CN201502492U - Electro-hydraulic proportional load-sensitive control variable-displacement axial piston pump - Google Patents
Electro-hydraulic proportional load-sensitive control variable-displacement axial piston pump Download PDFInfo
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- CN201502492U CN201502492U CN2009201440751U CN200920144075U CN201502492U CN 201502492 U CN201502492 U CN 201502492U CN 2009201440751 U CN2009201440751 U CN 2009201440751U CN 200920144075 U CN200920144075 U CN 200920144075U CN 201502492 U CN201502492 U CN 201502492U
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Abstract
An electro-hydraulic proportional load-sensitive control variable-displacement axial piston pump comprises a casing, a swash plate mounted in the casing, a rotor, a plunger piston installed in the rotor, a thrust plate and a transmission shaft mounted on a pump cover, a displacement-varying mechanism mounted on the casing, and an electro-hydraulic proportional load-sensitive control pile-up valve installed on the displacement-varying mechanism, wherein a high-pressure window and a low-pressure window are formed on the thrust plate; an oil inlet and an oil outlet are formed on the two side surfaces of the pump cover; semi-annular hydrostatic compensating grooves are formed on the inner and the outer sides of the high-pressure window on the thrust plate respectively; a hole is formed on each compensating groove, a through hole is connected with the lower end of each hole, and a variable damper is connected with each through hole and communicated with the high-pressure window; trapezoidal grooves are formed on the thrust plate; and an inclined hole is connected with the lower end of each trapezoidal groove and correspondingly communicated with the high-pressure window or the lower-pressure window. The utility model can realize hydrostatic back-up and computer control and reduce pressing force, abrasion and noise, and has the advantages of small volume, high pressure, low noise and energy consumption, long service life and high working efficiency.
Description
Technical field
The utility model relates to hydraulic pressure. and mechano-electronic control technique field is a kind of 250ml/r electric-hydraulic proportion load-sensitive control shaft orientation plunger variable pump specifically.
Background technique
Present various types of shaft type and direct shaft type axial piston pump kind are more, from pump structure and performance, the shaft orientation plunger variable pump that Germany BOSCH-REXROTH company produces is more advanced, pressure can reach 42Mpa, change scooter 2600r.pm, noise 84dB, total efficiency 86% is more than the life-span 5000h.Be applied to a plurality of fields such as machinery such as engineering machinery, steel rolling, forging and pressing, mine, petrochemical industry and injection moulding, and performance is reliable, owing to have wide range of applications, so countries in the world, as: the U.S., Japan, China, Britain and some European countries' major parts are from the import of German BOSCH-REXROTH company.China particularly, according to incompletely statistics, annual from German BOSCH-REXROTH company import axial piston pump more than 200,000.Also want long-term dependence on import, import price is up to 110,000/platform, and Lead Time reaches 6 months to a year and a half, has had a strong impact on the production development of some industries of China.The shaft orientation plunger variable pump that domestic in recent years a few family factory produces, the wild effect of its quality of product various degrees, with regard to its main cause be, it is poor that the pump internal friction is paid part material, the shaft orientation plunger variable pump of producing with German BOSCH-REXROTH company is the same, all exist the friction of thrust plate and rotor to pay eccentric wear, and cause plunger, the backhaul dish, the damage of piston shoes and swash plate, especially rubbing partially of thrust plate causes plunger to-and-fro motion process poor to neutrality, cause plunger and plunger hole lateral force excessive, defectives such as quick abrasion is paid in the friction of entire pump internal organ, and volumetric efficiency is low, and the life-span is short.
The model utility content
Technical problem to be solved in the utility model is exactly will overcome to have the thrust plate eccentric wear that high-pressure shaft exists to variable displacement pump both at home and abroad now, backhaul dish, swash plate damage fast, pump body temperature is high and the life-span is short, and problem such as control accuracy is low, a kind of 250ml/r electric-hydraulic proportion load-sensitive control shaft orientation plunger variable pump is provided, the control that adapts of the size that the flow of realization pump and pressure and system load need, and realize computer control.
