CN103591085B - For the full hydraulic power formula performance test apparatus of center-rotary joint - Google Patents
For the full hydraulic power formula performance test apparatus of center-rotary joint Download PDFInfo
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- CN103591085B CN103591085B CN201310624733.8A CN201310624733A CN103591085B CN 103591085 B CN103591085 B CN 103591085B CN 201310624733 A CN201310624733 A CN 201310624733A CN 103591085 B CN103591085 B CN 103591085B
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Abstract
The present invention discloses a kind of full hydraulic power formula performance test apparatus for center-rotary joint, comprises an oil hydraulic pump, the first selector valve, pressurizing elements and oil hydraulic motor; Wherein, oil hydraulic pump is got fluid from oil sources pump and is carried the pressure oil liquid that is for experiment; First selector valve is arranged on the downstream side of oil hydraulic pump, exports pressure simulation branch road or revolution simulation branch road to switch pressure oil liquid; Pressurizing elements is arranged on pressure simulation branch road, for exporting the test oil circuit of high-voltage oil liquid to center-rotary joint according to pressure oil liquid; Oil hydraulic motor is arranged on revolution simulation branch road, for exporting the rotatable parts of rotary driving force to center-rotary joint according to pressure oil liquid.This programme, for integrated, the unification process of test power source used, reduces element cost, and can reduce energy consumption; Meanwhile, reliably can realize the stepless time adjustment of rotation motion, the operations such as quick startup, braking, frequent commutation can be adapted to.
Description
Technical field
The present invention relates to the technical field of performance test of hydraulic element, be specifically related to a kind of full hydraulic power formula performance test apparatus for center-rotary joint.
Background technique
As everyone knows, center-rotary joint is used for greatly the relatively pivotal engineering machinery that gets on and off.Such as, excavator, excavator car load is divided into two parts of getting on the bus and get off, and lower vehicle hydraulic system and upper vehicle hydraulic system share a pumping plant, and the fluid needed for it needs to be connected by pipeline from getting on the bus; Can relatively rotate between the housing of center-rotary joint and mandrel, thus can guarantee that necessary connecting pipeline does not produce any torsion, meet the function needs that the hydraulic system that gets on and off shares a pumping plant.
Obviously, for the relatively pivotal hydraulic control engineering machinery that gets on and off, as the center-rotary joint of core component, all kinds of parameter requests of its reliability and stability and reactor product performance are particularly important.Separate between the inner different oil duct of center-rotary joint, the accuracy of manufacturing of housing parts and arbor portions directly has influence on the sealability between different oil duct, and therefore, the sealing experiment of center-rotary joint is indispensable.In addition, key parameter when torsional moment during running is swivel coupling design, the real-time measurement of moment is very important equally.
In prior art, the performance testing device of center-rotary joint mostly adopts motor to coordinate with speed reducer and drives the rotation motion of swivel coupling simulated implementation, utilize high-pressure service pump to simulate different operating loading simultaneously and provide high-voltage oil liquid.But, by the restriction of himself working principle, variable-frequency motor and frequency variator need be adopted to realize speed-regulating function, but when motor actual speed depart from rated speed excessive time, can amount of heat be produced, greatly reduce energy utilization rate, so can affect the working life of motor simultaneously for a long time; In addition, electric motor starting is more steady, and has reversing impact, cannot carry out quick starting, braking and the frequent test operation commutated.
In view of this, the performance test technology urgently looked for another way for existing center-rotary joint is optimized design, at effective use of energy sources, reduces on the basis of deployment cost, greatly improves the stable movement reliability of test operation.
Summary of the invention
For above-mentioned defect, the technical problem that the present invention solves is to provide a kind of full hydraulic power formula performance test apparatus for center-rotary joint, to be overcome the above-mentioned defect that prior art exists by system layout optimization.
