CN110206793A - A kind of high revolving speed main shaft load device - Google Patents
A kind of high revolving speed main shaft load device Download PDFInfo
- Publication number
- CN110206793A CN110206793A CN201910393113.5A CN201910393113A CN110206793A CN 110206793 A CN110206793 A CN 110206793A CN 201910393113 A CN201910393113 A CN 201910393113A CN 110206793 A CN110206793 A CN 110206793A
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- Prior art keywords
- hydraulic
- pressure
- electric control
- pump
- main shaft
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/04—Special measures taken in connection with the properties of the fluid
- F15B21/041—Removal or measurement of solid or liquid contamination, e.g. filtering
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/04—Special measures taken in connection with the properties of the fluid
- F15B21/042—Controlling the temperature of the fluid
- F15B21/0423—Cooling
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/08—Servomotor systems incorporating electrically operated control means
-
- G—PHYSICS
- G01—MEASURING; TESTING
- G01L—MEASURING FORCE, STRESS, TORQUE, WORK, MECHANICAL POWER, MECHANICAL EFFICIENCY, OR FLUID PRESSURE
- G01L3/00—Measuring torque, work, mechanical power, or mechanical efficiency, in general
- G01L3/16—Rotary-absorption dynamometers, e.g. of brake type
- G01L3/20—Rotary-absorption dynamometers, e.g. of brake type fluid actuated
-
- G—PHYSICS
- G01—MEASURING; TESTING
- G01L—MEASURING FORCE, STRESS, TORQUE, WORK, MECHANICAL POWER, MECHANICAL EFFICIENCY, OR FLUID PRESSURE
- G01L3/00—Measuring torque, work, mechanical power, or mechanical efficiency, in general
- G01L3/24—Devices for determining the value of power, e.g. by measuring and simultaneously multiplying the values of torque and revolutions per unit of time, by multiplying the values of tractive or propulsive force and velocity
-
- G—PHYSICS
- G01—MEASURING; TESTING
- G01L—MEASURING FORCE, STRESS, TORQUE, WORK, MECHANICAL POWER, MECHANICAL EFFICIENCY, OR FLUID PRESSURE
- G01L5/00—Apparatus for, or methods of, measuring force, work, mechanical power, or torque, specially adapted for specific purposes
- G01L5/0061—Force sensors associated with industrial machines or actuators
- G01L5/0076—Force sensors associated with manufacturing machines
-
- G—PHYSICS
- G01—MEASURING; TESTING
- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
- G01M13/00—Testing of machine parts
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- General Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Combustion & Propulsion (AREA)
- Testing Of Devices, Machine Parts, Or Other Structures Thereof (AREA)
Abstract
A kind of high revolving speed main shaft load device uses high analogue simulation load technology, belongs to the field of test technology of safe manufacturing, environmentally protective manufacture.It is characterized by: being made of mechanical part and electric control part two parts；Mechanical part is made of separation type hydraulic pump assembly and hydraulic oil container component；Separation type hydraulic pump assembly includes containing hydraulic pump and bracket；Hydraulic oil container component includes containing interface, pipeline, filter, overflow valve, ratio valve group, hydraulic cabinet, cooling unit；Electric control part is hydraulic electric control case；Hydraulic electric control case is to reach for implementing to adjust pressure and controlling fluid resistance and adjust the different torque demands of hydraulic pump output, that is, adjust magnitude of load.The present invention is suitable for the examination and test of products department and product quality supervision and inspection mechanism of all kinds of machinery production enterprises, whether the main-shaft torque (or power) for the product or examined product of verifying production reaches standard requirements, it can also be used to which whether the main cutting force of machine tool product main shaft reaches standard requirements.
Description
Technical field:
The present invention is suitable for the examination and test of products department and product quality supervision and inspection mechanism of all kinds of machinery production enterprises, mainly
Whether the main-shaft torque (or power) for the product or examined product of verifying production reaches standard requirements, it can also be used to machine
Whether the main cutting force of bed product main shaft reaches standard requirements, which uses high analogue simulation load technology, belongs to peace
The novel test technical field of full manufacture, environmentally protective manufacture.
