KR200367740Y1 - ydraulic supply Apparatus - Google Patents

Abstract

The present invention is a device for continuously supplying hydraulic oil for the hydraulic system

It is a hydraulic oil supply device that creates a hydraulic source using gravity principle.

The present invention is designed to store the hydraulic fluid required by the hydraulic actuator.

Is equipped with a tank, which is forced to continuously inject a suitable amount of low pressure oil

And a pressurizing means for automatically generating the required hydraulic pressure, and a working oil required on the load side.

It is provided with a supply means for automatically supplying according to the required size.

Therefore, the present invention omits the motor and the hydraulic pump for hydraulic oil,

As a safety technology, it generates high pressure hydraulic oil and supplies it to the hydraulic actuator to provide mechanical energy.

There is a revolutionary economic, efficient and environmentally friendly effect in obtaining.

Description

Hydraulic supply Apparatus

The present invention relates to a hydraulic system, and more particularly to the hydraulic actuator

Of hydraulic oil supply system to supply high pressure hydraulic fluid which is necessary for actuator

will be.

1 and 2 illustrate the concept of the prior art and will be described in detail.

It's like

In general, the oil of oil is a method of transmitting energy.

Hydraulic system method of transferring energy by using sieve as a medium is common.

In this hydraulic energy transmission method, oil must be hydraulicized.

Hydraulic energy transmission method is made as shown in Figure 1, the hydraulic system of the prior art

If the hydraulic oil supply system creates a hydraulic source from the system, the motor (or engine) and the hydraulic pump

It can be seen to include an oil tank.

Usually, as a technique for creating a conventional hydraulic source, first of all, an electric motor (or engine)

To generate mechanical energy and to hydraulically drive the hydraulic pump

will be.

In this process, the input input energy of the motor (Pg) and the loss energy of the hydraulic pump (Pp)

Is naturally prepared, and the input energy (Pg) of the motor and the loss energy (Pp) of the hydraulic pump

Compared to the final output mechanical energy (P1) of the hydraulic system, this input energy is

The problem is that the efficiency is low because it is too large, and thus energy

There is a problem that no energy is obtained other than the conversion of the form.

The energy transfer relation of the prior art described above is developed as follows.

From here

Pg: Input energy for operating the motor.

Pp: Energy lost from the hydraulic pump.

P1: The final output mechanical energy of the hydraulic system,

The energy balance law requires that Pg = P1, but the final energy output

Pg-Pp = P1 because the hydraulic pump loss should be excluded.

Therefore, the output-to-input efficiency is (P1 / Pg) × 100 = [(Pg-Pp) / Pg] × 100,

[1- (Pp / Pg)] × 100. (If the hydraulic circuit loss is ignored)

As a result, energy efficiency is reduced as much as loss energy Pp, and 100% is always

Ha.

On the other hand, accumulating hydraulic energy in the prior art accumulate in Figure 2

There is an accumulator, an accumulator.

This accumulator device also has a structure to store hydraulic energy

Hydraulic pumps that generate high pressure oil and motors (or engines)

It must be equipped and operated.

In addition, as shown in Fig. 2, the input / output port of the hydraulic fluid

Energy accumulation time and emission time cannot be done at the same time.

It can be used as a temporary energy supplement for electric lights, but the high pressure hydraulic fluid

There is a problem that it cannot play its role as a main energy source for supplying energy.

The present invention was created to solve the above problems, conventionally

The hydraulic pump and the hydraulic pump to hydraulic the hydraulic fluid in the hydraulic system of the hydraulic system

The motor (or engine) forcibly driven is omitted, and it is natural to replace the hydraulic source composition.

Since we use force (= pressure) energy, this natural gravity (= pressure) energy is converted into hydraulic energy.

Converted to provide a very energy efficient hydraulic oil supply structure.

have.

Another object of the present invention is to obtain the amount of natural gravity (= pressure) energy

Hydraulic energy is to obtain the effect of obtaining useful energy.