Full hydraulic power formula performance test apparatus for center-rotary joint provided by the invention, comprises an oil hydraulic pump, the first selector valve, pressurizing elements and oil hydraulic motor; Wherein, described oil hydraulic pump is got fluid from oil sources pump and is carried the pressure oil liquid that is for experiment; Described first selector valve is arranged on the downstream side of described oil hydraulic pump, exports pressure simulation branch road or revolution simulation branch road to switch described pressure oil liquid; Described pressurizing elements is arranged on pressure simulation branch road, for exporting the test oil circuit of high-voltage oil liquid to described center-rotary joint according to described pressure oil liquid; Described oil hydraulic motor is arranged on described revolution simulation branch road, for exporting the rotatable parts of rotary driving force to described center-rotary joint according to described pressure oil liquid.
Preferably, described pressurizing elements is specially pressurized cylinder.
Preferably, also comprise: be arranged on described pressurized cylinder and the second selector valve between described first selector valve and oil return circuit, be communicated with described pressure simulation branch road or oil return circuit with the large chamber switching described pressurized cylinder; Set up the first one-way valve of one-way conduction between the loculus of described pressurized cylinder and the import of described test oil circuit; Set up oil sources to described pressurized cylinder loculus between the second one-way valve of one-way conduction.
Preferably, described second selector valve has two working positions, be positioned at that its first hydraulic fluid port under the first working position is communicated with the second hydraulic fluid port, the 3rd hydraulic fluid port is communicated with the 4th hydraulic fluid port, be positioned at that its first hydraulic fluid port under the second working position is communicated with the 4th hydraulic fluid port, the 3rd hydraulic fluid port is communicated with the second hydraulic fluid port; Wherein, described first hydraulic fluid port is communicated with described first selector valve, and described second hydraulic fluid port is communicated with the large chamber of described pressurized cylinder, and described 3rd hydraulic fluid port is communicated with oil return circuit, and described 4th hydraulic fluid port is communicated with the lumen of described pressurized cylinder.
Preferably, the 3rd one-way valve setting up one-way conduction between described first selector valve to described second selector valve is also comprised.
Preferably, the switch valve between the outlet of the test oil circuit being arranged on described center-rotary joint and oil return circuit is also comprised.
Preferably, described first selector valve, described second selector valve and described switch valve are solenoid electric valve.
Preferably, also comprise: be arranged on the 3rd selector valve between two actuator ports of described oil hydraulic motor and described first selector valve and oil return circuit, to control the clockwise and anticlockwise of described oil hydraulic motor.
Preferably, be provided with the first relief valve between described oil hydraulic pump and described first selector valve, be provided with the second relief valve between described first selector valve and described 3rd selector valve, the setting pressure of described first relief valve is greater than the setting pressure of described second relief valve.
Preferably, described 3rd selector valve is solenoid electric valve.
Compared with prior art, the performance test apparatus of center-rotary joint of the present invention adopts an oil hydraulic pump as pressure simulation and the power source turning round simulation, utilize on the one hand and increase element according to the pressure oil liquid output high-voltage oil liquid entering pressure simulation branch road, to the test oil circuit of center-rotary joint, the tests such as sealing pressurize are carried out in the load of simulating under different operating mode; On the other hand, the pressure oil liquid entering revolution simulation outlet exports oil hydraulic motor to, by the rotatable parts rotation motion rotarily driving center-rotary joint of motor.Setting like this, this programme changes the dual power source form (oil hydraulic pump is supplied to hydraulic system pressure and flow, variable-frequency motor drives revolution) of traditional hydraulic system and revolving structure, achieve integrated, the unification of power source, decrease the use of turning motor and the optional equipment such as frequency variator, retarder, thus the element cost of system layout can be reduced, evading the problem of motor overload heating completely, having provided reliable guarantee for effectively controlling energy consumption; Meanwhile, in this programme pressurizing elements arrange can configure small flow, low-pressure oil hydraulic pump as power source, save energy consumption further.In addition, application oil hydraulic motor, as the executive component of revolution simulation, is convenient to the stepless time adjustment realizing rotation motion, can adapt to the similar operations such as quick startup, braking, frequent commutation, have good operational stability.