Background technique:
All kinds of mechanical main shafts for be unableing to do without rotation, in the technical indicator of live spindle, torque index is most important finger
One of mark, especially in machine industry field, can the output torque of machine tool chief axis be directly related to machine tool product and use.Traditional
Method is that a suitable cutter is installed on main shaft, installs a suitable workpiece on the table, then changes different
Operating parameter (cutting-in cuts the wide, amount of feeding and the speed of mainshaft), calculates, whether evaluation lathe reaches stated number while processing
According to.The unique advantage of this method is really to process, rather than simulating cutting, but its disadvantage is more prominent, main there are five aspect,
First is that test period is long, from installation and debugging to not a half day is completed to, second is that needing high cutter and more processed test specimen, try
Testing failure must begin the beguine, third is that being likely to cause machine tool chief axis damage when test, misoperation may cause casualties
Accident, fourth is that noise is big when test, chip splashing, coolant liquid are splashed, and pollution are be easy to cause, fifth is that needing to carry out after having tested
Cleaning and maintenance.
Currently, machinery industry also has a kind of alternative, such as magnetic powder brake, electric eddy current brake, it is small to belong to low speed
Resistance device or High speed and low resistance power device, it is maximum the disadvantage is that volume is big, quality weight in addition to this disadvantage, it is not easy to install
And carrying, it is frequently used in the fixed position in laboratory.
The present invention fundamentally solves drawback brought by conventional test methods and traditional load manner.Benefit of the invention
Hydraulic pressure and flow are adjusted with JCS hydraulic proportion valve (home brands), change hydraulic pump (gear pump, plunger pump or leaf
Piece pump etc.) liquid resistance, to reach required drag loads --- main-shaft torque.The main advantages of the present invention have eight sides
Face: first is that using pump, case isolation technics, hydraulic pump lighter in weight is also very light with alloy pump body support frame, carries and installation is very square
Just；Two are into and out, oil pipe uses safety quick joint, not only safely but also convenient for both ends Fast Installation；Third is that being adjusted by potentiometer
Hydraulic proportion valve output, increases load steadily, does not generate impact to test main shaft；Fourth is that after access three-phase power meter, simultaneously
It can calculated torque and the main component size of cutting；Fifth is that the danger splashed without chip, coolant liquid；Sixth is that not needing high cutting
Cutter overloads bored vehicle phenomenon without worry and main shaft is caused to damage；Seventh is that it is higher than traditional magnetic powder brake revolving speed, it reaches as high as
3000r/min；Eighth is that can be used as whole loads examination of all machine tool products (metal cutting machine, forging machine tool etc.) in addition to test of bearing a heavy burden
Test item-test.
Summary of the invention:
Object of the present invention is to provide controllable load (torque and power) for engineering goods (containing machine tool product) main shaft test.
The present invention is made of mechanical part and electric control part two parts.
Mechanical part of the invention (is contained by separation type hydraulic pump assembly (containing hydraulic pump and bracket) and hydraulic oil container component
Interface, pipeline, filter, overflow valve, ratio valve group, hydraulic cabinet, cooling unit) composition, see Fig. 1.
Electric control part of the invention is hydraulic electric control case.Hydraulic electric control case is for implementing to adjust pressure and controlling fluid resistance
Power reaches and adjusts the different torque demands of hydraulic pump output, that is, adjusts magnitude of load.Electric cabinet principle is shown in Fig. 2.
Hydraulic load device torque of the invention and pressure dependence are shown in formula (1) and formula (2).