1 is a black diagram showing the basic configuration of a hydraulic system according to the prior art,

Figure 2 is a cross-sectional view schematically showing the configuration of the accumulator according to the prior art,

Figure 3 shows the basic configuration for the hydraulic oil supply device according to an embodiment of the present invention

Giving Black Leads,

Figure 4 is a schematic configuration of a hydraulic system showing a first embodiment of the present invention device

Schematic,

5 is a configuration diagram showing a structure of a hydraulic oil supply device in the hydraulic system of FIG.

Figure 6 shows an exploded perspective view and assembly of the pressing means in the hydraulic system of Figure 4

schematic,

7 is a schematic view showing the configuration and operation of the injection means in the hydraulic system of FIG.

8 is a view showing an operation of the pressure intensifier section in the injection means of FIG.

9 shows the configuration of the supply means and the hydraulic circuit operation in the hydraulic system of FIG.

schematic,

10 is an increase of the injection means in the first embodiment of the present invention shown in Figs.

The amount of hydraulic oil injected into the oil tank by installing two or more presses in parallel and operating them sequentially.

Hydraulic circuit diagram showing a second embodiment to balance the discharge amount and

11 is an oil tank 2 in the first and second embodiments of the present invention shown in FIGS.

Install more than one in parallel and operate them alternately; The amount of hydraulic oil in the hydraulic system

Hydraulic circuit diagram showing the third embodiment in which the discharge amounts are balanced.

<Explanation of symbols for the main parts of the drawings>

100: hydraulic oil supply device 101: oil tank S: working oil

110: pressurization means 111: load partition 112: seal

113: upper load 114: circular rod 115: elastic member for pressure adjustment

200: injection means 201: pneumatic power source 202: shared pressure intensifier

203, 204, 302, 303: backflow preventer 205: hydraulic valve

300: supply means 301: stop valve 303: pressure control valve

304: flow control valve 305: directional control valve 1001, 1101: shuttle valve

1002: Pneumatic sequence control circuit 400: Hydraulic circuit 500: Hydraulic actuator

600: Return Oil Collection Tank

To create a hydraulic source for the hydraulic system, gravity (= pressure) energy is generated

In using, with reference to the accompanying drawings will be described in more detail the present invention

Is as follows.

4 is a layout of the entire circuit of the first preferred embodiment of the present invention.

to be.

Hydraulic oil supply device 100 of the present invention largely stores the operating oil (S). Discharge

At least one oil tank 101; The operating oil is installed on the oil tank 101

Pressing means (110) for generating a high pressure oil by pressing to the weight of the load (S); Said group

Injection means (200) for forcibly introducing the hydraulic oil (S) to the oil tank (101); Compressed air

A pneumatic power source 201 that generates and provides to the at least one co-pressure intensifier 202; Prize

The hydraulic pressure set by discharging the hydraulic oil S generated at the high pressure set by the oil tank 101

It is composed of; supply means 300 for supplying the hydraulic circuit at an excess flow rate.

You can select and remotely control the hydraulic oil (S) flow path during system operation.

A hydraulic circuit 400; and a hydraulic actuator 500 for converting hydraulic energy into mechanical energy; and

A first return flow path for returning the low pressure hydraulic oil that flows out after the hydraulic actuator 500 operates;

The second return flow path which collects the leakage oil generated in each hydraulic equipment to one place and the co-pressure increase

A supply flow path is provided for supplying hydraulic oil to the pressurizer 202 to store and provide return oil.

Return oil collection tank 600; further comprises a system.

5 and 6 are the first embodiment of the present invention configured as described above, the pressurized water

It shows the configuration of the stage 110 and its flow path, basically the oil tank 101

The hydraulic fluid S is stored, compressed and discharged inside.

The pressing means 110 is; It is installed on the upper side of the outside of the oil tank 101,

A load diaphragm 111 for blocking and shielding the inside and the outside of the oil tank 111; The oil tank

(101) A seal attached to seal between the load diaphragms 111 around the inner wall.

(seal: 112); A cylindrical rod 114 perpendicular to the center of the load diaphragm 111;

An upper load 113 fixedly mounted on the rod 114; Inside the oil tank 101

Elasticity for pressure adjustment arranged at equal intervals in the cylinder to adjust the hydraulic pressure to reach the set value

It is provided with the member 115.

