CN206338265U - A kind of power control system of hydraulic excavator - Google Patents
A kind of power control system of hydraulic excavator Download PDFInfo
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- CN206338265U CN206338265U CN201621443167.6U CN201621443167U CN206338265U CN 206338265 U CN206338265 U CN 206338265U CN 201621443167 U CN201621443167 U CN 201621443167U CN 206338265 U CN206338265 U CN 206338265U
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- 230000001105 regulatory effect Effects 0.000 claims description 49
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical compound [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 claims description 37
- 125000006850 spacer group Chemical group 0.000 claims description 26
- 238000009530 blood pressure measurement Methods 0.000 claims description 23
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Abstract
The utility model discloses a kind of power control system of hydraulic excavator, including engine, hydraulic pump, aux. control valve and banked direction control valves, hydraulic pump includes swash plate plunger pump and power governor；Engine is connected with swash plate plunger pump；Power governor includes the spring on push-rod piston, valve element and valve element；The first piston mouthful of first oil-out of swash plate plunger pump the first oil inlet respectively with banked direction control valves, the first oil-feed duct of aux. control valve and thrust piston is connected；The second piston mouthful of second oil-out of swash plate plunger pump the second oil inlet respectively with banked direction control valves, the second oil-feed duct of aux. control valve and thrust piston is connected；The oil-out of shuttle valve is connected with the valve element oil inlet of valve element and the right-hand member of swash plate plunger pump lifting force piston respectively；The valve element oil-out of valve element is connected with the left end of swash plate plunger pump lifting force piston.The utility model realizes Dynamic Matching engine output torque, improves hydraulic pressure pump power and excavator operating efficiency.
Description
Technical field
The utility model belongs to hydraulic control system technical field used in engineering machinery, more particularly to a kind of hydraulic pressure
Excavator power control system.
Background technology
As domestic and international infrastructure construction is slowed down, the significantly atrophy of hydraulic crawler excavator totality sales volume.Subdivision field, it is small-sized
Hydraulic crawler excavator is mainly used in the occasion such as municipal works and small rural operation, and being slowed down by infrastructure construction influences small, pin
Amount is stable, the main battle ground competed for market share as each main engine plants, each producer all actively releasing, cost is lower, oil consumption is lower and
The higher small type hydraulic excavator of operating efficiency.A kind of multifunctional small-size hydraulic excavating as disclosed in CN200420041431.4
Machine, it includes power transmission connecting mechanism, slewing equipment, excacation device and hydraulic control system, the excacation dress
Put and general connector is installed, the general connector is by connector holder, bearing pin, adjustable hanger, setting-up screw, stop nut
And its upper backup pad, lower supporting plate composition；Connector holder is provided with two pin shaft holes, and two pin shaft holes are coupled to bucket by bearing pin respectively
On the connecting rod of bar front end and bucket cylinder front end, pin shaft hole and adjustable hanger are then connected with scraper bowl；Pass through the general connector
Replaceable scraper bowl.
The current way of each main engine plants mainly has two ways：Hydraulic component is improved to improve hydraulic system efficiency and make
Increase engine power and moment of torsion with turbocharged engine.Examined from small type hydraulic excavator working condition and manufacture economy
Consider, the limitation of diesel engine drives band total power is used domestic small type hydraulic excavator (to avoid bearing power from crossing ambassador's hair more
Motivation suppress it is flame-out, to pump set highest use power) variable pump with parallel banked direction control valves power drive system combine.This gives
The mode that above two improves overall efficiency brings difficulty：
1st, from hydraulicefficiency the characteristics of analyze, to improve its transmission efficiency will reduce fluid flow resistance, measure
Improve the surface smoothness of quality of fit and passage between element volume sealing, part.Due to liquid such as pump, banked direction control valves and motors
Casting die is generally cast member, further improves the accuracy of manufacture and surface smoothness difficulty height, input are big；
2nd, band turbocharged engine is used to improve engine power and moment of torsion and then improve hydraulic pump power limit,
Core component is turbocharger, and full name is exhaust-driven turbo-charger exhaust-gas turbo charger, exactly drives turbo blade using engine exhaust, is come
Air is compressed in rear injection engine cylinder and burnt.Make the burning meeting in cylinder more abundant, so as to produce more
Many energy, on the premise of engine same displacement, can be substantially improved the power and moment of torsion of engine, and in theory about 40%
Left and right.Because turbocharger is driven by waste gas, under low engine speeds operating mode, when discharge amount of exhaust gas is not enough,
Turbocharger can not only bring the lifting of power, can also produce dynamic response hysteresis phenomenon because of hindering to be vented on the contrary, this
It is exactly turbo lag effect.It can be seen that output torque reduces obvious under low engine speed from Fig. 1 motor characteristic curves, but
It is that hydraulic pump load torque is only relevant with outer load and unrelated with engine speed, therefore turbo lag effect can cause raising liquid
Press pump power limited (pump moment of torsion will be less than engine torque under the low speed).
Utility model content
The purpose of this utility model, which is that, to be overcome the deficiencies in the prior art there is provided a kind of hydraulic crawler excavator Power Control
System, the utility model realizes Dynamic Matching engine output torque, and to improve hydraulic pressure pump power, realization makes full use of engine
Power, improves hydraulic crawler excavator operating efficiency.
To achieve these goals, the utility model provides a kind of power control system of hydraulic excavator, including starts
Machine, hydraulic pump, aux. control valve and banked direction control valves, the hydraulic pump include swash plate plunger pump and power governor；It is described to start
The output shaft of machine is connected by shaft coupling with the input shaft of the swash plate plunger pump；The pumping oil of the swash plate plunger pump
Mouth and drain tap are connected with the first fuel tank；The power governor includes the spring on push-rod piston, valve element and valve element；
First oil-out of the swash plate plunger pump the first oil inlet respectively with the banked direction control valves, aux. control valve
First oil-feed duct is connected with the first piston mouthful of thrust piston；Second oil-out of the swash plate plunger pump respectively with institute
The second piston mouthful for stating the second oil inlet of banked direction control valves, the second oil-feed duct of aux. control valve and thrust piston is connected；
First oil-out and the second oil-out are connected by shuttle valve, the oil-out of the shuttle valve respectively with the valve
The valve element oil inlet of core is connected with the right-hand member of swash plate plunger pump lifting force piston；The valve element oil-out of the valve element with it is described
The left end of swash plate plunger pump lifting force piston is connected；
The fuel-displaced duct of the aux. control valve is connected with the 3rd piston mouthful of the push-rod piston；The auxiliary control
The oil return duct of valve is connected with the second fuel tank；
The pressure adjustment formula of the power governor is：Fac+ (Fa1+Fa2)/2≤Fa, wherein Fac are the 3rd work
The pressure of mouth is filled in, Fa1 is the pressure of first piston mouthful, and Fa2 is the pressure of second piston mouthful, and Fa is the spring of spring on valve element
Power.
