JPH0244226A - Inspection of function for hydraulic vibrationproof apparatus - Google Patents

Abstract

PURPOSE:To facilitate the execution of functional inspection even at a small place by a method wherein a hydraulic vibrationproof apparatus is separated into a cylinder section and a control valve section and unitary functional inspections are performed to evaluate comprehensive functions from dimensions of the cylinder section based on a unitary functional data. CONSTITUTION:An opening/closing operation of stop valves 43 and 44 is performed for a hydraulic apparatus 40 to pressurize oil in a left chamber M and a right chamber N partitioned with a piston 3 and a rise in the pressure within the left and right chambers and a movement of the piston 3 are measured to determine a rigidity of a cylinder 2 and an action resistance of the piston 3. Then, discharge pipings 41 and 42 are connected to ports 54a and 54b at both ends of a control valve and with the stop valves 43 and 44 opened, oil is supplied gradually to the port 54a. Then, a pressure and a flow rate are measured at the ports 54a and 54b to allow the inverse operation of a moving speed of the piston 3 as given when a desired pressure and the maximum working pressure work thereon thereby facilitating inspection as specified even at a small place such as inside of a plant.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a method for inspecting the function of a hydraulic vibration isolator used as a vibration isolation support for heavy equipment installed in a power generation plant or the like.

[Conventional technology]

FIG. 6 is a diagram showing the configuration of the hydraulic vibration isolator. As shown in the figure, the hydraulic vibration isolator 1 includes a cylinder 2 and a piston 3.
The main components are a control valve 4 attached to the cylinder 2, and a connecting pipe 5.6 that communicates the control valve 4 with the cylinder 2. Note that a piston packing 11 and a rod packing 12 are inserted between the piston 3 and the cylinder 2. Further, 13 is an oil reservoir for supplying oil to the hydraulic vibration isolator 1. Furthermore, within the control valve 4, there are two poppet valves 14a.

14b are provided facing each other so as to operate in response to the movement of the piston 3 in the tension or compression direction.

In the hydraulic vibration isolator 1 configured in this way, the connecting fitting 7 provided on the side wall of the cylinder 2 is attached to the building structure 8, and the connecting fitting 9 provided at the tip of the piston 3 is attached to the heavy H1 equipment 10. Equipped with condition. The hydraulic vibration isolator 1 acts like a kind of damper to suppress the shaking of the heavy equipment 10 when a large shaking occurs in the heavy equipment 10 due to, for example, an earthquake.

That is, the poppet valve 14a in the control valve 4
, 14b are coil springs 22a in a normal state.
, 22b are positioned away from the valve seats 23a, 23b to maintain an open state. Therefore, against gradual movement of the piston 3 due to thermal expansion of the device 10, the vibration isolator 1 does not produce a damping effect. However, when the equipment 10 undergoes large shaking due to an earthquake or the like, and the piston 3 suddenly moves due to the shaking, a large amount of oil 24 in the cylinder 2 moves in response to the movement of the piston 3, creating a strong flow. When such a strong flow occurs, the oil passage holes 25a, 25b and orifice hole 26a provided in the poppet valves 14a, 14b.

The flow resistance at 26b causes the pressure within the hydraulic cylinder 2 to increase, resulting in a rise in the poppet valve 14a.

14b is pressed against the valve seat 23a or 23b.

Then, the oil flows only from the orifice holes 26a and 26b, the flow rate of the moving oil decreases, and the movement of the piston 3 is suppressed. In addition, the poppet valves 14a and 14b
The pressure applied to is controlled by relief valves 27a and 27b so as not to exceed a preset pressure.

Therefore, the control valve 4 has the central function of the oil-lock type hydraulic vibration isolator 1, and is a poppet valve 14a, 14b that immediately responds to the moving speed of the piston 3, that is, the amount of oil flowing into the control valve 4. The operation is
It has a very important role in the function of the hydraulic vibration isolator 1.

Note that the poppet valves 14a and I4b are valve seats 23a.

23b and the pressure inside the cylinder 2 suddenly rises, the maximum pressure is 500 to 60, depending on the weight of the device 10 and the moving speed of the piston 3.
0 reaches 5j/d, and piston 3 has 300 to 400
A load of tons is added. The large-capacity hydraulic vibration isolator 1 that is subjected to such a high load has an outer diameter of 400 to 500 m and a total length of 1.
It grows to a size of ~2m at night.

The function of the hydraulic vibration isolator 1 is conventionally inspected by the following method.

