CN111946609A - Method for measuring thickness of oil film of flow distribution pair - Google Patents

Method for measuring thickness of oil film of flow distribution pair Download PDF

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Publication number
CN111946609A
CN111946609A CN202010858770.5A CN202010858770A CN111946609A CN 111946609 A CN111946609 A CN 111946609A CN 202010858770 A CN202010858770 A CN 202010858770A CN 111946609 A CN111946609 A CN 111946609A
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Prior art keywords
oil film
flow distribution
distribution pair
angle
thickness
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Inventor
员海涛
李永堂
梁涛
仉志强
刘志奇
王鲁军
皮之中
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Tai'an Hualu Metalforming Machine Tool Co ltd
Taiyuan University of Science and Technology
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Tai'an Hualu Metalforming Machine Tool Co ltd
Taiyuan University of Science and Technology
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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
    • F04B51/00—Testing machines, pumps, or pumping installations
    • 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
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01B—MEASURING LENGTH, THICKNESS OR SIMILAR LINEAR DIMENSIONS; MEASURING ANGLES; MEASURING AREAS; MEASURING IRREGULARITIES OF SURFACES OR CONTOURS
    • G01B21/00—Measuring arrangements or details thereof, where the measuring technique is not covered by the other groups of this subclass, unspecified or not relevant
    • G01B21/02—Measuring arrangements or details thereof, where the measuring technique is not covered by the other groups of this subclass, unspecified or not relevant for measuring length, width, or thickness
    • G01B21/08—Measuring arrangements or details thereof, where the measuring technique is not covered by the other groups of this subclass, unspecified or not relevant for measuring length, width, or thickness for measuring thickness

Abstract

The invention provides a method for measuring the thickness of an oil film of a flow distribution pair, which is characterized in that the total wedge angle and the azimuth angle of the oil film of the flow distribution pair are determined according to the measured oil film thickness data of a position point adopted by the flow distribution pair; calculating the supporting force of the mixed friction area according to the total wedge angle and the rough contact surface G-S model; and determining the minimum oil film thickness by establishing a plunger cylinder axial force balance equation. The minimum oil film thickness obtained by the method is closer to an actual value, and important data are provided for the leakage amount of the flow distribution pair, the integral performance evaluation and the abrasion degree evaluation of the plunger type hydraulic component, so that the service life of the flow distribution pair is prolonged.