Vg--- pumpage (cm3/r)
△ P --- pressure variety (bar)
ηmh--- hydraulic efficiency (%)
K --- environmental coefficient, here k=1
D1 --- pump input oil pipe internal diameter (mm)
D2 --- pump output oil pipe internal diameter (mm)
P1 --- pump input oil pipe pressure (MPa)
P2 --- pump output oil pipe pressure (MPa)
Because hydraulic load device needs large torque and high-power, higher hydraulic pressure certainly will be needed to change according to formula (1)
△P(P2-P1), highest needs to be transferred to 30MPa, under high pressure effect, increases proportioning valve quantity to increase flow, can be only achieved phase
Answer power and torque, the pressure of oil pump and the proportion of input and output internal diameter of the pipeline, it is necessary to according to We at fault the lesson lost
With successful experience, in the case where only strictly observing and meeting formula (2), load device ability parameter (maximum speed, maximum torsion
Square, maximum power) it just can be carried out index calibration, it also just can be carried out steady load, the load device otherwise created can not be normal
It uses.
Load device of the present invention is achieved by the following technical solution:
Mechanical part of the invention as shown in Figure 1 is tested main shaft by shaft coupling and connects hydraulic pump operating, and hydraulic pump is opened
Beginning work, and oil suction is carried out by oil absorption filter 1 and oil inlet pipe quick coupling 6.1, then pass through flowline quick coupling 6.2
It is fuel-displaced, control by the pressure from proportioning valve 11 and electromagnetic relief valve 12 during fuel-displaced, and by controlling requirement for oil liquid
Send fuel tank back to.
Electric control part of the invention as shown in Figure 4 utilizes SVA-IV hydraulic servo controller chip controls electro-hydraulic servo
The openings of sizes of proportioning valve changes liquid resistance, realizes and adjusts to the pressure of pump.Using pressure sensor feedback system pressure,
Pressure closed loop control is realized by controller, and pump output pressure is accurately controlled, to change the input torque of hydraulic pump, is reached
To different size of torque or power loading.Load and unloading use electromagnetic relief valve, have both been able to achieve load, and can also limit liquid
The maximum pressure of pressure system protects system element.
Innovative point of the present invention is as follows:
(1) loading technique is separated using pump, case, i.e. hydraulic pump (using gear pump at present) is separated with hydraulic fluid tank, and centre is adopted
With into and out of Quick joint for oil pipe connection type, pump box connection is realized.
(2) multiple hydraulic proportion valves are directlyed adopt and collectively constitute valve group, to adjust the pressure of hydraulic system, and realize by than
Example control hydraulic pressure, feature is that output response is fast, precision is high, load is steady.
(3) device reaches IP65 or more because of hydraulic pump module leakproofness, and does not have electrical part, can apply the same of load
When can be with spraying cooling liquid, to reach analog main shaft working condition.
The key technical indexes of the present invention is as follows:
(1) torque range: 0~600Nm；
(2) maximum speed of spindle: 3000r/min adds 5000r/min after gearbox；
(3) maximum tangential component range: 12000N
(4) maximum power: 60kW.
(5) hydraulic maximum pressure: 30MPa
The present invention can replace machine cut process, and safety, economic, environmental protection meet as defined in machine industry standard
" lathe load test " demand.
Detailed description of the invention:
Fig. 1 is main shaft load device mechanical part schematic illustration；
Fig. 2 is hydraulic pump bracket figure (13 in Fig. 1)；
Fig. 3 is hydraulic box portion (1/2/3/4/5/8/11/12 in Fig. 1)；
Fig. 4 is hydraulic electric control box part schematic diagram；
Specific embodiment:
With reference to the accompanying drawing with illustrate the content of present invention for vertical machining centre.
A. hydraulic pump bracket component is mounted on platen, adjustment simulation cutter makes main-shaft axis and hydraulic pump
Axial line registration reaches within 0.015mm；
B. fluid pressure line is connected, and examines oil inlet pipe and flowline whether firm；
C. the power supply for connecting hydraulic electric control case, is placed in stress state for load/unload；
D. vertical machining centre main shaft selection of speed 2000r/min, rotational pressure adjusting knob, while observing data acquisition
Whether data reach prescribed torque or power requirement in device or the main shaft load expression condition of observation lathe judges.