7 shows the configuration of the injection means 200 and its flow path connection.

The injection means 200 is a pneumatic power source 201 and at least one shared pressure intensifier

202, check valves 203 and 204 (check valves) and hydraulic pressure valves 205, the low pressure oil

Inflow passage of the inlet flows into the co-pressure intensifier 202 from the return oil collection tank 600

And a flow path of the high pressure oil is increased in the co-pressure intensifier 202 to countercurrent flow.

It is formed to be injected into the oil tank 101 via the paper machine 203.

The pneumatic power source 201 produces compressed air to produce the shared pressure intensifier.

It is common as a power source for operating 202, and detailed description thereof will be omitted.

8 shows the structure and operation of the co-pressure intensifier 202.

In general, a co-pressure intensifier is used to increase the pressure of hydraulic oil using compressed air.

It is a pressure increasing device which operates a pressure machine and converts low pressure oil into high pressure oil.

The operation mechanism of the co-pressure intensifier 202 is the pneumatic power source 201

Of compressed air is pressurized to pneumatic P1 through port A of the co-pressure intensifier 202,

As the piston is exhausted to the hydraulic cylinder B, the piston is advanced to the hydraulic cylinder side.

Port S2 and the backflow preventer while increasing the hydraulic oil S higher than the oil pressure of the oil tank.

Injection into the oil tank 101 through the (203).

On the contrary, the compressed air is switched by the directional control valve so that the common pressure intensifier

When pressurized to port B of 202 and exhausted to port A, the hydraulic cylinder is retracted and vacuumed.

Since the operating oil of the return oil collection tank 600 is the backflow preventer 204 and the port S1

Through the hydraulic cylinder.

Low pressure of the return oil collection tank 600 while the operation cycle as described above is circulated

The oil is a high pressure oil higher than the hydraulic pressure of the oil tank 101 to the oil tank 101

Is injected.

On the other hand, the backflow preventer 203 prevents the back flow of the working oil in the oil tank

In addition, the backflow preventer 204 is the hydraulic oil in the hydraulic cylinder the return oil collection tank

Prevent backflow to 600.

The basic structure of the check valve (203, 204) is a check valve, but oil tank

The hydraulic valve 205 provided at the end of the inlet of the cylinder has a structure similar to the exploded perspective view of FIG.

If the oil tank hydraulic pressure is slightly higher than the inlet, the pressure of the hydraulic valve 205

The lid closes, preventing backflow very easily, preventing damage to the check valve and fatigue.

All.

Although not shown in the drawing, in this concept the ports S1 and S2 of the hydraulic cylinder

Can also be installed to prevent breakage and fatigue of the check valve.

9 is a view showing the configuration and the flow path of the supply means 300, the oil tank

The discharge flow path of the hydraulic oil S installed in the lower portion of the tank 101 and the flow of the hydraulic oil are manually

A stop valve 301 for adjusting, a backflow preventer 302 for preventing a backflow of the hydraulic oil, and a pressure

A pressure control valve 303 for setting a force and a flow control valve 304 for passing only a constant flow rate

And a conduit.

9 degrees converts the hydraulic circuit 400 and the fluid energy into mechanical energy.

Shows the connection of the hydraulic actuator 500, its configuration and operation are generally many

Since this is prevalent and there are many circuit configuration changes, the description thereof is omitted.

The second embodiment is shown in FIG.

The difference with respect to the first embodiment is that, as shown, the co-pressure intensifier

202 is further provided to be installed in parallel, and the flow directions of the two flow paths need to be combined into one.

Shuttle valve 1001 applied when there is; as shown above

Disposed between the co-pressure intensifier 202 and the oil tank 101, the co-pressure intensifier

Combine the two output flow paths arranged in parallel to (202) into one, and connect to the oil tank (101)

By injection.

On the other hand, in the pneumatic sequence control circuit 1002 when the booster is sequentially operated

The key plays a role.