Description

Method for measuring thickness of oil film of flow distribution pair
Technical Field
The invention belongs to the technical field of hydraulic elements, and particularly relates to a method for measuring the thickness of an oil film of a flow distribution pair.
Background
Plunger type hydraulic pump, motor and hydraulic transformer are core elements of the hydrostatic transmission system. The thickness of the lubricating oil film between the valve plate and the cylinder body of the element greatly affects the leakage and the friction loss of the plunger element, and the larger the thickness of the oil film of the valve pair is, the larger the leakage is, and the volumetric efficiency of the axial plunger pump is affected; the smaller the thickness is, the wear is aggravated, and the service life of the thrust plate is influenced, so that the important thing is to grasp the change rule of the oil film thickness value of the thrust pair. The oil film of the flow distribution pair is actually a three-dimensional wedge-shaped body which changes at any moment and can be represented by a trigonometric function formed by the minimum oil film thickness, the azimuth angle and the wedge angle. The current method for testing the thickness of the oil film of the flow distribution pair cannot effectively analyze important information such as wedge angle influence factors of the oil film of the flow distribution pair and the abrasion degree of a flow distribution disc.
Disclosure of Invention
The invention aims to provide a method for measuring the thickness of an oil film of a flow distribution pair, which can effectively calculate the thickness of the oil film of the flow distribution pair, know the influence factors of the wedge angle of the oil film of the flow distribution pair and the abrasion degree of a flow distribution plate and prolong the service life of the flow distribution plate.
In order to realize the aim, the invention adopts the technical scheme that a method for measuring the thickness of an oil film of a flow distribution pair,
1. determining the axial force borne by the plunger cylinder:
a. the force of the plunger cavity on the port plate,
Figure RE-RE-267803DEST_PATH_IMAGE001
in the formula (I), the compound is shown in the specification,
Figure RE-RE-247261DEST_PATH_IMAGE002
in order to discharge the oil pressure of the pump,dis the inner diameter of the plunger cavity,Znumber of plunger chambers;
b. the acting force of the valve plate on the plunger cylinder,
Figure RE-RE-338582DEST_PATH_IMAGE004
in the formula (I), the compound is shown in the specification,r 1、r 2respectively is the inner diameter and the outer diameter of the sealing belt in the valve plate,r 3、r 4respectively is the inner diameter and the outer diameter of the outer sealing belt of the valve plate,rthe radius of any position point of the flow distribution oil film,θ i、θ jthe starting angle and the ending angle of a high-pressure distribution area of an oil film of the thrust plate are set;
2. displacement sensors are arranged at three points or a plurality of points outside the outer seal of the valve plate, and the wedge angle and the azimuth angle of the valve plate are determined according to the measured oil film thickness data of a plurality of position points of the valve plate:
a. the total thickness of the wedge-shaped oil film of the flow distribution pair is as follows:
Figure RE-RE-264950DEST_PATH_IMAGE005
Figure RE-RE-610481DEST_PATH_IMAGE006
in the formula (I), the compound is shown in the specification,
Figure RE-RE-964102DEST_PATH_IMAGE007
for the maximum thickness and the minimum thickness of the oil film of the flow distribution pair,
Figure RE-RE-513026DEST_PATH_IMAGE008
、
Figure RE-RE-243084DEST_PATH_IMAGE009
x of XY wedge angle of oil film of flow distribution pair caused by plunger cylinder force and moment balanceThe azimuth angle of Y is set to be,
Figure RE-RE-443122DEST_PATH_IMAGE010
the value range of (A) is 0.00005-0.0002,
Figure RE-RE-967644DEST_PATH_IMAGE011
、
Figure RE-RE-502399DEST_PATH_IMAGE012
the Z wedge angle and the Z azimuth angle of the oil film of the flow distribution pair caused by the coaxiality error of the plunger cylinder and the main shaft,