Technical problem of the present utility model adopts following technical proposals to solve:
A kind of electric-hydraulic proportion load-sensitive control shaft orientation plunger variable pump, is contained in thrust plate and transmission shaft on the pump cover at the plunger that comprises housing, is contained in swash plate in the housing, is equipped with in the rotor, rotor; Described thrust plate is provided with high pressure window and low pressure window, and the bi-side of pump cover are provided with filler opening and oil outlet, it is characterized in that:
Also include the stroking mechanism that is contained on the housing, and be contained in the electric-hydraulic proportion load-sensitive control integrated valve above the stroking mechanism;
The inside and outside both sides of high pressure window have the ring-like static balance groove of semicircle on the described thrust plate, are provided with the hole on compensating groove, and the lower end, hole connects a through hole, and the through hole the other end is equipped with an adjustable damping, and adjustable damping communicates with described high pressure window;
Have dovetail groove on the high pressure window of described thrust plate and the low pressure window, the dovetail groove tip is provided with aperture, and the aperture lower end connects an inclined hole, and inclined hole communicates with corresponding high pressure window or low pressure window respectively.
Establish an endoporus that leads to the plug center on the described plunger, make a call to a damper aperture at the plunger ball left end, aperture and described endoporus are connected, and have circular groove at the bulb middle part, are arranged with two apertures on the circular groove, and aperture communicates with the damper aperture respectively.
Described stroking mechanism is to be provided with the stroking mechanism hole in the housing upper end, and left end is equipped with small piston in the hole, and the small piston right-hand member connects big piston, and spring is contained in the small piston left side, and the valve piece is equipped with in both sides, stroking mechanism hole; Below big small piston, the drive bar is housed, drives the bar lower end and vertically connect lever.
Include electro-hydraulic proportional throttle valve, electric-hydraulic proportion pressure valve, load-sensitive valve and safety valve in the described electric-hydraulic proportion load-sensitive control integrated valve; Be installed in parallel electro-hydraulic proportional throttle valve, load-sensitive valve and safety valve on the control oil channel of described integrated valve, the electric-hydraulic proportion pressure valve is housed after electro-hydraulic proportional throttle valve, between electro-hydraulic proportional throttle valve and electric-hydraulic proportion pressure valve, be provided with pressure transducer and flow transducer, connect load-sensitive valve after the electric-hydraulic proportion pressure valve, load-sensitive valve is connected with stroking mechanism by oil circuit.
The utility model pays rotor for the main friction of pump and thrust plate has been taked static balance technology and pressure gap compensation technique.Make rotor thrust plate and rotor surface of contact in rotary course that film lubrication be arranged all the time, realized the static pressure support, reduce its impacting force, thereby solved the thrust plate eccentric wear that existing shaft orientation plunger variable pump exists, cause plunger and plunger hole lateral force excessive, quick abrasion is paid in the friction of entire pump internal organ, problems such as low and life-span of volumetric efficiency is short, wearing and tearing have been reduced, simultaneously be provided with dovetail groove and add small sircle hole at thrust plate high low pressure window two ends, make rotor in rotary course, effectively reduce hydraulic shock and reduce noise, solved the variable problem of computer control highi degree of accuracy pump.General structure is because electric-hydraulic proportion load-sensitive control valve piece adopts integrated mode, and the volume ratio of this pump external product of the same type is little by 1/4th, and the control accuracy height, and the response time is short.The utility model is compared with external equivalents, and the basic mechanical design feature index reaches the advanced level that is higher than external like product with part index number.The long working life of pump not only, reduce energy loss, and make system works efficient height, therefore use more extensive, be mainly used in engineering machinery, steel rolling, forging and pressing, mine, petrochemical industry and injection moulding ship machinery, military projects etc. all are badly in need of this shaft orientation plunger variable pump, and are according to incompletely statistics, annual from German BOSCH-REXROTH company import axial piston pump more than 200,000.Also want long-term dependence on import, import price is up to 110,000 every, and Lead Time reaches 6 months to a year and a half, and annual ten thousand of the 2-3 that produce of China can save foreign exchange more than 800,000,000, and can fight for the overseas market share, and development prospect is wide.
Description of drawings
Fig. 1 is the utility model structural representation,
Fig. 2 is the utility model port plate structure schematic representation,
Fig. 3 is the C-C sectional view of Fig. 2,
Fig. 4 is the B-B sectional view of Fig. 2,
Fig. 5 is the utility model piston structure schematic representation,
Fig. 6 is an electric-hydraulic proportion load-sensitive control valve piece oil-way system schematic representation,
Fig. 7 is the electro-hydraulic proportional throttle valve schematic representation,
Fig. 8 is an electric-hydraulic proportion pressure valve schematic representation,
Fig. 9 is the load-sensitive valve schematic representation,
Figure 10 is the relief valve schematic representation,
Figure 11 is the stroking mechanism schematic representation.