FIG. 7 is a diagram showing a schematic configuration of a testing device for testing the functionality of the hydraulic vibration isolator 1 using a conventional method. This inspection device 30 includes support plates 31, 32a and 32b, and columns 33a and 3 that connect the support plates 31 and 32a and 32b.
3b, a load cell 34 attached to the support plate 31 and connected to the connection fitting 7 of the hydraulic vibration isolator 1, and a cylinder 35 connected to the piston 3 of the hydraulic vibration isolator 1 via the connection fitting 9. , a total M1 device 36, and a hydraulic device 37 are the main components.

Conventionally, the cylinder 35 is reciprocated using the hydraulic device 37 to forcefully displace the piston 3 of the hydraulic vibration isolator 1, thereby determining whether the poppet valves 14a, 14b close at a preset speed. The load W applied to the load meter 34, the amount of displacement X of the piston 3, and the speed V at that time are measured by the AJ1 device 36.

FIG. 8 shows the relationship among piston displacement ffiX, piston speed V, and piston operating resistance (piston load) F. The same figure (-a) shows the relationship between the displacement amount and the speed 1 operating resistance when the piston 3 is within the specified speed Vl, and the same figure (b)
) are the poppet valves 14a and 14 in the control valve 4.
Displacement amount 2 speed when b closes.

The relationship between operating resistance and the figure (c) shows the amount of displacement when the load applied to the piston 3 reaches the maximum load Fmax.

It shows the relationship between speed 1 and operating resistance. Among these, the following are generally used for functional evaluation of the hydraulic vibration isolator 1.

■ Operating resistance F1 when the piston 3 is moving at the specified speed V1, ■ Movement speed of the piston 3 when the piston 3 rises within the specified speed range and the poppet valves 14a and 14b in the control valve 4 are closed. V2,■ Movement speed of the piston 3 when the maximum load Fmax is applied to the piston 3 V3
, ■ Travel distance MXS of the piston 3 until the piston 3 rapidly moves and reaches the maximum load Fmax.

The functions (1) to (2) can be determined from the load W, the displacement X of the piston 3, and the speed V of the piston 3 measured by the inspection device 40.

[Problem to be solved by the invention]

However, in the conventional inspection method, the function of the hydraulic vibration isolator 1 is inspected using the inspection device 30 having the above-described structure.
In order to inspect a hydraulic vibration isolator 1 with a length of about 0 m and a length of approximately 1 m, the dimensions L (total length) and H (outer diameter) shown in Fig. 7 should be A large device weighing 3 to 5 tons is required, and when using such a large inspection device to conduct periodic inspections of hydraulic vibration isolators installed in plant equipment, it is extremely difficult to transport the inspection device. difficult,
Moreover, since the space within the plant is limited, there was a problem in terms of installation space.

SUMMARY OF THE INVENTION Therefore, it is an object of the present invention to provide a method for testing the function of a hydraulic vibration isolator, which allows the function of a hydraulic vibration isolator to be easily evaluated even in a comparatively narrow place.

[Means to solve the problem]

In order to solve the above problems and achieve the object, the present invention has taken the following measures. That is, the cylinder part and the control valve part of the hydraulic vibration isolator are divided, and the divided cylinder part is Oil is supplied to the cylinder chamber and the elastic modulus 1 actuation resistance is determined from the pressure inside the cylinder chamber and the distance traveled by the piston, and the pressure is determined by supplying oil to the divided control valve section and measuring the flow rate. 5
Calculate the flow rate characteristic value, and use the elastic modulus 2 operating resistance of the cylinder section obtained from the individual function test of the cylinder section and the control valve section, the pressure of the control valve section, the flow rate characteristic value, and the dimensions of the cylinder section. The overall function of the hydraulic vibration isolator was inspected and evaluated.

[Effect]

By taking the above measures, the following effects are achieved.

The hydraulic vibration isolator is divided into the cylinder section and the control valve section, and a single function test is performed on each of them.The overall function of the hydraulic vibration isolator is determined from the single function data obtained from this single function test and the various dimensions of the cylinder section. This enables us to evaluate the functions of hydraulic vibration isolators without using the large-scale testing equipment used in the past. , can be acquired for each control valve part, and the main function of the hydraulic vibration isolator can be evaluated from the combination of the acquired data.

(Example) The piston speed V and piston load F of the hydraulic vibration isolator 1 can be determined from the oil pressing area A of the piston 3 and the oil flow rate and pressure, which are known values.

Therefore, by inspecting the relationship between the oil flow rate and pressure in the cylinder 2 and the control valve 4, it is possible to inspect the functions (1) to (4) of the hydraulic vibration isolator 1 explained in the [Prior Art] section. Therefore, in this embodiment, the relationship between the piston displacement amount The hydraulic vibration isolator 1 was inspected to evaluate its functionality.

