CN202787369U - Hydraumatic excavating energy saving system - Google Patents

Abstract

The utility model discloses a hydraulic excavation energy-saving system, which comprises a boom driving oil cylinder and a boarding mechanism, and also includes an oil-electric-hydraulic hybrid driving system, a hydraulic energy accumulator control unit, a boom driving oil cylinder hydraulic control unit, and a hydraulic system of the boarding mechanism. control unit, the first one-way valve, the second one-way valve, the third one-way valve, the first hydraulic accumulator and the second hydraulic accumulator, the utility model integrates the oil-electric hybrid power system and The advantages of the hydraulic hybrid power system can meet the load's requirements for high power density and high energy density at the same time. In terms of energy recovery and reuse, the principle of minimum energy conversion is followed, and the power system and energy recovery system share hydraulic accumulators and The storage battery, by this, can not only improve the working efficiency of the engine, but also reduce the energy loss in the energy recovery system, without affecting the stable operation of the engine.

Description

A kind of hydraulic excavating energy conserving system

Technical field

The utility model relates to the drive system art, refers in particular to a kind of hydraulic excavating energy conserving system based on oily electrohydraulic mixed power and Energy Recovery Technology.

Background technology

One of most important engineering machinery machine that hydraulic crawler excavator is built as national basis has been widely used in building, traffic, and water conservancy is in mine and the military field.The energy-saving and emission-reduction of hydraulic crawler excavator have caused people's extensive concern and attention.Motor and hydraulic system inefficiency are the not high main causes of capacity usage ratio of hydraulic crawler excavator, so the energy-conservation research of dynamical system and hydraulic system is the research emphasis of hydraulic crawler excavator always.

The operating mode of hydraulic crawler excavator is complicated, and load variations is violent, and Technology of Hybrid Electric Vehicle is one of preferred plan that improves the dynamical system energy-saving effect.Hybrid power generally is divided into electric weight storage element (battery or electric capacity) as the oily electric hybrid technology of energy-storage travelling wave tube with the hydraulic hybrid technology of hydraulic accumulator as energy-storage travelling wave tube.The energy density of battery is high, but its power density is lower, and it is little to discharge and recharge frequency, can not transform rapidly to absorb a large amount of power.Super capacitor has long, the characteristics such as release current power is large of life-span, and in addition, hydraulic accumulator has the advantages that cost is low, the life-span is long, but the energy density of accumulator is very low, and accumulator is compared the finite energy of storage with the battery of formed objects.Therefore, current single oil electricity mixes and hydraulic hybrid has his own strong points between the two, the requirement of very difficult simultaneously high power density and high-energy-density.

At present, conventional movable arm potential energy recovery scheme mainly launches based on the oil electric mixed dynamic hydraulic crawler excavator.The oil back chamber that swing arm drives hydraulic cylinder links to each other with hydraulic motor, and this hydraulic motor links to each other with generator coaxle.The hydraulic oil that swing arm drives the oil cylinder oil back chamber drives the hydraulic motor revolution, is mechanical energy output with hydraulic energy transfer, and drives the generator generating, and threephase AC electric energy is direct current energy and is stored in the middle of the energy-storage travelling wave tube through the frequency converter rectification.When system needed, direct current energy was reverse into the threephase AC electric energy drive motor of target frequency by rectifier, jointly drives loaded work piece with motor.All movable arm potential energy recyclings are all passed through from the multiple energy conversion of the mechanical energy of potential energy-hydraulic energy-mechanical energy-electric energy-electric capacity-driving variable pump in this technical scheme, and the power conversion link is more in the system, has affected the energy recovery efficiency of system.

In like manner, conventional upper mechanism of car rotary braking energy recovery scheme also mainly launches based on the oil electric mixed dynamic hydraulic crawler excavator.System mainly adopts Motor Drive to substitute conventional hydraulic motors and drives upper mechanism of car, utilize motor two, a large amount of kinetic transformations of discharging during rotary braking of four-quadrant operation become electrical power storage in battery or electric capacity.Electric weight storage element in the system is the energy-storage travelling wave tube for recovering energy both, also is the dc source of motor in the hybrid electric drive system simultaneously.All braking recover kinetic energy recyclings repeatedly transform through energy in this technical scheme, and the power conversion link is more in the system, has affected the energy recovery efficiency of system.

The utility model content

In view of this, the utility model is for the disappearance of prior art existence, and its main purpose provides a kind of hydraulic excavating energy conserving system, can improve engine operation efficient, can reduce again the energy consumption loss in the energy-recuperation system, not affect the steady operation of motor simultaneously.

In order to achieve the above object, the technical solution adopted in the utility model is:

A kind of hydraulic excavating energy conserving system, it comprises that swing arm drives oil cylinder (17) and upper mechanism of car (34), comprises that also oily electric liquid hybrid drive system (100), hydraulic accumulator control module (200), swing arm drive oil cylinder hydraulic control module (300), the organization hydraulic pressure control module (400) of getting on the bus, the first one way valve (11), the second one way valve (13), the 3rd one way valve (14), the first hydraulic accumulator (24) and the second hydraulic accumulator (26);

The electric liquid hybrid drive system 100 of described oil comprises motor (3), dynamoelectric machine (4) and variable displacement motor (5), the first variable pump (6) and the second variable pump (7) that connects with axis mechanical drive;