Further, the aux. control valve include valve body, shuttle valve component and pressure adjusting part, the valve body include by
The functional areas that internal gutter is constituted, the functional areas include oil-feed area, pressure regulatory region and oil circuit break-make area；
The oil-feed area includes the first oil-feed duct, the second oil-feed duct, busway and oil discharge passage, and described first enters
Oilhole road, the second oil-feed duct are connected with the busway, and the busway is connected with the oil discharge passage；
The shuttle valve component includes shuttle valve spool, steel ball and positioning joint, and the shuttle valve spool center is from left to right successively
Oil-feed unthreaded hole, inner chamber and internal thread hole are provided with and communicated with, the left side of the inner chamber is in smooth cone structure, the cylinder of the inner chamber
Circumference uniform distribution is provided with multiple first through hole on face, and the steel ball is located at the inner chamber of the shuttle valve spool；The positioning joint
Left end be provided with left outside screw thread, be provided centrally with turning on the endoporus at the positioning joint two ends, the positioning joint endoporus
Left end aperture is in smooth cone structure, and the positioning joint passes through in the left outside screw thread connection and the shuttle valve spool
At screwed hole；The internal diameter of the internal diameter of the oil-feed unthreaded hole of the shuttle valve spool and the endoporus of positioning joint is respectively less than the straight of the steel ball
Footpath；
The shuttle valve component is installed in the busway, the oil-feed unthreaded hole of the shuttle valve spool and first oil-feed
Duct is connected, and the endoporus of the positioning joint is connected with the second oil-feed duct, the shuttle valve spool inner chamber face of cylinder
On first through hole connect the inner chamber and the fuel-displaced duct；
The pressure regulatory region includes pressure regulating hole road, a left side for valve body described in the two ends insertion in the pressure regulating hole road
The pressure adjusting part is installed, the pressure adjusting part includes valve in side and right flank, the pressure regulating hole road
Core spacer, regulation spring, adjusting pressuring valve core and the first plug, the left end and right-hand member in the pressure regulating hole road pass through described the respectively
One plug and valve element spacer are blocked；
The left end of the pressure spring withstands the right-hand member of the adjusting pressuring valve core, and the right-hand member of the pressure spring withstands the valve
Core spacer, the left end of the adjusting pressuring valve core withstands first plug；The face of cylinder of the adjusting pressuring valve core is adjusted with the pressure
The inner surface in duct is formed with oil suction chamber and goes out oil pocket, the oil suction chamber with it is described go out oil pocket be connected, the oil suction chamber and institute
Fuel-displaced duct is stated to be connected；
The adjusting pressuring valve core has oil through by left end center is axially disposed, and the aperture of the oil through is in smooth conical surface knot
Circumference uniform distribution is provided with multiple second through holes on structure, the face of cylinder of the adjusting pressuring valve core, and second through hole connects the logical oil
Hole and pressure regulating hole road；
The oil circuit break-make area includes oil inlet passage, oil circuit break-make duct, fuel-displaced duct and drainback passage, and the oil-feed is led to
Road with it is described go out oil pocket be connected, the oil inlet passage is connected with the oil circuit break-make duct；At the oil circuit break-make duct
Solenoid directional control valve is installed, the solenoid directional control valve forms oil circuit break-make inner chamber with the oil circuit break-make duct；The electromagnetism is changed
During to valve dead electricity, the oil inlet passage disconnects with the oil circuit break-make inner chamber, the oil circuit break-make inner chamber and the drainback passage
It is connected；When the solenoid directional control valve obtains electric, the oil inlet passage and the oil circuit break-make intracavity inter-connection, the oil circuit break-make
Inner chamber disconnects with the drainback passage, and the oil circuit break-make inner chamber is connected with the fuel-displaced duct.
Further, the oil-feed area also includes the first pressure measurement duct and the second pressure measurement duct, the first pressure measurement duct
It is connected with the first oil-feed duct, the second pressure measurement duct is connected with the second oil-feed duct；
The oil-feed area also includes the first technique duct, and the first technique duct is connected with the busway, institute
The center line and the center line in the fuel-displaced duct for stating the first technique duct are on the same line, the first technique duct
First expanded spheres are inside installed.
Further, the right-hand member of the positioning joint is provided with right external screw thread, and the inner surface setting of the busway has
Internal thread, the right external screw thread of the positioning joint coordinates with the internal thread screw thread of the busway；The right side of the positioning joint
End is provided with interior hexagonal endoporus；The right flank of valve body described in the right-hand member insertion of the busway；The shuttle valve component also includes
Second plug, the right-hand member of the busway is blocked by second plug.
Further, the face of cylinder of the shuttle valve spool left end is provided with annular groove, the annular groove and is provided with
Seal assembly, the seal assembly is made up of the first O-ring seal of folder in the middle of two back-up rings.
Further, the left end inner surface setting in the pressure regulating hole road has left end internal thread, right-hand member inner surface setting
There is right-hand member internal thread；External screw thread, external screw thread and the pressure regulating hole of first plug are provided with first plug
The left end internal thread threaded connection in road；Be provided with external screw thread on the valve element spacer, the external screw thread of the valve element spacer with it is described
The right-hand member internal thread threaded connection in pressure regulating hole road；Pass through the 2nd O between the valve element spacer and the pressure regulating hole road
Type sealing ring is sealed；
Cylindrical hole is provided with the valve element spacer, the right-hand member of the adjusting pressuring valve core, which is provided with step, the step, pacifies
Equipped with spring washer；The left end of the pressure spring withstands the spring washer, and right-hand member is installed on the cylinder of the valve element spacer
In hole and withstand the cylindrical hole bottom hole.
Further, the first gradual change type groove, the adjusting pressuring valve core are provided with the face of cylinder of the adjusting pressuring valve core left end
The face of cylinder pass through the first gradual change type groove and the pressure regulating hole road inner surface between form oil film.
Further, the pressure regulatory region also include the first connected pore channel and the second connected pore channel, it is described go out oil pocket lead to
Cross first connected pore channel with second connected pore channel to be connected, second connected pore channel is connected with the oil inlet passage
It is logical；
The pressure regulatory region also includes the second technique duct and the 3rd technique duct, the center in the second technique duct
Line and the center line of first connected pore channel are on the same line, and the second expansion is provided with the second technique duct
Ball；The center line and the center line of second connected pore channel in the 3rd technique duct are on the same line, and described
The 3rd expanded spheres are installed in three technique ducts.
Further, the solenoid directional control valve includes reversing valve core, fixed spool, back-moving spring, fixed electromagnet, movement
Electromagnet and magnet coil；The reversing valve core is installed in the oil circuit break-make duct, the outer surface of the reversing valve core with
The inner surface in the oil circuit break-make duct forms the oil circuit break-make inner chamber；
Fixed electromagnet and Mobile electromagnetic iron described in the magnet coil inner sleeve；The back-moving spring is installed on the movement
In electromagnet, the two ends of the back-moving spring are respectively against the fixed electromagnet and Mobile electromagnetic iron；The Mobile electromagnetic iron
It is connected with the left end of the reversing valve core, the right-hand member of the reversing valve core is provided with piston；The reversing valve core is installed on institute
State in the endoporus of fixed spool and can be horizontally slipped relative to the fixed spool；The outer surface of the reversing valve core with it is described solid
The inner surface formation hollow cavity of fixed valve plug, multiple the are respectively arranged with two circumference of the fixed spool vertically in uniform way
Three through holes and fourth hole, the third through-hole are connected with the oil inlet passage, and the fourth hole connects the oil circuit and led to
Disconnected inner chamber and hollow cavity；
During the solenoid directional control valve dead electricity, the oil circuit break-make inner chamber is successively through the fourth hole, hollow cavity, fixation
Gap between the right side of valve element and the left side of reversing valve core piston is connected with the drainback passage；
When the solenoid directional control valve obtains electric, the oil inlet passage is successively through the third through-hole, hollow cavity, fourth hole
It is connected with the fuel-displaced duct；
The second gradual change type groove is provided with the outer surface of the reversing valve core left end, the outer surface of the reversing valve core leads to
Cross form oil film between the second gradual change type groove and the inner surface of the fixed spool.
Further, the oil circuit break-make area also include the 4th technique duct, the center line in the 4th technique duct with
The center line of the oil inlet passage is on the same line, and the 4th expanded spheres are provided with the 4th technique duct；
The oil circuit break-make area also includes the 5th technique duct, and the 5th technique duct is connected with the drainback passage
It is logical, the 5th expanded spheres are installed in the 5th technique duct；
The oil circuit break-make area also includes the 3rd pressure measurement duct, and the 3rd pressure measurement duct is connected with the fuel-displaced duct
It is logical.
