of a coaxial line of the motor shell (1), the rotor cylinder body (3) is arranged on the inner side of the inner curve stator guide rail (2), and the center of the rotor cylinder body (3) is connected with the main shaft (4) through a spline; the plunger (5) is arranged in a plunger hole on the rotor cylinder body (3), the roller (6) is arranged in a groove of the plunger (5), and the aperture of the plunger on the rotor cylinder body (3) is arranged along the inclination angle theta of the rotor cylinder body (3) in the opposite direction of rotation, wherein the theta is 14 degrees; the plunger (5) is provided with a pressure equalizing groove (8) on the circumferential side wall of the plunger, a Gelai ring (7) is arranged on the plunger, and the Gelai ring (7) is used for preventing oil from leaking between the plunger (5) and a plunger hole on the rotor cylinder body (3).
2. An inner curve radial plunger motor with a plunger mounted obliquely according to claim 1, characterized in that the number of plungers (5) is 8, 8 of the plungers (5) being fitted evenly in the plunger holes in the circumferential direction of the rotor cylinder (3).
3. An inner curve radial plunger motor with a plunger mounted obliquely according to claim 2, characterized in that two adjacent plungers (5) are spaced at an angle of 45 ° to each other.
4. The plunger obliquely-installed inner curve radial plunger motor according to claim 1, wherein a plunger cavity (9) is arranged on the edge of the plunger (5), and an oil inlet and outlet port (10) is arranged on the central position of one side of the plunger cavity (9) towards the main shaft (4).
5. The plunger obliquely-mounted inner curve radial plunger motor according to claim 1, wherein the number of the pressure equalizing grooves (8) on the circumferential side wall of each plunger (5) is 5, each pressure equalizing groove (8) is an annular rectangular groove and surrounds the plunger (5) for one rotation, and the pressure equalizing grooves (8) are used for enabling oil to flow into the side wall of the plunger (5) for lubrication, so that the movement of the plunger (5) in the plunger hole of the rotor cylinder (3) is facilitated, and the output characteristic of the motor is improved.
6. A method of installing an inner curve radial plunger motor for plunger tilt installation employing an inner curve radial plunger motor according to claims 1 to 5, the method of plunger tilt installation comprising:
step S1, calculating the installation inclination angle theta of the plunger (5) by carrying out stress analysis on the plunger (5) -roller (6), wherein the concrete calculation process is as follows:
hydraulic pressure generated by pressure oil flowing into a plunger cavity (9) of the plunger (5) from an oil inlet and outlet (10):
in the formula (1), d is the diameter of the plunger 5, and P is the pressure of the plunger cavity 9;
inertial force generated by the movement of the plunger (5) -roller (6) relative to the rotor cylinder 3:
in the formula (2), m is the mass of a plunger (5) -a roller (6), ω is the angular velocity of a motor rotor cylinder (3), ρ is the polar diameter from the center of the pole of the inner curve stator guide rail (2) to the center of the roller (6),an angle of rotation for the rotor cylinder (3);
centrifugal force generated by the movement of the plunger (5) -roller (6) relative to the rotor cylinder (3):
F b ＝mω 2 ρ g (3)
in formula (3), ρ g The pole diameter from the pole center of the inner curve stator guide rail (2) to the mass center of the plunger (5) -roller (6);
motor angular acceleration causes inertial forces:
F c ＝mρ g ε (4)
in the formula (4), epsilon is motor angular acceleration;
the plunger (5) -roller (6) motion is a dragging motion, and the inertial force generated by the God acceleration:
friction force generated by the movement of the roller (5) on the inner curve stator guide rail (2):
F f3 ＝f 2 F n (6)
in the formula (6), f 2 Is the rolling friction coefficient between the roller (6) and the inner curve stator guide rail (2), F n The reaction force of the inner curve stator guide rail (2) to the roller (6);
reaction force F of inner curve stator guide rail (2) to roller (6) n Decomposed into tangential force F t And radial force F r
F t ＝F n sinβ (7)
F r ＝F n cosβ (8)
In the formulas (7) and (8), beta is a pressure angle, beta=gamma-theta, gamma is a pressure angle when the plunger (5) is not obliquely installed,θ is the plunger inclination angle;
lateral force N of plunger (5) and plunger hole inner wall of rotor cylinder body (3) 1 And N 2 And N 1 And N 2 Induced friction force F f1 And F f2 ；
F f1 ＝f 1 N 1 (9)
F f2 ＝f 1 N 2 (10)
F1 in the formulas (9) and (10) is a friction factor between the plunger (5) and the plunger hole of the rotor cylinder body (3);
simplifying all forces towards the centre of the roller (6) to obtain a force and moment balance equation set, i.e
F t -F f3 cosβ-F c cosθ+F b sinθ-F a sinθ-F d +N 1 -N 2 ＝0 (11)
-F r -F f3 sinβ+F b cosθ-F a cosθ+F c sinθ+F p -F f1 -F f2 ＝0 (12)
-F f3 R-N 1 (L 1 -(L 4 -L 3 )/3)+N 2 (L 1 -L 4 +L 3 /3)-F f1 d/2+F f2 d/2+(F c cosθ+F d )L 2 ＝0 (13)
In the formulas (11), (12) and (13), θ is the inclination angle of the plunger hole of the rotor cylinder (3) relative to the radius rotation reverse direction of the rotor cylinder (3), L 1 For the nominal length of the plunger (5) -roller (6), L 2 Is the distance from the center of mass of the plunger (5) -roller (6) to the center of the roller (6), L 3 Is N 2 Length of action of (L) 4 -L 3 ) Is N 2 Length of action, L 4 For the contact length of the plunger (5) in the plunger hole of the rotor cylinder (3), the contact length is changed along with the movement of the plunger (5) and has L 4 ＝L 0 +ρ-ρ min Wherein L is 0 Is the shortest contact length ρ when the roller (6) is at the maximum diameter position min The minimum pole diameter of the inner curve stator guide rail (2), R is the radius of the roller (6);