Embodiment
Below in conjunction with accompanying drawing the utility model is further elaborated:
The utility model is formed the seal operation volume by housing 1, swash plate 2, rotor 7, plunger 6, thrust plate 8, transmission shaft 9 and pump cover 15, can realize suction oil during the rotor rotation.Swash plate 2 is contained on the housing 1 interior swash plate seat, and swash plate 2 has a tilt angle gamma with rotor 7, and plunger 6 is housed in the plunger hole of rotor 7, and the bulb of plunger 6 is withheld with piston shoes 4 and is connected.Slide blocks 3 is housed on the swash plate 2, and plunger piston slippery boots 4 is pressed in by backhaul dish 5 on the slide blocks 3 of swash plate 2, and backhaul dish 5 is connected with slide blocks 3, and slide blocks 3 is connected with swash plate 2.Rotor 7 is provided with center bulb 11, is equipped with to give impacting force spring 12 in center bulb 11, and center bulb 11 inserts in slide blocks 3 endoporus.Thrust plate 8 is contained on the pump cover 15, and pump cover 15 is connected with housing 1.Stroking mechanism 13 is housed on the housing 1, electric-hydraulic proportion load-sensitive control integrated valve 14 is housed on stroking mechanism 13.The bi-side of pump cover 15 are provided with oil inlet P o and oil outlet Ps.
As shown in Figure 2, both sides have the ring-like static balance groove 8.1 of twice semicircle inside and outside high pressure window on thrust plate 8 surfaces, on compensating groove 8.1, be provided with hole 8.2 as shown in Figure 3,8.2 lower ends, hole connect a through hole 8.3, through hole 8.3 the other ends connect an adjustable damping 8.4, and adjustable damping 8.4 communicates with described high pressure window 8.8.High pressure oil enters the ring-like static balance groove 8.1 of semicircle from thrust plate window 8.8 by adjustable damper 8.4, the reaction thrust of 8 pairs of rotors 7 of may command thrust plate thus, to reach comparatively ideal impacting force coefficient, can carry out the compensation of pressure gap to rotor and thrust plate fastness like this, and remain certain film lubrication is arranged between the fastness, rotor and thrust plate are reduced wear and generate heat, and reach more than 6000 hours the working life that makes pump, external like product 5000 hours, and significantly reduce the noise and the heating of pump, reach this pump high performance technology index request.
High pressure window 8.8 on thrust plate 8 and low pressure window 8.9 two ends have dovetail groove 8.5 as shown in Figure 2, be provided with φ 2 apertures 8.6 as shown in Figure 4 in dovetail groove 8.5 tips, aperture 8.6 lower ends connect an inclined hole 8.7, communicate with high pressure window 8.8 and low pressure window 8.9 respectively by inclined hole 8.7.Thrust plate 8 is designed to the sphere distributing construction with the surface of contact of rotor 7, when rotor 7 rotations, low pressure area is to zone of high pressure transition and zone of high pressure during to the low pressure area transition, dovetail groove 8.5 effectively eliminate fluid to the impact of plunger 6, eliminate dead volume and reduce noise, the impact of pump, the noise of reduction pump can be eliminated, rotor running balance can be made simultaneously, steadily, reduce the disturbing moment of rotor, also reduced the lateral force of rotor radial load and plunger ball.
As shown in Figure 5, on plunger 6, be provided with φ 6 endoporus 6.1, lead to the plug center, make a call to a φ 1.6 apertures 6.2 from the bulb center to the bulb end face again, length is 7.2mm, as fixing damper, φ 6 endoporus 6.1 of pressure oil by plunger 6 are entering by damper 6.2 in the ball-and-socket of piston shoes 4 as shown in Figure 1 like this, and the bulb of plunger 6 is had certain reaction thrust, balance the impacting force of a big chunk plunger ball to piston shoes 4 ball-and-sockets, the position on the upper side at the plunger ball center, promptly the lower half portion that contacts with ball-and-socket is provided with circular groove 6.3, be arranged with two φ, 0.6 aperture 6.4 in groove, aperture 6.4 communicates with fixing damper 6.2.Hydraulic oil is by plunger 6 endoporus and damper 6.2, again by plunger ball aperture 6.4, enter on the bulb in the circular groove, so not only increase the reaction thrust of plunger ball, and the plunger ball swing time can make the ball-and-socket of plunger ball and piston shoes 4 that film lubrication is arranged all the time, reduced friction, particularly worked as the aperture (shown in Figure 1) of the pressure oil of plunger 6 bottoms in the rotor rotation process by plunger 6.1,6.2 and piston shoes 4.Pressure oil enters the piston shoes bottom, like this slide block on piston shoes bottom plane and the swash plate this fastness is had film lubrication all the time, and can also balance the impacting force of very most of plunger connecting rod piston shoes to slide block, reduced greatly the plunger connecting rod piston shoes to the wearing and tearing of slide block, reduced noise, effectively improve the working life of pump.