Figure RE-RE-770570DEST_PATH_IMAGE013
，
Figure RE-RE-825113DEST_PATH_IMAGE014
，
Figure RE-RE-786116DEST_PATH_IMAGE015
is the rotating angle of the plunger type cylinder,
Figure RE-RE-309632DEST_PATH_IMAGE016
for the abrasion wedge angle of the oil film of the distribution pair caused by the abrasion of the distribution pair,
Figure RE-RE-115914DEST_PATH_IMAGE017
is the outer diameter of the outer sealing belt of the flow distribution pair,
Figure RE-RE-290544DEST_PATH_IMAGE018
a polar angle of a certain position point of the oil film of the flow distribution pair;
b. assuming minimum gap thickness
Figure RE-RE-156869DEST_PATH_IMAGE019
Is equal to a fixed value, the value range is 0-10 um, and then any radius of the flow distribution pairrThe thickness of the gap is:
Figure RE-RE-666216DEST_PATH_IMAGE020
in the formula (I), the compound is shown in the specification,
Figure RE-RE-745031DEST_PATH_IMAGE021
is the included angle between the connecting line of the maximum oil film thickness point and the minimum oil film thickness point and the polar diameter,
Figure RE-RE-774167DEST_PATH_IMAGE022
the total wedge angle of the oil film of the flow distribution pair is expressed as
Figure RE-RE-76972DEST_PATH_IMAGE023
；
3. Calculating the supporting force generated in the mixed friction area along the axial direction of the plunger cylinder, wherein the plunger cylinder and the valve plate can generate local mixed friction contact near the minimum gap thickness point of the auxiliary supporting belt, the contact surface of the plunger cylinder and the valve plate is in wedge-shaped contact, and the bearing capacity of the contact peak in the contact areaWLoad force along the Z-axisF mixComprises the following steps:
Figure RE-RE-558769DEST_PATH_IMAGE025
in the formula (I), the compound is shown in the specification,n fis the number of contact peaks per unit area,
Figure RE-RE-441274DEST_PATH_IMAGE026
，σ e、σ 1respectively equivalent roughness and roughness of the surface profile of the port plate,R e=R 1/2，R e、R 1respectively the radius of the equivalent rough peak and the radius of the rough peak on the surface of the valve plate,θ imix、θ jmixa start angle and a final angle of the central angle corresponding to the frictional contact area, respectivelyθ imix=-π，θ jmix=π，
Figure RE-RE-75649DEST_PATH_IMAGE027
，E e、E 1、E 2Respectively is equivalent elastic modulus, elastic modulus of the surface material of the valve plate and elastic modulus of the surface material of the plunger cylinder,γ 1、γ 2respectively the Poisson's ratio of the surface material of the valve plate and the surface material of the plunger cylinder;
4. establishing a mechanical balance equation of the plunger cylinder in the axial direction,
Figure RE-RE-549356DEST_PATH_IMAGE028
；
5. and obtaining an oil film thickness curve of any position point of the flow distribution pair by adopting a four-stage for-cycle algorithm comprising a Z wedge angle, a wear wedge angle, an XY azimuth angle and the minimum oil film thickness, and obtaining a total wedge angle, a total azimuth angle, a Z wedge angle, a wear wedge angle, an XY azimuth angle and the minimum oil film thickness of the oil film of the flow distribution pair.
Further, the total azimuth angle obtained by the calculation in the steps 1-4
Figure RE-RE-518449DEST_PATH_IMAGE021
Within the variation range of (2), at a radiusr 1<r<r 2Or radiusr 3<r<r 4In the range of (1), surface material strengthening or wear-resisting treatment is carried out on the surface of a valve plate or a plunger cylinder contacted with a flow distribution pair oil film, and a circular pit micro array or a local texture structure is increased.
The oil film thickness measurement method has the advantages that the total wedge angle and the azimuth angle of the oil film of the flow distribution pair are determined according to the actually measured oil film thickness data of the position points adopted by the flow distribution pair; calculating the supporting force of the mixed friction area according to the total wedge angle and the rough contact surface G-S model; and determining the minimum oil film thickness by establishing a plunger cylinder axial force balance equation. The minimum oil film thickness obtained by the method is closer to an actual value, and important data are provided for the leakage amount of the flow distribution pair, the integral performance evaluation and the abrasion degree evaluation of the plunger type hydraulic component, so that the service life of the flow distribution pair is prolonged.