because the equation set has four unknowns, one equation is added to solve, so according to the triangle similarity principle, the method can be used for obtaining:
since this type of motor is characterized by a high torque at low speed and stable rotation at very low rotational speeds, it generates negligible inertial and centrifugal forces, while the rollers (6) run on the inner curved stator rail (2) to generate a friction force F f3 Much less than other forces, negligible; solving for N based on the above assumption 1 And N 2 Induced friction force F f1 And F f2 Reaction force F of inner curve stator guide rail (2) to roller (6) n ；
Bringing equation (14) into equation (13) to solve for L 3 ；
Wherein, K is a structural parameter,
s2, for an inner curve radial plunger motor, analyzing the problem of inclined installation of a plunger (5) -a roller (6) mainly in an oil inlet area; when high-pressure oil output by the hydraulic pump flows into the plunger cavity (9) of the motor through various control valves, the bottom of the plunger (5) is under the action of the high-pressure oil, so that the plunger (5) -the roller (6) are pushed by the plunger to cling to the inner surface of the inner curve stator guide rail (2) to extend outwards; however, when the plunger (5) -roller (6) is radially mounted in the plunger hole of the rotor cylinder (3), the lateral force applied to the plunger (5) -roller (6) is larger due to the larger pressure angle beta, so in order to reduce the problem that the lateral force applied to the plunger (5) -roller (6) is larger, the plunger (5) -roller (6) is mounted along the rotation opposite direction inclined angle theta of the rotor cylinder (3), and the lateral force N is smaller 1 And N 2 The inclination angle theta gradually decreases as the value increases, but there is also a problem in that the reaction force F of the inner curve stator rail (2) to the roller (6) n Also gradually decreases as the value of the inclination angle θ increases, the reaction force F n The tangential component force of the (2) is the power for pushing the rotor cylinder body 3 to rotate, so that the inclination angle theta cannot be increased limitlessly, and the output efficiency of the inner curve radial plunger motor needs to be comprehensively considered;
step S3, selecting the inclination angle theta of the plunger according to the inclination angle of the vane pump vane, wherein the inclination angle of the vane pump is generally 1/2 of the maximum pressure angle, and the maximum pressure angle of the inner curve radial plunger motor is 27.9 degrees through the calculation and analysis of the formulas (1) to (18) in the step S1, so that 14 degrees are selected as the inclination angle theta of the plunger (5) under comprehensive consideration;
step S4, a pressure equalizing groove (8) is formed in the circumferential side wall of the plunger (5), so that oil can flow into the side wall of the plunger (5) to achieve a lubricating effect, movement of the plunger (5) in a plunger hole of the rotor cylinder body (3) is facilitated, and friction factors f of the plunger (5) and the plunger hole side wall of the rotor cylinder body (3) are reduced 1 As can be seen from the analyses of the above formulas (1) - (18), after the plunger (5) improved at the same position is obliquely installed, the contact force N of the plunger (5) -roller (6) in the plunger hole inner wall of the rotor cylinder body (3) 1 And N 2 Smaller than in radial mounting, so that the friction force F caused thereby f1 And F f2 The design reduces friction and impact between the plunger (5) and the plunger hole of the rotor cylinder body (3), reduces energy loss of the motor and abrasion of the plunger (5) and the plunger hole of the rotor cylinder body (3), optimizes leakage condition of the plunger cavity (9), enables pressure flow pulsation of the plunger cavity (9) to be more stable, greatly improves movement condition of the plunger (5) -roller (6), and accordingly reduces noise and vibration generation of the system, improves comfort of working environment and reduces mechanical fatigue of mechanical equipment.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202311054192.XA CN117108442A (en) | 2023-08-21 | 2023-08-21 | Inner curve radial plunger motor with obliquely-installed plunger and installation method thereof |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202311054192.XA CN117108442A (en) | 2023-08-21 | 2023-08-21 | Inner curve radial plunger motor with obliquely-installed plunger and installation method thereof |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN117108442A true CN117108442A (en) | 2023-11-24 |
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ID=88806957
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202311054192.XA Pending CN117108442A (en) | 2023-08-21 | 2023-08-21 | Inner curve radial plunger motor with obliquely-installed plunger and installation method thereof |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN117108442A (en) |
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2023
- 2023-08-21 CN CN202311054192.XA patent/CN117108442A/en active Pending
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