Described hydraulic accumulator control module 200 comprises the first solenoid operated directional valve (15), the second solenoid operated directional valve (22), the 3rd solenoid operated directional valve (23), the 4th solenoid operated directional valve (25); Aforementioned the first hydraulic accumulator (24) meets the 3rd solenoid operated directional valve (23) hydraulic fluid port B, the hydraulic fluid port A of the 3rd solenoid operated directional valve (23) is divided into three the tunnel: the first via meets the hydraulic fluid port A of the first solenoid operated directional valve (15), the second the tunnel meets the hydraulic fluid port B of the 3rd one way valve (14), and Third Road meets the hydraulic fluid port B of the second solenoid operated directional valve (22); The second hydraulic accumulator (26) meets the hydraulic fluid port B of the 4th solenoid operated directional valve (25); The hydraulic fluid port A of this second solenoid operated directional valve (22) meets the hydraulic fluid port B of the second one way valve (13); The hydraulic fluid port A of the 4th solenoid operated directional valve (25) divides two-way: the first via meets the hydraulic fluid port B of the first solenoid operated directional valve (15), and the second the tunnel connects the oil-in of variable displacement motor (5);

Described swing arm drives oil cylinder hydraulic control module 300 and comprises the first proportional throttle valve (18), the second proportional throttle valve (19), the 3rd proportional throttle valve (20), the 4th proportional throttle valve (21), the hydraulic fluid port that described swing arm drives the rod chamber of oil cylinder (17) is divided into two-way: the first via meets the hydraulic fluid port B of the 3rd proportional throttle valve (20), and the second the tunnel meets the hydraulic fluid port A of the 4th proportioning valve (21); And the hydraulic fluid port that this swing arm drives the rodless cavity of oil cylinder (17) is divided into three the tunnel: the first via meets the hydraulic fluid port B of the first proportional throttle valve (18), the second the tunnel meets the hydraulic fluid port A of the second proportional throttle valve (19), and Third Road meets the hydraulic fluid port A of the 3rd one way valve (14); The hydraulic fluid port B connected tank of the hydraulic fluid port B of this second proportional throttle valve (19) and the 4th proportional throttle valve (21); The hydraulic fluid port A of the hydraulic fluid port A of this first proportional throttle valve (18) and the 3rd proportional throttle valve (20) meets the hydraulic fluid port A of the second solenoid operated directional valve (22);

The described organization hydraulic pressure control module 400 of getting on the bus comprises hydraulic control proportional direction valve (16), the first hydraulic control one-way valve (27), the second hydraulic control one-way valve (28), automatically controlled proportional reversing valve (29), the 4th one way valve (30), the 5th one way valve (31) and hydraulic motor (32), this hydraulic motor (32) connects aforementioned upper mechanism of car (34), the hydraulic fluid port P of this hydraulic control proportional direction valve (16) links to each other with the hydraulic fluid port B of the first one way valve (11), the hydraulic fluid port T of hydraulic control proportional direction valve (16) links to each other with fuel tank, the hydraulic fluid port A of hydraulic control proportional direction valve (16) divides three the tunnel: the first via meets the hydraulic fluid port A of the first hydraulic control one-way valve (27), the second the tunnel meets the hydraulic fluid port B of the 4th one way valve (30), and Third Road meets the hydraulic fluid port A of hydraulic motor (32); The hydraulic fluid port B of this hydraulic control proportional direction valve (16) also divides three the tunnel: the first via meets the hydraulic fluid port A of the second hydraulic control one-way valve (28), and the second the tunnel meets the hydraulic fluid port B of the 5th one way valve (31), and Third Road meets the hydraulic fluid port B of hydraulic motor (32); The hydraulic fluid port B of this first hydraulic control one-way valve (27) and the second hydraulic control one-way valve (28) links to each other with the hydraulic fluid port A of automatically controlled proportional direction valve (29), the hydraulic fluid port T connected tank of automatically controlled proportional direction valve (29), the hydraulic fluid port P of automatically controlled proportional direction valve (29) meets the hydraulic fluid port A of the 4th solenoid operated directional valve (25); The hydraulic fluid port A connected tank of the hydraulic fluid port A of the 4th one way valve (30) and the 5th one way valve (31); The control port K of the first hydraulic control one-way valve (27) links to each other with the control port K1 of hydraulic control proportional direction valve (16), and the control port K of the second hydraulic control one-way valve (28) links to each other with the control port K2 of hydraulic control proportional direction valve (16);

The outlet of described the first variable pump (6) meets the hydraulic fluid port A of the second one way valve (13); The outlet of described the second variable pump (7) meets the hydraulic fluid port A of the first one way valve (11).

Preferably, the pressure rating of described the first hydraulic accumulator (24) drives oil cylinder (17) needed pressure rating when stretching out less than swing arm, and the pressure rating of the second hydraulic accumulator (26) drives oil cylinder (17) needed pressure rating when stretching out greater than swing arm.

Preferably, further comprise shuttle valve (9) and safety valve (10), the hydraulic fluid port A1 of this shuttle valve (9) connects the oil-out of variable pump (6), the hydraulic fluid port A2 of shuttle valve (9) connects the oil-out of variable pump (7), the hydraulic fluid port B of shuttle valve (9) connects the import of safety valve (10), the outlet connected tank of safety valve (10).

Preferably, the control port K1 of described hydraulic control proportional direction valve (16) links to each other with conventional hydraulic excavator pilot control oil circuit respectively with control port K2.

Preferably, connection reducer (33) between described hydraulic motor (32) and the upper mechanism of car (34).