The other technical scheme of the invention is as follows: a method for measuring the thickness of an oil film of a flow distribution pair,
1. installing an eddy current displacement sensor at a T1 point outside the outer seal of the port plate, and measuring the thickness of a port pair oil film at the point;
2. the method comprises the steps of collecting oil film thickness measured data of three position points T1, T2 and T3 of a distribution pair of plunger type elements of the same type under different working conditions to form a data set, and determining an XY wedge angle and an XY azimuth angle of the distribution pair oil film of the distribution pair wedge oil film under different pressure, displacement and rotating speed working conditions
Figure RE-RE-939066DEST_PATH_IMAGE029
、
Figure RE-RE-942794DEST_PATH_IMAGE009
；
3. Obtaining a flow distribution pair oil film thickness curve at a T1 point,
a. the total thickness formula of the wedge-shaped oil film of the flow distribution pair is as follows:
Figure RE-RE-836669DEST_PATH_IMAGE031
b. and calculating to obtain an oil film thickness curve at a T1 point of the flow distribution pair by adopting a two-stage for-cycle algorithm comprising a Z wedge angle and a wear wedge angle, and obtaining a total wedge angle, a wear wedge angle and a Z wedge angle of the oil film of the flow distribution pair.
According to the technical scheme, the big data of the three-point oil film curve of the hydraulic pumps of the same model are utilized, and key parameters are obtained through calculation; and then a three-dimensional wedge-shaped body of the oil film of the flow distribution pair is obtained through a single displacement sensor on the flow distribution plate. The method further reduces the number of high-precision displacement sensors and the limitation of the installation space of the sensors. The total wedge angle and the abrasion wedge angle of the wedge-shaped oil film of the distribution pair are effectively obtained through the big data and the measured data obtained by the single sensor, and the service life of the distribution pair is further prolonged.
Drawings
FIG. 1 is a schematic diagram of a coordinate system of an oil film of a flow distribution pair, a wedge angle and an azimuth angle;
FIG. 2 is a 3-point test chart of an oil film of a flow distribution pair;
fig. 3, oil film thickness graph.
Detailed Description
In the case of the example 1, the following examples are given,
theoretical calculation and experimental tests are carried out on the axial plunger pump with the displacement of 40 ml/r.
A method for measuring the thickness of an oil film of a flow distribution pair,
1. determining the axial force borne by the plunger cylinder:
a. the force of the plunger cavity on the port plate,
Figure RE-RE-293058DEST_PATH_IMAGE032
in the formula (I), the compound is shown in the specification,
Figure RE-RE-517366DEST_PATH_IMAGE002
in order to discharge the oil pressure of the pump,dis the inner diameter of the plunger cavity,Znumber of plunger chambers;
b. the acting force of the valve plate on the plunger cylinder,
Figure RE-RE-110022DEST_PATH_IMAGE034
in the formula (I), the compound is shown in the specification,r 1、r 2respectively is the inner diameter and the outer diameter of the sealing belt in the valve plate,r 3、r 4respectively is the inner diameter and the outer diameter of the outer sealing belt of the valve plate,rthe radius of any position point of the flow distribution oil film,θ i、θ jthe starting angle and the ending angle of a high-pressure distribution area of an oil film of the thrust plate are set;
2. displacement sensors are arranged at three points and multiple points outside the outer seal of the valve plate, as shown in figure 2, data are recorded according to the oil film thickness of multiple position points of the valve pair, the wedge angle and the azimuth angle of the valve pair are determined,