Therefore, in the second embodiment, the hydraulic oil main of the oil tank 101 than the first embodiment

Effortlessly maintain the balance between the quantity of discharge and the quantity of discharge.

The third embodiment is shown in FIG.

The difference with respect to the first and second embodiments is that, as shown, the oil tank

Further provided with 101 and installed in parallel, as shown in the shuttle valve 1101

Arranged between the oil tank 101 and the hydraulic circuit 400, parallel to the oil tank 101

The two output flow paths which are arranged are combined into one, and the hydraulic oil S flows to the hydraulic system side.

Therefore, the hydraulic oil injection volume of the oil tank of either side during the operation of the hydraulic oil supply device

If the balance between the volume and discharge amount is broken and the hydraulic pressure fluctuates, the shuttle valve

1101 selectively operates to close the flow path and open the other flow path

It is operated by the hydraulic oil supply device of the side, during which the hydraulic oil supply device of one side is balanced

You will find. In this way, one side and the other side can be balanced by selective alternation.

To provide stable hydraulic fluid to the hydraulic system.

Experiment day in the first embodiment of the preferred Figure 4 based on the accompanying drawings

The explanation focuses on the site.

The first experimental data, the oil tank 101 of the hydraulic oil supply device 100

To store the hydraulic oil (S), and the pressurizing means 110 acts on the hydraulic oil at high pressure

It is an experiment to find the weight required for pressurization.

Next, under the experimental equipment, the oil tank 101 has a cylindrical shape with a radius of 10 cm,

When the effective height (H) is 200cm and the high pressure oil pressure setting (P) is 300㎏ / ㎠, it actually works

The average pressure P received by oil is equal to the following Equation 1 of hydrodynamics,

The total weight of the heavy material is obtained by the following equation (2) in which equation (1) is developed.

P = W / A = ωH [kg / ㎠]

In Equation 1, the total load weight W is equal to Equation 2 below.

W = ωAH [kg]

Here, the installation conditions and experimental conditions of the above formula are as follows.

ω: Weight per unit volume of working oil (kg / cm 3; calculated result = experimental value = 1.5 kg / cm 3).

A: load diaphragm cross section (cm2; radius 10²π = 314cm2).

H: working oil effective height (cm; 200cm).

P: average pressure of the hydraulic oil (kg / cm 2; 300kg / cm 2).

W: Total load weight (kg;?).

When the weight ω per unit volume of the working oil is obtained from the above formula (1) P = ωH [㎏ / ㎠],

300 = 200 ω and ω = 300/200 = 1.5 [kg / cm 3].

Total load weight (W) by substituting the above conditions in the equation (2) W = ωAH [kg]

If you find,

W = 1.5 x 314 x 200 = 94,200 [kg].

Above 94,200 ㎏, the total load weight to be pressurized, above the operating oil height of 200 ㎝

When installed in the tooth and pressurized the hydraulic oil, high-pressure hydraulic oil of 300 kg / ㎠.

The second test data, the hydraulic actuator 500 side in the oil tank 101

When the hydraulic oil (S) is discharged at 1,000ℓ / min, 300㎏ / ㎠, the output of the hydraulic actuator 500

It is converted into electric energy to know the amount of energy.

This conversion is calculated by the following equation (3)

Energy production can be obtained.

W (㎾) = η × {(Q × P) / 612｝ × 10­²

Equipment conditions and experimental conditions of the above formula is as follows.

W is a value obtained by converting the hydraulic actuator output into electrical energy [㎾; ? ].

Q: The working flow rate discharged from the hydraulic oil supply device and flowed into the hydraulic motor [ℓ / min; =

1,000].

P: Hydraulic pressure of input and output car transmitted from hydraulic oil supply device to hydraulic actuator [㎏ /

Cm 2; = 280].

η is the overall efficiency of the hydraulic motor [%; = 0.97].

Substituting the above condition into Equation 3, the electric energy output of the hydraulic actuator is

As follows.

W (mm) = 0.97 × {(1,000 × 280) / 612} × 10 mm &lt; 2 &gt; = (about) 44.4 (mm).

In other words, the final mechanical energy of the hydraulic actuator is converted into 44.4㎾ electric energy

All.