Preferably, further comprise scraper bowl fluid power system (8), the oil-out of this scraper bowl fluid power system (8) link variable pump (6).

Preferably, further comprise dipper fluid power system (12), the oil-out of this dipper fluid power system (12) link variable pump (7).

Preferably, described dynamoelectric machine (4) is electrically connected battery (2) by frequency converter (1), and this frequency converter (1) and dynamoelectric machine (4) are permasyn morot and electric machine controller.

Preferably, described variable displacement motor (5) and variable pump (6,7) are automatically controlled variable displacement motor and variable pump with displacement electricity feedback.

Preferably, described the first solenoid operated directional valve to the four solenoid operated directional valves (15,22,23,25) are by the two-way plug-in valve of solenoid operated directional valve as pilot stage.

The utility model compared with prior art has obvious advantage and beneficial effect, particularly, and as shown from the above technical solution:

1, dynamical system of the present utility model is oily electric liquid hybrid drive system, dynamical system both can be operated in oily electric combination drive pattern, the large advantage of performance storage battery energy density, the main comparatively mild operating mode of equilibrium fluctuations of being responsible for, can be operated in the hydraulic hybrid drive pattern again, utilize the large characteristics of hydraulic accumulator power density, satisfy the powerful requirement of load instantaneous.Therefore, the design of oily electric hybrid drive system no longer designs according to maximum load fluctuating power in the former hydraulic pressure excavator operating mode, so that the power grade of dynamoelectric machine and battery reduces greatly.

2, aspect the energy recovery, the utility model has been followed Conversion of Energy link minimum principle, has avoided energy repeatedly to transform the energy loss that causes.When the swing arm of excavator was transferred, the part hydraulic oil that swing arm drives the rodless cavity of oil cylinder can directly flow to the rod chamber that swing arm drives oil cylinder, realizes the flow regeneration function.Portion of energy changes into hydraulic energy by the first hydraulic accumulator (low pressure accumulator) and stores.When upper mechanism of car rotary braking, the hydraulic control proportional direction valve is in meta, hydraulic motor is because inertia continues rotation, produce high pressure in brake chamber one side, oil-filled to the second hydraulic accumulator (high pressure accumulator) by the hydraulic control one-way valve of correspondence, automatically controlled proportional direction valve, solenoid operated directional valve, realize the energy removal process.

3, aspect the recycling of energy, the utility model has been followed Conversion of Energy link minimum principle equally.The energy of the second hydraulic accumulator (high pressure accumulator) both can directly directly drive the mechanism of car revolution by automatically controlled proportional direction valve and hydraulic control one-way valve and accelerate, and can merge together by the oil-out pressure of the 4th solenoid operated directional valve, the 3rd solenoid operated directional valve and variable pump again the rising or the decline that realize swing arm by the first or second proportional throttle valve.The hydraulic oil of the second hydraulic accumulator (high pressure accumulator) and the first hydraulic accumulator (low pressure accumulator) can directly drive variable pump by variable displacement motor according to the needs of dynamical system and change into mechanical energy simultaneously, and unnecessary energy changes into electric energy by the dynamoelectric machine of variable displacement motor driving power system.

4, dynamical system and energy-recuperation system share a cover key element, relatively traditional oily electric hybrid drive train that is aided with energy-recuperation system hydraulic hybrid drive system of unifying, reduced the power grade of the key elements such as dynamoelectric machine and battery, reduce simultaneously the installation volume of hydraulic accumulator, on function, but realized the several functions such as oil electric mixed dynamic, hydraulic hybrid, movable arm potential energy recovery and the recovery of rotary braking energy.

For more clearly setting forth architectural feature of the present utility model and effect, come the utility model is elaborated below in conjunction with accompanying drawing and specific embodiment.

Description of drawings

Fig. 1 is the overall structure block diagram of the preferred embodiment of the utility model.

The accompanying drawing identifier declaration:

100, oily electric liquid hybrid drive system

200, hydraulic accumulator control module

300, swing arm drives the oil cylinder hydraulic control module

400, the organization hydraulic pressure control module of getting on the bus

1, frequency converter 2, battery

3, motor 4, dynamoelectric machine

5, variable displacement motor 6, the first variable pump

7, the second variable pump 8, scraper bowl fluid power system

9, shuttle valve 10, safety valve

11, the first one way valve 12, dipper fluid power system

13, the second one way valve 14, the 3rd one way valve

15, the first solenoid operated directional valve 16, hydraulic control proportional direction valve

17, swing arm drives oil cylinder 18, the first proportional throttle valve

19, the second proportional throttle valve 20, the 3rd proportional throttle valve

21, the 4th proportional throttle valve 22, the second solenoid operated directional valve

23, the 3rd solenoid operated directional valve 24, the first hydraulic accumulator

25, the 4th solenoid operated directional valve 26, the second hydraulic accumulator

27, the first hydraulic control one-way valve 28, the second hydraulic control one-way valve

29, automatically controlled proportional direction valve 30, the 4th one way valve

31, the 5th one way valve 32, hydraulic motor

33, reducer 34, upper mechanism of car.