E. vertical machining centre main shaft is shut down, and is selected 2500r/min revolving speed, is tested again.
Claims (2)
1. a kind of high revolving speed main shaft load device, it is characterised in that:
It is made of mechanical part and electric control part two parts；
Mechanical part is made of separation type hydraulic pump assembly and hydraulic oil container component；Separation type hydraulic pump assembly includes containing hydraulic
Pump and bracket；Hydraulic oil container component includes containing interface, pipeline, filter, overflow valve, ratio valve group, hydraulic cabinet, cooling list
Member；
Electric control part is hydraulic electric control case.Hydraulic electric control case is to reach adjusting for implementing to adjust pressure and controlling fluid resistance
Hydraulic pump exports different torque demands, that is, adjusts magnitude of load.
2. a kind of application high revolving speed main shaft load device as described in claim 1, it is characterised in that: hydraulic load device torque
T and pressure dependence are shown in formula (1) and formula (2).
Vg--- pumpage (cm3/r)
△ P --- pressure variety (bar)
ηmh--- hydraulic efficiency (%)
K --- environmental coefficient, k=1
d1--- pump input oil pipe internal diameter (mm)
d2--- pump output oil pipe internal diameter (mm)
P1--- pump input oil pipe pressure (MPa)
P2--- pump output oil pipe pressure (MPa)
Because hydraulic load device needs large torque and high-power, higher hydraulic pressure certainly will be needed to change △ P according to formula (1)
(P2-P1), highest needs to be transferred to 30MPa, under high pressure effect, increases proportioning valve quantity to increase flow, can be only achieved corresponding function
Rate and torque, the pressure of oil pump and the proportion of input and output internal diameter of the pipeline, it is necessary to according to
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910393113.5A CN110206793A (en) | 2019-05-10 | 2019-05-10 | A kind of high revolving speed main shaft load device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910393113.5A CN110206793A (en) | 2019-05-10 | 2019-05-10 | A kind of high revolving speed main shaft load device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN110206793A true CN110206793A (en) | 2019-09-06 |
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ID=67787187
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201910393113.5A Pending CN110206793A (en) | 2019-05-10 | 2019-05-10 | A kind of high revolving speed main shaft load device |
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Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2012054A (en) * | 1977-10-19 | 1979-07-18 | South Western Ind Res | Testing internal combustion engines |
| US20030150258A1 (en) * | 2002-02-13 | 2003-08-14 | Moskwa John J. | Internal combustion engine simulation and testing |
| CN101639414A (en) * | 2009-05-07 | 2010-02-03 | 北京理工大学 | Torque loading system of hydraulic pump |
| CN103353395A (en) * | 2013-05-27 | 2013-10-16 | 武汉理工大学 | Hydraulic loading device for large marine propulsion shafting test bed |
| CN104100585A (en) * | 2014-07-17 | 2014-10-15 | 高进美 | Hydraulic power device |
| CN204043913U (en) * | 2014-08-25 | 2014-12-24 | 李朔 | Hydraulic loaded formula engine performance test stand |
-
2019
- 2019-05-10 CN CN201910393113.5A patent/CN110206793A/en active Pending
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2012054A (en) * | 1977-10-19 | 1979-07-18 | South Western Ind Res | Testing internal combustion engines |
| US20030150258A1 (en) * | 2002-02-13 | 2003-08-14 | Moskwa John J. | Internal combustion engine simulation and testing |
| CN101639414A (en) * | 2009-05-07 | 2010-02-03 | 北京理工大学 | Torque loading system of hydraulic pump |
| CN103353395A (en) * | 2013-05-27 | 2013-10-16 | 武汉理工大学 | Hydraulic loading device for large marine propulsion shafting test bed |
| CN104100585A (en) * | 2014-07-17 | 2014-10-15 | 高进美 | Hydraulic power device |
| CN204043913U (en) * | 2014-08-25 | 2014-12-24 | 李朔 | Hydraulic loaded formula engine performance test stand |
Non-Patent Citations (3)
| Title |
|---|
| 山东省建设委员会执业资格注册中心: "《注册结构工程师考试手册》", 30 September 1998 * |
| 岑军健等: "《非标准设备设计手册》", 31 December 1983 * |
| 郭金刚: "《现代化矿井职工教育培训教材》", 31 August 2001 * |
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Application publication date: 20190906 |