The beneficial effects of the utility model：The utility model realizes Dynamic Matching engine output torque, to improve liquid
Press pump power, realization makes full use of engine power, improves hydraulic crawler excavator operating efficiency, and wherein aux. control valve is by shuttle valve group
Part, pressure adjusting part and solenoid directional control valve are concentrated in valve body, and compact conformation is lightweight, and small volume is cost-effective, are reduced
Pipeline space-consuming, reduces pipe joint quantity so that contact is few, and the risk leaked is reduced, lightweight, convenient dimension
Many advantages, such as repairing cost-effective.
Brief description of the drawings
, below will be to embodiment in order to illustrate more clearly of the utility model embodiment or technical scheme of the prior art
Or the accompanying drawing to be used needed for description of the prior art is briefly described, it should be apparent that, drawings in the following description are only
It is some embodiments of the present utility model, for those of ordinary skill in the art, is not paying the premise of creative work
Under, other accompanying drawings can also be obtained according to these accompanying drawings.
Fig. 1 is the hydraulic schematic diagram of the utility model embodiment.
Fig. 2 is the three dimensional structure diagram of the aux. control valve of the utility model embodiment.
Fig. 3 is the two-dimensional structure schematic diagram of the utility model embodiment.
Fig. 4 is this Fig. 3 left view.
Fig. 5 is Fig. 4 A-A sectional views.
Fig. 6 is Fig. 4 B-B sectional views.
Fig. 7 is Fig. 4 C-C sectional views.
Fig. 8 is Fig. 3 D-D sectional views.
Fig. 9 is Fig. 3 E-E sectional views.
Figure 10 is Fig. 3 F-F sectional views.
Figure 11 is the M enlarged diagrams in Fig. 5.
Figure 12 is the three dimensional structure diagram of valve body in the utility model embodiment.
Figure 13 is the two-dimensional structure schematic diagram of valve body in the utility model embodiment.
Figure 14 is Figure 13 left view.
Figure 15 is Figure 13 right view.
Figure 16 is Figure 13 rearview.
Figure 17 is Figure 14 G-G sectional views.
Figure 18 is Figure 14 H-H sectional views.
Figure 19 is Figure 14 I-I sectional views.
Figure 20 is Figure 13 J-J sectional views.
Figure 21 is Figure 13 K-K sectional views.
Figure 22 is Figure 13 L-L sectional views.
Figure 23 is the performance diagram of the hydraulic pump of the utility model embodiment.
Above-mentioned reference：
1 engine, 20 swash plate plunger pumps, 21 power governors, 201 thrust pistons, 202 shuttle valves, 210 push-rod pistons,
211 valve elements, 212 springs, 3 first fuel tanks, 4 aux. control valves, 5 banked direction control valves, 6 second fuel tanks,
B1 pumping hydraulic fluid ports, Dr1 drain taps, the oil-outs of C1 first, the oil-outs of C2 second, D1 oil-outs, A1, the first oil-feed
Mouthful, the oil inlets of A2 second, a1 first pistons mouthful, a2 second pistons mouthful, a3 valve element oil inlets, a4 valve element oil-outs, ac the 3rd lives
Fill in mouth,
41 valve bodies, 42 shuttle valve spools, 43 first expanded spheres, 44 steel balls, 45 positioning joints, 46 second plugs, 47 valve elements every
Set, 48 pressure springs, 49 spring washers, 410 adjusting pressuring valve cores, 411 reversing valve cores, 412 fixed spools, 413 back-moving springs, 414
Magnet coil, 415 Mobile electromagnetic iron, 416 fixed electromagnets, 417 first plugs, 418 the 4th expanded spheres, 419 the 5th expanded spheres,
420 second O-ring seals, 421 second expanded spheres, 422 the 3rd expanded spheres, 423 back-up rings, 424 first O-ring seals；
The fuel-displaced ducts of A, B busways, C pressure regulation duct, D oil circuit break-makes duct, T drainback passages, the oil-feeds of P1 first
Duct, the second oil-feeds of P2 duct, P3 oil circuit break-makes inner chamber, the first pressure measurement of M1 duct, the second pressure measurement of M2 duct, the pressure taps of M3 the 3rd
Road；
The first techniques of a duct, the fuel-displaced ducts of b, c oil suction chambers, d goes out oil pocket, and e pressure feedback chambers, g oil inlet passages, h second connects
Through hole road, the technique ducts of i the 3rd, the technique ducts of j the 4th, the connected pore channels of k first, the second techniques of n duct, the technique ducts of m the 5th.
Embodiment
Utility model is further illustrated below in conjunction with the accompanying drawings, but is not limited to scope of the present utility model.
Embodiment
As shown in figure 1, a kind of power control system of hydraulic excavator that the utility model is provided, including engine 1, hydraulic pressure
Pump, aux. control valve 4 and banked direction control valves 5, the hydraulic pump include swash plate plunger pump 20 and power governor 21；The engine
1 output shaft is connected by shaft coupling with the input shaft of the swash plate plunger pump 20；The pump of the swash plate plunger pump 20
Inlet port B1 and drain tap Dr1 are connected with the first fuel tank 3；The power governor 21 includes push-rod piston 210, valve element
211 and valve element 211 on spring 212；
First oil-out C1 of the swash plate plunger pump 20 the first oil inlet A1 respectively with the banked direction control valves 5, auxiliary
The first oil-feed duct P1 of valve 4 is controlled to be connected with the first piston mouthful a1 of thrust piston 210；The swash plate plunger pump 20
The second oil inlet A2, the second oil-feed duct P2 of aux. control valve 4 and the thrusts of second oil-out C2 respectively with the banked direction control valves 5
The second piston mouthful a2 of piston 210 is connected；
The first oil-out C1 and the second oil-out C2 are connected by shuttle valve 202, the oil-out D1 of the shuttle valve 202
It is connected respectively with the valve element oil inlet a3 of the valve element 211 and the right-hand member of the lifting force piston 201 of swash plate plunger pump 20；It is described
The valve element oil-out a4 of valve element 211 is connected with the left end of the lifting force piston 201 of swash plate plunger pump 20；
The fuel-displaced duct A of the aux. control valve 4 is connected with the 3rd piston mouthful ac of the push-rod piston 210；It is described
The oil return duct T of aux. control valve 4 is connected with the second fuel tank 6；
The pressure adjustment formula of the power governor 21 is：Fac+ (Fa1+Fa2)/2≤Fa, wherein Fac are the 3rd
Piston mouthful ac pressure, Fa1 is first piston mouthful a1 pressure, and Fa2 is second piston mouthful a2 pressure, and Fa is on valve element 211
The spring force of spring 212.
As shown in Fig. 2-22, the aux. control valve includes valve body 1, shuttle valve component and pressure adjusting part, the valve body 1
Including the functional areas being made up of internal gutter, the functional areas include oil-feed area, pressure regulatory region and oil circuit break-make area.
The oil-feed area includes the first oil-feed duct P1, the second oil-feed duct P2, busway B and oil discharge passage b, described
First oil-feed duct P1, the second oil-feed duct P2 are connected with the busway B, the busway B with it is described fuel-displaced logical
Road b is connected.
The shuttle valve component includes shuttle valve spool 42, steel ball 44 and positioning joint 45, and the center of shuttle valve spool 42 is by a left side
It is sequentially communicated to the right and is provided with oil-feed unthreaded hole, inner chamber and internal thread hole, the left side of the inner chamber is in smooth cone structure, described interior
Circumference uniform distribution is provided with multiple first through hole on the face of cylinder of chamber, and the steel ball 44 is located at the inner chamber of the shuttle valve spool 42；
The left end of the positioning joint 45 is provided with left outside screw thread, is provided centrally with turning on the endoporus at the two ends of positioning joint 45, institute
The left end aperture for stating the endoporus of positioning joint 45 is in smooth cone structure, and the positioning joint 45 is connected by the left outside screw thread
Connect at the internal thread hole with the shuttle valve spool 42；The internal diameter of the oil-feed unthreaded hole of the shuttle valve spool 42 and positioning joint 45 it is interior
The internal diameter in hole is respectively less than the diameter of the steel ball 44.