As shown in Figure 6, be electric-hydraulic proportion load-sensitive control oil channel principle schematic, by stroking mechanism 13 and integrated after electric-hydraulic proportion load-sensitive control valve 14 form.Include electro-hydraulic proportional throttle valve 14.1, electric-hydraulic proportion pressure valve 14.2, load-sensitive valve 14.3 and safety valve 14.4 in the electric-hydraulic proportion load-sensitive control integrated valve 14; Be installed in parallel electro-hydraulic proportional throttle valve 14.1, load-sensitive valve 14.3 and safety valve 14.4 on the control oil channel of described integrated valve 14, electric-hydraulic proportion pressure valve 14.2 is housed after electro-hydraulic proportional throttle valve 14.1, between electro-hydraulic proportional throttle valve 14.1 and electric-hydraulic proportion pressure valve 14.2, be provided with pressure transducer 14.5 and flow transducer 14.6, connect load-sensitive valve 14.3 after the electric-hydraulic proportion pressure valve 14.2, load-sensitive valve 14.3 is connected with stroking mechanism 13 by oil circuit.
As shown in Figure 7, electro-hydraulic proportional throttle valve 14.1, spool 14.1.4 are contained in the valve body 14.1.3, small valve core 14.1.5, and spring 14.1.6 is contained in the spool right side successively, and end cap 14.1.7 is connected with screw 14.1.8 with valve body 14.1.3.Proportion electro-magnet 14.1.1 is contained in the valve body 14.1.3 left side, and O type circle 14.1.2 is housed in the middle of proportion electro-magnet 14.1.1 and valve body 14.1.3.
Electric-hydraulic proportion pressure valve as shown in Figure 8, spool 14.2.3 is contained in the valve body 14.2.2, and valve end cap 14.2.1 is contained in the valve body left side, connects with screw 14.2.5, electromagnet 14.2.4 is contained in the valve body right side, and O type circle 14.2.6 is housed between valve body 14.2.2 and valve end cap 14.2.1.
Load-sensitive valve as shown in Figure 9, spool 14.3.2 is contained in the valve body 14.3.1, and valve body both sides end cap 14.3.6 connects by screw 14.3.5, and spring 14.3.4 is contained in spool the right, and O type circle 14.3.3 is housed between valve body 14.3.1 and end cap 14.3.6.
Relief valve from left to right is equipped with spool 14.4.3, spring 14.4.4, spring seat 14.4.7, pressure regulation bar 14.4.6 successively in the valve body 14.4.2 as shown in figure 10, and end cap 14.4.1 is equipped with in the valve body both sides, and O type circle 14.4.5 is contained in the end cap 14.4.1.
As shown in figure 11, stroking mechanism 13 is to be provided with stroking mechanism hole 17 in housing 1 upper end, and left end is equipped with small piston 13.2 in the hole 17, and small piston 13.2 right-hand members connect big piston 13.3, spring 13.1 is contained in the small piston left side, and valve piece 13.5,13.9 is equipped with in both sides, stroking mechanism hole; Below big small piston, be equipped with and drive bar 13.6, drive bar 13.6 lower ends and vertically connect lever 13.7.