Pressurizing elements in preferred version of the present invention is specially pressurized cylinder, and structure is simple and functional reliability is high.Further, the second selector valve is arranged on pressurized cylinder and between the first selector valve and oil return circuit, is communicated with the large chamber switching pressurized cylinder with pressure simulation branch road or oil return circuit; When pressure oil liquid enters the large chamber of pressurized cylinder, its internal piston displacement also exports high-voltage oil liquid to the test oil circuit of center-rotary joint from loculus, simulates the work loads of corresponding test oil circuit; When the large chamber of pressurized cylinder is communicated with piston reset with oil return circuit, being arranged so that between the test oil circuit of center-rotary joint to pressurized cylinder loculus of first one-way valve is non-conduction, the loculus being arranged so that pressurized cylinder of the second one-way valve can realize repairing from oil sources, stores up a high pressure oil thus and exports.
In another preferred version of the present invention, between the test oil way outlet and oil return circuit of center-rotary joint, be provided with switch valve, cutoff test oil circuit can be needed according to test, check the sealability of its static state, there is good operability.
Full hydraulic power formula performance test apparatus provided by the invention is applicable to any type of center-rotary joint, is specially adapted to engineering machinery center-rotary joint.
Accompanying drawing explanation
Fig. 1 is the hydraulic control principle schematic of hydraulic power formula performance test apparatus complete described in embodiment.
In figure:
Oil hydraulic pump 1, first selector valve 2, center-rotary joint 3, oil hydraulic motor 4, pressurized cylinder 5, second selector valve 6, first hydraulic fluid port 61, second hydraulic fluid port 62, the 3rd hydraulic fluid port 63, the 4th hydraulic fluid port 64, first one-way valve 7, second one-way valve 8, the 3rd one-way valve 9, switch valve 10, the 3rd selector valve 11, first relief valve 12, second relief valve 13, first filter 14, second filter 15.
Embodiment
Based on the performance test requirement of center-rotary joint, core of the present invention is to provide a kind of full hydraulic power performance test apparatus of configuration optimization, to achieve integrated, the unification of test power source used, reduces element cost, reduces energy consumption; Meanwhile, reliably can realize the stepless time adjustment of rotation motion, and adapt to the operations such as startup fast, braking, frequent commutation.Present embodiment is illustrated below in conjunction with Figure of description.
Refer to Fig. 1, this figure is the hydraulic control principle schematic of hydraulic power formula performance test apparatus complete described in present embodiment.
Without loss of generality, this programme is described in detail for main body to be measured with center-rotary joint 4, is specifically related to the simulation of working pressure and rotation motion.Should be appreciated that the structural type of this center-rotary joint 1 does not form the restriction to full hydraulic power formula performance test apparatus.
Compared with the performance test apparatus of existing center-rotary joint, this programme is full hydraulic power formula.That is, adopt an oil hydraulic pump 1 get fluid from oil sources pump and carry the pressure oil liquid that is for experiment, preferably adopt variable displacement pump.As shown in the figure, the power source that this full hydraulic power formula performance test apparatus is tested using an oil hydraulic pump as over-all properties, a road pressure oil liquid exports pressure simulation branch road A to, and another road pressure oil liquid exports revolution simulation branch road B to; Particularly, survey be provided with the first selector valve 2 in the downstream of oil hydraulic pump 1, the pressure oil liquid pumped to switch oil hydraulic pump 1 exports pressure simulation branch road A or revolution simulation branch road B to.Wherein, pressure simulation branch road A is provided with increase element, for exporting the test oil circuit of high-voltage oil liquid to center-rotary joint 3 according to the pressure oil liquid entering branch road, working pressure under fictitious load; Herein, " test oil circuit " refers to the difference working oil path to be measured that center-rotary joint inside is set up.Wherein, turn round on simulation branch road B and be provided with oil hydraulic motor 4, preferred variable motor, for exporting the rotatable parts of rotary driving force to center-rotary joint 3 according to the pressure oil liquid entering branch road, the operations such as simulation startup, braking, commutation and speed governing.According to the difference of specific product, this oil hydraulic motor 4 can select the housing or the mandrel revolution that drive center-rotary joint 3.