The shuttle valve component is installed in the busway B, the oil-feed unthreaded hole of the shuttle valve spool 42 and described first
Oil-feed duct P1 is connected, and the endoporus of the positioning joint 45 is connected with the second oil-feed duct P2, the shuttle valve spool
First through hole on the 42 inner chambers face of cylinder connects the inner chamber and the fuel-displaced duct b.
The pressure regulatory region includes pressure regulating hole road C, valve body 41 described in the two ends insertion of the pressure regulating hole road C
Left surface and right flank, the pressure adjusting part, the pressure adjusting part bag are installed in the pressure regulating hole road C
Include valve element spacer 47, regulation spring 48, the plug 417 of adjusting pressuring valve core 410 and first, the left end of the pressure regulating hole road C and the right side
End is blocked by first plug 417 and valve element spacer 47 respectively.
The left end of the pressure spring 48 withstands the right-hand member of the adjusting pressuring valve core 410, the right-hand member top of the pressure spring 48
Valve element spacer 47 is stated in residence, and the left end of the adjusting pressuring valve core 410 withstands first plug 417；The circle of the adjusting pressuring valve core 410
Cylinder and the pressure regulating hole road 4C inner surface be formed with oil suction chamber c and go out oil pocket d, the oil suction chamber c with it is described fuel-displaced
Chamber d is connected, and the oil suction chamber c is connected b with the fuel-displaced duct.
The adjusting pressuring valve core 410 has oil through by left end center is axially disposed, and the aperture of the oil through is in smooth cone
Face structure, the cone space that the cone structure in the oil through aperture is surrounded forms pressure feedback chamber e, the adjusting pressuring valve core 410
The face of cylinder on circumference uniform distribution be provided with multiple second through holes, second through hole connects the oil through and pressure regulating hole road
C。
The oil circuit break-make area includes oil inlet passage g, oil circuit break-make duct D, fuel-displaced duct A and drainback passage T, it is described enter
Oily passage g with it is described go out oil pocket d be connected, the oil inlet passage g is connected with the oil circuit break-make duct D；The oil circuit leads to
Solenoid directional control valve is installed, the solenoid directional control valve and the oil circuit break-make duct D-shaped are into oil circuit break-make inner chamber at disconnected duct D
P3；During the solenoid directional control valve dead electricity, the oil inlet passage g and oil circuit break-make inner chamber P3 disconnects, in the oil circuit break-make
Chamber P3 is connected with the drainback passage T-phase；When the solenoid directional control valve obtains electric, in the oil inlet passage g and the oil circuit break-make
Chamber P3 is connected, and the oil circuit break-make inner chamber P3 and the drainback passage T disconnect, the oil circuit break-make inner chamber P3 with it is described fuel-displaced
Duct A is connected.
The oil-feed area also includes the first pressure measurement duct M1 and the second pressure measurement duct M2, the first pressure measurement duct M1 and institute
State the first oil-feed duct P1 to be connected, the second pressure measurement duct M2 is connected with the second oil-feed duct P2.Pass through first
Pressure measurement duct M1 and the second pressure measurement duct M2 connect pressure measuring tie-in respectively, for the first oil-feed duct P1 of measurement and the second fuel feed hole
The pressure of hydraulic oil in road P2.
The oil-feed area also includes the first technique duct a, and the first technique duct a is connected with the busway B,
The center line of the center line of the first technique duct a and the fuel-displaced duct b is on the same line, first technique
First expanded spheres 43 are installed in a of duct.
The right-hand member of the positioning joint 45 is provided with right external screw thread, and the inner surface setting of the busway B has internal thread,
The internal thread screw thread of the right external screw thread of the positioning joint 45 and the busway B coordinates；The right-hand member of the positioning joint 45
It is provided with interior hexagonal endoporus；The right flank of valve body 41 described in the right-hand member insertion of the busway B；The shuttle valve component also includes
Second plug 46, the right-hand member of the busway B is blocked by second plug 46.In being provided with wherein the second plug 46
Hexagonal endoporus, to facilitate the dismounting of the second plug 46, convenient disassembly.
As shown in figure 11, the face of cylinder of the left end of shuttle valve spool 42 is provided with annular groove, the annular groove and pacified
Equipped with seal assembly, the seal assembly is made up of the first O-ring seal 424 of folder in the middle of two back-up ring 423.Seal assembly is realized
The face of cylinder of shuttle valve spool 42 and the sealing of busway B inner surfaces, good sealing effect, it is therefore prevented that the leakage of hydraulic oil.
The left end inner surface setting of the pressure regulating hole road C has left end internal thread, and right-hand member inner surface setting has in right-hand member
Screw thread；External screw thread, the external screw thread of first plug 417 and the pressure regulating hole road C are provided with first plug 417
Left end internal thread threaded connection；External screw thread, the external screw thread of the valve element spacer 47 and institute are provided with the valve element spacer 47
State pressure regulating hole road C right-hand member internal thread threaded connection；Pass through between the valve element spacer 47 and the pressure regulating hole road C
Second O-ring seal 420 is sealed.Interior hexagonal endoporus is provided with wherein the first plug 417, to facilitate tearing open for the first plug 417
Dress, convenient disassembly.Wherein valve element spacer 47 is provided with outer-hexagonal square toes, to facilitate the dismounting of valve element spacer 47.
Cylindrical hole is provided with the valve element spacer 47, the right-hand member of the adjusting pressuring valve core 410 is provided with step, the step
Place is provided with spring washer 49；The left end of the pressure spring 48 withstands the spring washer 49, and right-hand member is installed on the valve element
The cylindrical hole of spacer 47 is interior and withstands the cylindrical hole bottom hole.
The first gradual change type groove, the circle of the adjusting pressuring valve core 410 are provided with the face of cylinder of the left end of adjusting pressuring valve core 410
Form oil film between the inner surface that cylinder passes through the first gradual change type groove and the pressure regulating hole road C.First gradual change type
The setting of groove reduces the face of cylinder and the contact surface of pressure regulating hole road C inner surface of adjusting pressuring valve core 410, works as pressure regulator valve
Core 410 can store small part lubricating oil relative in the long-term sliding processes of pressure regulating hole road C in the first gradual change type groove, with
The lubrication in the sliding process of adjusting pressuring valve core 410 is played, to reduce resistance, reduces frictional force, reduces the cylinder of adjusting spool 410
The abrasion in face and the abrasion of pressure regulating hole road C inner surfaces, improve adjusting spool 410 and the service life of valve body 41.
The pressure regulatory region also include the first connected pore channel k and the second connected pore channel h, it is described go out oil pocket d pass through it is described
First connected pore channel k is connected with the second connected pore channel h, and the second connected pore channel h is connected with the oil inlet passage g
It is logical.
The pressure regulatory region also includes the second technique duct n and the 3rd technique duct i, the second technique duct n's
The center line of center line and the first connected pore channel k is on the same line, and is provided with the second technique duct n
Two expanded spheres 421；The centerline of the center line and the second connected pore channel h of the 3rd technique duct i is straight in same
On line, the 3rd expanded spheres 422 are installed in the 3rd technique duct i.
The solenoid directional control valve include reversing valve core 411, fixed spool 412, back-moving spring 413, fixed electromagnet 416,
Mobile electromagnetic iron 415 and magnet coil 414；The reversing valve core 411 is installed in the oil circuit break-make duct D, the commutation
The outer surface of valve element 411 and the inner surface of the oil circuit break-make duct D form the oil circuit break-make inner chamber P3.