The third test data, the injection of the hydraulic oil (S) to the oil tank 101

It is to calculate how much the input (required) energy generated by the injection means (200).

The co-pressure intensifier 202 of the injection means is of the pneumatic power source 201

By receiving the compressed air and supplying by increasing the hydraulic fluid, the input energy of the injection means 200

Loss is equal to the input energy of the pneumatic power source 201.

Therefore, the energy (force) relationship related to the co-pressure intensifier 202 must be solved

do.

The hydraulic pressure P2 generated by the common pressure intensifier 202 shown in FIG. 8 is a pneumatic seal.

Applied to the piston cross-sectional area (A1) of the linder, cross-sectional area (A2) of the ram and the piston of the pneumatic cylinder

Is determined by pneumatic pressure (P1), which is given by the following equations (4, 5, 6)

Lose.

Hydraulic output pressure; P2 = A1 / A2 × P1; <P2 is set to 320㎏ / ㎠>.

Air input pressure; P1 = A2 / A1 × P2

Magnification of intensifier; N = A1 / A2

The installation conditions and experimental conditions of the above formula are as follows.

P2: Hydraulic pressure generated (kg / cm 2; Condition setting = 320kg / cm 2).

P1: Pressure applied to the pneumatic cylinder (kg / cm 2; calculation result = experimental result = 15 kg / cm 2)

A1: cross-sectional area of the pneumatic cylinder piston (cm 2; cross-sectional area of 92 cm in diameter 46²π = 6,644

Cm 2, length 40 cm).

A2: cross-sectional area of the ram (cm 2; cross-sectional area 10²π = 314 cm 2 with a diameter of 20 cm, length 40 cm).

Since the hydraulic power output (P2) is set to 320㎏ / ㎠ in the equipment condition data,

Force air pressure (P1) is 15kg / ㎠ by the equation (5), the pressure intensifier magnification (N) is

21: 1 is obtained by Equation 6.

Therefore, according to the law of energy conservation, the second experimental data

In order to balance the energy output and the input energy of the intensifier,

The input energy B of the pneumatic power source 201 that injects compressed air into the inflator 202 is

Well calculated by equation (7).

B = Equation 3 × (1 / N) [㎾]

Here, the code explanation is as follows.

B: Input power of booster (= pneumatic power source) (㎾).

Equation 3: Electric energy output of hydraulic actuator (㎾; calculated value, experimental result

= 44.4 ms).

N: magnification of booster (A1 / A2 = 21: 1).

The booster input power is according to Equation 7:

44.4 x (1/21) = 2.1 (mm).

The fourth experimental data calculation is to find out the efficiency of the hydraulic system.

All.

The output energy (P2) is 44.4 (㎾) shown in the second experimental data, and input

The energy (P1) is 2.1 (㎾) shown in the third experimental data.

Therefore, the efficiency calculation by using the hydraulic oil supply device of the present invention is

This can be seen from the output versus output relationship.

Pure gain electric energy; Output-input (loss) = 44.4-2.1 = 42.3 (㎾).

Input efficiency versus gain; Gain / input = 42.3 / 2.1 = 20 (times).

As a result, the output energy is 20 times more effective than the input energy.

As described above, the present invention has been described based on the embodiments, but

Various changes can be made by those of ordinary skill in the field to which the proposal belongs.

Therefore, the present invention is not limited to the specific embodiments described above.

This invention has the following advantages.

First, when constructing a hydraulic system, the most expensive products such as electric motors and engines

The pump is omitted and replaced by the present invention, thereby reducing the hydraulic system cost.

Second, electric and hydraulic pumps should be replaced with limited equipment life for long term operation.

It costs a lot of rain and costs a lot of damage and repair costs in case of a breakdown.

This eliminates the effect of improving the operating efficiency of the hydraulic system.

Third, conventional hydraulic systems have energy form conversions under the conservation of energy law.

There is no energy acquisition, but the present invention converts natural gravity (= pressure) energy into hydraulic energy.

Useful energy is generated, providing a way of renewable energy (= alternative energy).