As shown in Figure 6, electric-hydraulic proportion load-sensitive Control work principle and control characteristic are described as follows:
In electric-hydraulic proportion load-sensitive control shaft orientation plunger variable pump variable process:
As two proportion electro-magnet 14.1.1, the voltage of 14.2.4 or electric current, according to the system works load, by after the computer settings, system pressure is constant by pressure transducer and flow transducer, again because of pressure reduction P before and after the throttle valve
3-P
4Be a normal value, for system provides a [constant, relief valve protective system safety.As when system load pressure raises, reduce by Fig. 8 electric-hydraulic proportion pressure valve 14.2 pressure, entering Fig. 9 load-sensitive valve 14.3 pressure P 1 also reduces, make and enter Figure 11 stroking mechanism oil cylinder working-pressure P2 reduction, driving bar 13.6 drive swash plates on the stroking mechanism moves to right, simultaneously at this instantaneous pressure sensor 14.5, by calculating given curtage value, P2 increases, make big piston 13.2 and small piston 13.3 stress balances, the certain tilt angle gamma 1 of swash plate 2 swings, be exactly the needed pressure of system load, pass through the given curtage value of computer by flow transducer 14.6 simultaneously in this,, make Fig. 7 electro-hydraulic proportional throttle valve 14.1 that certain opening be arranged, the flow that passes through is the needed flow of load system just, therefore the electric-hydraulic proportion load-sensitive is controlled shaft orientation plunger variable pump, and the flow of its output and pressure size adapt with needed flow of work system and pressure size.
If raise by electric-hydraulic proportion pressure valve 14.2 pressure when system load pressure reduces, entering Fig. 9 load-sensitive valve 14.3 pressure P 1 also raises, make and enter Figure 11 stroking mechanism oil cylinder working-pressure P2 rising, driving bar 13.6 drive swash plates on the stroking mechanism moves to left, pass through the given curtage value of computer at instantaneous pressure sensor 14.5 simultaneously, P2 reduces, and makes big piston 13.3 and small piston 13.2 reach new equilibrium of forces.(swash plate 2 get back certain tilt angle gamma 2) is exactly the required pressure of system load.Pass through the curtage value of the given electromagnet 14.1.1 of computer simultaneously by flow transducer 14.6 in this, make electro-hydraulic proportional throttle valve 14.1 that certain opening be arranged, the flow that passes through is the required flow of load system just, so electric-hydraulic proportion load-sensitive control shaft orientation plunger variable pump, required flow and the pressure size of the flow of its output and pressure size and work system load adapts, and is a high energy-conservation power source.
When the utility model transmission shaft 9 and rotor 7 rotations, when plunger 6 stretches out, fluid passes through filler opening, entering plunger base with thrust plate 8 low pressure windows is the pump oil suction, and when transmission shaft 9 and rotor 7 continuation rotations, the fluid of plunger 6 bottoms is discharged by oil drain out on thrust plate 8 high pressure windows and the pump cover, oil extraction for pump, just forming suction oil so respectively once when rotor 7 rotates a circle, promptly is pump delivery g, and the flow of this pump is Q=ng.Stroking mechanism 13 can be realized the flow size adjustment of pump by regulating the pivot angle of swash plate.Thrust plate 8 is contained on the pump cover 15, gives the impacting force size by 7 pairs of thrust plates 8 of the adjustable turn over of cushioning on the bulb inner spring of center.
The utility model control mode also has: constant voltage control, servocontrol, various control forms such as permanent power control and electric-hydraulic proportion control.
Claims (8)
1. electric-hydraulic proportion load-sensitive control shaft orientation plunger variable pump, is contained in thrust plate and transmission shaft on the pump cover at the plunger that comprises housing, is contained in swash plate in the housing, is equipped with in the rotor, rotor; Described thrust plate is provided with high pressure window and low pressure window, and the bi-side of pump cover are provided with filler opening and oil outlet, it is characterized in that:
Also include the stroking mechanism (13) that is contained on the housing (1), and be contained in the electric-hydraulic proportion load-sensitive control integrated valve (14) above the stroking mechanism (13);
The inside and outside both sides that described thrust plate (8) is gone up high pressure window (8.8) have the ring-like static balance groove of semicircle (8.1), on compensating groove (8.1), be provided with hole (8.2), lower end, hole (8.2) connects a through hole (8.3), through hole (8.3) the other end connects an adjustable damping (8.4), and adjustable damping (8.4) communicates with described high pressure window (8.8);
Have dovetail groove (8.5) on the high pressure window (8.8) of described thrust plate (8) and the low pressure window (8.9), dovetail groove (8.5) tip is provided with aperture (8.6), aperture (8.6) lower end connects an inclined hole (8.7), and inclined hole (8.7) communicates with corresponding high pressure window (8.8) or low pressure window (8.9) respectively.