Fixed electromagnet 416 and Mobile electromagnetic iron 415 described in the inner sleeve of magnet coil 414；The back-moving spring 413 is pacified
Loaded in the Mobile electromagnetic iron 415, the two ends of the back-moving spring 413 are respectively against the fixed electromagnet 416 and movement
Electromagnet 415；The Mobile electromagnetic iron 415 is connected with the left end of the reversing valve core 411, the right side of the reversing valve core 411
End is provided with piston；The reversing valve core 411 is installed in the endoporus of the fixed spool 412 and relative to the fixed spool
412 can horizontally slip；The outer surface of the reversing valve core 411 and the inner surface formation hollow cavity of the fixed spool 412, institute
State and be respectively arranged with multiple third through-holes and fourth hole, the described 3rd in uniform way on two circumference of fixed spool 412 vertically
Through hole is connected with the oil inlet passage g, and the fourth hole connects the oil circuit break-make inner chamber P3 and hollow cavity.
During the solenoid directional control valve dead electricity, the oil circuit break-make inner chamber P3 is successively through the fourth hole, hollow cavity, solid
Gap between the right side of fixed valve plug 412 and the left side of the piston of reversing valve core 411 is connected with the drainback passage T-phase.
When the solenoid directional control valve obtains electric, the oil inlet passage g is successively through the third through-hole, hollow cavity, four-way
Hole is connected with the fuel-displaced duct A.
It is provided with the outer surface of the left end of reversing valve core 411 outside second gradual change type groove, the reversing valve core 411
Surface passes through form oil film between the second gradual change type groove and the inner surface of the fixed spool 412.Second gradual change type ditch
The setting of groove reduces the outer surface surface of the contact with the inner surface of fixed spool 412 of reversing valve core 411, works as reversing valve core
During 411 horizontally slip relative to fixed spool 412, small part lubricating oil can be stored in the second gradual change type groove, to play
Lubrication in the sliding process of reversing valve core 411, to reduce resistance, reduces frictional force, reduces the outer surface of reversing valve core 411
Abrasion and the abrasion of the inner surface of fixed spool 412, improve the service life of reversing valve core 411 and fixed spool 412.
The oil circuit break-make area also includes the 4th technique duct j, center line and the oil-feed of the 4th technique duct j
Passage g center line is on the same line, and the 4th expanded spheres 18 are provided with the 4th technique duct j.
The oil circuit break-make area also includes the 5th technique duct m, the 5th technique duct m and the drainback passage T-phase
The 5th expanded spheres 419 are installed in connection, the 5th technique duct m.
The oil circuit break-make area also includes the 3rd pressure measurement duct M3, the 3rd pressure measurement duct M3 and the fuel-displaced duct A
It is connected.3rd pressure measurement duct M3 connects pressure measuring tie-in, to realize the measurement of hydraulic fluid pressure in fuel-displaced duct M3.
The setting in each technique duct of the utility model to facilitate the processing in other ducts and passage etc. valve body 41 Nei, wherein
Each expanded spheres crimp installed in each technique duct, is interlocked with the inner surface with each technique duct, each to realize
The sealing function in technique duct.
The operation principle of the utility model aux. control valve 4：First oil-feed duct P1 and the second oil-feed duct P2 connect respectively
The the first oil-out C1 and the second oil-out C2 of swash plate plunger pump 20, when the first oil-feed duct P1 comes in pressure oil or first
When the pressure for the pressure oil that oil-feed duct P1 comes in is more than the pressure for the pressure oil that the second oil-feed duct P2 comes in, the first fuel feed hole
The pressure oil that road P1 comes in enters shuttle valve spool 42, and oil-feed unthreaded hole of the pressure oil through shuttle valve spool 42 enters in shuttle valve spool 42
Chamber, promotes steel ball 44 to move right, until arrive to positioning joint 45, because the surface of steel ball 44 is sphere and the left end of positioning joint 45
Bore orifice is the conical surface, therefore steel ball 44 is with the formation conical surface seal of positioning joint 45, the pressure oil that the first oil-feed duct P1 comes in
The second oil-feed duct P2 will not be flowed to through busway B；Again because after steel ball moves right, the left side of the inner chamber of shuttle valve spool 42 with
Steel ball 44 has gap so that the pressure oil that the first oil-feed duct P1 comes in the oil-feed unthreaded hole through shuttle valve spool 42, inner chamber, successively
One through hole and flow to oil discharge passage b.Conversely, when the second oil-feed duct P2 pressure oils come in or the second oil-feed duct P2 come in
The pressure of pressure oil when being more than the pressure of the pressure oils come in of the first oil-feed duct P1, the pressure that the second oil-feed duct P2 comes in
Oil enters the endoporus of positioning joint 45 and enters shuttle valve spool 42, promotes steel ball 44 to be moved to the left, due to the inner chamber of shuttle valve spool 2
Left side is the conical surface, steel ball and the formation conical surface seal of shuttle valve spool 42, thus the pressure oil come in from the second oil-feed duct P2 is successively
Endoporus through positioning joint 45, the inner chamber of shuttle valve spool 42, first through hole and flow to oil discharge passage b.
Oil discharge passage b is connected with pressure regulating hole road C oil suction chamber c, thus the pressure oil in oil discharge passage b enters oil-feed
Chamber c, the oil circuit into oil suction chamber c is divided into two-way：Lead up to the face of cylinder of adjusting pressuring valve core 410 and pressure regulating hole road C inner surfaces
Between gap flow to out oil pocket d, the second through hole for separately leading up to the face of cylinder of adjusting pressuring valve core 410 is flowed in adjusting pressuring valve core 410
Oil through and reach pressure feedback chamber e, now enclosed volume all directions of the pressure of pressure oil in valve body 41 are equal, because
This goes out oil pocket d and pressure feedback chamber e pressure is equal, and wherein pressure feedback chamber e pressure is referred to as the feedback of oil pocket d pressure
Pressure.Produced when oil suction chamber c pressure oil flows to the gap between the face of cylinder of adjusting pressuring valve core 10 and pressure regulating hole road C inner surfaces
After tight knot stream, oil pocket d is output to out after the reduction of pressure oil pressure, wherein the big I for going out oil pocket d pressure is entered by pressure spring 48
Row regulation, keeps out oil pocket d output pressure Pd to be equal to the pressure that pressure spring 48 is produced, reaches balance.Go out oil pocket d pressure
Instantaneous rise so that pressure is also increased in pressure feedback chamber e, so that the thrust produced on adjusting pressuring valve core 410 accordingly increases
Greatly, this thrust destroys the balance of original power so that adjusting pressuring valve core 410 moves right, and adjusting pressuring valve core 410 moves right and turned down
Oil suction chamber c, throttling action is increased so that is gone out the decline of oil pocket d output pressures, untill new balance is reached, is now gone out oil pocket
Output pressure be returned to original arranges value Pd substantially.If the output pressure for going out oil pocket d instantaneously declines, correspondingly pressure feedback
Chamber e pressure reduces and less than the spring force of pressure spring 48, pressure spring 48 promotes adjusting pressuring valve core 410 to move to left, and oil suction chamber c is opened
Greatly, throttling action reduces so that the output pressure for going out oil pocket d also returns to substantially original arranges value Pd.