a. the total thickness of the wedge-shaped oil film of the flow distribution pair is as follows:
Figure RE-RE-925531DEST_PATH_IMAGE036
Figure RE-RE-619949DEST_PATH_IMAGE038
in the formula (I), the compound is shown in the specification,
Figure RE-RE-647948DEST_PATH_IMAGE039
for the maximum thickness and the minimum thickness of the oil film of the flow distribution pair,
Figure RE-RE-360689DEST_PATH_IMAGE008
、
Figure RE-RE-81520DEST_PATH_IMAGE009
setting XY azimuth angle of XY wedge angle of oil film of flow distribution pair caused by plunger cylinder force and moment balance
Figure RE-RE-512501DEST_PATH_IMAGE040
=0.0001，
Figure RE-RE-78612DEST_PATH_IMAGE011
、
Figure RE-RE-172425DEST_PATH_IMAGE012
The Z wedge angle and the Z azimuth angle of the oil film of the flow distribution pair caused by the coaxiality error of the plunger cylinder and the main shaft,
Figure RE-RE-64158DEST_PATH_IMAGE013
，
Figure RE-RE-982435DEST_PATH_IMAGE015
is the rotating angle of the plunger type cylinder,
Figure RE-RE-352237DEST_PATH_IMAGE016
for the abrasion wedge angle of the oil film of the distribution pair caused by the abrasion of the distribution pair,
Figure RE-RE-773991DEST_PATH_IMAGE041
is the outer diameter of the outer sealing belt of the flow distribution pair,
Figure RE-RE-852936DEST_PATH_IMAGE018
a polar angle of a certain position point of the oil film of the flow distribution pair;
b. assuming minimum gap thickness
Figure RE-RE-992930DEST_PATH_IMAGE042
Is equal to a fixed value, the value range is 0-10 um, and then any radius of the flow distribution pairrThe thickness of the gap is:
Figure RE-RE-697581DEST_PATH_IMAGE044
in the formula (I), the compound is shown in the specification,
Figure RE-RE-239421DEST_PATH_IMAGE021
is the included angle between the connecting line of the maximum oil film thickness point and the minimum oil film thickness point and the polar diameter,
Figure RE-RE-987803DEST_PATH_IMAGE022
the total wedge angle of the oil film of the flow distribution pair is expressed as
Figure RE-RE-615094DEST_PATH_IMAGE045
；
3. Calculating the supporting force generated in the mixed friction area along the axial direction of the plunger cylinder, wherein the plunger cylinder and the valve plate can generate local mixed friction contact near the minimum gap thickness point of the auxiliary supporting belt, the contact surface of the plunger cylinder and the valve plate is in wedge-shaped contact, and the bearing capacity of the contact peak in the contact areaWLoad force along the Z-axisF mixComprises the following steps:
Figure RE-RE-326698DEST_PATH_IMAGE047
in the formula (I), the compound is shown in the specification,n fis the number of contact peaks per unit area,
Figure RE-RE-723044DEST_PATH_IMAGE048
，σ e、σ 1respectively equivalent roughness and roughness of the surface profile of the port plate,R e=R 1/2，R e、R 1respectively the radius of the equivalent rough peak and the radius of the rough peak on the surface of the valve plate,θ i、θ ja start angle and a final angle of the central angle corresponding to the frictional contact area, respectivelyθ i=-π，θ j=π，
Figure RE-RE-393060DEST_PATH_IMAGE027
，E e、E 1、E 2Respectively is equivalent elastic modulus, elastic modulus of the surface material of the valve plate and elastic modulus of the surface material of the plunger cylinder,γ 1、γ 2respectively the Poisson's ratio of the surface material of the valve plate and the surface material of the plunger cylinder;
4. establishing an axial mechanical balance equation of the plunger cylinder and determining the minimum oil film thickness
Figure RE-RE-976488DEST_PATH_IMAGE049
；
5. And (3) obtaining an oil film thickness curve of any position point of the flow distribution pair as shown in the figure 3 by adopting a four-stage for-circulation algorithm comprising a Z wedge angle, a worn wedge angle, an XY azimuth angle and the minimum oil film thickness, and obtaining a total wedge angle, a total azimuth angle, a Z wedge angle, a worn wedge angle and an XY azimuth angle of the oil film of the flow distribution pair.