It should be noted that, the increase element being arranged at pressure simulation branch road A can adopt different implementations, and the pressurizing elements shown in figure is specially pressurized cylinder 5, utilizes the sectional area ratio of pressurized cylinder 5 input cavity and output cavity to realize the conversion of high pressure oil.Also can adopt pressure charging valve that the low pressure oil in Hydraulic Power Transmission System is converted into high pressure oil in proportion, as long as meet the reliable test needs exporting center-rotary joint.Certainly, employing pressurized cylinder 5 guarantees the high pressure oil needed for seal tightness test, and comparatively speaking, arrangements of components cost is lower, and maintenance easy to use.
In order to obtain more stable operability, at pressurized cylinder 5 and between the first selector valve 2 and oil return circuit T, the second selector valve 6 can be set, be communicated with pressure simulation branch road A or oil return circuit T with the large chamber switching pressurized cylinder 5, realize action and the reset of pressurized cylinder 5; Meanwhile, the first one-way valve 7 is arranged between the test oil circuit import of pressurized cylinder 5 loculus and center-rotary joint 3, to set up the one-way conduction between pressurized cylinder 5 loculus and the import testing oil circuit; Second one-way valve 8 is arranged between oil sources and pressurized cylinder 5 loculus, to set up the one-way conduction between oil sources to pressurized cylinder 5 loculus.Thus, in pressurized cylinder 5 internal piston reseting procedure, the deposit fluid that oil sources provides enters the loculus of pressurized cylinder 5 from the second one-way valve 8.Here " oil sources " can be the hydraulic oil container of separate configurations, the hydraulic oil container that also can share with other testing apparatuss, as long as meet the needs providing test oil.
Particularly, the pressure oil liquid entering pressure simulation branch road A can be utilized to realize increasing the reset of cylinder 5.Here, the second selector valve 6 is at least two-position four way change valve, and wherein, the first hydraulic fluid port 61 is communicated with the first selector valve 2, and the second hydraulic fluid port 62 is communicated with the large chamber of pressurized cylinder 5, and the 3rd hydraulic fluid port 63 is communicated with oil return circuit T, and the 4th hydraulic fluid port 64 is communicated with the lumen of pressurized cylinder 5.Be positioned at that its first hydraulic fluid port 61 under the first working position (left position) is communicated with the second hydraulic fluid port 62, the 3rd hydraulic fluid port 63 is communicated with the 4th hydraulic fluid port 64, under this state, after pressurized cylinder 5 action, loculus exports high pressure oil; Be positioned at that its first hydraulic fluid port 61 under the second working position (right position) is communicated with the 4th hydraulic fluid port 64, the 3rd hydraulic fluid port 63 is communicated with the second hydraulic fluid port 62, under this state, after pressurized cylinder 5 resets, loculus fills into deposit oil.Here " oil return circuit " can be the oil circuit be directly communicated with hydraulic oil container, also can be any low pressure oil way of indirect communication, as long as meet the reliable reset of pressurized cylinder 5.
Further, one-way conduction between the first selector valve 2 to the second selector valve 6 can be set up by the 3rd one-way valve 9, form to avoid pressure simulation branch road A the usability that improper compression shock affects oil hydraulic pump 1.
Under normal circumstances, the oil circuit to be measured for center-rotary joint is needed to carry out static experiments of sealing performance.As shown in the figure, can arrange switch valve 10 between the outlet of the test oil circuit of center-rotary joint 3 and oil return circuit T, switch valve 10 remains on cut-off state can carry out static experiments of sealing performance.
In addition, at two actuator ports of oil hydraulic motor 4 and between the first selector valve 2 and oil return circuit T, the 3rd selector valve 11 can be set with the clockwise and anticlockwise of hydraulic control motor 4.
In this programme, the first selector valve 2, second selector valve 6, switch valve 10 and the 3rd selector valve 11 can be all solenoid electric valve.Shown in figure, the first selector valve 2 has three working positions, is in the non-conduction working state of meta under normality, and left position state downforce fluid exports pressure simulation branch road to, and right position state downforce fluid exports revolution simulation branch road to; Certainly, this first commutation 2 also only can have the working position, two, left and right meeting two branch road and control.In addition, the bi-bit bi-pass selector valve that switch valve 10 also can be non-conduction under normality.