Go out oil pocket d again to connect with oil inlet passage g, thus the pressure oil gone out in oil pocket d enters oil inlet passage g, it is logical through oil-feed
The solenoid directional control valve entered after road g in the D of asphalt channel duct；When 414 dead electricity of magnet coil, oil inlet passage g and oil circuit break-make
Inner chamber P3 is disconnected, and oil circuit break-make inner chamber P3 is connected with drainback passage T, after magnet coil 414 must be electric, produces electromagnetic force, Gu
Determine electromagnet 416 and hold Mobile electromagnetic iron 415, Mobile electromagnetic iron 415 drives reversing valve core 411 to move to left, oil circuit break-make inner chamber P3
Disconnected with drainback passage T, and oil inlet passage g is connected through third through-hole, hollow cavity, fourth hole and fuel-displaced duct A successively,
Fuel-displaced duct A pressure oil outputs；After 414 dead electricity again of magnet coil, electromagnetic force disappears, and under the thrust of back-moving spring 413, changes
Moved to right to valve element 411 so that oil inlet passage g and oil circuit break-make inner chamber P3 disconnects, oil circuit break-make inner chamber P3 and drainback passage T connects
Logical, the pressure in oil circuit break-make inner chamber P3 is zero.
Shuttle valve component, pressure adjusting part and solenoid directional control valve are concentrated on valve body 41 by the utility model aux. control valve 4
Interior, compact conformation is lightweight, and small volume is cost-effective, reduces pipeline space-consuming, reduces pipe joint quantity so that
Contact is few, and the risk leaked is reduced, lightweight, many advantages, such as conveniently maintenance is cost-effective.
The operation principle of the utility model control system：The pressure oil that the swash plate plunger pump 20 of hydraulic pump is exported is through first
Oil-out C1 and the second oil-out C2 are separately input into the first oil inlet A1 and the second oil inlet A2 of banked direction control valves 5, by banked direction control valves 5
Oil circuit is distributed to each executing agency, the action required for hydraulic crawler excavator is completed.Wherein hydraulic pump P1 the first oil-out C1
Pressure oil pressure and the first oil-feed duct P1 and first piston mouthful a1 on pressure it is equal, hydraulic pump P1 the second oil-out
Pressure oil pressure on C2 is equal with the pressure on the second oil-feed duct P2 and first piston mouthful a2.First oil-out C1 and
Two oil-out C2 are communicated by shuttle valve 202, when the first oil-out C1 has pressure oil or the first oil-out C1 into shuttle valve 202 to enter
The pressure for entering the pressure oil of shuttle valve 202 is more than the pressure that the second oil-out C2 enters the pressure oil of shuttle valve 202, now shuttle valve 202
Interior steel ball is moved to right, and pressure oil reaches the thrust piston 201 of swash plate plunger pump 20 all the way from point two-way after oil-out D1 outputs
Right-hand member, the valve element oil inlet a3 of another valve element 211 of road ingoing power adjuster 21.When the push-rod piston 210 of power governor 21 is produced
When raw power is less than the spring force Fa of spring 212 on the valve element 211 of power governor 21, i.e. during Pac+ (Pa1+Pa2)/2≤Fa, valve
Core 211 is moved to left, and the valve element oil-out a4 of valve element 211 is communicated with the left end of the thrust piston 201 of swash plate plunger pump 20, and thrust is lived
The pressure for filling in 201 left ends is zero, so that the pressure of the right-hand member of 20 thrust piston of swash plate plunger pump 201 is more than its left end, it is inclined disc type
The swash plate angle of plunger pump 20 reaches maximum, and now the discharge capacity of swash plate plunger pump 20 is maximum, and hydraulic pump moment of torsion and power are maximum.
When the power that the push-rod piston 210 of power governor 21 is produced is more than the spring force Fa of spring 212 on the valve element 211 of power governor 21
When, i.e. during Pac+ (Pa1+Pa2)/2≤Fa, valve element 211 is moved to right, valve element oil inlet a3 and the valve element oil-out a4 phases of valve element 211
It is logical so that the pressure of the left end of 20 thrust piston of swash plate plunger pump 201 and right-hand member is equal, but due to a left side for swash plate plunger pump 20
End cross-sectional area is more than its right-hand member sectional area, therefore the left end thrust of swash plate plunger pump 20 is more than its right-hand member thrust, inclined disc type post
The plug thrust piston 201 of pump 20, which is moved to right, promotes the swash plate angle of swash plate plunger pump 20 to reduce so that the row of swash plate plunger pump 20
Amount is also corresponding to be reduced, that is, corresponds to hydraulic pump moment of torsion and power is reduced, and the power resources of hydraulic pump are in engine 1, therefore this reality
The output torque of Dynamic Matching engine 1 is realized with new, to improve hydraulic pressure pump power, realization makes full use of engine power,
Improve hydraulic crawler excavator operating efficiency.
Specifically, as shown in figure 23, curve a is the Power Control of hydraulic pump when control system does not increase aux. control valve 4
Curve, power is 43.1KW, and Power Control flex point abscissa is 10.8MPa, as the ＞ 10.8MPa of (Pa1+Pa2)/2, hydraulic pump
Discharge capacity reduces so that hydraulic pump actual power is not more than power settings 47.5KW, i.e. 47.5KW and is less than the work(of engine 1 all the time
Rate, from power and torque relationship and from stress balance reality, we require that hydraulic pump moment of torsion is less than the moment of torsion of engine 1,
The output torque reduction in the slow-speed of revolution of engine 1 is obvious, and hydraulic pump input torque is not influenceed by rotating speed substantially.Therefore hydraulic pump
Power settings need to be set according to the torque value of the slow-speed of revolution of engine 1, but so, turned round when engine 1 is maximum
When square is improved and improved with rotating speed, the moment of torsion of hydraulic pump is not improved and then, causes the actual torque of engine 1 also not carry
Height, limits the performance of the power of engine 1.
According to above-mentioned, the utility model adds aux. control valve 4 while improving hydraulic pressure pump power limit in control system
Value processed, is 7.5KW, F by hydraulic pump power limit arranges valuea=14.1MPa, is represented with curve b.Swash plate plunger pump 20
First oil-out C1 and the second oil-out C2 meet the first oil-feed duct P1 and the second oil-feed duct P2 of aux. control valve 4 respectively,
After aux. control valve 4, finally from the pressure oil that fuel-displaced duct A output pressures value is Pd, wherein Pd=3.6MPa, pressure oil enters
Enter the oil circuit break-make area of aux. control valve 4, when the rotating speed of engine 1 less than 1600rpm or engine 1 falls speed >=11%
When, controller gives the electric signal of aux. control valve 4, and solenoid directional control valve commutation, magnet coil 414 obtains electric, fuel-displaced duct A output pressures
Oil arrives the 3rd piston mouthful ac of power governor 21, because the pressure adjustment formula of power governor 21 is：Pac+(Pa1+
Pa2)/2≤Fa, because Pac=Pd=3.6MPa, Pa=14.1MPa, therefore (Pa1+Pa2)/2=10.5MPa, is no better than
Flex point pressure 10.8MPa before hydraulic pump, and it is 4.1KW that hydraulic pump actual power, which is curve a power, therefore engine 1 can be held
Carry on a shoulder pole the load of hydraulic pump.When the rotating speed of engine 1 is higher than 1600rpm or when falling speed less than 11% of engine 1, auxiliary control
The dead electricity of magnet coil 414 of valve 4 processed, solenoid directional control valve closes oil circuit, and the pressure oil of fuel-displaced duct A outputs is zero, Pac=Pd=
0MPa, (Pa1+Pa2)/2≤14.1MPa is obtained from Pac+ (Pa1+Pa2)/2≤Fa, and hydraulic pump peak power can reach curve b
Power 47.5KW, therefore the power output of hydraulic crawler excavator brings up to 47.5KW by 43.1KW before, improves 10% or so,
So as to prove that the utility model is applied on hydraulic crawler excavator, the power utilization of engine 1 of whole machine can be improved, whole machine work is improved
Make efficiency.