It is effective.

Fourth, the pulsation and vibration generated in the co-pressure machine is the hydraulic oil supply

Absorbed sufficiently by the device, it is possible to supply stable hydraulic fluid to the hydraulic actuator

Therefore, it is a useful design to obtain the overall performance improvement of the hydraulic system.

Claims (7)

Used to generate gravity energy to create hydraulic source of hydraulic system As, At least one oil tank 101 for storing and discharging hydraulic oil (S): Installed on the oil tank 101, the weight of the load to the hydraulic oil (S) Pressurizing means 110 for generating high pressure oil by pressurizing with: At least one forcing the hydraulic oil (S) to flow into the oil tank (101) Injection means 200 and: Discharge the hydraulic oil (S) generated at a high pressure set in the oil tank 101 Supply means 300 for supplying the hydraulic circuit at the set hydraulic pressure and flow rate; Hydraulic oil spilled after operation in the hydraulic actuator 500 and generated in each hydraulic equipment Hydraulic oil, characterized in that it comprises a return oil collection tank 600 for collecting the leakage in one place Oil feeder. The method of claim 1, The pressurizing means 110 is installed on the outside of the oil tank 101, A load diaphragm 111 for blocking and shielding the inside and the outside of the oil tank 111; Sealing between the load diaphragm 111 along the inner wall of the oil tank 101 A seal attached to be (seal) 112; A cylindrical rod 114 perpendicular to the center of the load diaphragm 111; An upper load 113 mounted and fixed to the rod 114; And The oil tank 101 is disposed at equal intervals to reach the set pressure Hydraulic oil, characterized in that it comprises an elastic member 115 for pressure adjustment to adjust Feeder. The method of claim 1, The injection means 200 is at the distal end of the oil tank 101 injection passage The door is opened and closed by the pressure of the fluid to prevent the back flow of the hydraulic oil (S). A hydraulic valve 205; The oil tank by increasing the pressure to a higher pressure than the oil pressure 101 At least one co-pressure intensifier 202 for injecting hydraulic oil into 101; Operating oil flows back from the oil tank 101 when the co-pressure intensifier 202 is operated. Backflow preventer 203 for preventing the flow of water; And Hydraulic oil supply device characterized in that a pipe line for forming a flow path is provided. The method of claim 1, The supply means 300 is: the hydraulic oil installed in the lower portion of the oil tank 101 A discharge passage of (S); A stop valve 301 for manually adjusting the flow of the working oil; A backflow preventer 302 for preventing backflow of the hydraulic oil; A pressure control valve 303 for setting a pressure in the hydraulic circuit; A flow control valve 304 for passing only a predetermined amount of the working oil; And Hydraulic oil supply device characterized in that it comprises a pipeline. The method of claim 1, The return oil collection tank 600: the operation leaked after the operation in the hydraulic actuator 500 A first return passage for returning oil; A second return flow path collecting the leakage oil generated in each hydraulic device into one place; It is provided with a supply passage for providing a return hydraulic fluid to the co-pressure intensifier 202, Storing the first and second return oils and providing the first and second return oils to the shared pressure intensifier 202. Hydraulic oil supply device, characterized in that. The method of claim 1, The injection means 200 and the co-pressure intensifier 202 is installed in parallel with: Shuttle valve disposed between the co-pressure intensifier 202 and the oil tank 101 (1001: shuttle valve); Further, The two output flow paths arranged in parallel in the common pressure intensifier 202 are combined into one, By injecting the connection into the oil tank 101, It is characterized in that the hydraulic oil injection amount and discharge amount of the oil tank 101 is balanced Hydraulic oil supply system. The method according to claim 1 or 6, The oil tank 101 is installed in parallel: A shuttle valve 1101 disposed between the oil tank 101 and the hydraulic circuit 400; more Equipped with Two output flow paths arranged in parallel in the oil tank 101 are combined into one, By supplying hydraulic oil to the hydraulic circuit and the hydraulic actuator 500 side, It is characterized in that the hydraulic oil injection amount and discharge amount of the hydraulic system is balanced. Hydraulic oil feeder.