2. electric-hydraulic proportion load-sensitive control shaft orientation plunger variable pump according to claim 1, it is characterized in that establishing on the described plunger (6) endoporus (6.1) that leads to the plug center, make a call to a damper aperture (6.2) at the plunger ball left end, aperture (6.2) is connected with described endoporus (6.1), have circular groove (6.3) at the bulb middle part, be arranged with two apertures (6.4) on the circular groove (6.3), aperture (6.4) communicates with damper aperture (6.2) respectively.
3. electric-hydraulic proportion load-sensitive control shaft orientation plunger variable pump according to claim 1, it is characterized in that described stroking mechanism (13) is to be provided with stroking mechanism hole (17) in housing (1) upper end, the interior left end in hole (17) is equipped with small piston (13.2), small piston (13.2) right-hand member connects big piston (13.3), spring (13.1) is contained in the small piston left side, and valve piece (13.5), (13.9) are equipped with in both sides, stroking mechanism hole; Below big small piston, be equipped with and drive bar (13.6), drive bar (13.6) lower end and vertically connect lever (13.7).
4. electric-hydraulic proportion load-sensitive control shaft orientation plunger variable pump according to claim 1, it is characterized in that including electro-hydraulic proportional throttle valve (14.1) in the described electric-hydraulic proportion load-sensitive control integrated valve (14), electric-hydraulic proportion pressure valve (14.2), load-sensitive valve (14.3) and safety valve (14.4); Be installed in parallel electro-hydraulic proportional throttle valve (14.1), load-sensitive valve (14.3) and safety valve (14.4) on the control oil channel of described integrated valve (14), at electro-hydraulic proportional throttle valve (14.1) electric-hydraulic proportion pressure valve (14.2) is housed afterwards, between electro-hydraulic proportional throttle valve (14.1) and electric-hydraulic proportion pressure valve (14.2), be provided with pressure transducer (14.5) and flow transducer (14.6), electric-hydraulic proportion pressure valve (14.2) connects load-sensitive valve (14.3) afterwards, and load-sensitive valve (14.3) is connected with stroking mechanism (13) by oil circuit.
5. electric-hydraulic proportion load-sensitive control shaft orientation plunger variable pump according to claim 4, the spool (14.1.4) that it is characterized in that described electro-hydraulic proportional throttle valve (14.1) is contained in the valve body (14.1.3), small valve core (14.1.5), spring (14.1.6) are contained in spool (14.1.4) right side successively, valve rear end is provided with end cap (14.1.7), end cap (14.1.7) and valve body (14.1.3), proportion electro-magnet (14.1.1) is equipped with on valve body (14.1.3) left side, is provided with O type circle (14.1.2) between proportion electro-magnet (14.1.1) and valve body (14.1.3).
6. electric-hydraulic proportion load-sensitive control shaft orientation plunger variable pump according to claim 4, the spool (14.2.3) that it is characterized in that described electric-hydraulic proportion pressure valve (14.2) is contained in the valve body (14.2.2), valve end cap (14.2.1) is contained in the valve body left side, electromagnet (14.2.4) is equipped with on the valve body right side, between valve body (14.2.2) and valve end cap (14.2.1) O type circle (14.2.6) is housed.
7. electric-hydraulic proportion load-sensitive control shaft orientation plunger variable pump according to claim 4, the spool (14.3.2) that it is characterized in that described load-sensitive valve (14.3) is contained in the valve body (14.3.1), valve body both sides end caps (14.3.6) connect by screw (14.3.5), spring (14.3.4) is contained in spool the right, between valve body (14.3.1) and end cap (14.3.6) O type circle (14.3.3) is housed.
8. electric-hydraulic proportion load-sensitive control shaft orientation plunger variable pump according to claim 4, it is characterized in that in the valve body (14.4.2) of described relief valve (14.4) spool (14.4.3), spring (14.4.4), spring seat (14.4.7), pressure regulation bar (14.4.6) being housed successively from left to right, end cap (14.4.1) is equipped with in the valve body both sides, and O type circle (14.4.5) is housed in the end cap (14.4.1).
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| CN2009201440751U CN201502492U (en) | 2009-09-19 | 2009-09-19 | Electro-hydraulic proportional load-sensitive control variable-displacement axial piston pump |
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| CN2009201440751U CN201502492U (en) | 2009-09-19 | 2009-09-19 | Electro-hydraulic proportional load-sensitive control variable-displacement axial piston pump |
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| CN104533742B (en) * | 2014-12-30 | 2017-02-22 | 南京萨伯工业设计研究院有限公司 | Hydraulic pump oil reversing device and control method thereof |
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