The utility model controls hydraulic pump by aux. control valve 4, the power limit of hydraulic pump is improved, when engine 1
Under slow-speed of revolution low torque, the control hydraulic pump reduction hydraulic pump input torque of aux. control valve 4, high rotating speed is big in engine 1
Under moment of torsion, output torque has more than needed, and the control hydraulic pump of aux. control valve 4 improves hydraulic pump input torque, due to having carried before
The high power limit of press pump, now press pump will obtain than higher before power and moment of torsion.So that engine 1 is in small-sized digging
Its energy is played on pick machine to a greater extent, pressure excavator operation efficiency is significantly improved.
General principle of the present utility model, principal character and advantage of the present utility model has been shown and described above.One's own profession
The technical staff of industry is it should be appreciated that the utility model is not restricted to the described embodiments, described in above-described embodiment and specification
Simply illustrate principle of the present utility model, the utility model can also on the premise of the utility model spirit and scope are not departed from
There are various changes and modifications, these changes and improvements are both fallen within the range of claimed the utility model.The utility model will
Protection domain is asked to be defined by appending claims and its equivalent.
Claims (10)
1. a kind of power control system of hydraulic excavator, it is characterised in that including engine (1), hydraulic pump, aux. control valve
(4) and banked direction control valves (5), the hydraulic pump includes swash plate plunger pump (20) and power governor (21)；The engine (1)
Output shaft is connected by shaft coupling with the input shaft of the swash plate plunger pump (20)；The pump of the swash plate plunger pump (20)
Inlet port (B1) and drain tap (Dr1) are connected with the first fuel tank (3)；The power governor (21) includes push-rod piston
(210), the spring (212) on valve element (211) and valve element (211)；
The first oil-out (C1) of the swash plate plunger pump (20) the first oil inlet (A1) respectively with the banked direction control valves (5),
First oil-feed duct (P1) of aux. control valve (4) is connected with the first piston mouthful (a1) of thrust piston (210)；The swash plate
The second oil-out (C2) of formula plunger pump (20) the second oil inlet (A2) respectively with the banked direction control valves (5), aux. control valve (4)
The second piston mouthful (a2) of the second oil-feed duct (P2) and thrust piston (210) be connected；
First oil-out (C1) is connected with the second oil-out (C2) by shuttle valve (202), the shuttle valve (202) it is fuel-displaced
Mouthful (D1) respectively with the valve element oil inlet (a3) of the valve element (211) and swash plate plunger pump (20) lifting force piston (201)
Right-hand member is connected；The valve element oil-out (a4) of the valve element (211) and the swash plate plunger pump (20) lifting force piston (201)
Left end be connected；
The fuel-displaced duct (A) of the aux. control valve (4) is connected with the 3rd piston mouthful (ac) of the push-rod piston (210)；
The oil return duct (T) of the aux. control valve (4) is connected with the second fuel tank (6)；
The pressure adjustment formula of the power governor (21) is：Pac+ (Pa1+Pa2)/2≤Fa, wherein Pac are the 3rd work
The pressure of mouth (ac) is filled in, Pa1 is the pressure of first piston mouthful (a1), and Pa2 is the pressure of second piston mouthful (a2), and Fa is valve element
(211) spring force of spring (212) on.
2. a kind of power control system of hydraulic excavator according to claim 1, it is characterised in that the aux. control valve
(4) valve body (41), shuttle valve component and pressure adjusting part are included, the valve body (41) includes the function being made up of internal gutter
Area, the functional areas include oil-feed area, pressure regulatory region and oil circuit break-make area；
The oil-feed area includes the first oil-feed duct (P1), the second oil-feed duct (P2), busway (B) and oil discharge passage
(b), the first oil-feed duct (P1), the second oil-feed duct (P2) are connected with the busway (B), the busway
(B) it is connected with the oil discharge passage (b)；
The shuttle valve component includes shuttle valve spool (42), steel ball (44) and positioning joint (45), shuttle valve spool (42) center
It is sequentially communicated from left to right and is provided with oil-feed unthreaded hole, inner chamber and internal thread hole, the left side of the inner chamber is in smooth cone structure, institute
State circumference uniform distribution on the face of cylinder of inner chamber and be provided with multiple first through hole, the steel ball (44) is located at the shuttle valve spool (42)
At inner chamber；The left end of the positioning joint (45) is provided with left outside screw thread, is provided centrally with turning on the positioning joint (45) two
The endoporus at end, the left end aperture of positioning joint (45) endoporus is in smooth cone structure, and the positioning joint (45) passes through institute
At the internal thread hole for stating left outside screw thread connection and the shuttle valve spool (42)；The oil-feed unthreaded hole of the shuttle valve spool (42)
The internal diameter of the endoporus of internal diameter and positioning joint (45) is respectively less than the diameter of the steel ball (44)；
The shuttle valve component is installed in the busway (B), the oil-feed unthreaded hole and described first of the shuttle valve spool (42)
(P1) is connected in oil-feed duct, and the endoporus of the positioning joint (45) is connected with the second oil-feed duct (P2), the shuttle
First through hole on valve core (42) inner chamber face of cylinder connects the inner chamber and the fuel-displaced duct (b)；
The pressure regulatory region includes pressure regulating hole road (C), valve body described in the two ends insertion of the pressure regulating hole road (C)
(41) the pressure adjusting part, the pressure regulation are installed in left surface and right flank, the pressure regulating hole road (C)
Component includes valve element spacer (47), regulation spring (48), adjusting pressuring valve core (410) and the first plug (417), the pressure regulating hole
The left end and right-hand member in road (C) are blocked by first plug (417) and valve element spacer (47) respectively；
The left end of the pressure spring (48) withstands the right-hand member of the adjusting pressuring valve core (410), the right-hand member of the pressure spring (48)
The valve element spacer (47) is withstood, the left end of the adjusting pressuring valve core (410) withstands first plug (417)；The pressure regulator valve
The inner surface of the face of cylinder of core (410) and the pressure regulating hole road (C) is formed with oil suction chamber (c) and goes out oil pocket (d), it is described enter
Oil pocket (c) with it is described go out oil pocket (d) be connected, the oil suction chamber (c) is connected (b) with the fuel-displaced duct；
The adjusting pressuring valve core (410) has oil through by left end center is axially disposed, and the aperture of the oil through is in the smooth conical surface
Circumference uniform distribution is provided with multiple second through holes on structure, the face of cylinder of the adjusting pressuring valve core (410), and second through hole connects institute
State oil through and pressure regulating hole road (C)；
The oil circuit break-make area includes oil inlet passage (g), oil circuit break-make duct (D), fuel-displaced duct (A) and drainback passage (T), institute
State oil inlet passage (g) with it is described go out oil pocket (d) be connected, the oil inlet passage (g) is connected with the oil circuit break-make duct (D)
It is logical；Oil circuit break-make duct (D) place is provided with solenoid directional control valve, the solenoid directional control valve and the oil circuit break-make duct (D)
Formed oil circuit break-make inner chamber (P3)；During the solenoid directional control valve dead electricity, the oil inlet passage (g) and the oil circuit break-make inner chamber
(P3) disconnect, the oil circuit break-make inner chamber (P3) is connected with the drainback passage (T)；When the solenoid directional control valve obtains electric, institute
State oil inlet passage (g) with the oil circuit break-make inner chamber (P3) to be connected, the oil circuit break-make inner chamber (P3) and the drainback passage
(T) disconnect, the oil circuit break-make inner chamber (P3) is connected with the fuel-displaced duct (A).
3. a kind of power control system of hydraulic excavator according to claim 2, it is characterised in that the oil-feed area is also wrapped
Include the first pressure measurement duct (M1) and the second pressure measurement duct (M2), the first pressure measurement duct (M1) and the first oil-feed duct
(P1) it is connected, the second pressure measurement duct (M2) is connected with the second oil-feed duct (P2)；
The oil-feed area also includes the first technique duct (a), and the first technique duct (a) is connected with the busway (B)
Logical, the center line in the first technique duct (a) and the center line of the fuel-displaced duct (b) are on the same line, described
The first expanded spheres (43) are installed in first technique duct (a).