Between oil hydraulic pump 1 and the first selector valve 2, be provided with the first relief valve 12, ensure security of system stable operation; Meanwhile, simulate the different pressure needs of branch road in order to take into account pressure simulation branch road from revolution, the setting pressure that can be provided with the second relief valve 13, first relief valve 12 between the first selector valve 2 and the 3rd selector valve 11 is greater than the setting pressure of the second relief valve 13.
The working principle of this full hydraulic power formula performance test apparatus of brief description below.
One, wiper seal performance is tested
Oil hydraulic pump 1 exports the second selector valve 2 to via the fluid after the first filter 14 oil filtrating after starting.When YA1 obtains electric, hydraulic oil enters the second selector valve 6 by the 3rd one-way valve 9, when YA3 obtains electric, hydraulic oil enters the large chamber of pressurized cylinder 5, and the working oil path to be measured that high pressure oil enters center-rotary joint 3 is discharged from the right chamber of pressurized cylinder 5, carry out pressurize test (now YA4 not electric), the sealability of inspection swivel coupling static state.When needs pressure release, YA4 obtains and electricly can realize pressure release.When YA1 obtain electric, YA3 not electric time, pressurized cylinder 5 internal piston can be made to get back to original position, carry out repairing by opening one-way valve 8 for the right chamber of pressurized cylinder 5 in piston retracts process simultaneously.
Two, turnability test
When YA2 obtains electric, hydraulic oil enters the 3rd selector valve 11, when YA5 must not electricity time, oil hydraulic motor 4 drives center-rotary joint 3 to rotate forward, and flows back to fuel tank via the second filter 15; When YA5 obtains electric, oil hydraulic motor 4 drives center-rotary joint 3 to rotate backward.Second relief valve 13 plays the protective action to motor.The stepless change of center-rotary joint 3 can be realized by the discharge capacity changing flow or the direct change oil hydraulic motor 4 entering oil hydraulic motor 4.When needing to measure moment of torsion, torque sensor of connecting between oil hydraulic motor 4 with center-rotary joint 3, can realize the measurement of its torque value.
The above is only the preferred embodiment of the present invention; it should be pointed out that for those skilled in the art, under the premise without departing from the principles of the invention; can also make some improvements and modifications, these improvements and modifications also should be considered as protection scope of the present invention.
Claims (10)
1., for the full hydraulic power formula performance test apparatus of center-rotary joint, it is characterized in that, comprising:
One oil hydraulic pump, gets fluid from oil sources pump and carries the pressure oil liquid that is for experiment;
First selector valve, is arranged on the downstream side of described oil hydraulic pump, exports pressure simulation branch road or revolution simulation branch road to switch described pressure oil liquid;
Pressurizing elements, is arranged on pressure simulation branch road, for exporting the test oil circuit of high-voltage oil liquid to described center-rotary joint according to described pressure oil liquid;
Oil hydraulic motor, is arranged on described revolution simulation branch road, for exporting the rotatable parts of rotary driving force to described center-rotary joint according to described pressure oil liquid.
2. the full hydraulic power formula performance test apparatus for center-rotary joint according to claim 1, it is characterized in that, described pressurizing elements is specially pressurized cylinder.
3. the full hydraulic power formula performance test apparatus for center-rotary joint according to claim 2, is characterized in that, also comprise:
Second selector valve, is arranged on described pressurized cylinder and between described first selector valve and oil return circuit, is communicated with the large chamber switching described pressurized cylinder with described pressure simulation branch road or oil return circuit;
First one-way valve, sets up the one-way conduction between the loculus of described pressurized cylinder and the import of described test oil circuit;
Second one-way valve, set up oil sources to described pressurized cylinder loculus between one-way conduction.
4. the full hydraulic power formula performance test apparatus for center-rotary joint according to claim 3, it is characterized in that, described second selector valve has two working positions, be positioned at that its first hydraulic fluid port under the first working position is communicated with the second hydraulic fluid port, the 3rd hydraulic fluid port is communicated with the 4th hydraulic fluid port, be positioned at that its first hydraulic fluid port under the second working position is communicated with the 4th hydraulic fluid port, the 3rd hydraulic fluid port is communicated with the second hydraulic fluid port; Wherein, described first hydraulic fluid port is communicated with described first selector valve, and described second hydraulic fluid port is communicated with the large chamber of described pressurized cylinder, and described 3rd hydraulic fluid port is communicated with oil return circuit, and described 4th hydraulic fluid port is communicated with the lumen of described pressurized cylinder.