Claims (3)

1. A method for measuring the thickness of an oil film of a flow distribution pair,
1. determining the axial force borne by the plunger cylinder:
a. the force of the plunger cavity on the port plate,
Figure 307965DEST_PATH_IMAGE001
in the formula (I), the compound is shown in the specification,
Figure 756263DEST_PATH_IMAGE002
in order to discharge the oil pressure of the pump,dis the inner diameter of the plunger cavity,Znumber of plunger chambers;
b. the acting force of the valve plate on the plunger cylinder,
Figure 67159DEST_PATH_IMAGE003
in the formula (I), the compound is shown in the specification,r 1、r 2respectively is the inner diameter and the outer diameter of the sealing belt in the valve plate,r 3、r 4respectively is the inner diameter and the outer diameter of the outer sealing belt of the valve plate,rthe radius of any position point of the flow distribution oil film,θ i、θ jthe starting angle and the ending angle of a high-pressure distribution area of an oil film of the thrust plate are set;
2. displacement sensors are arranged at three points or a plurality of points outside the outer seal of the valve plate, and the wedge angle and the azimuth angle of the valve plate are determined according to the measured oil film thickness data of a plurality of position points of the valve plate:
a. the total thickness of the wedge-shaped oil film of the flow distribution pair is as follows:
Figure 993527DEST_PATH_IMAGE004
Figure 89790DEST_PATH_IMAGE005
in the formula (I), the compound is shown in the specification,
Figure 443411DEST_PATH_IMAGE006
for the maximum thickness and the minimum thickness of the oil film of the flow distribution pair,
Figure 241602DEST_PATH_IMAGE007
、
Figure 971661DEST_PATH_IMAGE008
the XY azimuth angle of the XY wedge angle of the oil film of the flow distribution pair caused by the balance of the force and the moment of the plunger cylinder,
Figure 420966DEST_PATH_IMAGE009
the value range of (A) is 0.00005-0.0002,
Figure 945488DEST_PATH_IMAGE010
、
Figure 230976DEST_PATH_IMAGE011
the Z wedge angle and the Z azimuth angle of the oil film of the flow distribution pair caused by the coaxiality error of the plunger cylinder and the main shaft,
Figure 499146DEST_PATH_IMAGE012
，
Figure 304422DEST_PATH_IMAGE013
，
Figure 265425DEST_PATH_IMAGE014
is the rotating angle of the plunger type cylinder,
Figure 38209DEST_PATH_IMAGE015
for the abrasion wedge angle of the oil film of the distribution pair caused by the abrasion of the distribution pair,
Figure 313333DEST_PATH_IMAGE016
is the outer diameter of the outer sealing belt of the flow distribution pair,
Figure 487962DEST_PATH_IMAGE017
a polar angle of a certain position point of the oil film of the flow distribution pair;
b. assuming minimum gap thickness
Figure 603554DEST_PATH_IMAGE018
Is equal toSetting the value, wherein the value range is 0-10 um, and then any radius of the flow distribution pairrThe thickness of the gap is:
Figure 863634DEST_PATH_IMAGE019
in the formula (I), the compound is shown in the specification,
Figure 473607DEST_PATH_IMAGE020
is the included angle between the connecting line of the maximum oil film thickness point and the minimum oil film thickness point and the polar diameter,
Figure 971585DEST_PATH_IMAGE021
the total wedge angle of the oil film of the flow distribution pair is expressed as
Figure 274390DEST_PATH_IMAGE022
；
3. Calculating the supporting force generated in the mixed friction area along the axial direction of the plunger cylinder, wherein the plunger cylinder and the valve plate can generate local mixed friction contact near the minimum gap thickness point of the auxiliary supporting belt, the contact surface of the plunger cylinder and the valve plate is in wedge-shaped contact, and the bearing capacity of the contact peak in the contact areaWLoad force along the Z-axisF mixComprises the following steps:
Figure 506919DEST_PATH_IMAGE023
in the formula (I), the compound is shown in the specification,n fis the number of contact peaks per unit area,
Figure 920583DEST_PATH_IMAGE024
，σ e、σ 1respectively equivalent roughness and roughness of the surface profile of the port plate,R e=R 1/2， R e、R 1respectively the radius of the equivalent rough peak and the radius of the rough peak on the surface of the valve plate,θ imix、θ jmixa start angle and a final angle of the central angle corresponding to the frictional contact area, respectivelyθ imix=-π，θ jmix=π，
Figure 273067DEST_PATH_IMAGE025
，E e、E 1、E 2Respectively is equivalent elastic modulus, elastic modulus of the surface material of the valve plate and elastic modulus of the surface material of the plunger cylinder,γ 1、γ 2respectively the Poisson's ratio of the surface material of the valve plate and the surface material of the plunger cylinder;
4. establishing a mechanical balance equation of the plunger cylinder in the axial direction,
Figure 746774DEST_PATH_IMAGE026
；
5. and obtaining an oil film thickness curve of any position point of the flow distribution pair by adopting a four-stage for-cycle algorithm comprising a Z wedge angle, a wear wedge angle, an XY azimuth angle and the minimum oil film thickness, and obtaining a total wedge angle, a total azimuth angle, a Z wedge angle, a wear wedge angle, an XY azimuth angle and the minimum oil film thickness of the oil film of the flow distribution pair.
2. The method for measuring the thickness of the oil film of the flow distribution pair according to claim 1, wherein the method comprises the following steps: the total azimuth angle obtained by calculation in the steps 1-4
Figure 715867DEST_PATH_IMAGE020
Within the variation range of (2), at a radiusr 1<r<r 2Or radiusr 3<r<r 4In the range of (1), surface material strengthening or wear-resisting treatment is carried out on the surface of a valve plate or a plunger cylinder contacted with a flow distribution pair oil film, and a circular pit micro array or a local texture structure is increased.
3. A method for measuring the thickness of an oil film of a flow distribution pair,
1. installing an eddy current displacement sensor at a T1 point outside the outer seal of the port plate, and measuring the thickness of a port pair oil film at the point;
2. the method comprises the steps of collecting oil film thickness measured data of three position points T1, T2 and T3 of a distribution pair of plunger type elements of the same type under different working conditions to form a data set, and determining an XY wedge angle and an XY azimuth angle of the distribution pair oil film of the distribution pair wedge oil film under different pressure, displacement and rotating speed working conditions
Figure 916910DEST_PATH_IMAGE027
、
Figure 389480DEST_PATH_IMAGE008
；
3. Obtaining a flow distribution pair oil film thickness curve at a T1 point,
a. the total thickness formula of the wedge-shaped oil film of the flow distribution pair is as follows:
Figure 34088DEST_PATH_IMAGE029
b. and calculating to obtain an oil film thickness curve at a T1 point of the flow distribution pair by adopting a two-stage for-cycle algorithm comprising a Z wedge angle and a wear wedge angle, and obtaining a total wedge angle, a wear wedge angle and a Z wedge angle of the oil film of the flow distribution pair.
CN202010858770.5A 2020-08-24 2020-08-24 Method for measuring thickness of oil film of flow distribution pair Pending CN111946609A (en)