The specific embodiment

Please refer to shown in the accompanying drawing 1, it has demonstrated the concrete structure of the preferred embodiment of the utility model, it comprises that swing arm drives oil cylinder 17 and upper mechanism of car 34, also comprises oily electric liquid hybrid drive system 100, hydraulic accumulator control module 200, swing arm drives oil cylinder hydraulic control module 300, the organization hydraulic pressure control module 400 of getting on the bus, frequency converter 1, battery 2, the first one way valve 11, the second one way valve 13, the 3rd one way valve 14, shuttle valve 9, safety valve 10, scraper bowl fluid power system 8, dipper fluid power system 12, the first hydraulic accumulator 24, the second hydraulic accumulator 26 and mechanical connection are at the reducer 33 of upper mechanism of car 34.

Particularly, the interconnected relationship of each building block is as follows:

The electric liquid hybrid drive system 100 of described oil comprises motor 3, dynamoelectric machine 4 and variable displacement motor 5, the first variable pump 6 and the second variable pump 7 that connects with axis mechanical drive, this dynamoelectric machine 4 is electrical connected by frequency converter 1 and battery 2, and this variable displacement motor 5 links to each other with the oil circuit of the first hydraulic accumulator 24, the second hydraulic accumulator 26 by hydraulic accumulator control module 15,22,23,25;

Described hydraulic accumulator control module 200 comprises the first solenoid operated directional valve 15, the second solenoid operated directional valve 22, the 3rd solenoid operated directional valve 23, the 4th solenoid operated directional valve 25.The first hydraulic accumulator 24 meets the 3rd solenoid operated directional valve 23 hydraulic fluid port B, and the hydraulic fluid port A of the 3rd solenoid operated directional valve 23 is divided into three the tunnel: the first via meets the hydraulic fluid port A of the first solenoid operated directional valve 15; The second the tunnel meets the hydraulic fluid port B of the 3rd one way valve 14; Third Road meets the hydraulic fluid port B of the second solenoid operated directional valve 22; The second hydraulic accumulator 26 meets the hydraulic fluid port B of the 4th solenoid operated directional valve 25, and the hydraulic fluid port A of the 4th solenoid operated directional valve 25 is divided into three the tunnel: the first via meets the hydraulic fluid port B of the first solenoid operated directional valve 15; The second the tunnel connects the oil-in of variable displacement motor 5; Third Road meets the hydraulic fluid port P of following automatically controlled proportional direction valve 29, and the hydraulic fluid port A of the second solenoid operated directional valve 22 divides three the tunnel: the first via meets the hydraulic fluid port B of the second one way valve 13; The second the tunnel meets the hydraulic fluid port A of following the first proportional throttle valve 18; Third Road meets the hydraulic fluid port A of following the 3rd proportional throttle valve 20.

Described swing arm drives oil cylinder hydraulic control module 300 and comprises the first proportional throttle valve 18, the second proportional throttle valve 19, the 3rd proportional throttle valve 20, the 4th proportional throttle valve 21, the hydraulic fluid port that described swing arm drives the rod chamber of oil cylinder 17 is divided into two-way: the first via meets the hydraulic fluid port B of the 3rd proportional throttle valve 20, and the second the tunnel meets the hydraulic fluid port A of the 4th proportioning valve 21; And the hydraulic fluid port that this swing arm drives the rodless cavity of oil cylinder 17 is divided into three the tunnel: the first via meets the hydraulic fluid port B of the first proportional throttle valve 18; The second the tunnel meets the hydraulic fluid port A of the second proportional throttle valve 19; Third Road meets the hydraulic fluid port A of the 3rd one way valve 14, the hydraulic fluid port B connected tank of the hydraulic fluid port B of the second proportional throttle valve 19 and the 4th proportional throttle valve 21.

The described organization hydraulic pressure control module 400 of getting on the bus comprises hydraulic control proportional direction valve 16, the first hydraulic control one-way valve 27, the second hydraulic control one-way valve 28, automatically controlled proportional reversing valve 29, the 4th one way valve 30, the 5th one way valve 31 and hydraulic motor 32, the hydraulic fluid port P of hydraulic control proportional direction valve 16 links to each other with the hydraulic fluid port B of the first one way valve 11, the hydraulic fluid port T of hydraulic control proportional direction valve 16 links to each other with fuel tank, the hydraulic fluid port A of this hydraulic control proportional direction valve 16 divides three the tunnel: the first via meets the hydraulic fluid port A of the first hydraulic control one-way valve 27, the second the tunnel meets the hydraulic fluid port B of the 4th one way valve 30, and Third Road meets the hydraulic fluid port A of hydraulic motor 32; The hydraulic fluid port B of this hydraulic control proportional direction valve 16 also divides three the tunnel: the first via meets the hydraulic fluid port A of the second hydraulic control one-way valve 28, and the second the tunnel meets the hydraulic fluid port B of the 5th one way valve 31, and Third Road meets the hydraulic fluid port B of hydraulic motor 32; The hydraulic fluid port B of the hydraulic fluid port B of this first hydraulic control one-way valve 27 and the second hydraulic control one-way valve 28 links to each other with the hydraulic fluid port A of automatically controlled proportional direction valve 29, the hydraulic fluid port T connected tank of automatically controlled proportional direction valve 29; The hydraulic fluid port A connected tank of the hydraulic fluid port A of the 4th one way valve 30 and the 5th one way valve 31.The control port K of the first hydraulic control one-way valve 27 links to each other with the control port K1 of hydraulic control proportional direction valve 16, and the control port K of the second hydraulic control one-way valve 28 links to each other with the control port K2 of hydraulic control proportional direction valve 16.