FIG. 1 is a diagram showing a unit function testing means for the cylinder 2, and is a diagram showing a state in which a hydraulic device 40 is attached to the hydraulic vibration isolator 1 shown in FIG. 6. In the figure, 41 and 42 are discharge pipes, 43 and 44 are stop valves 245 are switching valves, 4
6 is a pressure regulating valve, and 47 and 48 are pressure gauges. Note that the discharge pipes 41 and 42 of the hydraulic device 40 are connected to the cylinder 2.

In the above configuration, the stop valves 43 and 44 are opened and closed to pressurize the oil in the left chamber M and the right chamber N, which are partitioned by the piston 3. The opening and closing operations of the stop valves 43 and 44 include opening the stop valve 44 when the stop valve 43 is closed, closing the stop valve 44 when the stop valve 43 is open, and 43 and the stop valve 44 are both open. Here, for example, with the stop valve 43 closed and the stop valve 44 opened, oil from the hydraulic system 40 is supplied to the right chamber N formed in the cylinder 2. Then, the piston 3 moves a small distance ΔX to the left in the figure.
, and the pressure inside the left ventricle M increases by Δp1.

At this time, the movement amount ΔX1 of the piston 3 and the increased pressure Δp1 in the left chamber M have a relationship as shown in FIG. 2(a). Also, with the stop valve 43 open and the stop valve 44 closed, the cylinder 2
Oil is supplied from the hydraulic system 40 into the left chamber M formed inside. Then, the piston 3 moves by ΔX2, and the pressure inside the stone chamber N increases by Δp2.

Therefore, the moving distance ΔX of the piston 3 and the increased pressure Δ
Find p. At the same time, check for oil leaks from the gaskets of each part. The rigidity (modulus of elasticity) Kc of cylinder 2 is K
It can be determined as c-xl Δp+/Δx1. xl is the width of the left ventricle M. In this way, the withstand pressure of cylinder 2 and leakage can be reduced.

Stiffness (modulus of elasticity) Kc can be determined.

Next, the stop valves 43 and 44 are both opened, and oil is supplied from the hydraulic system 40 to the left ventricle M via the discharge pipe 41. Then, the pressure inside the left ventricle M gradually increases, and when a certain pressure is reached, the piston 3 starts moving. At this time, the increased pressure Δp3 in the left ventricle M and the pressure Δ in the right ventricle N
Find p4.

The thus obtained Δps, Δp4, and the moving distance Δx3 of the piston 3 have a relationship as shown in FIG. 2(b). Moreover, the operating resistance Ff of the piston 3 is Ff-1
It can be obtained as ΔI)3@Al−Δp4fistA21. Note that AI is the oil pressing area of the piston 3 in the left ventricle M, and A2 is the oil pressing area of the piston 3 in the right ventricle N.

FIG. 3 is a diagram showing the unit function testing means of the control valve section, and is a diagram showing a state in which the hydraulic device 40 is attached to the control valve 4 shown in FIG. 6. Note that the hydraulic system 40 shown in FIG. 1 includes a flow meter 51 shown in FIG.
52 and pressure gauge 53 are omitted. Discharge piping 41.4 to both end boats 54a, 54b of control valve 4
Connect 2. Oil is then supplied to the boat 54a with the stop valves 43, 44 open. At this time, the amount of oil supplied to the control valve 4 is gradually increased by the flow rate adjustment valve 51, and the pressures PI and P of the ports 54a and 54b are
2 and measure the flow rate Q.

If the Mj determination result is correct, a relationship as shown in FIG. 4 will be obtained. From the figure, poppet valve 21a.

Flow rate Q2 when 21b closes. The flow m Q 3 when the pressure P1 and the maximum working pressure Pmax are applied can be determined. By dividing Q2 and Q3 obtained in this manner by the areas A1 and A2 of the piston 3, the moving speed of the piston 3 can be calculated backwards.

Therefore, the elastic modulus (including both cylinder 2 expansion and oil compressibility) Kc and operating resistance Ff of the cylinder 2 are determined by a single function test of the cylinder 2, and the poppet is determined by a single function test of the control valve 4. valve 21
a, Flow rate of 21b.

Pressure characteristic values (flow ff1Q:+ when the poppet valves 21a, 21b close, pressure P1, flow mQ3 at the maximum working pressure, etc.) can be determined, and the above-mentioned functions of the hydraulic vibration isolator 1 ~ ■Be able to evaluate.