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113008718A (en) * 2021-03-23 2021-06-22 太原科技大学 Axial plunger pump flow distribution pair test device and method
CN113607402A (en) * 2021-08-13 2021-11-05 浙江师范大学 Device, method and system for testing oil film of plunger pair of plunger pump
CN114166676A (en) * 2021-12-03 2022-03-11 中南大学 Hydraulic pump flow distribution pair friction and wear testing device with online monitoring function
CN115898851A (en) * 2022-11-29 2023-04-04 中南大学 Oil film thickness distribution measuring method for spherical flow distribution pair of plunger pump

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1847649A (en) * 2005-10-28 2006-10-18 兰州理工大学 Oil film thickness controlling system for end fluid-distributing axial plunger pump
US20090267620A1 (en) * 2008-04-24 2009-10-29 Hidetoshi Takimoto Film thickness measurement device and method
JP2011117756A (en) * 2009-12-01 2011-06-16 Ihi Corp Device and method for measuring film thickness
CN106595462A (en) * 2016-12-29 2017-04-26 北京理工大学 Axial plunger pump flow distribution pair test oil membrane thickness test system
CN107829926A (en) * 2017-09-30 2018-03-23 长安大学 A kind of detection means and method of quantitative plunger pump Slipper coupling oil film thickness

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1847649A (en) * 2005-10-28 2006-10-18 兰州理工大学 Oil film thickness controlling system for end fluid-distributing axial plunger pump
US20090267620A1 (en) * 2008-04-24 2009-10-29 Hidetoshi Takimoto Film thickness measurement device and method
JP2011117756A (en) * 2009-12-01 2011-06-16 Ihi Corp Device and method for measuring film thickness
CN106595462A (en) * 2016-12-29 2017-04-26 北京理工大学 Axial plunger pump flow distribution pair test oil membrane thickness test system
CN107829926A (en) * 2017-09-30 2018-03-23 长安大学 A kind of detection means and method of quantitative plunger pump Slipper coupling oil film thickness

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
王刚志 等: "多缸内燃机主轴承油膜厚度的试验研究", 《内燃机工程》 *

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113008718A (en) * 2021-03-23 2021-06-22 太原科技大学 Axial plunger pump flow distribution pair test device and method
CN113607402A (en) * 2021-08-13 2021-11-05 浙江师范大学 Device, method and system for testing oil film of plunger pair of plunger pump
CN113607402B (en) * 2021-08-13 2023-08-25 浙江师范大学 Plunger pump plunger pair oil film testing device, method and system
CN114166676A (en) * 2021-12-03 2022-03-11 中南大学 Hydraulic pump flow distribution pair friction and wear testing device with online monitoring function
CN114166676B (en) * 2021-12-03 2024-01-30 中南大学 Hydraulic pump flow distribution pair friction and wear testing device with online monitoring function
CN115898851A (en) * 2022-11-29 2023-04-04 中南大学 Oil film thickness distribution measuring method for spherical flow distribution pair of plunger pump
CN115898851B (en) * 2022-11-29 2024-04-09 中南大学 Method for measuring thickness distribution of oil film of spherical flow distribution pair of plunger pump

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Application publication date: 20201117