The outlet of described the first variable pump 6 divides three the tunnel: the first via meets the hydraulic fluid port A that scraper bowl fluid power system 8, the second tunnel connects the second one way valve 13, and Third Road meets the hydraulic fluid port A1 of shuttle valve 9; The outlet of described the second variable pump 7 also divides three the tunnel: the first via meets the hydraulic fluid port A that dipper fluid power system 12, the second tunnel connects the first one way valve 11, and Third Road meets the hydraulic fluid port A2 of shuttle valve 9.The hydraulic fluid port B of described shuttle valve 9 connects the import of safety valve 10, the outlet connected tank of safety valve 10.

The control port K1 of described hydraulic control proportional direction valve 16 links to each other with conventional hydraulic excavator pilot control oil circuit respectively with control port K2.

In the utility model, described variable displacement motor 5 and variable pump 6,7 can be selected automatically controlled variable displacement motor and the variable pump with displacement electricity feedback.Described frequency converter 1 and dynamoelectric machine 4 can be selected permasyn morot and electric machine controller.Described solenoid operated directional valve 15,22,23,25 can be selected by the two-way plug-in valve of solenoid operated directional valve as pilot stage.

Specific works principle of the present utility model is as follows:

The controller of excavator (not shown) gathers with data by the pressure signal to pilot control handle (not shown) output and processes, obtain pilot control pressure, judge that the mode of operation obtain swing arm is in rising and still is in and transfers and the mode of operation of upper mechanism of car 34 is in left revolution or right-hand rotation, the controller of excavator accepts to detect in this system two variable pumps 6 simultaneously, 7 outlet pressures, two hydraulic accumulators 24, the current signal of the pressure sensor of 26 pressure (not shown), the voltage signal of the sign discharge capacity of the voltage signal of sign battery 2 remaining capacity SOC of battery management controller (not shown) output and two volume adjustable hydraulic pump amplification boards (not shown) output.To motor 3, frequency converter 1, the first variable pump 6, the second variable pump 7, variable displacement motor 5, four solenoid operated directional valves (15,22,23,25), proportional direction valve 29 and four proportional throttle valves 18,19,20,21 sending controling instructions, thereby the spool displacement of the discharge capacity of the discharge capacity of the throttle of control engine 3, variable pump 6,7, variable displacement motor 5, solenoid operated directional valve 15,22,23,25 station, automatically controlled proportional direction valve 29, proportional throttle valve 18,19,20,21 spool displacement.Frequency converter 1 sends control instruction by the signal that the controller (not shown) that receives excavator transmits to dynamoelectric machine 4, with mode of operation and the target control signal of control dynamoelectric machine 4.

Concrete control procedure of the present utility model is as follows:

(1) dynamical system

Set each judgment threshold S of the SOC (dump energy) of battery 2 ₁, S ₂And satisfy S ₁＜S ₂Set the pressure p of the first hydraulic accumulator 24 ₁Each judgment threshold p ₁₁, p ₁₂And satisfy p ₁₁＜p ₁₂Set the pressure p of the second hydraulic accumulator 26 ₂Each judgment threshold p ₂₁, p ₂₂And satisfy p ₂₁＜p ₂₂The dynamical system workflow is as follows:

(1) the artificial initial gear of throttle of setting motor 3 according to loadtype.

(2) obtain the rotation speed n of the minimum correspondence of engine consumption rate corresponding to this throttle gear according to the universal characteristic curve of motor 3 _EtWith torque T _EtMotor 3 begins startup work.

(3) by detecting two variable pumps 6,7 outlet pressure and discharge capacity, the needed torque T of computational load _L

$T_L=\frac{p_{p1}{\mathrm{<figure-callout\; id="1"\; label="q\; p"\; filenames="HDA0000158262970000011.png"\; state="\{\{state\}\}">q</figure-callout>}}_p}{2\mathrm{\&pi;}}+\frac{p_{p2}{\mathrm{<figure-callout\; id="2"\; label="q\; p"\; filenames="HDA0000158262970000011.png"\; state="\{\{state\}\}">q</figure-callout>}}_p}{2\mathrm{\&pi;}}---\left(1\right)$

P in the formula _P1---the first variable pump outlet pressure; MPa

p _P2---the second variable pump outlet pressure; MPa

q _P1---the first variable pump discharge capacity; Ml/r

q _P2---the second variable pump discharge capacity; Ml/r

(4) according to the SOC of battery 2 and two hydraulic accumulators 24,26 pressure p ₁, p ₂Dynamically adjust the target torque T of dynamoelectric machine 4 _EMtTarget torque T with variable displacement motor _HMt

$T_{\mathrm{EMt}}=k_1\left\{\begin{array}{cc}{T}_{\mathrm{EM}\max };& T_L-T_{\mathrm{Et}}>Y_{\mathrm{EM}\max }\\ T_L-T_{\mathrm{Et}};& T_L-T_{\mathrm{Et}}\&le;T_{\mathrm{EM}\max }\end{array}\right.---\left(2\right)$

T _HMt＝T _L-T _Et-T _EMt (3)

T in the formula _EMmaxThe peak torque of-dynamoelectric machine; N _m

When the SOC of battery 2 satisfies SOC＞S ₂The time, this moment, the electric weight of battery 2 was more sufficient, k ₁Adjust as follows:

When the SOC of battery 2 satisfies S ₁≤ SOC≤S ₂The time, this moment, the electric weight of battery 2 was in reasonable fluctuation zone, k ₁Adjust as follows:

When the SOC of battery 2 satisfies SOC＜S ₁The time, this moment, the electric weight of battery 2 was not enough, k ₁Adjust as follows:

(5) the dynamic adjustment of the throttle gear of motor 3

The throttle gear of motor 3 is according to the SOC of battery 2, two hydraulic accumulators 24,26 pressure p ₁And p ₂Dynamically adjust, specific rules is as follows:

1) works as p ₁＜p ₁₁And SOC＜S ₁The time, motor 3 throttle gears rise one grade;

2) work as p ₂＜p ₂₁And SOC＜S ₁The time, motor 3 throttle gears rise one grade;

3) work as p ₂＜p ₂₁And p ₁＜p ₁₁The time, motor 3 throttle gears rise one grade;

4) work as p ₂＜p ₂₁And p ₁＜p ₁₁And during SOC＜S1, motor 3 throttle gears rise two grades;

5) work as p ₁＞p ₁₂And SOC＞S ₂The time, motor 3 throttle gears fall one grade;

6) work as p ₂＞p ₂₂And SOC＞S ₂The time, motor 3 throttle gears fall one grade;

7) work as p ₂＞p ₂₂And p ₁＞p ₁₂The time, motor 3 throttle gears fall one grade;

8) work as p ₂＞p ₂₂And p ₁＞p ₁₂And SOC＞S ₂The time, motor 3 throttle gears fall two grades;

9) all the other patterns, motor 3 throttle gears are constant.

(6) displacement control of variable displacement motor 5

Calculate the target torque T of variable displacement motor 5 according to formula (3) _Het, the first hydraulic accumulator 24 pressure p ₁Pressure p with the second hydraulic accumulator 26 ₂Calculate the discharge capacity q of variable displacement motor 5 _m

1) target torque T _HEtWhen larger, the first solenoid operated directional valve 15 is not worked, and the 4th solenoid operated directional valve 25 electromagnet get electric, and the second hydraulic accumulator 26 discharges hydraulic oil and drives variable displacement motor 5, and the discharge capacity account of variable displacement motor 5 is as follows:

$q_m=\frac{2\mathrm{\&pi;}{T}_{\mathrm{HMt}}}{p_2}---\left(7\right)$

2) target torque T _HEtHour, the first solenoid operated directional valve 15 electromagnet get electric, and the 4th solenoid operated directional valve 25 electromagnet must not electricity, and the first hydraulic accumulator 24 discharges hydraulic oil and drives variable displacement motors 5, and the discharge capacity account of variable displacement motor 5 is as follows:

$q_m=\frac{2\mathrm{\&pi;}{T}_{\mathrm{HMt}}}{p_1}---\left(8\right)$

(2) swing arm electrohydraulic control system

(1) swing arm drives oil cylinder 17 retractions

The second solenoid operated directional valve 22 electromagnet get electric, and swing arm drives the part fluid of the rodless cavity of oil cylinder 17, flow to the rod chamber that swing arm drives oil cylinder 17 through the second solenoid operated directional valve 22 and proportional throttle valve 20; The 3rd solenoid operated directional valve 23 electromagnet get electric, and the part fluid of the rodless cavity of swing arm driving oil cylinder 17 is oil-filled by 23 pairs of the first hydraulic accumulators 24 of the 3rd solenoid operated directional valve, movable arm potential energy is changed into hydraulic energy be stored in the first hydraulic accumulator 24; Drive the certain pressure of rod chamber of oil cylinder 17 by the proportion electro-magnet Current Control swing arm of controlling the 3rd proportional throttle valve 20, in case the rod chamber that stopper arms causes swing arm to drive oil cylinder 17 when transferring is fast inhaled empty.The electric current of the proportion electro-magnet by controlling the second proportional throttle valve 19 is adjusted the lowering velocity that swing arm drives oil cylinder 17.The first proportional throttle valve 18 and the 4th proportional throttle valve 21 are not all worked.

(2) swing arm driving oil cylinder 17 stretches out

Hydraulic oil both can be from the first variable pump 6, also can be from the second hydraulic accumulator 26, in the utility model, consider that actual hydraulic pressure digger revolving brake pressure generally is higher than the characteristics of boom cylinder pressure, described the first hydraulic accumulator 24 and the second hydraulic accumulator 26 adopt the different pressures grade.At this, for guarantee swing arm to transfer fast setting lower, needed pressure rating when the pressure rating of the first hydraulic accumulator 24 drives oil cylinder 17 and stretches out less than swing arm; And be higher that the braking ability of mechanism of car 34 arranges on guaranteeing, needed pressure rating when the pressure rating of the second hydraulic accumulator 26 is generally stretched out greater than swing arm driving oil cylinder 17.Enter the flow that swing arm drives the rodless cavity of oil cylinder 17 by the Current Control of controlling the first proportional throttle valve 18 electromagnet, drive the back pressure (mainly in order to improve movement velocity stability a less back pressure being set) of the rod chamber of oil cylinder 17 by controlling the 4th proportional throttle valve 21 electromagnet currents control swing arm.The second proportional throttle valve 19 and the 3rd proportional throttle valve 20 are not all worked.

(3) slew gear electrohydraulic control system.