4. a kind of power control system of hydraulic excavator according to claim 2, it is characterised in that the positioning joint
(45) right-hand member is provided with right external screw thread, and the inner surface setting of the busway (B) has internal thread, the positioning joint (45)
The internal thread screw thread of right external screw thread and the busway (B) coordinate；The right-hand member of the positioning joint (45) is provided with interior six
Angle endoporus；The right flank of valve body (41) described in the right-hand member insertion of the busway (B)；The shuttle valve component also includes second and blocked up
Head (46), the right-hand member of the busway (B) is blocked by second plug (46).
5. a kind of power control system of hydraulic excavator according to claim 1, it is characterised in that the shuttle valve spool
(42) face of cylinder of left end is provided with annular groove, the annular groove and is provided with seal assembly, and the seal assembly is by two
The first O-ring seal of folder (424) composition in the middle of back-up ring (423).
6. a kind of power control system of hydraulic excavator according to claim 2, it is characterised in that the pressure regulating hole
The left end inner surface setting in road (C) has left end internal thread, and right-hand member inner surface setting has right-hand member internal thread；First plug
(417) external screw thread, the external screw thread of first plug (417) and spiral shell in the left end of the pressure regulating hole road (C) are provided with
Line is threadedly coupled；External screw thread, external screw thread and the pressure of the valve element spacer (47) are provided with the valve element spacer (47)
Adjust the right-hand member internal thread threaded connection of duct (C)；Pass through between the valve element spacer (47) and the pressure regulating hole road (C)
Second O-ring seal (420) is sealed；
Cylindrical hole is provided with the valve element spacer (47), the right-hand member of the adjusting pressuring valve core (410) is provided with step, the step
Place is provided with spring washer (49)；The left end of the pressure spring (48) withstands the spring washer (49), and right-hand member is installed on institute
State in the cylindrical hole of valve element spacer (47) and withstand the cylindrical hole bottom hole.
7. a kind of power control system of hydraulic excavator according to claim 2, it is characterised in that the adjusting pressuring valve core
(410) the first gradual change type groove is provided with the face of cylinder of left end, the face of cylinder of the adjusting pressuring valve core (410) passes through described first
Form oil film between the inner surface in gradual change type groove and the pressure regulating hole road (C).
8. a kind of power control system of hydraulic excavator according to claim 1, it is characterised in that the pressure regulatory region
Also include the first connected pore channel (k) and the second connected pore channel (h), it is described go out oil pocket (d) by first connected pore channel (k) with
Second connected pore channel (h) is connected, and second connected pore channel (h) is connected with the oil inlet passage (g)；
The pressure regulatory region also includes the second technique duct (n) and the 3rd technique duct (i), the second technique duct (n)
Center line and the center line of first connected pore channel (k) it is on the same line, pacify in the second technique duct (n)
Equipped with the second expanded spheres (421)；The center line in the 3rd technique duct (i) and the center line of second connected pore channel (h)
It is on the same line, the 3rd expanded spheres (422) are installed in the 3rd technique duct (i).
9. a kind of power control system of hydraulic excavator according to claim 2, it is characterised in that the solenoid directional control valve
Including reversing valve core (411), fixed spool (412), back-moving spring (413), fixed electromagnet (416), Mobile electromagnetic iron (415)
With magnet coil (414)；The reversing valve core (411) is installed in the oil circuit break-make duct (D), the reversing valve core
(411) outer surface and the inner surface of the oil circuit break-make duct (D) form the oil circuit break-make inner chamber (P3)；
Fixed electromagnet (416) and Mobile electromagnetic iron (415) described in magnet coil (414) inner sleeve；The back-moving spring
(413) it is installed in the Mobile electromagnetic iron (415), the two ends of the back-moving spring (413) are respectively against the Motionless electromagnetic
Iron (416) and Mobile electromagnetic iron (415)；The Mobile electromagnetic iron (415) is connected with the left end of the reversing valve core (411),
The right-hand member of the reversing valve core (411) is provided with piston；The reversing valve core (411) is installed on the fixed spool (412)
In endoporus and it can be horizontally slipped relative to the fixed spool (412)；The outer surface of the reversing valve core (411) and the fixation
Set respectively in uniform way on the inner surface formation hollow cavity of valve element (412), two circumference of the fixed spool (412) vertically
There are multiple third through-holes and fourth hole, the third through-hole is connected with the oil inlet passage (g), the fourth hole connection
The oil circuit break-make inner chamber (P3) and hollow cavity；
During the solenoid directional control valve dead electricity, the oil circuit break-make inner chamber (P3) is successively through the fourth hole, hollow cavity, fixation
Gap between the right side of valve element (412) and the left side of reversing valve core (411) piston is connected with the drainback passage (T)
It is logical；
When the solenoid directional control valve obtains electric, the oil inlet passage (g) is successively through the third through-hole, hollow cavity, fourth hole
It is connected with the fuel-displaced duct (A)；
It is provided with the outer surface of reversing valve core (411) left end outside the second gradual change type groove, the reversing valve core (411)
Form oil film between the inner surface that surface passes through the second gradual change type groove and the fixed spool (412).
10. a kind of power control system of hydraulic excavator according to claim 2, it is characterised in that the oil circuit break-make
Area also includes the 4th technique duct (j), the center line in the 4th technique duct (j) and the center line of the oil inlet passage (g)
It is on the same line, the 4th expanded spheres (418) are installed in the 4th technique duct (j)；
The oil circuit break-make area also includes the 5th technique duct (m), the 5th technique duct (m) and the drainback passage (T)
It is connected, the 5th expanded spheres (419) is installed in the 5th technique duct (m)；
The oil circuit break-make area also includes the 3rd pressure measurement duct (M3), the 3rd pressure measurement duct (M3) and the fuel-displaced duct
(A) it is connected.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201621443167.6U CN206338265U (en) | 2016-12-27 | 2016-12-27 | A kind of power control system of hydraulic excavator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201621443167.6U CN206338265U (en) | 2016-12-27 | 2016-12-27 | A kind of power control system of hydraulic excavator |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN206338265U true CN206338265U (en) | 2017-07-18 |
Family
ID=59302636
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201621443167.6U Withdrawn - After Issue CN206338265U (en) | 2016-12-27 | 2016-12-27 | A kind of power control system of hydraulic excavator |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN206338265U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106499681A (en) * | 2016-12-27 | 2017-03-15 | 恒天九五重工有限公司 | A kind of power control system of hydraulic excavator |
| CN112747239A (en) * | 2021-01-06 | 2021-05-04 | 中国铁建重工集团股份有限公司 | Automatic lubricating system |
-
2016
- 2016-12-27 CN CN201621443167.6U patent/CN206338265U/en not_active Withdrawn - After Issue
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106499681A (en) * | 2016-12-27 | 2017-03-15 | 恒天九五重工有限公司 | A kind of power control system of hydraulic excavator |
| CN106499681B (en) * | 2016-12-27 | 2017-12-29 | 恒天九五重工有限公司 | A kind of power control system of hydraulic excavator |
| CN112747239A (en) * | 2021-01-06 | 2021-05-04 | 中国铁建重工集团股份有限公司 | Automatic lubricating system |
| CN112747239B (en) * | 2021-01-06 | 2022-03-01 | 中国铁建重工集团股份有限公司 | Automatic lubricating system |
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| GR01 | Patent grant | ||
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| AV01 | Patent right actively abandoned |
Granted publication date: 20170718 Effective date of abandoning: 20171229 |