5. the full hydraulic power formula performance test apparatus for center-rotary joint according to claim 3 or 4, is characterized in that, also comprise:
3rd one-way valve, sets up the one-way conduction between described first selector valve to described second selector valve.
6. the full hydraulic power formula performance test apparatus for center-rotary joint according to claim 5, is characterized in that, also comprise:
Switch valve, between the outlet being arranged on the described test oil circuit of described center-rotary joint and oil return circuit.
7. the full hydraulic power formula performance test apparatus for center-rotary joint according to claim 6, it is characterized in that, described first selector valve, described second selector valve and described switch valve are solenoid electric valve.
8. the full hydraulic power formula performance test apparatus for center-rotary joint according to claim 1, is characterized in that, also comprise:
3rd selector valve, is arranged between two actuator ports of described oil hydraulic motor and described first selector valve and oil return circuit, to control the clockwise and anticlockwise of described oil hydraulic motor.
9. the full hydraulic power formula performance test apparatus for center-rotary joint according to claim 8, it is characterized in that, the first relief valve is provided with between described oil hydraulic pump and described first selector valve, be provided with the second relief valve between described first selector valve and described 3rd selector valve, the setting pressure of described first relief valve is greater than the setting pressure of described second relief valve.
10. the full hydraulic power formula performance test apparatus for center-rotary joint according to claim 8 or claim 9, it is characterized in that, described 3rd selector valve is solenoid electric valve.
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| CN201310624733.8A CN103591085B (en) | 2013-11-28 | 2013-11-28 | For the full hydraulic power formula performance test apparatus of center-rotary joint |
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| CN201310624733.8A CN103591085B (en) | 2013-11-28 | 2013-11-28 | For the full hydraulic power formula performance test apparatus of center-rotary joint |
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Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN105179381B (en) * | 2015-10-21 | 2018-12-11 | 徐州重型机械有限公司 | The reliability test of rotating device and centre revolving joint |
| CN105332971A (en) * | 2015-11-26 | 2016-02-17 | 中国航空工业集团公司沈阳飞机设计研究所 | Lubricating oil pressure oiling hydraulic test stand |
| CN109029965A (en) * | 2018-09-03 | 2018-12-18 | 江苏腾旋科技股份有限公司 | Hydraulic system is used in a kind of test of center-rotary joint |
| CN110195732B (en) * | 2019-06-26 | 2020-10-30 | 山东大学 | Pressure load simulation system suitable for deep sea equipment hydraulic system and application thereof |
| CN112483511A (en) * | 2020-12-08 | 2021-03-12 | 四川凌峰航空液压机械有限公司 | Variable pressure ratio hydraulic pressure boost test system |
| CN114183413A (en) * | 2021-12-14 | 2022-03-15 | 三一汽车制造有限公司 | Detection device for central swivel joint and vehicle |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
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| JPH08219960A (en) * | 1995-02-14 | 1996-08-30 | Hitachi Cable Ltd | Withstanding pressure test equipment for brake hose |
| CN201069424Y (en) * | 2007-08-01 | 2008-06-04 | 合肥通用机械研究院 | 350MPa ultra-high pressure fatigue test system |
| CN102042934B (en) * | 2010-06-29 | 2012-07-11 | 徐工集团工程机械股份有限公司江苏徐州工程机械研究院 | Durability test method for central rotary joint and special device |
| CN102564860B (en) * | 2012-01-11 | 2014-08-06 | 南京林业大学 | Rotating joint durability testing principle and full-automatic testing machine |
| CN102944365B (en) * | 2012-12-07 | 2015-07-22 | 柳州柳工液压件有限公司 | Method and device for testing durability of central rotary joint |
| CN203702734U (en) * | 2013-11-28 | 2014-07-09 | 徐州徐工液压件有限公司 | Fully-hydraulic power-type performance test device for central rotary joint |
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