When (1) upper mechanism of car 34 is braked

Pilot control handle (not shown) returns meta, and the control port K1 at hydraulic control proportional direction valve 16 two ends, the hydraulic fluid pressure of control port K2 equate and be lower that hydraulic control proportional direction valve 16 is operated in meta.Upper mechanism of car 34 is rotated further under the effect of inertia, cause A (B) lateral pressure of hydraulic motor 32 to raise, and B (A) lateral pressure is lower.When the pressure of the second hydraulic accumulator 26 is higher, the electric current of automatically controlled proportional direction valve 29 left side electromagnet is maximum, or the pressure upper side of hydraulic motor 32 is by behind the first hydraulic control one-way valve 27 second hydraulic control one-way valves 28, rear oil-filled to the second hydraulic accumulator 26 by automatically controlled proportional direction valve 29, the 4th reversal valve 25, the energy removal process of the braking kinetic energy of mechanism of car 34 in the realization.Or hydraulic motor 32 carry out repairing than downside by the 4th one way valve 30 the 5th one way valve 31.When the pressure of the second hydraulic accumulator 26 was low, the size of current of the right proportion electro-magnet by regulating proportional direction valve 29 realized the throttling braking procedure of upper mechanism of car 34.

(2) upper mechanism of car 34 Acceleration of startings or when at the uniform velocity rotating

The control port K1 of hydraulic control proportional direction valve 16 connects the hydraulic oil with certain pressure, is operated in left station, simultaneously by oily reverse first hydraulic control one-way valve 27 of opening of the control of control port K1, mechanism of car 34 anticlockwises in the realization.Connect the hydraulic oil with certain pressure with control port K2 that should hydraulic control proportional direction valve 16, be operated in right working position, reverse second hydraulic control one-way valve 28 of opening of control oil by control port K2 simultaneously, mechanism of car 34 right rotations in the realization.Hydraulic oil both can be from the second variable pump 7, also can be from the second hydraulic accumulator 26.

In sum, of the present utility model focusing on:

This system adopts the oily electric liquid hybrid drive system that is comprised of motor, dynamoelectric machine, variable displacement motor, the first variable pump, the second variable pump, battery, hydraulic accumulator, two kinds of patterns of oily electric mixed mode and hydraulic hybrid can be operated in, the requirement of high-energy-density and high power density can be satisfied simultaneously.

Moreover, swing arm drives and forms movable arm potential energy recovery system and upper mechanism of car rotary braking energy-recuperation system by cylinder hydraulic control unit, hydraulic accumulator control module and the organization hydraulic pressure control module reasonable coordination of getting on the bus, the energy composite energy recovery system that it has adopted a cover to be comprised of the dynamical system key element, movable arm potential energy both can directly flow to the swing arm rod chamber, can reclaim by hydraulic accumulator again, the while can directly drive hydraulic pump or drive dynamoelectric machine by hydraulic motor and convert electrical power storage in battery.

Secondly, when rotary braking, recoverable energy both can realize reclaiming by hydraulic accumulator, also can directly drive swing arm and drive oil cylinder, converts electrical power storage in battery by can hydraulic motor directly driving hydraulic pump or drive dynamoelectric machine simultaneously.

In addition, the energy of the second hydraulic accumulator can directly drive mechanism of car revolution acceleration.

The utility model combines the advantage of oil electric mixed dynamic system and hydraulic hybrid power system aspect dynamical system, followed Conversion of Energy link minimum principle in the energy recovery with aspect utilizing, improved energy recovery efficiency, dynamical system and energy-recuperation system share a cover key element (hydraulic accumulator control module and battery etc.) simultaneously, take this, can improve engine operation efficient, can reduce again the energy consumption loss in the energy-recuperation system, not affect the steady operation of motor simultaneously.

The above, it only is preferred embodiment of the present utility model, be not that technical scope of the present utility model is imposed any restrictions, so every foundation technical spirit of the present utility model all still belongs in the scope of technical solutions of the utility model any trickle modification, equivalent variations and modification that above embodiment does.

Claims (10)