FIG. 5 is a flowchart for functional evaluation of a hydraulic vibration isolator. The operating resistance Ff of the piston 3 obtained in the above-mentioned unit function test is compared with the specified value FIL of the operating resistance of the piston 3 using the comparator 61. Evaluate and determine the operating resistance Fl) when the In addition, the comparator 62 compares the moving speed v2 of the piston 3 obtained by multiplying the flow ff1Q2 obtained in the individual function test of the control valve 4 by the cylinder dimension and the specified value V2L of the moving speed of the piston 3 when the poppet valve closes. In comparison, the function (2) described above (the piston 3 rises within the specified speed range,
The moving speed V2) of the piston 3 when the piston 4b is closed is evaluated and determined. In addition, a comparator is used to compare the piston speed V3 obtained by multiplying the flow mQ3 obtained by the individual function test of the control valve 4 by the cylinder dimensions and the specified value V3L of the movement speed of the piston 3 when the maximum load is applied to the piston. 63, the function of ■ mentioned above (maximum load Fmax on piston 3)
The moving speed V3) of the piston 3 when it acts is evaluated and determined. In addition, the elastic modulus Kc of the cylinder 2 obtained from the individual function test of the cylinder 2 and the control valve 4, the flow rate Q when the poppet valve closes: +, the maximum working pressure Pmax
and current IQ3. Compare the moving distance Xs of the piston 3 obtained by simulation analysis using the cylinder dimension A, the width x1 of the left ventricle M formed in the cylinder 2, and the width X2 in the right ventricle N with the specified value XSL of this moving distance. 64 to evaluate and determine the function (2) described above (the amount of movement MXS of the piston 3 until the piston 3 rapidly moves and reaches the maximum load amount ax).

As described above, according to this embodiment, the individual functions of the cylinder 2 and the control valve 4 are inspected using the hydraulic system 40, and the function given to the hydraulic vibration isolator is determined based on the function data obtained from this individual function inspection. Since comparisons are made with specified values, various characteristics and maintenance or deterioration status of the hydraulic vibration isolator can be evaluated and judged, and the function inspection of the hydraulic vibration isolator can be performed by simply using the hydraulic device 40. So,
Inspections can be easily carried out even in relatively narrow spaces.

〔Effect of the invention〕

According to the present invention, since the hydraulic vibration isolator is divided into parts and the functions of the cylinder section and the control valve section are performed individually, the required functional characteristics of the hydraulic vibration isolator can be checked without using a large-scale inspection device. It is possible to provide a functional inspection method for a hydraulic vibration isolator that can perform evaluation and judgment, and can also sufficiently handle inspections of narrow places such as inside a plant.

[Brief explanation of the drawing]

Figures 1 to 5 are diagrams showing one embodiment of the present invention. Figure 1 is a diagram showing a unit function test means of the cylinder part, and Figure 2 is a diagram showing the relationship between the amount of movement of the piston and the pressure inside the cylinder. Figure 3 is a diagram showing the unit function test means of the control valve part, Figure 4 is a diagram showing the relationship between flow rate, pressure and time when the poppet valve is closed, and Figure 5 is a diagram showing the hydraulic vibration isolation system. FIG. 2 is a flowchart for evaluating the function of a device. Figure 6 is a sectional view showing the configuration of a hydraulic vibration isolator, Figure 7 is a perspective view of a conventional hydraulic vibration isolator function inspection device, and Figures 8 (a) to (c) are main parts of a hydraulic vibration isolator. FIG. 3 is a diagram for explaining functions. 1... Hydraulic vibration isolator, 2... Cylinder, 3... Papiston, 4... Control valve, 14a, 14b
... Hohesoto valve, 40... Hydraulic system. Applicant's agent Patent attorney Takehiko Suzue Figure 1 (a) (b) Figure 2

Claims (1)

[Claims] The cylinder part and the control valve part of the hydraulic vibration isolator are divided, oil is supplied to the divided cylinder part, and the elastic modulus and operating resistance are determined from the pressure in the cylinder chamber and the moving distance of the piston. Pressure and flow characteristic values are obtained by supplying oil to the divided control valve parts and measuring the flow rate, and then the pressure and flow characteristic values of the cylinder part obtained by the individual function test of the cylinder part and control valve part are calculated. A hydraulic vibration isolator characterized in that the overall function of the hydraulic vibration isolator is inspected and evaluated using elastic modulus, operating resistance, pressure of the control valve section, flow rate characteristic values, and dimensions of the cylinder section. How to test the function of the device.