1. A hydraulic excavation energy-saving system, which includes a boom drive cylinder (17) and a boarding mechanism (34), is characterized in that: it also includes an oil-electric-hydraulic hybrid drive system (100), a hydraulic accumulator control unit (200 ), boom drive cylinder hydraulic control unit (300), boarding mechanism hydraulic control unit (400), first check valve (11), second check valve (13), third check valve (14), a first hydraulic accumulator (24) and a second hydraulic accumulator (26); The oil-electric-hydraulic hybrid drive system 100 includes an engine (3), an electric motor/generator (4) and a variable displacement motor (5), a first variable displacement pump (6) and a second variable displacement pump (7) connected by a coaxial mechanical transmission. ); The hydraulic accumulator control unit 200 includes a first electromagnetic reversing valve (15), a second electromagnetic reversing valve (22), a third electromagnetic reversing valve (23), a fourth electromagnetic reversing valve (25) The aforementioned first hydraulic accumulator (24) is connected to the oil port B of the third electromagnetic reversing valve (23), and the oil port A of the third electromagnetic reversing valve (23) is divided into three routes: the first road is connected to the first electromagnetic reversing valve The oil port A of the reversing valve (15), the second road is connected to the oil port B of the third check valve (14), the third road is connected to the oil port B of the second electromagnetic reversing valve (22); the second hydraulic accumulator The energy device (26) is connected to the oil port B of the fourth electromagnetic reversing valve (25); the oil port A of the second electromagnetic reversing valve (22) is connected to the oil port B of the second check valve (13); the fourth The oil port A of the electromagnetic reversing valve (25) is divided into two routes: the first route is connected to the oil port B of the first electromagnetic reversing valve (15), and the second route is connected to the oil inlet of the variable motor (5); The boom driving cylinder hydraulic control unit 300 includes a first proportional throttle valve (18), a second proportional throttle valve (19), a third proportional throttle valve (20), a fourth proportional throttle valve (21 ), the oil port of the rod cavity of the boom driving oil cylinder (17) is divided into two routes: the first route is connected to the oil port B of the third proportional throttle valve (20), and the second route is connected to the fourth proportional valve ( 21) oil port A; and the oil port of the rodless cavity of the boom driving cylinder (17) is divided into three routes: the first route is connected to the oil port B of the first proportional throttle valve (18), and the second route is connected to The oil port A of the second proportional throttle valve (19), the third road is connected to the oil port A of the third check valve (14); the oil port B of the second proportional throttle valve (19) and the fourth proportional throttle The oil port B of the throttle valve (21) is connected to the oil tank; the oil port A of the first proportional throttle valve (18) and the oil port A of the third proportional throttle valve (20) are connected to the second electromagnetic reversing valve (22) oil port A; The hydraulic control unit 400 of the boarding mechanism includes a hydraulically controlled proportional directional valve (16), a first hydraulically controlled check valve (27), a second hydraulically controlled check valve (28), an electronically controlled proportional directional valve (29 ), the fourth one-way valve (30), the fifth one-way valve (31) and the hydraulic motor (32), the hydraulic motor (32) is connected to the aforementioned boarding mechanism (34), and the hydraulic control proportional directional valve (16) The oil port P of the first check valve (11) is connected to the oil port B, the oil port T of the hydraulic control proportional directional valve (16) is connected to the oil tank, and the oil port A of the hydraulic control proportional directional valve (16) is divided into three routes : The first road is connected to the oil port A of the first hydraulic control check valve (27), the second road is connected to the oil port B of the fourth check valve (30), and the third road is connected to the oil port A of the hydraulic motor (32) ; The oil port B of the hydraulic control proportional directional valve (16) is also divided into three routes: the first road is connected to the oil port A of the second hydraulic control check valve (28), and the second road is connected to the fifth check valve (31) The oil port B of the hydraulic motor (32) is connected to the third road; the oil port B of the first hydraulic control check valve (27) and the second hydraulic control check valve (28) are connected to the electric control proportional direction The oil port A of the valve (29) is connected, the oil port T of the electronically controlled proportional directional valve (29) is connected to the fuel tank, and the oil port P of the electronically controlled proportional directional valve (29) is connected to the oil port of the fourth electromagnetic reversing valve (25) A; the oil port A of the fourth check valve (30) and the oil port A of the fifth check valve (31) are connected to the oil tank; the control oil port K and the hydraulic control ratio of the first hydraulic control check valve (27) The control oil port K1 of the directional valve (16) is connected, and the control oil port K of the second hydraulic control check valve (28) is connected with the control oil port K2 of the hydraulic control proportional directional valve (16); The outlet of the first variable displacement pump (6) is connected to the oil port A of the second check valve (13); the outlet of the second variable displacement pump (7) is connected to the oil port A of the first check valve (11). 2. A hydraulic excavation energy-saving system according to claim 1, characterized in that: the pressure level of the first hydraulic accumulator (24) is lower than the pressure level required when the boom drive cylinder (17) is extended , and the pressure level of the second hydraulic accumulator (26) is greater than the required pressure level when the boom drive oil cylinder (17) is extended. 3. A hydraulic excavation energy-saving system according to claim 1, characterized in that it further comprises a shuttle valve (9) and a safety valve (10), the oil port A1 of the shuttle valve (9) is connected to the variable pump (6) The oil outlet of the shuttle valve (9), the oil port A2 of the shuttle valve (9) is connected to the oil outlet of the variable pump (7), the oil port B of the shuttle valve (9) is connected to the inlet of the safety valve (10), and the outlet of the safety valve (10) Connect to the fuel tank. 4. A hydraulic excavation energy-saving system according to claim 1, characterized in that: the control oil port K1 and the control oil port K2 of the hydraulic control proportional directional valve (16) are respectively connected with the pilot control oil circuit of the traditional hydraulic excavator connected. 5. The hydraulic excavation energy-saving system according to claim 1, characterized in that: a speed reducer (33) is connected between the hydraulic motor (32) and the boarding mechanism (34). 6. A hydraulic excavation energy-saving system according to claim 1, characterized in that it further comprises a bucket hydraulic drive system (8), and the bucket hydraulic drive system (8) is connected to the oil outlet of the variable displacement pump (6) . 7. A hydraulic excavation energy-saving system according to claim 1, characterized in that it further comprises a stick hydraulic drive system (12), and the stick hydraulic drive system (12) is connected to the oil outlet of the variable displacement pump (7) . 8. A hydraulic excavation energy-saving system according to claim 1, characterized in that: the motor/generator (4) is electrically connected to the battery (2) through a frequency converter (1), and the frequency converter (1) and The motor/generator (4) is a permanent magnet synchronous motor and a motor controller. 9. The energy saving system for hydraulic excavation according to claim 1, characterized in that: the variable variable motor (5) and variable variable pump (6, 7) are electronically controlled variable variable motor and variable variable pump with electric displacement feedback. 10. A hydraulic excavation energy-saving system according to claim 1, characterized in that: the first to fourth electromagnetic reversing valves (15, 22, 23, 25) are electromagnetic reversing valves 2-way cartridge valve as pilot stage.

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